JP2000120545A - Valve structure and compressor therewith - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable it to improve a valve structure capable of reducing pressure loss and vibration where a fluid passes, and its compression efficiency, besides preventing noise from occurring. SOLUTION: The leg part 53s of a discharge valve 53 is provided with a second flow-through hole 101 allowing a flow of refrigerant gas in a valve opening state in the discharge valve 53. Likewise, a third flow-through hole 102 is installed on an incline 54a of a discharge retainer 54 regulating the maximum opening of the discharge valve 53 so as to make it continue to the second flow-through hole 101 in a contacted state with the discharge valve 53. In addition, the tip part 51a of an inlet valve 51 is provided with a fourth flow-through hole 103 allowing the flow of the refrigerant gas in a valve opening state in the inlet valve 51. Then, a cut flow groove 104 is formed on a bottom face 52a of an inlet valve stopper 52 regulating the maximum opening of the inlet valve 51 so as to make it continue to the fourth flow-through hole 103 in a contacted state with the inlet valve 51.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve structure of a fluid machine used for transporting a fluid, for example, and a compressor for compressing and sending a compressible fluid.

[0002]

2. Description of the Related Art As a valve structure for a fluid machine of this kind, for example, a compressor, a discharge valve structure having a discharge valve formed of, for example, a thin flat reed valve is known. That is, in this discharge valve structure, when the refrigerant gas is compressed in the working chamber and exceeds a predetermined pressure, the compressed refrigerant gas pushes open the valve hole opening / closing portion at the tip of the discharge valve and is discharged into the discharge chamber. It has become so. The opening and closing timing of the discharge valve is mainly interposed between the spring force of the discharge valve itself, the difference between the pressures acting on both sides of the discharge valve, and the discharge valve and the valve plate facing the discharge valve. Of the lubricating oil, which depends on the surface tension of the lubricating oil. Further, when this discharge valve is pushed up, a valve holding portion is provided which contacts the back surface from the base leg side of the discharge valve to the valve hole opening / closing portion and regulates excessive pushing up, and the discharge valve is damaged. There is also a known one that suppresses the occurrence of blemishes.

Further, for example, there has been known a suction valve structure of a piston type compressor in which a suction valve including a reed valve similar to the discharge valve is employed. That is, when the working chamber becomes negative pressure with the retreat of the piston from the top dead center position to the bottom dead center position, the refrigerant gas in the suction chamber pushes open the valve hole opening / closing part at the tip of the suction valve, and the working chamber is opened. Has been introduced. Further, a notch is provided in the vicinity of the open end of the cylinder bore for accommodating the piston, and the contact between the notch and the tip of the suction valve restricts excessive lifting of the suction valve, thereby damaging the suction valve. There is also a known one that suppresses the occurrence of blemishes.

[0004]

In the above-described conventional discharge valve structure, the high-pressure refrigerant gas in the working chamber is:
It is discharged through a gap between the discharge hole and the pushed open discharge valve. Here, a leg portion having a predetermined width exists between the valve hole opening / closing portion of the discharge valve and a base end portion of the discharge valve. Further, on the rear side of the leg portion, there is a valve pressing portion.
For this reason, the discharge of the refrigerant gas from the working chamber is hindered by the width of the leg portion, and the refrigerant gas discharge passage may be in an excessively narrowed state. Accordingly, even at the end of the discharge stroke, the high-pressure refrigerant gas in the working chamber is not sufficiently released, and the pressure loss increases. In the subsequent suction stroke, the high-pressure refrigerant gas remaining in the working chamber is re-expanded, so that there is a problem that improvement in compression efficiency cannot be expected.

[0005] The conventional suction valve structure also has substantially the same problems as the discharge valve structure. That is, in a state where the suction valve is pushed up, the introduction of the refrigerant gas from the suction chamber is inhibited by an amount corresponding to the width of the contact portion between the front end portion and the notch portion, and an extra throttle is formed in the refrigerant gas suction passage. May be applied. Accordingly, even at the end of the suction stroke, the amount of refrigerant gas drawn into the working chamber is limited, and the pressure loss increases. Then, there is a problem that the amount of the refrigerant gas supplied for the compression in the subsequent compression stroke is reduced, and the improvement of the compression efficiency cannot be expected.

Further, in the variable displacement compressor in which the discharge capacity of the working chamber can be changed, it is possible to operate at an intermediate discharge capacity where the discharge capacity does not reach the maximum. When the refrigerant gas is discharged in such an operation state at the intermediate capacity, depending on the difference in pressure acting on both side surfaces of the discharge valve, the discharge valve may be in a state of floating between the valve plate and the valve holding portion. May be. At this time, when the discharge valve starts being pushed up, the discharge valve is pushed up beyond the opening position which converges temporarily according to the pressure difference due to the attraction force with the valve plate, and then converges to the opening position while vibrating. May be done. Further, in this state, a narrow, closed space appears between the discharge valve and the valve holding portion. A part of the refrigerant gas discharged from the working chamber enters this space to generate a vortex, and the discharge valve may vibrate due to the action of the vortex.

[0007] The vibration of the discharge valve not only causes abnormal noise by itself, but also fluctuates the compression force in the working chamber, and generates a fluctuating load on the compressor. This fluctuating load becomes an exciting force of the entire compressor, and eventually causes resonance with various devices connected to the compressor, which leads to generation of noise. As described above, when vibration occurs in the discharge valve, various frequency components are complicatedly mixed and noise is generated. The present invention focuses on such a problem existing in the related art. It was done. An object thereof is to provide a valve structure capable of reducing pressure loss and vibration when a fluid passes. Another object of the present invention is to provide a compressor capable of improving compression efficiency and generating less noise.

[0008]

In order to achieve the above object, a first aspect of the present invention relating to a valve structure is a flat plate having a valve hole opening / closing portion for opening / closing a valve hole formed in a valve plate. In a valve structure having a valve body and an opening regulating portion that abuts on the valve body and regulates the maximum opening of the valve body, the valve body and the opening regulating portion include the valve hole opening / closing portion. The gist of the invention is to provide a permitting means for permitting the passage of the fluid flowing out of the valve hole with the valve hole opened.

Therefore, according to the first aspect of the present invention, the fluid flowing out of the valve hole is formed not only in the gap between the valve hole and the peripheral portion of the valve body and the opening regulating portion, but also in the valve body and the opening degree. It also passes through the permitting means provided in the regulating section. Thereby, the cross-sectional area of the passage of the refrigerant gas in the valve structure is enlarged, and the resistance of the valve structure when the fluid passes therethrough is reduced. Moreover, even if the fluid flowing out of the valve hole enters between the valve plate and the opening regulating portion while the valve body is floating between the valve plate and the opening regulating portion, the fluid is swirled. And flows out of the valve structure through the permitting means formed in the opening degree regulating portion without causing the opening.

According to a second aspect of the present invention, in the first aspect of the invention, the permitting means is formed so as to be substantially continuous with the valve body and the opening degree regulating portion in contact with each other. The gist is that it has been done.

Therefore, according to the second aspect of the present invention, in addition to the effect of the first aspect, the resistance when the fluid passes through the permitting means can be reduced. The invention of claim 3 of the present application is characterized in that, in the invention of claim 1 or claim 2, the valve hole is formed in a long hole shape extending in a direction substantially perpendicular to a longitudinal direction of the valve body. It is assumed that.

Therefore, in the third aspect of the present invention, in addition to the effect of the first or second aspect, the ratio of the valve hole opening / closing portion in the longitudinal direction of the valve body can be reduced, The space for the permitting means can be increased.

According to a fourth aspect of the present invention, in the invention according to any one of the first to third aspects, the permitting means formed on the valve body is configured to open and close a valve hole of the valve body. The gist of the present invention consists of a through hole formed between the portion and the base end.

Therefore, in the invention of claim 4 of the present application, in addition to the function of the invention of any one of claims 1 to 3, it is possible to reduce the spring constant of the valve body. Thus, the frequency of the self-excited vibration of the valve body can be changed. Then, in such a state that the valve body floats between the valve plate and the opening degree regulating portion, the valve body momentarily pushes up beyond the opening position which converges according to the difference in pressure acting on both sides. Even if it is performed, it is possible to quickly converge to the opening position.

According to a fifth aspect of the present invention, there is provided a suction chamber containing a low-pressure compressible fluid, and a working chamber for compressing the compressible fluid introduced from the suction chamber until the pressure reaches a predetermined pressure. And a discharge chamber containing a compressed high-pressure compressible fluid, wherein the space between the working chamber and the discharge chamber is defined in any one of claims 1 to 4. The gist of the present invention is that the partitioning is performed through the valve structure described above.

For this reason, in the invention of claim 5 of the present application, in addition to the function of any one of claims 1 to 4, the discharge of the compressible fluid compressed in the working chamber is achieved. Pressure loss at the time of discharge into a room can be reduced. As a result, the amount of the high-pressure compressible fluid to be re-expanded can be reduced, and a sufficient suction capacity can be secured in the subsequent suction stroke.

According to a sixth aspect of the present invention, in the fifth aspect of the present invention, the discharge capacity of the working chamber is changed by changing an amount of the compressive fluid introduced into the working chamber. The gist is to provide a capacity changing means.

Therefore, in the invention of claim 6 of the present application, in addition to the operation of the invention of claim 5, the operation is performed at an intermediate discharge capacity that does not reach the maximum discharge capacity, and the valve body is connected to the valve plate. Even if the valve floats between the valve and the opening regulating portion, it is possible to suppress the occurrence of vibration in the valve body.

The invention according to claim 7 of the compressor relates to a suction chamber for storing a low-pressure compressible fluid, and a working chamber for compressing the compressible fluid introduced from the suction chamber until reaching a predetermined pressure. And a discharge chamber containing a compressed high-pressure compressible fluid, wherein a space between the suction chamber and the working chamber is defined by any one of claims 1 to 4. The gist of the present invention is that the partitioning is performed through the valve structure described above.

Therefore, in the invention of claim 7 of the present application, in addition to the operation of the invention of any one of claims 1 to 4, in addition to the operation of the invention, the flow of the compressive fluid from the suction chamber to the working chamber is performed. Pressure loss at the time of inhalation can be reduced. Thereby, a sufficient suction amount of the compressible fluid in the suction stroke can be secured.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) Hereinafter, the valve structure of the present invention will be specifically described as a discharge valve structure and a suction valve structure of a single-headed piston type variable displacement compressor (hereinafter simply referred to as "compressor"). A first embodiment will be described with reference to FIGS.

First, the configuration of the entire compressor will be described. As shown in FIG. 2, the front housing 21 is fixedly joined to the front end of the cylinder block 22. The rear housing 23 is fixedly connected to the rear end of the cylinder block 22 via a valve / valve hole forming body 24. A front housing 21, a cylinder block 22, and a rear housing 23 constitute a housing of the compressor. Here, the front and the rear refer to the base end side of the drive shaft 26 whose front side is operatively connected to a vehicle engine Eg serving as a drive source to be described later, and the rear side is the same as the drive shaft 26.
Pointing to the tip side. The crank chamber 25 is defined by being surrounded by the front housing 21 and the cylinder block 22.

The drive shaft 26 is rotatably supported by a radial bearing 27 between the front housing 21 and the cylinder block 22 so as to cross the crank chamber 25. The front end 26a of the drive shaft 26 is connected to the opening 21a of the front housing 21.
From the outside. Between the drive shaft 26 and the inner peripheral surface of the opening 21a of the front housing 21,
A lip seal 28 for ensuring the airtightness of the crank chamber 25 is interposed.

A pulley 29 is fixed to the front end 26a of the drive shaft 26 so as to be integrally rotatable. The pulley 29 is supported by the front housing 21 via an angular bearing 30. Front housing 2
Reference numeral 1 denotes an angular bearing 30 that applies both an axial load and a radial load acting on the pulley 29.
Take it through. A belt 31 from a vehicle engine Eg serving as a driving source is wound around an outer peripheral portion of the pulley 29. Thus, this compressor is a so-called "clutchless" type compressor in which the drive shaft 26 is directly operatively connected to the vehicle engine Eg without using a clutch.

The lug plate 33 is connected to the crank chamber 25.
At the drive shaft 26. The front side surface 33a of the lug plate 33 and the front housing 21
A thrust bearing 34 for receiving a thrust load acting on the lug plate 33
Is interposed.

The swash plate 35 forming a cam plate is supported on the drive shaft 26 so as to be slidable in the axial direction and tiltable. The hinge mechanism 36 is interposed between the lug plate 33 and the swash plate 35. Swash plate 3
The drive shaft 26 is driven by the hinge mechanism 36.
, And can be integrally rotated. The radial center of the swash plate 35 is
When moving to the side, the inclination angle of the swash plate 35 is reduced, and when moving to the lug plate 33 side, the inclination angle of the swash plate 35 is increased. The maximum inclination angle of the swash plate 35 is defined by the contact between the maximum inclination defining protrusion 37 formed on the front side surface 35 a of the swash plate 35 and the rear side surface 33 b of the lug plate 33.

The inclination reducing spring 38 is formed of a coil spring, and the lug plate 33 on the drive shaft 26 and the swash plate 3
5 is wound. This inclination reduction spring 38
The radial center of the swash plate 35 is urged toward the cylinder block 22, that is, toward the side where the inclination angle of the swash plate 35 is reduced.

A plurality of cylinder bores 22 a are formed in the cylinder block 22 so as to surround the drive shaft 26. The one-sided piston 39 has one end housed in the cylinder bore 22a and the other end moored to the outer peripheral portion of the swash plate 35 via the shoe 40.
In each of the cylinder bores 22a, a working chamber is defined by the piston 39 and the valve / valve hole forming body 24. The piston 39 is reciprocated in the front-rear direction in the cylinder bore 22a by the rotation of the swash plate 35.

As shown in FIGS. 1 and 2, the rear housing 23 is formed with a discharge chamber 43 on the outer periphery and a suction chamber 44 on the center. The valve / valve forming body 24 is formed by sequentially joining a suction valve forming plate 45, a valve plate 46, a discharge valve forming plate 47, and a gasket 48.

The valve plate 46, the discharge valve forming plate 47, and the gasket 48 are provided with a suction hole 49 as a valve hole for communicating the suction chamber 44 with each of the cylinder bores 22a. On the periphery of the opening on the front end side of the suction hole 49,
An annular step portion 49a having a predetermined width is recessed. The valve plate 46 and the suction valve forming plate 45 are provided with discharge holes 50 as valve holes for communicating the respective cylinder bores 22a with the discharge chamber 43. An annular step portion 50a having a predetermined width is formed in the periphery of the opening on the rear end side of the discharge hole 50.

As shown in FIGS. 1, 2 and 6, the suction valve forming plate 45 is made of a thin metal plate and has a disk shape. The suction valve forming plate 45 is formed with a suction valve 51 as a valve body composed of a flat reed valve for opening and closing the suction hole 49 so as to correspond to each suction hole 49. A suction valve stopper 52 as an opening regulating portion having a substantially semicircular planar shape corresponding to the front end portion 51a of the suction valve 51 is provided on the periphery of the rear end side opening of the cylinder bore 22a.
Is recessed. When the suction valve 51 is pushed open, its tip 51a contacts the bottom surface 52a of the suction valve stopper 52, and the maximum opening of the suction valve 51 is regulated.

As shown in FIGS. 1, 2, 4 and 5,
The discharge valve forming plate 47 is made of a thin metal plate and has a disk shape. The discharge valve forming plate 47 has the discharge hole 5
A discharge valve 53 as a valve body composed of a plate-shaped reed valve for opening and closing 0 is formed to correspond to each discharge hole 50. The gasket 48 is made of a thin metal plate coated on both sides with rubber. The gasket 48 is provided with a discharge valve retainer 54 as a degree-of-opening regulating portion having a predetermined inclined surface 54a so as to correspond to each of the discharge valves 53 so as to bulge rearward. At the tip and both sides of the discharge valve retainer 54, a first circulation hole 55 that allows circulation of the refrigerant gas as a fluid is formed. When the discharge valve 53 is pushed open, the rear surface 53a thereof comes into contact with the inclined surface 54a of the discharge valve retainer 54, and the maximum opening of the discharge valve 53 is regulated.

As shown in FIGS. 2 and 3, a housing hole 58 is formed in the center of the cylinder block 22 along the axial direction of the drive shaft 26. A cylindrical blocking body 59 is slidably housed in the housing hole 58. The blocking body 59 includes a large diameter portion 59a and a small diameter portion 59b. A suction passage opening spring 60 is interposed between a step portion between the large diameter portion 59a and the small diameter portion 59b and a step portion 58a formed on the inner peripheral surface near the rear end of the accommodation hole 58. The blocking body 59 is urged toward the swash plate 35 by the suction passage opening spring 60.

The rear end 26 b of the drive shaft 26 is slidably inserted into the cylinder of the blocking body 59 via a radial bearing 61. The radial load acting on the rear end 26 b of the drive shaft 26 is supported on the inner peripheral surface of the housing hole 58 via the radial bearing 61 and the blocking body 59.

A suction passage 62 is formed in the center of the rear housing 23. The suction passage 62 is on an extension of the drive shaft 26 serving as a movement path of the blocking body 59. The suction passage 62 communicates with the accommodation hole 58, and a positioning surface 63 is formed around the opening of the suction passage 62 on the accommodation hole 58 side.
Are formed. The positioning surface 63 is on the valve / valve hole forming body 24. The tip surface of the small diameter portion 59b of the blocking body 59 is
It can contact the positioning surface 63. When the distal end surface of the small diameter portion 59b contacts the positioning surface 63, the blocking member 59
Is restricted from moving backward.

On the drive shaft 26 between the swash plate 35 and the blocking body 59, a thrust bearing 64 is slidably supported on the drive shaft 26. The thrust bearing 64 is always sandwiched between the rear side surface 35b of the swash plate 35 and the end surface of the large diameter portion 59a of the blocking body 59 by the urging force of the suction passage opening spring 60.

As the swash plate 35 moves toward the blocking body 59, the tilt of the swash plate 35 is transmitted to the blocking body 59 via the thrust bearing 64. By this tilt transmission, the interrupter 5
9 moves to the positioning surface 63 side against the urging force of the suction passage opening spring 60, and the blocking body 59 contacts the positioning surface 63. In this state, the minimum inclination position of the swash plate 35 is defined. The rotation of the swash plate 35 is prevented from being transmitted to the blocking body 59 by the presence of the thrust bearing 64.

The suction chamber 44 communicates with a receiving hole 58 through a through hole 65. When the blocking body 59 comes into contact with the positioning surface 63, the front end of the suction passage 62 is closed, and the communication port 65 is shut off from the suction passage 62. Drive shaft 26
Inside, an axial passage 66 is formed. Shaft passage 66
Opens into the crank chamber 25 near the radial bearing 27 and the lip seal 28 and opens into the cylinder of the blocking body 59. On the peripheral surface of the blocking body 59, the blocking body 59
A pressure release passage 67 that communicates the inside of the cylinder with the housing hole 58 is provided therethrough. Then, the shaft passage 66, the inside of the blocking body 59,
A bleed passage 70 connecting the crank chamber 25 and the suction chamber 44 is constituted by the pressure release port 67, the housing hole 58, and the port 65.

The discharge chamber 43 and the crank chamber 25 are connected by an air supply passage 71, and a capacity control valve 72 as a discharge capacity changing means is interposed on the air supply passage 71. Further, between the suction passage 62 and the displacement control valve 72, a pressure detection passage 73 for guiding the suction pressure Ps into the displacement control valve 72 is formed.

The suction passage 62 serving as an inlet for introducing refrigerant gas into the suction chamber 44 and a discharge flange 74 for discharging refrigerant gas from the discharge chamber 43 are connected by an external refrigerant circuit 75. On the external refrigerant circuit 75, the condenser 7
6. An expansion valve 77 and an evaporator 78 are interposed. A temperature sensor 79 is provided near the evaporator 78.
The temperature sensor 79 detects the temperature in the evaporator 78,
This detected temperature information is sent to the control computer 80.
Further, the control computer 80 is connected to a room temperature setting device 81, a room temperature sensor 82, an air conditioner operation switch 83, and the like for designating the temperature in the vehicle compartment.

Then, the control computer 80 calculates the room temperature specified by the room temperature setting unit 81 in advance, the detected temperature obtained from the room temperature sensor 82 and the temperature sensor 79,
The input current value is instructed to the drive circuit 84 based on an external signal from the air conditioner operation switch 83 regarding information such as ON or OFF. The drive circuit 84 outputs the commanded input current value to an electromagnetic drive unit 85 of the capacity control valve 72 described later. Other external signals include, for example, signals from an outdoor temperature sensor, an engine speed, and the like, and the input current value is determined according to the environment of the vehicle.

The capacity control valve 72 has a valve chamber 8 at its center.
A control valve element 87 is accommodated in a valve chamber 86 of the control valve element 6. One end of a control valve hole 88 formed to extend in the axial direction of the displacement control valve 72 is opened in the valve chamber 86 so as to face the control valve element 87. The control valve body 87 is urged by a forcible opening spring 89 in a direction to open the control valve hole 88. The valve chamber 86
Is connected to the discharge chamber 43 in the rear housing 23 via the valve chamber port 86a and the air supply passage 71.

A pressure-sensitive chamber 90 is provided at the tip of the capacity control valve 72.
Are formed. The pressure sensing chamber 90 communicates with the suction passage 62 of the rear housing 23 via a pressure sensing port 90a and a pressure detection passage 73. A bellows 91 that operates according to the suction pressure Ps in the suction passage 62 is accommodated in the pressure-sensitive chamber 90. This bellows 91
Is operatively connected to the control valve body 87 via a pressure-sensitive rod 92 so as to be able to come and go.

A port 93 is formed between the valve chamber 86 and the pressure sensing chamber 90 so as to be orthogonal to the control valve hole 88, and the other end of the control valve hole 88 is provided at an intermediate portion of the port 93. Is open. The port 93 is connected to the crank chamber 25 via the air supply passage 71.

At the base end of the displacement control valve 72, the electromagnetic drive section 85 is provided. A moving chamber 94 is defined in the electromagnetic driving unit 85, and a fixed iron core 95 is provided in an upper opening thereof.
Are fitted. The movable chamber 94 accommodates a movable iron core 96 having a substantially closed cylindrical shape so as to reciprocate. The movable iron core 96 is operatively connected to a control valve body 87 via an electromagnetic drive rod 97.

Outside the fixed iron core 95 and the movable iron core 96, a cylindrical coil 98 is provided so as to straddle both the iron cores 95 and 96.
Is arranged. A predetermined current is supplied to the coil 98 from a drive circuit 84 based on a command from the control computer 80.

Next, the features of this embodiment will be described, including the peripheral configuration. 1, 4, 5, and 7
As shown in the figure, the discharge valve 53 includes a valve hole opening / closing portion 53b on the distal end side and a leg 53c on the proximal end side. The valve hole opening / closing portion 53b is provided by the circulation of the refrigerant gas to the rear side surface 46a of the valve plate 46 while always covering the discharge hole 50 of the valve plate 46 and the annular step portion 50a formed therearound. The valve is in a closed state where it is adsorbed via the lubricating oil. The leg portion 53c is provided with a second flow hole 101 as a through hole constituting a permitting means at a predetermined distance from the valve hole opening / closing portion 53b. This second flow hole 10
Reference numeral 1 denotes a state where the discharge valve 53 is closed by the valve plate 46 when the discharge valve 53 is closed (see FIG. 1). Further, on the inclined surface 54a of the discharge valve retainer 54, a third valve as a permitting means is provided such that the discharge valve 53 is pushed up and continues to the second flow hole 101 in a state of being in contact with the discharge valve retainer 54. A flow hole 102 is formed (see FIG. 7).

Also, as shown in FIGS. 1, 6 and 8,
The suction valve 51 includes the front end portion 51a and the front end portion 5a.
1a, a valve hole opening / closing portion 51b adjacent to the base portion, and a leg portion 51 on the proximal side.
c. The valve hole opening / closing portion 51b always covers the suction hole 49 of the valve plate 46 and the annular step portion 49a formed therearound, and the front side surface 46b of the valve plate 46
The valve is in a closed state where it is adsorbed through the lubricating oil provided by the circulation of the refrigerant gas. A fourth flow hole 103 as permissive means is formed in the distal end portion 51a at a predetermined distance from the valve hole opening / closing portion 51b. When the suction valve 51 is closed, the fourth flow hole 103 is provided with the valve plate 46.
(See FIG. 1). The suction valve 51 is pushed up on the bottom surface 52a of the suction valve stopper 52 so that the bottom surface 5a of the suction valve stopper 52
A notch-shaped flow groove 104 is provided as an allowance so as to be continuous with the fourth flow hole 103 in a state of contact with the second flow hole 2a (see FIG. 8).

Next, the operation of the compressor configured as described above will be described. When the driving force of the vehicle engine Eg is transmitted to the drive shaft 26 via the belt 31 and the pulley 29 in the activated state of the vehicle engine Eg, the drive shaft 26 is rotated, and the swash plate 35 is It is rotated together. The rotation of the swash plate 35 is
0 is converted into a reciprocating motion of the piston 39 in the front-rear direction.

When the piston 39 moves from the top dead center side to the bottom dead center side, the refrigerant gas in the suction chamber 44 passes through the suction hole 49 and pushes back the suction valve 51 to be sucked into the cylinder bore 22a. You. Next, when the piston 39 moves from the bottom dead center side to the top dead center side, the cylinder bore 22
The refrigerant gas sucked into a is compressed until reaching a predetermined pressure, passes through the discharge hole 50, and pushes out the discharge valve 53 to be discharged into the discharge chamber 43.

Next, a description will be given of the operation of changing the discharge capacity of the compressor configured as described above. When the detected temperature obtained from the room temperature sensor 82 is equal to or higher than the temperature set by the room temperature setter 81 with the air conditioner operation switch 83 turned on, the control computer 80 sets the electromagnetic drive 85
Command. Then, the drive circuit 84 is connected to the coil 98.
, A predetermined current is supplied to the fixed iron core 95 and the movable iron core 96, as shown in FIG. This suction force is applied to the forcible release spring 89.
Is transmitted to the control valve body 87 via the electromagnetic drive rod 97 as a force in a direction in which the opening of the control valve hole 88 decreases, against the urging force of the control valve body 87.

On the other hand, when the electromagnetic drive unit 85 is in the excited state, the bellows 91 moves from the suction passage 62 to the detection passage 73.
Is displaced in accordance with the fluctuation of the suction pressure Ps introduced into the pressure-sensitive chamber 90 via. The displacement of the bellows 91 is transmitted to the control valve body 87 via the pressure-sensitive rod 92. Therefore, in the displacement control valve 72, the opening degree of the control valve hole 88 is determined by the balance between the urging force from the electromagnetic driving unit 85, the urging force from the bellows 91, and the urging force of the forcible opening spring 89.

Here, when the cooling demand in the vehicle compartment is large and the heat load on the evaporator 78 of the external refrigerant circuit 75 is large, for example, the temperature detected by the room temperature sensor 82 and the set value of the room temperature in the room temperature setter 81 And the difference becomes large. The control computer 80 controls the input current value so as to change the set value of the suction pressure Ps based on the detected temperature and the set value of the room temperature. That is, the control computer 80
Commands the drive circuit 84 to increase the input current value as the detected temperature increases. Therefore, the fixed iron core 9
The suction force between the armature 5 and the movable iron core 96 increases, and the urging force in the direction of decreasing the set value of the opening of the control valve hole 88 by the control valve body 87 increases. Then, the control valve hole 88 is opened and closed at a lower suction pressure Ps. Therefore, the capacity control valve 72 operates so as to maintain the lower suction pressure Ps by increasing the current value.

When the opening degree of the control valve hole 88 is reduced, the amount of refrigerant gas flowing from the discharge chamber 43 into the crank chamber 25 via the air supply passage 71 is reduced. On the other hand, the refrigerant gas in the crank chamber 25 flows through the bleed passage 70 to the suction chamber 44.
Has leaked to Therefore, the pressure P in the crank chamber 25
c decreases. When the heat load is large, the pressure in the suction chamber 44 is also high, and the pressure P in the crank chamber 25 is high.
The difference between c and the pressure in the cylinder bore 22a is reduced.
For this reason, the inclination angle of the swash plate 35 increases.

When the opening cross-sectional area of the capacity control valve 72 of the air supply passage 71 is zero, that is, the control valve body 87 of the capacity control valve 72 completely closes the control valve hole 88, the discharge chamber 4
The supply of the refrigerant gas from 3 to the crank chamber 25 is not performed. Eventually, the pressure Pc in the crank chamber 25 becomes substantially the same as the pressure Ps in the suction chamber 44, the inclination angle of the swash plate 35 becomes maximum, and the discharge capacity becomes maximum.

Conversely, when the cooling demand in the vehicle compartment is small and the heat load is small, the difference between the temperature detected by the room temperature sensor 82 and the set value of the room temperature in the room temperature setter 81 becomes small. The control computer 80 instructs the drive circuit 84 to decrease the input current value as the detected temperature is lower. For this reason, the attraction force between the fixed iron core 95 and the movable iron core 96 is weakened, and the urging force of the control valve body 87 in the direction of decreasing the set value of the opening degree of the control valve hole 88 is reduced. Then, the control valve hole 88 is opened and closed at a higher suction pressure Ps. Therefore, the capacity control valve 72 operates so as to maintain a higher suction pressure Ps by reducing the current value.

When the opening of the control valve hole 88 increases, the amount of refrigerant gas flowing from the discharge chamber 43 into the crank chamber 25 increases, and the pressure Pc in the crank chamber 25 increases. Also,
When the heat load is small, the pressure Ps in the suction chamber 44
And the difference between the pressure Pc in the crank chamber 25 and the pressure in the cylinder bore 22a increases. Therefore, the swash plate 3
5 becomes smaller.

When approaching the state without the heat load,
The temperature in the evaporator 78 decreases so as to approach the temperature at which frost occurs. When the temperature detected by the temperature sensor 79 falls below the set temperature, the control computer 80
Commands the drive circuit 84 to demagnetize the electromagnetic drive unit 85. The set temperature reflects a situation where frost is likely to occur in the evaporator 78. Then, the supply of current to the coil 98 is stopped, the electromagnetic drive unit 85 is demagnetized, and the attractive force between the fixed iron core 95 and the movable iron core 96 disappears.

For this reason, as shown in FIG.
7 is moved downward in the figure by the urging force of the forcible opening spring 89 and shifts to the opening position where the control valve hole 88 is opened to the maximum. Therefore, a large amount of high-pressure refrigerant gas in the discharge chamber 43 is supplied into the crank chamber 25 through the air supply passage 71, and the pressure Pc in the crank chamber 25 increases. Due to the pressure increase in the crank chamber 25, the swash plate 35 indicated by the two-dot chain line in FIG. 2 shifts to the minimum tilt position.

Further, the control computer 80 controls the electromagnetic drive unit 85 based on the OFF signal of the air conditioner operation switch 83.
, The swash plate 35 also moves to the minimum tilt position.

As described above, the opening / closing operation of the capacity control valve 72 changes according to the magnitude of the input current value to the coil 98 of the electromagnetic drive unit 85. That is, when the input current value increases, the opening and closing are performed at a low suction pressure Ps, and when the input current value decreases, the opening and closing operation is performed at a high suction pressure Ps. The compressor changes the inclination of the swash plate 35 to maintain the set suction pressure Ps, and changes the discharge capacity.

That is, the capacity control valve 72 has a role of changing the set value of the suction pressure Ps by changing the input current value, and a role of performing the minimum capacity operation regardless of the suction pressure Ps. By providing such a capacity control valve 72, the compressor plays a role of changing the refrigeration capacity of the refrigeration circuit (external refrigerant circuit 75).

When the inclination angle of the swash plate 35 is minimized, the blocking body 5
9 contacts the positioning surface 63, and the suction passage 62 is shut off. In this state, the cross-sectional area of the opening in the suction passage 62 becomes zero, and the flow of the refrigerant gas from the external refrigerant circuit 75 into the suction chamber 44 is prevented. The minimum inclination angle of the swash plate 35 is 0 °.
It is set to be slightly larger than. In this minimum inclination state, the blocking body 59 is connected to the suction passage 62 and the accommodation hole 58.
When placed in a closed position that blocks communication with the device. The blocking body 59 is switched between the closed position and the open position separated from the closed position in conjunction with the swash plate 35.

Since the minimum inclination angle of the swash plate 35 is not 0 °,
Even in the minimum inclination state, the refrigerant gas is discharged from the cylinder bore 22a to the discharge chamber 43. The refrigerant gas discharged from the cylinder bore 22a into the discharge chamber 43 flows into the crank chamber 25 through the air supply passage 71. The refrigerant gas in the crank chamber 25 flows into the suction chamber 44 through the bleed passage 70. The refrigerant gas in the suction chamber 44 is sucked into the cylinder bore 22 a and discharged again to the discharge chamber 43.

That is, in the minimum inclination state, the discharge chamber 4
3. A circulation passage passing through the air supply passage 71, the crank chamber 25, the bleed passage 70, the suction chamber 44, and the cylinder bore 22a
It is formed in the compressor. A pressure difference occurs between the discharge chamber 43, the crank chamber 25, and the suction chamber 44. Therefore, the refrigerant gas circulates in the circulation passage, and the lubricating oil flowing with the refrigerant gas ensures lubrication of each sliding portion in the compressor.

With the air conditioner operation switch 83 turned on and the swash plate 35 in the minimum tilt position, the temperature in the vehicle compartment rises and the heat load increases.
2 exceeds the set value of the room temperature in the room temperature setter 81. The control computer 80 commands the excitation of the electromagnetic drive unit 85 based on the change in the detected temperature, and the air supply passage 71 is closed. And crankcase 2
5 is applied to the suction chamber 44 through the bleed passage 70.
The pressure is reduced based on the pressure released to Due to this pressure reduction, the suction passage opening spring 60 extends from the contracted state in FIG. Then, the blocking body 59 is separated from the positioning surface 63, and the inclination angle of the swash plate 35 increases from the minimum inclination state shown by the two-dot chain line in FIG.

With the separation of the blocking body 59, the suction passage 6
2, the opening cross-sectional area gradually increases, and the amount of refrigerant gas flowing from the suction passage 62 to the suction chamber 44 gradually increases. Therefore, the amount of the refrigerant gas sucked into the cylinder bore 22a from the suction chamber 44 gradually increases, and the discharge capacity gradually increases. Therefore, the discharge pressure Pd gradually increases, and the load torque in the compressor does not fluctuate greatly in a short time. As a result, the fluctuation of the load torque in the compressor from the minimum discharge capacity to the maximum discharge capacity becomes slow, and the impact due to the load torque fluctuation is reduced.

When the vehicle engine Eg, which is the driving source, stops, the operation of the compressor also stops, that is, the rotation of the swash plate 35 stops, and the energization of the coil 98 of the displacement control valve 72 stops. Therefore, the electromagnetic drive unit 85 is demagnetized, the air supply passage 71 is opened, and the inclination angle of the swash plate 35 is minimized. If the operation stop state of the compressor continues, the pressure in the compressor becomes uniform, but the inclination angle of the swash plate 35 is maintained at a small inclination angle by the biasing force of the inclination reduction spring 38. Therefore, the vehicle engine Eg
When the operation of the compressor is started by the activation of the swash plate 35,
Starts rotating from the minimum tilt state where the load torque is the least, and there is almost no shock when the compressor is started.

Therefore, according to the present embodiment configured as described above, the following effects can be obtained. (A) In the compressor of the present embodiment, the leg 5 of the discharge valve 53
3c is provided with a second flow hole 101 that allows the passage of the refrigerant gas discharged from the discharge hole 50 in a state where the valve hole opening / closing portion 53b opens the discharge hole 50. Also,
Discharge valve retainer 5 for regulating the maximum opening of the discharge valve 53
4 also has a third circulation hole 102 that allows the passage of the refrigerant gas.

For this reason, the refrigerant gas discharged from the discharge hole 50 is supplied to the gap between the conventional discharge hole 50 and the peripheral portion of the discharge valve 53 and the discharge valve retainer 54 connected to the gap.
Of the discharge valve 53 and the third flow hole 102 of the discharge valve retainer 54 as well as the passage formed by the first flow hole 55 on the tip and both sides of the discharge valve 53.
Thereby, when the refrigerant gas is discharged from the cylinder bore 22a to the discharge chamber 43, the cross-sectional area of the passage through which the refrigerant gas passes can be increased. Therefore, the resistance at the time of passage of the refrigerant gas around the discharge valve 53 is reduced, and the pressure loss at the time of discharge of the refrigerant gas compressed in the cylinder bore 22a can be reduced.

Further, by reducing the pressure loss, the amount of refrigerant gas left in the cylinder bore 22a at the end of the discharge stroke can be reduced. For this reason,
The amount of the high-pressure refrigerant gas to be re-expanded can be reduced, and the suction capacity does not decrease in the subsequent suction stroke. Therefore, waste of the driving force from the vehicle engine Eg is suppressed, and the compression efficiency of the compressor can be improved.

(B) In the compressor of the present embodiment,
A capacity control valve 72 is provided for changing the difference between the pressure Pc in the crank chamber 25 and the pressure in the cylinder bore 22a to tilt the swash plate 35 and change the discharge capacity.

In such a compressor, the crank chamber 2
Depending on the difference between the pressure Pc in the cylinder 5 and the pressure in the cylinder bore 22a, the swash plate 35 may be disposed at an intermediate position between the maximum tilt position and the minimum tilt position. In such a state, the compressor is operated at an intermediate displacement which does not reach the maximum displacement. During the operation with the intermediate capacity, the discharge valve 53 may float between the valve plate 46 and the discharge valve retainer 54 without contacting the discharge valve retainer 54 when the refrigerant gas is discharged.

Here, in the present embodiment, even in such a state, a part of the refrigerant gas discharged from the discharge hole 50 is discharged from the second flow hole 101 of the discharge valve 53 to the discharge valve retainer 54. It diffuses into the discharge chamber 43 through the three flow holes 102. Therefore, even if another part of the discharged refrigerant gas enters between the rear surface 53a of the discharge valve 53 and the inclined surface 54a of the discharge valve retainer 54 from the peripheral portion of the discharge valve 53,
The refrigerant gas merges with the flow of the refrigerant gas passing through the second flow hole 101 and is quickly diffused into the discharge chamber 43. Therefore, the generation of a vortex between the back surface 53a of the discharge valve 53 and the inclined surface 54a of the discharge valve retainer 54 is suppressed, and the generation of vibration in the discharge valve 53 can be suppressed.
Therefore, generation of noise based on the vibration of the discharge valve 53 can be suppressed.

(C) In the compressor of the present embodiment,
A fourth flow hole 103 is provided at the distal end portion 51a of the suction valve 51 to allow the passage of the refrigerant gas flowing from the suction hole 49 when the valve hole opening / closing portion 51b opens the suction hole 49. . The suction valve stopper 52 that regulates the maximum opening of the suction valve 51 is also provided with a flow groove 104 that allows the passage of the refrigerant gas.

For this reason, the refrigerant gas sucked into the cylinder bore 22 a from the suction hole 49 flows through the suction valve 51 in addition to the conventional passage formed by the gap between the suction hole 49 and the peripheral portion of the suction valve 51. Also passes through a passage formed by the fourth flow hole 103 and the flow groove 104 of the suction valve stopper 52.
Thereby, when the refrigerant gas is sucked from suction chamber 44 into cylinder bore 22a, the cross-sectional area of the passage through which the refrigerant gas passes can be increased. Therefore, the resistance at the time of passage of the refrigerant gas around the suction valve 51 is reduced, and the pressure loss at the time of suction of the refrigerant gas into the cylinder bore 22a can be reduced.

By reducing the pressure loss, the amount of the refrigerant gas sucked into the cylinder bore 22a in the suction stroke can be increased, and a sufficient suction capacity can be secured. Therefore, waste of the driving force from the vehicle engine Eg is suppressed, and the compression efficiency of the compressor can be improved.

(D) In the compressor of the present embodiment,
The second communication hole 101 of the discharge valve 53 and the third communication hole 102 of the discharge valve retainer 54 are substantially continuous with the back surface 53a of the discharge valve 53 and the inclined surface 54a of the discharge valve retainer 54 in contact with each other. It is formed as follows.

For this reason, the refrigerant gas flows through the two flow holes 10.
1 and 102, the resistance can be reduced. Therefore, the pressure loss when the refrigerant gas is discharged from the cylinder bore 22a into the discharge chamber 43 can be further reduced, and the compression efficiency of the compressor can be further improved.

(E) In the compressor of the present embodiment,
The fourth flow hole 103 of the suction valve 51 and the flow groove 104 of the suction valve stopper 52 are substantially continuous with each other in a state where the tip 51a of the suction valve 51 and the bottom surface 52a of the suction valve stopper 52 are in contact with each other. Is formed.

Therefore, the refrigerant gas flows through the fourth flow holes 10.
3 and the resistance when passing through the flow groove 104 can be reduced. Therefore, the cylinder bore 22a is moved from the suction chamber 44 to the cylinder bore 22a.
The pressure loss when the refrigerant gas is sucked into the inside can be further reduced, and the compression efficiency of the compressor can be further improved.

(F) In the compressor of the present embodiment,
The second flow hole 101 is formed in the leg 53 a of the discharge valve 53. Therefore, the spring constant of the discharge valve 53 can be kept low, and the frequency of the self-excited vibration of the discharge valve 53 can be changed, so that the discharge valve 53 can be made difficult to vibrate. Here, in a state in which the discharge valve 53 floats between the valve plate 46 and the discharge valve retainer 54, for example, during operation at an intermediate displacement, the discharge valve 53 Depending on the difference in pressure acting on both sides of the valve 53, the valve 53 may be pushed up beyond the opening position to be converged. However, as described above, since the discharge valve 53 itself does not easily vibrate, even if the discharge valve 53 is pushed up beyond the opening position, it can be quickly converged to the opening position. . Therefore, noise generated due to the vibration of the discharge valve 53 can be further reduced.

(Second Embodiment) Next, a second embodiment of the present invention will be described focusing on parts different from the first embodiment.

In the second embodiment, as shown in FIG. 9, the shapes of a discharge hole 111 and a discharge valve 112 for opening and closing the discharge hole 111 are different from those of the first embodiment. That is, the discharge hole 111 has a long hole shape. The discharge hole 111 is provided so as to extend in a direction perpendicular to the longitudinal direction from the base end to the distal end of the discharge valve 112. Note that the discharge hole 111 has an opening cross-sectional area equivalent to that of the discharge hole 50 described in the first embodiment. Thereby, the opening diameter of the discharge hole 111 in the longitudinal direction of the discharge valve 112 is shorter than that of the discharge hole 50.

On the other hand, the discharge valve 112 is formed to have the same length in the longitudinal direction as the discharge valve 53 described in the first embodiment. For this reason, the discharge valve 1 is formed into a flat elliptical shape corresponding to the shape of the discharge hole 111.
The proportion of the twelve valve opening / closing portions 112a in the longitudinal direction of the discharge valve 112 is reduced. Then, the leg portion 112 of the discharge valve 112 is reduced by the reduced amount.
b and the fifth communication hole 1 drilled in the leg 112b
13 is extended in the longitudinal direction.

Therefore, according to the present embodiment, in addition to the effects (a) to (f) of the first embodiment,
The following effects can be obtained. (G) In the compressor of the present embodiment, the discharge hole 111 is formed in a long hole shape extending in a direction orthogonal to the longitudinal direction of the discharge valve 112.

Therefore, the ratio of the valve hole opening / closing portion 112a in the longitudinal direction of the discharge valve 112 can be reduced, and the space for the fifth flow hole 113 in the leg portion 112b can be increased. Therefore, the degree of freedom in designing the fifth flow hole 113 in the discharge valve 112 can be increased. Further, the cross-sectional area of the passage of the refrigerant gas in the fifth flow hole 113 can be enlarged, and the pressure loss at the time of discharging the refrigerant gas from the cylinder bore 22a to the discharge chamber 43 can be further reduced.

(Modification) The embodiment of the present invention may be modified as follows. In the above embodiments, the leg 51c of the suction valve 51
A circulation hole which allows the circulation of the refrigerant gas may be formed in the hole.

With this configuration, when the refrigerant gas is sucked from the suction chamber 44 into the cylinder bore 22a,
The cross-sectional area of the passage of the refrigerant gas can be further increased,
The pressure loss during the suction can be further reduced.

In each of the above embodiments, the discharge valve 5
A cutout portion is provided from the side edge portion of each of the discharge valves 51 and 112 toward the center in place of the second flow hole 101 and the fifth flow hole 113 of the first and second 112 to allow the flow of the refrigerant gas. May be. Further, a cutout may be provided instead of the third flow hole 102 of the discharge valve retainer 54 so as to correspond to the cutout, so as to allow the flow of the refrigerant gas.

In the above embodiments, a plurality of the flow holes 101, 102, 103, 113 and the flow grooves 104 may be provided. In the second embodiment, the shape of the discharge hole 111 is formed, for example, in an elliptical cross section, and the discharge valve 1
The twelve valve hole opening / closing portions 112a may be formed in, for example, a plane elliptical shape.

In each of the above embodiments, the valve structure of the present invention is embodied in a discharge valve structure and a suction valve structure of a clutchless type single head piston variable displacement compressor.
For example, compressors with clutches, fixed displacement compressors, double-headed piston compressors, wobble compressors, vane compressors,
The present invention may be embodied in a discharge valve structure or a suction valve structure of a scroll compressor.

In the above embodiments, the valve structure of the present invention is embodied in a discharge valve structure and a suction valve structure of a compressor for compressing a refrigerant gas. For example, a compressor for compressing air, a gas, The present invention may be embodied in a valve structure provided on a suction side or a discharge side of a fluid machine such as a pump for transporting a fluid such as a liquid or a granular material.

Even with such a configuration, substantially the same effects as in the above embodiments can be expected.

[0095]

As described in detail above, according to the first aspect of the present invention, the resistance of the valve structure during passage of the fluid can be reduced, and the pressure loss can be reduced. Moreover, even if the fluid enters between the valve plate and the opening regulating portion in a state where the valve body is floating between the valve plate and the opening regulating portion, no vortex is generated,
Generation of vibration in the valve body can be suppressed.

According to the second aspect of the present invention, in addition to the effect of the first aspect, the pressure loss when the fluid passes through the valve structure can be further reduced. Further, according to the invention of claim 3 of the present application, the claim 1 or claim 2 is provided.
In addition to the effects of the invention described in (1), the degree of freedom in designing allowable means in the valve body can be increased. Further, the cross-sectional area of the fluid passage in the permitting means can be enlarged, and the pressure loss can be further reduced.

According to the invention of claim 4 of the present application, in addition to the effects of any one of claims 1 to 3, the frequency of the self-excited vibration of the valve body is changed. Thereby, the valve body can be made hard to vibrate. Therefore, noise generated based on the vibration of the valve body can be further reduced.

According to the invention of claim 5 of the present application, in addition to the effect of the invention of any one of claims 1 to 4, in addition to the effect of discharging the compressive fluid to the discharge chamber, The pressure loss can be reduced, and the compression efficiency can be improved.

According to the invention of claim 6 of the present application, in addition to the effect of the invention of claim 5, noise caused by vibration of the valve body during operation at an intermediate displacement that does not reach the maximum discharge displacement. Can be suppressed.

According to the seventh aspect of the present invention, in addition to the effect of the first aspect of the present invention, when the compressive fluid is sucked into the working chamber. The pressure loss can be reduced, and the compression efficiency can be improved.

[Brief description of the drawings]

FIG. 1 is an enlarged sectional view showing a suction valve structure and a discharge valve structure according to a first embodiment.

FIG. 2 is a cross-sectional view showing the entire compressor having the suction valve structure and the discharge valve structure of FIG. 1;

FIG. 3 is a partial cross-sectional view showing a state in which a swash plate is arranged at a minimum tilt position in the compressor of FIG. 2;

FIG. 4 is a sectional view taken along line 4-4 of FIG. 1;

FIG. 5 is an enlarged plan view showing one discharge valve of FIG. 1;

FIG. 6 is a sectional view taken along line 6-6 of FIG. 1;

FIG. 7 is an enlarged sectional view showing a state in which the discharge valve of FIG. 1 is opened to the maximum.

FIG. 8 is an enlarged sectional view showing a state where the suction valve of FIG. 1 is opened to the maximum.

FIG. 9 is an enlarged plan view showing one discharge valve in the discharge valve mechanism of the second embodiment.

[Explanation of symbols]

43 ... discharge chamber, 44 ... suction chamber, 46 ... valve plate, 49 ... suction hole as valve hole, 50, 111 ... discharge hole as valve hole,
51 ... a suction valve as a valve body, 51b, 53b, 112a ...
Valve hole opening / closing part, 52 ... Suction valve stopper as opening degree regulating part, 53, 112 ... Discharge valve as valve body, 54 ... Discharge valve retainer as opening degree regulating part, 72 ... Capacity control valve as discharge capacity changing means .., 101... A second through-hole forming a permissible means and forming a through hole;
Reference numeral 103 denotes a fourth flow hole serving as a permitting means, 104 denotes a flow groove serving as a permitting means, and 113 denotes a fifth flow hole serving as a permitting means.

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Eiji Tokunaga 2-1-1 Toyota-cho, Kariya-shi, Aichi F-term in Toyota Industries Corporation (reference) 3H003 AA03 AC03 AD01 BA00 CC11 3H045 AA04 AA10 AA27 BA12 CA09 CA24 CA29 DA12 DA25 EA16 EA26 EA38 EA44 3H058 AA03 AA15 BB11 BB34 BB35 BB40 CA03 CA20 CB16 CB22 CD16 CD18 EE05 EE13

Claims (7)

[Claims] 1. A flat valve body having a valve hole opening / closing portion for opening and closing a valve hole formed in a valve plate, and an opening restriction for contacting the valve body and restricting a maximum opening of the valve body. In the valve structure, the valve body and the opening degree regulating unit are provided with an allowance unit that allows passage of a fluid flowing out of the valve hole in a state where the valve hole opening / closing unit opens the valve hole. Valve structure. 2. The valve structure according to claim 1, wherein said permitting means is formed so as to be substantially continuous in a state where said valve body and said opening degree regulating portion are in contact with each other. 3. The valve structure according to claim 1, wherein the valve hole is formed in a long hole shape extending in a direction substantially perpendicular to a longitudinal direction of the valve body. 4. The valve according to claim 1, wherein the permitting means formed in the valve body comprises a through hole formed between a valve hole opening / closing portion and a base end of the valve body. The valve structure according to claim 1. 5. A suction chamber containing a low-pressure compressible fluid,
A compressor having a working chamber for compressing a compressible fluid introduced from the suction chamber until a predetermined pressure is reached, and a discharge chamber containing a compressed high-pressure compressible fluid; A compressor partitioned from a chamber through the valve structure according to any one of claims 1 to 4. 6. The compressor according to claim 5, further comprising a discharge capacity changing unit that changes an amount of the compressible fluid introduced into the working chamber to change a discharge capacity of the working chamber. 7. A suction chamber containing a low-pressure compressible fluid;
A compressor including a working chamber that compresses a compressible fluid introduced from the suction chamber until a predetermined pressure is reached, and a discharge chamber that stores the compressed high-pressure compressible fluid; A compressor partitioned from a chamber through the valve structure according to any one of claims 1 to 4.