JP2003129958A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of effectively suppressing the noises and vibration caused by discharge pulsation of refrigerant gas. SOLUTION: This rotary compressor is provided with an electric element in a sealed vessel and a rotary compression element driven by a rotary shaft of the electric element. It is provided with a cylinder constituting the rotary compression element, an upper part support member 54 blocking an opening face of the cylinder and having a bearing 54A of the rotary shaft at the center, and a discharge noise reduction chamber 62 formed in the upper part support member on a bearing outer side, communicated with the inside of the cylinder in a refrigerant flow-in part, and provided with a discharge passage 171. The discharge noise reduction chamber is composed of a plurality of divided chambers 62A to 62D and passages 62E, etc., communicating a plurality of these divided chambers mutually and having a small width. The refrigerant flow-in part and the discharge passage are provided in the divided chambers 62A, 62D at both ends which are communicated mutually, respectively.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor provided with an electric element and a rotary compression element driven by the electric element in a closed container.

[0002]

2. Description of the Related Art In a conventional rotary compressor of this type, in particular, an internal intermediate pressure type multi-stage compression type rotary compressor, a refrigerant gas is sucked into a low pressure chamber side of a cylinder from a suction port of a first rotary compression element, and a roller and a vane. Is compressed to an intermediate pressure and discharged from the high pressure chamber side of the cylinder into the closed container through the discharge port and the discharge muffling chamber.
Then, the intermediate pressure refrigerant gas in the closed container is sucked into the low pressure chamber side of the cylinder from the suction port of the second rotary compression element, and the second stage compression is performed by the operation of the roller and the vane, so that the high temperature and high pressure is achieved. It becomes refrigerant gas, flows into the radiator from the high pressure chamber side through the discharge port and the discharge muffling chamber, and after radiating heat,
The cycle of being squeezed by the expansion valve, absorbing heat by the evaporator, and being sucked into the first rotary compression element is repeated.

When a refrigerant having a large difference in high pressure and low pressure, for example, carbon dioxide (CO ₂ ) as an example of carbon dioxide is used as the refrigerant in the rotary compressor, the refrigerant pressure reaches 12 MPaG in the second rotary compression element which becomes high pressure. ,on the other hand,
It becomes 8 MPaG (intermediate pressure) in the first rotary compression element on the low stage side.

[0004]

In such an internal intermediate pressure type multi-stage compression type rotary compressor, the opening surface of the cylinder constituting each rotary compression element is closed by a support member, and the inside of the support member is covered by the above-mentioned structure. It constitutes the discharge silencer chamber. In this case, since the bearing of the rotary shaft is formed in the center of the support member, the discharge muffling chamber is formed by utilizing the space outside the bearing.

Since the discharge muffling chamber is constructed in such a limited space, its volume is limited. In addition, since the discharge muffling chamber is conventionally formed as a single chamber, there is a problem that the discharge pulsation of the refrigerant gas cannot be sufficiently absorbed and noise and vibration cannot be effectively suppressed.

The present invention has been made in order to solve the problems of the prior art, and provides a rotary compressor capable of effectively suppressing noise and vibration due to discharge pulsation of refrigerant gas.

[0007]

That is, a rotary compressor of the present invention comprises an electric element in a closed container and a rotary compression element driven by a rotary shaft of the electric element. A cylinder for constituting the element, a support member that closes the opening surface of the cylinder, has a bearing for the rotating shaft in the center, and a support member outside the bearing, and communicates with the inside of the cylinder at the refrigerant inflow portion. Together with a discharge muffling chamber having a refrigerant outflow portion, the discharge muffling chamber is composed of a plurality of divided chambers, and a narrow passage that communicates these plurality of divided chambers, refrigerant inflow portion and It is characterized in that the refrigerant outflow portion is provided in each of the divided chambers at both ends in communication with each other.

According to the present invention, in a rotary compressor provided with an electric element in a closed container and a rotary compression element driven by a rotary shaft of the electric element, a cylinder for constituting the rotary compression element, and It is a support member that has a bearing for the rotating shaft in the center and a support member outside the bearing that closes the opening surface of the cylinder and that communicates with the inside of the cylinder at the refrigerant inflow part, and has a discharge muffling equipped with a refrigerant outflow part The discharge muffling chamber includes a plurality of divided chambers and a narrow passage that communicates the plurality of divided chambers with each other. Since it is provided in each of the division chambers, the refrigerant gas compressed inside the cylinder and flowing into the discharge muffling chamber from the refrigerant inflow portion successively passes through the plurality of division chambers and the narrow passages communicating with each other and the refrigerant flow. Leaving the department.

As a result, the pulsation of the refrigerant gas is effectively absorbed in the process of passing through the divided chambers and the narrow passages, so that the noise and vibration of the rotary compressor can be effectively suppressed. It will be.

A rotary compressor according to a second aspect of the present invention is provided with a plurality of bolts for connecting the support member to the cylinder in the above description, the discharge silencing chamber division chambers are arranged between the respective bolts, and narrow passages are provided. It is characterized in that it is arranged on the bearing side of the bolt.

According to the invention of claim 2, in addition to the above, a plurality of bolts for connecting the support member to the cylinder are provided, the division chambers of the discharge silencing chamber are arranged between the bolts, and a narrow passage is formed. Since it is arranged on the bearing side of each bolt, it is possible to efficiently use the space other than the bolt that connects the support member and the cylinder to form a plurality of divided chambers of the discharge silencing chamber and a narrow passage. It is a thing.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows, as an embodiment of the rotary compressor of the present invention, first and second rotary compression elements 32, 3
4 is a longitudinal sectional view of an internal intermediate pressure type multi-stage (two-stage) compression type rotary compressor 10, FIG. 2 is a front view of the rotary compressor 10, FIG. 3 is a side view of the rotary compressor 10, and FIG. One longitudinal sectional view, FIG. 5 is another longitudinal sectional view of the rotary compressor 10, FIG. 6 is a plan sectional view of the electric element 14 portion of the rotary compressor 10, and FIG. 7 is a rotary compression mechanism portion 18 of the rotary compressor 10. Each of the enlarged cross-sectional views is shown.

In each figure, 10 is carbon dioxide (C
This is an internal intermediate pressure type multi-stage compression type rotary compressor using O ₂ ) as a refrigerant.
Reference numeral 0 denotes a cylindrical hermetic container 12 made of a steel plate, and an electric element 14 arranged and housed above the inner space of the hermetic container 12.
And the electric element 14 disposed below the electric element 14.
First rotary compression element 32 driven by the rotary shaft 16 of
The rotary compression mechanism portion 18 includes the (first stage) and the second rotary compression element 34 (second stage). The height dimension of the rotary compressor 10 of the embodiment is 220 mm (outer diameter 120 mm), and the height dimension of the electric element 14 is about 80 mm.
(Outer diameter 110 mm), the height dimension of the rotary compression mechanism portion 18 is about 70 mm (outer diameter 110 mm), and the distance between the electric element 14 and the rotary compression mechanism portion 18 is about 5 mm. The excluded volume of the second rotary compression element 34 is set smaller than the excluded volume of the first rotary compression element 32.

The closed container 12 has a thickness of 4.5 mm in the embodiment.
It is composed of the steel plate of
4A and the container main body 12A that houses the rotary compression mechanism portion 18,
It is composed of a substantially bowl-shaped end cap (lid) 12B that closes the upper opening of the container body 12A, and a circular mounting hole 12D is formed in the center of the upper surface of the end cap 12B.
Is formed, and the electric element 14 is provided in the mounting hole 12D.
Terminal for supplying power to the unit (wiring omitted) 20
Is attached.

In this case, the end cap 12B around the terminal 20 is formed with a step portion 12C having a predetermined curvature in an annular shape by press forming. Also, Terminal 2
Reference numeral 0 denotes a circular glass portion 20A to which the electrical terminal 139 is attached and is attached, and a metal attaching portion 20 formed around the glass portion 20A and protruding obliquely outward and downward to form a brim.
It is composed of B and. The thickness of the mounting portion 20B is 2.4 ± 0.5 mm. Then, in the terminal 20, the glass portion 20A is inserted from the lower side into the mounting hole 12D so as to face the upper side, and the mounting portion 20B is brought into contact with the peripheral edge of the mounting hole 12D, and the peripheral edge of the mounting hole 12D of the end cap 12B. It is fixed to the end cap 12B by welding the mounting portion 20B to.

The electric element 14 is a stator 22 mounted in an annular shape along the inner peripheral surface of the upper space of the closed container 12.
And a rotor 24 inserted and arranged inside the stator 22 with a slight gap. The rotor 24 is fixed to the rotating shaft 16 that extends vertically through the center.

The stator 22 includes a laminated body 26 in which donut-shaped electromagnetic steel sheets are laminated, and a stator coil 2 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method.
8 (FIG. 6). Like the stator 22, the rotor 24 is also formed of a laminated body 30 of electromagnetic steel plates, and a permanent magnet MG is inserted into the laminated body 30.

An intermediate partition plate 36 is sandwiched between the first rotary compression element 32 and the second rotary compression element 34. That is, the first rotary compression element 32 and the second rotary compression element 34 include an intermediate partition plate 36, cylinders 38 and cylinders 40 arranged above and below the intermediate partition plate 36, and inside the upper and lower cylinders 38 and 40. And the upper and lower rollers 46 and 48 which are fitted to the upper and lower eccentric portions 42 and 44 provided on the rotary shaft 16 with a phase difference of 180 degrees and rotate eccentrically.
Upper and lower vanes 5 to be described later, which abut against the upper and lower cylinders 38 and 40 to divide them into the low pressure chamber side and the high pressure chamber side, respectively.
0 (the lower vane is not shown) and an upper support member as a support member that also serves as a bearing for the rotary shaft 16 by closing the upper opening surface of the upper cylinder 38 and the lower opening surface of the lower cylinder 40. 54 and the lower support member 56.

Upper support member 54 and lower support member 56
The suction ports 161 and 162 at the upper and lower cylinders 3.
Suction passages 58, 60 communicating with the insides of 8, 40, respectively.
And the recessed discharge muffling chambers 62 and 64 are formed, and the cylinders 38 of both the discharge muffling chambers 62 and 64 are formed.
The openings on the opposite side to 40 are closed by covers. That is, the discharge muffling chamber 62 is an upper cover 66 as a cover, and the discharge muffling chamber 64 is a lower cover 6 as a cover.
It is closed at 8.

In this case, a bearing 54A is formed upright in the center of the upper support member 54, and the discharge muffling chamber 62 is formed outside the bearing 54A. A tubular bush 122 is attached to the inner surface of the bearing 54A. Further, a bearing 56A is provided at the center of the lower support member 56.
Is formed through the discharge muffling chamber 64.
It is formed outside 6A. The lower surface of the lower support member 56 (the surface opposite to the lower cylinder 40) is a flat surface, and the inner surface of the bearing 56A has a cylindrical bush 1.
23 is attached. These bushes 122, 123
Is made of a material having good slidability and wear resistance as will be described later, and the rotary shaft 16 is made of these bushes 122, 123.
Via the bearing 54A of the upper support member 54 and the bearing 56A of the lower support member 56.

In this case, the lower cover 68 is made of a donut-shaped circular steel plate, and is fixed to the lower support member 56 from the bottom at four places in the peripheral portion by the main bolts 129, and the discharge port 41 (refrigerant inflow). Part) closes the lower surface opening of the discharge muffling chamber 64 (divided chamber 62A described later) that communicates with the inside of the lower cylinder 40 of the first rotary compression element 32. The tips of the main bolts 129 ...
Screw to 4. The inner peripheral edge of the lower cover 68 projects inward from the inner surface of the bearing 56A of the lower support member 56, whereby the lower end surface of the bush 123 (the end opposite to the lower cylinder 40) is held by the lower cover 68. ,
It is prevented from falling off (Fig. 9).

As a result, the bearing 5 of the lower support member 56
It is not necessary to form the retaining shape of the bush 123 at the lower end portion of 6A, the shape of the lower support member 56 is simplified, and the production cost can be reduced. Incidentally, FIG.
Shows the lower surface of the lower support member 56, and 128 is the discharge valve of the first rotary compression element 32 that opens and closes the discharge port 41 in the discharge muffling chamber 64.

Here, the lower support member 56 is made of an iron-based sintered material (a casting is also possible), and the lower cover 6
The surface on which 8 is attached (lower surface) is processed to have a flatness of 0.1 mm or less and then subjected to steam treatment. By this steam treatment, the surface on the side to which the lower cover 68 is attached becomes iron oxide, so that the holes inside the sintered material are closed and the sealing performance is improved. This eliminates the need to provide a gasket between the lower cover 68 and the lower support member 56.

The refrigerant outflow portion of the discharge muffling chamber 64 and the electric element 14 side of the upper cover 66 in the closed container 12 are
The upper and lower cylinders 38, 40 and the intermediate partition plate 36 are communicated with each other through a communication passage 63 which is a hole (FIG. 4). In this case, an intermediate discharge pipe 121 is erected at the upper end of the communication passage 63, and the intermediate discharge pipe 121 is adjacent to the stator coil 2 wound around the stator 22 of the upper electric element 14.
It is directed to the gap between 8 and 28 (Fig. 6).

The upper cover 66 has a discharge port 39.
The (refrigerant inflow portion) closes the upper opening (the opening on the electric element 14 side) of the discharge muffling chamber 62 that communicates with the inside of the upper cylinder 38 of the second rotary compression element 34, and discharge muffles the inside of the closed container 12. The chamber 62 and the electric element 14 side are partitioned. The upper cover 66 has a thickness of 2 mm or more and 10 mm or less (most preferably 6 mm in the embodiment), and is made of a substantially donut-shaped circular steel plate having a hole through which the bearing 54A of the upper support member 54 is formed. With the gasket 124 with a bead sandwiched between the upper support member 54 and the upper support member 54, the upper support member 54 is covered from above by the four main bolts 78 ... It is fixed to. The tips of the main bolts 78 ... Are screwed into the lower support member 56, whereby the upper cover 66 and the upper support member 54 are combined and integrated with the upper cylinder 38 and the like.

Here, the thickness dimension of the upper cover 66 is set to 2 m.
When the test was performed with the thickness thinner than m, there was a risk of deformation due to the internal pressure of the discharge muffling chamber 62. On the other hand, the upper cover 6
When the thickness dimension of 6 was made thicker than 10 mm, the upper surface of this time approached the stator 22 (stator coil 28), resulting in a fear of insulation. In the present invention, the upper cover 66 has a thickness within the above range, and the rotary compressor 10 itself can be miniaturized while sufficiently withstanding the pressure of the discharge muffling chamber 62, which is higher than that in the closed container 12. However, it becomes possible to secure an insulation distance from the electric element 14. Further, an O-ring 126 is provided between the inner peripheral end surface of the upper cover 66 and the outer surface of the bearing 54A (FIG. 12). By sealing the bearing 54A side by the O-ring 126, the inner peripheral end surface of the upper cover 66 can be sufficiently sealed to prevent gas leakage, and the volume of the discharge muffling chamber 62 can be increased. It is not necessary to fix the inner edge portion of the upper cover 66 to the bearing 54A with the C ring as in the conventional case. Here, in FIG. 11, 127 is a discharge valve of the second rotary compression element 34 that opens and closes the discharge port 39 in the discharge muffling chamber 62.

Next, the shape of the discharge muffling chamber 62 in the upper support member 54 will be described with reference to FIG. Figure 1
Reference numeral 1 denotes a top view of the upper support member 54.
2 is a hole through which the main bolt 78 is inserted, and the bearing 54
It is formed on the outside of A at intervals of 90 degrees such as four places. Further, 173 are holes through which auxiliary bolts 136, which will be described later, are inserted, and two holes are formed outside the holes 172.

In the embodiment, the discharge muffling chamber 62 has four division chambers 62A, 62B, 62C and 62D and narrow passages 62E ... (3) for communicating these division chambers 62A to 62D in series with each other. Locations) and. That is, the division chambers 62A and 62B, 62B and 62C, 62C and 62D are connected by the passage 62E, respectively.
No passage exists between the division chambers 62A and 62D.

Further, each of the divided chambers 62A to 62D and the passage 62
.. are arranged outside the bearing 54A so as to surround it, and the division chambers 62A to 62D are respectively provided in the adjacent holes 1
72, 172, and the passage 62E ...
.. are arranged on the bearing 54A side. Then, the discharge port 39 opens into the division chamber 62A located at one end, and the discharge valve 127 extends from the division chamber 62B to the passage 6.
It is stored in the form of 2A through 62A. Further, the upper support member 5 is provided in the division chamber 62D located at the other end.
The discharge passage 172 (refrigerant outflow portion) formed in the opening 4 is open.

In this way, each of the divided chambers 62 of the discharge muffling chamber 62 is
By arranging A to 62D and the passage 62E ..., each of the division chambers 62A to 62D is located between the main bolts 78, 78,
The passage 62E is located on the bearing 54A side of the main bolt 78. As a result, the space other than the main bolt 78 ...
2D and narrow passages 62E ... Can be formed.

Next, the intermediate partition plate 3 for closing the lower opening surface of the upper cylinder 38 and the upper opening surface of the lower cylinder 40.
In FIG. 6, a position corresponding to the suction side in the upper cylinder 38 extends from the outer peripheral surface to the inner peripheral surface as shown in FIGS. 13 and 14, and the outer peripheral surface and the inner peripheral surface communicate with each other to form an oil supply passage. The through hole 131 is formed by fine hole processing, and the sealing material (blanket pin) 132 on the outer peripheral surface side of the through passage 131 is press-fitted to seal the outer peripheral surface side opening. In addition, a communication hole (vertical hole) 13 extending upward is formed in the middle of the through hole 131.
3 is drilled.

On the other hand, the suction port 161 of the upper cylinder 38
A communication hole 134 for injection, which communicates with the communication hole 133 of the intermediate partition plate 36, is formed on the (suction side). Further, as shown in FIG. 7, an oil hole 80 extending in the vertical direction with respect to the shaft center and horizontal oil supply holes 82, 84 communicating with the oil hole 80 (upper and lower eccentric portions 42, 44) are also formed in the rotary shaft 16. Is formed, and the opening on the inner peripheral surface side of the through hole 131 of the intermediate partition plate 36 is provided with these oil supply holes 8
It communicates with the oil hole 80 via 2, 84.

As will be described later, it is difficult to supply oil into the upper cylinder 38, which has a high pressure in the second stage, because of the intermediate pressure in the closed container 12. However, the intermediate partition plate 36 is provided. , Pumped up from the oil sump at the bottom of the closed container 12 to raise the oil hole 80,
The oil discharged from No. 4 enters the through hole 131 of the intermediate partition plate 36 and is supplied to the suction side (suction port 161) of the upper cylinder 38 from the communication holes 133 and 134.

In FIG. 16, L indicates the pressure fluctuation in the upper cylinder 38, and P1 in the figure indicates the pressure on the inner peripheral surface of the intermediate partition plate 36. As indicated by L1 in this figure, the pressure on the suction side of the upper cylinder 38 (suction pressure) becomes lower than the pressure on the inner peripheral surface side of the intermediate partition plate 36 due to suction pressure loss during the suction process. During this period, from the oil hole 80 of the rotary shaft 16 to the intermediate partition plate 36.
Oil is injected into the upper cylinder 38 from the communication hole 134 of the upper cylinder 38 via the through hole 131 and the communication hole 133 of FIG.

As described above, the upper and lower cylinders 38 and 40, the intermediate partition plate 36, the upper and lower support members 54 and 56, and the upper and lower covers 6
6 and 68 are respectively fastened from above and below by four main bolts 78 ... And main bolts 129 ..., but further, upper and lower cylinders 38, 40, intermediate partition plate 36, and upper and lower support members 5
4, 56 are fastened by auxiliary bolts 136, 136 located outside these main bolts 78, 129 (FIG. 4). The auxiliary bolt 136 is inserted from the upper support member 54 side, and the tip end is screwed into the lower support member 56.

The auxiliary bolt 136 is located near a guide groove 70, which will be described later, of the vane 50 described above.
By thus adding the auxiliary bolts 136 and 136 to integrate the rotary compression mechanism portion 18, the sealing performance against the extremely high pressure inside is ensured and the vicinity of the guide groove 70 of the vane 50 is ensured. Since it is tightened, the back pressure gas leak from the guide groove 70 can be prevented.

On the other hand, inside the upper cylinder 38, a guide groove 70 for accommodating the vane 50 and an accommodating portion 70A located outside the guide groove 70 for accommodating a spring 76 as a spring member are formed. The storage section 70A is open to the guide groove 70 side and the closed container 12 (container body 12A) side (FIG. 8). The spring 76 contacts the outer end of the vane 50 and constantly urges the vane 50 toward the roller 46. Further, a metal plug 137 is provided in the housing portion 70A of the spring 76 on the side of the closed container 12 and serves to prevent the spring 76 from coming off. Since the discharge pressure of the second rotary compression element 34 is applied as a back pressure to a back pressure chamber (not shown) that communicates with the guide groove 70, the spring 76 side of the plug 137 has a high pressure and the closed container 12 side has an intermediate pressure.

In this case, the outer size of the plug 137 is the storage portion 7.
The plug 137 is set to be smaller than the inner dimension of 0A, and is inserted into the accommodating portion 70A by a clearance fit. Further, an O-ring 138 for sealing between the plug 137 and the inner surface of the housing portion 70A is attached to the peripheral surface of the plug 137. The outer end of the upper cylinder 38, that is, the distance between the outer end of the storage portion 70A and the container body 12A of the closed container 12 is smaller than the distance from the O-ring 138 to the end of the plug 137 on the closed container 12 side. It is set.

Due to the above dimensional relationship, the plug 1
As in the case where 37 is press-fitted and fixed in the accommodating portion 70A, it is possible to avoid the inconvenience that the upper cylinder 38 is deformed and the sealing performance between the upper cylinder 38 and the upper support member 54 is deteriorated, resulting in deterioration of performance. become. Even with such a clearance fit, the distance between the upper cylinder 38 and the closed container 12 is set smaller than the distance from the O-ring 138 to the end of the plug 137 on the closed container 12 side. Even if the plug 138 is moved in the direction of being pushed out from the storage portion 70A, the O-ring 138 is still positioned and sealed inside the storage portion 70A at the time when the movement is blocked by coming into contact with the closed container 12, so that the function of the plug 138 is No problems arise.

By the way, the connecting portion 90 which connects the upper and lower eccentric portions 42 and 44 integrally formed with the rotating shaft 16 with a phase difference of 180 degrees has a sectional shape of the rotating shaft 16.
The non-circular shape, for example, a rugby ball shape, has a larger cross-sectional area than the circular cross-section and has rigidity (FIG. 17). That is, the vertical eccentric parts 42, 4 provided on the rotary shaft 16
The cross-sectional shape of the connecting portion 90 connecting the four is the vertical eccentric portion 42
The wall thickness is increased in the direction orthogonal to the eccentric direction of 44 (hatched portion in the figure).

As a result, the cross-sectional area of the connecting portion 90 that connects the vertical eccentric portions 42 and 44 integrally provided on the rotary shaft 16 is increased, and the second moment of area is increased to increase the strength (rigidity) and durability. It improves the reliability and reliability. Especially when two-stage compression of a refrigerant having a high working pressure is performed, the load applied to the rotating shaft 16 increases due to a large pressure difference between high pressure and low pressure, but the cross-sectional area of the connecting portion 90 is increased to increase its strength (rigidity).
Therefore, the rotation shaft 16 is prevented from being elastically deformed.

In this case, the center of the upper eccentric portion 42 is O1.
And the center of the lower eccentric portion 44 is O2, the center of the arc of the surface of the coupling portion 90 on the eccentric direction side of the eccentric portion 42 is O.
1, the center of the arc of the surface of the connecting portion 90 on the eccentric direction side of the eccentric portion 44 is O2. As a result, the rotary shaft 16 is chucked by the cutting machine and the vertical eccentric parts 42 and 44 and the connecting part 9 are attached.
When cutting 0, after processing the eccentric portion 42, only the radius is changed to process one surface of the connecting portion 90, the chuck position is changed to process the other surface of the connecting portion 90, and only the radius is changed. Then, the work of machining the eccentric portion 44 becomes possible. As a result, the number of times of re-chucking the rotary shaft 16 is reduced, and the productivity is remarkably improved.

In this case, as the refrigerant, carbon dioxide (CO ₂ ) as an example of carbon dioxide which is a natural refrigerant is used in consideration of flammability, toxicity, etc. As the oil, existing oils such as mineral oil, alkylbenzene oil, ether oil and ester oil are used.

The suction passage 5 of the upper support member 54 and the lower support member 56 is provided on the side surface of the container body 12A of the closed container 12.
8, 60, the discharge passage 171 continuing to the discharge muffling chamber 62, and the sleeves 141, 142, 1 at positions corresponding to the upper side of the upper cover 66 (the position substantially corresponding to the lower end of the electric element 14).
43 and 144 are fixed by welding. The sleeves 141 and 142 are vertically adjacent to each other, and
44 is at a position shifted from the sleeve 141 by approximately 90 degrees.

Then, one end of a refrigerant introducing pipe 92 for introducing a refrigerant gas into the upper cylinder 38 is inserted and connected in the sleeve 141, and one end of the refrigerant introducing pipe 92 is communicated with the suction passage 58 of the upper cylinder 38. It This refrigerant introduction pipe 9
2 passes through the upper side of the closed container 12 to reach the sleeve 144, and the other end is inserted and connected in the sleeve 144 to communicate with the closed container 12.

In the sleeve 142, the lower cylinder 4
One end of a refrigerant introduction pipe 94 for introducing the refrigerant gas to 0 is inserted and connected, and one end of this refrigerant introduction pipe 94 is communicated with the suction passage 60 of the lower cylinder 40. This refrigerant introducing pipe 94
The other end of is connected to the lower end of the accumulator 146. A refrigerant discharge pipe 96 is inserted and connected in the sleeve 143, and one end of the refrigerant discharge pipe 96 is connected to the upper support member 5.
4 is communicated with the division chamber 62D of the discharge muffling chamber 62 via the discharge passage 171.

The accumulator 146 is a tank for separating the suction refrigerant into gas and liquid, and is the container body 1 of the closed container 12.
It is attached via a bracket 148 on the accumulator side to a bracket 147 on the closed container side welded and fixed to the upper side surface of 2A. The bracket 148 extends upward from the bracket 147 and holds the substantially central portion of the accumulator 146 in the vertical direction. In this state, the accumulator 146 is arranged along the side of the closed container 12. The refrigerant introduction pipe 92, after coming out of the sleeve 141, bends to the right in the embodiment and then rises, and the lower end of the accumulator 146 is in the form of being close to the refrigerant introduction pipe 92. Therefore, the refrigerant introduction pipe 94 that descends from the lower end of the accumulator 146 is routed so as to bypass the left side of the sleeve 141 opposite to the bending direction of the refrigerant introduction pipe 92 and reach the sleeve 142 (FIG. 3). ).

That is, the upper support member 38 and the lower support member 4
Refrigerant introduction pipes 92 and 94 communicating with the suction passages 58 and 60 of 0 are bent in the opposite directions in the horizontal direction when viewed from the closed container 12, whereby the vertical dimension of the accumulator 146 is enlarged. Therefore, even if the volume is increased, consideration is given so that the refrigerant introduction pipes 92 and 94 do not interfere with each other.

Further, a flange portion 15 is formed around the outer surfaces of the sleeves 141, 143, 144 so that a coupler for pipe connection can be engaged.
1 is formed, and a thread groove 152 for pipe connection is formed on the inner surface of the sleeve 142. As a result, the sleeves 141, 143, 144 can be easily connected to the flange 151 while the coupler of the test pipe is easily connected to the sleeve 142 when the air tightness test is performed in the completion inspection in the manufacturing process of the rotary compressor 10. Screw groove 152
You can easily screw the test pipe with. In particular, the upper and lower sleeves 141 and 142 are
Since the flange 151 is formed on one sleeve 141 and the thread groove 152 is formed on the other sleeve 142, the test pipe can be connected to each sleeve 141, 142 in a narrow space.

The rotary compressor 1 of the embodiment
0 is used in the refrigerant circuit of the water heater 153 as shown in FIG. That is, the refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the gas cooler 154 for heating water. The gas cooler 154 is provided in a hot water storage tank (not shown) of the hot water supply device 153. The pipe exiting the gas cooler 154 is passed through an expansion valve 156 as a pressure reducing device and then an evaporator 157.
And the outlet of the evaporator 157 is connected to the refrigerant introduction pipe 94. Further, although not shown in FIGS. 2 and 3, a defrost pipe 158 constituting a defrosting circuit branches from the middle portion of the refrigerant introduction pipe 92, and the defrost pipe 158 of the gas cooler 154 is connected via an electromagnetic valve 159 as a flow path control device. It is connected to the refrigerant discharge pipe 96 leading to the inlet. The accumulator 146 is omitted in FIG.

The operation of the above configuration will be described below. In the heating operation, the solenoid valve 159 is closed. Electric element 1 via terminal 20 and wiring not shown
When the stator coil 28 of No. 4 is energized, the electric element 14
Starts and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted in the upper and lower eccentric portions 42 and 44 integrally provided with the rotating shaft 16 eccentrically rotate in the upper and lower cylinders 38 and 40.

As a result, the low pressure (first stage suction pressure LP: 4 MPaG) sucked from the suction port 162 to the low pressure chamber side of the lower cylinder 40 via the suction passage 60 formed in the refrigerant introduction pipe 94 and the lower support member 56. ) The refrigerant gas is
The intermediate pressure (M
P1: 8 MPaG), and is discharged from the high pressure chamber side of the lower cylinder 40 into the closed container 12 from the discharge port 41, the discharge muffling chamber 64 formed in the lower support member 56, the communication passage 63, and the intermediate discharge pipe 121.

At this time, since the intermediate discharge pipe 121 is directed toward the gap between the adjacent stator coils 28, 28 wound around the stator 22 of the upper electric element 14, the refrigerant gas having a relatively low temperature is still present. Can be positively supplied in the direction of the electric element 14, and the temperature rise of the electric element 14 can be suppressed. Moreover, by this, the closed container 1
The inside of 2 becomes an intermediate pressure (MP1).

The intermediate pressure refrigerant gas in the closed container 12 is discharged from the sleeve 144 (the intermediate discharge pressure is equal to the above-mentioned MP value).
1) The refrigerant is introduced into the low pressure chamber side of the upper cylinder 38 from the suction port 161 through the refrigerant introduction pipe 92 and the suction passage 58 formed in the upper support member 54 (second-stage suction pressure MP
2). The sucked intermediate-pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the vane 50 to become high-temperature high-pressure refrigerant gas (second-stage discharge pressure HP: 12 MPa.
G), the liquid is discharged from the high-pressure chamber side into the divided chamber 62A of the discharge muffling chamber 62 formed in the upper support member 54 through the discharge port 39.

The high-pressure refrigerant gas flowing into the divided chamber 62A exits the divided chamber 62A and passes through the narrow passage 62E,
Next, the division chamber 62B is entered. Then, next, this division chamber 62
Exit B and pass through passage 62E and then into split chamber 62C. Furthermore, next, the divided chamber 62C exits, passes through the passage 62E, and finally enters the divided chamber 62D. And the division chamber 62
The gas exits from D, enters the discharge passage 171, passes through the discharge passage 171, passes through the refrigerant discharge pipe 96, and flows into the gas cooler 154.

Thus, the high-pressure refrigerant gas compressed in the upper cylinder 38 and flowing into the discharge muffling chamber 62 from the discharge port 39 is connected to the plurality of divided chambers 62A to 62D and the narrow passage 62E. .. sequentially pass through the discharge passage 171, so that the pulsation of the refrigerant gas is effectively absorbed in the process of passing through the divided chambers 62A to 62D and the narrow passage 62E. The noise and vibration of the rotary compressor 10 can be effectively suppressed.

The temperature of the refrigerant when flowing into the gas cooler 154 has risen to approximately + 100 ° C., and the high-temperature and high-pressure refrigerant gas radiates heat to heat the water in the hot water storage tank to generate hot water of approximately + 90 ° C. To generate.

On the other hand, the refrigerant itself is cooled in the gas cooler 154 and exits the gas cooler 154. Then, after being decompressed by the expansion valve 156, it flows into the evaporator 157 and evaporates, and the accumulator 146 (not shown in FIG. 18).
After that, the cycle of being sucked into the first rotary compression element 32 from the refrigerant introduction pipe 94 is repeated.

In particular, in an environment of low outside temperature, such heating operation causes frost to grow on the evaporator 157. In that case, the solenoid valve 159 is opened, the expansion valve 156 is fully opened, and the evaporator 157 is defrosted. As a result, the medium-pressure refrigerant (including a small amount of high-pressure refrigerant discharged from the second rotary compression element 34) in the closed container 12 reaches the gas cooler 154 through the defrost pipe 158. The temperature of this refrigerant is about +50 to + 60 ° C., and the gas cooler 154 does not dissipate heat, but the refrigerant initially absorbs heat. The refrigerant discharged from the gas cooler 154 is the expansion valve 1
It passes through 56 and reaches the evaporator 157. That is,
The evaporator 157 is substantially directly supplied with the refrigerant having a substantially intermediate pressure and having a relatively high temperature without being decompressed, whereby the evaporator 157 is heated and defrosted.

As described above, since the intermediate pressure refrigerant gas discharged from the first rotary compression element 32 is taken out from the closed container 12 to defrost the evaporator 157, the second rotary compression element is used. It is possible to prevent the pressure reversal phenomenon between the discharge (high pressure) and the suction (intermediate pressure) of the second rotary compression element 34 which occurs when the high pressure refrigerant discharged from the compressor 34 is supplied to the evaporator 157 without being decompressed. become able to.

Although the internal intermediate pressure type multi-stage compression type rotary compressor has been described in the above embodiment, the present invention is not limited to this and is also effective for a rotary compressor having a single rotary compression element. Further, although the rotary compressor 10 is used in the refrigerant circuit of the hot water supply device 153 in the embodiment, the present invention is not limited to this and is also effective when used for heating the room.

[0062]

As described in detail above, according to the present invention, a rotary compression element is configured in a rotary compressor including an electric element in a closed container and a rotary compression element driven by a rotating shaft of the electric element. And a support member having a bearing for the rotary shaft in the center and a support member outside the bearing, which communicates with the inside of the cylinder at the coolant inlet, and A discharge muffling chamber having an outflow portion is provided, and the discharge muffling chamber is composed of a plurality of divided chambers and a narrow passage that communicates the plurality of divided chambers with each other. , Because it was provided in each of the divided chambers on both ends of the communication,
The refrigerant gas compressed in the cylinder and flowing into the discharge muffling chamber from the refrigerant inflow portion sequentially passes through the plurality of division chambers and the narrow passages communicating with each other, and then exits from the refrigerant outflow portion.

As a result, the pulsation of the refrigerant gas is effectively absorbed in the process of passing through the divided chambers and the narrow passages, and the noise and vibration of the rotary compressor can be effectively suppressed. It will be.

According to the invention of claim 2, in addition to the above, a plurality of bolts for connecting the support member to the cylinder are provided, the division chambers of the discharge muffling chamber are arranged between the bolts, and a narrow passage is formed. Since it is arranged on the bearing side of each bolt, it is possible to efficiently use the space other than the bolt that connects the support member and the cylinder to form a plurality of divided chambers of the discharge silencing chamber and a narrow passage. It is a thing.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a rotary compressor according to an embodiment of the present invention.

FIG. 2 is a front view of the rotary compressor of FIG.

3 is a side view of the rotary compressor of FIG. 1. FIG.

FIG. 4 is another vertical cross-sectional view of the rotary compressor of FIG.

FIG. 5 is another vertical cross-sectional view of the rotary compressor of FIG.

6 is a plan sectional view of an electric element portion of the rotary compressor of FIG. 1. FIG.

7 is an enlarged sectional view of a rotary compression mechanism portion of the rotary compressor of FIG.

8 is an enlarged sectional view of a vane portion of a second rotary compression element of the rotary compressor of FIG.

9 is a cross-sectional view of a lower support member and a lower cover of the rotary compressor of FIG.

10 is a bottom view of a lower support member of the rotary compressor of FIG. 1. FIG.

11 is a top view of an upper support member of the rotary compressor of FIG. 1. FIG.

12 is a sectional view of an upper support member and an upper cover of the rotary compressor of FIG.

FIG. 13 is a top view of an intermediate partition plate of the rotary compressor of FIG.

FIG. 14 is a sectional view taken along the line AA of FIG.

15 is a top view of the upper cylinder of the rotary compressor of FIG. 1. FIG.

16 is a diagram showing pressure fluctuations on the suction side of the upper cylinder of the rotary compressor of FIG.

FIG. 17 is a cross-sectional view for explaining the shape of the connecting portion of the rotary shaft of the rotary compressor of FIG.

18 is a refrigerant circuit diagram of a hot water supply device to which the rotary compressor of FIG. 1 is applied.

[Explanation of symbols]

10 Rotary compressor 12 airtight container 14 Electric elements 16 rotation axes 18 Rotary compression mechanism 20 terminals 32 First rotary compression element 34 Second rotary compression element 36 Intermediate partition plate 38, 40 cylinders 39, 41 Discharge port 42 Eccentric part 44 Eccentric part 46 Laura 48 Roller 50 vanes 54 Upper support member 56 Lower support member 62 Discharge silencer 62A-62D division room 62E passage 64 discharge silencer 66 Top cover 68 Lower cover 70 Guide groove 70A storage 76 Spring (Spring member) 78,129 Main bolt 90 Connection 92,94 Refrigerant introduction pipe 96 Refrigerant discharge pipe 124 gasket 126 O-ring 153 water heater 154 gas cooler 156 expansion valve 157 evaporator 158 Defrost Tube 159 Solenoid valve 171 Discharge passage

Continued front page    (72) Inventor Kenzo Matsumoto             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Dai Matsuura             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Kazuya Sato             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Takayasu Saito             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Toshiyuki Ehara             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Satoru Imai             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Atsushi Oda             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Takashi Sato             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Hiroyuki Matsumori             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. F-term (reference) 3H003 AA05 AB04 AC03 BA03 CD00                       CD03 CE02 CE05                 3H029 AA04 AA09 AA13 AB03 BB22                       BB32 CC03 CC04 CC05 CC06                       CC15 CC25 CC26 CC28

Claims (2)

[Claims] 1. A rotary compressor comprising an electric element in a closed container and a rotary compression element driven by a rotary shaft of the electric element, wherein a cylinder for constituting the rotary compression element and an opening of the cylinder. A support member that closes the surface and that has a bearing for the rotating shaft in the center and the support member outside the bearing, communicates with the inside of the cylinder at the refrigerant inflow portion, and has a refrigerant outflow portion A discharge muffling chamber, wherein the discharge muffling chamber is composed of a plurality of divided chambers and a narrow passage communicating with the plurality of divided chambers, and the refrigerant inflow portion and the refrigerant outflow portion are connected to each other. A rotary compressor provided in each of the divided chambers at both ends. 2. A plurality of bolts for connecting the support member to the cylinder are provided, a division chamber of the discharge muffling chamber is arranged between the bolts, and the narrow passage is provided on the bearing side of each bolt. The rotary compressor according to claim 1, characterized in that