JP3232839B2 - 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, in a displacement type compressor, Japanese Patent Publication No.
As shown in Japanese Patent No. 832, 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 as a flow passage hole and a reed valve-shaped suction valve. . Then, after the refrigerant gas is compressed according to the change in volume of the compression chamber, the refrigerant gas is discharged from the compression chamber to the discharge chamber through a discharge port as a flow passage hole and a discharge valve in the form of a reed valve, and is discharged to an external refrigeration circuit. Derived. 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 of the reed valves is in a state in which each port is closed when elastic deformation is not performed.

[0003] The refrigerant gas contains mist-like lubricating oil, and when the port is closed by a reed valve, the valve seat surface of the peripheral portion of the port and the reed valve adhere to each other due to the adhesive force of the lubricating oil. And seal the port. However, the adhesive force of the lubricating oil is surprisingly large, and there is a problem that the reed 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 reed valve increases 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 reduced. growing. Further, at this time, the reed valve itself vibrates greatly, and 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.

For this reason, a valve device of a type in which foreign matter is blown onto the valve seat surface to roughen the valve seat surface so that the reed valve is easily separated from the valve seat surface when the valve is opened, or a port peripheral portion is provided on the valve seat surface. A valve device has been devised in which a contact area between the reed valve and the valve seat surface when the valve is closed is reduced by engraving a groove around the valve so that the reed valve is easily separated from the valve seat surface when the valve is opened. Was.

[0006]

However, in the type in which foreign matter is blown onto the valve seat surface to roughen the valve seat surface, the foreign matter is caused by the pressing force at which the reed valve repeatedly comes into contact with the valve seat surface. Because of this, the valve plate having the valve seat surface must be formed of a highly durable material. In the case of a type in which a groove is formed around the periphery of the port on the valve seat surface, a ring-shaped protrusion formed by the port and the groove may be deformed due to the repeated pressing force of the reed valve. Also, even when the valve is closed, a gap is formed between the reed valve and the valve seat surface, which causes leakage of the refrigerant gas. Therefore, also in this type of valve device, the valve plate having the valve seat surface must be formed of a highly durable material.

Further, the process of spraying foreign matter on the valve seat surface and the process of engraving a groove around the periphery of the port on the valve seat surface are troublesome and costly. SUMMARY OF THE INVENTION The present invention has been made in view of the problems existing in the prior art described above, and has as its object to reduce power loss and pulsation, improve performance and reliability with a lightweight and simple valve device. To provide a compressor that achieves the above.

[0008]

Means for Solving the Problems In order to achieve the above object, the present invention is configured as follows.
That is, at least one of the compression chamber and the suction chamber, and at least one of the compression chamber and the discharge chamber, are partitioned by a valve plate between the chambers, and are communicated with a flow path hole formed on the valve plate. In the compressor, at least one of which is opened and closed by an elastically deformable reed valve, inflow and outflow of refrigerant gas, the valve plate has a bulging portion formed by plastic working around the flow passage hole. As a result, in the assembled state before the compressor operation,
A gap is formed between the reed valve and the valve seat surface around the flow path hole.

In the present invention, it is effective if the bulging portion is formed to include a flow passage hole on the valve plate. In this case, the swelling portion may swell to the side where the reed valve exists, or may swell to the side opposite to the side where the reed valve exists. Further, in the present invention, it is effective that the bulging portion is formed on the periphery of the flow passage hole on the valve plate, particularly on the side of the reed valve at the periphery of the flow passage hole.

[0010]

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 both chambers and the elastic restoring force due to the elastic deformation of the reed valve act on the suction valve interposed between the suction valve and the suction port, which has been elastically deformed by the pressing force of the refrigerant gas from the compression chamber side and closed the suction port. Then, the suction valve is easily opened from the valve seat surface at the periphery of the suction port. Further, the discharge valve interposed between the compression chamber and the discharge chamber is elastically deformed by the pressing force of the refrigerant gas from the discharge chamber side, and is brought into close contact with the valve seat surface at the periphery of the discharge port to close the port. are doing.

On the other hand, during the discharge stroke, the volume of the compression chamber is closed and contracted, and the pressure of the refrigerant gas in the compression chamber rises. In addition, an elastic restoring force due to the elastic deformation of the reed valve itself acts, and the discharge valve is easily opened from the valve seat surface at the periphery of the discharge port similarly to the above-described suction valve. In addition, the suction valve is elastically deformed by the refrigerant gas pressure 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.

By repeating the suction stroke and the compression stroke as described above, the suction valve and the discharge valve are always smoothly opened at an appropriate valve opening timing. If the bulge is formed to include a port on the valve plate, the intake and discharge valves will deform along the bulge when the valve is closed, completely closing the port. When the bulging portion is formed on the periphery of the port on the valve plate, the suction valve and the discharge valve contact a part of the bulging portion and close the port when the valve is closed.

[0013]

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 joined 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 through suction ports 8a and 13a as flow passage holes on the valve plates 8 and 13, and the discharge chambers 7b and 12b communicate with the flow passages on the valve plates 8 and 13 respectively. Discharge port 8 as road hole
b and 13b communicate with the cylinder bores 1a and 2a. The suction ports 8a, 13a are connected to the valve forming plate 9,
Suction valves 9a, 14a formed in a reed valve shape on
Are opened and closed by the elastic deformation of the discharge ports 8b, 13b.
Are opened and closed by the elastic deformation of the discharge valves 10a, 15a similarly formed in a reed valve shape on the valve forming plates 10, 15.

In FIG. 1, if 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 the suction valve 9a away 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.

FIG. 2 shows the valve plate 13 and the discharge valve 15a in the assembled state before the compressor operation at the rear discharge valve portion.
Is shown. As shown in FIG. 2, the valve plate 13 has a bulging portion 13c that bulges around the discharge port on the discharge valve 15a side by performing plastic working such as press working. Also, the discharge valve 15a
As shown in FIG. 3, the seal portion 15b is formed integrally with the valve forming plate 15, and is in close contact with the valve seat surface of the peripheral portion of the discharge port 13b to close the port. 15b and a base portion 15c which is a bearing for connecting to the base portion 15c.

Then, as shown in FIG. 2, the root portion 15c of the valve and a part of the seal portion 15b abut on the bulging portion 13c of the valve plate 13 and deform along the bulging portion 13c. For this reason, in the assembled state before the compressor operation, the discharge valve 15a does not come into close contact with the valve seat surface around the discharge port 13b, and does not close the discharge port 15. At this time, the bulging height of the bulging portion 13c is set to be equal to or less than the thickness of the discharge valve 15a, and the bulging shape of the bulging portion 13c is changed to a curve forming an arbitrary cross section of the bulging shape. Thickness of 5
It is formed so as to be an aggregate of arcs of a circle having a size of 00 or more.

The valve plate 8 in the discharge valve section on the front side also has a similar bulging portion. Next, the operation of the compressor having the discharge valve 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 closed in close contact with the valve seat surface at the periphery. At this time, the discharge valve 15a elastically deforms from the assembled state, and comes into close contact with the valve seat surface at the peripheral portion of the discharge port 13b. Since the bulging shape of the bulging portion 13c of the valve plate 13 is formed gently as described above, the discharge valve 15a
Deformable along the bulging shape of the bulging portion 13c,
The discharge port 13b is easily closed.

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 of the lubricating oil, the seal portion 15b is quickly separated from the discharge port 13b.

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 restoring force due to the elastic deformation of the reed valve itself act, the discharge valve 10
a, 15a are opened from the valve seat surface at the periphery of the discharge port,
The discharge of the refrigerant gas is performed promptly at an appropriate discharge timing.
For this reason, overcompression of the refrigerant gas is prevented, and the power of the compressor is reduced. Also, by preventing over-compression,
The rise in temperature of the discharged refrigerant gas is suppressed, and accordingly, the deterioration of the seal ring made of rubber used in various parts of the compressor and the decrease in the fatigue strength of the constituent materials of the compressor body are suppressed, 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 discharge of the refrigerant gas is performed vigorously, thereby causing discharge pulsation. Further, at this time, the reed valve itself greatly vibrates 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.

Further, in this embodiment, the bulge 13
c is an arc of a circle whose bulging height is not more than the thickness of the discharge valve 15a, and whose bulge shape forms an arbitrary cross section of the bulge shape has a radius of 500 times or more the thickness of the discharge valve 15a. Are formed very loosely, as defined as a collection of For this reason, the bulging portion 13c
The valve is not deteriorated by being repeatedly pressed by the discharge valve 15a, and the valve plates 8, 13 having the bulging portion 13c are formed of a material such as aluminum, so that the weight of the compressor can be reduced. In addition, the discharge valve 15a is easily deformed along the bulging shape of the bulging portion 13c during the suction stroke and closes the discharge port 13b, so that the compression efficiency in the compression chamber is not reduced.

In this embodiment, the valve plates 8 and 13
A swelling portion which swells around the suction ports 8a and 13a may be provided on the upper side. In this case, the opening of the suction valves 9a and 14a in the suction stroke and the discharge valve 10
This is performed promptly as in the case of opening the valves a and 15a. 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 refrigerant gas is sufficiently sucked, the refrigerant gas is effectively compressed by the compressor, and the performance of the compressor is improved. Further, since the differential pressure across the valve when the suction valve is opened does not increase too much, suction pulsation is reduced, and vibration and noise of the compressor body are reduced.

In this embodiment, as shown in FIG. 4, the bulging portion 13d may bulge to the side opposite to the discharge valve 15a. In addition, the discharge port 13b is not necessarily
It may not be at the center of c, but may be at a position shifted from the center. Next, a second embodiment of the present invention will be described with reference to FIG. In this embodiment, FIG.
As shown in the figure, at the periphery of the discharge port 21b on the valve plate 21, the sealing portion 15 of the discharge valve 15a is provided.
b, at the point where the edge opposite to the root portion 15c side abuts,
A bulging portion 21c is provided. On the other hand, the discharge valve 15a
Are formed in the same plane as the valve forming plate 15 as in the first embodiment. When the bulging portion 21c on the valve plate 21 abuts against the edge of the seal portion 15b as shown in FIG. 5 during assembly, the discharge on the valve plate 21 in the assembly state before the compressor operation is performed. A gap is formed between the periphery of the port 21b and the seal portion 15b.

The discharge valve 10a on the front side also comes into contact with a bulge formed on the peripheral edge of the discharge port on the valve plate, so that the peripheral portion of the discharge port on the valve plate in the assembled state before operation of the compressor. And a gap between them. Also in this embodiment, since the bulging portion 21c is formed in the same definition as the bulging portion 13c of the first embodiment, it is very gentle.

When the compressor constructed as described above is operated, when the discharge valve 15a is closed, a part of the seal portion 15b contacts a part of the bulging portion 21c, and the seal portion 15b is connected to the discharge port. The discharge port 21b is closed by closely adhering to the valve seat surface of the periphery of 21b. Also in this embodiment, the discharge valves 10a and 15a undergo elastic deformation when the valve is closed, and close the discharge port 21b. Therefore, the compression chambers Pa and Pb and the discharge chambers 7b and 12 are provided to the discharge valves 10a and 15a during the discharge stroke.
b, and a restoring force due to the elastic deformation of the reed valve itself acts, so that the discharge valves 10a and 15a are quickly opened from the valve seat surface at the periphery of the discharge port. Therefore, the same operation and effect as those of the above-described first embodiment are obtained, such as the over-compression of the refrigerant gas is prevented and the discharge pulsation is reduced.

In this embodiment, the bulging portion 21c is formed at such a position that only a part of the bulging portion 21c comes into contact with the sealing portion 15b. Is required. Therefore, the bulging portion 21c can be formed by plastic working more easily than in the first embodiment. In this embodiment, the bulging portion 21c is connected to the discharge port 2
It may be formed at an arbitrary position on the periphery of 1b.

Also in this embodiment, a bulge may be provided at the peripheral edge of the suction port. In this case, the opening of the suction valves 9a and 14a in the suction stroke is not limited to the discharge valve 1 in the discharge stroke.
Since it is performed promptly in the same manner as the opening of the valves 0a and 15a, the suction pressure loss in the suction stroke is prevented and the suction pulsation is reduced. Next, a third embodiment of the present invention will be described with reference to FIG.

In the present embodiment, as shown in FIG. 6, the first and the second portions of the peripheral portion of the discharge port 31b on the valve plate 31 are brought into contact with the base portion 15c, which is the support portion of the discharge valve 15a. A bulging portion 31c having a gentle bulging shape as defined in the second embodiment is provided. On the other hand, the discharge valve 15a is formed in the same plane as the valve forming plate 15. The bulging portion 31c on the valve plate 13 comes into contact with the root portion 15c at the time of assembling, so that, in the assembled state before the operation of the compressor, the valve seat surface of the peripheral portion of the discharge port 31b on the valve plate 31 A gap is formed between the seal portion 15b.

The front discharge valve 10a also has a gap between the discharge port 10a and the valve seat surface at the periphery of the discharge port on the valve plate by contacting the bulging portion provided on the valve plate. Also in the present embodiment, the discharge valves 10a, 1
5a performs elastic deformation when the valve is closed to close the discharge port 21b, so that the discharge valve 10a, 15
a is quickly opened from the valve seat surface at the periphery of the discharge port. For this reason, the same operation and effect as those of the above-described first and second embodiments are obtained, such as the over-compression of the refrigerant gas is prevented and the discharge pulsation is reduced.

In this embodiment, since the bulging portion 31c requires dimensional accuracy only in its bulging height,
The formation of c by plastic working can be performed more easily than in the first embodiment. Further, in this embodiment, the bulge 3
1c is formed very loosely as defined in the first and second embodiments, and discharge valve 10
a, 15a, the repeated pressing force is applied to the bulging portion 3
The bulge 31c is excellent in durability against the repeated pressing force because the bulge 31c acts on the whole. Therefore, the valve plate 31 having the bulging portion 31c may be formed of a material such as aluminum, and the weight of the compressor can be reduced.

Also in this embodiment, the bulging portion may be provided at a position where the root portion of the suction valve abuts on the peripheral portion of the suction port. In this case, the suction valves 9a, 1 in the suction stroke are provided.
The opening of the discharge valve 10a, 15a in the discharge stroke
As soon as the valve is opened, suction pressure loss in the suction stroke is prevented and suction pulsation is reduced.

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. By providing a gently bulging portion on the valve plate, the discharge valve and the suction valve are elastically deformed when the valve is closed, so that the port can be opened. Any configuration may be used as long as the reed is opened and the reed valve is opened by the restoring force of its elastic deformation.

[0036]

As described in detail above, according to the present invention,
With a simple configuration in which only the shape of the valve plate is changed, an excellent effect of reducing the power and pulsation of the compressor is achieved. 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.

According to the present invention, since the valve plate can be formed of aluminum or the like, the weight of the compressor can be reduced. Further, when the bulge is formed to include the port on the valve plate, the port is completely closed because the reed valve is deformed along the bulge, thereby improving the compression efficiency of the compressor. When the bulging portion is formed on the peripheral edge of the port on the valve plate, the dimensional accuracy of the bulging portion is required only for the bulging height, so that the production is easy. When the bulging portion is formed on the side of the port near the support portion of the reed valve, the durability of the bulging portion against the repeated pressing force of the reed valve increases.

[Brief description of the drawings]

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

FIG. 2 is a view showing the shapes of a valve plate and a discharge valve in an assembled state of the first embodiment.

FIG. 3 is a diagram for explaining a discharge valve shape according to the first embodiment.

FIG. 4 is a view showing another example of the shapes of the valve plate and the discharge valve in the assembled state of the first embodiment.

FIG. 5 is a diagram showing the shapes of a valve plate and a discharge valve in an assembled state according to a second embodiment.

FIG. 6 is a view showing the shapes of a valve plate and a discharge valve in an assembled state according to a third embodiment.

[Explanation of symbols]

8, 13 ... valve plate, 8a, 13a ... suction port as flow path hole, 8b, 13b ... discharge port as flow path hole, 13c, 13d, 21c, 31c ... bulging part, 9
a, 14a: suction valves as reed valves, 10a, 15a
... Discharge valve as reed valve

Continuation of front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F04B 39/10

Claims (6)

(57) [Claims] At least one of a compression chamber and a suction chamber, and at least one of a compression chamber and a discharge chamber, is partitioned between the chambers by a valve plate, and communicates with a channel hole formed on the valve plate. In the compressor in which the hole is opened and closed by an elastically deformable reed valve, the inflow and outflow of the refrigerant gas are performed, the valve plate has a bulging portion formed by plastic working around the flow path hole. A valve device for a compressor, wherein a gap is formed between a reed valve and a valve seat surface around a passage hole in an assembled state before the compressor is operated. 2. The valve device for a compressor according to claim 1, wherein the bulging portion is formed to include a flow passage hole on the valve plate. 3. The valve device for a compressor according to claim 2, wherein said bulging portion is formed by bulging toward a side where a reed valve exists. 4. The valve device for a compressor according to claim 2, wherein the bulging portion is formed by bulging to a side opposite to a side where the reed valve is present. 5. The valve device for a compressor according to claim 1, wherein the bulging portion is formed on a periphery of a flow path hole on the valve plate. 6. A valve device for a compressor according to claim 5, wherein said bulging portion is formed on a side of a reed valve at a periphery of a flow path hole on said valve plate.