WO2006006560A1

WO2006006560A1 - Capacity control valve for clutchless variable displacement swash plate-type compressor

Info

Publication number: WO2006006560A1
Application number: PCT/JP2005/012760
Authority: WO
Inventors: Yukihiko Taguchi
Original assignee: Sanden Corporation
Priority date: 2004-07-13
Filing date: 2005-07-11
Publication date: 2006-01-19
Also published as: EP1775470A1; US20070183904A1; DE602005013969D1; JP2006029150A; EP1775470B1; CN1985090A; CN100507267C; EP1775470A4

Abstract

A capacity control valve for a clutchless variable displacement swash plate-type compressor, in which the discharge capacity of the compressor is controlled by opening and closing a communication path between a discharge chamber and a crank chamber. The capacity control valve has a valve hole (106) formed in the communication path and always communicating with the discharge chamber, an inside control valve (100) for opening and closing the valve hole (106) by a valve body (112) operated in response to expansion and contraction of a pressure sensing member (109) for sensing a suction pressure, and an operation switchover device (120) connected to the inside control valve and switching the inside control valve between an operation state where the valve body opens and closes the valve hole in response to the expansion and contraction of the pressure sensing member and a non-operation state where the valve body opens the valve hole independent of the expansion and retraction of the pressure sensing member. In this capacity control valve, because a discharge pressure Pd acts on both the valve body (112) and a pressure sensing rod (110), that force of the discharge pressure Pd which urges the valve body (112) in a valve opening direction is (Sr - Sv)Pd. The capacity control valve (2) can be made smaller than conventional capacity control valves because (Sr - Sv) is very small.

Description

Specification

Capacity control valve for clutchless variable displacement swash plate compressor

Technical field

The present invention relates to a capacity control valve for a clutchless variable displacement swash plate compressor that is directly connected to a drive source without a clutch.

Background art

[0002] Capacity control of a clutchless variable displacement swash plate compressor that opens and closes a valve hole formed in a communication path between a discharge chamber and a crank chamber of a variable displacement swash plate compressor to control the discharge capacity of the compressor A valve hole that communicates with the crank chamber at all times, an internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of a pressure-sensitive member that senses suction pressure, and an internal control valve The internal control valve is set to an operating state in which the valve body opens and closes the valve hole in response to expansion and contraction of the pressure-sensitive member, and an inoperative state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member. Patent Document 1 discloses a capacity control valve that includes an electromagnetic solenoid for switching and controls the discharge capacity so that the suction pressure and the discharge pressure have a predetermined correlation. Patent Document 1 describes that in the region of Pd> Pd, the capacity control characteristic is expressed by the following equation.

0

Ps = P-(Pd-Pc) S / S

0 1 2

here,

Pd: discharge pressure,

Pc: Crank chamber pressure,

Ps: suction pressure,

P: Equivalent internal pressure of bellows,

0

s: valve hole cross-sectional area,

1

s: Bellows effective cross-sectional area,

2

It is.

Patent Document 1: Japanese Patent Laid-Open No. 7-127566

Disclosure of the invention

Problems to be solved by the invention However, the capacity control valve disclosed in Patent Document 1 has the following problems. Since the discharge pressure Pd biases the valve body in the closing direction, in order to demagnetize the electromagnetic solenoid and force the valve body to open, the force of the opening panel of the electromagnetic solenoid must be (Pd-Pc) S or higher.

1 Must be set. In order to forcibly open the valve body in the region where the discharge pressure Pd is high, it is necessary to use an open panel with a large spring force. The electromagnetic core is excited and piled on the panel force of the open panel to attract the movable iron core. It is necessary to generate a large electromagnetic force to increase the size of the electromagnetic solenoid.

In view of the above problems, an object of the present invention is to provide a capacity control valve for a clutchless variable capacity swash plate compressor that can be made smaller than the capacity control valve disclosed in Patent Document 1. There is to do.

Means for solving the problem

In order to solve the above problems, a capacity control valve of a clutchless variable displacement swash plate compressor according to the present invention opens and closes a communication path between a discharge chamber and a crank chamber of the variable displacement swash plate compressor. A capacity control valve of a clutchless variable capacity swash plate type compressor for controlling the discharge capacity of the variable capacity swash plate compressor, a valve hole formed in the communication passage and always communicating with the discharge chamber, and a suction pressure An internal control valve that opens and closes the valve hole by a valve element that operates in response to expansion and contraction of the pressure-sensitive member, and is connected to the internal control valve, and the internal control valve is used to expand and contract the pressure-sensitive member. In response, the valve body has an operation switching device that switches between an operation state in which the valve body opens and closes the valve hole and a non-operation state in which the valve body opens the valve hole regardless of expansion and contraction of the pressure-sensitive member. It consists of the capacity | capacitance control valve characterized by this.

[0006] In the present invention, since the valve hole is always in communication with the discharge chamber, the force by which the discharge pressure Pd urges the valve body in the closing direction is reduced compared to the capacity control valve of Patent Document 1 described above. The switching device that forcibly opens the valve disc can be downsized.

In such a capacity control valve according to the present invention, the operation switching device has an electromagnetic solenoid, and when the electromagnetic solenoid is energized, the internal control valve is activated, and the electromagnetic solenoid is demagnetized. It is preferable that the internal control valve is configured to be in an inactive state when it is! With this configuration, the variable capacity swash plate compressor can be switched between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid. The control device for the variable capacity swash plate compressor is simplified.

[0008] Further, in the capacity control valve according to the present invention, the electromagnetic solenoid positions the internal control valve in the operating position when the electromagnetic solenoid is excited, and the movable iron core connected to the internal control valve. It is preferable to have a positioning member. By arranging the positioning member, it is possible to position the internal control valve to the operating position by exciting the electromagnetic solenoid, and it is possible to switch to the operating state of the variable capacity swash plate compressor by exciting the electromagnetic solenoid. .

[0009] Further, in the capacity control valve according to the present invention, it is preferable that the positioning member is formed by one end of the pressure-sensitive member and an end surface of the case of the electromagnetic solenoid. Positioning member force By forming one end of the pressure-sensitive member and the case of the electromagnetic solenoid, it is not necessary to separately provide a special positioning member, and the structure of the capacity control valve is simplified.

[0010] Further, in the capacity control valve according to the present invention, the electromagnetic solenoid has an open panel that urges the movable iron core in a direction away from the fixed iron core force. Preferably, the control valve is deactivated. If the electromagnetic solenoid release panel renders the internal control valve inactive, there is no need to separately provide a panel for disabling the internal control valve, and the structure of the capacity control valve is simplified.

[0011] In a preferred aspect of the present invention, the internal control valve has a pressure-sensitive rod formed in the valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body. The cross-sectional area of the pressure-sensitive rod is set larger than the cross-sectional area of the valve hole. With this configuration, since the suction pressure decreases when the discharge pressure increases, the suction pressure decreases. Therefore, the discharge capacity increases in a high heat load region where the discharge pressure is high. Therefore, the cooling device provided with the variable capacity swash plate compressor having the capacity control valve does not deteriorate the cooling performance even in the high heat load region where the discharge pressure is high.

Alternatively, in a preferred aspect of the present invention, the internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body. The cross-sectional area of the pressure-sensitive rod is set smaller than the cross-sectional area of the valve hole. With this configuration, the control characteristic is such that the suction pressure increases as the discharge pressure increases. Therefore, the discharge capacity is reduced in the region where the discharge pressure is high. As a result, the occurrence of a situation where the compressor operates with an excessive load is suppressed.

The invention's effect

[0013] In the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention, the valve hole is always in communication with the discharge chamber, so that the force by which the discharge pressure urges the valve body in the closing direction is provided. Compared with the capacity control valve of Patent Document 1, the switching device for forcibly opening the valve body can be made smaller than the capacity control valve of Patent Document 1. Therefore, the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention can be reduced in size compared to the capacity control valve of Patent Document 1.

Brief Description of Drawings

FIG. 1 is a longitudinal sectional view of a clutchless variable displacement swash plate compressor provided with a displacement control valve according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view of a capacity control valve according to an embodiment of the present invention, and FIGS. 2 (A) and 2 (B) are diagrams showing the operation of the internal control valve when the electromagnetic solenoid is excited. FIG. 2 (C) is a diagram showing the operation of the internal control valve when the electromagnetic solenoid is demagnetized, and FIG. 2 (D) is an enlarged partial sectional view of the internal control valve.

FIG. 3 is a control characteristic diagram of a displacement control valve according to an embodiment of the present invention, FIG. 3 (A) is a control characteristic diagram when Sr> Sv, and FIG. 3 (B) is a control characteristic when Sr> Sv. FIG.

Explanation of symbols

[0015] 1: Clutchless variable displacement swash plate compressor

2: Capacity control valve

17: Crank chamber

21: Inhalation chamber

22: Discharge chamber

26: recess

100: Internal control valve

101: Valve housing

102: Pressure sensitive chamber 103: Valve room

106: Valve hole

109: Bellows assembly

110: Pressure sensitive rod

112: Valve

120: Electromagnetic solenoid

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, preferred embodiments of the capacity control valve of the clutchless variable capacity swash plate compressor according to the present invention will be described with reference to the drawings.

1 and 2 show a variable displacement swash plate compressor provided with a displacement control valve according to an embodiment of the present invention. As shown in FIG. 1, a variable capacity swash plate compressor 1 includes a main shaft 10, a rotor 11 fixed to the main shaft 10, and a swash plate 12 supported on the main shaft 10 so that the tilt angle is variable. The swash plate 12 is connected to the rotor 11 via a link mechanism 13 that allows the tilt angle of the swash plate 12 to be changed, and rotates in synchronization with the rotor 11 and the main shaft 10. The piston 15 is engaged with the swash plate 12 via a pair of slides 14 that are in sliding contact with the outer peripheral edge of the swash plate 12. The piston 15 is inserted into a cylinder bore 16a formed in the cylinder block 16 !. A plurality of pistons 15 are arranged around the main shaft 10 at intervals in the circumferential direction.

A crank chamber 17 that houses the main shaft 10, the rotor 11, and the swash plate 12 is formed by a cylinder block 16 and a dish-shaped front housing 18. The main shaft 10 extends through the front housing 18 to the outside. A shaft sealing member 19 for sealing the front housing penetrating portion of the main shaft 10 is disposed in the front housing 18. A pulley 20 is fixed to the tip of the main shaft 10. When the variable displacement swash plate compressor 1 is a compressor used for a refrigeration site of a vehicle air conditioner, the pulley 20 is connected to a vehicle engine (not shown) via a belt (not shown), for example. The

A cylinder head 23 that forms a suction chamber 21 and a discharge chamber 22 is disposed at a position opposite to the front housing 18 of the cylinder block 16. The suction chamber 21 is connected to an external circuit, for example, an evaporator (not shown) provided in the refrigeration cycle of the vehicle air conditioner via a suction port (not shown). The discharge chamber 22 is connected to a discharge port (not shown). In addition, it is connected to an external circuit, for example, a condenser (not shown) provided in the refrigeration cycle of the vehicle air conditioner.

[0019] A valve plate 24 is formed between the cylinder block 16 and the cylinder head 23. The valve plate 24 has a suction port 2la communicating with the cylinder bore 16a and a discharge port 22a. A discharge valve and a suction valve are mounted on the valve plate 24 (not shown). The crank chamber 17 and the suction chamber 21 communicate with each other through an orifice hole 24 a formed in the valve plate 24.

[0020] The front housing 18, the cylinder block 16, the valve plate 24, and the cylinder head 23 are integrated by a plurality of through bolts 25 that are spaced apart from each other along a circumference centered on the main shaft 10. It is concluded.

A capacity control valve 2 for controlling the discharge capacity of the variable capacity swash plate compressor 1 is fitted and fixed in a recess 26 formed in the cylinder head 23 adjacent to the discharge chamber 22. As shown in FIGS. 1 and 2, the capacity control valve 2 includes an internal control valve 100 and an electromagnetic solenoid 120.

The internal control valve 100 has a cylindrical valve housing 101. Two O-rings 101a and 101b closely fitted to the outer peripheral surface of the valve housing 101 and one O-ring 121a tightly fitted to the outer peripheral surface of the case 121 of the electromagnetic solenoid 120 Around the housing 101, three closed spaces 27a, 27b, 27c are formed.

The valve housing 101 is formed with a transverse partition wall 104 that divides the internal space of the valve housing 101 into a pressure-sensitive chamber 102 on one end side and a valve chamber 103 on the other end side. The transverse partition wall 104 is formed with a rod through hole 105 communicating with the pressure sensing chamber 102 and a valve hole 106 communicating with the valve chamber 103. The rod through hole 105 and the valve hole 106 are arranged coaxially and communicate with each other. A communication hole 107 is formed in the horizontal partition wall 104 so as to pass through the horizontal partition wall 104 in the radial direction through a communication portion between the rod through hole 105 and the valve hole 106.

[0024] The pressure sensing chamber 102 communicates with the suction chamber 21 via a communication hole 108 formed in the peripheral wall of the valve housing 101, a closed space 27c, and a communication passage 23a formed in the cylinder head 23. ing . The communication hole 107 communicates with the discharge chamber 22 via a closed space 27b and a communication passage 23b formed in the cylinder head 23. The valve hole 106 communicating with the communication hole 107 is always in communication with the discharge chamber 22. The valve chamber 103 communicates with the crank chamber 17 through a closed space 27a, a communication path 23c formed in the cylinder head 23, and a communication path 16b formed in the cylinder block 16. ing.

[0025] In the pressure sensing chamber 102, a base assembly 109 functioning as a pressure sensing device in which the inside is evacuated and the panel is arranged is disposed. One end of the pressure sensitive rod 110 is connected to one end 109a of the bellows assembly 109, and the other end is slidably inserted into the rod through hole 105. A small-diameter rod 111 extending from the other end of the pressure-sensitive rod 110 is passed through the valve hole 106 so as to be freely movable. A valve body 112 connected to the end of the small-diameter rod 111 is disposed in the valve chamber 103. A panel 113 that urges the valve body 112 toward the valve hole 106 is disposed in the valve chamber 103. The internal control valve 100 is formed by a series of structures from the valve housing 101 to the panel 113.

The end of the valve housing 101 of the internal control valve 100 on the pressure sensing chamber 102 side is press-fitted and fixed to one end of the case 121 of the electromagnetic solenoid 120. As described above, the O-ring 121a that forms the closed space 27c is fitted to the outer peripheral surface on one end side of the case 121.

[0027] The electromagnetic solenoid 120 includes a fixed iron core 122 disposed in the case 121, a movable iron core 123 disposed with one end facing the one end of the fixed iron core 122, and the movable iron core 123 from the fixed iron core. It has an open panel 124 that urges in a separating direction, and an electromagnetic coil 125 that surrounds the fixed iron core 122 and the movable iron core 123. The space for accommodating the movable iron core 123 communicates with the pressure sensing chamber 102 and is at the same pressure as the pressure sensing chamber 102. The other end 109b of the bellows assembly 109 is connected to the other end of the movable iron core 123. The other end 109b is disposed so as to be engageable with the end surface inner edge portion 121a in the vicinity of the one end of the case 121 of the electromagnetic solenoid 120.

Next, the operation of the capacity control valve 2 will be described.

When the clutchless variable displacement swash plate compressor 1 is operated in the capacity control state, the electromagnetic coil 125 is excited to attach the open panel 124 as shown in FIGS. 2 (A) and 2 (B). Move the movable iron core 123 toward the fixed iron core 122 against the force, and bring the other end 10 9b of the bellows assembly 109 into contact with the inner edge 12 lb of the end face 121 of the electromagnetic solenoid 120. Position it in the operating position, and consequently position the internal control valve 100 in the operating position. The internal control valve 100 enters an operation state in which the valve body 112 opens and closes the valve hole 106 in response to expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member.

[0029] When the internal control valve 100 is in an operating state, if the suction pressure is lower than the set value, the flow rate is reduced as shown in FIG. As shown in Fig. 1, the bellows assembly 109 extends, and the valve body 112 connected to the bellows thread and solid 109 via the pressure-sensitive rod 110 and the small diameter rod 111 responds to the expansion of the bellows thread and solid 109. Then, the valve hole 106 is opened. From the discharge chamber 22, high-pressure refrigerant gas is supplied to the crank chamber 17 through the communication hole 23b, the communication hole 107, the valve hole 106, the valve chamber 103, the closed space 27a, the communication path 23c, and the communication path 16b. . The crank chamber pressure increases, the swash plate tilt angle decreases, the discharge capacity of the variable capacity swash plate compressor 1 decreases, and the suction pressure gradually increases.

[0030] When the suction pressure exceeds the set value, the bellows assembly 109 contracts and is connected to the bellows assembly 109 via the pressure-sensitive rod 110 and the small-diameter rod 111, as shown in FIG. In response to the contraction of the bellows assembly 109, the valve hole 106 is closed. Thereby, the supply of the high-pressure refrigerant gas from the discharge chamber 22 to the crank chamber 17 is stopped. The orifice passage 24a has a sufficient cross-sectional area to discharge blow-by gas leaking from the cylinder bore 16a to the crank chamber 17 to the suction chamber 21 when the piston 15 compresses the refrigerant gas in the cylinder bore 16a. The crank chamber pressure gradually decreases. When the crank chamber pressure decreases, the swash plate inclination angle increases, the discharge capacity of the variable displacement swash plate compressor 1 increases!], And the suction pressure gradually decreases.

As described above, by the operation of the internal control valve 100, the opening and closing of the valve hole 106 is repeated so that the suction pressure becomes a set value, and the discharge capacity of the variable capacity swash plate compressor 1 is variably controlled.

When the electromagnetic coil 125 is demagnetized, the other end 109b of the bellows assembly 109 receives the biasing force of the open panel 124 and the inner edge 121b of the end surface of the case 121 of the electromagnetic solenoid 120 as shown in FIG. , The bellows assembly 109 is positioned in the inoperative position and the internal control valve 100 is positioned in the inoperative position. As a result, the internal control valve 100 is in an inoperative state in which the valve body 112 opens the valve hole 106 regardless of the expansion and contraction of the bellows assembly 109 that is a pressure-sensitive member. The lift amount of the valve body 112 is regulated by the end 109 a of the bellows assembly 109 coming into contact with the horizontal partition wall 104. In this state, high-pressure refrigerant gas is supplied from the discharge chamber 22 to the crank chamber 17, the crank chamber pressure increases, the swash plate inclination decreases to the minimum inclination, and the discharge capacity of the variable capacity swash plate compressor 1 increases. Reduced to minimum capacity and maintained at minimum capacity. Since the discharge capacity of the variable capacity swash plate compressor 1 can be minimized by demagnetizing the electromagnetic coil 125, the capacity control valve 2 is connected to an external drive source without a clutch. Can be used as a variable capacity swash plate compressor.

[0033] The control characteristic of the displacement control valve 2 is expressed by the following equation (1).

Ps = — (Sr-Sv) Pd / {Sb- (Sr— Sv)} + (f + a Sv-F) / {Sb- (Sr— Sv)} (1)

here,

Pd: discharge pressure,

a: Pressure difference between crank chamber and suction chamber,

F: Energizing force of bellows assembly 109 with a panel inside,

f: Power of panel 113,

Sb: effective cross-sectional area of bellows assembly 109,

Sv: cross-sectional area of valve hole 106,

Sr: Cross-sectional area of pressure-sensitive rod 110,

It is.

In the capacity control valve 2, the discharge pressure Pd acts on the valve body 112 and the pressure-sensitive rod 110, so the force that the discharge pressure Pd urges in the direction to close the valve body 112 is (Sr− Sv) Pd. Since (Sr−Sv) is very small, (Sr−Sv) Pd is much smaller than PdSv in Patent Document 1 described above. Therefore, the capacity control valve 2 can be reduced in size compared to the capacity control valve of Patent Document 1.

[0035] In the displacement control valve of Patent Document 1 described above, the slope of the correlation line of Ps with respect to Pd is S ZS.

1 2 1

The inclination cannot be changed without changing the cross-sectional area s. That is, capacity system

2

The characteristics cannot be easily changed. On the other hand, in the capacity control valve 2, the slope of the correlation line of Ps with respect to Pd is-(Sr-Sv) Z {Sb- (Sr-Sv)}, so if the cross-sectional area Sr of the pressure-sensitive rod is changed, The inclination can be changed without changing the cross sectional area Sv of the valve hole and the effective cross sectional area Sb of the bellows assembly, which are the basic specifications of the capacity control valve 2. Therefore, the capacity control characteristic can be easily changed.

[0036] In the capacity control valve of Patent Document 1 described above, if it is attempted to downsize the capacity control valve without changing the slope of the correlation line of Ps with respect to Pd and thus without changing the capacity control characteristic, S , S must be simultaneously reduced. Small cross-sectional area S of valve hole As a result, the flow rate of the high-pressure refrigerant gas flowing into the crank chamber through the valve hole after forcibly opening the valve body decreases, and the time required for the capacity of the swash plate compressor to increase to the minimum capacity increases. Capacity control performance deteriorates. Therefore, downsizing is difficult. On the other hand, in the capacity control valve 2, the slope of the correlation line of Ps with respect to Pd is — (Sr—Sv) Z {Sb— (Sr—Sv)}, so the cross sectional area Sv of the valve hole 106 must be changed. By changing the cross-sectional area Sr of the pressure-sensitive rod 110, the bellows effective cross-sectional area Sb can be reduced without changing the slope of the correlation line of Ps with respect to Pd. Therefore, downsizing is easy.

[0037] The capacity control valve 2 can switch the clutchless variable capacity swash plate compressor 1 between the capacity control state and the minimum capacity state by exciting and demagnetizing the electromagnetic solenoid 120. If used, the control device of the variable capacity swash plate compressor 1 is simplified.

[0038] In the capacity control valve 2, since the positioning member constituted by the other end 109b of the bellows assembly 109 and the end surface inner edge 121b of the case 121 of the electromagnetic solenoid 120 is disposed, Positioning of the internal control valve 100 to the operating position by excitation is possible, and switching to the capacity control state of the variable displacement swash plate compressor 1 by excitation of the electromagnetic solenoid 120 is possible. In the displacement control valve 2, the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge 121b of the end surface 121 of the case 121 of the electromagnetic solenoid 120, so there is no need to separately provide a special positioning member. The valve structure has been simplified.

[0039] Further, in the capacity control valve 2, since the open panel 124 of the electromagnetic solenoid 120 puts the internal control valve 100 into the non-operating state, it is necessary to separately arrange a panel for putting the internal control valve 100 into the non-operating state. The valve structure has been simplified.

[0040] In the displacement control valve 2, when the cross-sectional area Sr of the pressure-sensitive rod 110 is set larger than the cross-sectional area Sv of the valve hole, as shown in Fig. 3 (A), the suction is increased when the discharge pressure Pd increases. Since the control characteristic is such that the pressure Ps decreases, the discharge capacity of the variable capacity swash plate compressor 1 increases in the high discharge pressure and high heat load range. Therefore, the cooling device provided with the variable capacity swash plate compressor 1 having the capacity control valve 2 does not deteriorate the cooling performance even in the high heat load region where the discharge pressure is high.

[0041] On the other hand, when the cross sectional area Sr of the pressure sensitive rod 110 is set smaller than the valve hole cross sectional area Sv in the displacement control valve 2, the discharge pressure Pd increases as shown in FIG. 3 (B). Then suction pressure Ps Since the control characteristics increase, the variable capacity swash plate compressor is used in the high discharge pressure range.

1 discharge capacity is reduced. As a result, the variable capacity swash plate compressor 1 is operated with an excessive load, and the occurrence of damage is suppressed.

In the above embodiment, the positioning member is formed by the other end 109b of the bellows assembly 109 and the inner edge portion 12 lb of the end surface 121 of the electromagnetic solenoid 120. However, the adsorbing portion of the movable iron core 123 and the fixed iron core 122 A positioning member may be formed. Furthermore, an adjustment member that adjusts the urging force of the panel 113 from the outside may be provided.

Industrial applicability

[0043] The present invention can be widely used for a capacity control valve of a clutchless variable capacity swash plate compressor. In particular, it is suitable as a capacity control valve for a compressor provided in a refrigeration cycle of a vehicle air conditioner.

Claims

The scope of the claims

[1] The capacity control valve of the clutchless variable displacement swash plate compressor that controls the discharge capacity of the variable displacement swash plate compressor by opening and closing the communication path between the discharge chamber and the crank chamber of the variable displacement swash plate compressor An internal control that opens and closes the valve hole by a valve hole that is formed in the communication passage and communicates with the discharge chamber at all times, and a valve element that operates in response to expansion and contraction of a pressure-sensitive member that senses suction pressure. A valve and an internal control valve connected to the internal control valve. The internal control valve is related to an operating state in which the valve element opens and closes the valve hole in response to expansion and contraction of the pressure sensitive member, and expansion and contraction of the pressure sensitive member. And a switching control device for switching the valve body to a non-operating state in which the valve hole is opened. A capacity control valve for a clutchless variable displacement swash plate compressor.

[2] The operation switching device has an electromagnetic solenoid, and when the electromagnetic solenoid is energized, the internal control valve is activated, and when the electromagnetic solenoid is demagnetized, the internal control valve is deactivated. The capacity control valve for a clutchless variable capacity swash plate compressor according to claim 1, wherein:

[3] The electromagnetic solenoid includes a movable iron core connected to the internal control valve, and a positioning member that positions the internal control valve in an operating position when the electromagnetic solenoid is excited. A capacity control valve for a clutchless variable capacity swash plate compressor according to claim 2.

[4] The capacity of the clutchless variable displacement swash plate compressor according to claim 3, wherein the positioning member is formed by one end of the pressure-sensitive member and an end face of the case of the electromagnetic solenoid. Control valve.

[5] The electromagnetic solenoid has an open panel that urges the movable iron core in a direction away from the fixed iron core force. When the electromagnetic solenoid is demagnetized, the internal control valve is deactivated by the open panel. The capacity control valve for a clutchless variable capacity swash plate compressor according to any one of claims 2 to 4, wherein

[6] The internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted into a hole communicating with the valve hole and connected to the valve body. 6. The capacity control valve for a clutchless variable displacement swash plate compressor according to any one of claims 1 to 5, wherein the area is set to be larger than a valve hole cross-sectional area. [7] The internal control valve has a pressure-sensitive rod formed in a valve housing and slidably inserted in a hole communicating with the valve hole and connected to the valve body. 6. The capacity control valve for a clutchless variable capacity swash plate compressor according to any one of claims 1 to 5, wherein the area is set smaller than a valve hole cross-sectional area.