WO1999030036A1

WO1999030036A1 - Reciprocating compressor

Info

Publication number: WO1999030036A1
Application number: PCT/JP1998/005482
Authority: WO
Inventors: Makoto Tabata; Kiyoshi Yoshii; Katsutoshi Enomoto; Katsuhiko Arai
Original assignee: Zexel Corporation
Priority date: 1997-12-05
Filing date: 1998-12-04
Publication date: 1999-06-17
Also published as: JPH11173269A

Abstract

A reciprocating compressor, wherein a discharge valve (27a, 28a) is positioned halfway between a stopper plate (29, 30) and a valve plate (3, 5) when the compressor is stopped, the amount of movement of the discharge valve (27a, 28a) becoming small when it is opened and closed, whereby an impact occurring when the discharge valve (27a, 28a) is seated on the valve plate (3, 5) is cushioned.

Description

Description Reciprocating compressor Technical field

The present invention relates to a reciprocating compressor such as a swash plate compressor and an oscillating plate compressor. Background art

A conventional swash plate type compressor is disposed between a cylinder block and a cylinder head, and a valve plate that separates a compression chamber from a discharge chamber and a suction chamber, and discharges refrigerant gas from the compression chamber. A discharge port for discharging into the chamber, a suction port for drawing refrigerant gas from the suction chamber into the compression chamber, a discharge valve for opening and closing the discharge port, and a suction valve for opening and closing the suction port. And a stopper for suppressing the opening amount of the discharge valve.

FIG. 5 is a partial cross-sectional view of a conventional swash plate compressor in which a valve plate, a valve sheet, and a top plate are stacked.

A discharge port 103 a is formed in the knob plate 103.

The valve sheet 127 has a discharge valve 127a opposed to the discharge port 103a.

The stop plate 1229 is provided with a stop 1229a corresponding to the discharge valve 127a.

If the displacement of the discharge valve 1 2 7a during opening and closing is large, Since the discharge valve 1 27a moves from the position shown by the two-dot chain line as shown by the arrow in FIG. There was a problem that not only would occur, but the discharge valve 127a would be damaged during high-speed operation.

The present invention has been made in view of such circumstances, and an object thereof is to provide a reciprocating compressor having excellent discharge valve durability and low noise. Disclosure of the invention

In order to solve the above-mentioned problems, a reciprocating compressor according to the present invention is provided between a cylinder block and a cylinder head to partition a compression chamber from a high-pressure chamber and a low-pressure chamber. A discharge port for discharging the refrigerant gas from the compression chamber to the high-pressure chamber; a suction port for drawing the refrigerant gas from the low-pressure chamber into the compression chamber; and a discharge port for opening and closing the discharge port. A reciprocating compressor comprising: a discharge valve; a suction valve for opening and closing the suction port; and a stopper for suppressing an opening amount of the discharge valve. It is characterized in that it is located between the stopper and the valve plate.

When the compressor is stopped, the discharge valve is located between the stop and the valve plate.Therefore, when the discharge valve is opened and closed, the displacement of the discharge valve decreases, and the discharge valve valve The impact at the time of sitting on the vehicle is reduced. As a result, the impact sound is suppressed, and the discharge valve can be prevented from being damaged, and the durability is improved. improves.

In the reciprocating compressor according to the present invention, the stop and the suction port are formed on the same plate, and the tip of the suction valve is separated from the plate when the compressor stops operating. It is characterized by

When the compressor is stopped, the tip of the suction valve is away from the stove, so the suction valve opens quickly, refrigerant gas flows from the compression chamber into the suction chamber, and after the compression stroke, the suction The backflow of the refrigerant gas generated in the discharge valve at the time of entering the stroke is canceled, and the performance is prevented from deteriorating. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a cross-sectional view taken along the line 1A-1A in FIG. 4 (a).

FIG. 2 is a longitudinal sectional view of the swash plate compressor according to one embodiment of the present invention.

FIG. 3 is an exploded perspective view showing a valve plate, a valve sheet, and a top plate.

Fig. 4 (a) is a plan view of a part of the stop plate when the valve plate, valve sheet and stop plate are stacked, and Fig. 4 (b) is Fig. 4 (b). It is sectional drawing which follows the 4B-4B line of (a).

FIG. 5 is a cross-sectional view of a conventional swash plate type compressor in which a valve plate, a valve sheet, and a top plate are stacked. BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings.

The front-side cylinder block 1 and the rear-side cylinder block 2 are axially opposed to each other. One end of the joined cylinder blocks 1 and 2 is connected to the front head 4 via a valve plate 3, a valve sheet 27 and a stop plate (plate) 29. Is fixed, and the other end is fixed to a rear head 6 via a valve plate 5, a valve sheet 28 and a stop plate (plate) 30.

A front shell 13 is provided integrally with the front head 4 and a rear shell 14 is provided integrally with the rear head 6, and the front shell 13 and the rear shell 13 are provided integrally. The shell 14 is fitted in the axial direction via the O-ring 38. The front head 4, the cylinder blocks 1 and 2, the shells 13 and 14, and the rear head 6 pass through and are axially connected by a port 39.

A drive shaft 7 is disposed at the center of the cylinder blocks 1 and 2, and a swash plate 8 is fixed to the drive shaft 7. The drive shaft 7 and the swash plate 8 are bearings 9 and 1. It is rotatably supported by 0. The swash plate 8 tilts and lays on an imaginary plane orthogonal to the drive shaft 7.

Each of the cylinder blocks 1 and 2 is provided with a plurality of cylinder pores 11. Each of the cylinder pores 11 is parallel to the drive shaft 7 and has a predetermined interval in a circumferential direction around the drive shaft 7. It is arranged every other. A piston 12 is slidably accommodated in each cylinder bore 11.

Compression chambers 21 and 22 are formed on both sides of the piston 12 in each cylinder pore 11. The piston 12 is connected to the swash plate through a substantially hemispherical shroud 19, 20, and the piston 12 is provided in the cylinder bore 11 as the swash plate 8 rotates. Reciprocate.

Fig. 3 is an exploded perspective view showing a valve plate, a valve sheet and a stop plate, and Fig. 4 (a) shows a valve plate, a valve sheet and a stop plate. Fig. 4 (b) is a cross-sectional view taken along line 4B-4B of Fig. 4 (a), and Fig. 1 is a cross-sectional view of a part of the top plate when stacked. FIG. 2 is a cross-sectional view taken along line 1 A-1 A of a).

The substantially disk-shaped valve plates 3 and 5 have compression chambers 21 and

Discharge ports 3a and 5a for discharging the refrigerant gas of 22 to the discharge chamber (high-pressure chamber) 24, and the suction valves 27d and 28d are released to the compression chambers 21 and 22 during suction. Suction valve escape holes 3b, 5b and port through holes for inserting through port 39

3 c and 5 c are formed respectively.

The suction valve relief holes 3b and 5b are adjacent to the suction ports 29d and 30d via the suction valves 27d and 28d, respectively, and the suction valves 27d and 28d When opened, it communicates with suction ports 29d and 30d.

Tongue-shaped discharge valves 27a, 28a and tongue-shaped suction valves 27d, 28d are formed in the substantially disk-shaped valve sheets 27, 28, respectively. With the bolt through hole 27 c and 28 c are formed.

As shown in Fig. 1, when the compressor is stopped, the discharge valves 27a and 28a are connected to the stoppers 29a and 30a and the noble plate.

It is located between 3, 5 and.

The substantially disk-shaped toe plate 29, 30 has a groove-shaped toe plate 29a, 30 that suppresses the opening or deformation of the discharge valves 27a, 28a. a, suction ports 29 d and 30 d for allowing the refrigerant gas in the suction chamber (low-pressure chamber) 23 to be sucked into the compression chambers 21 and 22, and port through holes 29 c and 30 c are provided. Each is formed.

In the stop plates 29 and 30, discharge holes 29b and 30b are formed along the longitudinal direction of the stop holes 29a and 30a.

When the nozzle plates 3, 5 and the valve sheets 27, 28 and the top plate 29, 30 are overlapped, the discharge valves 27a, 2a are placed on the discharge ports 3a, 5a. 8a are opposed to each other via the discharge ports 3a and 5a of the valve plates 3 and 5 and the discharge holes 29b and 30b of the stopper \ ° plates 29 and 30. The compression chambers 2 1 and 2 2 communicate with the discharge chamber 24.

Next, the operation of the swash plate type compressor of this embodiment will be described. When the drive shaft 7 rotates, the swash plate 8 also rotates integrally. The rotation of the swash plate 8 causes the piston 12 to reciprocate in the cylinder pore 11. When the swash plate 8 rotates 1 Z 2 from the position where piston 12 is closest to the valve plate 3 (when piston 12 is located at the top dead center on the compression chamber 21 side). The piston 12 moves to the valve plate 5 side, and the compression chamber 21 side moves. In, the suction stroke is completed, and in the compression chamber 22, the compression stroke and the discharge stroke are completed. When the swash plate 8 further rotates 1 Z 2 from this state, the suction stroke is completed in the compression chamber 22, and the compression stroke and the discharge stroke are completed in the compression chamber 21.

In the suction stroke, the suction valves 27 d and 28 d serve as suction valve escape holes.

It is elastically deformed to the 3b, 5 side, and low-pressure refrigerant gas flows into the compression chambers 21, 22 through the suction ports 29d, 30d and the suction valve relief holes 3b, 5b.

In the discharge stroke, the discharge valves 27a and 28a are elastically deformed toward the discharge chamber by the refrigerant gas compressed in the compression chambers 21 and 22 and the discharge ports 3a and 5a and the discharge ports are discharged. High-pressure refrigerant gas is discharged from the compression chambers 21 and 22 to the discharge chamber 24 through the holes 29b and 30b.

Since the discharge valves 27a and 28a are located between the stoppers 29a and 30a and the valve plates 3 and 5, the discharge valves 27a and 28a are opened and closed. The movement amount of 28a is small, and the shock when the discharge valves 27a, 28a are seated on the knob plates 3, 5 is reduced. As a result, noise is reduced, and the discharge valves 27a and 28a can be prevented from being damaged, and durability is improved.

As a result, the impact noise is suppressed, and the discharge valves 27a and 28a are hardly damaged during high-speed operation, and the discharge valves 27a and 28a (valve sheet 2 The durability of 7, 28) is improved.

Also, the discharge valves 27a and 28a are pulled toward the valve plates 3 and 5 during the refrigerant gas suction stroke, so that the compression The valve will open promptly.

As a result, the high-pressure refrigerant gas quickly flows from the compression chambers 21 and 22 to the discharge chamber 24, suppressing overcompression of the refrigerant gas and reducing power consumption.

In the above embodiment, the discharge valves 27a and 28a are arranged in the middle between the stoppers 29a and 30a and the discharge ports 3a and 5a. At the beginning, before the discharge valves 27a and 28a close, the high-pressure refrigerant gas flows back into the compression chambers 21 and 22 and the performance may be reduced.

To solve this problem, the tip of the suction valve 27d, 28d in the assembled state should be bent so as to be away from the top plate 29, 30. With this configuration, the high-pressure refrigerant gas flowing backward from the discharge chamber 24 to the compression chambers 21 and 22 flows out to the suction chamber 23, and the suction valves 27d and 28d are quickly discharged. Since the valve opens very well, performance degradation can be suppressed.

In the above embodiment, the invention of the present application is applied to a swash plate compressor with a shell. However, the invention can be applied to a compressor without a shell. Industrial applicability

As described above, the reciprocating compressor according to the present invention is useful as a refrigerant compressor for an air conditioner for a vehicle.

Claims

The scope of the claims

1. A valve plate that is arranged between the cylinder block and the cylinder head and separates the compression chamber from the high-pressure chamber and the low-pressure chamber;

A discharge port for discharging the refrigerant gas from the compression chamber to the high-pressure chamber;

A suction port for sucking the refrigerant gas in the low-pressure chamber into the compression chamber;

A discharge valve for opening and closing the discharge port;

A suction valve for opening and closing the suction port;

A reciprocating compressor comprising: a stove that suppresses an opening amount of the discharge valve;

The reciprocating compressor, wherein the discharge valve is located at an intermediate position between the stop and the valve plate when the operation of the compressor is stopped.

2. The stop and the suction port are formed in the same plate, and the tip of the suction valve is separated from the plate when the compressor operation is stopped. The reciprocating compressor according to claim 1, wherein: