JPH0310395Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a vane compressor for compressing refrigerant gas, etc. for a vehicle air conditioner.

(Prior Art) Generally, a vane type compressor, which has a simple configuration and is suitable for high-speed rotation, is employed as a refrigerant gas compressor for a vehicle air conditioner. Conventionally, this type of vane compressor is constructed as shown in FIGS. 1 and 2. That is, the discharge port 1a has a cylindrical shape.
By bolting the front head 2, which is provided with a suction port 2a and suction chambers 2b, 2c communicating with the suction port 2a, to a case 1 provided with a
The housing 3 has a closed structure. Inside the housing 3 is a cam ring 4 which has an elliptical cam surface on its inner peripheral surface 4c, is open at both end surfaces, and has discharge ports 4d and 4e bored in its peripheral wall that communicate with compression chambers 10 and 11, which will be described later. is stored. One end surface 4a of the cam ring 4 has suction chambers 2b, 2c.
and one end of the compression chambers 10, 11.
Front side block 5 with holes b and 5c
One end surface 5a of the two is airtightly abutted. A rear side block 6 is attached to the other end surface 4b of the cam ring 4.
One end surface of the two is airtightly abutted. A rotating shaft 7 is rotatably supported by the front side block 5 and the rear side block 6. A rotor 8 rotatably housed within a cam ring 4 is fixed to the rotating shaft 7. Vanes 9 are slidably fitted into a plurality of vane grooves 8b which are formed in the rotor 8 at predetermined intervals in the circumferential direction and along the radial direction. The tips of these vanes 9 are adapted to come into sliding contact with the inner circumferential surface 4c of the cam ring 4. Inner peripheral surface 4 of cam ring 4
c, the outer peripheral surface 8a of the rotor 8, and the vane 9,
Compression chambers 10, 11 are defined. Discharge valves 12 and 13 are attached to discharge ports 4d and 4e of the cam ring 4. A discharge chamber 15 is defined between the inner circumferential surface of the housing 3, the outer circumferential surface of the cam ring 4, and the outer circumferential surface of the rear side block 6. In addition,
The cam ring 4 and both side blocks 5 and 6 constitute a pump body 14.

When the rotor 8 rotates together with the rotating shaft 7 in relation to the engine, the volumes of the compression chambers 10 and 11 change from the minimum to the maximum during the suction stroke, and from the maximum to the minimum during the discharge stroke. During the suction stroke, the refrigerant gas introduced into the suction chambers 2b, 2c from the suction port 2a flows through the suction ports 5b, 5c into the compression chamber 1.
0 and 11, is compressed during the discharge stroke, and is discharged into the discharge chamber 15 from the discharge ports 4d and 4e. This action is repeated to suction, compress and discharge the refrigerant gas.

(Problem to be solved by the invention) By the way, the pressure of the refrigerant gas discharged into the discharge chamber 15 is very high, approximately 14 to 15 kg/cm ² , and the wall of the pump body 14 is designed to absorb the pressure of this high-pressure refrigerant gas. Is receiving. On the other hand, the pressure of the refrigerant gas sucked is approximately 2
Kg/cm ² is low, and for this reason, especially A,
The pressure difference between the internal pressure and the external pressure of the pump body 14 is greatest in the range near the suction ports 5b, 5c of the compression chambers 10, 11 of the pump body 14, indicated by A'. As a result, the cam ring 4 in this range
High pressure refrigerant gas easily enters into the compression chambers 10, 11 from the contact points between the side blocks 5, 6 and the side blocks 5, 6.

When high-pressure refrigerant gas enters the compression chambers 10, 11, low-pressure refrigerant gas is no longer sucked into the compression chambers 10, 11 from the suction ports 5b, 5c, resulting in a reduction in compression performance. In order to prevent such a decrease in compression performance, both end surfaces 4a and 4b of the cam ring 4 must be
It is essential to improve the accuracy of assembly of the end faces 5a, 6a of the side blocks 5, 6, thereby increasing the accuracy of assembly and improving airtightness.

However, each end surface 4a, 4b, 5a, 6a
Improving the processing accuracy of the pump body 14 and the assembly accuracy of the pump body 14 have led to an increase in costs.

The present invention has been made in view of the above circumstances, and aims to provide a vane type compressor that has a simple configuration and can prevent leakage of high-pressure refrigerant gas into the compression chamber without increasing costs. It is something.

(Means for Solving the Problems) In order to achieve the above object, the vane type compressor of the present invention provides a vane type compressor that is located on at least one of both end faces of a cam ring and the abutment faces of both side blocks that come into contact with these end faces. In addition, a groove is provided at a location where there is a large pressure difference between the inside and outside of the pump body, the groove approximately following the compression chamber and located outside the suction port in the circumferential direction of the suction port.

(Function) When the high-pressure refrigerant gas that attempts to enter the compression chamber expands within the groove, its energy is lost, and the high-pressure refrigerant gas does not leak into the compression chamber.

(Example) An example of the present invention will be described in detail below with reference to FIGS. 3 and 4.

3 and 4 are a longitudinal sectional view and a transverse sectional view of the vane type compressor of the present invention. In both figures, the same components as those of the conventional vane compressor shown in FIGS. 1 and 2 are designated by the same reference numerals, and detailed explanation thereof will be omitted.

In FIGS. 3 and 4, the front side Block 5
substantially arc-shaped grooves 4f, which are located on the outside of each refrigerant gas inlet 5b, 5c and run along the compression chambers 10, 11;
4g is formed. Each of these grooves 4f, 4g
The length along the circumferential direction is set longer than the length along the circumferential direction of the suction ports 5b and 5c. Additionally, grooves 4f and 4g are also provided on the other end surface 4b of the cam ring 4.
Arc-shaped grooves 4f' and 4g' similar to these grooves 4f and 4g are formed at positions corresponding to the grooves 4f and 4g.

A front side block 5 and a rear side block 6 are fixed to both end surfaces 4a and 4b of the cam ring 4, respectively, by bolts (not shown) as in the conventional case. Each of these side blocks 5,
The end surfaces 5a and 6a of the cam ring 6 are in airtight contact with both end surfaces 4a and 4b of the cam ring 4, respectively.

The rest of the structure is similar to the conventional vane type compressor shown in FIGS. 1 and 2 described above.

In the above configuration, the pressure of the high-pressure refrigerant gas in the discharge chamber 15 applied to the outside of the pump body 14 is controlled by the cam ring 4 constituting the pump body 14 as described above.
and the contact surfaces 4a and 5 of both side blocks 5 and 6.
a and from between 4b and 6a, the compression chamber 1
Inlet port 5 where the pressure difference between the inside and outside of 0 and 11 is maximum
It is easy to enter the compression chambers 10 and 11 from the vicinity of b and 5c, that is, from the range indicated by arrows B and B' in FIG.

The high-pressure refrigerant gas that has entered the suction side of the compression chambers 10 and 11 from the range indicated by these arrows B and B' is
During the intrusion, grooves 4f, 4f' and 4g, 4
It will cross g'. However, when the high-pressure refrigerant gas passes through each of these grooves 4f, 4f', 4g, 4g',
It expands in g′, dissipates its energy, and its pressure decreases. That is, the pressure of the high-pressure refrigerant gas that has entered the vicinity of the suction ports 5b and 5c decreases due to the labyrinth effect. As a result, these inlets 5b, 5
The pressure difference between the inside and outside of the compression chambers 10, 11 near c becomes smaller, making it difficult for high-pressure refrigerant gas to leak from the discharge chamber 15 into the compression chambers 10, 11. Therefore, the sealing properties near the suction ports 5b and 5c of the compression chambers 10 and 11 are substantially improved, and the air flow from the discharge chamber 15 to the compression chamber 1 is substantially improved.
Refrigerant gas is prevented from entering into the interiors of 0 and 11.

In the above embodiment, the grooves 4f, 4f', 4g, 4g' are formed on both end surfaces 4a, 4b of the cam ring 4, respectively. A groove may be formed on each end surface 5a, 6a of the cam ring 4, or a groove may be formed on both end surfaces 4a, 4b of the cam ring 4 and each end surface 5a, 6a of both side blocks 5, 6, respectively.

Further, in the above embodiment, each suction port 5b,
Although a case has been described in which one groove is formed on each outer side of the groove 5c, the present invention is not limited to this, and a plurality of grooves may be formed concentrically.

(Effects of the invention) As explained above, the vane type compressor of the invention is located on at least one of the end faces of the cam ring and the contact faces of both side blocks that contact these end faces, and on the pump body. A groove is provided at a location where there is a large pressure difference between the inside and outside, substantially along the compression chamber, and located outside the suction port and along the circumferential direction of the suction port,
The high-pressure gas that attempts to enter the compression chamber from the discharge chamber is expanded in the groove to dissipate its energy and reduce the pressure, so that the high-pressure gas does not leak into the compression chamber. , the sealing performance of the portions of the pump body where there is a large pressure difference between the inside and outside is substantially improved, and the compression performance of the compressor is accordingly improved. In addition, the structure is extremely simple, as it is only necessary to form grooves at locations where the pressure difference is large, and the cost does not increase.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of a conventional vane type compressor, Fig. 2 is a sectional view taken along the - line in Fig. 1, and Fig. 3 is a longitudinal sectional view of a vane type compressor showing an embodiment of the present invention. , FIG. 4 is a sectional view taken along the - line in FIG. 3. 4...Cam ring, 4a...One end surface, 4b...
Other end surface, 4c...inner peripheral surface, 4f, 4f', 4g, 4
g'...Groove, 5...Front side block, 5a
...One end surface of the front side block, 5b, 5
c...Intake port, 6...Rear side block, 6a
... One end surface of rear side block, 8 ... Rotor, 8b ... Vane groove, 9 ... Vane, 10, 1
1 compression chamber, 14... pump body, 15... discharge chamber.

Claims (1)

[Scope of utility model registration request] The vane is slidably fitted into the vane groove of the rotor rotatably housed in the pump body, which is made up of a cam ring that has a cam surface on its inner circumferential surface and is open at both ends, with side blocks attached to each end surface. death,
The centrifugal force of the vane as the rotor rotates causes the vane to slide into contact with the inner circumferential surface of the cam ring, and as the rotor rotates, the inner circumferential surface of the cam ring, the outer circumferential surface of the rotor, and the vane form a defined area. In the vane type compressor, a compression chamber is expanded or contracted to suck in and compress gas, and the compressed gas is discharged into a discharge chamber defined outside the pump body. The pump body is located on at least one of both end faces and the abutment faces of the side blocks that come into contact with these end faces, and is located at a location where there is a large pressure difference between the inside and outside of the pump body, and is located approximately along the compression chamber and of the suction port. A vane type compressor characterized by having a groove located on the outside and extending along the circumferential direction of the suction port.