CN1719034A - Compression system, multi-cylinder rotary compressor and refrigeration equipment using it - Google Patents

Abstract

The present invention is intended to avoid the generation of a collision noise of a second vane in a compression system having a multi-cylinder rotary compressor which can be used by switching between a first operation mode in which both rotary compression elements perform compression work and a second operation mode in which substantially only the first rotary compression element performs compression work, and is characterized in that, when switching from the second operation mode to the first operation mode, an intermediate pressure between a suction-side pressure and a discharge-side pressure of both rotary compression elements is applied after a discharge-side pressure of both rotary compression elements is applied as a back pressure of the second vane and, when switching from the first operation mode to the second operation mode, a back pressure of the second vane is applied after the inflow of refrigerant into the second cylinder is shut off by a valve device, the suction side pressures of the two rotary compression elements are applied.

Description

Compression system, multi-cylinder rotary compressor and refrigeration equipment using it

technical field

The present invention relates to a compression system, a multi-cylinder rotary compressor constituting it, and a refrigeration device using the same.

technical background

Conventionally, such a compression system is constituted by a multi-cylinder rotary compressor, a control device for controlling the operation of the multi-cylinder rotary compressor, and the like. The multi-cylinder rotary compressor, for example, a two-cylinder rotary compressor having first and second rotary compression elements accommodates a drive element and the first and second rotary compression elements driven by the rotary shaft of the drive element in a sealed container. become. The first and second rotary compression elements are composed of first and second cylinders, first and second rollers, and first and second blades, and the first and second rollers are fitted in a groove formed on a rotating shaft. The eccentric portion rotates eccentrically in each cylinder, and the first and second vanes come into contact with the first and second cylinders to divide the interior of each cylinder into a low-pressure chamber side and a high-pressure chamber side, respectively. In addition, the first and second blades are always biased toward the first and second rollers by the spring member, respectively.

In this way, when the driving element is driven by the above-mentioned control device, the low-pressure refrigerant gas is sucked into the low-pressure chamber side of each cylinder of the first and second rotary compression elements from the suction passage, and is respectively controlled by the action of each roller and each vane. Compressed, high-temperature and high-pressure refrigerant gas is discharged from the high-pressure chamber side of each cylinder to the discharge muffler chamber through the discharge port, then discharged into the sealed container, and then discharged to the outside (for example, refer to JP-A 5- Bulletin No. 99172).

In a compression system having such a multi-cylinder rotary compressor, in a low-capacity region such as light load or low-speed rotation, when the compression operation is performed by the first and second cylinders, it is necessary to suck the energy of the two cylinders. Refrigerant gas is compressed by removing the volumetric amount, so this amount is passed through the control device, and the rotation speed of the drive element is reduced for operation. However, if the number of rotations decreases too much, the efficiency of the driving element decreases, and at the same time, the leakage loss increases, resulting in a problem that the operating efficiency significantly decreases.

Therefore, in view of this problem, a compression system capable of switching between one-cylinder operation and two-cylinder operation according to capacity has been developed. That is, removing any one of the spring members that urge the first and second blades of the multi-cylinder rotary compressor to the first and second rollers, for example, removing the spring member that urges the second blades to the second roller, During the two-cylinder operation, the control device becomes a compression system in which the refrigerant pressure on the discharge side of the two rotating compression elements is applied as the back pressure of the second vane. Accordingly, the second vane is elastically pressed toward the second roller to complete compression work.

On the other hand, when switching from the above-mentioned two-cylinder operation to the one-cylinder operation, the control device provides a compression system in which the refrigerant pressure on the suction side of the two-rotation compression element is applied as the back pressure of the second vane. Since the suction pressure is a low pressure, the second vane cannot be spring-pressed toward the second roller. Therefore, substantially no compression work is performed in the second rotary compression element, and only the compression work of the refrigerant is performed in the first rotary compression element.

In this way, the amount of refrigerant gas to be compressed can be reduced by the one-cylinder operation in the small-capacity range, so that the number of revolutions can be increased. According to this, the operating efficiency of the drive element can be improved, and leakage loss can also be reduced.

Here, as described above, during the two-cylinder operation, among the second rotary compression elements without spring members, the discharge side pressure fluctuations of the two rotary compression elements that bias the second roller are large. The performance deteriorated because a clashing sound was generated between the second roller and the second vane, so the applicant tried to apply an intermediate pressure between the suction side pressure and the discharge side pressure of the two rotating compression elements as the back pressure of the second roller.

However, when the above-mentioned intermediate pressure is applied as the back pressure of the second vane, there arises a problem that the second vane follows the second roller when switching from the one-cylinder operation to the two-cylinder operation. It takes time, during which the second blade collides with the second roller, producing a clashing sound.

On the other hand, there is also a problem that, during one-cylinder operation, since the same suction-side pressure is applied to the pressure in the second cylinder and the back pressure of the second vane, there is a problem that when changing from two-cylinder operation to one-cylinder operation, During switching, the second blade is difficult to be drawn in from the second cylinder 40, and in the meantime, collides with the second roller, and still produces a collision sound.

In addition, although pressure pulses are generated on the back pressure side of the blades (the side opposite to the rollers) by the biasing action of the blades against the rollers during operation of the multi-cylinder rotary compressor, there is still a problem that there is no The second vane provided with the spring member deteriorates the followability of the second vane due to the pressure pulse, and collides with the second roller to generate a collision sound.

In addition, the discharge side pressure of the two rotary compression elements applied as the back pressure of the second vane fluctuates greatly. Even so, the followability of the second vane without the spring member is deteriorated, and there is a gap between the second roller and the second vane. clashing sounds.

Also, although the second roller becomes idling in the second rotary compression element during one-cylinder operation, there is still the following problem, that is, because at this time, the pressure in the second cylinder and the second vane The same suction side pressure is exerted by the back pressure. Due to the balance change of the two spaces, the second vane protrudes into the second cylinder and collides with the second roller, which still produces a conflict sound.

Contents of the invention

The present invention is an invention to solve the problems of the prior art. In a compression system with a multi-cylinder rotary compressor, the purpose of avoiding the collision sound of the second vane when switching the operation mode is to avoid the multi-cylinder rotary compressor. The machine only springs the first vane to the first roller through the spring member, and can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work. In the second operation mode, substantially only the first rotating compression element performs compression work.

The compression system of the present invention has a multi-cylinder rotary compressor, and the compressor accommodates a drive element and first and second rotary compression elements driven by the rotary shaft of the drive element in a sealed container. The element is composed of first and second cylinders, first and second rollers, and first and second blades. The first and second rollers are fitted with eccentric parts formed on the rotating shaft, and are respectively placed in the respective cylinders. Eccentric rotation; the first and second vanes are in contact with the first and second rollers, respectively dividing each cylinder into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the compressor only moves the first vane to the second roller through a spring component. One-roll spring compression can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work. In the above-mentioned second operation mode, only the first rotation The compression element performs compression work. When switching from the second operation mode to the first operation mode, after the discharge side pressure of the two rotation compression elements is applied as the back pressure of the second vane, the suction side of the two rotation compression elements is applied. Intermediate pressure between pressure and discharge side pressure.

In addition, the compression system of the present invention has a multi-cylinder rotary compressor that houses a drive element and first and second rotary compression elements driven by the rotation shaft of the drive element in an airtight container. The rotary compression element is composed of first and second cylinders, first and second rollers, and first and second vanes. The cylinder rotates eccentrically; the first and second blades are in contact with the first and second rollers, and each cylinder is divided into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the compressor only pushes the first blade Springing to the first roller can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work. In the above-mentioned second operation mode, only the first A rotary compression element performs compression work, and a valve device for controlling the flow of refrigerant to the second cylinder is provided. When switching from the first operation mode to the second operation mode, the valve device cuts off the flow to the second cylinder. After the refrigerant flows in, the suction side pressure of the two rotary compression elements is applied as the back pressure of the second vane.

In addition, the compression system of the present invention has a multi-cylinder rotary compressor that houses a drive element and first and second rotary compression elements driven by the rotation shaft of the drive element in an airtight container. The rotary compression element is composed of first and second cylinders, first and second rollers, and first and second vanes. The cylinder rotates eccentrically; the first and second blades are in contact with the first and second rollers, and each cylinder is divided into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the compressor only pushes the first blade Springing to the first roller can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work. In the above-mentioned second operation mode, only the first A rotary compression element performs compression work, and a valve device is provided for controlling the flow of refrigerant to the second cylinder. In the first mode of operation, the refrigerant flows into the second cylinder through the valve device, and acts as a second The back pressure of the vane, which applies an intermediate pressure between the suction side pressure and the discharge side pressure of the two rotary compression elements, prevents the refrigerant from flowing into the second cylinder through the valve device in the second operation mode, and, as the second The back pressure of the vane is the suction side pressure of the two rotary compression elements, and at the same time, when switching from the second operation mode to the first operation mode, as the back pressure of the second vane, the discharge side pressure of the two rotary compression elements is applied After that, the intermediate pressure between the suction side pressure and the discharge side pressure of the two rotary compression elements is applied. When switching from the first operation mode to the second operation mode, after the refrigerant inflow to the second cylinder is cut off by the valve device , as the back pressure of the second vane, exerts the suction side pressure of the two rotating compression elements.

In addition, in the compression system of the present invention, at the time of mode switching in each of the above inventions, the drive element of the multi-cylinder rotary compressor is rotated at a low speed so that the compression ratio of the first rotary compression element or the two rotary compression elements is 3.0 or less .

According to this invention, when switching from the second operation mode to the above-mentioned first operation mode, since the suction side pressure of the two rotation compression elements is applied after the discharge side pressure of the two rotation compression elements is applied as the back pressure of the second vane The intermediate pressure between the discharge side pressure and the discharge side pressure, so the second blade can be moved to the second roller side early by the discharge side pressure of the two rotating compression elements. According to this, it is possible to improve the followability of the second vane when switching from the second operation mode to the first operation mode, thereby improving the operation efficiency, and avoiding the generation of the collision sound of the second vane.

In addition, after the discharge side pressure of the two rotating compression elements is applied to the second blade, and the second blade follows the second roller, by applying the intermediate pressure between the suction side pressure and the discharge side pressure of the two rotating compression elements, the Compared with the case where the back pressure of the two vanes is applied to the discharge side pressure of the two rotary compression elements, since the pressure fluctuation is significantly reduced, the followability of the second vane of the multi-cylinder rotary compressor after switching the operation mode is improved, and the The compression efficiency of the second rotary compression element is improved, and, in the first operation mode, generation of collision sound of the second roller and the second vane can be avoided in advance.

In addition, when switching from the first operation mode to the second operation mode, since the inflow of the refrigerant to the second cylinder is blocked by the valve device, the suction of the two rotary compression elements is applied as the back pressure of the second vane. Side pressure, so the pressure in the second cylinder can be higher than the back pressure of the second vane. Accordingly, the second vane of the multi-cylinder rotary compressor is pushed to the side opposite to the second roller by the pressure in the second cylinder, and since it will not come out of the second cylinder, it is possible to avoid conflict with the second roller. There is a problem that the rolls collide and a clashing sound is generated.

As described above, the performance and reliability of the multi-cylinder rotary compressor can be improved significantly, and the performance can be significantly improved as a compression system. The multi-cylinder rotary compressor can be used by switching between the first operation mode and the second operation mode. , in the above-mentioned first operation mode, the first and second rotating compression elements perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element performs compression work.

Especially in the transition mode, if the driving element of the multi-cylinder rotary compressor is rotated at a low speed so that the compression ratio of the first rotary compression element or both rotary compression elements is 3.0 or less, the pressure fluctuation during the transition of the operation mode can be suppressed.

In addition, the refrigerating apparatus of the present invention uses the compression system of each of the above-mentioned inventions to constitute a refrigerant circuit.

According to this invention, since the refrigerant circuit of the refrigerating apparatus is constituted using the compression system of each of the above-mentioned inventions, it is also possible to improve the operating efficiency of the entire refrigerating apparatus.

In addition, the present invention is aimed at avoiding the generation of the second vane's clashing noise at startup in a compression system having a multi-cylinder rotary compressor in which only the first vane is biased toward the first roller by the spring member.

That is, the compression system of the present invention has a multi-cylinder rotary compressor, and the compressor accommodates a drive element and first and second rotary compression elements driven by the rotary shaft of the drive element in an airtight container. The two rotary compression elements are composed of first and second cylinders, first and second rollers, and first and second vanes. The first and second rollers are fitted with eccentric portions formed on the rotating shaft, respectively Each cylinder rotates eccentrically; the first and second vanes are in contact with the first and second rollers, respectively dividing each cylinder into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the compressor only divides the first The blade springs against the first roller, and when starting the multi-cylinder rotary compressor, it starts under the state that the suction side pressure of the two rotary compression elements is applied as the back pressure of the second blade, and at the same time, after starting, it acts as the back pressure of the second blade. pressure, apply the discharge side pressure of the two rotary compression elements, and then make the back pressure of the second vane an intermediate pressure between the suction side pressure and the discharge side pressure of the two rotary compression elements.

In addition, in the compression system of the present invention, in the above invention, the multi-cylinder rotary compressor can be used by switching between the first operation mode and the second operation mode, and in the first operation mode, the two rotary compression elements compress For work, in the above-mentioned second operation mode, only the first rotating compression element performs compression work in essence.

According to this invention, when the multi-cylinder rotary compressor is started, it is started in a state where the suction side pressure of both rotary compression elements is applied as the back pressure of the second vane, and the second rotary compression element is not substantially completed. Compression works.

In addition, after starting, the discharge side pressure of the two rotary compression elements is applied as the back pressure of the second vane, and the second vane is biased against the second roller to start the compression work in the second rotary compression element.

Furthermore, after applying the discharge side pressure of the two rotary compression elements as the back pressure of the second vane, by making the back pressure of the second vane an intermediate pressure between the suction side pressure and the discharge side pressure of the two rotary compression elements , Compared with the case where the discharge side pressure of both rotary compression elements is applied against the back pressure of the second vane, since the pressure fluctuation is significantly reduced, the second operation of the multi-cylinder rotary compressor in normal operation after startup is improved. The followability of the blades improves the compression efficiency of the second rotary compression element, and can prevent the generation of collision sounds between the second roller and the second blades.

In particular, the performance and reliability of the multi-cylinder rotary compressor can be improved, and the performance can be significantly improved as a compression system. The multi-cylinder rotary compressor can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the first and second rotating compression elements perform compression work, and in the above-mentioned second operation mode, substantially only the first rotating compression element performs compression work.

In addition, the refrigerating apparatus of the present invention uses the compression system of each of the above-mentioned inventions to constitute a refrigerant circuit.

According to this invention, the refrigerant circuit of the refrigerating apparatus is configured using the compression system of each of the above-mentioned inventions, and it is also possible to improve the operating efficiency of the entire refrigerating apparatus.

In addition, the present invention improves the followability of the second vane and avoids the occurrence of the second vane in the multi-cylinder rotary compressor in which only the first vane is biased toward the first roller by the spring member and the compression system having the multi-cylinder rotary compressor. For the purpose of clashing sound of two blades.

That is, in the multi-cylinder rotary compressor of the present invention, the drive element and the first and second rotary compression elements driven by the rotation shaft of the drive element are accommodated in the airtight container. The first and second rotary compression elements are driven by the first rotary compression element. One and the second cylinder, the first and the second roller, the first and the second vane respectively, the first and the second roller are fitted with the eccentric part formed on the rotating shaft, and rotate eccentrically in each cylinder respectively; The first and second vanes are in contact with the first and second rollers, respectively dividing each cylinder into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the multi-cylinder rotary compressor only moves the first vane to the second A roller spring has a back pressure chamber for exerting back pressure on the second vane and springing it toward the second roller, and the back pressure chamber is a muffler chamber having a predetermined volume.

In this invention, the back pressure chamber is used as a muffler chamber having a predetermined space volume, and the pressure pulse generated by the spring action of the second vane is reduced by this space volume, and the pressure pulse as the second blade can also be reduced. The pressure fluctuation of the discharge side pressure of the two rotating compression elements is exerted by the back pressure of the vane.

According to this, the followability of the second vane can be improved, the compression efficiency of the second rotary compression element can be improved, and the generation of collision sound between the second roller and the second vane can be avoided as much as possible.

In this way, the performance and reliability of the multi-cylinder rotary compressor can be improved through the above. The multi-cylinder rotary compressor can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the first And the second rotating compression element performs compression work. In the above-mentioned second operation mode, only the first rotating compression element actually performs compression work.

In addition, in the multi-cylinder rotary compressor of the present invention, the drive element and the first and second rotary compression elements driven by the rotation shaft of the drive element are accommodated in the airtight container. The first and second rotary compression elements are driven by the first rotary compression element. One and the second cylinder, the first and the second roller, the first and the second vane respectively, the first and the second roller are fitted with the eccentric part formed on the rotating shaft, and rotate eccentrically in each cylinder respectively; The first and second vanes are in contact with the first and second rollers, respectively dividing each cylinder into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the multi-cylinder rotary compressor only moves the first vane to the second A roller spring has a back pressure passage for applying back pressure to the second vane, and the cross-sectional area of the back pressure passage is greater than or equal to the average value of the surface areas of the second vanes exposed in the second cylinder.

In this invention, by making the cross-sectional area of the passage for back pressure greater than or equal to the average value of the surface areas of the second vanes exposed in the second cylinder, the passage for back pressure can be sufficiently ensured, reducing the impact on the second vane. It is also possible to reduce the pressure fluctuation of the refrigerant applied as the back pressure of the second blade due to the pressure pulse generated by the snap action.

According to this, the followability of the second vane can be improved, the compression efficiency of the second rotary compression element can be improved, and the generation of collision sound between the second roller and the second vane can be avoided as much as possible.

As described above, it is possible to improve the performance and reliability of the multi-cylinder rotary compressor in which only the first vane is biased toward the first roller by the spring member.

In addition, in the multi-cylinder rotary compressor of the present invention, the drive element and the first and second rotary compression elements driven by the rotation shaft of the drive element are accommodated in the airtight container. The first and second rotary compression elements are driven by the first And the second cylinder, the first and the second roller, the first and the second vane, the first and the second roller are fitted with the eccentric part formed on the rotating shaft, and rotate eccentrically in each cylinder respectively; The first and second vanes are in contact with the first and second rollers, respectively dividing each cylinder into a low-pressure chamber side and a high-pressure chamber side. At the same time, the multi-cylinder rotary compressor springs the first vane to the first roller through a spring member. , can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work. In the second operation mode, only the first rotation compression element performs compression To do work, set up an elastic pressing mechanism that presses the second blade to the second roller, so that the elastic force of the elastic pressing mechanism is less than or equal to the two rotating compression elements, or the suction side pressure of the first rotating compression element is applied as the back pressure of the second blade The elastic force of the situation.

In addition, in the multi-cylinder rotary compressor of the present invention, in the above-mentioned invention, a valve device for controlling flow of refrigerant to the second cylinder is provided, and in the first operation mode, the refrigerant passes through the valve device. Flow into the second cylinder, and as the back pressure of the second vane, apply the intermediate pressure between the suction side pressure and the discharge side pressure of the two rotating compression elements, or apply the discharge side pressure of the two rotating compression elements, in the second operating mode In this case, the refrigerant flow into the second cylinder is blocked by the valve device, and the suction side pressure of the two rotary compression elements is applied as the back pressure of the second vane.

In addition, the compression system of the present invention has a multi-cylinder rotary compressor that houses a drive element and first and second rotary compression elements driven by the rotation shaft of the drive element in an airtight container. The rotary compression element is composed of first and second cylinders, first and second rollers, and first and second vanes. The cylinder rotates eccentrically; the first and second blades are in contact with the first and second rollers, and each cylinder is divided into a low-pressure chamber side and a high-pressure chamber side, and at the same time, the compressor only pushes the first blade Springing to the first roller can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work. In the above-mentioned second operation mode, only the first A rotating compression element performs compression work, a valve device for controlling the flow of refrigerant to the second cylinder, and a spring pressing mechanism for springing the second vane to the second roller, so that the spring force of the spring pressing mechanism is less than or equal to two The rotary compression element, or the spring force in the case where the suction side pressure of the first rotary compression element is applied as the back pressure of the second vane, and at the same time, in the first operation mode, the refrigerant flows into the second cylinder through the valve device , and as the back pressure of the second vane, apply the intermediate pressure between the suction side pressure and the discharge side pressure of the two rotating compression elements, or apply the discharge side pressure of the two rotating compression elements, in the second operation mode, through the valve The device cuts off the refrigerant flow into the second cylinder, and applies the suction side pressure of the two rotary compression elements as the back pressure of the second vane.

In addition, in the multi-cylinder rotary compressor of the present invention, the drive element and the first and second rotary compression elements driven by the rotation shaft of the drive element are accommodated in the airtight container. The first and second rotary compression elements are driven by the first And the second cylinder, the first and the second roller, the first and the second vane, the first and the second roller are fitted with the eccentric part formed on the rotating shaft, and rotate eccentrically in each cylinder respectively; The first and second vanes are in contact with the first and second rollers, respectively dividing each cylinder into a low-pressure chamber side and a high-pressure chamber side. At the same time, the multi-cylinder rotary compressor springs the first vane to the first roller through a spring member. , can be used by switching between the first operation mode and the second operation mode. In the above-mentioned first operation mode, the two rotating compression elements perform compression work, and in the above-mentioned second operation mode, substantially only the first rotation compression element performs Compression work, on the opposite side of the second roller side of the second blade, a weak spring for tensile load is set, so that the tensile force of the weak spring is less than or equal to the two rotating compression elements, or the suction of the first rotating compression element The spring force when the side pressure is applied as the back pressure of the second vane.

According to this invention, for example, the followability of the second vane in the first operation mode can be improved by the biasing mechanism constituted by a weak spring or the like. Specifically, in the first operation mode, between the suction-side pressure and the discharge-side pressure of the two rotating compression elements applied as the back pressure of the second vane, the refrigerant flows into the second cylinder through the valve means. When the intermediate pressure is applied, or the discharge side pressure of the two rotating compression elements is applied, the spring pressing mechanism can avoid the problem of deterioration of the followability of the second vane due to the pressure pulse of the intermediate pressure or the discharge side pressure. .

In addition, by making the biasing force of the biasing mechanism less than or equal to the biasing force of the two rotary compression elements, or the suction side pressure of the first rotary compression element as the back pressure of the second vane, in the second operation mode, the valve The device cuts off the flow of refrigerant into the second cylinder, and, as the back pressure of the second vane, applies the suction side pressure of the two rotating compression elements, and can spring the second vane to the back pressure side by the pressure in the second cylinder The springing force is greater than the suction side pressure and the springing force of the springing mechanism for springing the second blade to the second roller.

Accordingly, even if the biasing mechanism for biasing the second vane against the second roller is provided, in the second operation mode, even if the biasing member is provided, due to the pressure in the second cylinder, The second vane of the multi-cylinder rotary compressor will not come out of the second cylinder, so the problem of collision with the second roller and the generation of collision noise can be avoided beforehand.

As described above, the performance and reliability of the multi-cylinder rotary compressor can be improved, and the performance can be significantly improved as a compression system. The multi-cylinder rotary compressor can be used by switching between the first operation mode and the second operation mode. , in the above-mentioned first operation mode, the first and second rotating compression elements perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element performs compression work.

In addition, due to the weak spring for tension load, in the second operation mode, the second vane will not come out of the second cylinder due to the tension force of the weak spring, so it is possible to avoid collision with the second roller beforehand. , the problem of conflicting sounds.

Description of drawings

Fig. 1 is a longitudinal sectional side view of a multi-cylinder rotary compressor of a compression system according to an embodiment of the present invention.

Fig. 2 is another longitudinal sectional side view of the multi-cylinder rotary compressor of Fig. 1 .

Fig. 3 is a diagram of a refrigerant circuit of an air conditioner using a compression system according to an embodiment of the present invention.

Fig. 4 is a diagram showing a switching operation from the second operation mode to the first operation mode of the multi-cylinder rotary compressor of Fig. 1 .

Fig. 5 is a longitudinal sectional side view of a multi-cylinder rotary compressor of a compression system according to Embodiment 2 of the present invention.

Fig. 6 is a diagram showing a switching operation from the first operation mode to the second operation mode of the multi-cylinder rotary compressor of Fig. 5 .

Fig. 7 is a diagram showing a switching operation from the second operation mode to the first operation mode of the multi-cylinder rotary compressor of Fig. 5 .

Fig. 8 is a longitudinal sectional side view of a multi-cylinder rotary compressor of a compression system according to Embodiment 3 of the present invention.

9 is a diagram showing the operation of the solenoid valves in the second operation mode of the multi-cylinder rotary compressor of the compression system according to Embodiment 5 of the present invention.

Fig. 10 is a longitudinal sectional side view of a multi-cylinder rotary compressor according to Embodiment 7 of the present invention.

11 is a top sectional view of the second cylinder of Embodiment 8 of the multi-cylinder rotary compressor.

Fig. 12 is a top cross-sectional view of the second cylinder in the case where the second roller of the second rotary compression element of Embodiment 11 of the multi-cylinder rotary compressor of the present invention is located at the top dead center.

Fig. 13 is a top cross-sectional view of the second cylinder in the case where the second roller of the second rotary compression element of the eleventh embodiment of the multi-cylinder rotary compressor of the present invention is located at the bottom dead center.

Fig. 14 is a longitudinal sectional side view of a multi-cylinder rotary compressor according to Embodiment 14 of the present invention.

Fig. 15 is another longitudinal sectional side view of the multi-cylinder rotary compressor of Fig. 14 .

16 is a top cross-sectional view of the second cylinder of the second rotary compression element of the multi-cylinder rotary compressor of FIG. 14 .

Fig. 17 is a diagram of a refrigerant circuit of an air conditioner using a compression system according to Embodiment 14 of the present invention.

FIG. 18 is a diagram showing the flow of refrigerant in the first operation mode of the multi-cylinder rotary compressor of Embodiment 14. FIG.

FIG. 19 is a diagram showing the flow of refrigerant in the second operation mode of the multi-cylinder rotary compressor of Embodiment 14. FIG.

Fig. 20 is a diagram showing the flow of refrigerant in the first operation mode of the multi-cylinder rotary compressor in another embodiment.

Fig. 21 is a longitudinal sectional side view of a multi-cylinder rotary compressor according to Embodiment 15 of the present invention.

Fig. 22 is another longitudinal sectional side view of the multi-cylinder rotary compressor of Fig. 21 .

FIG. 23 is an enlarged view of the weak spring of the second rotary compression element of the multi-cylinder rotary compressor of FIG. 21 .

FIG. 24 is an enlarged view of the weak spring of the second rotary compression element of another embodiment of the multi-cylinder rotary compressor of FIG. 23 .

FIG. 25 is an enlarged view of the weak spring of the second rotary compression element of another embodiment of the multi-cylinder rotary compressor of FIG. 23 .

Detailed ways

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

(Example 1)

1 is a longitudinal sectional side view of an internal high-pressure type rotary compressor 10 having first and second rotary compression elements, which is an embodiment of a multi-cylinder rotary compressor as a compression system CS of the present invention, and FIG. 2 is a A vertical side view of the rotary compressor 10 in FIG. 1 is shown (a cross section different from that in FIG. 1 is shown). In addition, the compression system CS of the present embodiment is a part of the refrigerant circuit constituting an air conditioner as a refrigeration device for air conditioning a room.

In each figure, the rotary compressor 10 of the embodiment is an internal high-pressure type rotary compressor, and a motor element 14 and a rotary compression mechanism part 18 are accommodated in a vertical cylindrical hermetic container 12 made of steel plate. The electric element 14 is a driving element disposed on the upper side of the inner space of the airtight container 12, and the rotary compression mechanism part 18 is composed of first and second rotary compression elements 32, 34. The compression elements 32 and 34 are arranged below the electric element 14 and are driven by the rotation shaft 16 of the electric element 14 .

The airtight container 12 uses the bottom as an oil sump, and is composed of a container body 12A accommodating the electric element 14 and the rotary compression mechanism 18, and a substantially bowl-shaped end cap (cover body) 12B that closes the upper opening of the container body 12A, and A circular mounting hole 12D is formed on the upper surface of the end cover 12B, and a terminal (wiring is omitted) 20 for supplying electric power to the electric element 14 is mounted in the mounting hole 12D.

In addition, a refrigerant discharge pipe 96 described later is attached to the end cover 12B, and one end of the refrigerant introduction pipe 96 communicates with the inside of the sealed container 12 . Furthermore, a mount 11 for attachment is provided at the bottom of the airtight container 12 .

The electric element 14 is formed by a stator 22 welded and fixed annularly along the inner peripheral surface of the upper space of the airtight container 12, and inside the stator 22, a plurality of rotors 24 inserted at intervals are arranged, and the rotor 24 is fixed. On the axis of rotation 16 extending vertically through the center.

The stator 22 has a laminated body 26 in which ring-shaped electromagnetic steel sheets are laminated, and stator coils 28 wound around the teeth of the laminated body 26 by serial winding (concentric winding). In addition, the rotor 24 is also formed of a laminated body 30 of electrical steel sheets, similarly to the stator 22 .

Between the first rotary compression element 32 and the second rotary compression element 34, an intermediate partition 36 is interposed. That is, the first rotary compression element 32 and the second rotary compression element 34 are composed of the intermediate partition plate 36 , the first and second cylinders 38 , 40 , the first and second rollers 46 , 48 , the first and second blades 50 , 52. The upper support member 54 and the lower support member 56 are composed of the first and second cylinders 38, 40 arranged above and below the intermediate partition 36; the first and second rollers 46, 48 are arranged on the first and second There is a phase difference of 180 degrees in the two cylinders 38, 40, which are fitted on the upper and lower eccentric parts 42, 44 arranged on the rotating shaft 16, and rotate eccentrically in each cylinder 38, 40 respectively; the first and second vanes 50 , 52 are in contact with the first and second rollers 46, 48, and each cylinder 38, 40 is divided into a low-pressure chamber side and a high-pressure chamber side; The side opening surface and the lower opening surface of the second cylinder 40 serve as a support member also serving as a bearing for the rotary shaft 16 .

On the above-mentioned first and second cylinders 38, 40, there are provided suction passages 58, 60 communicating with the insides of the first and second cylinders 38, 40 respectively, and the suction passages 58, 60 are respectively connected with Refrigerant inlet pipes 92,94.

In addition, a discharge muffler chamber 62 is provided on the upper side of the upper support member 54 , and the refrigerant gas compressed by the first rotary compression element 32 is discharged into the discharge muffler chamber 62 . The discharge muffler chamber 62 is formed in a substantially bowl-shaped cover member 63 having a hole in the center through which the rotating shaft 16 and the upper supporting member 54 also serving as a bearing for the rotating shaft 16 pass, and covers the upper supporting member 54. The electric element 14 side (upper side). Then, above the cover member 63 , the electric element 14 is provided at a predetermined interval from the cover member 63 .

On the lower supporting member 56, a discharge muffler chamber 64 formed by closing a recess formed on the lower side of the lower supporting member 56 with a cover serving as a wall is provided. That is, the discharge muffling chamber 64 is closed by the lower cover 68 that partitions the discharge muffling chamber 64 .

A guide groove 70 for accommodating the first vane 50 is formed in the first cylinder 38, and an accommodating portion for accommodating a spring 74 as a spring member is formed outside the guide groove 70, that is, on the back side of the first vane 50. 70A. The spring 74 is in contact with the rear end of the first vane 50 and always biases the first vane 50 toward the first roller 46 side. In addition, to the housing portion 70A, for example, a discharge-side pressure (high pressure) described later that is also introduced into the airtight container 12 is applied as the back pressure of the first vane 50 . In this way, the accommodating portion 70A is opened on the guide groove 70 side and the airtight container 12 (container body 12A) side, and on the airtight container 12 side of the spring 74 accommodated in the accommodating portion 70A, a metal plug 137 is provided to prevent the spring 74 from Shedding effect.

In addition, a guide groove 72 for accommodating the second vane 52 is formed in the second cylinder 40 , and a back pressure chamber 72A is formed outside the guide groove 72 , that is, on the back side of the second vane 52 . The back pressure chamber 72A is opened on the side of the guide groove 72 and the side of the sealed container 12 , and the opening on the side of the sealed container 12 is connected to a pipe 75 which will be described later, and is sealed in the sealed container 12 .

On the side of the container main body 12A of the airtight container 12, at positions corresponding to the suction passages 58, 60 of the first cylinder 38 and the second cylinder 40, sliding sleeves 141 and 142 are welded and fixed, respectively. These sliding sleeves 141 and 142 adjoin one another above and below.

Thus, in the sliding sleeve 141 , one end of the refrigerant introduction pipe 92 for introducing refrigerant gas into the first cylinder 38 is inserted and connected, and one end of the refrigerant introduction pipe 92 communicates with the suction passage 58 of the upper cylinder 38 . . The other end of the refrigerant introduction pipe 92 opens into the accumulator 146 .

One end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the second cylinder 40 is inserted into the sliding sleeve 142 , and one end of the refrigerant introduction pipe 94 communicates with the suction passage 60 of the second cylinder 40 . The other end of the refrigerant introduction pipe 94 is opened in the pressure accumulator 146 similarly to the refrigerant introduction pipe 92 described above.

The accumulator 146 is a tank for separating the gas and liquid of the sucked refrigerant, and is attached to the upper side surface of the container main body 12A of the airtight container 12 through the bracket 147 . In this way, the refrigerant introduction pipe 92 and the refrigerant introduction pipe 94 are inserted into the pressure accumulator 146 from the bottom, and the openings at the other ends are positioned above the inside of the pressure accumulator 146 . In addition, one end of the refrigerant pipe 100 is inserted into the upper portion of the accumulator 146 .

In addition, the discharge muffler chamber 64 communicates with the discharge muffler chamber 62 through a communication path 120 that passes through the upper and lower support members 54, 56, the first and second cylinders 38, 40 and the intermediate space in the axial direction (vertical direction). plate 36. Thus, the high-temperature and high-pressure refrigerant gas compressed by the second rotary compression element 34 and discharged to the discharge muffler chamber 64 is discharged to the discharge muffler chamber 62 through the communication path 120 , and the high-temperature refrigerant gas compressed by the first rotary compression element 32 The high-pressure refrigerant gas merges.

In addition, the discharge muffler chamber 62 communicates with the inside of the airtight container 12 through a hole (not shown) penetrating the cover member 63, and is compressed by the first rotary compression element 32 and the second rotary compression element 34 through the hole, and is discharged into the discharge muffler chamber. The high-pressure refrigerant gas at 62 is discharged into the sealed container 12 .

Here, a refrigerant pipe 101 is connected in communication with an intermediate portion of the refrigerant pipe 100 , and this pipe is connected to the above-mentioned pipe 75 through a solenoid valve 105 . In addition, a refrigerant pipe 102 is also communicated to a midway portion of the refrigerant discharge pipe 96 , and is connected to the pipe 75 through a solenoid valve 106 similarly to the refrigerant pipe 101 . In addition, the opening and closing of these solenoid valves 105 and 106 are individually controlled by a controller 210 described later. That is, when the valve device 105 is opened and the valve device 106 is closed by the controller 210, the refrigerant pipe 101 and the pipe 75 communicate. Accordingly, part of the suction-side refrigerant of both rotary compression elements 32 and 34 that flows into the accumulator 146 and flows into the refrigerant pipe 100 enters the refrigerant pipe 101 and flows from the pipe 75 into the back pressure chamber 72A. Accordingly, the suction-side pressure of both rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 .

In addition, when the valve device 105 is closed and the valve device 106 is opened by the controller 210, the refrigerant discharge pipe 96 and the pipe 75 communicate with each other. Accordingly, a part of the discharge-side refrigerant of both rotary compression elements 32 and 34 discharged from the sealed container 12 and passed through the refrigerant discharge pipe 96 flows into the back pressure chamber 72A from the pipe 75 through the refrigerant pipe 102 . Accordingly, the discharge side pressures of both rotary compression elements 32 , 34 are applied as the back pressure of the second vane 52 .

Here, the above-mentioned controller 210 is a member constituting a part of the compression system CS of the present invention, and controls the rotation speed of the electric element 14 of the rotary compressor 10 . In addition, as described above, the opening and closing of the electromagnetic valve 105 of the refrigerant piping 101 and the electromagnetic valve 106 of the refrigerant piping 102 are controlled.

Next, FIG. 3 is a diagram showing a refrigerant circuit of the above air conditioner configured using the compression system CS. That is, the compression system CS of the embodiment constitutes a part of the refrigerant circuit of the air conditioner shown in FIG. 3 , and is composed of the above-mentioned rotary compressor 10 , controller 210 and the like. The refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the outdoor side heat exchanger 152 . The controller 210, the rotary compressor 10, and the outdoor side heat exchanger 152 are installed in an unillustrated outdoor unit of the air conditioner. A pipe connected to the outlet of the outdoor heat exchanger 152 is connected to an expansion valve 154 as a pressure reducing mechanism, and a pipe leading out of the expansion valve 154 is connected to an indoor heat exchanger 156 . The expansion valve 154 and the indoor side heat exchanger 156 are provided in an unillustrated indoor unit of the air conditioner. Further, the refrigerant piping 100 of the rotary compressor 10 is connected to the outlet side of the indoor heat exchanger 156 .

In addition, HFC or HC refrigerants are used as refrigerants, and conventional machine oils such as mineral oil (petroleum), hydrocarbon oil, ether oil, and ester oil are used as lubricating oil.

With the above configuration, the operation of the rotary compressor 10 will be described next.

(1) The first operation mode (operation under normal load or high load)

First, the first operation mode in which the two rotating compression elements 32 and 34 perform compression work will be described. The controller 210 controls the number of revolutions of the electric element 14 of the rotary compressor 10 according to the operation command input from the controller on the side of the indoor unit (not shown) installed on the indoor unit. In this case, the controller 210 implements the first operation mode. In the first operation mode, the controller 210 closes the solenoid valve 105 of the refrigerant pipe 101 and the solenoid valve 106 of the refrigerant pipe 102 .

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . As described above, since the solenoid valve 105 of the refrigerant pipe 100 is closed, the refrigerant passing through the refrigerant pipe 100 does not flow into the pipe 75 but all flows into the accumulator 146 .

In this way, after the low-pressure refrigerant that has flowed into the pressure accumulator 146 is separated into gas and liquid, only the refrigerant gas enters the respective refrigerant discharge pipes 92 and 94 opened in the pressure accumulator 146 . The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 passes through the suction passage 58 and is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

On the other hand, the low-pressure refrigerant gas entering the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34 . The refrigerant gas sucked into the low-pressure chamber side of the second cylinder 40 is compressed by the operation of the second roller 48 and the second vane 52 .

At this time, as described above, since the solenoid valve 105 and the solenoid valve 106 are closed, the inside of the pipe 75 communicating with the back pressure chamber 72A of the second vane 52 is a sealed space. Furthermore, since a lot of refrigerant in the second cylinder 40 flows into the back pressure chamber 72A from between the second vane 52 and the housing portion 70A, the pressure in the back pressure chamber 72A of the second vane 52 becomes the pressure of the two rotating compression elements. 32 , 34 is an intermediate pressure between the suction side pressure and the discharge side pressure, and this intermediate pressure is applied as the back pressure of the second vane 52 . Due to this intermediate pressure, the second blade 52 can be sufficiently biased toward the second roller 48 without using a spring member.

In addition, conventionally, a high pressure as the discharge side pressure of both rotary compression elements 32 and 34 has been applied as the back pressure of the second vane 52, but in this case, there is a problem that the pressure due to the discharge side pressure pulsation Since the pulsation is large and there is no spring member, the followability of the second vane 52 is deteriorated, the compression efficiency is reduced, and a collision sound is generated between the second vane 52 and the second roller 48 .

However, by applying an intermediate pressure between the suction-side pressure and the discharge-side pressure of the two rotary compression elements 32, 34 as the back pressure of the second vane 52, the pressure pulsation becomes smaller compared to the case where the discharge-side pressure is applied as described above. Significantly reduced. In particular, in this embodiment, since the solenoid valves 105, 106 are closed to block the flow of the suction-side refrigerant and the discharge-side refrigerant of the two rotary compression elements 32, 34 from the pipe 75, better performance can be achieved. The pulsation of the back pressure of the second vane 52 is suppressed. Accordingly, the followability of the second vane 52 in the first operation mode is improved, and the compression efficiency of the second rotary compression element 34 is also improved.

In addition, the high-temperature and high-pressure refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 is discharged from the high-pressure chamber side of the second cylinder 40 to the discharge muffler chamber 64 through a discharge port (not shown). middle. The refrigerant gas discharged to the discharge muffling chamber 64 is discharged to the discharge muffling chamber 62 via the communication passage 120 , and joins the refrigerant gas compressed by the first rotary compression element 32 . In this way, the refrigerant gas merged is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Then, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed in the end cover 12B of the airtight container 12 , and flows into the outdoor side heat exchanger 152 . Here, the refrigerant gas releases heat, is depressurized by the expansion valve 154 , and flows into the indoor heat exchanger 156 . Here, the refrigerant evaporates, and at this time, absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

(2) Second operation mode (operation at light load)

Next, the second operation mode will be described. When the indoor load is light, the controller 210 switches to the second operation mode. This second operation mode is essentially a mode in which only the first rotating compression element 32 performs compression work, and is an operation mode in which the electric element 14 rotates at a low speed in the above-mentioned first operation mode when the indoor load is light. . In the small capacity region of the compression system CS, the compression work is performed by only the first rotating compression element 32, compared with the case where the compression work is performed by the first and second cylinders 38, 40, since the compression work can be reduced Therefore, the amount of refrigerant gas increases the rotation speed of the electric element 14 at light load, improves the operating efficiency of the electric element 14, and also makes it possible to reduce the leakage loss of the refrigerant.

In this case, the controller 210 opens the solenoid valve 105 of the refrigerant pipe 101 and closes the solenoid valve 106 of the refrigerant pipe 102 . Accordingly, the refrigerant pipe 101 communicates with the pipe 75, and the refrigerant on the suction side of the first rotary compression element 32 flows into the back pressure chamber 72A. Pressure is applied.

On the other hand, the controller 210 energizes the stator coil 28 of the electric element 14 through the above-mentioned terminals 20 and wiring not shown, and rotates the rotor 24 of the electric element 14 . By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . At this time, as described above, since the solenoid valve 105 of the refrigerant piping 101 is opened, part of the refrigerant passing through the suction side of the first rotary compression element 32 of the refrigerant piping 100 passes through the refrigerant piping 101 . The piping 75 flows into the back pressure chamber 72A. Accordingly, the back pressure chamber 72A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

Here, since the suction side pressure of both the rotary compression elements 32 and 34 applied as the back pressure of the second rotary compression element 34 is low pressure, the second vane 52 cannot be biased against the second roller 48 . Therefore, in the second rotary compression element 34, substantially no compression work is performed, and only the first rotary compression element 32 provided with the spring 74 completes the compression work of the refrigerant.

On the other hand, after the low-pressure refrigerant flowing into the accumulator 146 is gas-liquid separated here, only the refrigerant gas enters the refrigerant discharge pipe 92 opened in the accumulator 146 . The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become high-temperature and high-pressure refrigerant gas, which passes through the high-pressure chamber side of the first cylinder 38 The inside of the discharge port (not shown) is discharged into the discharge muffler chamber 62 . In this case, in the second operation mode, the discharge muffling chamber 62 functions as an expansion-type muffling chamber, and the discharge muffling chamber 64 functions as a resonating type muffling chamber, so that the first rotary compression element can be further reduced. 32 pressure pulses of compressed refrigerant. Accordingly, in the second operation mode in which substantially only the first rotary compression element 32 performs compression work, the noise reduction effect can be further improved.

The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 . Then, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cap 12B of the airtight container 12 , and flows into the outdoor-side heat exchanger 152 . Here, the refrigerant gas releases heat, is depressurized by the expansion valve 154 , and flows into the indoor heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

(3) Switching from the second operation mode to the first operation mode

On the other hand, the controller 210 switches from the second operation mode to the first operation mode when the room changes from the above-mentioned light load state to a normal load state or a high load state. Here, the switching operation from the second operation mode to the first operation mode will be described using FIG. 4 . In this case, the controller 210 controls to rotate the electric element 14 at a low speed (the number of revolutions is equal to or less than 50 Hz), so that the compression ratio of the two rotating compression elements 32 and 34 is equal to or less than 3.0. In addition, the controller 210 closes the electromagnetic valve 105 of the refrigerant piping 101 and opens the electromagnetic valve 106 of the refrigerant piping 102 ((2) in FIG. 4 ).

Accordingly, the refrigerant pipe 102 communicates with the pipe 75, and the refrigerant on the discharge side of the two rotary compression elements 32, 34 flows into the back pressure chamber 72A, and acts as a back pressure on the second vane 52 to apply to the two rotary compression elements 32, 34. discharge side pressure.

As the back pressure of the second vane 52, by applying the discharge side pressure of both rotary compression elements 32 and 34, the back pressure chamber 72A of the second vane 52 becomes significantly higher pressure than the inside of the second cylinder 40, so the second The blade 52 is pushed toward the second roller 48 side by the high pressure of the back pressure chamber 72A to follow it.

Here, as the back pressure of the second vane 52 at the time of switching, the second vane 52 can be sufficiently pushed out to the second roller 48 side by applying the discharge side pressure of both rotary compression elements. That is, when switching from the second operation mode to the first operation mode, as the back pressure of the second vane 52, as in the above-mentioned normal operation of the first operation mode, the pressure on the suction side of both rotary compression elements 32 and 34 is applied. In the case of an intermediate pressure between the discharge side pressure and the discharge side pressure, in this intermediate pressure, since the pressure difference between the second cylinder 40 and the back pressure chamber 72A is small, it takes a long time until the second vane 52 follows the second roller 48. Time, during which the second blade 52 collides with the second roller 48, there arises a problem that a collision sound occurs.

However, in the present invention, when switching from the second operation mode to the first operation mode, as the back pressure of the second vane 52, by applying the discharge side pressure of both rotary compression elements 32, 34, the discharge side pressure can be passed. , the second blade 52 is sufficiently biased toward the second roller 48 side, so that the second roller 48 follows early.

This improves the followability of the second vane 52 at the time of switching from the second operation mode to the first operation mode, improves operation efficiency, and prevents the generation of collision noise of the second vane 52 .

In addition, when switching, the controller 210 controls to make the electric element 14 rotate at a low speed (the number of revolutions is less than or equal to 50 Hz), so that the compression ratio of the two rotating compression elements 32 and 34 is less than or equal to 3.0. Accordingly, since pressure fluctuations can be suppressed, even when the discharge side pressure of both rotary compression elements 32 and 34 is applied as back pressure of the second rotary compression element 34 , it is hardly affected by the pressure fluctuations.

In addition, after the controller 210 applies the discharge side pressure of the two rotating compression elements 32 and 34 to the second vane 52 so that the second vane 52 follows the second roller 48, the suction side pressure and discharge pressure of the two rotating compression elements 32 and 34 are applied. The intermediate pressure between the side pressures ((3) in Figure 4). According to this, since the pressure fluctuation can be significantly reduced compared with the case where the discharge side pressure of the two rotary compression elements 32, 34 is applied to the back pressure of the second vane 52 as described above, it is possible to improve the in-running operation. The followability of the second vane 52 of the rotary compressor 10 after switching in the mode improves the compression efficiency of the second rotary compression element 34, and, in the first mode of operation, the generation of the second roller 48 and the second Clash of blades 52.

As described above, according to the present invention, it is possible to improve the performance and reliability of the compression system CS having the rotary compressor 10 that can be used by switching between the first operation mode and the second operation mode, In the above-mentioned first operation mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the compression system CS, the operating efficiency and performance of the air conditioner can be improved, and power consumption can be reduced.

(Example 2)

Next, another embodiment of the compression system CS of the present invention will be described. FIG. 5 is a longitudinal sectional side view showing an internal high-pressure type rotary compressor 110 having first and second rotary compression elements as a multi-cylinder rotary compressor of the compression system CS in this case. In addition, in FIG. 5 , components given the same symbols as those in FIGS. 1 to 4 are components that can produce the same or similar effects.

In FIG. 5 , 200 denotes a valve device, which is provided on the outlet side of the accumulator 146 in the middle of the refrigerant introduction pipe 94 on the inlet side of the hermetic container 12 . The solenoid valve 200 is a valve device for controlling the flow of refrigerant into the second cylinder 40, and is controlled by the above-mentioned controller 210 as a control device.

In addition, in this embodiment, as the refrigerant, HFC or HC refrigerant is used as in the above-mentioned embodiment, and as the engine oil of the lubricating oil, for example, mineral oil (petroleum), hydrocarbon oil, ether oil, Existing engine oils such as ester oil.

With the above configuration, the operation of the rotary compressor 110 will be described next.

(1) The first operation mode (operation under normal load or high load)

First, the first operation mode in which the two rotating compression elements 32 and 34 perform compression work will be described. The controller 210 controls the number of revolutions of the electric element 14 of the rotary compressor 110 according to the operation command input from the controller on the side of the indoor unit (not shown) installed on the indoor unit. In the case of , the controller 210 implements the first operation mode. In the first operation mode, the controller 210 opens the solenoid valve 200 of the refrigerant introduction pipe 94 and closes the solenoid valve 105 of the refrigerant pipe 101 and the solenoid valve 106 of the refrigerant pipe 102 .

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 110 into the accumulator 146 . As described above, since the solenoid valve 105 of the refrigerant pipe 101 is closed, the refrigerant passing through the refrigerant pipe 100 does not flow into the pipe 75 but all flows into the accumulator 146 .

In this way, after the low-pressure refrigerant that has flowed into the pressure accumulator 146 is separated into gas and liquid, only the refrigerant gas enters the respective refrigerant discharge pipes 92 and 94 opened in the pressure accumulator 146 . The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

On the other hand, the low-pressure refrigerant gas entering the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34 . The refrigerant gas sucked into the low-pressure chamber side of the second cylinder 40 is compressed by the operation of the second roller 48 and the second vane 52 .

At this time, as described above, since the solenoid valve 105 and the solenoid valve 106 are closed, the inside of the pipe 75 communicating with the back pressure chamber 72A of the second vane 52 is a sealed space. In addition, since a lot of refrigerant in the second cylinder 40 flows into the back pressure chamber 72A from between the second vane 52 and the housing portion 70A, the pressure in the back pressure chamber 72A of the second vane 52 becomes two-rotation compression. The intermediate pressure between the suction side pressure and the discharge side pressure of the elements 32 and 34 is applied as the back pressure of the second vane 52 . Due to this intermediate pressure, the second blade 52 can be sufficiently urged toward the second roller 48 without using a spring member.

Accordingly, similarly to the above-described embodiment, the followability of the second vane 52 in the first operation mode is improved, and the compression efficiency of the second rotary compression element 34 can also be improved.

In addition, the high-temperature and high-pressure refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 is discharged from the high-pressure chamber side of the second cylinder 40 to the discharge muffler chamber through a discharge port (not shown). 64 in. The refrigerant gas discharged to the discharge muffling chamber 64 is discharged to the discharge muffling chamber 62 via the communication passage 120 , and joins the refrigerant gas compressed by the first rotary compression element 32 . In this way, the refrigerant gas merged is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, the refrigerant gas releases heat, is decompressed by the expansion valve 154 , and flows into the indoor heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 110 is repeated.

(2) Switching from the first operation mode to the second operation mode

Next, the controller 210 switches from the first operation mode to the second operation mode when the room changes from the above-mentioned normal load or high load state to a light load state.

Here, the switching operation from the first operation mode to the second operation mode will be described using FIG. 6 . In addition, when the mode is switched, the controller 210 controls to make the electric element 14 rotate at a low speed, for example, make the rotation speed less than or equal to 50 Hz, so that the compression ratio of the two rotating compression elements 32 is less than or equal to 3.0.

First, the controller 210 closes the above-mentioned solenoid valve 200 to cut off the flow of refrigerant into the second cylinder 40 ((2) in FIG. 6 ). Accordingly, in the second rotary compression element 34, no compression work is performed. If the inflow of the refrigerant to the second cylinder 40 is blocked, the pressure in the second cylinder 40 becomes slightly higher than the pressure on the suction side of the two rotating compression elements 32 and 34 (because the second roller 48 rotates and , the high pressure in the airtight container 12 flows slightly from the gap of the second cylinder 40, etc., so the pressure in the second cylinder 40 is slightly higher than the pressure on the suction side).

In addition, since the pressure in the back pressure chamber 72A as described above becomes an intermediate pressure between the suction side pressure and the discharge side pressure of both rotary compression elements 32 and 34 in the above-mentioned first operation mode, the pressure in the second cylinder 40 The pressure and the pressure in the back pressure chamber 72A of the second vane 52 are substantially the same pressure.

Then, the controller 210 opens the solenoid valve 105 of the refrigerant piping 101 . In addition, the solenoid valve 106 of the refrigerant pipe 102 is in a closed state ((3) in FIG. 6 ). Accordingly, the refrigerant pipe 101 communicates with the pipe 75, and the refrigerant on the suction side of the first rotary compression element 32 flows into the back pressure chamber 72A, and the suction pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52. side pressure.

Accordingly, part of the suction-side refrigerant passing through the first rotary compression element 32 of the refrigerant pipe 100 flows from the refrigerant pipe 101 through the pipe 75 into the back pressure chamber 72A. Accordingly, the back pressure chamber 72A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

Since the second cylinder 40 has a pressure higher than the suction side pressure of the first rotary compression element 32 as described above, by applying the suction side pressure of the first rotary compression element 32 as the back pressure of the second vane 52, it can be made The pressure of the second cylinder 40 is higher than the back pressure chamber 72A of the second vane 52 . Therefore, the second vane 52 is pushed toward the back pressure chamber 72A side opposite to the second roller 48 by the pressure in the second cylinder 40 , and is accommodated in the guide groove 72 . Accordingly, when switching to the second operation mode, the second vane 52 can be early introduced from the second cylinder 40 and accommodated in the guide groove 72, so it is possible to prevent the second vane 52 from colliding with the second The collision of the rollers 48 causes a problem of collision sound.

(3) The second operation mode

Next, the operation of rotary compressor 110 in the second operation mode will be described. The low-pressure refrigerant flowing from the refrigerant piping 100 of the rotary compressor 110 into the accumulator 146 undergoes gas-liquid separation here, and only the refrigerant gas enters the refrigerant opening in the accumulator 146. discharge pipe 92. The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 . The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, the refrigerant gas releases heat, is decompressed by the expansion valve 154 , and flows into the indoor heat exchanger 156 . Here, the refrigerant evaporates, and at this time, absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Then, a cycle of discharging the refrigerant from the indoor heat exchanger 156 and sucking the refrigerant into the rotary compressor 110 is repeated.

In addition, in the second operation mode, the controller 210 operates in a state in which the inflow of the refrigerant into the second cylinder 40 is blocked by closing the above-mentioned solenoid valve 200 , and in the second operation mode, the second cylinder 40 The pressure of is kept in a state higher than the back pressure of the second vane 52 in this way. Therefore, the second vane 52 is pushed toward the back pressure chamber 72A side opposite to the second roller 48 by the pressure in the second cylinder 40 , and does not come out of the second cylinder 40 . Accordingly, during operation in the second operation mode, the problem that the second vane 52 comes out of the second cylinder 40 and collides with the second roller 48 to generate a collision sound can be avoided in advance.

(4) Switching from the second operation mode to the first operation mode

On the other hand, the controller 210 switches from the second operation mode to the first operation mode when the room changes from the above-mentioned light load state to a normal load state or a high load state. Here, the switching operation from the second operation mode to the first operation mode will be described using FIG. 7 . In this case, the controller 210 opens the electromagnetic valve 200 to allow the refrigerant to flow into the second cylinder 40, and at the same time closes the electromagnetic valve 105 of the refrigerant piping 101 and opens the electromagnetic valve 106 of the refrigerant piping 102 (Fig. (2)).

Accordingly, the refrigerant pipe 102 communicates with the pipe 75, and the refrigerant on the discharge side of the two rotary compression elements 32, 34 flows into the back pressure chamber 72A, and acts as a back pressure on the second vane 52 to apply to the two rotary compression elements 32, 34. discharge side pressure.

As the back pressure of the second vane 52 , by applying the discharge side pressure of the two rotary compression elements 32 , 34 , since the back pressure chamber of the second vane 52 is significantly high pressure compared with the inside of the second cylinder 40 , the second vane 52 This high pressure passing through the back pressure chamber 72A is pushed to the second roller 48 side to follow it.

Here, as the back pressure of the second vane 52 at the time of switching, the second vane 52 can be fully pushed out toward the second roller side by applying the discharge side pressure of both rotary compression elements. That is, when switching from the second operation mode to the first operation mode, as the back pressure of the second vane 52, as in the above-mentioned normal operation of the first operation mode, the pressure on the suction side of both rotary compression elements 32 and 34 is applied. In the case of an intermediate pressure between the discharge side pressure and the discharge side pressure, in this intermediate pressure, since the pressure difference between the second cylinder 40 and the back pressure chamber 72A is small, it takes a long time until the second vane 52 follows the second roller 48. During this time, the second blade 52 collides with the second roller 48, causing a problem that a clashing sound occurs.

However, in the present invention, when switching from the second operation mode to the first operation mode, as the back pressure of the second vane 52, by applying the discharge side pressure of both rotary compression elements 32, 34, the discharge side pressure can be passed. , the second blade 52 is sufficiently biased toward the second roller 48 side, so that the second roller 48 follows early.

This improves the followability of the second blades 52 when switching from the second operation mode to the first operation mode, improves operation efficiency, and prevents the occurrence of collision noise of the second blades 52 .

In addition, when switching, the controller 210 controls to make the electric element 14 rotate at a low speed (the number of revolutions is less than or equal to 50 Hz), so that the compression ratio of the two rotating compression elements 32 and 34 is less than or equal to 3.0. Accordingly, since pressure fluctuations can be suppressed, even when the discharge side pressure of both rotary compression elements 32 and 34 is applied as back pressure of the second rotary compression element 34 , it is hardly affected by the pressure fluctuations.

In addition, the controller 210 closes the electromagnetic valve 106 ((3) in FIG. Intermediate pressure between the suction side pressure and the discharge side pressure of the two rotary compression elements 32,34. Accordingly, since the pressure fluctuation is remarkably small compared with the case where the discharge side pressure of the two rotating compression elements 32, 34 is applied to the back pressure of the second vane as described above, it is possible to improve the operation mode. After switching, the followability of the second blades 52 of the rotary compressor 110 improves the compression efficiency of the second rotary compression element 34, and, in the first mode of operation, can prevent the generation of the second roller 48 and the second blade. 52 clashing sounds.

As described above, even in the present embodiment, it is possible to improve the performance and reliability of the compression system CS having the rotary compressor 110 which can switch between the first operation mode and the second operation mode. However, in the above-mentioned first operation mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the compression system CS, the operating efficiency and performance of the air conditioner can be improved, and power consumption can be reduced.

(Example 3)

In each of the above-described embodiments, as the refrigerant, HFC or HC-based refrigerants are used, and carbon dioxide and other refrigerants with a large high-pressure difference may also be used. For example, as the refrigerant, the A refrigerant that combines carbon dioxide and PAG (polyglycol). In this case, since the refrigerant compressed by the rotary compression elements 32 and 34 has a very high pressure, the discharge muffler chamber 62 is made to cover the upper part of the upper support member 54 with the cover member 63 as in the above-mentioned embodiments. If the side shape is different, the cover member 63 may be damaged due to the high pressure.

Therefore, if the shape of the discharge muffler chamber on the upper side of the upper support member 54 where the refrigerant compressed by the two rotary compression elements 32 and 34 merges is shaped as shown in FIG. 8 , pressure resistance can be ensured. That is, the discharge muffler chamber 162 in FIG. 8 is configured by forming a recessed portion on the upper side of the upper support member 54 and closing the recessed portion with an upper cover 66 as a cover. Accordingly, the present invention can be applied even in the case of containing a refrigerant having a large high-pressure difference such as carbon dioxide.

(Example 4)

Next, the operation when the compression system CS of the present invention is activated will be described. In addition, in this embodiment, the compression system CS, the multi-cylinder rotary compressor, and the refrigerant circuit used are the same as those of FIGS. 1 to 3 used in Embodiment 1. As shown in FIG. Therefore, descriptions of these configurations are omitted. In addition, the refrigerant used is also the same as in the above-mentioned embodiments. HFC or HC refrigerants are used, and as lubricating oil, existing oils such as mineral oil (petroleum), hydrocarbon oil, ether oil, ester oil, etc. are used. of motor oil.

Here, using FIG. 9, the operation|movement at the time of startup of the rotary compressor 10 of this embodiment is demonstrated. The controller 210 energizes the electric element 14 of the rotary compressor 10 in response to an input of an operation command from a controller on the side of the indoor unit (not shown) provided in the indoor unit. At this time, the controller 210 opens the solenoid valve 105 of the refrigerant pipe 101 and closes the solenoid valve 106 of the refrigerant pipe 102 while energizing the electric element 14 ((1) of FIG. 9 ). Accordingly, the refrigerant pipe 101 communicates with the pipe 75 , and the controller 210 controls the electric element of the rotary compressor 10 in a state where the suction side pressure of both the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 . 14 revolutions, start.

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . At this time, as described above, since the solenoid valve 105 of the refrigerant piping 101 is opened, part of the refrigerant passing through the suction side of the two rotary compression elements 32 and 34 of the refrigerant piping 100 is released from the refrigerant piping 101 It flows into the back pressure chamber 72A through the pipe 75 .

On the other hand, after the refrigerant that has flowed into the accumulator 146 is gas-liquid separated here, only the refrigerant gas enters the refrigerant introduction pipe 92 opened in the accumulator 146 . The refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 . The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Here, the inside of the refrigerant circuit is at a balanced pressure when the rotary compressor 10 is started. That is, since the rotary compressor 10 gradually balances the pressure after the previous stop of operation, and when a predetermined time elapses, the pressure in the refrigerant circuit becomes balanced, so when the pressure in the refrigerant circuit becomes balanced, start In the case of the rotary compressor 10, immediately after the rotary compressor 10 is started, the pressure of the refrigerant on the suction side of both the rotary compression elements 32 and 34 applied as the back pressure of the second vane 52 becomes a substantially balanced pressure. . Similarly, the pressure in the second cylinder 40 also becomes a substantially balanced pressure. Therefore, since the second vane 52 does not spring to the second roller 48, substantially no compression work is performed in the second rotary compression element 34, and only the first rotary compression element 32 provided with the spring 74 completes it. Compression of the refrigerant does work.

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, the refrigerant gas releases heat, is decompressed by the expansion valve 154 , and flows into the indoor heat exchanger 156 . The refrigerant flowing into the indoor side heat exchanger 156 evaporates there, absorbs heat from the air circulating in the room, exerts a cooling effect, and cools the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

On the other hand, when the rotary compressor 10 is started and a predetermined time elapses, a pressure difference between high and low is formed in the refrigerant circuit, and the state in the refrigerant circuit gradually stabilizes. In addition, at this time, although the pressure of the refrigerant on the suction side of both rotary compression elements 32 and 34 applied as the back pressure of the second vane 52 is a low pressure, the second vane 52 cannot be moved at this low pressure. Since it is biased toward the second roller 48, substantially only the first rotating compression element 32 completes the compression work in the same manner as above.

Here, when the rotary compressor 10 is started and a predetermined time elapses, the controller 210 closes the electromagnetic valve 105 of the refrigerant piping 101 and opens the electromagnetic valve 106 of the refrigerant piping 102 as shown in (2) of FIG. 9 . . Accordingly, the refrigerant piping 102 communicates with the piping 75 , and all of the refrigerant flowing through the refrigerant piping 100 of the rotary compressor 10 flows into the accumulator 146 .

In addition, part of the refrigerant discharged from the sealed container 12 to the refrigerant discharge pipe 96 flows from the refrigerant pipe 102 through the pipe 75 into the back pressure chamber 72A. Accordingly, the back pressure chamber 72A is the discharge side pressure of both the rotary compression elements 32 and 34 , and the discharge side pressure of both the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 .

As the back pressure of the second vane 52 , by applying the discharge side pressure of the two rotary compression elements 32 , 34 , since the back pressure chamber of the second vane 52 is significantly high pressure compared with the inside of the second cylinder 40 , the second vane 52 The high pressure passing through the back pressure chamber 72A is biased toward the second roller 48 to follow it, and the second rotary compression element 34 starts to perform compression work.

That is, only the refrigerant gas separated into gas and liquid in the accumulator 146 enters the refrigerant discharge pipes 92 and 94 opened in the accumulator 146 . The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 passes through the suction passage 58 as described above, and is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

On the other hand, the low-pressure refrigerant gas entering the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34 . The refrigerant gas sucked into the low-pressure chamber side of the second cylinder 40 is compressed by the operation of the second roller 48 and the second vane 52 .

Here, the controller 210 closes the solenoid valve 105, opens the solenoid valve 106, and applies the discharge side pressure of both the rotary compression elements 32 and 34 as the back pressure of the second vane 52, when the rotary compressor 10 is started. Next, since the pressure inside the refrigerant circuit is substantially balanced pressure immediately after startup as described above, even if the solenoid valve 106 is opened, the pressure applied as the back pressure of the second vane 52 is the balanced pressure, and the two It takes time to rotate the pressure on the discharge side of the compression elements 32 and 34 until it becomes high pressure. Therefore, the second vane 52 cannot be made to follow the second roller 48 until the discharge side pressure of both rotary compression elements 32, 34 rises to a certain level.

In addition, since the state in the refrigerant circuit is unstable immediately after starting, the pulsation of the pressure on the discharge side of both rotary compression elements 32, 34 also increases significantly. Therefore, in the case of starting with the discharge side pressures of both rotary compression elements 32, 34 being applied, there is a problem that the second vane 52 is swayed due to the pulsation of the discharge side pressures of both rotary compression elements 32, 34. The followability deteriorates, and the second blade 52 collides with the second roller 48 to generate a collision sound.

However, as in the present invention, by opening the electromagnetic valve 105 and applying the suction side pressure of the two rotary compression elements 32 and 34, the second vane 52 is not followed by the second roller 48, and the second rotary compression element 34 The compression work is substantially ineffective, and at the same time, in a stable state in the refrigerant circuit after starting, the discharge side pressure of the two rotating compression elements 32, 34 is applied, and the second vane 52 is pushed toward the second blade 52 by the discharge side pressure. The roller 48 is spring-pressed so that it follows the second roller 38, so that the above-mentioned problems can be avoided, and the followability of the second blade 52 can be improved when starting.

According to this, the operating efficiency of the rotary compressor 10 is improved, and the generation of the clashing sound of the second blades 52 can be avoided.

In addition, the high-temperature and high-pressure refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 is discharged into the discharge muffler chamber 64 from the high-pressure chamber side of the second cylinder 40 through an unillustrated discharge port. . The refrigerant gas discharged to the discharge muffling chamber 64 passes through the communication passage 120 , is discharged into the discharge muffling chamber 62 , and joins the refrigerant gas compressed by the first rotary compression element 32 . Then, the joined refrigerant gas is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . In addition, part of the refrigerant on the discharge side of the two rotary compression elements 32 and 34 passing through the refrigerant discharge pipe 96 flows into the back pressure chamber from the refrigerant pipe 102 through the pipe 75 because the solenoid valve 106 is opened as described above. 72A. Accordingly, the discharge side pressures of both rotary compression elements 32 , 34 are applied as the back pressure of the second vane 52 .

On the other hand, the refrigerant gas flowing into the outdoor side heat exchanger 152 releases heat there, is depressurized by the expansion valve 154 , and then flows into the indoor side heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

On the other hand, when the discharge side pressure of both rotary compression elements 32 and 34 is applied to make the second vane 52 follow the second roller 48, the controller 210 then closes the solenoid valve 106 ((3) in FIG. 9 ). Accordingly, the inside of the pipe 75 communicating with the back pressure chamber 72A of the second vane 52 becomes a closed space. Here, since a lot of refrigerant in the second cylinder 40 flows into the back pressure chamber 72A from between the second vane 52 and the housing portion 70A, the pressure in the back pressure chamber 72A of the second vane 52 becomes two-rotation compression. The intermediate pressure between the suction side pressure and the discharge side pressure of the elements 32 and 34 is in a state where the intermediate pressure is applied as the back pressure of the second vane 52 . Because of this intermediate pressure, the second blade 52 can be sufficiently urged against the second roller 48 without using a spring member.

Here, when the high pressure as the discharge-side pressure of the two rotary compression elements 32 and 34 described above continues to be applied as the back pressure of the second vane 52 , since the discharge-side pressure pulse is large and the second rotary compression element 34 Since there is no spring member, there arises a problem that the followability of the second vane 52 is deteriorated due to the pulse, the compression efficiency is lowered, and a collision sound is generated between the second vane 52 and the second roller 48 .

In addition, when starting the rotary compressor 10, as the back pressure of the second vane 52, high pressure as the discharge side pressure of the above-mentioned both rotary compression elements 32, 34 is not applied, and the back pressure chamber 72A is made to be the space between the two rotary compression elements 32, 34. In the case of an intermediate pressure between the suction side pressure and the discharge side pressure, there is a problem that, at this intermediate pressure, the pressure difference between the second cylinder 40 and the back pressure chamber 72A is small, so the second vane 52 It takes time to follow up to the second roller 48 , and during this time, the second blade 52 collides with the second roller 48 to generate a collision sound.

Therefore, by applying the discharge side pressure of both rotary compression elements 32 and 34 as the back pressure of the second vane 52, the second vane 52 is biased toward the second roller 48 side by the discharge side pressure so that it follows the second roller. After 48, make the back pressure chamber 72A an intermediate pressure between the suction side pressure and the discharge side pressure of the two rotary compression elements 32, 34, which can improve the followability of the second vane 52 and improve the compression efficiency of the second rotary compression element 34 , And, it is possible to avoid the collision sound of the second roller 48 and the second blade 52 at the time of startup.

In addition, in this embodiment, although the controller 210 controls to open the solenoid valve 105 and close the solenoid valve 106 while the electric element 14 is energized, it may also be performed before the rotary compressor 10 is started. 106 , for example, the controller 210 may open the solenoid valve 105 and close the solenoid valve 106 before energizing the electric element 14 .

Note that the first operation mode performed under normal load or high load and the second operation mode performed under light load operate in the same way as those in the first embodiment, and thus description thereof will be omitted.

(Example 5)

Furthermore, in the compression system CS of the present invention, it may also be on the outlet side of the pressure accumulator 146 as shown in FIG. The solenoid valve 200 is controlled by the controller 210 in the middle of the agent introduction pipe 94 .

In this way, the electromagnetic valve 200 is provided on the refrigerant introduction pipe 94, and the electromagnetic valve is closed at the time of starting to completely cut off the inflow of the refrigerant to the second rotary compression element 34, and the electromagnetic valve 106 of the refrigerant piping 102 is opened. , the solenoid valve 200 is opened, which is also effective in the present invention.

In addition, in the second operation mode, by closing the electromagnetic valve 200 by the controller 210 to prevent the refrigerant from flowing into the second cylinder 40, the inside of the second cylinder 40 can be made to be cooler than the first one. The suction side of the rotary compression element 32 is under high pressure.

In addition, in this embodiment, as the refrigerant, HFC or HC refrigerant is used as in the above-mentioned embodiment, and as the engine oil of the lubricating oil, for example, mineral oil (petroleum), hydrocarbon oil, ether oil, Existing engine oils such as ester oil.

The operation in this case will be described. The controller 210 closes the above-mentioned solenoid valve 200 to prevent the refrigerant from flowing into the second cylinder 40 . Accordingly, in the second rotary compression element 34, no compression work is performed. In addition, if the inflow of the refrigerant into the second cylinder 40 is prevented, the pressure inside the second cylinder 40 becomes slightly higher than the pressure on the suction side of the two rotating compression elements 32 and 34 (because the second roller 48 rotates and , the high pressure in the airtight container 12 flows in from the gap of the second cylinder 40, etc., so the pressure in the second cylinder 40 becomes higher than the pressure on the suction side).

Also, the controller 210 opens the solenoid valve 105 of the refrigerant pipe 101 and closes the solenoid valve 106 of the refrigerant pipe 102 . Accordingly, the refrigerant pipe 101 communicates with the pipe 75, and the refrigerant on the suction side of the first rotary compression element 32 flows into the back pressure chamber 72A, and the suction pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52. side pressure.

Then, part of the refrigerant passing through the refrigerant piping 100 of the rotary compressor 110 on the suction side of the first rotary compression element 32 flows from the refrigerant piping 101 through the piping 75 into the back pressure chamber 72A. Accordingly, the back pressure chamber 72A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

Here, if the solenoid valve 200 is closed to prevent the inflow of the refrigerant into the second cylinder 40, and the pressure in the second cylinder 40 is higher than the pressure on the suction side of the first rotary compression element 32, the second vane The back pressure of the second vane 52 makes the pressure in the second cylinder 40 higher than the back pressure of the second vane 52 by applying the suction side pressure of the first rotary compression element 32 . Therefore, the second vane 52 is pushed toward the back pressure chamber 72A side opposite to the second roller 48 by the pressure in the second cylinder 40 , and does not come out of the second cylinder 40 . According to this, the problem that the second vane 52 comes out of the second cylinder 40 and collides with the second roller 48 to generate a collision sound can be avoided in advance.

On the other hand, after the low-pressure refrigerant flowing into the accumulator 146 is gas-liquid separated here, only the refrigerant gas enters the refrigerant discharge pipe 92 opened in the accumulator 146 . The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 . The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, the refrigerant gas releases heat, is decompressed by the expansion valve 154 , and flows into the indoor heat exchanger 156 . In the indoor side heat exchanger 156, the refrigerant evaporates and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 110 is repeated.

In this way, the solenoid valve 200 is provided in the middle of the refrigerant introduction pipe 94. In the second operation mode, by closing the solenoid valve 200 by the controller 210, the inflow of the refrigerant into the second cylinder 40 is prevented. Down operation, in the second operation mode, the pressure in the second cylinder 40 is kept higher than the back pressure of the second vane 52 as it is. Therefore, the second vane 52 is pushed toward the back pressure chamber 72A side opposite to the second roller 48 by the pressure in the second cylinder 40 , and does not come out of the second cylinder 40 . According to this, the problem that the second vane 52 comes out of the second cylinder 40 and collides with the second roller 48 during operation in the second operation mode can be avoided beforehand, causing a collision sound.

As described above, according to the present invention, the performance and reliability of the compression system CS having the rotary compressor 110 that can be used by switching between the first operation mode and the second operation mode can be achieved. In the above-mentioned first operation mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the compression system CS, the operating efficiency and performance of the air conditioner can be improved, and power consumption can be reduced.

(Example 6)

In addition, in the above-mentioned Embodiment 4 and Embodiment 5, as the refrigerant, HFC or HC-based refrigerant is used, but it is also possible to use a refrigerant such as carbon dioxide with a large pressure difference between high and low pressure, for example, as the refrigerant , A combination of carbon dioxide and PAG (polyglycol) can also be used as a refrigerant. In this case, since the refrigerant compressed by the respective rotary compression elements 32 and 34 has a very high pressure, if the discharge muffler chamber 62 is made to cover the upper part of the upper support member 54 with the cover member 63 If the side shape is different, the cover member 63 may be damaged due to the high pressure.

Therefore, if the shape of the discharge muffler chamber on the upper side of the upper support member 54 where the refrigerant compressed by the two rotary compression elements 32 and 34 merges is the shape shown in FIG. 8 , pressure resistance can be ensured. That is, the discharge muffler chamber 162 in FIG. 8 is configured by forming a recessed portion on the upper side of the upper support member 54 and closing it with an upper cover 66 that covers the recessed portion. Accordingly, the present invention can be applied even in the case of containing a refrigerant having a large high-pressure difference such as carbon dioxide.

(Example 7)

Next, another embodiment of the multi-cylinder rotary compressor of the present invention will be described. Fig. 10 is a longitudinal sectional side view of the multi-cylinder rotary compressor of the present invention in this case. In addition, another longitudinal sectional side view of the multi-cylinder rotary compressor of this embodiment is the same as FIG. 1 of the first embodiment, and the refrigerant circuit diagram is also the same as FIG. 3 of the first embodiment. Therefore, in this embodiment, only the parts different from the configuration of the first embodiment will be described. In addition, in this embodiment, components given the same symbols as those in FIGS. 1 to 3 are components that can produce the same or similar effects.

The back pressure chamber 172A of this embodiment is opened on the side of the guide groove 72 and the side of the airtight container 12 , and the opening on the side of the airtight container 12 is connected to a pipe 75 which will be described later, and the inside of the airtight container 12 is sealed.

In addition, the back pressure chamber 172A of the present invention is a muffler chamber having a predetermined volume. As shown in FIG. 10, the back pressure chamber 172A of the embodiment has a shape having a recessed chamber at a position where the above-mentioned pipe 75 and the guide groove 72 are connected on the upper side of the lower supporting member 56. Has a specified volume of space. That is, the back pressure chamber 172A of this embodiment is formed at a position corresponding to the upper surface piping 75 and the guide groove 72 of the lower support member 56 that closes the lower opening surface of the second cylinder 40, and is closed by the lower support member 56. The opening of the lower surface of the second cylinder 40 forms a recessed portion.

In this way, by making the back pressure chamber 172A a shape having a predetermined space volume, the pressure pulse generated by the biasing action of the second vane 52 and the back pressure of the second vane 52 can be reduced by the back pressure chamber 172A. while the pulse of pressure is applied.

In addition, HFC or HC refrigerants are used as refrigerants, and conventional machine oils such as mineral oil (petroleum), hydrocarbon oil, ether oil, and ester oil are used as lubricating oil.

With the above configuration, the operation of the rotary compressor 10 will be described next.

(1) The first operation mode (normal load or high load)

First, the first operation mode in which the two rotating compression elements 32 and 34 perform compression work will be described. The controller 210 controls the number of revolutions of the electric element 14 of the rotary compressor 10 according to the operation instruction input from the controller on the side of the indoor unit (not shown) installed on the indoor unit, and at the same time, the indoor is in a normal load or a high load state. In the case of , the controller 210 implements the first operation mode. In the first operation mode, the controller 210 closes the solenoid valve 105 of the refrigerant pipe 101 and opens the solenoid valve 106 of the refrigerant pipe 102 . Accordingly, the refrigerant pipe 102 communicates with the pipe 75, and the refrigerant on the suction side of the two rotary compression elements 32 and 34 flows into the back pressure chamber 172A, and acts as the back pressure of the second vane 52 to apply the suction pressure of the two rotary compression elements 32. side pressure.

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . As described above, since the solenoid valve 105 of the refrigerant pipe 100 is closed, the refrigerant passing through the refrigerant pipe 100 does not flow into the pipe 75 but all flows into the accumulator 146 .

In this way, after the low-pressure refrigerant that has flowed into the accumulator 146 is separated into gas and liquid, only the refrigerant gas enters the respective refrigerant discharge pipes 92 and 94 opened in the accumulator 146 . The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

On the other hand, the low-pressure refrigerant gas entering the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34 . The refrigerant gas sucked into the low-pressure chamber side of the second cylinder 40 is compressed by the operation of the second roller 48 and the second vane 52 .

At this time, as described above, pressure pulses are generated in the back pressure chamber 172A side of the second blade 52 opposite to the second roller 48 due to the biasing operation of the second blade 52 against the second roller 48 . In this case, in the second rotary compression element 34 not provided with a conventional spring member, there arises a problem that the following property of the second vane 52 to the second roller is deteriorated due to the pressure pulse.

Furthermore, since the discharge-side pressure pulses of the two rotary compression elements 32 and 34 applied as the back pressure of the second vane 52 are large and there is no spring member, there is a problem that the second vane 52 will be damaged due to the pulse. The followability of the compressor is deteriorated, thereby reducing the compression efficiency, and a clashing sound is generated between the second vane 52 and the second roller 48 .

However, as in the present invention, by making the back pressure chamber 172A a muffler chamber having a predetermined volume, it is possible to reduce the pressure pulse generated by the biasing operation of the second vane 52 . In addition, the pressure pulsation is significantly reduced when the discharge-side refrigerant from the two rotary compression elements 32 and 34 of the piping 75 passes through the back pressure chamber 172A. Accordingly, the second blade 52 can be sufficiently biased toward the second roller 48 without using a spring member.

Accordingly, the followability of the second vane 52 in the first operation mode is improved, and the compression efficiency of the second rotary compression element 34 is also improved. Furthermore, by improving the followability of the second blade 52, the above-mentioned collision with the second roller 48 can be avoided. Therefore, it is also possible to avoid as much as possible the problem of the collision sound with the second roller 48 .

In addition, it is compressed by the operation of the second roller 48 and the second vane 52 to become a high-temperature and high-pressure refrigerant gas, and is discharged from the high-pressure chamber side of the second cylinder 40 through a discharge port not shown in the figure to the discharge muffler. Room 64. The refrigerant gas discharged into the discharge muffling chamber 64 passes through the communication passage 120 , is discharged into the discharge muffling chamber 62 , and joins the refrigerant gas compressed by the first rotary compression element 32 . In this way, the refrigerant gas merged is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . On the one hand, as described above, since the solenoid valve 106 is opened by the controller 210, a part of the refrigerant on the discharge side of the two rotary compression elements 32, 34 flowing in the refrigerant discharge pipe 96 passes through the refrigerant pipe 102. The pipe 75 flows into the back pressure chamber 172A. Accordingly, the discharge side pressures of both rotary compression elements 32 , 34 are applied as the back pressure of the second vane 52 .

On the other hand, the refrigerant gas flowing into the outdoor side heat exchanger 152 releases heat there, is depressurized by the expansion valve 154 , and then flows into the indoor side heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

In addition, in the above-mentioned first operation mode, the controller 210 closes the solenoid valve 105 of the refrigerant pipe 101, opens the solenoid valve 106 of the refrigerant pipe 102, and communicates the refrigerant pipe 102 and the pipe 75 as the second operation mode. The back pressure of the vane 52 is applied to the discharge side pressure of the two rotary compression elements 32 and 34 which are high pressure, but in this first operation mode, the two rotary compression elements 32 and 34 may be applied as the back pressure of the second vane 52 . Intermediate pressure between suction side pressure and discharge side pressure of 34. In this case, when the solenoid valve 105 of the refrigerant pipe 101 and the solenoid valve 106 of the refrigerant pipe 102 are closed by the controller 210, the inside of the pipe 75 communicating with the back pressure chamber 172A of the second vane 52 becomes a closed space. , then since a lot of refrigerant in the second cylinder 40 flows into the back pressure chamber 172A from between the second vane 52 and the housing portion 70A, the pressure in the back pressure chamber 172A of the second vane 52 becomes the pressure of the two rotating compression elements. The intermediate pressure between the suction side pressure and the discharge side pressure of 32 , 34 is applied as the back pressure of the second vane 52 .

In this way, even when an intermediate pressure is applied as the back pressure of the second blade 52 , the second blade 52 can be sufficiently urged against the second roller 48 by the intermediate pressure without using a spring member. In addition, since the pressure pulsation is significantly reduced compared with the case where the discharge side pressure of both rotary compression elements 32 and 34 is applied, it is possible to achieve further reduce the pulse. In particular, as described above, by closing the electromagnetic valves 105 and 106, the inflow of the suction-side refrigerant and the discharge-side refrigerant from the pipe 75 to both the rotary compression elements 32 and 34 is cut off, thereby further suppressing the flow of refrigerant. The pulse of the back pressure of the second vane 52 .

(2) Second operation mode (operation at light load)

Next, the second operation mode will be described. When the indoor load is light, the controller 210 switches to the second operation mode. This second operation mode is a mode in which substantially only the first rotating compression element 32 performs compression work, and is an operation mode performed when the electric element 14 rotates at a low speed in the above-mentioned first operation mode under a light indoor load. . In the small-capacity area, by substantially only the first rotary compression element 32 performing compression work, compared with the case where the compression work is performed by the first and second cylinders 38 and 40, the compressed refrigerant gas can be reduced. Therefore, this amount increases the number of revolutions of the electric element 14 even at a light load, improves the operating efficiency of the electric element 14, and also makes it possible to reduce the leakage loss of the refrigerant.

In this case, the controller 210 opens the solenoid valve 105 of the refrigerant pipe 101 and closes the solenoid valve 106 of the refrigerant pipe 102 . Accordingly, the refrigerant pipe 101 communicates with the pipe 75, and the refrigerant on the suction side of the first rotary compression element 32 flows into the back pressure chamber 172A, and the suction pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52. side pressure.

On the other hand, the controller 210 energizes the stator coil 28 of the electric element 14 through the above-mentioned terminals 20 and wiring not shown, and rotates the rotor 24 of the electric element 14 . By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . At this time, as described above, since the solenoid valve 105 of the refrigerant piping 100 is opened, part of the refrigerant passing through the suction side of the first rotary compression element 32 of the refrigerant piping 100 passes through the refrigerant piping 101 . The piping 75 flows into the back pressure chamber 172A. Accordingly, the back pressure chamber 172A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

Here, since the suction side pressure of both the rotary compression elements 32 and 34 applied as the back pressure of the second rotary compression element 34 is low pressure, the second vane 52 cannot be biased against the second roller 48 . Therefore, in the second rotary compression element 34, substantially no compression work is performed, and only the first rotary compression element 32 provided with the spring 74 completes the compression work of the refrigerant.

In this case, since the pressure in the second cylinder 40 is equal to the back pressure of the second vane, the suction side pressure is applied, so conventionally, the second vane appears in the second cylinder due to a change in the balance between the two spaces, and the The second roll conflict, there will still be the problem of conflict sound. However, since the back pressure chamber 172A having the predetermined space volume of the present invention can reduce fluctuations, it is possible to avoid as much as possible that the second vane 52 appears in the second cylinder 40 and collides with the second roller 48 to generate a collision sound. question.

On the other hand, after the low-pressure refrigerant flowing into the accumulator 146 is gas-liquid separated here, only the refrigerant gas enters the refrigerant discharge pipe 92 opened in the accumulator 146 . The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 . The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, the refrigerant gas releases heat, is decompressed by the expansion valve 154 , and flows into the indoor heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

As described above, according to the present invention, it is possible to improve the performance and reliability of the rotary compressor 10 which can be used by switching between the first operation mode and the second operation mode. mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the rotary compressor 10, the operating efficiency and performance of the air conditioner can be improved, and power consumption can be reduced.

(Embodiment 8)

In addition, in Example 7, the back pressure chamber 172A is shaped as a recessed chamber having a predetermined volume, but it is not limited to this, and the back pressure chamber of the present invention can be Can. For example, the present invention is also effective when the back pressure chamber has the shape shown in FIG. 11 . In addition, FIG. 11 is a top sectional view of the second cylinder in this case. In FIG. 11 , components given the same symbols as those in FIGS. 1 to 10 are components that can produce the same or similar effects.

In FIG. 11 , 49 is a discharge port of the second rotary compression element 34 . The back pressure chamber 272A has an expanded portion with a predetermined volume in the lateral direction of the second cylinder 40 and has a substantially cylindrical shape as a whole. Thus, even when the back pressure chamber 272A has the shape of the present embodiment, the pressure pulse can be reduced by the back pressure chamber 272A, the followability of the second vane 52 can be improved, and collision with the second roller 48 can be avoided.

(Example 9)

In addition, even in the case of the seventh and eighth embodiments described above, as shown in FIG. A solenoid valve 200 for controlling the inflow of refrigerant to the second rotary compression element 34 is provided at an intermediate portion of the pipe 94. In the second operation mode, the solenoid valve 200 is closed to cut off the inflow of refrigerant to the second cylinder 40. OK.

In this case, if the inflow of refrigerant to the second cylinder 40 is cut off, the pressure inside the second cylinder 40 becomes slightly higher than the pressure on the suction side of both rotary compression elements 32 and 34 as described above (because the second The roller 48 rotates, and the high pressure in the airtight container 12 inflows from the gap of the second cylinder 40 to some extent, so the pressure in the second cylinder 40 becomes slightly higher than the pressure on the suction side).

Therefore, the second vane 52 is pushed to the side of the back pressure chamber 172A (or back pressure chamber 272A) opposite to the second roller 48 by the pressure in the second cylinder 40 , and does not appear in the second cylinder 40 . Inside. Accordingly, in addition to the effects of the above-described back pressure chamber 172A (or back pressure chamber 272A), it is possible to more effectively avoid the problem that the second vane 52 collides with the second roller 48 .

(Example 10)

In the above-mentioned Embodiment 7, Embodiment 8, and Embodiment 9, as the refrigerant, HFC or HC-based refrigerants are used, but it is also possible to use refrigerants such as carbon dioxide with a large high-pressure difference, for example, as As the refrigerant, a refrigerant obtained by combining carbon dioxide and PAG (polyglycol) can also be used. In this case, since the refrigerant compressed by the respective rotary compression elements 32 and 34 has a very high pressure, if the discharge muffler chamber 62 is made to cover the upper part of the upper support member 54 with the cover member 63 If the side shape is different, the cover member 63 may be damaged due to the high pressure.

Therefore, if the shape of the discharge muffler chamber on the upper side of the upper support member 54 where the refrigerant compressed by the two rotary compression elements 32 and 34 merges is shaped as shown in FIG. 8 , pressure resistance can be ensured. That is, the discharge muffler chamber 162 in FIG. 8 is configured by forming a recessed portion on the upper side of the upper support member 54 and closing it with an upper cover 66 that covers the recessed portion. Accordingly, the present invention can be applied even in the case of containing a refrigerant having a large high-pressure difference such as carbon dioxide.

(Example 11)

Next, another embodiment of the multi-cylinder rotary compressor of the present invention will be described using FIG. 12 and FIG. 13 . Fig. 12 is a top sectional view of the second cylinder showing that the second roller of the second rotary compression element of the multi-cylinder rotary compressor of the present invention is located at the top dead center, and Fig. 13 is a top view showing that the second roller of the second rotary compression element is located at the bottom Top sectional view of the second cylinder in dead center condition.

1 and 2 of the first embodiment, and the refrigerant circuit diagram is also the same as that of FIG. 3 of the first embodiment, so they are omitted. Therefore, in this embodiment, only the parts different from the configuration of the first embodiment will be described. In addition, in this embodiment, components given the same symbols as in FIGS. 1 to 3 are components that can produce the same or similar effects.

Here, a back pressure chamber 72A is formed on the back side of the second vane 52 . The back pressure chamber 72A is opened on the side of the guide groove 72 and the side of the sealed container 12 , and a pipe 375 ( FIGS. 12 to 13 ) serving as a passage for back pressure is connected through the opening on the side of the sealed container 12 , and the inside of the sealed container 12 is sealed.

The above-mentioned piping 375 is a back pressure passage for applying back pressure to the second blade 52 of the second rotary compression element 34, and passes through the refrigerant piping 101 described later and the suction side of the two rotary compression elements 32, 34, respectively. The refrigerant pipe 100 communicates with the refrigerant pipe 102 and communicates with the refrigerant discharge pipe 96 on the discharge side of the two rotary compression elements 32 and 34 through the refrigerant pipe 102 . In this way, the refrigerant on the discharge side of both rotary compression elements 32 and 34 or the refrigerant on the suction side of both rotary compression elements 32 and 34 flows into the back pressure chamber 72A from the pipe 75, and acts as a back pressure on the second vane 52 to apply both. The discharge side pressure of the rotary compression elements 32 , 34 or the suction side pressure of both rotary compression elements 32 , 34 .

In addition, in the present invention, the cross-sectional area of the piping 375 is greater than or equal to the average value of the surface areas of the second vanes 52 exposed in the second cylinder 40 . That is, it is calculated from the top dead center in which the second vane 52 of the second roller 48 following the eccentrically rotating second cylinder 40 shown in FIG. The second vane 52 shown in 13 is between the bottom dead center of the state most exposed in the second cylinder 40 (the dotted line of the second vane 52 in FIG. The average value of the surface areas of the second vanes 52 in the second cylinder 40 is set to be equal to or greater than the average value of the surface areas of the cross-sectional area of the pipe 375 .

In this way, by making the cross-sectional area of the pipe 375 equal to or greater than the average value of the surface areas of the second vanes 52 exposed in the second cylinder 40, it is possible to sufficiently ensure that the second vane 52 is on the opposite side to the second roller 48. The area of the back pressure chamber 72A side.

As the refrigerant, HFC or HC refrigerants are used, and as the lubricating oil, conventional machine oils such as mineral oil (petroleum), hydrocarbon oil, ether oil, and ester oil are used.

With the above configuration, the operation of the rotary compressor 10 will be described next.

(1) The first operation mode (normal load or high load)

First, the first operation mode in which the two rotating compression elements 32 and 34 perform compression work will be described. The controller 210 controls the number of revolutions of the electric element 14 of the rotary compressor 10 according to the operation instruction input from the controller on the side of the indoor unit (not shown) installed on the indoor unit, and at the same time, the indoor is in a normal load or a high load state. In the case of , the controller 210 implements the first operation mode. In the first operation mode, the controller 210 closes the solenoid valve 105 of the refrigerant pipe 101 and opens the solenoid valve 106 of the refrigerant pipe 102 . Accordingly, the refrigerant pipe 102 communicates with the pipe 375, and the refrigerant on the discharge side of the two rotary compression elements 32, 34 flows into the back pressure chamber 72A, and the two rotary compression elements 32, 34 are applied as the back pressure of the second vane 52. discharge side pressure.

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . As described above, since the solenoid valve 105 of the refrigerant pipe 100 is closed, the refrigerant passing through the refrigerant pipe 100 does not flow into the pipe 375 but all flows into the accumulator 146 .

In this way, after the low-pressure refrigerant that has flowed into the pressure accumulator 146 is separated into gas and liquid, only the refrigerant gas enters the respective refrigerant discharge pipes 92 and 94 opened in the pressure accumulator 146 . The low-pressure refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

On the other hand, the low-pressure refrigerant gas entering the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34 . The refrigerant gas sucked into the low-pressure chamber side of the second cylinder 40 is compressed by the operation of the second roller 48 and the second vane 52 .

At this time, as described above, pressure pulses are generated in the back pressure chamber 72A side of the second blade 52 opposite to the second roller 48 due to the biasing operation of the second blade 52 against the second roller 48 . In this case, in the second rotary compression element 34 not provided with the conventional spring member, there arises a problem that the followability of the second vane 52 to the second roller 48 is deteriorated due to the pressure pulse.

Furthermore, since the discharge-side pressure pulses of the two rotary compression elements 32, 34 applied as the back pressure of the second vane 52 are large, and there is no spring member on the second rotary compression element 34, there is the following problem, that is, Due to this pulsation, the followability of the second vane 52 deteriorates, whereby the compression efficiency decreases, and a clashing sound is generated between the second vane 52 and the second roller 48 .

However, as described above, by making the cross-sectional area of the piping 375 equal to or greater than the average value of the surface areas of the second vanes 52 exposed in the second cylinder 40, it is possible to sufficiently ensure that the second vanes 52 are opposite to the second roller 48. The area on the side of the back pressure chamber 72A can reduce the pressure pulse generated by the spring action of the second vane 52 . In addition, when the refrigerant on the discharge side of the two rotary compression elements 32 and 34 from the pipe 375 passes through the pipe 375, the pressure pulsation is significantly reduced. Accordingly, the second blade 52 can be sufficiently biased toward the second roller 48 without using a spring member.

Accordingly, the followability of the second vane 52 in the first operation mode is improved, and the compression efficiency of the second rotary compression element 34 is also improved. Furthermore, by improving the followability of the second blade 52, the above-mentioned collision with the second roller 48 can be avoided. Therefore, it is also possible to avoid as much as possible the problem of the collision sound with the second roller 48 .

In addition, the high-temperature and high-pressure refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 is discharged from the high-pressure chamber side of the second cylinder 40 into the discharge muffler chamber 64 through the discharge port 49 . The refrigerant gas discharged to the discharge muffling chamber 64 passes through the communication passage 120 , is discharged to the discharge muffling chamber 62 , and joins the refrigerant gas compressed by the first rotary compression element 32 . The merged refrigerant gas is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, as described above, since the electromagnetic valve 106 of the piping 102 is opened, part of the refrigerant on the discharge side of the two rotary compression elements 32 and 34 passing through the refrigerant discharge pipe 96 is discharged from the refrigerant piping as described above. 102 enters the pipe 375 and is applied as a back pressure of the second vane 52 .

On the other hand, the refrigerant gas flowing into the outdoor side heat exchanger 152 releases heat there, is depressurized by the expansion valve 154 , and then flows into the indoor side heat exchanger 156 . In the indoor side heat exchanger 156, the refrigerant evaporates and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

In addition, in the above-mentioned first operation mode, the controller 210 closes the electromagnetic valve 105 of the refrigerant piping 101, opens the electromagnetic valve 106 of the refrigerant piping 102, and communicates the refrigerant piping 102 and the piping 375 as the second operation mode. The back pressure of the vane 52 is applied as the high-pressure discharge side pressure of the two rotary compression elements 32 and 34, however, as the back pressure of the second vane 52, the suction side pressure and the discharge side pressure of the two rotary compression elements 32 and 34 may be applied. Intermediate pressure between pressures. In this case, for example, by closing the solenoid valve 105 of the refrigerant pipe 101 and the solenoid valve 106 of the refrigerant pipe 102 by the controller 210, the inside of the pipe 375 communicating with the back pressure chamber 72A of the second vane 52 becomes If the space is closed, since a lot of refrigerant in the second cylinder 40 flows into the back pressure chamber 72A from between the second vane 52 and the accommodating portion 70A, the pressure in the back pressure chamber 72A of the second vane 52 becomes two rotations. The intermediate pressure between the suction side pressure and the discharge side pressure of the compression elements 32 , 34 is applied as a back pressure of the second vane 52 .

In this way, when an intermediate pressure is applied as the back pressure of the second vane 52 , the second vane 52 can be sufficiently biased toward the second roller 48 by this intermediate pressure without using a spring member. In addition, since the pressure pulsation is significantly reduced compared with the case where the discharge side pressure of both rotary compression elements 32 and 34 is applied, further reduction of pulsation can be achieved in addition to the effect of the piping 375 described above. In particular, as described above, by closing the solenoid valves 105 and 106, the inflow of the suction-side refrigerant and the discharge-side refrigerant from the pipe 375 to both the rotary compression elements 32 and 34 is cut off, thereby further suppressing The pulse of the back pressure of the second vane 52 .

(2) Second operation mode (operation at light load)

Next, the second operation mode will be described. When the indoor load is light, the controller 210 switches to the second operation mode. This second operation mode is a mode in which substantially only the first rotating compression element 32 performs compression work, and is an operation mode performed when the electric element 14 rotates at a low speed in the above-mentioned first operation mode under a light indoor load. . Since only the first rotating compression element 32 performs compression work in the small capacity area, the compressed refrigerant gas can be reduced compared with the case where the first and second cylinders 38, 40 perform compression work. Therefore, this amount increases the rotation speed of the electric element 14 even at light load, improves the operation efficiency of the electric element 14, and also makes it possible to reduce the leakage loss of the refrigerant.

In this case, the controller 210 opens the solenoid valve 105 of the refrigerant pipe 101 and closes the solenoid valve 106 of the refrigerant pipe 102 . Accordingly, the refrigerant pipe 101 communicates with the pipe 375, and the refrigerant on the suction side of the first rotary compression element 32 flows into the back pressure chamber 72A, and the suction pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52. side pressure.

On the other hand, the controller 210 energizes the stator coil 28 of the electric element 14 through the above-mentioned terminals 20 and wiring not shown, and rotates the rotor 24 of the electric element 14 . By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the low-pressure refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . At this time, as described above, since the solenoid valve 105 of the refrigerant piping 101 is opened, part of the refrigerant passing through the suction side of the first rotary compression element 32 of the refrigerant piping 100 passes through the refrigerant piping 101 . The piping 375 flows into the back pressure chamber 72A. Accordingly, the back pressure chamber 72A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

Here, since the suction side pressure of both the rotary compression elements 32 and 34 applied as the back pressure of the second rotary compression element 34 is low pressure, the second vane 52 cannot be biased against the second roller 48 . Therefore, in the second rotary compression element 34, substantially no compression work is performed, and only the first rotary compression element 32 provided with the spring 74 completes the compression work of the refrigerant.

In this case, since the same suction side pressure as the pressure in the second cylinder 40 and the back pressure of the second vane 52 is applied, conventionally, the second vane 52 appears on the second side due to a change in the balance between the two spaces. In the cylinder 40, the second roller 48 collides, and there is still a problem that a collision sound is generated. However, as in the present invention, by making the cross-sectional area of the piping 375 connected to the back pressure chamber 72A of the second vane 52 greater than or equal to the average value of the surface areas of the second vane 52 exposed in the second cylinder 40, the Since the piping 375 can reduce fluctuations, it is possible to avoid as much as possible the problem that the second vane 52 appears in the second cylinder 40 and collides with the second roller 48 to generate a collision sound.

On the other hand, after the low-pressure refrigerant flowing into the accumulator 146 is gas-liquid separated here, only the refrigerant gas enters the refrigerant discharge pipe 92 opened in the accumulator 146 . The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 . The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cover 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . Here, the refrigerant gas releases heat, is decompressed by the expansion valve 154 , and flows into the indoor heat exchanger 156 . The refrigerant flowing into the indoor side heat exchanger 156 evaporates there, absorbs heat from the air circulating in the room, exerts a cooling effect, and cools the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

As described above, according to the present invention, it is possible to improve the performance and reliability of the rotary compressor 10 which can be used by switching between the first operation mode and the second operation mode. mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the rotary compressor 10, the operating efficiency and performance of the air conditioner can be improved, and power consumption can be reduced.

(Example 12)

In addition, as shown in FIG. 5 , on the outlet side of the pressure accumulator 146 of the rotary compressor 10 , at the middle part of the refrigerant introduction pipe 94 on the inlet side of the hermetic container 12 , a second rotary compression element that controls the direction of rotation may be provided. The solenoid valve 200 for the refrigerant flow into the second cylinder 40 of 34 is closed in the second operation mode to cut off the refrigerant flow into the second cylinder 40 . In addition, in FIG. 5 , components given the same symbols as those in FIGS. 1 to 13 are components that produce the same effects.

In this case, if the inflow of the refrigerant to the second cylinder 40 is cut off, the pressure inside the second cylinder 40 becomes slightly higher than the pressure on the suction side of both rotary compression elements 32 and 34 as described above (because the second roller 48 rotates, and the high pressure in the airtight container 12 flows in from the gap of the second cylinder 40 etc. slightly, so the pressure in the second cylinder 40 becomes slightly higher than the suction side pressure).

Therefore, the second vane 52 is pressed toward the back pressure chamber 72A side opposite to the second roller 48 by the pressure in the second cylinder 40 , and does not appear in the second cylinder 40 . Accordingly, in addition to the effect of the piping 375 described above, it is possible to further effectively avoid the occurrence of a problem that the second vane 52 collides with the second roller 48 .

(Example 13)

In addition, in the above-mentioned Embodiment 11 and Embodiment 12, as the refrigerant, HFC or HC-based refrigerants are used, but it is also possible to use refrigerants such as carbon dioxide with a large pressure difference, for example, as a refrigerant As a refrigerant, a refrigerant obtained by combining carbon dioxide and PAG (polyglycol) can also be used. In this case, since the refrigerant compressed by the respective rotary compression elements 32 and 34 has a very high pressure, if the discharge muffler chamber 62 is made to cover the upper part of the upper support member 54 with the cover member 63 If the side shape is different, the cover member 63 may be damaged due to the high pressure.

Therefore, if the shape of the discharge muffler chamber on the upper side of the upper support member 54 where the refrigerant compressed by both rotary compression elements 32 and 34 merges is shaped as shown in FIG. 8 , pressure resistance can be ensured. That is, the discharge muffler chamber 162 in FIG. 8 is configured by forming a recessed portion on the upper side of the upper support member 54 and closing it with an upper cover 66 that covers the recessed portion. Accordingly, the present invention can be applied even in the case of containing a refrigerant having a large high-pressure difference such as carbon dioxide.

(Example 14)

Next, another embodiment of the compression system CS of the present invention will be described. 14 is an embodiment of a multi-cylinder rotary compressor as the compression system CS of the present invention, showing a longitudinal sectional side view of an internal high-pressure type rotary compressor 10 having first and second rotary compression elements, and FIG. 15 is a A vertical side view of the rotary compressor 10 in FIG. 1 is shown (a cross section different from that in FIG. 1 is shown). In addition, the compression system CS of the present embodiment is a part of the refrigerant circuit constituting an air conditioner as a refrigeration device for air-conditioning a room. In addition, in FIG. 14 and FIG. 15 , components given the same symbols as those in FIG. 1 to FIG. 13 of the above-mentioned embodiments are components that can produce the same or similar effects, and description thereof will be omitted.

In addition, on the above-mentioned second cylinder 40, a guide groove 72 for accommodating the second vane 52 is formed, and on the outside of the guide groove 72, that is, on the back side of the second vane 52, a housing as shown in FIG. 16 is formed. The receiving part 472A of the weak spring 76. The storage portion 472A is opened on the guide groove 72 side and the airtight container 12 side, and a pipe 75 described later is connected to the opening on the airtight container 12 side, and the inside of the airtight container 12 is sealed.

The above-mentioned weak spring 76 is used to spring the second vane 52 toward the second roller 48, one end of which is in contact with the back side end of the second vane 52, and the other end is installed and fixed on the sealed container 12 side of the storage portion 472A to communicate with it. The front end of the piping 75. In addition, the biasing force of the weak spring 76 is set to be equal to or less than the biasing force of the two rotary compression elements 32 , 34 , or when the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 . .

In addition, a solenoid valve 200 is provided on the outlet side of the accumulator 146 and in the middle of the refrigerant introduction pipe 94 on the inlet side of the hermetic container 12 . The solenoid valve 200 is a valve device for controlling the flow of the refrigerant into the second cylinder 40, and is controlled by a controller 210 described later as a control device.

Here, the above-mentioned controller 210 constitutes a part of the compression system CS of the present invention, and controls the rotation speed of the electric element 14 of the rotary compressor 10 . In addition, as described above, the opening and closing of the solenoid valve 200 of the refrigerant introduction pipe 94 , the solenoid valve 105 of the refrigerant pipe 101 , and the solenoid valve 106 of the refrigerant pipe 102 are controlled.

Next, FIG. 17 is a refrigerant circuit diagram showing the above air conditioner configured using the compression system CS. That is, the compression system CS of the embodiment constitutes a part of the refrigerant circuit of the air conditioner shown in FIG. 17, and is composed of the above-mentioned rotary compressor 10, controller 210, and the like. The refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the outdoor side heat exchanger 152 . The above-described controller 210, rotary compressor 10, and outdoor side heat exchanger 152 are installed in an unillustrated outdoor unit of the air conditioner. A pipe connected to the outlet of the outdoor heat exchanger 152 is connected to an expansion valve 154 as a decompression mechanism, and a pipe leading out of the expansion valve 154 is connected to an indoor heat exchanger 156 . The expansion valve 154 and the indoor side heat exchanger 156 are provided in an unillustrated indoor unit of the air conditioner. Further, the refrigerant piping 100 of the rotary compressor 10 is connected to the outlet side of the indoor heat exchanger 156 .

As the refrigerant, HFC or HC refrigerants are used, and as the lubricating oil, conventional machine oils such as mineral oil (petroleum), hydrocarbon oil, ether oil, and ester oil are used.

With the above configuration, the operation of the rotary compressor 10 will be described next.

(1) The first operation mode (operation under normal load or high load)

First, using FIG. 18 , the first operation mode in which the two rotating compression elements 32 and 34 perform compression work will be described. In addition, FIG. 18 is a diagram showing the flow of the refrigerant in the first operation mode of the rotary compressor 10 (thick lines in the figure indicate the flow of the refrigerant).

The controller 210 energizes the electric element 14 of the rotary compressor 10 in response to an input of an operation command from a controller on the side of the indoor unit (not shown) provided in the indoor unit. At this time, the controller 210 opens the electromagnetic valve 200 of the refrigerant introduction pipe 94 and the electromagnetic valve 106 of the refrigerant piping 102 while energizing the electric element 14, and closes the electromagnetic valve 105 of the refrigerant piping 101 (FIG. 18 ). Accordingly, the refrigerant pipe 102 communicates with the pipe 75, and the controller 210 controls the electric element of the rotary compressor 10 under the condition that the discharge side pressure of both the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52. 14 revolutions, start. In addition, although the controller 210 controls to open the solenoid valve 200 and the solenoid valve 106 and close the solenoid valve 105 while the electric element 14 is energized, as long as the solenoid valve 200 and the solenoid valves 105, 106 are rotating The compressor 10 may be started before starting. For example, the controller 210 may be configured to open the solenoid valve 200 and the solenoid valve 106 and close the solenoid valve 105 before energizing the electric element 14 .

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the refrigerant flows from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 . At this time, as described above, since the solenoid valve 105 of the refrigerant pipe 101 is closed, the refrigerant passing through the suction side of the two rotary compression elements 32, 34 of the refrigerant pipe 100 does not flow into the pipe 75, but It all flows into the pressure accumulator 146 .

After the refrigerant that has flowed into the pressure accumulator 146 is separated into gas and liquid here, only the refrigerant gas enters the refrigerant introduction pipe 92 and the refrigerant introduction pipe 94 opened in the pressure accumulator 146 . . The refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

On the other hand, the low-pressure refrigerant gas entering the refrigerant introduction pipe 94 passes through the suction passage 60 and is sucked into the low-pressure chamber side of the second cylinder 40 of the second rotary compression element 34 . The refrigerant gas sucked into the low-pressure chamber side of the second cylinder 40 is compressed by the operation of the second roller 48 and the second vane 52 .

Here, the inside of the refrigerant circuit is at a balanced pressure when the rotary compressor 10 is started. That is, since the pressure of the rotary compressor 10 is gradually balanced after the last operation was stopped, and when a predetermined time elapses, the entire refrigerant circuit becomes a balanced pressure. Therefore, the entire refrigerant circuit becomes a balanced pressure. In the case where the rotary compressor 10 is started, immediately after the rotary compressor 10 is started, the pressure of the refrigerant on the discharge side of the two rotary compression elements 32 and 34 applied as the back pressure of the second vane 52 become the approximate equilibrium pressure. Similarly, the pressure in the second cylinder 40 also becomes a substantially balanced pressure.

Therefore, in the case where the second vane 52 is biased against the second roller only by the back pressure, the second vane 52 cannot be caused to follow until the pressure on the discharge side of both the rotary compression elements 32 and 34 rises to a certain level. Second roller 48 . Therefore, in the second rotary compression element 34, substantially no compression work is performed, and only the first rotary compression element 32 provided with the spring 74 completes the compression work of the refrigerant.

In addition, since the state in the refrigerant circuit is unstable immediately after start-up, the pulsation of the pressure on the discharge side of both rotary compression elements 32, 34 is also significantly increased. Therefore, in the case where the second vane 52 is started with the discharge side pressure of the two rotary compression elements 32, 34 being applied without any spring pressing mechanism, there is a problem that the two rotary compression elements 32, 34 The pulsation of the discharge side pressure at 34 deteriorates the followability of the second vane 52, and the second vane 52 collides with the second roller 48 to generate a collision sound.

However, by providing the weak spring 76 that urges the second vane 52 toward the second roller 48, even when the second cylinder 40 and the accommodating portion 472A are at substantially equal pressure (balanced pressure) during startup, the weak spring 76 can The spring force makes the second blade 52 follow the second roller 48 . Accordingly, the followability of the second vane 52 at the time of starting can be improved. In addition, since the compression work can be performed even in the second rotary compression element 34 from the start, the performance of the air conditioner including the rotary compressor 10 can be improved.

Further, refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 to become high temperature and high pressure is discharged from the high pressure chamber side of the second cylinder 40 through the discharge port 49 to the discharge muffler chamber 64 . The refrigerant gas discharged to the discharge muffling chamber 64 passes through the communication passage 120 , is discharged into the discharge muffling chamber 62 , and joins the refrigerant gas compressed by the first rotary compression element 32 . Then, the joined refrigerant gas is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cap 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . On the other hand, since the controller 210 opens the solenoid valve 106 as described above, part of the refrigerant passing through the refrigerant discharge pipe 96 flows from the refrigerant pipe 102 through the pipe 75 into the housing portion 472A.

On the other hand, the refrigerant gas flowing into the outdoor heat exchanger 152 releases heat, is decompressed by the expansion valve 154 , and then flows into the indoor heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

(2) Switching from the first operation mode to the second operation mode (operation at light load)

Next, the controller 210 switches from the first operation mode to the second operation mode when the room changes from the above-mentioned normal load or high load state to a light load state. The second operation mode is a mode in which only the first rotating compression element 32 performs compression work substantially, and is an operation mode in which the indoor load is light, and the electric element 14 rotates at a low speed in the above-mentioned first operation mode. In the small capacity region of the compression system CS, the compression work is performed by only the first rotating compression element 32, compared with the case where the compression work is performed by the first and second cylinders 38, 40, since the compression work can be reduced Therefore, this amount increases the rotation speed of the electric element 14 even at light load, improves the operation efficiency of the electric element 14, and also makes it possible to reduce the leakage loss of the refrigerant.

Here, when switching from the first operation mode to the second operation mode, the controller 210 rotates the electric element 14 at a low speed, for example, controls the number of revolutions to be equal to or less than 50 Hz, and adjusts the compression ratio of the two-rotation compression element 32 to 50 Hz. The control is less than or equal to 3.0.

In this way, the controller 210 closes the above-mentioned solenoid valve 200 as shown in FIG. 19 to cut off the inflow of the refrigerant into the second cylinder 40 . Therefore, in the second rotary compression element 34, no compression work is performed. If the inflow of refrigerant to the second cylinder 40 is cut off, the pressure in the second cylinder 40 becomes slightly higher than the pressure on the suction side of the above-mentioned two rotating compression elements 32, 34 (because the second roller 48 rotates and the sealing The high pressure in the container 12 flows in from the gap of the second cylinder 40 to some extent, so the pressure in the second cylinder 40 is slightly higher than the pressure on the suction side).

In this way, the controller 210 opens the electromagnetic valve 105 of the refrigerant piping 101 and closes the electromagnetic valve 106 of the refrigerant piping 102 . Accordingly, refrigerant pipe 101 communicates with pipe 75 , and part of the refrigerant passing through refrigerant pipe 100 on the suction side of first rotary compression element 32 flows from refrigerant pipe 101 through pipe 75 into housing portion 472A. Accordingly, the storage portion 472A becomes the suction side pressure of the first rotary compression element 32 , and applies the suction side pressure of the first rotary compression element 32 as the back pressure of the second vane 52 .

Here, since the urging force of the weak spring 76 against the second roller 48 is set to be equal to or less than the suction side pressure of the first rotary compression element 32 , as described above, the pressure in the second cylinder 40 is higher than that of the first rotary compression element 32 . As the back pressure of the second vane 52, the suction side pressure of the first rotary compression element 32 is applied to the suction side pressure of the second vane 52 due to the pressure and weak The elastic force of the spring 76 increases the pressure in the second cylinder 40 .

That is, because the pressure in the second cylinder 40 urges the second vane 52 toward the back pressure side (accommodating portion 472A side), the biasing force is greater than the pressure and weak force of the accommodating portion 472A biasing the second blade 52 toward the second roller 48 . Due to the urging force of the spring 76 , the second vane 52 is pressed toward the storage portion 472A side opposite to the second roller 48 and stored in the guide groove 72 . Accordingly, when shifting to the second operation mode, the second vane 52 can be drawn in from the second cylinder 40 early and accommodated in the guide groove 72 .

At this time, in the case where the spring pressing mechanism is not provided on the back pressure side of the second vane 53, there is a problem that the second vane 52 is pushed by the pressure in the second cylinder 40 at the time of switching, and the When it is introduced into the cylinder 40, the second vane 52 collides with the wall of the housing portion 472A or the front end of the pipe 75 to generate a collision sound. However, by providing the weak spring 76 , when the second vane 52 is drawn in from the second cylinder 40 , the shock can be absorbed by the weak spring 76 . Accordingly, problems such as conflict between the second vane 52 and the second roller 48 and generation of collision noise can be avoided, and it is possible to switch to the second operation mode in which substantially only the first rotating compression element 32 completes the compression work.

(3) The second operation mode

Next, the operation of the rotary compressor 10 in the second operation mode will be described. In addition, similar to the transition from the first operation mode to the second operation mode described above, the solenoid valve 200 of the refrigerant introduction pipe 94 is closed, the solenoid valve 105 of the refrigerant pipe 101 is opened, and the refrigerant pipe 102 is opened. The solenoid valve 106 of the valve is just closed (FIG. 19). The low-pressure refrigerant flowing from the refrigerant piping 100 of the rotary compressor 10 into the accumulator 146 is gas-liquid separated here, and only the refrigerant gas enters the refrigerant opening in the accumulator 146. discharge pipe 92. The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

On the other hand, since the solenoid valve 105 of the refrigerant pipe 101 is opened by the controller 210 , part of the refrigerant passing through the refrigerant pipe 100 flows from the refrigerant pipe 101 through the pipe 75 into the housing portion 472A. Accordingly, the storage portion 472A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

On the other hand, the refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas, which is released from the first cylinder 38 The high-pressure chamber side is discharged into the discharge muffler chamber 62 through an unshown discharge port. The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cap 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . In addition, since the solenoid valve 106 is closed as described above, the refrigerant on the discharge side of the first rotary compression element 32 flowing through the refrigerant discharge pipe 96 does not flow into the pipe 75 but all flows into the outdoor heat exchange unit. device 152. In this way, the refrigerant gas flowing into the outdoor heat exchanger 152 releases heat, is depressurized by the expansion valve 154 , and then flows into the indoor heat exchanger 156 . Here, the refrigerant evaporates, and at this time, absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 10 is repeated.

In addition, in this second operation mode, by causing the controller 210 to close the above-mentioned solenoid valve 200 and operate in a state in which the refrigerant flow into the second cylinder 40 is cut off, in the second operation mode, the second cylinder 40 The pressure of is kept in a state higher than the back pressure of the second vane 52 in this way. Therefore, the second vane 52 is pushed toward the storage portion 472A side (the weak spring 76 side) opposite to the second roller 48 by the pressure inside the second cylinder 40 , and does not appear inside the second cylinder 40 . Accordingly, during operation in the second operation mode, the problem that the second vane 52 appears in the second cylinder 40 and collides with the second roller 48 to generate a collision sound can be avoided in advance.

(4) Switching from the second operation mode to the first operation mode

On the other hand, the controller 210 switches from the second operation mode to the first operation mode when the room changes from the above-mentioned light load state to a normal load state or a high load state. Here, the switching operation from the second operation mode to the first operation mode will be described. In this case, the controller 210 controls to rotate the electric element 14 at a low speed (the number of revolutions is equal to or less than 50 Hz), so that the compression ratio of the two rotating compression elements 32 and 34 is equal to or less than 3.0. The controller 210 opens the solenoid valve 200 to allow refrigerant to flow into the second cylinder 40 , closes the solenoid valve 105 of the refrigerant pipe 101 , and opens the solenoid valve 106 of the refrigerant pipe 102 .

As a result, the refrigerant pipe 102 communicates with the pipe 75 , and the refrigerant on the discharge side of both the rotary compression elements 32 and 34 flows into the housing portion 472A, and the pressure of the two rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 . discharge side pressure.

As the back pressure of the second vane 52 , by applying the discharge side pressure of the two rotary compression elements 32 and 34 , since the storage portion 472A of the second vane 52 has a higher pressure than the inside of the second cylinder 40 , the second vane 52 52 is pushed toward the second roller 48 side by the high pressure and the weak spring 76 of the storage portion 472A, and follows. Accordingly, in the second rotary compression element 34, the compression work starts again.

By providing the weak spring 76 in this way, the second vane 52 can be sufficiently biased toward the second roller 48 and follow the second roller 48 early when switching from the second operation mode to the first operation mode.

This improves the followability of the second vane 52 at the time of switching from the second operation mode to the first operation mode, improves operation efficiency, and prevents the generation of collision noise of the second vane 52 .

As described above, according to the present invention, it is possible to improve the performance and reliability of the compression system CS having the rotary compressor 10 that can be used by switching between the first operation mode and the second operation mode, In the above-mentioned first operation mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the compression system CS, the operating efficiency and performance of the air conditioner can be improved, and power consumption can also be reduced.

In addition, in the present embodiment, the controller 210 opens the solenoid valve 106 of the refrigerant piping 102 to communicate refrigerant in the first operation mode, at startup, and when switching from the second operation mode to the first operation mode. The pipe 102 and the pipe 75 allow the refrigerant on the discharge side of the two rotary compression elements 32 and 34 to flow into the housing portion 472A, and the discharge side pressure of the two rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 . Not limited to this, an intermediate pressure between the suction side pressure and the discharge side pressure of both rotary compression elements 32 and 34 may be applied as the back pressure of the second vane 52 .

In this case, for example, as shown in FIG. 20 , if the controller 210 closes the electromagnetic valve 105 and the electromagnetic valve 106 to make the inside of the piping 75 communicating with the storage portion 472A of the second vane 52 a closed space, because many The refrigerant in the second cylinder 40 flows into the storage portion 472A from between the second vane 52 and the storage portion 70A, so the pressure in the storage portion 472A of the second vane 52 becomes the sum of the suction side pressures of the two rotary compression elements 32 and 34 . An intermediate pressure between the discharge side pressures is applied as a back pressure of the second vane 52 .

Like this, when the intermediate pressure is applied as the back pressure of the second blade 52, the biasing force of the weak spring 76 can be applied in the same way as in the above-mentioned embodiment, so that the second blade 52 can be pushed toward the second roller 48 sufficiently. Squeeze to make it follow early.

(Example 15)

Next, a multi-cylinder rotary compressor (rotary compressor) of a compression system according to another embodiment of the present invention will be described. 21 and 22 are vertical side views of the rotary compressor 310 in this embodiment, respectively. In addition, in FIG. 21 and FIG. 22 , components given the same symbols as those in FIGS. 1 to 20 are components that can produce the same or similar effects.

In FIG. 22 , 176 is a weak spring for tensile load, which is installed outside the guide groove 72 of the second blade 52 of the second rotary compression element 34 , that is, on the storage portion 472A on the back side of the second blade 52 . . The weak spring 176 is used to pull the second blade 52 to the side opposite to the second roller 48 , and one end thereof is attached to the front end of the second blade 52 , and the other end thereof is attached to the pipe 75 . In addition, the tensile force of the weak spring 176 is equal to or less than the elastic force when the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

Here, using FIG. 23, the method of attaching this weak spring 176 is demonstrated. The weak spring 176 is formed such that the diameter of both ends is larger than that of other parts. Thus, a groove 52A corresponding to one end of the weak spring 176 is formed at the center of the end of the second vane 52 on the side not in contact with the second roller 48 , and one end of the weak spring 176 fits into the groove 52A. Similarly, a groove 75A corresponding to the other end of the weak spring 176 is formed on the inner wall of the pipe 75 connected to the housing portion 472A, and the other end of the weak spring 176 fits into the groove 75A. Accordingly, the weak spring 176 can be attached to the back side of the second blade 52, and the second blade 52 can be pulled to the side opposite to the second roller 48. FIG. In addition, it is not limited to the case of using the weak springs 176 with large diameters at both ends and small other parts as described above, and it can also be installed in this way. For example, as shown in FIG. 24, when using weak springs with the same overall diameter, if Enlarging the distance between both ends of the spring prevents the weak spring from touching the second vane 52 . In addition, as shown in Figure 25, a hook 177 is set at one end of the weak spring, and the hook 177 is installed on the second blade 52 (a hole 178 for installing the hook 177 is formed on the second blade 52), and the traction the second blade 52 .

With the above configuration, the operation of the rotary compressor 310 will be described.

(1) The first operation mode (operation under normal load or high load)

First, the first operation mode in which the two rotating compression elements 32 and 34 perform compression work will be described. The controller 210 energizes the electric element 14 of the rotary compressor 310 in response to an operation command input from a controller on the side of the indoor unit (not shown) provided in the indoor unit. At this time, the controller 210 opens the electromagnetic valve 106 of the refrigerant piping 102 and closes the electromagnetic valve 105 of the refrigerant piping 101 while energizing the electric element 14 . Accordingly, the refrigerant pipe 102 communicates with the pipe 75 , and the controller 210 controls the electric element of the rotary compressor 310 in a state where the discharge side pressure of both the rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 . 14 revolutions, start. In addition, although the controller 210 controls to open the solenoid valve 106 and close the solenoid valve 105 while energizing the electric element 14, as long as the solenoid valves 105, 106 are opened and closed before the rotary compressor 310 is started, For example, the controller 210 may open the electromagnetic valve 106 and close the electromagnetic valve 105 before energizing the electric element 14 .

In this way, when the stator coil 28 of the electric element 14 is energized through the terminal 20 and the wiring not shown, the electric element 14 starts and the rotor 24 rotates. By this rotation, the first and second rollers 46 , 48 are fitted to vertical eccentric portions 42 , 44 provided integrally with the rotating shaft 16 , and rotate eccentrically in the first and second cylinders 38 , 40 .

Accordingly, the refrigerant flows from the refrigerant piping 100 of the rotary compressor 310 into the accumulator 146 . At this time, as described above, since the solenoid valve 105 of the refrigerant pipe 101 is closed, the refrigerant passing through the suction side of the two rotary compression elements 32, 34 of the refrigerant pipe 100 does not flow into the pipe 75, but It all flows into the pressure accumulator 146 .

After the refrigerant that has flowed into the pressure accumulator 146 is separated into gas and liquid here, only the refrigerant gas enters the refrigerant introduction pipe 92 and the refrigerant introduction pipe 94 opened in the pressure accumulator 146 . . The refrigerant gas that has entered the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

The refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas. It passes through a discharge port (not shown) and is discharged into the discharge muffler chamber 62 .

Here, the inside of the refrigerant circuit is at a balanced pressure when the rotary compressor 310 is started. That is, since the pressure is gradually balanced after the last operation of the rotary compressor 310 is stopped, and when a predetermined time elapses, the entire refrigerant circuit becomes a balanced pressure, so the entire refrigerant circuit becomes a balanced pressure. In the case where the rotary compressor 310 is started, immediately after the rotary compressor 310 is started, the pressure of the refrigerant on the discharge side of the two rotary compression elements 32 and 34 applied as the back pressure of the second blade 52 become the approximate equilibrium pressure. Similarly, the pressure in the second cylinder 40 also becomes a substantially balanced pressure.

Therefore, the second vane 52 cannot be made to follow the second roller 48 until the pressure on the discharge side of both rotary compression elements 32 and 34 rises to a certain level. Therefore, in the second rotary compression element 34, substantially no compression work is performed, and only the first rotary compression element 32 provided with the spring 74 completes the compression work of the refrigerant.

In this case, since the state in the refrigerant circuit is unstable immediately after the startup, the pulsation of the discharge side pressures of both rotary compression elements 32 , 34 also significantly increases. Therefore, in the case of starting with the discharge side pressures of both rotary compression elements 32, 34 being applied, there is a problem that the second vane 52 is swayed due to the pulsation of the discharge side pressures of both rotary compression elements 32, 34. The followability deteriorates, and the second blade 52 collides with the second roller 48 to generate a collision sound.

However, in this embodiment, by providing the weak spring 176 for tension load that pulls the second blade 52 to the side opposite to the second roller 48, the tensile force of the weak spring 76 causes the second blade 52 to Since it does not appear in the second cylinder 40, it is possible to avoid the problem that the second vane 52 collides with the second roller 48 to generate a collision sound.

On the other hand, the refrigerant gas compressed by the first rotary compression element 32 and discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cap 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . On the other hand, since the controller 210 opens the solenoid valve 106 as described above, part of the refrigerant passing through the refrigerant discharge pipe 96 flows from the refrigerant pipe 102 through the pipe 75 into the housing portion 472A.

On the other hand, the refrigerant gas flowing into the outdoor heat exchanger 152 releases heat, is depressurized by the expansion valve 154 , and then flows into the indoor heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 310 is repeated.

On the other hand, when the rotary compressor 310 is activated, a high and low pressure difference gradually occurs in the refrigerant circuit 10 after a predetermined time has elapsed. That is, the suction side pressure of the first rotary compression element 32 becomes low pressure, and the discharge side pressure becomes high pressure. Accordingly, the second vane 52 follows the second roller 48 due to the discharge side pressure, and performs compression work even in the second rotating compression element 34 . Here, since the tensile force of the weak spring 176 is equal to or less than the case where the suction side pressure of the first rotary compression element 32 (or both rotary compression elements 32 , 34 ) is applied as the back pressure of the second vane 52 Therefore, the second vane 52 can follow the second roller 48 without being affected by the high pressure as the discharge side pressure.

Further, refrigerant gas compressed by the operation of the second roller 48 and the second vane 52 to become high temperature and high pressure is discharged from the high pressure chamber side of the second cylinder 40 through the discharge port 49 to the discharge muffler chamber 64 . The refrigerant gas discharged into the discharge muffling chamber 64 passes through the communication passage 120 , is discharged into the discharge muffling chamber 62 , and joins the refrigerant gas compressed by the first rotary compression element 32 . Then, the joined refrigerant gas is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cap 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . On the other hand, since the solenoid valve 106 is opened by the controller 210 as described above, part of the refrigerant passing through the refrigerant discharge pipe 96 flows from the refrigerant pipe 102 through the pipe 75 into the accommodating portion 472A.

On the other hand, the refrigerant gas flowing into the outdoor heat exchanger 152 releases heat, is depressurized by the expansion valve 154 , and then flows into the indoor heat exchanger 156 . The refrigerant evaporates in the indoor side heat exchanger 156 and absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 310 is repeated.

(2) Switching from the first operation mode to the second operation mode (operation at light load)

Next, the controller 210 switches from the first operation mode to the second operation mode when the room changes from the above-mentioned normal load or high load state to a light load state. The second operation mode is a mode in which only the first rotating compression element 32 performs compression work substantially, and is an operation mode in which the indoor load is light, and the electric element 14 rotates at a low speed in the above-mentioned first operation mode. In the small capacity region of the compression system CS, the compression work is performed by only the first rotating compression element 32, compared with the case where the compression work is performed by the first and second cylinders 38, 40, since the compression work can be reduced Therefore, this amount increases the rotation speed of the electric element 14 even at light load, improves the operation efficiency of the electric element 14, and also makes it possible to reduce the leakage loss of the refrigerant.

Here, when switching from the first operation mode to the second operation mode, the controller 210 rotates the electric element 14 at a low speed, for example, controls the number of revolutions to be equal to or less than 50 Hz, and adjusts the compression ratio of the two-rotation compression element 32 to 50 Hz. The control is less than or equal to 3.0.

In this way, the controller 210 opens the electromagnetic valve 105 of the refrigerant piping 101 and closes the electromagnetic valve 106 of the refrigerant piping 102 . Accordingly, the refrigerant pipe 101 communicates with the pipe 75 , and part of the refrigerant passing through the suction side of the two rotary compression elements 32 and 34 of the refrigerant pipe 100 flows from the refrigerant pipe 101 through the pipe 75 into the housing portion 472A. . Accordingly, the storage portion 472A becomes the suction side pressure of both the rotary compression elements 32 and 34 , and applies the suction side pressure of both the rotary compression elements 32 and 34 as the back pressure of the second vane 52 .

Here, the back pressure in the second cylinder 40 and the second vane 52 becomes the same suction side pressure of both rotary compression elements 32 and 34 . At this time, if the weak spring 176 is not provided on the back pressure side of the second vane 52, since the pressure in the second cylinder 40 is the same as that of the second vane 52 as described above, there is a problem that the second It takes time for the two blades 52 to be introduced from the second cylinder 40 , during this period, the second blades 52 collide with the second roller 48 to generate a collision sound.

However, by providing the weak spring 176 for tensile load, the second blade 52 is pulled toward the storage portion 472A side opposite to the second roller 48 by the tensile force of the weak spring 176, and is stored in the storage portion 472A. Inside the guide groove 72. Accordingly, when shifting to the second operation mode, the second vane 52 can be drawn in from the second cylinder 40 early and accommodated in the guide groove 72 .

Accordingly, problems such as collision noise between the second vane 52 and the second roller 48 can be avoided in advance, and it is possible to switch to the second operation mode in which substantially only the first rotating compression element 32 completes the compression work.

(3) The second operation mode

Next, the operation of rotary compressor 310 in the second operation mode will be described. In addition, the solenoid valve 105 of the refrigerant pipe 101 is opened and the solenoid valve 106 of the refrigerant pipe 102 is closed, similarly to the transition from the first operation mode to the second operation mode described above. The low-pressure refrigerant flowing from the refrigerant piping 100 of the rotary compressor 310 into the accumulator 146 is gas-liquid separated here, and only the refrigerant gas enters the refrigerant opening in the accumulator 146. discharge pipe 92. The low-pressure refrigerant gas entering the refrigerant introduction pipe 92 is sucked into the low-pressure chamber side of the first cylinder 38 of the first rotary compression element 32 through the suction passage 58 .

On the other hand, since the solenoid valve 105 of the refrigerant pipe 101 is opened by the controller 210 , part of the refrigerant passing through the refrigerant pipe 100 flows from the refrigerant pipe 101 through the pipe 75 into the housing portion 472A. Accordingly, the storage portion 472A becomes the suction side pressure of the first rotary compression element 32 , and the suction side pressure of the first rotary compression element 32 is applied as the back pressure of the second vane 52 .

On the other hand, the refrigerant gas sucked into the low-pressure chamber side of the first cylinder 38 is compressed by the action of the first roller 46 and the first vane 50 to become a high-temperature and high-pressure refrigerant gas, which is released from the first cylinder 38 The high-pressure chamber side is discharged into the discharge muffler chamber 62 through an unshown discharge port. The refrigerant gas discharged into the discharge muffler chamber 62 is discharged into the airtight container 12 through a hole (not shown) penetrating the cover member 63 .

Thereafter, the refrigerant in the airtight container 12 is discharged to the outside from the refrigerant discharge pipe 96 formed on the end cap 12B of the airtight container 12 , and flows into the outdoor heat exchanger 152 . In addition, since the solenoid valve 106 is closed as described above, the refrigerant on the discharge side of the first rotary compression element 32 flowing through the refrigerant discharge pipe 96 does not flow into the pipe 75 but all flows into the outdoor heat exchange unit. device 152. In this way, the refrigerant gas flowing into the outdoor heat exchanger 152 releases heat, is depressurized by the expansion valve 154 , and then flows into the indoor heat exchanger 156 . Here, the refrigerant evaporates, and at this time, absorbs heat from the air circulating in the room to exert a cooling effect and cool the room. Thereafter, a cycle in which the refrigerant is discharged from the indoor side heat exchanger 156 and sucked into the rotary compressor 310 is repeated.

In addition, due to the above-mentioned weak spring 176, in the second operation mode, the second vane 52 is pulled toward the storage portion 472A side (the side of the weak spring 176) opposite to the second roller 48, so that it does not appear in the second operation mode. Inside the second cylinder 40. Accordingly, during operation in the second operation mode, the problem that the second vane 52 appears in the second cylinder 40 and collides with the second roller 48 to generate a collision sound can be avoided in advance.

(4) Switching from the second operation mode to the first operation mode

On the other hand, the controller 210 switches from the second operation mode to the first operation mode when the room changes from the above-mentioned light load state to a normal load state or a high load state. Here, the switching operation from the second operation mode to the first operation mode will be described. In this case, the controller 210 controls to rotate the electric element 14 at a low speed (the number of revolutions is equal to or less than 50 Hz), so that the compression ratio of the two rotating compression elements 32 and 34 is equal to or less than 3.0. The controller 210 closes the electromagnetic valve 105 of the refrigerant piping 101 and opens the electromagnetic valve 106 of the refrigerant piping 102 .

As a result, the refrigerant pipe 102 communicates with the pipe 75 , and the refrigerant on the discharge side of both the rotary compression elements 32 and 34 flows into the housing portion 472A, and the pressure of the two rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 . discharge side pressure.

As the back pressure of the second vane 52, by applying the discharge side pressure of the two rotary compression elements 32, 34, since the biasing force for biasing the second vane 52 toward the second roller 48 is greater than the tensile force of the weak spring 176, the second The two blades 52 are pushed toward the second roller 48 side by the high pressure of the housing portion 472A, and follow them. Accordingly, in the second rotary compression element 34, the compression work starts again.

As described above, according to the present invention, it is possible to improve the performance and reliability of the compression system CS having the rotary compressor 310 that can be used by switching between the first operation mode and the second operation mode, In the above-mentioned first operation mode, the first and second rotary compression elements 32 and 34 perform compression work, and in the above-mentioned second operation mode, substantially only the first rotary compression element 32 performs compression work.

Accordingly, by configuring the refrigerant circuit of the air conditioner using the compression system CS, the operating efficiency and performance of the air conditioner can be improved, and power consumption can also be reduced.

In addition, in the present embodiment, the controller 210 opens the solenoid valve 106 of the refrigerant pipe 102 to communicate with the refrigerant during the first operation mode, when starting up, and when switching from the second operation mode to the first operation mode. The refrigerant pipe 102 and the pipe 75 allow the refrigerant on the discharge side of the two rotary compression elements 32 and 34 to flow into the housing portion 472A, and the discharge side pressure of the two rotary compression elements 32 and 34 is applied as the back pressure of the second vane 52 . However, it is not limited thereto, and an intermediate pressure between the suction side pressure and the discharge side pressure of both rotary compression elements 32 and 34 may be applied as the back pressure of the second vane 52 . Even in this case, since the tensile force of the weak spring 176 is set to be equal to or less than the pressure on the suction side of the above-mentioned two rotary compression elements 32, 34 or the first rotary compression element 32 as the back pressure of the second vane 52 Since the spring force is applied under pressure, the second blade 52 can follow the second roller 48 without being affected.

In addition, in each of the above-mentioned embodiments, as the refrigerant, HFC or HC-based refrigerants are used, but it is also possible to use carbon dioxide and other refrigerants with a large high-pressure difference. For example, as the refrigerant, it is also possible to A refrigerant combining carbon dioxide and PAG (polyglycol) is used. In this case, since the refrigerant compressed by the respective rotary compression elements 32 and 34 has a very high pressure, if the discharge muffler chamber 62 is made to cover the upper part of the upper support member 54 with the cover member 63 If the side shape is different, the cover member 63 may be damaged due to the high pressure.

Therefore, if the shape of the discharge muffler chamber on the upper side of the upper support member 54 where the refrigerant compressed by the two rotary compression elements 32 and 34 merges is shaped as shown in FIG. 8 , pressure resistance can be ensured. That is, the discharge muffler chamber 162 in FIG. 8 is configured by forming a recessed portion on the upper side of the upper support member 54 and closing the recessed portion with an upper cover 66 having a predetermined thickness. Accordingly, the present invention can be applied even in the case of containing a refrigerant having a large high-pressure difference such as carbon dioxide.

In addition, in each of the above-mentioned embodiments, description has been made using a rotary compressor whose rotary shaft 16 is vertically mounted, but this invention is of course also applicable to a case of using a rotary compressor whose rotary shaft is horizontally mounted.

Furthermore, in the above-mentioned embodiments, a two-cylinder rotary compressor is used, of course, it can also be applied to a compression system of a multi-cylinder rotary compressor with three or more rotary compression elements.

Claims (14)

1. compression system, this compression system has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compressor only suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that

From above-mentioned second operation mode during to the conversion of above-mentioned first operation mode, in back pressure as above-mentioned second blade, after having applied the discharge side pressure of above-mentioned two rotation compressing members, apply the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure.

2. compression system, this compression system has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compressor only suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that

Be provided for controlling control valve unit to the refrigerant circulation of above-mentioned second cylinder,

During to the conversion of above-mentioned second operation mode,,, applying the suction side pressure of above-mentioned two rotation compressing members from above-mentioned first operation mode as the back pressure of above-mentioned second blade cutting off by above-mentioned control valve unit after the refrigerant of above-mentioned second cylinder flows into.

3. compression system, this compression system has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compressor only suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that

Be provided for controlling control valve unit to the refrigerant circulation of above-mentioned second cylinder,

In above-mentioned first operation mode,, make refrigerant flow into above-mentioned second cylinder by above-mentioned control valve unit, and back pressure as above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure, in above-mentioned second operation mode, by above-mentioned control valve unit, prevention flows into refrigerant to above-mentioned second cylinder, and,, apply the suction side pressure of above-mentioned two rotation compressing members as the back pressure of above-mentioned second blade, simultaneously

From above-mentioned second operation mode during to the conversion of above-mentioned first operation mode, in back pressure as above-mentioned second blade, after having applied the discharge side pressure of above-mentioned two rotation compressing members, apply the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure, from above-mentioned first operation mode during to the conversion of above-mentioned second operation mode, cutting off by above-mentioned control valve unit after the refrigerant of above-mentioned second cylinder flows into, as the back pressure of above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members.

4. as each the described compression system in the claim 1 to 3, it is characterized in that, when above-mentioned mode switch, make the above-mentioned driving element low speed rotation of above-mentioned compression system, multi-cylinder rotary compressor, making the compression ratio of above-mentioned first rotation compressing member or two rotation compressing members is smaller or equal to 3.0.

5. a refrigerating plant is characterized in that, uses each the described compression system in the claim 1 to 4, constitutes cryogen circuit.

6. compression system, this compression system has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade contacts with this first and second roller, to be divided into low pressure chamber side and hyperbaric chamber side in above-mentioned each cylinder respectively, simultaneously, this compression system, multi-cylinder rotary compressor only suppresses above-mentioned first blade by spring members to above-mentioned first roller, it is characterized in that

When the above-mentioned compression system, multi-cylinder rotary compressor of starting, in back pressure as above-mentioned second blade, apply the state starting down of the suction side pressure of above-mentioned two rotation compressing members, simultaneously, after starting,, apply the discharge side pressure of above-mentioned two rotation compressing members as the back pressure of above-mentioned second blade, then, make the back pressure of above-mentioned second blade become the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure.

7. compression system as claimed in claim 6, it is characterized in that, above-mentioned compression system, multi-cylinder rotary compressor can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, above-mentioned two rotation compressing members compress work done, at above-mentioned second operation mode, have only the above-mentioned first rotation compressing member to compress work done in fact.

8. a refrigerating plant is characterized in that, uses claim 6 or 7 described compression systeies, constitutes cryogen circuit.

9. compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of respectively first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade contacts with this first and second roller, to be divided into low pressure chamber side and hyperbaric chamber side in above-mentioned each cylinder respectively, simultaneously, this compression system, multi-cylinder rotary compressor only suppresses above-mentioned first blade by spring members to above-mentioned first roller, it is characterized in that

Have back pressure chamber, this back pressure chamber is used for above-mentioned second blade is applied back pressure, it is suppressed to above-mentioned second roller,

With this back pressure chamber as baffler chamber with regulation spatial volume.

10. compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of respectively first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade contacts with this first and second roller, to be divided into low pressure chamber side and hyperbaric chamber side in above-mentioned each cylinder respectively, simultaneously, this compression system, multi-cylinder rotary compressor only suppresses above-mentioned first blade by spring members to above-mentioned first roller, it is characterized in that

Have the back pressure path that is used for above-mentioned second blade is applied back pressure,

Make this back pressure with the cross-section area of path mean value more than or equal to the surface area that exposes above-mentioned second blade in above-mentioned second cylinder.

11. compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compression system, multi-cylinder rotary compressor suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that

Be provided with above-mentioned second blade suppressed mechanism to what above-mentioned second roller suppressed,

Make this elastic force pressure that suppresses mechanism apply elastic force pressure under the situation as the back pressure of above-mentioned second blade smaller or equal to suction side pressure with the above-mentioned two rotation compressing members or the first rotation compressing member.

12. compression system, multi-cylinder rotary compressor as claimed in claim 11 is characterized in that, is provided for controlling the control valve unit to the refrigerant circulation of above-mentioned second cylinder,

In above-mentioned first operation mode, make refrigerant flow into above-mentioned second cylinder by above-mentioned control valve unit, and back pressure as above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure, or apply the above-mentioned two discharge side pressure of rotating compressing members, in above-mentioned second operation mode, cut off to above-mentioned second cylinder inflow refrigerant by above-mentioned control valve unit, and, as the back pressure of above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members.

13. compression system, this compression system has compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compressor suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that

Be provided for controlling to the control valve unit of the refrigerant circulation of above-mentioned second cylinder and

Above-mentioned second blade is suppressed mechanism to what above-mentioned second roller suppressed,

Make this elastic force pressure that suppresses mechanism apply elastic force pressure under the situation as the back pressure of above-mentioned second blade smaller or equal to suction side pressure with the above-mentioned two rotation compressing members or the first rotation compressing member, simultaneously,

In above-mentioned first operation mode, make refrigerant flow into above-mentioned second cylinder by above-mentioned control valve unit, and back pressure as above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure, or apply the above-mentioned two discharge side pressure of rotating compressing members, in above-mentioned second operation mode, cut off to above-mentioned second cylinder inflow refrigerant by above-mentioned control valve unit, and, as the back pressure of above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members.

14. compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compression system, multi-cylinder rotary compressor suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that

Opposite side in the above-mentioned second roller side of above-mentioned second blade is provided with the weak spring that tensile load is used,

The tensile force that makes this weak spring is smaller or equal to the elastic force pressure that the suction side pressure of the above-mentioned two rotation compressing members or the first rotation compressing member is applied as the back pressure of above-mentioned second blade under the situation.

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