JP2003201982A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To simplify a structure for applying back pressure to a vane of a second rotary compression element and improve operation efficiency and durability of an internal intermediate-pressure multistage rotary compressor. <P>SOLUTION: This rotary compressor 10 with first and second rotary compression elements 32 and 34 has a roller 46 which is engaged with an eccentric unit 42 of a rotary shaft of an electric element 14 constituting the second rotary compression element 34 and rotates eccentrically in a cylinder 38, a vane 50 which abuts on the roller 46 and divides the cylinder 38 into a low-pressure chamber and a high-pressure chamber, and a back pressure chamber which communicates with a guide groove formed in the cylinder 38 and storing a vane 50, is formed in the cylinder 38, and applies back pressure to the vane 50. A vane-side recessed groove is formed on the vane 50 at the position opposite to a cylinder-side recessed groove formed inside the guide groove. The vane-side recessed groove and the cylinder-side recessed groove communicate with the high-pressure chamber and the back pressure chamber in the cylinder 38 within the designated rotation angle of the roller 46. <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 first and second rotary compression elements driven by electric elements in a closed container, compressed by the first rotary compression element and discharged into the closed container. The present invention also relates to a rotary compressor that compresses intermediate pressure gas with a second rotary compression element.

[0002]

2. Description of the Related Art In a conventional internal intermediate pressure type multi-stage compression type rotary compressor, a gas (refrigerant gas) is sucked into a low pressure chamber side of a cylinder from a suction port of a first rotary compression element and compressed by an operation of a roller and a vane. Then, the pressure becomes an intermediate pressure and is 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 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 gas is generated. Next to
It is discharged from the high-pressure chamber side through the discharge port and the discharge muffling chamber.

The gas discharged from the rotary compressor flows into the radiator of the refrigerant circuit, and after radiating the heat, it is throttled by the expansion valve, absorbed by the evaporator, and sucked by the first rotary compression element of the rotary compressor. repeat.

When a refrigerant having a large difference in high pressure and low pressure, for example, carbon dioxide (CO ₂ ) is used as the refrigerant in the rotary compressor, the pressure of the discharged refrigerant reaches 12 MPaG in the second rotary compression element which becomes high pressure, while The first rotary compression element on the lower stage side has a pressure of 8 MPaG (intermediate pressure) (the suction pressure of the first rotary compression element is 4 MPa).

[0005]

A vane attached to such a rotary compressor is inserted into a guide groove provided in the radial direction of the cylinder so as to be movable in the radial direction of the cylinder. Since this vane needs to be pressed against the roller side, conventionally, a structure has been adopted in which the vane is pressed against the roller by the biasing force of the spring and the back pressure from the back pressure chamber. In the rotary compression element of No. 2, since the pressure in the cylinder becomes higher than the intermediate pressure in the closed container, the pressure in the closed container cannot be used as the back pressure of the vane, and it is extremely difficult to apply the back pressure. It was a thing.

The present invention was made in order to solve the problems of the prior art, and in a so-called internal intermediate pressure type multi-stage compression type rotary compressor, a structure for applying a back pressure to the vane of the second rotary compression element. It is intended to simplify the operation and improve the operation efficiency and durability.

[0007]

That is, a rotary compressor of the present invention comprises an electric element in a hermetically sealed container and first and second rotary compression elements driven by the electric element. A gas compressed by a compression element is discharged into a closed container, and the discharged intermediate-pressure gas is compressed by a second rotary compression element, which constitutes a second rotary compression element. A roller that is fitted to an eccentric portion formed on the rotary shaft of the cylinder and the electric element and rotates eccentrically in the cylinder; a vane that abuts the roller and divides the cylinder into a low pressure chamber side and a high pressure chamber side; A guide groove for accommodating the vane, a back pressure chamber communicating with the guide groove and formed in the cylinder for applying a back pressure to the vane, and a cylinder side recess formed on the inner surface of the guide groove. Facing the groove and the groove on the cylinder side And a vane which is formed in the vane side groove of the location, these side vane groove and the cylinder-side groove is
The high pressure chamber side and the back pressure chamber in the cylinder communicate with each other within a predetermined rotation angle range of the roller.

In addition to the above, in the rotary compressor of the invention of claim 2, the vane side concave groove and the cylinder side concave groove have a roller position of 180 when the vane is most protruded.
When the angle is °, the high pressure chamber side and the back pressure chamber in the cylinder communicate with each other within a predetermined angle range including the 180 °.

Further, in the rotary compressor of the third aspect of the present invention, in addition to the second aspect, the vane-side concave groove and the cylinder-side concave groove have a high roller pressure within the cylinder at an angle of 120 ° or more and 240 ° or less. The chamber side and the back pressure chamber communicate with each other.

Further, in the rotary compressor of the invention of claim 4, in addition to the invention of claim 2, the vane side concave groove and the cylinder side concave groove have a high roller pressure within the cylinder at an angle of 90 ° to 270 °. The chamber side and the back pressure chamber communicate with each other.

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 the roller to divide the inside of the cylinder into a low pressure chamber side and a high pressure chamber side; and a vane formed in the cylinder for accommodating the vane. A guide groove, a back pressure chamber that is formed in the cylinder in communication with the guide groove and applies a back pressure to the vane, a cylinder-side groove formed in the inner surface of the guide groove, and a cylinder-side groove that faces the groove. Is formed in the vane where The vane side concave groove and the cylinder side concave groove communicate with the high pressure chamber side and the back pressure chamber inside the cylinder, so that the vane side concave groove and the cylinder side concave groove are connected to each other through the vane side concave groove and the cylinder side concave groove. The pressure on the high pressure chamber side can be supplied to the back pressure chamber.

As a result, in the rotary compressor having an intermediate pressure in the closed container, a back pressure for urging the vane toward the roller can be applied without any hindrance, and particularly the concave groove is guided to the cylinder. Since it is a simple structure that it is formed on the inner surface of the groove and the vane, the structure can be simplified and the production cost can be reduced.

Particularly, the vane side groove and the cylinder side groove are
A predetermined rotation angle range of the roller, that is, when the position of the roller when the vane is most protruded is 180 ° as shown in claims 2 to 4, within a predetermined angle range including the 180 °. For example, 120 ° or more and 240 ° or less,
Alternatively, the high pressure chamber side and the back pressure chamber in the cylinder are communicated with each other within an angle range of 90 ° or more and 270 ° or less. As a result, the gas remaining in the back pressure chamber is re-expanded when the pressure in the cylinder is reduced by sucking the gas, and the compression efficiency is reduced. It becomes possible to effectively eliminate inconveniences such as entering the pressure chamber and increasing the vane biasing force to increase the input, or lowering the durability of the vane and the roller.

As a result, according to the present invention, both the operating efficiency and the durability can be improved while simplifying the structure of the rotary compressor.

[0015]

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 electric element 1
4 has a height of about 80 mm (outer diameter 110 mm), and the rotary compression mechanism 18 has a height of about 70 mm (outer diameter 110 m).
m), the distance between the electric element 14 and the rotary compression mechanism portion 18 is about 5 mm. In addition, the second rotary compression element 34
The excluded volume of 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 20
Is a circular glass portion 20A to which the electrical terminal 139 is attached and is attached, and a metal attachment portion 20 formed around the glass portion 20A and projecting obliquely outward and downward in a brim shape.
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 formed 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 (FIG. 12) sandwiched between the main gasket 7 and the main bolt 7 having four peripheral parts through the gasket 124.
It is fixed to the upper support member 54 from above by 8 ... The tips of the main bolts 78 ...
Screw to 6.

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 gas leakage, and it is possible to expand 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 84 is the through hole 131 of the intermediate partition plate 36.
Then, the gas is supplied from the communication holes 133 and 134 to the suction side (suction port 161) of the upper cylinder 38.

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 the inconvenience that the high pressure back pressure applied to the vane 50 leaks from the back pressure chamber 74 described later.

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. Due to this dimensional relationship, the plug 137 is accommodated in the storage portion 70A.
As in the case where the upper cylinder 38 is deformed by press-fitting the inside, the sealability between the upper cylinder 38 and the upper support member 54 is deteriorated, and it is possible to avoid the inconvenience that the performance is deteriorated.

The outer dimension of the plug 137 is set smaller than the inner dimension of the storage portion 70A so that the plug 137 can be stored in the storage portion 70A.
Even when the clearance is fitted in A, the distance between the upper cylinder 38 and the closed container 12 is set smaller than the distance from the O-ring 138 to the end of the plug 137 on the closed container 12 side. High pressure (back pressure of vane 50)
Even if the plug 137 moves in the direction of being pushed out of the storage portion 70A, the O-ring 138 is still positioned in the storage portion 70A and seals when the plug 137 comes into contact with the closed container 12 and is prevented from moving. There is no problem with the function of.

Further, the back pressure chamber 74 for applying a back pressure for urging the vane 50 to the roller 46 to the vane 46 is formed on the accommodating portion 70A side of the guide groove 70 in the upper cylinder 38. ing. The back pressure chamber 74 has a substantially cylindrical shape extending between the intermediate partition plate 36 and the upper support member 54, and is formed so as to penetrate into the upper cylinder 38 (FIG. 19).
The back pressure chamber 74 is provided with the inner guide groove 70 and the storage portion 7.
It is connected to both 0A.

Further, on the inner surface of the guide groove 70 on the discharge port 39 side, as shown in FIG. 19, a plurality of cylinder side concave grooves 72 (three in the embodiment) extend in the radial direction of the upper cylinder 38. Each of the cylinder-side recessed grooves 72 ... Ends in front of the high pressure chamber of the upper cylinder 38, and the outer end thereof is opened in the back pressure chamber 74. That is, in this state, the cylinder side concave groove 72 ... Does not communicate with the high pressure chamber of the upper cylinder 38, but communicates only with the back pressure chamber 74.

On the other hand, on the side surface of the vane 50 on the side of the discharge port 39 at a position corresponding to each cylinder side concave groove 72, ... As shown in FIG. (3) This also extends in the radial direction of the upper cylinder 38 and is formed as a recess. Each vane-side recessed groove 52 ... From a position that is a predetermined dimension before the tip of the vane 50 (a tip that abuts against the roller 46) to a position that is a predetermined dimension before the rear end (the end on the back pressure chamber 74 side). It is formed in the range of.

Here, assuming that the rotation angle position of the roller 46 when the vane 50 is most retracted to the outer peripheral side of the upper cylinder 38 is 0 °, the rotation of the roller 46 when the vane 50 is most protruded into the upper cylinder 38. The angular position is 180 °. The rear portion of the vane-side groove 52, ... Wraps and communicates with the cylinder-side groove 72, ... even when the roller 46 reaches the rotation angle position of 180 °.
At that time, the front portion of the vane-side concave groove 52 ... Opens to the high-pressure chamber side in the upper cylinder 38. As a result, the high pressure chamber and the back pressure chamber 74 in the upper cylinder 38 are separated from each other by the concave groove 52 on the vane side.
.. and the cylinder side concave groove 72 ..

In this case, the front end of the vane-side concave groove 52 ... Is guided by the guide groove 70 of the upper cylinder 38 when the rotation angle position of the roller 46 is rotated from 0 ° and reaches an angle of 180 ° -α. From the top into the upper cylinder 38, and then 18
Upper cylinder 3 at the time of rotating up to 0 ° + α
It is submerged in the guide groove 70 of No. 8. In the embodiment, the vane side concave groove 5
When the rotation angle position of the roller 46 is rotated from 0 ° to an angle of 120 °, the front end of 2 ... is peeped into the upper cylinder 38 from the guide groove 70 of the upper cylinder 38, and 240 ° from there. It is formed at a position where it is submerged in the guide groove 70 of the upper cylinder 38 when rotated to an angle.

With this configuration, the vane side groove 5 is provided when the rotation angle position of the roller 46 is in the range of 120 ° to 240 °.
2 ··· and cylinder side concave groove 72 ···
The high pressure chamber side of No. 8 and the back pressure chamber 74 are communicated with each other, and the refrigerant gas in the high pressure chamber has a double recessed groove 52, ...
.. through the back pressure chamber 74, and the high pressure chamber side and the back pressure chamber 74 are not communicated with each other in the other angular range, and the refrigerant gas is prevented from flowing into the back pressure chamber 74. become.

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

The suction passage 5 of the upper support member 54 and the lower support member 56 is provided on the side surface of the container body 12A of the closed container 12.
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 attached to the closed container side bracket 147 welded and fixed to the upper side surface of the container body 12A of the closed container 12 via the accumulator side bracket 148. Has been. The bracket 148 extends upwardly from the bracket 147, and the accumulator 146
Is held in a substantially central portion in the vertical direction, and in this state, the accumulator 146 is arranged along the side of the closed container 12.

The refrigerant introducing pipe 92, after coming out of the sleeve 141, bends to the right in the embodiment and then rises, so that the lower end of the accumulator 146 comes close to the refrigerant introducing 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 airtightness test is performed in the completion inspection in the manufacturing process of the rotary compressor 10. Screw groove 15
2 can be used to easily screw the test pipe.

In particular, the upper and lower sleeves 141 and 1 which are adjacent to each other
42 has a flange 151 formed on one sleeve 141 and a thread groove 152 formed on the other sleeve 142, so that the test pipes can be connected to the sleeves 141, 142 in a narrow space.
Can be connected to.

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 introducing pipe 92, and via a solenoid valve 159 as a flow path control device. It is connected to a refrigerant discharge pipe 96 leading to the inlet of the gas cooler 154. 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: LP) which is 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 (4 MPaG) is compressed by the operation of the roller 48 and the vane to an intermediate pressure (MP1: 8 MPaG) from the high pressure chamber side of the lower cylinder 40 to the discharge port 41 and the discharge muffling chamber 64 formed in the lower support member 56. Intermediate discharge pipe 121 via communication passage 63
Is discharged into the closed container 12.

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).

The intermediate pressure refrigerant gas in the closed container 12 is discharged from the sleeve 144 (the intermediate discharge pressure is equal to the MP
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.

In the above-described second stage compression in the upper cylinder 38, in the initial stage of sucking the refrigerant gas in which the rotational angular position of the roller 46 starts from 0 °, the suction pressure (MP1) is also applied to the high pressure chamber side in the upper cylinder 38. Is equivalent to Therefore, when the back pressure chamber 74 and the upper cylinder 38 are communicated with each other in this state, the refrigerant gas remaining in the back pressure chamber 74 is re-expanded and the compression efficiency is reduced. Further, the function as a back pressure for urging the vane 50 toward the roller 46 side cannot be expected.

On the other hand, the rotation angle position of the roller 46 is 360
At the final stage of compression of the refrigerant gas heading toward °, the high-pressure chamber side has the extremely high high-pressure HP described above. Therefore, when the extremely high-pressure refrigerant gas flows into the back pressure chamber 74, the vane 50 is pressed against the roller 46 by the back pressure. The force becomes excessively large, the work amount for pushing the vane 50 into the guide groove 70 side becomes large, and the input (electric power) increases, so that the efficiency decreases.

However, in the present invention, as described above, the high pressure chamber side and the back pressure chamber 74 are communicated with each other only when the rotation angle position of the roller 46 is in the range of 120 ° to 240 °, and 0 ° to 1 °
Since the initial stage of suction in the range of 20 ° and the final stage of compression of 240 ° to 360 ° are not communicated with each other, such efficiency deterioration can be prevented. Further, since it is possible to prevent excessive back pressure that presses the vane 50 against the roller 46, the durability of both is improved and the lubrication characteristics are improved.

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

In particular, in an environment of low outside temperature, such heating operation causes frost to grow on the evaporator 157. In that case, the solenoid valve 159 is opened, the expansion valve 156 is fully opened, and the evaporator 157 is defrosted. As a result, the medium-pressure refrigerant (including a small amount of high-pressure refrigerant discharged from the second rotary compression element 34) in the closed container 12 reaches the gas cooler 154 through the defrost pipe 158. The temperature of this refrigerant is about +50 to + 60 ° C., and the gas cooler 154 does not radiate 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 of 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 high pressure chamber side and the back pressure chamber 74
180 as the rotational angle position of the roller 46 for communicating with
Although it is set to 120 ° to 240 ° which is a range of ° ± α, the rotational angle position of the roller 46 that connects the high pressure chamber side and the back pressure chamber 74 is actually the discharge port 39, the suction port, and the vane 5.
Since it is decided by the positional relationship of 0, for example, 90 ° or more and 270 °
The back pressure chamber 74 of the vane 50 may communicate with the high pressure chamber of the cylinder 38 at the following angles.

In the embodiment, in order to connect the high pressure chamber side in the upper cylinder 38 and the back pressure chamber 74 to each other, the cylinder side concave groove 72 and the vane side concave groove 52 are formed on the inner surface of the upper cylinder 38 and the side surface of the vane 50. Although three are provided, the number of the cylinder-side recessed grooves 72 and the vane-side recessed grooves 52 is not limited to this as long as the vane 50 can be smoothly operated.
Alternatively, four or more may be provided.

[0071]

As described above in detail, according to the present invention, the first rotary compression element is provided with the electric element and the first and second rotary compression elements driven by the electric element in the closed container. In the rotary compressor that discharges the gas compressed by the above into the closed container and further compresses the discharged intermediate pressure gas by the second rotary compression element, a cylinder and an electric motor for constituting the second rotary compression element. 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 against the roller and divides the inside of the cylinder into a low pressure chamber side and a high pressure chamber side, a guide groove formed in the cylinder and for accommodating the vane, and a vane formed in communication with the guide groove in the cylinder. A back pressure chamber for applying a back pressure to the cylinder, a cylinder side concave groove formed on the inner surface of the guide groove, and a vane side concave groove formed in a vane at a position facing the cylinder side concave groove. Since the vane side groove and the cylinder side groove communicate with the high pressure chamber side and the back pressure chamber in the cylinder, the pressure on the high pressure chamber side in the cylinder is backed up via these vane side groove and the cylinder side groove. The pressure chamber can be supplied.

As a result, in the rotary compressor having an intermediate pressure in the closed container, the back pressure for urging the vane toward the roller can be applied without any hindrance, and especially the concave groove can be guided to the cylinder. Since it is a simple structure that it is formed on the inner surface of the groove and the vane, the structure can be simplified and the production cost can be reduced.

Particularly, the vane side concave groove and the cylinder side concave groove are
A predetermined rotation angle range of the roller, that is, when the position of the roller when the vane is most protruded is 180 ° as shown in claims 2 to 4, within a predetermined angle range including the 180 °. For example, 120 ° or more and 240 ° or less,
Alternatively, the high pressure chamber side and the back pressure chamber in the cylinder are communicated with each other within an angle range of 90 ° or more and 270 ° or less. As a result, the gas remaining in the back pressure chamber is re-expanded when the pressure in the cylinder is reduced by sucking the gas, and the compression efficiency is reduced. It becomes possible to effectively eliminate inconveniences such as entering the pressure chamber and increasing the vane biasing force to increase the input, or lowering the durability of the vane and the roller.

As a result, according to the present invention, it is possible to improve both operating efficiency and durability while simplifying the structure 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.

FIG. 19 is an enlarged perspective view near the guide groove of the upper and lower cylinders.

FIG. 20 is an enlarged perspective view of a vane.

FIG. 21 is a diagram showing a state in which the refrigerant gas on the high pressure chamber side flows into the back pressure chamber.

[Explanation of symbols]

10 Rotary compressor 12 airtight container 14 Electric elements 16 rotation axes 18 Rotary compression mechanism 20 terminals 32 First rotary compression element 34 Second rotary compression element 36 Intermediate partition plate 38, 40 cylinders 39, 41 Discharge port 42 Eccentric part 44 Eccentric part 46 Laura 48 Roller 50 vanes 52 Vane side concave groove 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 72 Cylinder side concave groove 74 Back pressure chamber 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 Takashi Sato             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 Hiroyuki Matsumori             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 Takayasu Saito             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. (72) Inventor Masaya Tadano             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. (72) Inventor Atsushi Ono             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. F-term (reference) 3H029 AA04 AA09 AA13 AB03 AB08                       BB42 BB43 BB44 CC03 CC04                       CC06 CC54

Claims (4)

[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 the roller to partition the inside of the cylinder into a low pressure chamber side and a high pressure chamber side; a guide groove formed in the cylinder for accommodating the vane; and a vane communicating with the guide groove. A back pressure chamber formed in a cylinder for applying a back pressure to the vane, a cylinder side groove formed in an inner surface of the guide groove, and a vane formed at a position facing the cylinder side groove. A vane side concave groove, wherein the vane side concave groove and the cylinder side concave groove communicate with the high pressure chamber side and the back pressure chamber in the cylinder within a range of a predetermined rotation angle of the roller. You Rotary compressor. 2. The vane-side groove and the cylinder-side groove are
The position of the roller when the vane is most protruded is set to 1
The rotary compressor according to claim 1, wherein, when it is set to 80 °, the high pressure chamber side in the cylinder and the back pressure chamber communicate with each other within a predetermined angle range including the 180 °. 3. The vane side concave groove and the cylinder side concave groove,
The rotary compressor according to claim 2, wherein the position of the roller communicates the high pressure chamber side in the cylinder with the back pressure chamber at an angle of 120 ° or more and 240 ° or less. 4. The vane side groove and the cylinder side groove are
The rotary compressor according to claim 2, wherein the position of the roller communicates the high pressure chamber side in the cylinder with the back pressure chamber at an angle of 90 ° or more and 270 ° or less.