WO2018220747A1 - Scroll compressor and refrigeration cycle apparatus - Google Patents

Abstract

This scroll compressor is provided with: an oil separator which separates oil from a refrigerant discharged from a compression mechanism; an oil return pipe, one end of which is connected to the oil separator; and a first pump element which is connected to the other end of the oil return pipe and which supplies oil to a bearing operating space through an intra-shaft flow channel formed within a rotary shaft. The scroll compressor is configured such that the oil within the oil separator is returned directly to the first pump element through the oil return pipe and then supplied to the bearing operating space from the first pump element, whereby the pressure within the bearing operating space is kept higher than that in a suction space.

Description

Scroll compressor and refrigeration cycle apparatus

The present invention relates to a low-pressure shell type scroll compressor and a refrigeration cycle apparatus.

Conventionally, in a scroll compressor, the refrigerant is compressed in a compression chamber configured by meshing each spiral body by swinging the swing scroll with respect to the fixed scroll. In such a scroll compressor, by integrating the processing error and assembly error of each of the fixed scroll and the swing scroll, the distance between the respective tip portions of the two spiral bodies and the opposite scroll base plate is obtained. An axial gap is formed in When a gap is generated in this way, the refrigerant in the compression chamber leaks from the gap and the performance of the compressor is deteriorated.

As a general workaround for this problem, a ring-shaped back pressure space is provided on the back, which is the surface opposite to the fixed scroll of the orbiting scroll, and a high-pressure refrigerant at the end of compression is introduced into the back pressure space. The swinging scroll is pressed against the fixed scroll side to eliminate the axial gap (see, for example, Patent Document 1).

JP 2010-101188 A

The scroll compressor of Patent Document 1 is a so-called low-pressure shell-type scroll compressor in which the inner space of the container becomes an intake pressure atmosphere. For this reason, it is structurally difficult to introduce sufficient pressing pressure to the back of the orbiting scroll only by the high pressure in the back pressure space. That is, in the low-pressure shell type scroll compressor, the internal space of the container is at a low pressure. For this reason, the space inside the back pressure space, that is, the space for the oscillating bearing of the orbiting scroll to rotate (hereinafter referred to as the bearing operating space) has a low pressure. Therefore, although the back pressure space can be increased in the back surface of the orbiting scroll, the bearing operating space is at a low pressure, so that the pressing force is not sufficient for the entire orbiting scroll. Therefore, the axial gap cannot be eliminated and leakage loss occurs.

解 消 To eliminate the gap in the axial direction, it is necessary to ensure sufficient back pressure to stably press the orbiting scroll against the fixed scroll side. For this purpose, it is conceivable to increase the diameter of the base plate of the orbiting scroll so that a sufficient pressure-receiving area on which the back pressure acts can be secured. However, with this measure, there is a problem that the size of the whole compressor is enlarged and the manufacturing cost is increased.

The present invention has been made in view of the above points, and in a low-pressure shell-type scroll compressor, it is possible to stably press the swing scroll toward the fixed scroll side while avoiding an increase in the size of the entire compressor. An object is to provide a scroll compressor and a refrigeration cycle apparatus.

A scroll compressor according to the present invention includes a container in which refrigerant is sucked into an internal suction space, an electric mechanism installed in the container, and an oil that is installed in the container and sucks oil together with the refrigerant in the suction space. A compression mechanism that compresses the refrigerant in a compression chamber constituted by a scroll and an orbiting scroll; a rotary shaft that is connected to the orbiting scroll via an orbiting bearing and that transmits the rotational force of the electric mechanism to the compression mechanism; A frame having a bearing operating space for supporting the rocking scroll on the back side opposite to the compression chamber of the dynamic scroll and housing the rocking bearing between the rocking scroll and oil from the refrigerant discharged from the compression mechanism. An oil separator to be separated, an oil return pipe having one end connected to the oil separator, and an oil return pipe connected to the other end of the oil return pipe to supply oil to the bearing operating space via an in-shaft channel formed in the rotating shaft. With first pump element The oil in the oil separator is returned directly to the first pump element through the oil return pipe and supplied to the bearing operating space from the first pump element, so that the pressure in the bearing operating space is higher than the pressure in the suction space. It will be preserved.

The refrigeration cycle apparatus according to the present invention includes a scroll compressor, a condenser, a decompression device, and an evaporator.

According to the present invention, since oil is supplied directly from the oil separator to the in-axis flow path of the rotating shaft, high pressure can be introduced into the bearing operating space communicating with the in-axis flow path. Therefore, it is possible to stably press the orbiting scroll toward the fixed scroll while avoiding an increase in the size of the entire compressor.

It is a schematic longitudinal cross-sectional view of the whole structure of the scroll compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing of the positional relationship of the horizontal direction of an Oldham ring and a sealing member in the scroll compressor which concerns on Embodiment 1 of this invention. It is a schematic longitudinal cross-sectional view of the whole structure of the scroll compressor which concerns on Embodiment 2 of this invention. It is a schematic longitudinal cross-sectional view of the whole structure of the scroll compressor which concerns on Embodiment 3 of this invention. It is a schematic longitudinal cross-sectional view of the whole structure of the scroll compressor which concerns on Embodiment 4 of this invention. It is a schematic longitudinal cross-sectional view of the whole structure of the scroll compressor which concerns on Embodiment 5 of this invention. It is a schematic longitudinal cross-sectional view of the whole structure of the scroll compressor which concerns on Embodiment 6 of this invention. It is a refrigerant circuit figure of the refrigerating cycle device concerning Embodiment 7 of the present invention. It is a figure which shows schematic structure of the other oil separator applied to the refrigerating-cycle apparatus which concerns on Embodiment 7 of this invention. It is a figure which shows schematic structure of another oil separator applied to the refrigerating-cycle apparatus which concerns on Embodiment 7 of this invention.

Hereinafter, a scroll compressor according to an embodiment of the present invention will be described with reference to the drawings. Here, in FIG. 1 and the following drawings, the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification. Further, the pressure and compression ratios are not particularly determined in relation to absolute values, but are relatively determined in terms of the state and operation of the system, apparatus, and the like.

Embodiment 1 FIG.
FIG. 1 is a schematic longitudinal sectional view of the overall configuration of a scroll compressor according to Embodiment 1 of the present invention. In FIG. 1, arrows indicate the flow of refrigerant and oil. The same applies to the drawings described later.
The scroll compressor 100A of the first embodiment is a low-pressure shell type in which the internal space of the container 100 is a suction pressure. 1 illustrates a so-called vertical type scroll compressor that is used in a state in which a rotation shaft 6 described later is in the direction of gravity, but a horizontal type may be used.

The scroll compressor 100A includes the compression mechanism 3, the electric mechanism 110, and other components. The scroll compressor 100A has a configuration in which these components are housed in a container 100 that forms an outer shell. The compression mechanism 3 and the electric mechanism 110 are connected via the rotating shaft 6, and the rotational force generated by the electric mechanism 110 is transmitted to the compression mechanism 3 via the rotating shaft 6, and the rotational force causes the compression mechanism 3 to The refrigerant is compressed.

The container 100 is provided with a suction pipe 101 for sucking the refrigerant and a discharge pipe 102 for discharging the refrigerant.

In the container 100, a frame 7 and a sub frame 9 for fixing the compression mechanism 3 to the container 100 are arranged. The frame 7 is disposed above the electric mechanism 110 and below the compression mechanism 3, and is fixed to the inner peripheral surface of the container 100 by shrink fitting, welding, or the like. The subframe 9 is disposed on the lower side of the electric mechanism 110, and is fixed to the inner peripheral surface of the container 100 by shrink fitting, welding, or the like via the subframe plate 9a. A pump element 111 including a positive displacement pump is attached below the subframe 9 so as to support the rotary shaft 6 in the axial direction at the upper end surface. The pump element 111 corresponds to the first pump element of the present invention.

Here, the space in the container 100 is defined as follows. Of the internal space of the container 100, an inner wall of a recess formed on the upper surface of the frame 7, and an outermost peripheral surface of a structural body portion that meshes a swinging spiral body 2 b and a fixed spiral body 1 b described later of the compression mechanism 3. The space formed by the above is called a spiral installation space 70. Of the internal space of the container 100, a space below the frame 7 is referred to as a shell suction space 71. The shell suction space 71 is a low-pressure space filled with the suction refrigerant flowing from the suction pipe 101. Of the internal space of the container 100, a space closer to the discharge pipe 102 than a fixed base plate 1 a described later of the compression mechanism 3 is called a shell discharge space 72. Of the internal space of the container 100, a space formed in the frame 7 for accommodating a rocking bearing 2c described later and rotating the rocking bearing 2c is referred to as a bearing operation space 73.

The compression mechanism 3 has a fixed scroll 1 and a swing scroll 2. The fixed scroll 1 is fixedly arranged with respect to the frame 7. The orbiting scroll 2 is disposed on the lower side of the fixed scroll 1 and is supported on the eccentric shaft portion 6a of the rotating shaft 6 so as to be freely swingable. Also, an Oldham ring 14 is installed between the orbiting scroll 2 and the frame 7 to prevent the orbiting scroll 2 from rotating.

The fixed scroll 1 has a fixed base plate 1a and a fixed spiral body 1b provided upright on one surface of the fixed base plate 1a. The swing scroll 2 has a swing base plate 2a and a swing spiral body 2b provided on one surface of the swing base plate 2a. The fixed scroll 1 and the oscillating scroll 2 are disposed in the container 100 in a symmetrical spiral shape in which the fixed vortex body 1b and the oscillating spiral body 2b are engaged with each other in the opposite phase with respect to the rotation center of the rotary shaft 6. Yes. A compression chamber 8 is formed between the fixed spiral body 1b and the oscillating spiral body 2b. The compression chamber 8 has a volume that decreases from the radially outer side toward the inner side as the rotary shaft 6 rotates.

Further, a discharge port 1c communicating with the compression chamber 8 is formed through the fixed base plate 1a of the fixed scroll 1, and a discharge valve 11 is provided in the discharge port 1c. A discharge muffler 12 is attached so as to cover the discharge port 1c. A discharge port 12 c is formed through the discharge muffler 12.

A hollow cylindrical boss 2d is formed at a substantially central portion of a surface (hereinafter referred to as a back surface) opposite to the surface on which the rocking spiral body 2b is formed in the rocking base plate 2a of the rocking scroll 2. An eccentric shaft portion 6a formed at the upper end portion of the rotating shaft 6 is connected to the inside of the boss portion 2d.

A seal member 210 is arranged between the rocking scroll 2 and the frame 7 on the back of the rocking base plate 2a, and the bearing operating space 73 and the spiral installation space 70 are airtightly separated by the seal member 210.

FIG. 2 is an explanatory diagram of a horizontal positional relationship between the Oldham ring and the seal member in the scroll compressor according to Embodiment 1 of the present invention.
The seal member 210 is installed on the outer side in the radial direction with respect to the Oldham ring 14 and on the inner side in the radial direction with respect to the outer periphery of the swing base plate 2a. The seal member 210 is disposed at a position that does not interfere with the outer periphery of the Oldham ring 14 and the swing base plate 2a regardless of the rotational phase.

The rotary shaft 6 is composed of an eccentric shaft portion 6 a on the upper side of the rotary shaft 6, a main shaft portion 6 b, and a sub-shaft portion 6 c on the lower side of the rotary shaft 6. The eccentric shaft portion 6a is rotatably fitted to the boss portion 2d of the rocking scroll 2 via the rocking bearing 2c, and slides with the rocking bearing 2c via an oil film made of oil. The oscillating bearing 2c is fixed in the boss portion 2d by press-fitting a bearing material used for a sliding bearing such as a copper-lead alloy, and the oscillating scroll 2 oscillates as the rotary shaft 6 rotates. It is like that. The main shaft portion 6b is rotatably fitted to a main bearing 7b provided on the frame 7, and slides on the main bearing 7b through an oil film made of oil. The main bearing 7b is fixed to the frame 7 by press-fitting a bearing material used for a sliding bearing such as a copper-lead alloy.

The central portion of the sub-frame 9 includes a sub-bearing 10 made of a ball bearing, and supports the rotary shaft 6 in the radial direction below the electric mechanism 110. The auxiliary bearing 10 may have another bearing configuration other than the ball bearing. The auxiliary shaft portion 6 c of the rotating shaft 6 is fitted with the auxiliary bearing 10 and slides with the auxiliary bearing 10. The axis of the main shaft portion 6 b and the sub shaft portion 6 c coincides with the axis of the rotary shaft 6.

The electric mechanism 110 has an electric motor stator 110a and an electric motor rotor 110b. The motor stator 110a is connected to a glass terminal (not shown) existing between the frame 7 and the motor stator 110a with a lead wire (not shown) in order to obtain electric power from the outside. The electric motor rotor 110b is fixed to the rotating shaft 6 by shrink fitting or the like. Further, in order to balance the entire rotation system of the scroll compressor 100A, the first balance weight 60 is fixed to the rotating shaft 6, and the second balance weight 61 is fixed to the motor rotor 110b. Yes.

Further, the rotary shaft 6 is provided with an in-shaft channel 6d. The in-shaft channel 6d has an oil hole 6da extending in the axial direction at the center of the rotating shaft 6, and a plurality of oil supply holes 6db communicating with the oil hole 6da and extending in the radial direction. The oil supply hole 6db is formed at a position facing each of the rocking bearing 2c, the main bearing 7b, and the auxiliary bearing 10, and supplies the oil supplied from the pump element 111 to the sliding portion including these bearings. It is like that.

Oil flows in from the suction pipe 101 together with the refrigerant into the scroll compressor 100A configured as described above. The oil is used for the purpose of improving the lubricity of the sliding portion and the sealing function for suppressing gap leakage in the compression chamber 8. An oil separator 202A that separates oil from the refrigerant discharged from the scroll compressor 100A is disposed downstream of the scroll compressor 100A.

The oil separator 202A is connected to the discharge pipe 102 of the scroll compressor 100A by a pipe 201, and the oil separator 202A is connected to a pipe 203 that guides the separated refrigerant to a condenser (not shown). . An oil return pipe 204 is connected to the bottom of the oil separator 202A to return the oil accumulated at the bottom of the oil separator 202A to the scroll compressor 100A. With this configuration, the oil accumulated in the oil separator 202A is returned to the scroll compressor 100A via the oil return pipe 204, so that the oil in the scroll compressor 100A is not depleted and does not cause poor lubrication.

As a feature of the first embodiment, the high-pressure oil in the oil separator 202A is directly returned to the pump element 111 instead of the oil sump at the bottom of the container 100, and the in-axis flow path of the rotary shaft 6 from the pump element 111 is obtained. 6d so as to keep the inside flow path 6d at a high pressure. Since the in-shaft passage 6d communicates with the bearing operating space 73 via the rocking bearing 2c, the high-pressure oil in the in-shaft passage 6d is supplied to the bearing operating space 73. During operation, the pressure in the bearing operating space 73 is always kept high. In other words, the pressure in the bearing operating space 73 is always kept higher than the pressure in the shell suction space 71 so that the bearing operating space 73 functions as a back pressure space that presses the orbiting scroll 2 against the fixed scroll 1 side. It is characterized by that.

As a specific configuration for returning the high-pressure oil in the oil separator 202A directly to the pump element 111, one end of the oil return pipe 204 is connected to the bottom of the oil separator 202A, and the other end of the oil return pipe 204 penetrates the container 100. The pump element 111 is connected to the suction port. The discharge port of the pump element 111 is connected to the in-axis flow path 6d.

Next, the flow of the refrigerant will be described. The low-pressure refrigerant sucked into the shell suction space 71 in the container 100 from the suction pipe 101 passes through the communication channel 7 c formed in the frame 7 and flows into the spiral installation space 70. The refrigerant that has flowed into the spiral installation space 70 is sucked into the compression chamber 8 as the swing scroll 2 swings.

The refrigerant sucked into the compression chamber 8 is boosted from a low pressure to a high pressure by a geometric volume change of the compression chamber 8 accompanying the swing motion of the swing scroll 2. When the pressure in the compression chamber 8 becomes higher than the pressure in the shell discharge space 72, the discharge valve 11 is opened, and the refrigerant in the compression chamber 8 is discharged into the discharge muffler 12 from the discharge port 1c. The ink is discharged from the discharge port 12c to the outside of the discharge muffler 12. The high-pressure refrigerant discharged to the shell discharge space 72 outside the discharge muffler 12 is discharged from the discharge pipe 102. The refrigerant discharged from the discharge pipe 102 flows into the oil separator 202A through the pipe 201. In the oil separator 202A, the oil contained in the refrigerant is separated, and the refrigerant from which the oil has been separated flows out to the pipe 203 toward the condenser (not shown).

Next, the flow of oil will be described. High-pressure oil separated by the oil separator 202A from the high-pressure refrigerant discharged from the scroll compressor 100A is collected at the bottom of the oil separator 202A. When the rotary shaft 6 rotates and the pump element 111 operates, the high-pressure oil stored in the oil separator 202A is returned to the scroll compressor 100A through the oil return pipe 204. Here, the oil return pipe 204 is connected to the suction port of the pump element 111. For this reason, the high-pressure oil in the oil separator 202A is supplied through the oil return pipe 204 to the in-shaft flow path 6d of the rotary shaft 6 with a high pressure. The high-pressure oil supplied to the in-shaft passage 6d is supplied to sliding parts such as the rocking bearing 2c, the main bearing 7b, and the auxiliary bearing 10. Part of the oil supplied to the sliding portion is supplied with a high pressure to the bearing operating space 73 located on the downstream side of the rocking bearing 2c and the main bearing 7b. Thus, the oil is supplied to the bearing operation space 73 with a high pressure, so that the pressure in the bearing operation space 73 becomes high.

The bearing operating space 73 is airtightly separated from the spiral installation space 70 by the seal member 210. For this reason, the high-pressure oil in the bearing operating space 73 does not flow into the spiral installation space 70 but flows out into the shell suction space 71 through the gap of the main bearing 7b. The oil flowing out into the shell suction space 71 is wound up by the flow of the refrigerant gas sucked from the suction pipe 101 and sucked into the compression chamber 8. The oil sucked into the compression chamber 8 together with the refrigerant gas is compressed together with the refrigerant in the compression chamber 8 and then discharged to the outside of the compressor. The oil discharged together with the refrigerant to the outside of the compressor flows into the oil separator 202A through the pipe 201, is separated from the refrigerant gas, and the separated oil is stored at the bottom of the oil separator 202A.

Next, the gas load acting on the orbiting scroll 2 will be described. On the upper surface of the swing base plate 2 a of the swing scroll 2, a gas load is applied by the refrigerant having the discharge pressure from the intermediate pressure of the compression chamber 8. On the other hand, a gas load due to a high-pressure refrigerant including high-pressure oil supplied to the bearing operating space 73 acts on the back surface of the rocking base plate 2 a of the rocking scroll 2. Therefore, the moving direction of the orbiting scroll 2 in the axial direction is determined by the difference in the gas load acting on the orbiting base plate 2a of the orbiting scroll 2 from above and below. That is, when the gas load in the bearing operating space 73 is larger, the orbiting scroll 2 moves upward and contacts the fixed scroll 1 in the axial direction.

As described above, in the first embodiment, the high-pressure oil separated by the oil separator 202A is directly supplied to the in-shaft passage 6d of the rotating shaft 6, and the high-pressure oil in the in-shaft passage 6d is supplied to the bearing operating space. By supplying to 73, it becomes possible to introduce a high pressure into the bearing operating space 73. For this reason, the load generated in the bearing operating space 73 can be used as a force for pressing the orbiting scroll 2 against the fixed scroll 1 side. That is, in the low-pressure shell type scroll compressor, the bearing operating space 73 that has been conventionally low pressure can be made high, so that the rocking scroll 2 can be stably fixed even when the base plate diameter of the rocking scroll 2 is small. It is possible to secure a pressure receiving area necessary for pressing against the first side. Accordingly, it is possible to provide an inexpensive and highly reliable scroll compressor 100A while avoiding an increase in the size of the entire compressor.

In addition, since the swing scroll 2 can be stably pressed against the fixed scroll 1 side, axial gaps at the respective distal ends of the fixed spiral body 1b and the swing spiral body 2b can be eliminated, and leakage loss can be reduced. Can be reduced.

Furthermore, in the first embodiment, oil is directly supplied from the oil separator 202A to the in-axis flow path 6d of the rotating shaft 6 without going through the oil sump in the container 100. For this reason, it is not necessary to supply the oil accumulated at the bottom of the container 100 to the in-shaft channel 6d. Therefore, even when the refrigerant sucked into the scroll compressor 100A is moistened, that is, when the dryness of the refrigerant is lowered, the oil supplied to the sliding portion such as the bearing is diluted by the sucked refrigerant. The oil having a high viscosity returned from the oil separator 202A can always be supplied to the sliding portion. In addition, since the oil having a high viscosity can always be supplied to the sliding portion, the scroll compressor 100A having high reliability is provided even in an operating condition where a high compression ratio is required in a cold region and the force applied to the bearing is increased. can do.

Embodiment 2. FIG.
FIG. 3 is a schematic longitudinal sectional view of the overall configuration of the scroll compressor according to Embodiment 2 of the present invention. Hereinafter, the second embodiment will be described focusing on a configuration different from the first embodiment. The second embodiment has the configuration of the first embodiment. In addition to obtaining the same effect as the first embodiment, the second embodiment has a specific configuration of the second embodiment described below. , With further effects. The embodiment described later also has the same configuration as that of the first embodiment, and the same effect as that of the first embodiment can be obtained.

In the scroll compressor 100B of the second embodiment, a communication flow path 220 that connects the bearing operating space 73 and the shell suction space 71 is formed in the frame 7. A discharge valve 221 that opens and closes due to a pressure difference between the bearing operating space 73 and the shell suction space 71 is disposed at the end of the communication flow path 220. The discharge valve 221 is configured by a leaf spring-shaped reed valve. The discharge valve 221 is designed to open when the pressure in the bearing operating space 73 is excessively increased. The pressure at which the discharge valve 221 opens may be arbitrarily designed.

In the orbiting scroll 2 during the orbiting operation in the scroll compressor 100B, due to the compression action of the compression chamber 8, not only the axial force pressing the orbiting scroll 2 against the fixed scroll 1 but also radial force is generated. . If the force for pressing the orbiting scroll 2 against the fixed scroll 1 is insufficient, a so-called capsizing moment is generated that causes the orbiting scroll 2 to tilt, and the orbiting scroll 2 is overturned so that the operation is impossible. Become stable.

On the other hand, when the force for pressing the orbiting scroll 2 toward the fixed scroll 1 is excessive, the distal ends of the fixed spiral body 1b and the orbiting spiral body 2b are opposed to the distal end portion of the orbiting base plate 2a and The pressing force pressed against the fixed base plate 1a increases. For this reason, sliding loss increases and the performance of a compressor falls. Note that the pressing force of the orbiting scroll 2 increases under the high compression ratio operating condition in which the difference between the gas load due to the gas refrigerant in the bearing operating space 73 and the gas load due to the gas refrigerant at the discharge pressure in the compression chamber 8 is large.

In the second embodiment, as described above, the bearing operation space 73 communicates with the shell suction space 71 via the communication flow path 220, and the discharge valve 221 is provided. For this reason, under an operating condition in which the pressure in the bearing operating space 73 is excessively increased, the discharge valve 221 can be opened to relieve the pressure in the bearing operating space 73 to the shell suction space 71. On the other hand, since the discharge valve 221 is closed under operating conditions where the pressure in the bearing operating space 73 is small, the swing scroll 2 can be stably pressed against the fixed scroll 1 as in the first embodiment. Thus, by controlling the gas pressure in the bearing operating space 73 according to the operating conditions, a scroll compressor having high performance and reliability in a wide operating range can be provided.

In the second embodiment, the example in which the discharge valve 221 is configured by a leaf spring-shaped reed valve has been described. However, a slide valve in which the valve body and the spring are formed separately may be used. Similar effects can be obtained with the configuration. In order to optimize the pressure condition that the discharge valve 221 opens, the spring constant of the discharge valve 221 and the surplus load at the closed position may be adjusted.

Embodiment 3 FIG.
FIG. 4 is a schematic longitudinal sectional view of the overall configuration of the scroll compressor according to Embodiment 3 of the present invention. Hereinafter, the third embodiment will be described focusing on a configuration different from the first embodiment.
In the scroll compressor 100 </ b> C of the third embodiment, a ring-shaped recess is formed on the opposite surface of the frame 7 that slides with the back surface of the swing base plate 2 a of the swing scroll 2. A ring-shaped space is formed by the recess and the swing base plate 2 a of the swing scroll 2, and this space is a back pressure space 211.

The back pressure space 211 is formed outside the ring-shaped seal member 210, and the ring-shaped seal member 212 is disposed further outside the back pressure space 211. Therefore, the seal members 210 and 212 are arranged on the inner side and the outer side of the back pressure space 211, and the back pressure space 211 is in pressure with respect to each of the spiral installation space 70 and the bearing operation space 73. It has a sealed configuration. In the third embodiment, the rocking base plate 2 a of the rocking scroll 2 is formed with an internal flow path 213 that connects the back pressure space 211 and the compression chamber 8.

In the third embodiment configured as described above, the back pressure space 211 and the compression chamber 8 are intermittently communicated with each other through the internal flow path 213 as the swing scroll 2 swings. Then, the pressure in the compression chamber 8 at the rotational phase where the back pressure space 211 and the compression chamber 8 communicate with each other is introduced into the back pressure space 211. The back pressure space 211 is pressure-sealed with respect to each of the spiral installation space 70 and the bearing operation space 73 as described above, and a pressure different from that of the bearing operation space 73 is introduced. Therefore, different pressures are applied to the back surface of the rocking base plate 2a of the rocking scroll 2 from the back pressure space 211 and the bearing operating space 73, and the rocking scroll 2 is pressed against the fixed scroll 1 side. .

Here, in general, when the orbiting scroll 2 is pressed against the fixed scroll 1 by a single gas pressure, and when the orbiting scroll 2 is pressed against the fixed scroll 1 by a plurality of different gas pressures. In the case where a plurality of different gas loads are used, the degree of freedom in designing the pressing force is higher. For this reason, as described above, by adopting a configuration in which a plurality of different gas loads are applied to the orbiting scroll 2, it is possible to ensure a stable pressing force in a wider operating range.

Note that the pressure in the back pressure space 211 is determined by the compression ratio of the compression chamber 8 in a rotational phase where the back pressure space 211 and the compression chamber 8 communicate with each other. For this reason, when it is desired to reduce the pressing force of the orbiting scroll 2 against the fixed scroll 1, it is only necessary to determine the arrangement of the internal flow path 213 so as to communicate with a low compression ratio. Conversely, when the pressing force is to be increased, it is high. What is necessary is just to determine arrangement | positioning of the internal flow path 213 so that it may communicate by a compression ratio.

Embodiment 4 FIG.
FIG. 5 is a schematic longitudinal sectional view of the overall configuration of the scroll compressor according to Embodiment 4 of the present invention. Hereinafter, the fourth embodiment will be described focusing on the configuration different from the first embodiment.
The scroll compressor 100D according to the fourth embodiment has a configuration in which a new pump element 112 that pumps up oil accumulated in the oil sump 100a at the bottom of the container 100 is provided below the pump element 111. The pump element 112 is a positive displacement pump that is driven by the rotation of the rotary shaft 6. One end of an oil suction pipe 113 is connected to the suction port of the pump element 112, and the other end of the oil suction pipe 113 extends toward the bottom of the container 100 so as to be immersed in the oil in the oil reservoir 100a. One end of an oil supply pipe 114 is connected to the discharge port of the pump element 112, and the other end of the oil supply pipe 114 is connected to the spiral installation space 70.

With the above configuration, the oil accumulated in the oil sump 100a of the container 100 is sucked up into the oil suction pipe 113 by the pump element 112. The sucked oil is supplied to the spiral installation space 70 through the oil supply pipe 114. The pump element 112 corresponds to the second pump element of the present invention.

As described in the first embodiment, the high-pressure oil in the bearing operating space 73 flows out into the shell suction space 71 through the gap in the main bearing 7b. The oil that has flowed into the shell suction space 71 is wound up by the flow of the refrigerant gas sucked from the suction pipe 101 and sucked into the compression chamber 8. Here, under an operating condition where the flow rate of the refrigerant gas is high, the oil that has flowed out into the shell suction space 71 is wound up and sucked into the compression chamber 8 as described above. However, under the operating condition where the flow rate of the refrigerant gas is low, the effect of the refrigerant gas winding up the oil in the shell suction space 71 becomes small, so that the oil falls into the oil sump 100a of the container 100 and accumulates. When the amount of oil accumulated in the oil sump 100a of the container 100 increases, the amount of oil in the oil separator 202A decreases, so that the operating range in which oil can be stably supplied from the oil separator 202A to the sliding portion is limited. Become.

Here, in the fourth embodiment, the oil accumulated in the oil sump 100a of the container 100 is pumped up by the pump element 112 and supplied to the spiral installation space 70. For this reason, the oil supplied to the spiral installation space 70 is sucked into the compression chamber 8 and compressed, and then discharged from the discharge pipe 102 to the outside. That is, in the scroll compressor 100D of the fourth embodiment, the oil accumulated in the oil sump 100a of the container 100 is supplied to the spiral installation space 70 and is forced to flow out of the scroll compressor 100D. . For this reason, it is possible to suppress oil from being accumulated in the oil sump 100a of the container 100, and to stably supply oil from the oil separator 202A to the sliding portion. Thereby, a scroll compressor having high reliability in a wide operation range can be provided.

Embodiment 5 FIG.
FIG. 6 is a schematic longitudinal sectional view of the overall configuration of the scroll compressor according to Embodiment 5 of the present invention. Hereinafter, only the configuration of the fifth embodiment different from that of the first embodiment will be described.
The scroll compressor 100E according to the fifth embodiment is configured such that the suction pipe 101 is connected to the container 100 below the height position of the electric mechanism 110. That is, the suction pipe 101 was installed in the vicinity of the oil sump 100 a at the bottom of the container 100.

With this configuration, the oil accumulated in the oil sump 100a of the container 100 can be positively wound up by the refrigerant gas flowing into the container 100 from the suction pipe 101. Therefore, as in the fourth embodiment, the oil is prevented from collecting in the oil sump 100a of the container 100, and the oil flows out of the scroll compressor 100E. Thereby, oil can be stably supplied from the oil separator 202A to the sliding portion. Further, in the fifth embodiment, since only the position of the suction pipe 101 is changed, the same effect as in the fourth embodiment can be realized with a simpler structure.

Embodiment 6 FIG.
FIG. 7 is a schematic longitudinal sectional view of the overall configuration of the scroll compressor according to Embodiment 6 of the present invention. In the following, the sixth embodiment will be described focusing on the configuration different from the first embodiment.
The scroll compressor 100F according to the sixth embodiment has a configuration in which an oil separator 230 is provided in the container 100. For this reason, the oil separator 202A of Embodiment 1 is not connected to the scroll compressor 100F, and the oil return pipe 204 is not connected.

The oil separator 230 includes a cup-shaped member 231 installed in the shell discharge space 72 so as to cover the discharge port 1c instead of the discharge muffler 12 of the first embodiment. The cup-shaped member 231 has a side surface portion 231a and an upper surface portion 231b. A discharge port 231c is formed through the side surface portion 231a so that the refrigerant in the cup-shaped member 231 is discharged from the discharge port 231c. . Of the shell discharge space 72, a space surrounded by the cup-shaped member 231, the container 100, and the fixed base plate 1a of the fixed scroll 1 is an oil separation space 72a that separates oil from the refrigerant discharged from the discharge port 231c. It is supposed to function as. One end of the oil return pipe 232 is connected to the oil separation space 72a through the fixed base plate 1a, and the other end is connected to the suction port of the pump element 111.

In the scroll compressor 100F configured as described above, the oil separated in the oil separation space 72a is accumulated at the bottom of the oil separation space 72a, and the accumulated oil is collected in the suction port of the pump element 111 via the oil return pipe 232. It has come to be guided. The oil separator 230 may be of a centrifugal separation type that separates the two by a centrifugal force using the density difference between the refrigerant gas and the oil, or the oil is applied to a filter or a wall surface using the surface tension of the oil. The thing of the gravity separation system which makes it adhere and isolate | separates using gravity may be used.

According to the sixth embodiment, since it is not necessary to separately install an oil separator outside the scroll compressor 100F, the structure of the refrigeration cycle apparatus to which the scroll compressor 100F is applied can be simplified.

Embodiment 7 FIG.
The seventh embodiment relates to a refrigeration cycle apparatus including the scroll compressor configured as described above.

FIG. 8 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 7 of the present invention.
The refrigeration cycle apparatus 300 is a refrigerant in which a scroll compressor 301, an oil separator 202A, a condenser 302, a decompression device 303 configured by an expansion valve or a capillary tube, and an evaporator 304 are connected in order by refrigerant piping. It has a circuit. The refrigeration cycle apparatus 300 is further provided with an oil return pipe 204 that returns the oil separated by the oil separator 202A to the pump element 111 of the scroll compressor 301. As the scroll compressor 301, the scroll compressors 100A to 100E of the first to fifth embodiments are used. In addition, when the scroll compressor 100F of Embodiment 6 is used for the scroll compressor 301, since the oil separator 230 is incorporated in the scroll compressor 100F, the oil separator 202A of the refrigerant circuit is omitted. The

In the refrigeration cycle apparatus 300 configured as described above, the scroll compressor 301 sucks and compresses the refrigerant gas and then discharges it. The discharge gas discharged from the scroll compressor 301 flows into the oil separator 202A. In the oil separator 202A, the refrigerant and the oil mixed in the refrigerant are separated, and the refrigerant is cooled by the condenser 302. The refrigerant cooled by the condenser 302 is decompressed by the decompression device 303 and then heated by the evaporator 304 to become a refrigerant gas. The refrigerant gas flowing out of the evaporator 304 is sucked into the scroll compressor 301.

Also, the flow of oil discharged from the scroll compressor 301 together with the refrigerant is as described above.

As described above, in the refrigeration cycle apparatus 300 of the seventh embodiment, since the scroll compressor is applied, a highly reliable refrigeration cycle apparatus can be obtained.

Here, the oil separator 202A provided in the refrigeration cycle apparatus 300 is not limited to the oil separator 202A, and the oil separator 202A having the following configuration (1) or (2) may be used.

(1) Oil separator provided with baffle plate FIG. 9 is a diagram showing a schematic configuration of another oil separator applied to the refrigeration cycle apparatus according to Embodiment 7 of the present invention.
The oil separator 202B in FIG. 9 is installed so that the central axis of the oil separator 202B is in the direction of gravity, and a baffle plate 240 that divides the internal space of the oil separator 202B up and down in the installed state is provided inside the oil separator 202B. Is installed. Further, the baffle plate 240 is installed horizontally, and one or a plurality of through holes 240a are formed, and the upper and lower spaces of the baffle plate 240 communicate with each other through the through holes 240a.

Since oil is always stored inside the oil separator 202B, if the baffle plate 240 is not provided, the oil surface is agitated by the flow of the refrigerant gas inside the oil separator 202B. Thereby, oil flows out to the exterior of oil separator 202B with refrigerant gas, and oil separation efficiency falls. When the oil separation efficiency is lowered, the operating range in which oil can be stably supplied from the oil separator 202B to the sliding portion becomes narrow as in the case of the fourth embodiment.

In contrast, since the baffle plate 240 is installed inside the oil separator 202B, the inside of the oil separator 202B is divided into two spaces, that is, a bottom where oil is stored and an upper portion where refrigerant gas flows. As a result, the following effects can be obtained. That is, it is possible to prevent a part of the refrigerant gas flowing into the oil separator 202B from colliding with the baffle plate 240 and directly hitting the oil surface. Therefore, it can suppress that the oil stored in the bottom part of the oil separator 202B is wound up by the flow of the refrigerant gas. Thus, by using the oil separator 202B provided with the baffle plate 240, as a result, a refrigeration cycle apparatus having high reliability in a wide operation range can be provided.

The oil separator 202B may be a centrifugal separation method or a gravity separation method.

(2) Oil Separator with Separate Oil Separation Unit and Oil Storage Tank FIG. 10 is a diagram showing a schematic configuration of another oil separator applied to the refrigeration cycle apparatus according to Embodiment 7 of the present invention. It is.
An oil separator 202C in FIG. 10 has an oil separation unit 202a that separates oil and an oil storage tank 202b that stores oil separated by the oil separation unit 202a. By using the oil separator 202C configured as described above, a space where the flow rate of the refrigerant gas is large and a space where oil is stored can be separated. Thereby, similarly to the case of using the oil separator 202B, it is possible to provide the refrigeration cycle apparatus 300 having high reliability in a wide operation range.

Although the embodiments have been described above, the scroll compressor may be configured by appropriately combining the characteristic configurations of the embodiments. For example, each of the second, third, fifth, and sixth embodiments and the fourth embodiment are combined, and the scroll compressor shown in FIGS. 3, 4, 6, and 7 is further provided with a pump element 112. Also good. In addition, for example, the back pressure space 211 may be provided in the scroll compressor 100B shown in FIG. 3 by combining the second embodiment shown in FIG. 3 and the third embodiment shown in FIG.

1 fixed scroll, 1a fixed base plate, 1b fixed spiral body, 1c discharge port, 2 rocking scroll, 2a rocking base plate, 2b rocking spiral body, 2c rocking bearing, 2d boss part, 3 compression mechanism, 6 rotations Shaft, 6a Eccentric shaft part, 6b Main shaft part, 6c Sub shaft part, 6d In-shaft flow path, 6da oil hole, 6db oil supply hole, 7 frame, 7b main bearing, 7c communication flow path, 8 compression chamber, 9 subframe, 9a Sub-frame plate, 10 Sub-bearing, 11 Discharge valve, 12 Discharge muffler, 12c Discharge port, 14 Oldham ring, 60 1st balance weight, 61 2nd balance weight, 70 Spiral installation space, 71 Shell suction space, 72 Shell discharge Space, 72a oil separation space, 73 bearing operating space, 100 container, 100A scroll compressor, 00B scroll compressor, 100C scroll compressor, 100D scroll compressor, 100E scroll compressor, 100F scroll compressor, 100a oil sump, 101 suction pipe, 102 discharge pipe, 110 electric mechanism, 110a electric motor stator, 110b electric motor rotor , 111 pump element, 112 pump element, 113 oil suction pipe, 114 oil supply pipe, 201 pipe, 202A oil separator, 202B oil separator, 202C oil separator, 202a oil separator, 202b oil storage tank, 203 pipe, 204 oil return pipe, 210 seal member, 211 back pressure space, 212 seal member, 213 internal flow path, 220 communication flow path, 221 discharge valve, 230 oil separator, 231 cup-shaped member, 231a side surface part, 231b upper surface part, 31c the discharge port, 232 oil return pipe, 240 baffle plates, 240a through hole 300 refrigeration cycle apparatus, 301 a scroll compressor, 302 a condenser, 303 decompressor, 304 evaporator.

Claims (11)

A container into which the refrigerant is sucked into the internal suction space;
An electric mechanism installed inside the container;
A compression mechanism that is installed inside the container, sucks oil together with the refrigerant in the suction space, and compresses the refrigerant in a compression chamber composed of a fixed scroll and an orbiting scroll;
A rotating shaft coupled to the orbiting scroll via an orbiting bearing and transmitting the rotational force of the electric mechanism to the compression mechanism;
A frame having a bearing operating space for supporting the rocking scroll on the back side opposite to the compression chamber of the rocking scroll and housing the rocking bearing between the rocking scroll;
An oil separator for separating the oil from the refrigerant discharged from the compression mechanism;
An oil return pipe having one end connected to the oil separator;
A first pump element connected to the other end of the oil return pipe and supplying the oil to the bearing operating space via an in-shaft channel formed in the rotating shaft;
The oil in the oil separator is returned directly to the first pump element through the oil return pipe, and is supplied from the first pump element to the bearing operating space, so that the pressure in the bearing operating space is A scroll compressor that is kept higher than the pressure in the suction space. 2. A second pump element that sucks and discharges oil stored in an oil sump of the container, and an oil supply pipe that supplies the oil discharged from the second pump element to the compression chamber. The scroll compressor described. In a state where the container is installed so that the rotation axis is in the direction of gravity, the electric mechanism is disposed below the compression mechanism, and a suction pipe for sucking refrigerant into the container is higher than the electric mechanism. The scroll compressor according to claim 1, wherein the scroll compressor is connected to the container at a vertical position. The frame is formed with a communication channel that communicates the bearing operation space and the suction space, and opens and closes at an end of the communication channel due to a pressure difference between the bearing operation space and the suction space. The scroll compressor according to any one of claims 1 to 3, wherein a discharge valve is disposed. A back pressure space for pressing the rocking scroll against the fixed scroll side is formed on the back side of the rocking scroll, and the back pressure space is formed through an internal channel formed in the rocking scroll. The scroll compressor according to any one of claims 1 to 4, wherein the scroll compressor communicates with the compression chamber. The said internal flow path is formed in the said rocking scroll in the position which connects the said back pressure space and the said compression chamber intermittently when the said rocking scroll is rocking | fluctuating. Scroll compressor. The scroll compressor according to any one of claims 1 to 6, wherein the oil separator and the oil return pipe are installed in an internal space of the container. The fixed scroll is formed with a discharge port through which the refrigerant compressed in the compression chamber is discharged,
The oil separator is installed so as to cover the discharge port, and has a cup-shaped member having a side surface portion and an upper surface portion in which a discharge port is formed, and the cup-shaped member, the container, and the fixed scroll include The scroll compressor according to claim 7, wherein oil is separated from the refrigerant discharged from the discharge port to the oil separation space using the enclosed space as an oil separation space. A refrigeration cycle apparatus comprising the scroll compressor according to any one of claims 1 to 8, a condenser, a decompression device, and an evaporator. Comprising the oil separator;
The oil separator is installed such that the center axis of the oil separator is in the direction of gravity, and a baffle plate that divides the inside of the oil separator vertically in the installed state is installed, and the baffle plate penetrates The refrigeration cycle apparatus according to claim 9, which is dependent on claim 1 to claim 6, wherein a hole is formed, and a space above and below the baffle plate communicates with the through hole. Comprising the oil separator;
The oil separator according to any one of claims 1 to 6, wherein the oil separator is composed of an oil separation unit that separates oil and an oil storage tank that stores oil separated by the oil separation unit. The refrigeration cycle apparatus according to claim 9 that is dependent thereon.

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