JP2003161279A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary compressor capable of providing a plug for preventing the falling of a spring member in a prescribed position and also preventing the deformation of a cylinder. <P>SOLUTION: This rotary compressor comprises a roller 46 fitted to an upper cylinder 38 for constituting the rotary compressing element 34 of the rotary compressor and an eccentric part formed on the rotating shaft of an electric element and eccentrically rotated within the upper cylinder; a vane 50 allowed to abut on the roller to partition the upper cylinder inner part to a low-pressure chamber side and a high-pressure chamber side; a spring 76 for regularly energizing the vane to the roller side; a housing part 70A for the spring formed on the upper cylinder and opened to the vane side and a sealed casing 12 side; and a plug 137 located on the sealed casing side of the spring and inserted into the housing part by clearance-fitting. A locking part 201 on which the plug 137 abuts in a prescribed position is formed on the inner wall of the housing part 70A located on the spring 76 side of the plug 137. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention comprises an electric element in a closed container and first and second rotary compression elements driven by the electric element, and a gas compressed by the first rotary compression element. The present invention relates to a rotary compressor that discharges a gas having a medium pressure into a closed container and further compresses the discharged intermediate-pressure gas by a second rotary compression element.

[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. The refrigerant gas is discharged from the high pressure chamber side through the discharge port and the discharge muffling chamber. Then, for example, in the case of a hot water supply device, the discharged refrigerant gas then flows into the radiator, radiates heat, is throttled by the expansion valve, absorbs heat in the evaporator, and is sucked into the first rotary compression element. Repeat the cycle.

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).
aG).

[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.

Therefore, for example, if the outer diameter of the plug is made smaller than the inner diameter of the spring hole to prevent the deformation of the cylinder (in this case, it is necessary to prevent the plug from coming off to the closed container side). .), When the rotary compressor stops and the pressure on the high-pressure side in the cylinder drops, the intermediate pressure in the closed container pushes the plug toward the spring side, crushing the spring and hindering the operation. Occurs.

On the other hand, for example, when the outer diameter of the plug is made larger than the inner diameter of the spring hole to the extent that the cylinder is not deformed, there is a problem that it is difficult to determine how much the plug should be inserted in the process of press-fitting the plug into the spring hole. Occur.

The present invention has been made in order to solve the problems of the prior art, and a plug for preventing the spring member from falling off is provided at a predetermined position, and deformation of the cylinder can be prevented. It is intended to provide a rotary compressor.

[0009]

That is, a rotary compressor of the present invention comprises an electric element in a closed container and first and second rotary compression elements driven by the electric element.
The gas compressed by the first rotary compression element is discharged into the closed container, and the discharged intermediate-pressure gas is compressed by the second rotary compression element. 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, a spring member for constantly urging the vane toward the roller, 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 located on the closed container side. The housing is provided with a plug for sealing the housing, and a locking portion with which the plug abuts at a predetermined position is formed on the inner wall of the housing located on the spring member side of the plug. It is characterized by

In the rotary compressor according to a second aspect of the present invention, the outer diameter of the plug is set to be larger than the inner diameter of the accommodating portion within the range where the cylinder is not deformed when the plug is inserted into the accommodating portion. Is characterized by.

The rotary compressor of the invention of claim 3 is characterized in that, in claim 1, the outer diameter of the plug is set smaller than the inner diameter of the housing portion.

The rotary compressor according to a fourth aspect of the present invention is characterized in that, in each of the above inventions, the locking portion is formed by reducing the inner peripheral wall of the storage portion in a stepped shape.

The rotary compressor according to a fifth aspect of the present invention is characterized in that, in each of the above inventions, the first and second rotary compression elements compress CO ₂ gas as a refrigerant.

According to the present invention, the closed container is provided with the electric element and the first and second rotary compression elements driven by the electric element, and the gas compressed by the first rotary compression element is closed. In a rotary compressor that discharges into a container and further compresses the discharged intermediate-pressure gas by a second rotary compression element, the rotary compressor is formed on a rotary shaft of a cylinder and an electric element for constituting the second rotary compression element. A roller that is fitted to the eccentric portion and rotates eccentrically in the cylinder; a vane that abuts this roller to divide the inside of the cylinder into a low pressure chamber side and a high pressure chamber side; and to constantly bias this vane to the roller side. The spring member and the storage portion of the spring member formed in the cylinder, which is open to the vane side and the closed container side, and the spring member, which is provided in the storage portion on the closed container side and seals the storage portion. Equipped with a plug The inner wall of the housing part located on the spring member side of the plug, since the plug was formed in contact with the locking portion at a predetermined position, the plug can not move any further spring member side by the locking unit.

This makes it possible to define the position of the plug at a predetermined position. Therefore, for example, when the outer diameter of the plug is set to be larger than the inner diameter of the accommodating portion within the range where the cylinder is not deformed when the plug is inserted into the accommodating portion, the cylinder is deformed by the plug insertion. While avoiding this, positioning can be performed when the plug is press-fitted into the housing, and the workability of attaching the plug is improved.

When the outer diameter of the plug is set to be smaller than the inner diameter of the storage portion, for example, when the rotary compressor stops, the intermediate pressure in the closed container causes the plug to move toward the spring member side. It is possible to avoid the inconvenience of being pushed into.

According to the invention of claim 4, in addition to the above-mentioned inventions, the locking portion is formed by reducing the inner peripheral wall of the storage portion in a stepped shape, so that the locking portion is locked in the storage portion of the cylinder. The parts can be easily formed, and the production cost is reduced.

In particular, when the CO ₂ gas is used as the refrigerant and the pressure difference becomes large as in the fifth aspect of the invention, the present invention exerts a remarkable effect in improving the performance of the rotary compressor.

[0019]

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 a ring 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.

The lower support member 56 is made of an iron-based sintered material (or a casting), and the surface (lower surface) on which the lower cover 68 is attached 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 portion of the discharge muffling chamber 62 communicating 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 upper cover 66 have such a thickness dimension, it is possible to achieve miniaturization while sufficiently withstanding the pressure of the discharge muffling chamber 62, which is higher than that in the closed container 12, and to achieve the size reduction of 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. , 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 the 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, there are formed 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. 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. A metal plug 137 is press-fitted into the housing portion 70A of the spring 76 on the airtight container 12 side from an opening on the outer side of the housing portion 70A (on the airtight container 12 side) to prevent the spring 76 from coming off. Play a role.

In this case, the outer diameter dimension of the plug 137 is set larger than the inner diameter dimension of the storage section 70A so that the upper cylinder 38 does not deform when it is pressed into the storage section 70A. That is, in the embodiment, the outer diameter dimension of the plug 137 is 4 μm to 2 μm smaller than the inner diameter dimension of the housing portion 70A.
It is designed to be 3 μm larger. 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.

Further, as shown in an enlarged manner in FIG. 19, the outer end of the plug 137 is located outside the housing portion 70A (the closed container 12).
Side), when the plug 137 is press-fitted to a predetermined position located at the opening edge (outer end of the storage portion 70A), the plug 13
A locking portion 201 with which the inner end of the plug 137 abuts is formed at a portion of the storage portion 70A where the end portion (inner end) of the spring 7 on the spring 76 side is located. When the storage portion 70A is cut into the upper cylinder 38, the locking portion 201 is thinner than a drill that cuts the inside diameter of the storage portion 70A inside (the vane 50 side) of the storage portion 70A. It is formed by changing the diameter of the inner peripheral wall of the storage portion 70A into a stepped shape instead of the one.

The outer end of the upper cylinder 38, that is, the distance between the outer end of the housing portion 70A and the container body 12A of the closed container 12 is determined by the O-ring 138 to the outer end of the plug 137 (the end on the closed container 12 side). ) Is set smaller than the distance. 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 plug 13
7, the spring 76 side has a high pressure, and the closed container 12 side has an intermediate pressure.

By setting the dimensional relationship between the plug 137 and the accommodating portion 70A as described above, the upper cylinder 38 is deformed by the press-fitting of the plug 137, and the sealing performance between the upper support member 54 and the upper support member 54 is deteriorated to deteriorate the performance. It becomes possible to avoid the inconvenience. Further, with such a structure, when the plug 137 is press-fitted from the opening on the outside of the storage section 70A, the predetermined position shown in FIG. 19 (the outer end of the plug 137 is located at the opening edge on the outside of the storage section 70A). (When it is located), the plug 137 is engaged with the locking portion 20.
As it abuts 1 and can no longer be press-fitted, plug 1
Positioning can be performed when 37 is press-fitted into the storage portion 70A,
The workability of attaching the plug 137 is improved. In particular, since the plug 137 is not forcedly pushed, the upper cylinder 38 can be prevented from being deformed due to the forced press-fitting.

By the way, the connecting portion 90 which connects the upper and lower eccentric portions 42 and 44 formed integrally 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 and the like, and oil as a lubricating oil is used. 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 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 to 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).

Then, 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.

Particularly, 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 to make the first rotation. 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 outer diameter of the plug 137 is set larger than the inner diameter of the accommodating portion 70A so that the upper cylinder 38 does not deform, and the plug 137 is press-fitted into the accommodating portion 70A. However, without being limited to this, the outer diameter dimension of the plug 137 may be set smaller than the inner diameter dimension of the storage portion 70A, and the plug 137 may be inserted into the storage portion 70A by a clearance fit.

With such a dimensional relationship, the upper cylinder 38 is deformed and the sealing property with the upper support member 54 deteriorates,
It becomes possible to surely avoid the inconvenience that deteriorates the performance. Even with such a clearance fit, as described above, the space between the upper cylinder 38 and the closed container 12 is set to the O-ring 13.
Since it is set to be smaller than the distance from 8 to the end of the plug 137 on the closed container 12 side, the high pressure on the spring 76 side (back pressure of the vane 50) causes the plug 137 to move in the direction in which it is pushed out of the housing portion 70A. Even closed container 1
O-ring 13 still remains when it abuts 2 and is blocked from moving.
No. 8 does not cause any problem in the function of the plug 138, because 8 is located and sealed in the storage portion 70A.

When the rotary compressor 10 is stopped, the pressure in the upper cylinder 38 is influenced by the low pressure side via the refrigerant circuit and becomes lower than the intermediate pressure in the closed container 12. In such a case, the plug 137 tends to be pushed into the spring 76 side by the pressure in the closed container 12. However, in this case, the plug 137 abuts the locking portion 201 and cannot move to the spring 76 side any more. The inconvenience that the plug 137 is crushed by the movement of the plug 137 does not occur.

Further, in the embodiment, the rotary compressor 1
Although 0 is used for the refrigerant circuit of the hot water supply device 153, the present invention is not limited to this and is also effective when used for heating the room.

[0066]

As described above in detail, according to the present invention, the electric element in the closed container and the first element driven by the electric element are provided.
And a second rotary compression element, the gas compressed by the first rotary compression element is discharged into a closed container, and the discharged intermediate-pressure gas is compressed by the second rotary compression element. In a cylinder for constituting the second rotary compression element and an eccentric portion formed on the rotary shaft of the electric element, a roller that eccentrically rotates in the cylinder and a low pressure inside the cylinder that abuts on the roller. A vane that divides the chamber side and the high-pressure chamber side, a spring member that constantly urges the vane toward the roller side, a storage portion of a spring member that is formed in the cylinder and that opens to the vane side and the closed container side, and a spring. The plug is provided on the closed container side of the member and is provided in the storage part, and has a plug for sealing the storage part, and the plug is located at a predetermined position on the inner wall of the storage part located on the spring member side of the plug. Abutting contact Since part was formed, the plug can not move any further spring member side by the locking unit.

This makes it possible to define the position of the plug at a predetermined position. Therefore, for example, when the outer diameter of the plug is set to be larger than the inner diameter of the accommodating portion within the range where the cylinder is not deformed when the plug is inserted into the accommodating portion, the cylinder is deformed by the plug insertion. While avoiding this, positioning can be performed when the plug is press-fitted into the housing, and the workability of attaching the plug is improved.

When the outer diameter of the plug is set to be smaller than the inner diameter of the storage portion, for example, when the rotary compressor stops, the intermediate pressure in the closed container causes the plug to move toward the spring member side. It is possible to avoid the inconvenience of being pushed into.

According to the invention of claim 4, in addition to the above inventions, the locking portion is formed by reducing the inner peripheral wall of the storage portion in a stepped shape, so that the locking portion is locked in the storage portion of the cylinder. The parts can be easily formed, and the production cost is reduced.

In particular, when the CO ₂ gas is used as the refrigerant and the pressure difference becomes large as in the fifth aspect of the invention, the present invention exerts a remarkable effect in improving the performance of the rotary compressor.

[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 the plug portion of the second rotary compression element of the rotary compressor of FIG.

[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 Vertical cylinder 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) 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 153 water heater 154 gas cooler 156 expansion valve 157 evaporator 158 Defrost Tube 159 Solenoid valve 201 Locking part

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Dai Matsuura             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 Masaya Tadano             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Haruhisa Yamazaki             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. F-term (reference) 3H029 AA05 AA13 AB03 AB08 BB32

Claims (5)

[Claims] 1. A hermetic container provided with an electric element and first and second rotary compression elements driven by the electric element, wherein the 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 the storage portion of the spring member opened to the closed container side, and provided in the storage portion located on the closed container side of the spring member, and a plug for sealing the storage portion, A rotary compressor characterized in that an engaging portion with which the plug abuts at a predetermined position is formed on an inner wall of the accommodating portion located on the spring member side of the plug. 2. The outer diameter of the plug is set to be larger than the inner diameter of the accommodating portion within a range in which the cylinder is not deformed when the plug is inserted into the accommodating portion. 1 rotary compressor. 3. The outer diameter of the plug is set smaller than the inner diameter of the housing portion.
Rotary compressor. 4. The rotary compressor according to claim 1, wherein the locking portion is formed by reducing the inner peripheral wall of the storage portion in a stepped shape. 5. The first and second rotary compression elements are C
The rotary compressor according to claim 1, claim 2, claim 3 or claim 4, wherein O ₂ gas is compressed as a refrigerant.