KR20010022024A - Reciprocating compressor - Google Patents

Abstract

The stopper valve plates 29 and 30 are composed of stopper portions 29a and 30a and fixing portions 29e and 30e, and are provided between the stopper members 29a and 30a and the fixing portions 29e and 30e. The jaw portions 29f and 30f are formed in the jaw portions, and the jaw portions 29f and 30f are used as the lift points of the discharge valve portions 29a and 28a.

Description

Reciprocating Compressor {RECIPROCATING COMPRESSOR}

FIG. 5 is a partial cross-sectional view of a valve plate, a valve seat, and a stopper plate of a conventional swash plate compressor.

The valve plate 103 is provided with a discharge port 103a for discharging the refrigerant gas of the compression chamber to the discharge chamber.

The valve seat 127 is provided with a flat discharge valve 127a for opening and closing the discharge port 103a.

The stopper plate 129 is provided with a stopper portion 129a for suppressing the opening amount of the discharge valve portion 127a and communicates with the discharge port 103a and the compression chamber when the discharge valve portion 127a is opened. Discharge holes (not shown) are formed.

The valve plate 103, the valve sheet 127, and the stopper plate 129 overlap each other and are disposed between the cylinder block and the cylinder head (not shown). The compression chamber is formed in the cylinder block, and the discharge chamber is formed in the cylinder head.

When the discharge valve 127a is opened as indicated by the dashed-dotted line in Fig. 5, the compression chamber and the discharge chamber communicate with each other through the discharge port 103a and the discharge hole, and a high-pressure refrigerant gas flows from the compression chamber to the discharge chamber.

The stopper portion 129a is formed in a shape having a predetermined angle or curvature with respect to the valve seat side end surface 129c of the fixing portion 129b.

Since the flow of the refrigerant gas is concentrated near the top of the discharge valve 127a rather than near the boundary between the discharge valve portion 127a and the valve body 127b, the impact force at the seat of the discharge valve 127a is greatly increased. do.

As a result, there was a problem that a large impact sound was generated when the discharge valve portion moved and seated as indicated by the arrow a from the position indicated by the dashed-dotted line in Fig. 5. In particular, the valve seat 127 is broken during high speed operation, and durability is reduced.

Further, when the discharge valve portion 127a is opened, the open angle near the bottom of the discharge valve portion 127a is small, so that the refrigerant gas is difficult to flow and there is a problem of overcompression.

In addition, in order to ensure the airtightness of the valve seat 127 and the stopper plate 129, the contact surface of the stopper plate 129 and the valve seat 127 is polished.

However, since the radius of curvature of the stopper portion 129a is increased, when the thickness of the stopper plate 129 changes due to polishing, there is a possibility that the point of the valve seat 127 is greatly shifted.

As a result, the amount of plate opening of the discharge valve changes for each cylinder, so that the flow of refrigerant gas changes, causing compression disturbance and large pulsation.

The present invention has been made in view of the above circumstances, and therefore, an object of the present invention is to provide a reciprocating compressor having a low power consumption, excellent durability, and small pulsation.

The present invention relates to a reciprocating compressor such as a swash plate compressor and a rocking plate compressor.

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

Fig. 1 (a) shows the state when the valve is opened, and Fig. 1 (b) shows the state when the valve is closed.

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

3 is an exploded perspective view showing the valve plate, the valve sheet and the stopper plate.

Fig. 4A is a plan view of a part of the stopper plate when the valve plate, valve seat and stopper plate are overlapped, and Fig. 4B is a sectional view taken along the line 4B-4B in Fig. 4A.

5 is a partial cross-sectional view of a valve plate, a valve sheet, and a stopper plate of a conventional swash plate type compressor.

In order to solve the above problems, the reciprocating compressor of the present invention is disposed between a cylinder block having a plurality of cylinders and a cylinder head, and a compression chamber located on the cylinder block side and a high pressure chamber located on the cylinder head side; A valve plate for dividing the low pressure chamber, a valve port formed in the valve plate, for discharging the refrigerant gas of the compression chamber to the high pressure chamber, a valve body fixed to the valve plate, and a valve part for opening and closing the discharge port. A reciprocating compressor comprising a stopper member having a valve member, a stopper portion for suppressing an opening amount of the valve portion, and a fixing portion fixed to the valve plate through the valve body,

A jaw portion is formed between the stopper portion and the fixing portion.

Since the jaw portion is formed between the stopper portion and the fixed portion, the position of the point at the time of the lift of the valve portion becomes constant, and the lift amount of each valve portion becomes uniform, thereby eliminating the compression disturbance and reducing the pulsation. Moreover, since the opening size of the valve part near the point at the time of a lift increases, and the flow of refrigerant gas becomes favorable, overcompression is prevented and consumption power is reduced.

In addition, since the refrigerant gas does not concentrate on the top portion of the valve portion and the impact force applied to the valve portion when the discharge valve is closed is alleviated, noise is reduced and durability of the discharge valve is improved.

The reciprocating compressor of the present invention is characterized in that the jaw side edge portion of the fixed portion, which is a point when the valve portion is opened, is curved.

When the valve part is opened, the valve part is supported by the surface, and the force acting on the valve part is distributed, thereby improving durability of the valve member.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described based on drawing.

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

The cylinder block 1 on the front side and the cylinder block 2 on the rear side are opposed to each other in the axial direction. The front head 4 is fixed to one end of the joined cylinder block 1, 2 through a valve plate 3, a valve seat (valve member) 27 and a stopper plate (stopper member) 29, and the other end. The rear head 6 is fixed through the valve plate 5, the valve sheet (valve member) 28, and the stopper plate (stopper member) 30.

The front shell 4 is provided with the front shell 13 and the rear head 6 is integrally provided with the rear shell 14, so that the front shell 13 and the rear shell 14 are The O rings 38 are fitted together in the axial direction.

The front head 4, the cylinder blocks 1, 2, the shells 13, 14 and the rear head 6 are axially coupled to the through bolts 39.

The drive shaft 7 is disposed at the center of the cylinder block 1, 2, and the swash plate 8 is fixed to the drive shaft 7, and the drive shaft 7 and the swash plate 8 are bearings 9, 10. It is rotatably supported by. The swash plate 8 is inclined with respect to the imaginary surface orthogonal to the drive shaft 7.

The cylinder blocks 1 and 2 are provided with a plurality of cylinders 11. Each cylinder 11 is parallel to the drive shaft 7 and is arrange | positioned at predetermined intervals in the circumferential direction centering on the drive shaft 7. In each cylinder 11, the piston 12 is accommodated so that sliding is possible.

Compression chambers 21 and 22 are formed on both sides of the piston 12 in each cylinder 11. The piston 12 is connected to the swash plate through a giant hemispherical shoe 19, 20, and the piston 12 reciprocates in the cylinder 11 in accordance with the rotation of the swash plate 8.

3 is an exploded perspective view showing a valve plate, a valve seat and a stopper plate;

4 (a) is a plan view of a portion of the stopper plate when the valve plate, valve seat and stopper plate are overlapped;

(B) is sectional drawing along the 4B-4B line | wire of (a),

1: is sectional drawing along the 1A-1A line | wire of FIG.

1 (a) shows the state when the valve is opened,

Fig. 1 (b) is a diagram showing a state when the valve is closed, respectively.

At the time of suctioning the discharge ports 3a and 5a, the valve plates 3 and 5 having a substantially disk shape are discharged to discharge the refrigerant gas from the compression chambers 21 and 22 into the discharge chamber (high pressure chamber) 24. Bolt through-holes 3c and 5c for inserting suction valve release holes 3b and 5b and through-bolt 39 for releasing the valve portions 27d and 28d to the compression chamber 21 and 22 side. These are formed, respectively.

When the suction valve release holes 3b and 5b are adjacent to the suction ports 29d and 30d through the suction valve portions 27d and 28d, and the suction valve portions 27d and 28d open at the time of suction. Is communicated with the suction ports 29d and 30d.

In the substantially disk-shaped valve seats 27 and 28, flat discharge valves (valve parts) 27a and 28a and flat suction valve parts 27d and 28d are respectively grooved. At the same time, bolt through holes 27c and 28c are formed.

The stopper plates 29 and 30 having a substantially disc shape have a refrigerant gas in the suction chamber (low pressure chamber) 23 for suppressing the amount of opening or deformation of the discharge valve portions 27a and 28a. Suction ports 29d and 30d and bolt through-holes 29c and 30c for suctioning the pressure into the compression chambers 21 and 22 are formed, respectively.

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

As shown in FIG. 1, the stopper portions 29a and 30a are formed with grooves formed in the side surfaces of the compression chambers of the stopper plates 29 and 30, and the stopper portions 29a and 30a and the fixing portion 29e. The jaw portions 29f and 30f are formed between the 30e. The jaw side edge portion P of the fixing portions 29e and 30e of the stopper plates 29 and 30, which becomes the point of the discharge valve portions 27a and 28a at the time of lift, is curved.

When the valve plates 3, 5, the valve sheets 27, 28, and the stopper plates 29, 30 overlap, the discharge ports 3a, 5a and the discharge valve portions 27a, 28a face each other. And the compression chambers 21 and 22 through the discharge ports 3a and 5a of the valve plates 3 and 5 and through the discharge holes 29b and 30b of the stopper plates 29 and 30, respectively. The discharge chamber 24 communicates.

Also, the valve bodies 27e and 28e connected to the discharge valves 27a and 28a are formed by the fixing portions 29e and 30e and the valve plates 3 and 5 of the stopper plates 29 and 30, respectively. It is fixed.

Next, the operation of the swash plate compressor of the present embodiment will be described.

When the drive shaft 7 rotates, the swash plate 8 also rotates integrally. The piston 12 reciprocates in the cylinder 11 by the rotation of the swash plate 8. From the position where the piston 12 is closest to the valve plate 3 (when the piston 12 is located at the top dead center on the compression chamber 21 side), when the swash plate 8 rotates 1/2, the piston 12 is moved to the valve plate ( 5), the suction stroke is completed on the compression chamber 21 side, and the compression stroke and discharge stroke are terminated on the compression chamber 22. As shown in FIG. In this state, when the swash plate 8 rotates again 1/2, the suction stroke is completed in the compression chamber 22, and the compression stroke and the discharge stroke are finished on the compression chamber 21 side.

In the suction stroke, the suction valves 27d and 28d elastically deform to the suction valve release holes 3b and 5b, and are provided through the suction ports 29d and 30d and the suction valve release holes 3b and 5b. A low pressure refrigerant gas flows into the compression chambers 21 and 22.

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

By the tuck portions 29f and 30f, the position of the point at which each of the discharge valve portions 27a and 28a lifts becomes constant, and the lift amount of each of the discharge valve portions 27a and 28a becomes uniform so that There is no disturbance, and the pulsation caused by the disturbance of compression is reduced.

When the valves of the discharge valve portions 27a and 28a are opened, the jaw portions 27f and 28f are located near the points of the discharge valve portions 27a and 28a by the discharge pressure of the refrigerant gas (Fig. 1 (a)). ), The valve opening of the discharge valve portions 27a and 28a increases, and the flow of the refrigerant gas becomes good, so that overcompression is prevented and consumption power is reduced.

In addition, the flow of the refrigerant gas is not concentrated at the top of the discharge valve portions 27a and 28a, and the impact force applied to the discharge valve portions 27a and 28a when the discharge valve portions 27a and 28a is closed. Since this is alleviated, noise is reduced and durability of the discharge valve parts 27a and 28a is improved.

Moreover, when the discharge valve parts 27a and 28a are opened, the discharge valve parts 27a and 28a are curved surfaces of the jaw side edge portions P of the fixing parts 29e and 30e of the stopper plates 29 and 30. And the force acting on the discharge valve portions 27a and 28a does not concentrate on one place, so the durability of the discharge valve portions 27a and 28a is improved.

Moreover, in the said embodiment, although this invention was applied to the swash plate type compressor with a shell, it can also apply to the thing of a structure without a shell.

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

Claims (2)

A valve plate disposed between the cylinder block having a plurality of cylinders and the cylinder head, wherein the valve plate separates the compression chamber located on the cylinder block side and the high pressure chamber and the low pressure chamber located on the cylinder head side; A discharge port formed in the valve plate and configured to discharge refrigerant gas of the compression chamber to the high pressure chamber; A valve member fixed to the valve plate and having a valve portion for opening and closing the valve body and the discharge port; In the reciprocating compressor having a stopper portion for suppressing the opening amount of the valve portion and a stopper member having a fixed portion fixed to the valve plate through the valve body, A reciprocating compressor, characterized in that the jaw portion is formed between the stopper portion and the fixed portion. The reciprocating compressor according to claim 1, wherein the jaw side edge portion of the fixing portion, which is a point when the valve portion is opened, is curved.