JP3259205B2 - Compressor valve device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor used for air conditioning of a vehicle, and more particularly to a valve structure of a suction valve and a discharge valve interposed between a compression chamber and a suction chamber and a discharge chamber. Things.

[0002]

2. Description of the Related Art Conventionally, a positive displacement compressor has
As disclosed in Japanese Patent No. 2832, refrigerant gas guided from an external refrigeration circuit to a suction chamber is sucked from the suction chamber to the compression chamber via a suction port and a suction valve. Then, after the refrigerant gas is compressed according to a change in volume of the compression chamber, the refrigerant gas is discharged from the compression chamber to the discharge chamber via a discharge port and a discharge valve,
It is led to an external refrigeration circuit. Normally, the suction valve and the discharge valve are elastically deformed by the pressure difference between the front and rear of the valve, that is, the pressure difference between the compression chamber and the suction chamber and the discharge chamber, and come into contact with the valve seat surfaces around the suction port and the discharge port. The ports are opened and closed by separating the ports. Normally, each valve is in a state in which each port is closed when elastic deformation is not performed.

[0003]

Mist-like lubricating oil is contained in the refrigerant gas, and when the port is closed by the valve, the valve seat surface of the peripheral portion of the port and the valve adhere to the lubricating oil. Close the port by force. However, the adhesive force of the lubricating oil is unexpectedly large, and there is a problem that the valve is difficult to separate from the valve seat surface when the valve is opened. If the suction valve is hard to open, a loss of suction pressure of the refrigerant gas occurs, and if the discharge valve is hard to open, an over-compression phenomenon that excessively compresses the refrigerant gas occurs. In either case, an extra drive torque of the compressor is required, resulting in power loss. Also,
If it is difficult to open the valve, the pressure difference before and after the valve is increased when the valve is actually opened, so that the suction and discharge of the refrigerant gas are performed vigorously, so that the suction pulsation and the discharge pulsation are large. Become. At that time, the valve itself vibrates greatly,
The vibration also contributes to pulsation.

[0004] Further drawbacks induced by the suction pressure loss and over-compression are that when the suction pressure loss reduces the amount of refrigerant gas sucked into the compression chamber, the efficiency and performance of the compressor are reduced. In addition, when the temperature of the refrigerant gas discharged due to over-compression increases, the seal ring made of rubber material used in each part of the compressor deteriorates, and the fatigue strength of the material of the compressor body decreases, so that the durability of the compressor decreases. Is adversely affected.

The present invention has been made in view of the above-mentioned problems in the prior art, and has as its object to provide a compressor with high performance and reliability with small power loss and pulsation. is there.

[0006]

Means for Solving the Problems In order to achieve the above object, the present invention is configured as follows.
That is, the compression chamber is communicated with the suction chamber and the discharge chamber at the suction port and the discharge port, respectively, and at least one of the suction port and the discharge port is opened and closed by an elastically deformable reed valve, so that the refrigerant gas is discharged. Reed valve abuts in compressor with inflow and outflow
When the valve seat surface around the port is in contact with the reed valve,
It is characterized by a slope giving a kinking deformation .

[0007] In the present invention, it is effective to oblique surfaces especially is a plane parallel to the tilted surface in the width direction of the center line as an axis of the reed valve.

[0008]

According to the valve structure having the above construction, during the suction stroke, the volume of the compression chamber is expanded in a closed state, and the pressure in the compression chamber becomes lower than the pressure in the suction chamber. The pressure difference between the two chambers and the elastic restoring force due to the torsional deformation of the valve act on the suction valve, which is interposed between the suction valves and closes the suction port by performing torsional deformation due to the pressing force of the refrigerant gas from the compression chamber side. The suction valve is opened so as to be partially peeled off from the valve seat surface at the periphery of the suction port. Also,
The discharge valve interposed between the compression chamber and the discharge chamber performs torsional deformation due to the pressing force of the refrigerant gas from the discharge chamber side, closely adheres to the valve seat surface at the periphery of the discharge port, and closes the port. I have.

On the other hand, during the discharge stroke, the volume of the compression chamber is hermetically closed and contracted, and the refrigerant gas pressure in the compression chamber rises. Therefore, the pressure applied by the refrigerant gas pressure in the compression chamber is applied to the discharge valve closing the discharge port. In addition, an elastic restoring force due to the torsional deformation of the valve itself acts, and the discharge valve is opened so as to be partially peeled off from the valve seat surface at the periphery of the discharge port in the same manner as the above-described suction valve. In addition, the suction valve is torsionally deformed by the pressure of the refrigerant gas in the compression chamber, and is in close contact with the valve seat surface at the peripheral portion of the suction port to close the port.

[0010] By repeating the above-described suction stroke and compression stroke, the suction valve and the discharge valve are always smoothly opened at an appropriate valve opening timing.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment in which the present invention is embodied in a double-headed piston swash plate compressor will be described below with reference to FIGS. As shown in FIG. 1, a pair of front and rear cylinder blocks 1 and 2 that are fastened and joined support a rotating shaft 4 to which a swash plate 3 is fixed. Are formed with a plurality of cylinder bores 1a and 2a. A double-headed piston 5 is reciprocally housed in the pair of front and rear cylinder bores 1 a and 2 a, and a shoe 6 is interposed between the double-headed piston 5 and the swash plate 3. Therefore, the rotation of the swash plate 3 causes the double-headed piston 5 to move back and forth in the cylinder bores 1a and 2a.

A front housing 7 is joined to the end surface of the cylinder block 1 via a valve plate 8, a pair of valve forming plates 9, 10 and a retainer forming plate 11, and the rear housing 12 is also connected to the end surface of the cylinder block 2. Are connected via a valve plate 13, a pair of valve forming plates 14, 15 and a retainer forming plate 16.

In both housings 7 and 12, a suction chamber 7 is provided.
a, 12a and discharge chambers 7b, 12b are formed.
The suction chambers 7a and 12a communicate with the cylinder bores 1a and 2a via the suction ports 8a and 13a on the valve plates 8 and 13, and the discharge chambers 7b and 12b connect the discharge ports 8b and 13b on the valve plates 8 and 13. Through the cylinder bores 1a and 2a. Suction ports 8a, 13
a is opened and closed by the elastic deformation of the suction valves 9a and 14a formed in a reed valve shape on the valve forming plates 9 and 14, and the discharge ports 8b and 13b are connected to the valve forming plates 10 and 14.
15 also has a discharge valve 10 formed in the shape of a reed valve.
a and 15a are opened and closed by elastic deformation.

In FIG. 1, when the head end face 5a of the double-headed piston 5 is on the front side and the head end face 5b is on the rear side, the refrigerant gas in the suction chamber 7a pushes back the suction valve 9a during the suction stroke on the front side. It is sucked into the compression chamber Pa of the cylinder bore 1a, and during the discharge stroke, the compression chamber Pa
The refrigerant gas inside pushes the discharge valve 10a and is discharged to the discharge chamber 7b. The same suction and discharge are performed on the rear side, and the discharge valves 10a and 15a which are rejected with the discharge of the refrigerant gas from the compression chambers Pa and Pb of the cylinder bores 1a and 2a to the discharge chambers 7b and 12b are provided with retainer forming plates. 1
The abutment is restricted by the abutment on the retainers 11a and 16a on the upper and lower retainers 1 and 16.

FIGS. 2 and 3 are enlarged views of the rear discharge valve portion, and show the shape of the discharge valve 15a in an assembled state before the compressor operation. The discharge valve 15a shown in FIG. 4 is formed integrally with the valve forming plate 15, and has a sealing portion 15b which is in close contact with a valve seat surface of a peripheral portion of the discharge port 13b to close the port, a valve forming plate 15 main body. Root part 1 connecting with sealing part 15b
5c. Then, by pressing the root portion 15c of the valve, as shown in FIGS. 2 and 3, the valve is formed in a torsion shape that is rotated around the center line Y in the width direction of the valve. I have. The above-described press working is performed such that, for example, as shown in FIG. 4, a broken line S orthogonal to the center line Y is made into a mountain fold, and an oblique dashed line T closer to the seal portion 15c than the broken line S is bent into a valley fold. Good. By making the broken line S mountain-folded, the seal portion 15b above the broken line S is separated from the port peripheral edge, and by making the broken line T valley folded, the seal portion 15c is twisted with respect to the valve seat surface of the port peripheral portion. And as a result valve 1
5a can be formed in a desired shape. For this reason,
The discharge valve 15a does not come into close contact with the valve seat surface at the periphery of the discharge port 13b in a state where the elastic deformation is not performed.
Do not close. Further, the discharge valve 10a in the front discharge valve portion also includes a seal portion 10b for closing the discharge port 8b similarly to the discharge valve 15a, and a root portion 10c for connecting the valve forming plate 10 main body and the seal portion 10b. It is formed in a twisted shape as if it were rotated about the center line of the valve.

Next, the operation of the compressor having the discharge valve section configured as described above will be described. When the rear side of the compressor is in the suction stroke, the refrigerant gas pressure in the compression chamber Pb of the cylinder bore 2a decreases, so that the discharge valve 15a is sucked into the compression chamber Pb, and the discharge port 13b as shown in FIG. The discharge port 13b is in close contact with the peripheral valve seat surface.
To close. At this time, the discharge valve 15a elastically deforms from the natural torsion shape and comes into close contact with the valve seat surface at the peripheral portion of the discharge port 13b. Since the discharge valve 15a is deformed to rotate about the center line Y of the valve as an axis, this elastic deformation is easily performed. Therefore, if the twisted shape of the discharge valve 15a in the natural state is appropriately formed, the sealing portion 1
5b can be tightly joined to the valve seat surface at the periphery of the discharge port 13b to close the discharge port 13b with good sealing.

When the rear side is in the discharge stroke, the pressure of the refrigerant gas in the compression chamber Pb increases, so that the discharge valve 15a is pressed by the refrigerant gas in the cylinder bore 2a. At this time, the seal portion 15b is in close contact with the valve seat surface of the peripheral portion of the discharge port 13b by the mist-like lubricating oil contained in the refrigerant gas, but this contact force is unexpectedly large. However, since the pressing force of the refrigerant gas and the restoring force due to the elastic deformation of the valve itself oppose the adhesion force due to the lubricating oil, the sealing portion 15b is quickly removed from the discharge port 13b so as to be partially peeled off. Separate.

Also on the front side of the compressor, the discharge valve 10a is connected to the discharge valve 15 during the suction stroke and the discharge stroke.
The same operation as in a is performed. In this example,
In the discharge stroke, the compression chambers Pa,
Since the pressure difference between Pb and the discharge chambers 7b and 12b and the elastic restoring force due to the torsional deformation of the valve itself act, the discharge valve 10
The valves 15a and 15a are opened so as to be partially peeled off from the valve seat surface at the periphery of the discharge port. Then, since the discharge of the refrigerant gas is performed promptly at an appropriate discharge timing, overcompression of the refrigerant gas is prevented, and the power of the compressor is reduced. Also, by preventing over-compression, the temperature rise of the discharged refrigerant gas is suppressed, and accordingly, the seal ring of rubber material used in various parts of the compressor is deteriorated, and the fatigue strength of the constituent materials of the compressor body is reduced. And the durability of the compressor is increased.

If the discharge valves 10a and 15a are difficult to open, the differential pressure across the valves increases when the valves are opened, and the refrigerant gas is discharged vigorously, thereby causing discharge pulsation. Further, at this time, the valve itself vibrates greatly due to the dynamic pressure of the refrigerant gas, and pulsation due to the vibration also occurs. In this embodiment, since the discharge valves 10a and 15a are properly opened, the discharge pulsation as described above is reduced, and the vibration and noise of the compressor body are reduced.

In this embodiment, the suction valves 9a and 14a may be formed in the same torsion shape as the discharge valves 10a and 15a. In this case, the suction valves 9a and 14a in the suction stroke are used.
Is quickly performed similarly to the opening of the discharge valves 10a and 15a in the discharge stroke. In this case, since the suction pressure loss in the suction stroke is prevented, the power of the compressor is reduced. In addition, since the suction of the refrigerant gas is sufficiently performed,
The compression action of the refrigerant gas of the compressor is efficiently performed, and the performance of the compressor is improved. Furthermore, since the differential pressure across the valve at the time of opening the suction valve does not increase too much, suction pulsation is reduced,
Vibration and noise of the compressor body are reduced.

Next, a second embodiment of the present invention will be described with reference to FIGS. In the present embodiment, a protruding portion 17 is provided at a position where the root portion 15c of the discharge valve 15a contacts the peripheral portion of the discharge port 13b on the valve plate 13. On the other hand, the discharge valve 15a
Are formed in the same plane as the valve forming plate 15. At the time of assembly, the protrusion 1 on the valve plate 13 is
7 comes into contact with the root portion 15c, so that the discharge valve 1
5a is formed in a twisted shape. Discharge valve 1 on front side
Oa is also provided with a torsion shape by abutting on a protrusion provided on the valve plate 8.

Also in this embodiment, the discharge valves 10a and 15a in the assembled state have a twisted shape, so that the same operations and effects as those of the above-described first embodiment are achieved. Also, in the present embodiment, the suction valves 9a and 14a are formed in a twisted shape by providing projections at the peripheral edges of the suction ports 8a and 13a where the root portions of the suction valves 9a and 14a abut. It is possible to smoothly open the valves 9a and 14a.

In this embodiment, the valve plates 8 and 13
The torsional shape of the discharge valves 10a, 15a may be formed by interposing an intervening member 9 between the valve plates 8, 13 and the root portions 10c, 15c at the time of assembling without providing the protrusion 17 on the upper side. . Next, a third embodiment of the present invention will be described with reference to FIGS. In this embodiment, the discharge valve 15a is press-worked so as to be bent in a mountain fold along a broken line S in FIG. Therefore, in the assembled state of the discharge valve 15a, as shown in FIGS. 7 and 8, all of the seal portions 15b are separated from the valve seat surface of the port peripheral portion. The front-side discharge valve 10a is also formed in a similar shape.

The operation of the discharge valve 15a having such a configuration will be described. When the rear side of the compressor is in the suction stroke, the pressure in the compression chamber Pb decreases, so that the discharge valve 15a
a performs elastic deformation from a natural state separated from the peripheral portion of the port and makes close contact with the valve seat surface of the peripheral portion of the discharge port 13b.
During the discharge stroke on the rear side of the compressor, a restoring force due to elastic deformation acts on the discharge valve 15a in addition to the pressing force of the refrigerant gas in the compression chamber Pb. The valve is opened so as to be peeled off. Discharge valve 10a also on the front side
Performs the same operation.

In this embodiment, the compression chambers Pa and Pb and the discharge chamber 7 are provided to the discharge valves 10a and 15a during the discharge stroke.
b and 12b and a restoring force due to elastic deformation of the valve itself act, so that the discharge valves 10a and 15a are opened smoothly. As a result, the same effects as those of the first and second embodiments can be obtained in the valve structure of this embodiment. Also in the present embodiment, the suction valves 9a and 14a are connected to the discharge valves 10a and 15a.
In this case, the opening of the suction valves 9a and 14a in the suction stroke is performed promptly in the same manner as the opening of the discharge valves 10a and 15a in the discharge stroke. Also in this case, similarly to the above-described embodiment, the suction pressure loss in the suction stroke is prevented, so that the power and suction pulsation of the compressor are reduced, and the performance of the compressor is improved because the refrigerant gas is sufficiently sucked. It produces effects such as:

Next, a fourth embodiment of the present invention will be described with reference to FIG. In this embodiment, the valve seat surface at the periphery of the discharge port 13b is formed by a slope 19 as shown in FIG. On the other hand, the discharge valve 15a is formed in the same plane as the valve forming plate 15.
Therefore, when closing the discharge port 13b, the discharge valve 15a performs a torsional deformation such that the discharge valve 15a rotates around the center line of the valve, and comes into close contact with the inclined surface 19. Further, since the valve seat surface at the periphery of the discharge port 8b is also formed with the same slope as the slope 19, the discharge valve 10a is torsionally deformed and adheres to the slope to close the discharge port 8b.

In the compressor having the discharge valve portion configured as described above, the discharge valves 10a and 15a are elastically restored by the torsional deformation of the discharge valves 10a and 15a during the discharge stroke, as in the above-described embodiment. The opening is made smoothly.
Also in the present embodiment, the valve seat surfaces of the peripheral portions of the suction ports 8a, 13a are formed with inclined surfaces, and when the suction valves 9a, 14a close the suction ports 8a, 13a, they undergo torsional deformation to perform the torsional deformation. , 13a may be in close contact with the valve seat surface at the peripheral edge. Also in this case, the opening of the suction valves 9a and 14a is smoothly performed by the elastic restoring force of the torsional deformation of the suction valves 9a and 14a.

In each of the above embodiments, the present invention has been embodied in the double-headed piston swash plate type compressor.
The present invention can be applied to any compressor having a swash plate type, a wobble type, a vane type, a scroll type, and the like having a reed valve-shaped discharge valve or a suction valve. is there. Further, the present invention is applicable to both fixed displacement and variable displacement compressors.

The present invention is not limited to the configuration of the above-described embodiment. The valve seat surface of the peripheral portion of the port and the sealing portion of the valve need not be parallel in the assembled state. Any structure may be used as long as it performs elastic deformation to close the port and the valve is opened by the restoring force of the elastic deformation. For example, a configuration is possible in which the valve is formed in a torsion shape and the valve seat surface at the peripheral portion of the port is formed as a slope.

[0030]

As described in detail above, according to the present invention,
An excellent effect that power and pulsation of the compressor are reduced by simple means only by changing the shapes of the suction valve and the discharge valve portion. In addition, during the suction stroke, the air is sufficiently sucked into the compression chamber, so that the efficiency and performance of the compressor are improved. During the discharge stroke, the temperature rise of the refrigerant gas discharged due to overcompression is suppressed. Is improved. Furthermore, since the vibration and noise of the compressor are reduced with the reduction of the pulsation, there is no need to provide a muffler or the like in the refrigerant gas passage, and there is an advantage that the cost is reduced.

[Brief description of the drawings]

FIG. 1 is a side sectional view of an entire compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a discharge valve section showing a valve structure of the first embodiment.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a view for explaining a discharge valve shape according to the first embodiment.

FIG. 5 is an enlarged sectional view of a discharge valve portion showing a valve structure according to a second embodiment.

FIG. 6 is a sectional view taken along line BB of FIG. 5;

FIG. 7 is an enlarged sectional view of a discharge valve section showing a valve structure of a third embodiment.

FIG. 8 is a sectional view taken along the line CC in FIG. 7;

FIG. 9 is a sectional view showing a valve structure according to a fourth embodiment.

[Explanation of symbols]

8a, 13a: suction port, 8b, 13b: discharge port, 9a, 14a: suction valve, 10a, 15a: discharge valve,
19 ... Slope

────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-60-227075 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04B 39/10 F04B 27/08

Claims (2)

(57) [Claims] 1. A compression chamber is communicated with a suction chamber and a discharge chamber at a suction port and a discharge port, respectively, and at least one of the suction port and the discharge port is opened and closed by an elastically deformable reed valve. In the compressor where the refrigerant gas flows in and out , the valve seat surface around the port where the reed valve comes in contact
Wherein the reed valve is a slope that gives a torsional deformation to the reed valve . 2. The valve seat surface around the port is in the width direction of the reed valve.
The plane must be parallel to the plane inclined about the center line of
The valve device for a compressor according to claim 1, wherein: