JPH11117868A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently reduce mechanical noise generated in a coolant flowing port in a compressor, and to prevent occurrence of inferior operation during low load and high speed operation. SOLUTION: In a compressor, a valve plate 19 partitioning coolant flowing ports 17, 18 from a compression chamber 15 is formed therein with coolant openings 20, 21 for communicating the coolant flowing ports 17, 18 with the compression chamber 15, and control valves 22, 23 are attached to the valve plate 19, having proximal end parts 22a, 23a fixed to the valve plate 19 and distal end parts 22b, 23b resiliently abutting against the coolant openings 20, 21 which are therefore openable and closable. Annular grooves 26, 27 are formed in the valve plate 19, around the coolant openings 20, 21. With this arrangement, the diametrical width of a seal surface is set to be at least 0.6 mm but at most 0.9 mm.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor for use in, for example, a cooling cycle for an automobile, and more particularly to a compressor which reduces noise at a suction port and a discharge port and does not cause a malfunction.

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 8, a variable displacement swash plate type compressor 50 used in an air conditioner for a vehicle has a compression chamber 15 for compressing a refrigerant and a suction port 17 for the refrigerant.
And a discharge port 18 (hereinafter, generally referred to as a refrigerant flow port) is partitioned by a valve plate 19, and the valve plate 19 has an inlet 20 communicating the compression chamber 15 with the ports 17, 18. And a discharge port 21 (hereinafter, generally referred to as a refrigerant opening).

The suction port 20 is provided with a long plate-shaped suction valve 22 which is elastically abutted and opens and closes on the compression chamber 15 side of the valve plate 19. A plate-shaped discharge valve 23 is provided on the discharge port 18 side of the valve plate 19.

As shown in FIG. 8, annular grooves 26 and 27 are formed around the suction port 20 and the discharge port 21, respectively.
Seal surfaces 28, 2 with which a suction valve 22 and a discharge valve 23 (hereinafter, collectively referred to as a control valve) abut between the discharge valve 21 and the discharge port 21.
9 are formed.

The annular grooves 26 and 27 suppress the impact force when the suction valve 22 or the discharge valve 23 comes into contact with the sealing surfaces 28 and 29 at the time of suction or discharge of the refrigerant.
This protects the suction valve 22 or the discharge valve 23 from damage (for example, see Japanese Utility Model Application Laid-Open No. Sho 62-156181, Japanese Utility Model Application Laid-Open No. 63-113779).

[0006]

By the way, in the conventional compressor 50 described above, the sealing surface 2 formed in the space between the annular grooves 26, 27 and the refrigerant openings 20, 21 is provided.
The widths of 8, 29 are relatively wide, generally about 1.2 to 1.3 mm.

However, especially when the width of the seal surface 28 is about 1.2 to 1.3 mm on the suction port 20 side, when the suction valve 22 is changed from the closed state to the open state, the suction valve 22 is not closed. It sticks to the seal surface 28, and the opening timing of the suction valve 22 is delayed. For this reason, the refrigerant flows into the suction port 20 at a stretch, causing pressure fluctuation of the refrigerant. Therefore, there has been a problem that the suction pressure pulsation of the refrigerant increases and the sound vibration level increases.

When the compressor 50 is operated at low load and high speed, the opening timing of the suction valve 22 is delayed, and
There is a possibility that the suction valve 22 does not open due to the start of the discharge process before the valve opens. For this reason, in a compressor in which the pressure in the crank chamber is controlled by the pressure of the discharged refrigerant and the swash plate angle is changed to change the capacity of the discharged refrigerant, the swash plate is stretched to the minimum destroke which is the most standing state with respect to the shaft. Will stick
There is a problem that the function of the compressor 50 is not fulfilled.

Further, when the width of the seal surface 28 is large, there is a problem that the tapping sound when the suction valve 22 comes into contact with the seal surface 28 becomes loud and noise is generated.

The present invention has been proposed in view of the above-mentioned problems of the prior art. The present invention sufficiently reduces mechanical noise generated at a refrigerant circulation port of a compressor and operates even at low load and high speed operation. The purpose is to prevent defects.

[0011]

According to the present invention, in order to achieve the above object, a valve plate for partitioning a refrigerant flow port and a compression chamber is provided with a refrigerant opening for communicating the two,
A control valve having a base end fixed to the valve plate and a front end elastically abutting on the refrigerant opening so as to be openable and closable is attached, and an annular groove is formed around the refrigerant opening of the valve plate. And a radial width of a seal surface of the valve plate with which the suction-side control valve abuts is set to 0.6 mm or more and 0.9 mm or less.

In the present invention, the radial width of the seal surface of the valve plate with which the suction-side control valve comes into contact is smaller than that of the conventional compressor. For this reason, the occurrence of tapping noise when the suction side control valve abuts on the valve plate can be reduced, and the pressure fluctuation of the refrigerant due to the vibration of the suction side control valve can be reduced. Even at the time, no malfunction occurs.

[0013]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a sectional view of a variable displacement swash plate compressor according to an embodiment of the present invention, FIG. 2 is an enlarged sectional view of a main part of FIG. 1, and FIG. 3 is a valve plate shown in FIG. FIG. 4 is an enlarged view of the sealing surface of the valve plate shown in FIG.

As shown in FIG. 1, a variable displacement swash plate type compressor 1 according to the present embodiment has a drive shaft 3 which is rotationally driven by an engine via a belt, a pulley 2, and a magnet clutch 2a. This drive shaft 3 has
A drive rod 3 a is provided projecting in a direction perpendicular to the drive shaft 3, and rotates together with the drive shaft 3 in the crank chamber 4.

A drive swash plate 5 is connected to the drive rod 3a so as to be tiltable and swingable with respect to the drive shaft 3 with a pin 3b as a swing fulcrum. Therefore, the rotational force of the drive shaft 3 is transmitted to the drive swash plate 5 via the drive rod 3a and the pin 3b. A non-rotating wobble plate 8 is slidably attached to the drive swash plate 5 via a thrust bearing 6 and a radial bearing 7.

The wobble plate 8 has a shoe 11 slidably connected to a guide pin 10 fixed to a casing 9 of the crank chamber 4. The shoe 11 prevents rotation while the shoe 11 prevents rotation. Reciprocation in the direction is allowed. A plurality of piston rods 12 are attached to the wobble plate 8 at equal intervals in a circumferential direction via a spherical bearing 12a. A piston 13 is connected to the other end of the piston rod 12 via a spherical bearing 12b. Are linked.

Therefore, when the driving swash plate 5 rotates, the wobble plate 8 reciprocates in the axial direction by performing a so-called miso-sliding operation, whereby the piston 13 reciprocates via the piston rod 12. Further, the front side portion of the piston 13 of the cylinder 14 in which the piston 13 is inserted serves as a compression chamber 15, and the rear side portion communicates with the crank chamber 4.

The cylinder head 16 has a suction port 17 into which return refrigerant from an evaporator (not shown) flows,
A discharge port 18 for discharging the compressed refrigerant to a condenser (not shown) is provided. The suction port 17 and the discharge port 18 function as refrigerant circulation ports.

Between the suction port 17 and the discharge port 18 and the compression chamber 15, a valve plate 19 for dividing the suction port 17 and the discharge port 18 from the compression chamber 15 is provided. This valve plate 19 has a suction port 1
A suction port 20 communicating the compression chamber 7 with the compression chamber 15 and a discharge port 21 communicating the discharge port 18 with the compression chamber 15 are formed. The suction port 20 and the discharge port 21 function as a refrigerant opening.

FIG. 3 is a view of the above-described valve plate 19 viewed from the cylinder 14 side. The suction port 20 and the discharge port 21 are arranged at a constant interval in the circumferential direction. The number of the suction ports 20 and the number of the discharge ports 21 correspond to the number of the compression chambers 15, and are provided, for example, five each.

The valve plate 19 is provided with a long plate-shaped suction valve 22 or discharge valve 23 for opening and closing the suction port 20 or the discharge port 21 facing the suction port 20 or the discharge port 21 described above. . The suction valve 22 and the discharge valve 23 function as a control valve.

The suction valve 22 or the base end 22a of the discharge valve 23 is provided with a retainer 2 for holding the discharge valve 23.
Rivets 25 on the valve plate 19 together with the base end of
And the like. Also, the suction valve 22
Alternatively, the discharge valve 23 is made of a leaf spring material, and the distal end portion 22 of each of the suction valve 22 and the discharge valve 23.
The b and 23b are elastically in contact with the periphery of the suction port 20 or the discharge port 21 in an openable and closable manner. Although not shown, the suction valve 22 or the discharge valve 23 is formed, for example, in a starfish type, that is, in a shape extending radially in five directions.

Accordingly, when the refrigerant is sucked by the piston 13, the suction valve 22 is bent as shown by the solid line in FIG. 2 to open the suction port 20, and the refrigerant is introduced from the suction port 17 into the compression chamber 15. At this time, the discharge valve 23 is in a closed state as shown by a virtual line in FIG. On the other hand, when the refrigerant is discharged, the discharge valve 23 curves as shown by a solid line in FIG. 2 to open the discharge port 21, and discharges the compressed refrigerant from the compression chamber 15 to the discharge port 18. At this time, the suction valve 22 is in a closed state as shown by a virtual line in FIG.

As shown in FIG. 3, the above-described valve plate 19 is provided around the suction port 20 or the discharge port 21.
Annular grooves 26 and 27 are formed respectively, and
0 or between the discharge port 21 and the annular grooves 26 and 27,
Annular sealing surfaces 28 and 29 with which the suction valve 22 or the discharge valve 23 contacts are formed.

The seal surface 28 on the suction port 20 side is
As shown in FIG. 4, the radial width L is formed to be 0.6 mm or more and 0.9 mm or less.

The reason why the width of the seal surface 28 on the suction port 20 side is set to be 0.6 mm or more and 0.9 mm or less as described above is shown in FIG.
This will be described with reference to FIG.

FIG. 5 is an explanatory view showing a temporal change of the cylinder internal pressure when the width of the seal surface 28 is changed. FIG. 6 is a diagram showing the width of the seal surface 28, the cylinder internal pressure immediately before the valve is opened, and the suction pressure. FIG. 7 is a diagram illustrating the relationship between the pressure difference and
It is explanatory drawing which showed the relationship between the width | variety of 8 and a pressure pulsation level.

As shown in FIG. 5, when the width of the sealing surface 28 is narrow (indicated by a dashed line in the figure) when the piston 13 moves to the bottom dead center after passing through the top dead center, 28
Is wider (shown by a solid line in the figure).
When the width of the seal surface 28 is smaller, the valve opening delay of the suction valve 22 is smaller. Therefore, when the width of the seal surface 28 is small, the pressure difference between the cylinder internal pressure and the suction pressure immediately before the valve opens due to the valve opening delay becomes smaller. For this reason, the pressure pulsation of the refrigerant is reduced, and an increase in the sound vibration level is suppressed.

More specifically, as shown in FIG.
It can be seen that the difference between the cylinder internal pressure and the suction pressure immediately before the valve opening due to the valve opening delay of 2 suddenly increases when the width of the sealing surface 28 exceeds 0.9 mm.

Further, as shown in FIG. 7, it can be seen that the pressure pulsation level suddenly increases when the width of the sealing surface 28 exceeds 0.9 mm.

Therefore, the width of the sealing surface 28 is 0.9
mm or less.

On the other hand, when the width of the seal surface 28 is reduced, stress concentrates on a portion of the suction valve 22 which abuts on the seal surface 28, and there is a possibility that the suction valve 22 may be damaged. . Therefore, the width of the sealing surface 28 is 0.6 mm without lowering the durability of the suction valve 22.
It is preferable that it is above.

That is, the width of the sealing surface 28 is set to 0.6 mm.
When the thickness is set to 0.9 mm or less, the suction valve 22 can be connected to the sealing surface 28 without lowering the durability of the suction valve 22.
Can be reduced, and the pressure fluctuation of the refrigerant due to the vibration of the suction valve 28 can be reduced. Furthermore, even during low-load, high-speed operation, the suction valve 2
2 does not stick to the sealing surface 28, so that no malfunction occurs.

The present invention is not limited to the above-described embodiment, but can be variously modified. For example, the present invention can be applied not only to a variable displacement swash plate type compressor but also to various types of compressors such as a rotary compressor and a normal reciprocating type.

[0036]

As described above, according to the present invention, the width of the seal surface of the valve plate with which the suction-side control valve abuts is set to 0.6 mm or more and 0.9 mm or less, which is smaller than in the prior art.

Therefore, the tapping noise when the suction side control valve comes into contact with the sealing surface is reduced, so that the noise and vibration of the compressor can be reduced.

Further, the delay of the valve opening timing during the operation of the compressor is reduced, and the sound vibration level accompanying the pressure pulsation of the refrigerant can be reduced.

Further, when the compressor is rotated at a low load and at a high speed, there is no possibility that the suction side control valve sticks to the sealing surface, so that the compressor does not malfunction.

In addition, even when the width of the sealing surface is made smaller than before, the performance of the compressor alone does not decrease and the cost does not increase.

[Brief description of the drawings]

FIG. 1 is a sectional view of a variable displacement swash plate compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part of FIG.

FIG. 3 is an enlarged front view of the valve plate shown in FIG. 2;

FIG. 4 is an enlarged view of a sealing surface of the valve plate shown in FIG.

FIG. 5 is an explanatory diagram showing a temporal change of the cylinder internal pressure when the seal surface width is changed.

FIG. 6 is an explanatory diagram showing a relationship between a seal surface width and a differential pressure between a cylinder internal pressure and a suction pressure immediately before a valve is opened.

FIG. 7 is an explanatory diagram showing a relationship between a seal surface width and a pressure pulsation level.

FIG. 8 is an enlarged sectional view of a main part of a conventional compressor.

FIG. 9 is an enlarged view of a sealing surface of the valve plate shown in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Pulley, 2a ... Magnet clutch, 3 ... Drive shaft, 3a ... Drive rod, 3b ... Pin, 4 ... Crank chamber, 5 ... Drive swash plate, 6 ... Thrust bearing, 7 ... Radial bearing, 8 ... Wobble plate, 9: Casing, 10: Guide pin, 11: Shoe, 12: Piston rod, 12a, b: Spherical bearing, 13: Piston, 14: Cylinder, 15: Compression chamber, 16: Cylinder head, 17: Suction port Reference numeral 18 discharge port, 19 valve plate, 20 suction port, 21 discharge port, 22 suction valve, 22a base end, 22b distal end, 23 discharge valve, 23a base end, 23b Tip part, 24: retainer, 25: rivet, 26, 27: annular groove, 28, 29: sealing surface, 50: conventional compressor.

Claims (1)

[Claims] A valve opening (20, 21) for connecting a refrigerant flow port (17, 18) and a compression chamber (15) to a valve plate (19) is provided at a base end (1). 22a, 23a) are fixed to the valve plate (19) and the tip portions (22b, 23b)
Attach control valves (22, 23) elastically abuttable to the refrigerant openings (20, 21) to open and close the refrigerant openings (20, 21). Annular groove in (26,27)
The radial width (L) of the sealing surface (28) of the valve plate (19) with which the suction-side control valve (22) abuts is set to 0.6 mm or more and 0.9 mm or less. A compressor characterized in that: