JP2003097468A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of preventing the deterioration of performance caused by a fixation of a plug for preventing falling-off of a spring member. SOLUTION: This rotary compressor is provided with an upper cylinder 38 for constituting a rotary compression element 34 of the rotary compressor, a roller 46 fitted to an eccentric part formed on a rotary shaft of a motor-driven element, and eccentrically rotating in the upper cylinder, a vane 50 for partitioning the inside of the upper cylinder into the low pressure chamber side and the high pressure chamber side by abutting to the roller, a spring 76 for always energizing the vane to the roller side, a spring housing part 70A formed in the upper cylinder and opening to the vane side and the sealed vessel 12 side, the plug 137 positioned on the sealed vessel side of the spring and inserted into the housing part by clearance-fitting, and an O ring 138 installed on the peripheral surface of the plug and sealing the plug and the housing part. An interval between the upper cylinder and the sealed vessel is set smaller than a distance between a sealed vessel side end part of the plug from the O ring.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor including 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 gas is used as a refrigerant in the rotary compressor, the pressure of the discharged refrigerant becomes 12 MPaG in the second rotary compression element which becomes high pressure. On the other hand, the pressure becomes 8 MPaG (intermediate pressure) in the first rotary compression element on the low stage side (the suction pressure of the first rotary compression element is 4 MP).
a).

[0004]

The vane attached to such a rotary compressor is inserted in a groove provided in the radial direction of the cylinder so as to be movable in the radial direction of the cylinder. And behind the vane (closed container side)
A spring hole (storage part) that opens to the outside of the cylinder is provided in this cylinder, and a coil spring (spring member) that constantly biases the vane toward the roller is inserted into this spring hole. After inserting
It was blocked by a plug (retainer) to prevent the spring from jumping out.

In this case, the eccentric rotation of the roller causes the plug to receive a force in the direction of being pushed outward from the spring hole. Particularly, in the internal intermediate pressure type rotary compressor, the pressure inside the closed container is lower than that inside the cylinder of the second rotary compression element, so that the plug is pushed out due to the pressure difference between the inside and the outside of the cylinder. for that reason,
In the past, the plug was fixed to the cylinder by pressing it into the spring hole, but this pressing deforms the cylinder so that it expands, creating a gap between it and the support member (bearing) that closes the opening surface of the cylinder. As a result, there is a problem in that the sealability inside the cylinder cannot be ensured and the performance deteriorates.

The present invention has been made in order to solve the problems of the prior art, and provides a rotary compressor capable of preventing the deterioration of the performance due to the fixing of the plug for preventing the spring member from coming off. The purpose is to provide.

[0007]

That is, a rotary compressor according to the invention of claim 1 comprises an electric element and a rotary compression element driven by the electric element in a hermetically sealed container. A roller that is fitted to an eccentric portion formed on a rotating shaft of a cylinder and an electric element that configures a compression element and that rotates eccentrically in the cylinder, and a low pressure chamber side and a high pressure chamber side inside the cylinder that abut on the roller. And a spring member for constantly biasing the vane to the roller side, a storage portion of the spring member formed in the cylinder and opened to the vane side and the closed container side, and a closed container side of the spring member. It is equipped with a plug that is positioned and is inserted into the storage part by a clearance fit, and an O-ring that is attached to the peripheral surface of the plug and seals between the plug and the storage part. , O Characterized by being smaller than the distance from ring to the end of the sealed container side of the plug.

A rotary compressor according to a second aspect of the present invention includes an electric element in a closed container and first and second rotary compression elements driven by the electric element, and is compressed by the first rotary compression element. The compressed gas is discharged into the closed container, and the discharged intermediate-pressure gas is compressed by the second rotary compression element. The cylinder and the electric element for constituting the second rotary compression element are A roller that is fitted to an eccentric portion formed on the rotary shaft and rotates eccentrically in the cylinder, a vane that abuts this roller and divides the cylinder into a low pressure chamber side and a high pressure chamber side, and this vane is always on the roller side. A spring member for urging the spring member, a housing portion of the spring member formed in the cylinder and opened to the vane side and the closed container side, and a spring member positioned on the closed container side and inserted into the housing portion with a clearance fit. And this plug It is equipped with an O-ring that is attached to the peripheral surface and seals between the plug and the housing, and the distance between the cylinder and the closed container is set smaller than the distance from the O-ring to the end of the plug on the closed container side. It is characterized by having done.

According to the first aspect of the present invention, in a rotary compressor including an electric element and a rotary compression element driven by the electric element in a closed container, a cylinder for forming the rotary compression element and an electric motor are provided. A roller that is fitted to an eccentric portion formed on the rotary shaft of the element and rotates eccentrically in the cylinder, a vane that abuts this roller and divides the cylinder into a low pressure chamber side and a high pressure chamber side, and this vane is always A spring member for urging to the roller side, a storage portion of the spring member formed in the cylinder and opened to the vane side and the closed container side, and a spring member positioned on the closed container side of the spring member with a gap fit in the storage portion. Since the inserted plug and the O-ring that is attached to the peripheral surface of the plug and seals between the plug and the accommodating portion are provided, the cylinder is used as in the case of press-fitting and fixing the plug in the accommodating portion. Deformed by the sealing property decreases, it is possible to avoid in advance a disadvantage that lead to performance deterioration.

Even with such clearance fitting, since the distance between the cylinder and the closed container is set smaller than the distance from the O-ring to the end of the plug on the closed container side, the plug is pushed out from the storage part. There is no problem in the function of the plug, because the O-ring is still located in the storage portion and seals when it moves in the closed direction and comes into contact with the closed container to prevent the movement.

Particularly, in the rotary compressor of the multi-stage compression type in which the inside of the hermetically sealed container has an intermediate pressure,
When CO ₂ gas as described in claim 5 is used as a refrigerant and the inside of the closed container has an intermediate pressure and the inside of the second rotary compression element has an extremely high pressure, a remarkable effect is obtained in maintaining the performance of the compressor and preventing the spring member from coming off. It plays.

A rotary compressor according to a third aspect of the present invention comprises an electric element and a rotary compression element driven by the electric element in a hermetic container, and a cylinder for constituting the rotary compression element. And a roller that is fitted to an eccentric portion formed on the rotary shaft of the electric element and rotates eccentrically in the cylinder, and a support member that closes the opening surface of the cylinder and that has a bearing for the rotary shaft, and contacts the roller. A vane that divides the inside of the cylinder into a low-pressure chamber side and a high-pressure chamber side, a spring member that constantly urges the vane toward the roller side, and a spring member that is formed in the cylinder and that opens to the vane side and the closed container side. And a plug which is located on the closed container side of the spring member and is press-fitted and fixed in the accommodating portion.The support member at the portion corresponding to this plug has a recess recessed in the direction away from the cylinder. Parts characterized by being formed.

A rotary compressor according to a fourth aspect of the present invention is provided with an electric element and first and second rotary compression elements driven by the electric element in a hermetic container, and is compressed by the first rotary compression element. The compressed gas is discharged into the closed container, and the discharged intermediate-pressure gas is compressed by the second rotary compression element. The cylinder and the electric element for constituting the second rotary compression element are A roller fitted into an eccentric portion formed on the rotary shaft to rotate eccentrically in the cylinder, a vane that abuts on the roller to divide the cylinder into a low pressure chamber side and a high pressure chamber side, and an opening surface of the cylinder is closed. At the same time, a support member having a bearing for the rotating shaft, a spring member for constantly urging the vane toward the roller, and a cylinder are formed.
A storage portion of the spring member opened to the vane side and the closed container side,
The spring member is provided on the side of the closed container and is press-fitted and fixed in the accommodating portion.The support member at a portion corresponding to the plug has a relief portion recessed in a direction away from the cylinder. Characterize.

According to the third aspect of the present invention, in a rotary compressor having an electric element and a rotary compression element driven by the electric element in a closed container, a cylinder for forming the rotary compression element and an electric motor. A roller fitted in an eccentric part formed on the rotary shaft of the element to rotate eccentrically in the cylinder, a support member that closes the opening surface of the cylinder and has a bearing of the rotary shaft, and a roller that contacts the roller A vane that divides the vane into a low-pressure chamber side and a high-pressure chamber side, a spring member for constantly biasing the vane to the roller side, and a storage portion of a spring member formed in the cylinder and opened to the vane side and the closed container side. A plug that is located on the closed container side of the spring member and is press-fitted and fixed in the housing, and a relief portion that is recessed in the direction away from the cylinder is provided in the support member of the portion corresponding to this plug. Since form was, even if the cylinder by a press-fitting the plug in the housing portion is deformed so as to expand the support member side, to absorb the deformation of the cylinder by the relief portion,
It is possible to avoid the inconvenience that a gap is generated between the cylinder and the support member. As a result, it is possible to avoid the inconvenience that the performance is deteriorated due to the deterioration of the sealing property due to the deformation of the cylinder.

Particularly, in the multistage compression type rotary compressor in which the inside of the hermetically sealed container has an intermediate pressure,
When CO ₂ gas as described in claim 5 is used as a refrigerant and the inside of the closed container has an intermediate pressure and the inside of the second rotary compression element has an extremely high pressure, a remarkable effect is obtained in maintaining the performance of the compressor and preventing the spring member from coming off. It plays.

[0016]

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 stepped 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.
Then, the recessed discharge silencing chambers 62 and 64 are formed, and the openings of the discharge silencing chambers 62 and 64 are closed by covers. That is, the discharge muffling chamber 62 is closed by the upper cover 66 as a cover, and the discharge muffling chamber 64 is closed by the lower cover 68 as a cover.

In this case, a bearing 54A is formed upright in the center of the upper support member 54, and a cylindrical bush 122 is attached to the inner surface of the bearing 54A. Also,
A bearing 56A is formed through the center of the lower support member 56, and the cylindrical bush 1 is also formed on the inner surface of the bearing 56A.
23 is attached. These bushes 122, 123
Is made of a material with good slidability as described below,
The rotary shaft 16 is held by the bearing 54A of the upper support member 54 and the bearing 56A of the lower support member 56 via the bushes 122 and 123.

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 below by four main bolts 129 ... The lower surface opening of the discharge muffling chamber 64 that communicates with the inside of the lower cylinder 40 of the first rotary compression element 32 is closed. The tips of the main bolts 129 ... Are screwed into the upper support member 54. 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 is held by the lower cover 68 and prevented from falling off (FIG. 9). FIG. 10 shows the lower surface of the lower support member 56, and 128 is the discharge port 41 in the discharge muffling chamber 64.
Is a discharge valve of the first rotary compression element 32 that opens and closes.

Here, the lower support member 56 is made of an iron-based sintered material (or a casting may be used), and the surface (lower surface) on which the lower cover 68 is mounted has a flatness of 0.
After being processed to 1 mm or less, steam treatment is added. 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 discharge muffler chamber 64 and the electric element 14 side of the upper cover 66 in the closed container 12 are communicated with each other by a communication passage 63 which is a hole penetrating the upper and lower cylinders 38, 40 and the intermediate partition plate 36. (Fig. 4). In this case, the communication passage 6
An intermediate discharge pipe 121 is erected at the upper end of the stator 3. The intermediate discharge pipe 121 is a stator 22 of the upper electric element 14.
It is directed to the gap between the adjacent stator coils 28, which are wound on each other (FIG. 6).

Further, the upper cover 66 closes the upper opening of the discharge muffling chamber 62 which communicates with the inside of the upper cylinder 38 of the second rotary compression element 34 at the discharge port 39, and the closed container 1
The inside of 2 is partitioned into the discharge silencing chamber 62 and the electric element 14 side. This upper cover 66 has a thickness of 2 mm or more 1 as shown in FIG.
The upper support member 54 has a diameter of 0 mm or less (most preferably 6 mm in the embodiment) and is formed of a substantially donut-shaped circular steel plate having a hole through which the bearing 54A of the upper support member 54 passes. With the beaded gasket 124 sandwiched between and, the peripheral portion is fixed to the upper support member 54 from above by four main bolts 78 ... Through the gasket 124. The tips of the main bolts 78 ... Are screwed into the lower support member 56.

By making the thickness of the upper cover 66 to be such a size, it is possible to withstand the pressure of the discharge muffling chamber 62, which is higher than the pressure inside the closed container 12, and to achieve the downsizing, and the electric element 1
It is also possible to secure an insulation distance from 4. Further, an O-ring 126 is provided between the inner peripheral edge 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, it is possible to sufficiently seal the inner peripheral edge of the upper cover 66 and prevent the gas leak, and it is possible to increase the volume of the discharge muffling chamber 62 and It is not necessary to fix the inner peripheral edge side of the upper cover 66 to the bearing 54A by the ring. 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 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, and the sealing material 132 on the outer peripheral surface side of the through passage 131 is press-fitted to seal the outer peripheral surface side opening. A communication hole 133 extending upward is formed in the middle of the through hole 131.

On the other hand, the suction port 161 of the upper cylinder 38
A communication hole 134 that 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 is formed in the rotary shaft 16 in the vertical direction about the shaft center.
And a lateral oil supply hole 82 communicating with the oil hole 80,
84 (also formed on the vertical eccentric portions 42 and 44 of the rotary shaft 16) is formed, and the through hole 1 of the intermediate partition plate 36 is formed.
The opening on the inner peripheral surface side of 31 communicates with the oil hole 80 via these oil supply holes 82, 84.

As will be described later, since the inside pressure of the closed container 12 becomes an intermediate pressure, it becomes difficult to supply the oil into the upper cylinder 38 which becomes a high pressure in the second stage. 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 shows the pressure fluctuation on the suction side of the upper cylinder 38, and P1 shows 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, oil is supplied from the through hole 131 and the communication hole 133 of the intermediate partition plate 36 into the upper cylinder 38 through the communication hole 134 of the upper cylinder 38.

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, it is possible to prevent leakage of the high pressure back pressure applied to the vane 50.

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.

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. Then, a high pressure, which is the discharge pressure of the second rotary compression element 34, is applied as a back pressure to a back pressure chamber (not shown) communicating with the guide groove 70 of the vane 50. Therefore, the spring 76 side of the plug 137 has a high pressure, and the closed container 12 side has an intermediate pressure.

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 clearance fitting, the gap 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, so that the spring 76 side. Even if the plug 137 moves in the direction in which it is pushed out of the storage portion 70A due to the high pressure (back pressure of the vane 50), the O-ring 138 is still inside the storage portion 70A when it abuts against the closed container 12 and is prevented from moving. Since it is in position and sealed, there is no problem with the function of the plug 138.

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 which connects the vertical eccentric portions 42 and 44 integrally provided on the rotary shaft 16 is increased, the second moment of area is increased, and the strength (rigidity) is increased, resulting in 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 and toxicity, and it is an oil as a lubricating oil. 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.
The sleeves 141, 142, 143, and 144 are welded and fixed to the positions corresponding to the upper side of the discharge silencer chamber 62 and the upper cover 66 (the position substantially corresponding to the lower end of the electric element 14). The sleeves 141 and 142 are vertically adjacent to each other, and the sleeve 143 is
1 is on a substantially diagonal line. Further, the sleeve 144 is located at a position displaced 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. Further, a refrigerant discharge pipe 96 is inserted and connected in the sleeve 143, and one end of the refrigerant discharge pipe 96 has a discharge muffling chamber 62.
Be communicated to.

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 refrigerant introduction pipe 94 and the suction passage 60 formed in 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) From the high pressure chamber side, the gas flows into the gas cooler 154 through the discharge port 39, the discharge muffling chamber 62 formed in the upper support member 54, and the refrigerant discharge pipe 96. At this time, the refrigerant temperature 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 approximately +
It produces hot water at 90 ° C.

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, frost is formed on the evaporator 157 by such heating operation. 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.

Here, when the high-pressure refrigerant discharged from the second rotary compression element 34 is supplied to the evaporator 157 without depressurization and defrosted, the expansion valve 156 is fully opened and the first rotation is performed. The suction pressure of the compression element 32 rises, which causes the first
The discharge pressure (intermediate pressure) of the rotary compression element 32 is increased.
This refrigerant is discharged through the second rotary compression element 34, but because the expansion valve 156 is fully open, the second rotary compression element 3
Since the discharge pressure of No. 4 becomes the same as the suction pressure of the first rotary compression element 32, a pressure reversal phenomenon occurs between the discharge (high pressure) and suction (intermediate pressure) of the second rotary compression element 34. I will end up. However, since the refrigerant gas at the intermediate pressure discharged from the first rotary compression element 32 is taken out from the closed container 12 to defrost the evaporator 157 as described above, the reversal phenomenon of the high pressure and the intermediate pressure. Will be able to prevent.

In the above embodiment, the plug 137 was inserted into the accommodating portion 70A by a clearance fit. However, even when the plug 137 is press-fitted into the accommodating portion 70A, the portion corresponding to the plug 137 as shown in FIG. If an escape portion 54C recessed in a direction away from the upper cylinder 38 is formed in the upper support member 54, the deformation of the upper cylinder 38 due to the press-fitting of the plug is absorbed by the escape portion 54C, and the sealing performance is prevented from being deteriorated. Is possible.

Further, the rotary compressor is not limited to the internal intermediate pressure type multi-stage compression type rotary compressor as in the embodiment, but is also effective for a single cylinder rotary compressor in claims 1 and 2. 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.

[0059]

As described above in detail, according to the invention of claim 1, in a rotary compressor having an electric element and a rotary compression element driven by the electric element in a closed container, the rotary compression element is provided. A roller that is fitted to an eccentric portion formed on the rotating shaft of the cylinder and the electric element for constituting and that rotates eccentrically in the cylinder, and abuts on this roller to divide the inside of the cylinder into a low pressure chamber side and a high pressure chamber side. A vane and a spring member for constantly urging the vane toward the roller,
A storage portion of the spring member formed on the cylinder and opened to the vane side and the closed container side, a plug located on the closed container side of the spring member and inserted into the storage portion with a clearance fit, and a peripheral surface of the plug. Since it is attached and has an O-ring that seals between the plug and the housing, the cylinder deforms and the sealing performance deteriorates, resulting in poor performance, as when the plug is press-fitted in the housing. You will be able to avoid.

Even with such clearance fitting, since the distance between the cylinder and the closed container is set smaller than the distance from the O-ring to the end of the plug on the closed container side, the plug is pushed out of the storage part. There is no problem in the function of the plug, because the O-ring is still located in the storage portion and seals when it moves in the closed direction and comes into contact with the closed container to prevent the movement.

Particularly, in the multistage compression type rotary compressor in which the inside of the hermetically sealed container has an intermediate pressure,
When CO ₂ gas as described in claim 5 is used as a refrigerant and the inside of the closed container has an intermediate pressure and the inside of the second rotary compression element has an extremely high pressure, a remarkable effect is obtained in maintaining the performance of the compressor and preventing the spring member from coming off. It plays.

According to the third aspect of the present invention, in a rotary compressor having an electric element and a rotary compression element driven by the electric element in a closed container, a cylinder and an electric element for constituting the rotary compression element are provided. A roller fitted in an eccentric part formed on the rotary shaft of the element to rotate eccentrically in the cylinder, a support member that closes the opening surface of the cylinder and has a bearing of the rotary shaft, and a roller that contacts the roller A vane that divides the vane into a low-pressure chamber side and a high-pressure chamber side, a spring member for constantly biasing the vane to the roller side, and a storage portion of a spring member formed in the cylinder and opened to the vane side and the closed container side. A plug that is located on the closed container side of the spring member and is press-fitted and fixed in the housing, and a relief portion that is recessed in the direction away from the cylinder is provided in the support member of the portion corresponding to this plug. Since form was, even if the cylinder by a press-fitting the plug in the housing portion is deformed so as to expand the support member side, to absorb the deformation of the cylinder by the relief portion,
It is possible to avoid the inconvenience that a gap is generated between the cylinder and the support member. As a result, it is possible to avoid the inconvenience that the performance is deteriorated due to the deterioration of the sealing property due to the deformation of the cylinder.

Particularly, in the rotary compressor of the multi-stage compression type in which the inside of the hermetically sealed container has an intermediate pressure,
When CO ₂ gas as described in claim 5 is used as a refrigerant and the inside of the closed container has an intermediate pressure and the inside of the second rotary compression element has an extremely high pressure, a remarkable effect is obtained in maintaining the performance of the compressor and preventing the spring member from coming off. It plays.

[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 and an upper cover of the rotary compressor of 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.

19 is an enlarged cross-sectional view of another embodiment of the vane portion of the second rotary compression element of the rotary compressor of FIG.

[Explanation of symbols]

10 Rotary compressor 12 airtight container 12A end cap 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 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 131 Through hole (oil supply passage) 132 sealing material 133,134 communication holes 137 plug 138 O-ring 141, 142, 143, 144 Sleeves 146 Accumulator 147,148 Bracket 151 Tsuba 153 water heater 154 gas cooler 156 expansion valve 157 evaporator 158 Defrost Tube 159 Solenoid valve

   ─────────────────────────────────────────────────── ─── 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) 3H029 AA05 AA13 AB03 BB43 CC03                       CC05 CC19

Claims (5)

[Claims] 1. A rotary compressor comprising an electric element and a rotary compression element driven by the electric element in a closed container, wherein a cylinder for constituting the rotary compression element and a rotary shaft of the electric element are provided. A roller fitted into the formed eccentric portion and rotating eccentrically in the cylinder, a vane that abuts the roller and divides the inside of the cylinder into a low pressure chamber side and a high pressure chamber side, and the vane is always on the roller side. A spring member for urging the spring member, an accommodating portion of the spring member formed on the cylinder and opening to the vane side and the closed container side, and a storage member located on the closed container side of the spring member in the accommodating portion. And a O-ring that is attached to the peripheral surface of the plug and seals between the plug and the accommodating portion, and a gap between the cylinder and the closed container. , Rotary compressor is characterized in that set smaller than the distance from the O ring to the end of the sealed container side of the plug. 2. A hermetic container is provided with an electric element and first and second rotary compression elements driven by the electric element, and gas compressed by the first rotary compression element is contained in the hermetic container. Is discharged to the second, and the discharged intermediate pressure gas is discharged to the second
In the rotary compressor for compressing with the rotary compression element, a roller for eccentrically rotating in the cylinder, which is fitted to a cylinder for forming the second rotary compression element, and an eccentric portion formed on a rotation shaft of the electric element. A vane that abuts on the roller and divides the inside of the cylinder into a low pressure chamber side and a high pressure chamber side; a spring member for constantly biasing the vane toward the roller side; and a vane formed on the cylinder. Side and an opening of the spring member that is open to the closed container side, a plug that is located on the closed container side of the spring member and that is inserted into the storage part by a gap fit, and attached to the peripheral surface of the plug. And an O-ring for sealing between the plug and the accommodating portion, and a distance between the cylinder and the closed container is a distance from the O-ring to an end of the plug on the closed container side. A rotary compressor characterized by being set smaller than the separation. 3. A rotary compressor comprising an electric element and a rotary compression element driven by the electric element in a hermetically sealed container, wherein a cylinder for constituting the rotary compression element and a rotary shaft of the electric element are provided. A roller fitted into the formed eccentric portion and rotating eccentrically in the cylinder; a support member that closes the opening surface of the cylinder and has a bearing for the rotary shaft; A vane for partitioning the vane into a low-pressure chamber side and a high-pressure chamber side, a spring member for constantly biasing the vane toward the roller side, and a spring formed in the cylinder and opened to the vane side and the closed container side. A storage part for the member, and a plug located on the closed container side of the spring member and press-fitted and fixed in the storage part. Rotary compressor, characterized in that the formation of the relief portion which is recessed in a direction away from the cylinder. 4. A hermetic container provided with an electric element and first and second rotary compression elements driven by the electric element, wherein gas compressed by the first rotary compression element is stored in the hermetic container. Is discharged to the second, and the discharged intermediate pressure gas is discharged to the second
In the rotary compressor for compressing with the rotary compression element, a roller for eccentrically rotating in the cylinder, which is fitted to a cylinder for forming the second rotary compression element, and an eccentric portion formed on a rotation shaft of the electric element. A vane that abuts the roller to partition the inside of the cylinder into a low pressure chamber side and a high pressure chamber side; a support member that closes the opening surface of the cylinder and has a bearing for the rotating shaft; A spring member for urging to the roller side, a housing portion of the spring member formed in the cylinder and opened to the vane side and the closed container side, and a spring member located on the closed container side of the spring member. A plug press-fitted and fixed in the accommodating portion, and a relief portion recessed in a direction away from the cylinder is formed in a portion of the support member corresponding to the plug. A rotary compressor characterized by. 5. The rotary compression element compresses CO ₂ gas as a refrigerant, wherein the rotary compression element compresses CO ₂ gas as a refrigerant.
The rotary compressor according to claim 3 or 4.