Capacity control valve having an auxiliary communication part allowing communication with an intermediate passage

A capacity control valve (1) for controlling a flow rate or pressure of a variable capacity compressor according to a valve opening degree of a valve section includes: a valve main body (10) having a first valve chamber (14), a second valve chamber (15) and an interior space (16); a valve body (21) having an intermediate communication passage (26) for allowing communication between the first valve chamber and the interior space, a first valve part (21c1) arranged in the first valve chamber, a second valve part (21b1) for opening and closing communication between the interior space and the second valve chamber, and a shaft part (21a) arranged in the interior space; a solenoid (30); a pressure-sensitive body (22) arranged in the interior space; and an auxiliary communication part (21f) which is arranged in the interior space and which allows communication between the interior space and the intermediate communication passage.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is the U.S. National Phase under 35 U.S.C. § 371 of International Application PCT/JP2018/025123, filed Jul. 3, 2018, which claims priority to Japanese Patent Application No. JP2017-133157, filed Jul. 6, 2017. The International Application was published under PCT Article 21(2) in a language other than English.

TECHNICAL FIELD

The present invention relates to a capacity control valve for controlling a flow rate or pressure of a variable capacity compressor, and, particularly, relates to a capacity control valve for controlling a discharge rate of a variable capacity compressor and the like used for an air-conditioning system for motor vehicle and the like according to a pressure load.

BACKGROUND ART

A swash plate type variable capacity compressor used for an air-conditioning system for motor vehicle and the like includes a rotating shaft rotationally driven by the rotational force of an engine, a swash plate which is coupled to the rotating shaft so that its inclination angle may be varied, a piston for compression coupled to the swash plate, and the like, and changes the inclination angle of the swash plate, thereby changing a stroke of the piston and controlling a discharge rate of a refrigerant.

By appropriately controlling pressure within a control chamber and adjusting a balancing state of the pressure acting on the both surfaces of the piston by means of a capacity control valve which is driven to be opened or closed by electromagnetic force while utilizing a suction pressure of a suction chamber for suctioning a refrigerant, a discharge pressure of a discharge chamber for discharging the refrigerant pressurized by the piston, and a control chamber pressure of the control chamber (a crank chamber) containing the swash plate, the inclination angle of the swash plate can continuously change the stroke of the piston.

As shown inFIG. 6, such a capacity control valve160includes: a valve section170having a second valve chamber182communicating with a discharge chamber via a second communication passage173, a first valve chamber183communicating with a suction chamber via a first communication passage171, and a third valve chamber184communicating with a control chamber via a third communication passage174; a pressure-sensitive body178which is arranged in the third valve chamber to extend and contract by ambient pressure and which has a valve seat body180provided at a free end in an extension and contraction direction; a valve body181having a second valve part176for opening and closing a valve hole177for communicating the second valve chamber182and the third valve chamber184, a first valve part175for opening and closing the first communication passage171and a circulation groove172, and a third valve part179for opening and closing the third valve chamber184and the circulation groove172by engagement and disengagement to and from the valve seat body180in the third valve chamber184; a solenoid section190for exerting an electromagnetic driving force on the valve body181, and the like. Then, in the control capacity valve160, without providing a clutch mechanism in a variable capacity compressor, a pressure in the control chamber (a control chamber pressure) Pc and a suction pressure Ps (a suction pressure) can be adjusted by communicating the discharge chamber and the control chamber in a case where the need to change the control chamber pressure arises (Hereinafter, it is referred to as a “conventional art”. For example, see Patent Document 1.).

CITATION LIST

Patent Documents

Patent Document 1: JP 5167121 B

SUMMARY OF THE INVENTION

Problem to be Solved by the Invention

In the conventional art, if the swash plate type variable capacity compressor is stopped and then is intended to be started after a long-time standing, a liquid refrigerant (the refrigerant which is liquefied by being cooled during standing) is accumulated in the control chamber (crank chamber), and therefore it is impossible to secure a set discharge rate by compressing the refrigerant unless the liquid refrigerant is discharged. Therefore, in order to perform a desired capacity control just after start-up, the liquid refrigerant in the control chamber (crank chamber) needs to be discharged as quickly as possible.

Thus, as shown inFIG. 7andFIG. 8, the conventional capacity control valve160includes a liquid refrigerant discharge function in order to discharge the liquid refrigerant in the control chamber (crank chamber) as quickly as possible at the time of start-up. That is, if the variable capacity compressor is stopped and then is intended to be started after a long-time standing, high-pressure liquid refrigerant accumulated in the control chamber (crank chamber) flows into the third valve chamber184from the third communication passage174. Then, the pressure-sensitive body (bellows)178contracts and the third valve part179and the valve seat body180are opened therebetween. An opening area between the third valve part179and the valve seat body180is large, and therefore the liquid refrigerant can be discharged to the suction chamber out of the control chamber (crank chamber) in a short time, through the auxiliary communication passage185, the intermediate communication passage186and the circulation groove172from the third valve chamber184, thereby capable of quickly shifting to a cooling operation state at maximum capacity.

Subsequently, when discharge of the liquid refrigerant in the control chamber (crank chamber) is finished, the control chamber pressure Pc and the suction pressure Ps are decreased, and the third valve part179and the valve seat body180are closed therebetween. At the same time, the second valve part176is opened from a fully closed state by the solenoid section S and shifts to a control state. When shifted to the control state, the fluid at the discharge pressure Pd is supplied to the third valve chamber184from the second valve chamber182, and thereby a differential pressure between the suction pressure Ps and the control chamber pressure Pc is changed, an inclination angle of the swash plate is changed, and a stroke (discharge capacity) of a piston is controlled.

However, in the above-described conventional art, even if a control operation begins and the third valve part179and the valve seat surface of the valve seat body180are closed therebetween, a little gap is generated between the third valve part179and the valve seat body180when the pressure of the third valve chamber184is fluctuated. Therefore, the fluid volume flowing to the first valve chamber183via the auxiliary communication passage185and the intermediate communication passage186from the third valve chamber184is fluctuated. As a result, the pressure of the suction chamber communicating with the first valve chamber183is fluctuated, and thus there was a problem that a control performance of the variable capacity compressor is deteriorated.

The present invention has been made to solve the problems the above-described conventional art has, and an object thereof is to provide a capacity control valve for controlling a flow rate or pressure of a variable capacity compressor according to a valve opening degree of a valve main body, the capacity control valve capable of making constant a fluid volume flowing to a first valve chamber from a third valve chamber even if the pressure of the third valve chamber is fluctuated and capable of improving a control performance of the variable capacity compressor.

Means for Solving Problem

To attain the above object, a capacity control valve according to a first aspect of the present invention is a capacity control valve for controlling a flow rate or pressure according to a valve opening degree of a valve section, the capacity control valve including:

a valve main body having an interior space communicating with a third communication passage through which a fluid at a control pressure passes, a second valve chamber communicating with a second communication passage through which a fluid at discharge pressure passes and having a valve hole communicating with the interior space and a second valve seat arranged in the valve hole, and a first valve chamber communicating with a first communication passage through which a fluid at a suction pressure passes and having a first valve seat;

a valve body having an intermediate communication passage communicating with the interior space and the first communication passage, a second valve part for opening and closing the valve hole by separating from and making contact with the second valve seat, a first valve part which performs opening/closing action in reverse association with the second valve part and which opens and closes communication between the intermediate communication passage and the first communication passage by separating from and making contact with the first valve seat, and a shaft part arranged in the interior space;

a pressure-sensitive body which is arranged in the interior space and extends and contracts in response to the pressure of the interior space and which has a free end part sliding with the shaft part of the valve body;

an auxiliary communication part which is arranged in the interior space and which allows communication between the interior space and the intermediate communication passage; and

a solenoid section which is mounted to the valve main body and actuates the valve body to opening/closing direction according to current.

According to the first aspect, a fluid volume flowing to the first valve chamber from the interior space is adjusted by the auxiliary communication part arranged in the interior space, thereby capable of improving operation efficiency of a variable capacity compressor.

In the capacity control valve according to a second aspect of the present invention, the auxiliary communication part has an opening area smaller than a flow passage cross-sectional area of the intermediate communication passage.

According to the second aspect, the auxiliary communication part serves as a bottleneck, and therefore the fluid flowing to the first valve chamber from the interior space is adjusted by adjusting only the auxiliary communication passage, thereby capable of improving operation efficiency of the variable capacity compressor.

In the capacity control valve according to a third aspect of the present invention, the auxiliary communication part is a hole part arranged in the valve body.

According to the third aspect, the opening area of the auxiliary communication part can be adjusted by adjusting the diameter of the hole part.

In the capacity control valve according to a fourth aspect of the present invention, the auxiliary communication part has an opening area larger than a gap part between the shaft part of the valve body and the free end part of the pressure-sensitive body.

According to the fourth aspect, even if flow passages leading to the first valve chamber from the interior space exist in parallel to each other, the fluid volume flowing to the first valve chamber from the interior space can be adjusted by adjusting only the auxiliary communication part.

In the capacity control valve according to a fifth aspect of the present invention, the valve body includes a plurality of the auxiliary communication parts.

According to the fifth aspect, the opening area of the auxiliary communication parts can be adjusted by adjusting the number of the auxiliary communication parts.

In the capacity control valve according to a sixth aspect of the present invention, the auxiliary communication part is made up of a gap part between the shaft part of the valve body and the free end part of the pressure-sensitive body.

According to the sixth aspect, the fluid volume flowing to the first valve chamber from the interior space is adjusted by adjusting the gap part between the shaft part of the valve body and the free end part of the pressure-sensitive body, thereby capable of improving operation efficiency of the variable capacity compressor.

DESCRIPTION OF EMBODIMENTS

Hereinafter referring to the drawings, modes for carrying out the present invention will be described illustratively based on an embodiment. However, the dimensions, materials, shapes, relative arrangements, and others of components described in the embodiment are not intended to limit the scope of the present invention only to them unless otherwise described explicitly.

Referring toFIG. 1toFIG. 3, a capacity control valve according to a first embodiment of the present invention will be described. InFIG. 1, 1denotes a capacity control valve. The capacity control valve1mainly consists of a valve main body10, a valve body21, a pressure-sensitive body22, and a solenoid30. Hereinafter, the main configuration of the capacity control valve1will be described.

The valve main body10is composed of a metal such as brass, iron, aluminum, or stainless steel, a synthetic resin material, or the like. The valve main body10is a hollow cylindrical member having a through hole penetrating in an axial direction, and in a compartment of the through hole, a first valve chamber14, a second valve chamber15adjacent to the first valve chamber14, and an interior space16adjacent to the second valve chamber15are sequentially arranged.

To the second valve chamber15, a second communication passage12is consecutively provided. The second communication passage12is configured to communicate with a discharge chamber (not shown) of a variable capacity compressor such that a fluid at a discharge pressure Pd can flow into the interior space16from the second valve chamber15by opening and closing of the capacity control valve1.

To the interior space16, a third communication passage13is consecutively provided. The third communication passage13is communicated with a control chamber (not shown) of the variable capacity compressor, and allows the fluid at the discharge pressure Pd flowed into the interior space16from the second valve chamber15by opening and closing of the capacity control valve1to flow out to the control chamber (crank chamber) of the variable capacity compressor and allows the fluid at a control chamber pressure Pc flowed into the interior space16to flow out to a suction chamber of the variable capacity compressor through the first valve chamber14via an intermediate communication passage26described later.

Further, in the first valve chamber14, a first communication passage11is consecutively provided. The first communication passage11allows the fluid at the control chamber pressure Pc flowed into the interior space16from the control chamber (crank chamber) of the variable capacity compressor to flow out to the suction chamber through the first valve chamber14via the intermediate communication passage26described later.

Between the second valve chamber15and the interior space16, a valve hole17having a smaller diameter than the diameters of these chambers is consecutively provided, and around the valve hole17on the second valve chamber15side, a second valve seat15ais formed. Moreover, between the first valve chamber14and the second valve chamber15, a hole part18having a smaller diameter than the diameters of these chambers is consecutively provided.

In addition, the first communication passage11, the second communication passage12, and the third communication passage13penetrate through a peripheral surface of the valve main body10respectively, for example, at two equal intervals to six equal intervals. Further, on an outer peripheral surface of the valve main body10, mounting grooves for O-rings are provided at three positions apart from each other in the axial direction. Then, to the respective mounting grooves, O rings71,72,73to seal between the valve main body10and a mounting hole (not shown) of a casing to which the valve main body10is fitted is mounted, and each of the first communication passage11, the second communication passage12, and the third communication passage13is configured as an independent flow passage.

In the interior space16, the pressure-sensitive body22is arranged. In the pressure-sensitive body22, one end part of a metallic bellows22ais sealingly coupled to a partition adjustment part3. This bellows22ais manufactured by phosphor bronze, stainless, or the like, and is designed such that its spring constant is a predetermined value. An interior of the pressure-sensitive body22is a vacuum or air exists therein. Then, with respect to an effective pressure receiving area of the bellows22aof the pressure-sensitive body22, the pressure-sensitive body24is extended and contracted according to the pressure in the interior space16, and the valve body21is configured to actuate a predetermined driving force. On a free end part side of the pressure-sensitive body22moving so as to extend and contract in response to the suction pressure in the interior space16, a free end part22cis arranged.

Then, the partition adjustment part3of the pressure-sensitive body22is sealingly fitted and fixed so as to block the interior space16of the valve main body10. In addition, if the partition adjustment part3is screwed, or fixed by a set screw (not shown), spring force of compression springs arranged in parallel within the bellows22aor of the bellows22acan be adjusted to be moved in the axial direction.

Next, the valve body21will be described. The valve body21is made of a hollow cylindrical member. The valve body21mainly consists of a fourth shaft part21kintegrally coupled to a solenoid rod36described later, a first shaft part21cprovided consecutively to the fourth shaft part21kand formed to have a diameter larger than that of the fourth shaft part21k, a labyrinth part21gprovided consecutively to the first shaft part21c, a second shaft part21bprovided consecutively to the labyrinth21g, and a third shaft part21a(a shaft part according to the present invention) provided consecutively to the second shaft part21band formed to have a diameter smaller than that of the second shaft part21b. The first shaft part21cand the second shaft part21bare arranged on the first valve chamber14side and the second valve chamber15side across the labyrinth part21g, and the labyrinth part21gslides with the hole part18formed between the first valve chamber14side and the second valve chamber15side and seals the first valve chamber14and the second valve chamber15. Thereby, the first valve chamber14and the second valve chamber15are configured as independent valve chambers.

Moreover, at an end part of the first shaft part21carranged in the first valve chamber14, a first valve part21c1is formed, and the first valve part21c1opens and closes communication between the intermediate communication passage26and the first valve chamber14by separating from and making contact with a first valve seat31cformed on an end surface of a stator core31of the solenoid30described later. At an end part of the second shaft part21barranged in the second valve chamber15, a second valve part21b1is formed, and the second valve part21b1opens and closes the valve hole17for communicating the second valve chamber15and the interior space16by separating from and making contact with the second valve seat15a.

Further, the valve body21has an intermediate communication passage26penetrating a center part thereof. The intermediate communication passage26consists of a first intermediate communication passage26apenetrating in its axial direction, and a second intermediate communication passage26bwhich is formed in the fourth shaft part21kand which communicates the first intermediate communication passage26aand the first valve chamber14.

An end part21a1of the third shaft part21aof the valve body21is relatively slidably fitted in a hole part22c1of the free end part22cof the pressure-sensitive body22. Moreover, in the third shaft part21a, an auxiliary communication part21f(or multiple auxiliary communication parts as shown inFIG. 9) made up of a hole penetrating in a radial direction is formed, and the intermediate communication passage26and the interior space16are communicated with each other by the auxiliary communication part21f. Here, an opening area S1of the auxiliary communication part21fis formed to be sufficiently larger than a gap area S2between the end part21a1of the third shaft part21aand the hole part22c1of the pressure-sensitive body22. Moreover, a fitting length of the end part21a1of the third shaft part21aand the hole part22c1of the pressure-sensitive body22is set larger than a displacement amount of the free end part22cof the pressure-sensitive body22by the pressure in the interior space16, and the fitting state is always maintained. As the flow passage leading to the intermediate communication passage26from the interior space16, two routes of a flow passage leading to the intermediate communication passage26through the auxiliary communication part21ffrom the interior space16(hereinafter, described as a “first passage”.) and a flow passage leading to the intermediate communication passage26through the gap between the end part21a1of the third shaft part21aand the hole part22c1of the pressure-sensitive body22from the interior space16(hereinafter, described as a “second passage”.) exist in parallel to each other. The opening area S1of the first flow passage is sufficiently larger than the gap area S2of the second flow passage, and therefore the fluid almost flows through the first flow passage and hardly flows through the second flow passage.

Moreover, a groove part21his formed in an end part21a1of the third shaft part21aof the valve body21, and an opening area S5of the groove part21his set larger than the gap area S2of the second flow passage. Here, if the groove part21his not provided in the end part21a1of the valve body21, from the state that an end part21eof the valve body21contacts an end surface22dof the pressure-sensitive body22, that is, the state that the area between the end part21eof the valve body21and the end surface22dof the pressure-sensitive body22is zero (FIG. 2), the area is suddenly changed when the end part21eof the valve body21is separated from the end surface22dof the pressure-sensitive body22(FIG. 1). Then, the fluid volume flowing through the second flow passage is fluctuated, and therefore the fluid volume flowing through the first flow passage cannot be maintained constant. Thus, by providing the groove part21hin the end part21a1of the valve body21, sudden change of the area by contact and separation of the end part21eof the valve body21and the end surface22dof the pressure-sensitive body22is mitigated, thereby the fluid volume flowing through the first flow passage can be maintained constant.

Next, the solenoid30will be described. The solenoid30is constituted by a solenoid rod36(a rod according to the present invention), a plunger case38, a plate34, an electromagnetic coil35, a stator core31consisting of a center post31aand a base part31darranged in an inner peripheral part of the electromagnetic coil35, a plunger32, and a biasing means28arranged between the plunger32and the center post31awhich are contained in a solenoid case33. The valve body21and the plunger32are coupled by the solenoid rod36movably fitted in a through hole31hof the stator core31, and the valve body21and the plunger32are integrally driven.

Between the center post31aof the stator core31and the plunger32, the biasing means28for biasing the plunger32so as to be separated from the stator core31is arranged. That is, the biasing means28biases the first valve part21c1so as to be in a closed state from an opened state and the second valve part21b1so as to be in an opened state from a closed state.

The plunger case38is a bottomed hollow cylindrical member whose one end is opened. An open end of the plunger case38is sealingly fixed to the base part31dof the stator core31, and between a bottom part of the plunger case38and the center post31aof the stator core31, the plunger32is movably arranged in the axial direction. Thereby, the electromagnetic coil35is sealed by the plunger case38, the base part31dof the stator core31, and the solenoid case33, and does not contact the refrigerant, and therefore it is possible to prevent reduction in insulation resistance.

The operation of the capacity control valve1having the configuration described above will be described with reference toFIG. 1toFIG. 3. In addition, the flow passage leading to the first valve chamber14through the intermediate communication passage26from the interior space16is hereinafter described as a “Pc-Ps flow passage”. Moreover, a flow passage leading to the interior space16through the valve hole17from the second valve chamber15is hereinafter described as a “Pd-Pc flow passage”.FIG. 3shows a relationship between a solenoid current and a minimum flow passage cross-sectional area of each flow passage. The dot and dash line inFIG. 3shows a relationship between the solenoid current and the minimum flow passage cross-sectional area in the Pc-Ps flow passage, and the solid line inFIG. 3shows a relationship between the solenoid current and the minimum flow passage cross-sectional area in the Pd-Pc flow passage.

As shown inFIG. 1, in a state that the electromagnetic coil35of the solenoid30is not energized, that is, in a state of a solenoid current I=0 inFIG. 3, a maximum air gap is formed between an attraction surface31bof the stator core31and an operation surface32bof the plunger32by repulsion of the biasing means28, and the second valve part21b1is opened. Therefore, in the state of the solenoid current I=0, an opening area S4of the second valve part21b1in the Pd-Pc flow passage becomes maximum. On the other hand, the opening area S1of the auxiliary communication part21fis the minimum opening area in the Pc-Ps flow passage leading to the first valve chamber14through the intermediate communication passage26from the interior space16.

Next, the state that energization to the solenoid30is started and the solenoid current is below a first current value I1(0<I<I1), that is, a control state will be described with reference toFIG. 1toFIG. 3. The control state is a state that the capacity control valve is controlled such that the pressure of the suction chamber is a set value Pset. When energization to the solenoid is started, the operation surface32bof the plunger32is gradually attracted to the attraction surface31bof the stator core31, and the opening area of the second valve part21b1is gradually narrowed in inverse proportion to the solenoid current. Therefore, as shown inFIG. 3, in the state that the solenoid current is below the first current value I1(0<I<I1), the opening area S4of the second valve part21b1is gradually narrowed, and therefore the area of the Pd-Pc flow passage is also gradually reduced according to an increase in current.

On the other hand, as shown inFIG. 3, the minimum flow passage cross-sectional area of the Pc-Ps flow passage is determined by the area of the auxiliary communication part21f, and therefore the area of the Pc-Ps flow passage is maintained at a constant value S1regardless of magnitude of current supplied to the solenoid in the control state of the solenoid. Thereby, the fluid volume flowing through the Pc-Ps flow passage can be easily adjusted to be constant. In this way, the fluid volume flowing through the Pc-Ps flow passage can be easily adjusted only by adjusting the size of the opening area S1of the auxiliary communication part21f, and therefore in the control state, a constant volume of fluid can be allowed to flow to the first valve chamber14from the interior space16, and thus the pressure of the suction chamber communicating with the first valve chamber14can be stabilized, thereby capable of improving controllability of the variable capacity compressor.

The configuration of the capacity control valve1according to the first embodiment of the present invention is described above and exhibits the following excellent effects.

By setting the opening area S1of the auxiliary communication part21fto the minimum among the Pc-Ps flow passage, the fluid volume flowing through the Pc-Ps flow passage can be easily adjusted only by adjusting the size of the opening area S1of the auxiliary communication part21f, and therefore in the control state, constant fluid can be allowed to flow to the first valve chamber14from the interior space16, and thus the pressure of the suction chamber communicating with the first valve chamber14can be stabilized, thereby capable of improving controllability of the variable capacity compressor.

Moreover, in the capacity control valve1, the pressure-sensitive body22and the valve body21are relatively displaced in the interior space16, and therefore the gap area S2exists between the end part21a1of the third shaft part21aand the hole part22c1of the pressure-sensitive body22. Therefore, as the Pc-Ps flow passage, two routes of the Pc-Ps flow passage via the first flow passage and the Pc-Ps flow passage via the second flow passage exist. Also in such a case, by sufficiently increasing the opening area S1with respect to the gap area S2, the fluid can be allowed to almost flow through the first flow passage and hardly flow through the second flow passage. Thereby, even if the Pc-Ps flow passages exist in parallel, the fluid volume flowing to the first valve chamber14from the interior space16can be adjusted only by adjusting the size of the opening area S1of the auxiliary communication part21f.

Hereinbefore, although the embodiment of the present invention has been described by the drawings, its specific configuration is not limited to the embodiment, and any changes and additions made without departing from the scope of the present invention are included in the present invention.

In the above embodiment, by providing the groove part21hin the end part21a1of the third shaft part21aof the valve body21, sudden change of the area by contact and separation of the end part21eof the valve body21and the end surface22dof the pressure-sensitive body22is mitigated, thereby a flow rate flowing to the first valve chamber from the interior space16is maintained constant. However, the mitigation method for the change of flow rate by contact and separation of the end part21eof the valve body21and the end surface22dof the pressure-sensitive body22is not limited thereto.

For example, as shown inFIG. 4, by providing an opening hole41jin an end part41a1of a valve body41, even if the state that an end part41eof the valve body41and the end surface22dof the pressure-sensitive body22are separated from each other as shown inFIG. 4Aand the state that the end part41eof the valve body41and the end surface22dof the pressure-sensitive body22are in contact with each other as shown inFIG. 4Bare repeated, the change of flow rate can be mitigated.

Further, as another modification, by blocking an opening part of the end part21a1of the valve body21with a plug or the like, the fluid volume flowing through the Pc-Ps flow passage via the second flow passage can be set to zero. In this case, a fluid draining hole or the like is provided such that an enclosed space is not formed between the end part21a1of the valve body21and the free end part22cof the pressure-sensitive body22, thereby it is prevented from being resistance when the valve body21and the pressure-sensitive body22are relatively displaced.

Moreover, in the above embodiment, although the fluid volume flowing through the Pc-Ps flow passage is adjusted by adjusting the opening area S1of the auxiliary communication part21f, the minimum opening area of the Pc-Ps flow passage may be adjusted without providing the auxiliary communication part21f. For example, as shown inFIG. 5, by adjusting the gap area between an end part51a1of a valve body51and the hole part22c1of the pressure-sensitive body22, the fluid volume flowing through the Pc-Ps flow passage may be adjusted to be constant. Also in this case, by providing an opening hole51jin the end part51a1of the valve body51, even if the state that an end part51eof the valve body51and the end surface22dof the pressure-sensitive body22are separated from each other as shown inFIG. 5Aand the state that the end part51eof the valve body51and the end surface22dof the pressure-sensitive body22are in contact with each other as shown inFIG. 5Bare repeated, the change of flow rate can be prevented.

REFERENCE SIGNS LIST

1 capacity control valve

3partition adjustment part

10valve main body

11first communication passage

12second communication passage

13third communication passage

15asecond valve seat

21athird shaft part

21bsecond shaft part

21b1second valve part

21cfirst shaft part

21c1first valve part

21fauxiliary communication part

22cfree end part

26intermediate communication passage

31cfirst valve seat

Pd discharge chamber pressure

Ps suction chamber pressure

Pc control chamber pressure

S1opening area of auxiliary communication part

S2gap area between end part of valve body and hole part of pressure-sensitive body

S4opening area between second valve part and second valve seat

S5opening area of groove part