CAPACITY CONTROL VALVE

Description

Technical Field

[0001] The present invention relates to a capacity control valve according to the pre-characterizing part of claim 1, in particular to a capacity control valve that controls the capacity or the pressure of a working fluid so that the capacity or the pressure thereof can be varied, and, more particularly, to a capacity control valve that controls the pressure of a control chamber of, for example, a capacity-variable compressor used in an air-conditioning system of, for example, an automobile.

Background Art

[0002] A swash plate type capacity-variable compressor used in an air-conditioning system of an automobile or the like is provided with a rotary shaft that is rotated and driven by a rotation force of an engine, a swash plate connected to the rotary shaft with a variable inclination angle, a piston for compression that is connected to the swash plate and the like. This capacity-variable compressor controls the amount of refrigerant gas discharged while changing the stroke of the piston by changing the inclination angle of the swash plate.

[0003] The inclination angle of the swash plate canbe continuously changed by adjusting a pressure balance acting on both faces of the piston through appropriate control of a pressure in a control chamber using a capacity control valve opening/closing -driven by an electro-magnetic force while using a suction pressure of a suction chamber into which a refrigerant gas is sucked, a discharge pressure of a discharge chamber from which the refrigerant gas pressurized by a piston is discharged, and a control chamber pressure of the control chamber (crank chamber) in which the swash plate is accommodated.

[0004] The capacity control valve includes a lead-in passage through which the discharge chamber and the control chamber are allowed to communicate with each other and through which a discharge fluid (refrigerant gas) is introduced into the control chamber, a first valve chamber formed in an enlarged shape at a place on the lead-in passage, a lead-out passage through which the suction chamber and the control chamber are allowed to communicate with each other and through which a fluid (e. g., refrigerant gas or blowby gas) is led out from the control chamber, a second valve chamber formed in an enlarged shape at a place on the lead-out passage, a valve body in which a first valve part that is disposed in the first valve chamber and that opens and closes the lead-in passage and a second valve part that is disposed in the second valve chamber and that opens and closes the lead-out passage are reciprocated together, and, at the same time, perform an open-close operation in mutually opposite directions (i.e., the second valve part is fully closed (or fully opened) when the first valve part is fully opened (or fully closed)), and a solenoid that operates the valve body, which is formed so that a discharge pressure acts on one side (first valve part side) of the valve body and a suction pressure acts on an opposite side (second valve part side) thereof, with an electromagnetic force so as to perform an open-close operation (see, for example, EP 1 363 023 A2, and JP 2004 116407 A).

[0005] Further, in this capacity control valve, a control-chamber pressure acts on the first valve part that receives a discharge pressure from an opposite side, and a control-chamber pressure acts on the second valve part that receives a suction pressure from an opposite side. With this structure, the influence of the control-chamber pressure on the valve body is counterbalanced, and only a differential pressure between the discharge pressure and the suction pressure is caused to act on the valve body so as to control the control-chamber pressure.

[0006] By the way, attention is paid to carbon dioxide (CO₂) to be used as a refrigerant gas serving as the replacement of a fron gas. The carbon dioxide is about ten times as great as the existing refrigerant gas in the pressure area (i.e., in pressure fluctuation width) to be used, and a differential pressure acting on the valve body becomes great because of a structure in which the two passages (i.e., the lead-in passage through which a discharge pressure and a control-chamber pressure are allowed to communicate with each other and the lead-out passage through which a suction pressure and a control-chamber pressure are allowed to communicate with each other) are opened and closed. As a result, when the valve body controls a fluid flow (i.e., flow rate), a differential pressure between the discharge pressure and the control-chamber pressure becomes greater than a differential pressure between the suction pressure and the control-chamber pressure, and hence the fluid flow of the lead-out passage opened and closed by the second valve part is a tendency to become shorter than the fluid flow of the lead-in passage opened and closed by the first valve part.

[0007] Therefore, to eliminate this tendency, there is a need to make the passage area of the lead-out passage opened and closed by the second valve part (and the opening area of a valve seat) greater than the passage area (opening area) of the lead-in passage opened and closedby the first valve part. If the opening area (passage area) is increased, a differential pressure caused by the control-chamber pressure is increased. Therefore, to maintain the balance of a force exerted on the valve body, the driving force of the solenoid by which the valve body is driven is required to be increased, in other words, the solenoid is required to be enlarged. This brings about an increase in device size and an increase in cost.

[0008] EP 1 612 420 A2 describes a displacement control valve for a variable displacement compressor. In a housing of the compressor, a swash plate is supported on a rotary shaft, and is permitted to incline with respect to the rotary shaft. A suction chamber and a discharge chamber are defined in the housing. A suction passage for guiding refrigerant into the suction chamber and a discharge passage for discharging refrigerant from the discharge chamber are connected to each other by an external refrigerant circuit. An electromagnetic displacement control valve is installed in the housing, which includes a solenoid and within a chamber a first valve body integrally formed with a transmission rod and a second valve body slidably fitted around the transmission rod. The first valve body is configured to close a first valve hole and the second valve body is configured to close a second valve hole. A compression spring urges the second valve body towards a closing position.

[0009] EP 1 279 831 describes a variable displacement compressor including a valve element for controlling refrigerant flow from a discharge chamber into a pressure-regulating chamber. The valve comprises two integrally formed valve elements operating in an interlocked fashion. A central shaft is axially guided in a central opening. If no control current is supplied to a solenoid coil, a first valve element fully opens a first valve seat, whereas a second valve element fully closes a second valve seat. At a maximum current supplied to the solenoid coil, the first valve element fully closes the first valve seat and the second valve element fully opens the second valve seat.

Disclosure of Invention

Problems to be solved by the Invention

[0010] The present invention has been made in consideration of these circumstances. It is therefore an object of the present invention to provide a capacity control valve capable of minimizing the influence of a control-chamber pressure on a valve body, capable of performing capacity control more stably, and capable of achieving a reduction in, for example, solenoid size and a reduction in cost while securing a fluid flow obtained when a control chamber and a suction chamber are controlled even if a refrigerant gas having a large pressure area is used.

Means for solving the Problems

[0011] A capacity control valve of the present invention is adapted to be applied to a compressor including a discharge chamber for discharging a fluid, a suction chamber for sucking in the fluid, and a control chamber for controlling a discharge amount of the fluid. It includes a first communication path (lead-in passage) through which the discharge chamber and the control chamber are allowed to communicate with each other and through which the fluid is introduced into the control chamber; a second communication path (lead-out passage) through which the suction chamber and the control chamber are allowed to communicate with each other and through which the fluid is led out from the control chamber; a first valve chamber formed midway of the first communication path ; a second valve chamber formed midway of the second communication path; a valve body formed integrally with a first valve part that is disposed in the first valve chamber and opens and closes the first communication path and a second valve part that is disposed in the second valve chamber and opens and closes the second communication path. A pressure receiving part is disposed at an end on an opposite side of the first valve part, with the second valve part placed therebetween.

[0012] The capacity control valve further comprises a solenoid that exerts an electro-magnetic driving force on the pressure receiving part of the valve body via a driving rod that is brought into contact with the pressure receiving part. In the capacity control valve, a body accommodates the valve body, and defines the first communication path, the second communication path, the first valve chamber, the second valve chamber, and the guide path.

[0013] According to the invention, the valve body is configured to act such that when moving in one direction, the first valve part is separated from a first valve seat so as to open a lead-in first communication path extending towards the valve seat. At the same time, the second valve part is seated on a second valve seat so as to close a lead-out communication path extending from the second valve seat. When moving in another direction, the second valve part is separated from the second valve seat so as to open the lead-out second communication path. At the same time, the first valve part is seated on the first valve seat so as to close the lead-in first communication path.

[0014] A pressure receiving area of the pressure receiving part is formed to become equal to a difference between a pressure receiving area of the second valve part in the second communication path and a pressure receiving area of the first valve part in the first communication path extending toward the first valve seat.

[0015] According to this structure, when the pressure (control-chamber pressure) of the inside of the control chamber is increased, the second valve part closes the lead-out passage, and prevents a fluid from being suctioned from the control chamber to the suction chamber, whereas the first valve part opens the lead-in passage, and leads a discharge fluid (or discharge pressure) from the discharge chamber into the control chamber. On the other side, when the pressure (control-chamber pressure) of the inside of the control chamber is decreased, the first valve part closes the lead-in passage, and prevents a discharge fluid (or discharge pressure) from being introduced from the discharge chamber to the control chamber, whereas the second valve part opens the lead-out passage, and leads out a fluid from the control chamber toward the suction chamber.

[0016] In this capacity control, in the valve body, a differential pressure between the discharge pressure and the control-chamber pressure acts on the first valve part, a differential pressure between the control-chamber pressure and the suction pressure acts on the second valve part, and a differential pressure between the suction pressure and the control-chamber pressure acts on the pressure receiving part. Herein, since the pressure receiving area of the pressure receiving part is formed to become substantially equal to a difference between the pressure receiving area of the second valve part and the pressure receiving area of the first valve part, the influence of the control-chamber pressure on the valve body can be minimized, and the optimum capacity control can be performed by applying a control signal corresponding to a pressure load onto the solenoid. Additionally, even if the passage area between the control chamber and the suction chamber is increased when a refrigerant gas (e.g., carbon dioxide) having a large pressure area is used, the solenoid can be reduced in size, and capacity control can be performed in a stabler manner, because the influence of the control-chamber pressure in the pressure load is minimized.

[0017] In the above-mentioned structure, the first valve chamber and the second valve chamber may be formed as one valve chamber by which the first and second valve chamber communicate with each other, and the communication path which is located on a downstream side of the lead-in first communication path extending towards the first valve seat and through which the first valve chamber and the control chamber communicate with each other.

[0018]  According to this structure, one valve chamber in which the first valve chamber and the second valve chamber communicate with each other is formed, and the lead-in passage on a downstream side of the first valve chamber and the lead-out passage on an upstream side of the second valve chamber are used as a shared passage. Therefore, the structure can be simplified, and a reduction in size can be achieved.

[0019] In the above-mentioned structure, the capacity control valve may further include a third valve chamber to which the pressure receiving part is exposed and which communicates with the control chamber, and the valve body may have the pressure receiving part at an end thereof on an opposite side of the first valve part, and a driving rod that is included in the solenoid and that comes into contact with the pressure receiving part so as to exert an electro-magnetic driving force thereon may be reciprocatably disposed in the third valve chamber.

[0020] According to this structure, the first valve chamber in which the first valve part is disposed, the second valve chamber in which the second valve part is disposed (or one valve chamber used both as the first valve chamber and as the second valve chamber), and the third valve chamber to which the pressure receiving part is exposed can be easily arranged in the longitudinal direction (reciprocating direction) of the valve body including the first valve part, the second valve part, and the pressure receiving part, and, accordingly, the solenoid (or the driving rod of the solenoid) can be easily arranged. Therefore, compaction as a whole and structural simplification can be achieved.

[0021] In the above-mentioned structure, the capacity control valve may further include a pressure-sensitive body that exerts an urging force on the valve body according to an increase and a decrease in pressure.

[0022] According to this structure, since the pressure-sensitive body exerts an urging force on the valve body according to an increase and a decrease in pressure (for example, discharge pressure or suction pressure), smoother capacity control complying with a change in pressure load can be performed.

[0023] In the above-mentioned structure, the lead-in passage may be provided with a housing chamber in which the pressure-sensitive body is housed at an upstream side of the first valve chamber; the valve body may have an extension part passing through the lead-in passage and extending from the first valve part to the housing chamber; and the pressure-sensitive body may come into contact with a tip of the extension part in a reciprocating direction of the valve body so as to open the first valve part and so as to close the second valve part according to an increase in discharge pressure.

[0024] According to this structure, the first valve chamber in which the first valve part is disposed, the second valve chamber in which the second valve part is disposed (or one valve chamber used both as the first valve chamber and as the second valve chamber), and the housing chamber can be easily arranged in the longitudinal direction (reciprocating direction) of the valve body including the extension part, the first valve part, the second valve part, and the pressure receiving part. Therefore, a smooth operation complying with a change in discharge pressure can be performed, and compaction as a whole and structural simplification can be achieved.

Advantageous Effects of the Invention

[0025] The above-mentioned capacity control valve is capable of minimizing the influence of a control-chamber pressure on the valve body, is capable of performing capacity control more stably, and is capable of achieving a reduction in, for example, solenoid size and a reduction in cost while securing a fluid flow obtained when the control chamber and the suction chamber are controlled even if a refrigerant gas (e.g., carbon dioxide) having a large pressure area is used.

Brief Description of the Drawings

[0026] 

FIG. 1 is a schematic view showing a swash plate type capacity-variable compressor that includes a capacity control valve according to the present invention;

FIG. 2 is a sectional view showing one embodiment of the capacity control valve according to the present invention;

FIG. 3 is a partially enlarged sectional view of the capacity control valve of FIG. 2 whose part is enlarged;

FIG. 4 is a partially enlarged sectional view of the capacity control valve of FIG. 2 whose part is enlarged;

FIG. 5 is a sectional view showing another embodiment of the capacity control valve according to the present invention;

FIG. 6 is a partially enlarged sectional view of the capacity control valve of FIG. 5 whose part is enlarged; and

FIG. 7 is a partially enlarged sectional view of the capacity control valve of FIG. 5 whose part is enlarged.

Description of Signs

[0027] 

M

Swash plate type capacity-variable compressor

V

Capacity control valve

10

Casing

11

Discharge chamber

12

Control chamber

13

Suction chamber

14

Cylinder

15

Communication path (lead-in passage)

16

Communication path (lead-in passage, lead-out passage)

17

Communication path (lead-out passage)

18

Communication path

20

Rotary shaft

21

Swash plate

22

Piston

23

Connection rod

24

Driven pulley

25

Condenser

26

Expansion valve

27

Evaporator

30

Body

B1

Partition member

31 (31a)

Communication path (lead-in passage)

31a'

First valve seat

31b

Communication path (lead-in passage, lead-out passage)

32 (32a, 32b)

Communication path (lead-out passage)

33

Guide path

34

Communication path

35

Enlarged chamber (housing chamber)

36

valve chamber (first valve chamber, second valve chamber)

37

Valve chamber (third valve chamber)

38

Regulation plate

40,40'

Valve body

41

First valve part

42

Second valve part

43

Diameter-reduced part

44

Pressure receiving part

45

Extension part

50

Coil spring

60

Solenoid

61

Solenoid body

62

Casing

63

Sleeve

64

Fixed iron core

65

Driving rod

66

Movable iron core

67

Coil spring

68

Coil

70

Pressure-sensitive body

Best Mode for Carrying Out the Invention

[0028] The best mode for carrying out the present invention will be hereinafter described with reference to the accompanying drawings.

[0029] First, a description will be given of an embodiment in which a capacity control valve according to the present invention is applied to a swash plate type capacity-variable compressor M with reference to FIG. 1 to FIG. 4.

[0030] As shown in FIG. 1, the swash plate type capacity-variable compressor M includes a discharge chamber 11, a control chamber (also called a "crank chamber") 12, a suction chamber 13, a plurality of cylinders 14, a port 11b through which the cylinders 14 and the discharge chamber 11 are allowed to communicate with each other and which is opened and closed by a discharge valve 11a, a port 13b through which the cylinders 14 and the suction chamber 13 are allowed to communicate with each other and which is opened and closed by a suction valve 13a, a discharge port 11c and a suction port 13c connected to an external cooling circuit, a communication path 15 serving as a lead-in passage through which a discharge fluid is introduced into the control chamber 12 from the discharge chamber 11, a communication path 16 serving as the above-mentioned lead-in passage and a lead-out passage through which a fluid is led out from the control chamber 12 toward the suction chamber 13, a communication path 17 serving as a lead-out passage, a casing 10 that defines, for example, a communication path 18 through which the pressure (control-chamber pressure) of the inside of the control chamber 12 is led, a rotary shaft 20 that is rotatably provided and is extended from the inside of the crank chamber 12 outwardly, a swash plate 21 that is rotated together with the rotary shaft 20 and is connected to the rotary shaft 20 such that the inclination angle of the swash plate 21 can be varied with respect to the rotary shaft 20, a plurality of pistons 22 reciprocatably fitted into the cylinders 14 respectively, a plurality of connection rods 23 by each of which the swash plate 21 and each piston 22 are connected to each other, a driven pulley 24 attached to the rotary shaft 20, and a capacity control valve V incorporated into the casing 10.

[0031] A cooling circuit is connected to the swash plate type capacity-variable compressor M through the discharge port 11c and the suction port 13c. The cooling circuit includes a condenser 25, an expansion valve 26, and an evaporator 27, which are arranged in this order.

[0032] As shown in FIG. 2, the capacity control valve V includes a body 30 made of a metallic or resinous material, a valve body 40 reciprocatably disposed in the body 30, a coil spring 50 by which the valve body 40 is urged in one direction, and a solenoid 60 connected to the body 30 and the like.

[0033] As shown in FIG. 2, the body 30 is provided with a communication path 31 (31a, 31b), a communication path 32 (32a, 32b), a guide path 33, a communication path 34, an enlarged chamber 35 that is formed on the upstream side of the communication path 31a and communicates with the communication path 15 of the casing 10, a valve chamber 36 that is formed in the middle of the communication path 31 and serves as first and second valve chambers communicating with each other, and a valve chamber 37 that is formed between the guide path 33 and the communication path 34 and serves as a third valve chamber.

[0034] A first valve seat 31a' on which a first valve part 41 of the valve body 40 described later is seated is formed at an end of the communication path 31a, and a second valve seat 32a' on which a second valve part 42 of the valve body 40 described later is seated is formed at an end of the communication path 32a.

[0035] The communication path 32a and the guide path 33 are defined by a partition member B1 fitted into the body 30. Since the partition member B1 is formed independently of the body 30, the valve body 40 can be reduced in length in its axial direction and can be easily attached, thus making it possible to lower the assembly cost. If a wear-resistance metallic material that differs from that of the body 30 is used as a material for making the partition member B1, the guide path 33 can be prevented from being worn out as much as possible, and the valve body 40 can be stably guided.

[0036] As shown in FIG. 2, the valve body 40 is provided integrally with the first valve part 41 whose end has a tapered surface, a second valve part 42 that is greater in diameter than the first valve part 41 and whose end has a tapered surface so as to perform an open-close operation in a direction opposite to the direction of the first valve part 41, a diameter-reduced part 43 reciprocatably inserted in the communication path 32a, and a pressure receiving part 44 that is greater in diameter than the diameter-reduced part 43, that is slidably fitted into the guide path 33, and that is exposed to the valve chamber 37.

[0037] That is, the pressure receiving part 44 is formed at an end on the opposite side of the first valve part 41 with the second valve part 42 placed between the pressure receiving part 44 and the first valve part 41. Thus,a control-chamber pressure led through the communication path 34 can effectively act by providing the pressure receiving part 44 at the end.

[0038] When the valve body 40 is moved downwardly in FIG. 2, the first valve part 41 is separated from the first valve seat 31a' so as to open the communication path (lead-in passage) 31a, and, at the same time, the second valve part 42 is seated on the second valve seat 32a' so as to close the communication path (lead-out passage) 32a as shown in FIG. 3. On the other hand, when the valve body 40 is moved upwardly in FIG. 2, the first valve part 41 is seated on the first valve seat 31a' so as to close the communication path (lead-in passage) 31a, and, at the same time, the second valve part 42 is separated from the second valve seat 32a' so as to open the communication path (lead-out passage) 32a as shown in FIG. 4.

[0039] The coil spring 50 exerts a downward urging force on the valve body 40 in FIG. 2 so that the first valve part 41 opens the communication path 31a and so that the second valve part 42 closes the communication path 32a.

[0040] As shown in FIG. 2, the solenoid 60 includes a solenoid body 61 connected to the body 30, a casing 62 by which the whole of the device is enclosed, a sleeve 63 one end of which is closed, a cylindrical fixed iron core 64 disposed inside the solenoid body 61 and the sleeve 63, a driving rod 65 reciprocatably disposed inside the fixed iron core 64 so that its tip protrudes into the valve chamber 37 and is brought into contact with the pressure receiving part 44, a movable iron core 66 fixed to an opposite end of the driving rod 65, a coil spring 67 that urges the movable iron core 66 in a direction in which the driving rod 65 is separated from the valve body 40, and an exciting coil 68 wound on the outside of the sleeve 63.

[0041] In the above-mentioned capacity control valve V, the communication path 31 allows the discharge chamber 11 and the control chamber 12 to communicate with each other, and leads a discharge fluid (refrigerant gas) into the control chamber 12. In detail, in the communication path 31a, a discharge pressure Pd acts on the first valve part 41 from the upstream side, and, at the same time, a control-chamber pressure Pc acts thereon from the downstream side.

[0042] The communication path 32 allows the control chamber 12 and the suction chamber 13 to communicate with each other, and leads out a fluid (control-chamber pressure Pc) in the control chamber 13 toward the suction chamber 13. In detail, in the communication path 32a, a control-chamber pressure Pc acts on the second valve part 42 through the communication path 31b from the upstream side, and, at the same time, a suction pressure Ps acts thereon through the communication path 32b from the downstream side.

[0043] Herein, the first valve chamber in which the first valve part 41 is disposed and the second valve chamber in which the second valve part 42 is disposed are formed in the shape of one valve chamber 36 in which the first and second valve chambers communicate with each other. In addition to this, the communication path 31b located on the downstream side of the communication path 31 serves as a lead-in passage that leads a discharge fluid (or discharge pressure Pd) into the control chamber 12, and serves also as a lead-out passage that is located on the upstream side of the communication path 32 and leads out a fluid (or control-chamber pressure Pc) in the control chamber 12 toward the suction chamber 13.

[0044] Therefore, the simplification of the structure can be performed, and the capacity control valve v can be reduced in size, as compared with a device in which a first valve chamber and a second valve chamber are formed independently of each other and in which a lead-in passage located on the downstream side of the first valve chamber and a lead-out passage located on the upstream side of the second valve chamber are formed independently of each other.

[0045] In the above-mentioned structure, the guide path 33 is formed so as to have an axis line exactly aligned with the communication path 31a and the communication path 32a, and serves to reciprocatably guide the pressure receiving part 44 of the valve body 40. The communication path 34 leads the control-chamber pressure Pc of the inside of the control chamber 12 toward the third valve chamber 37, and allows this pressure to act on the pressure receiving part 44.

[0046] Additionally, in the above-mentioned structure, as shown in FIG. 3, a relationship among a pressure receiving area S1 in which the first valve part 41 is defined by the sectional area of the communication path 31a, a pressure receiving area S2 in which the second valve part 42 is defined by the sectional area of the communication path 32a, and a pressure receiving area S3 in which the pressure receiving part 44 is defined by the sectional area of the guide path 33 may be formed so as to satisfy the following equation (1):


in other words, so that the pressure receiving area S3 becomes equal to a difference between the pressure receiving area S2 and the pressure receiving area S1. Without being limited to the same value as the value of S2-S1, the value of S3 may be nearly equal to the value of S2-S1, including its approximate value.

[0047] The operation of this structure will be described. The balance of a force acting on the valve body 40 in a state in which the solenoid 60 is energized is expressed by the following equation (2):


Herein, F is an urging force applied by the solenoid 60 in a direction in which the first valve part 41 is closed, Pd is a discharge pressure, Pc is a control-chamber pressure, Ps is a suction pressure, S1 is a pressure receiving area of the first valve part 41, S2 is a pressure receiving area of the second valve part 42, S3 is a pressure receiving area of the pressure receiving part 44, fk1 is an urging force of the coil spring 50, and fk2 is an urging force of the coil spring 67.

[0048] Equation (2) is transformed, and the following equation (3) is obtained:


When the condition S3=S2-S1, i.e., S1=S2-S3 of equation (1) is substituted for equation (3), equation (3) is transformed into the following equation (4) since the relation S1•Pc= (S2-S3) Pc is satisfied:

[0049] That is, the control-chamber pressure Pc is set so that the influence of the control-chamber pressure Pc does not occur as shown in equation (4) mentioned above or so that the influence of the control-chamber pressure Pc is minimized according to the balance relationship of a force applied onto the valve body 40 during a control operation even if the control-chamber pressure Pc exists in the system. Therefore, the valve body 40 can be driven and controlled more swiftly and more stably by a relatively small electromagnetic driving force (urging force) F generated by the solenoid 60. Therefore, in the swash plate type capacity-variable compressor M provided with the capacity control valve V, a change in angle of the swash plate 21, i.e., a change in discharge pressure Pd can be carried out in an extremely short time.

[0050] Next, a description will be given of an operation performed when the swash plate type capacity-variable compressor M provided with the capacity control valve V is applied to an automobile air-conditioning system.

[0051] First, the rotary shaft 20 is rotated by the rotational driving force of an engine via a transmission belt (not shown) and the driven pulley 24, and, correspondingly, the swash plate 21 is rotated together with the rotary shaft 20. Correspondingly to the rotation of the swash plate 21, the piston 22 is reciprocated inside the cylinder 14 with a stroke corresponding to the inclination angle of the swash plate 21, and a refrigerant gas sucked from the suction chamber 13 into the cylinder 14 is compressed with the piston 22, and is discharged into the discharge chamber 11. The refrigerant gas discharged into the discharge chamber 11 is supplied to the evaporator 27 from the condenser 25 via the expansion valve 26, and is returned to the suction chamber 13 while performing a refrigerating cycle.

[0052] Herein, the amount of refrigerant gas discharged is determined by the stroke of the piston 22. The stroke of the piston 22 is determined by the inclination angle of the swash plate 21 controlled by the pressure (control-chamber pressure Pc) of the inside of the control chamber 12.

[0053] First, in an operating state in which the amount of refrigerant gas discharged is lowest, the solenoid 60 (i.e., coil 68) is in a non-energized state, and the movable iron core 66 and the driving rod 65 are allowed to recede by the urging force of the coil spring 67, and are stopped at a position of rest. The valve body 40 is moved by the urging force of the coil spring 50 as shown in FIG. 3. The first valve part 41 is separated from the first valve seat 31a' so as to open the communication path (lead-in passage) 31a, whereas the second valve part 42 is seated on the second valve seat 32a' so as to close the communication path (lead-out passage) 32a.

[0054] As a result, a discharge fluid (discharge pressure Pd) is led into the control chamber 12 through the communication paths (lead-inpassages)31a and 31b. The swash plate 21 is controlled to have a smallest inclination angle, and the stroke of the piston 22 is minimized. As a result, the amount of refrigerant gas discharged becomes lowest. In this flow control, only the discharge pressure Pd and the suction pressure Ps substantially act on the valve body 40, and the control-chamber pressure Pc exerts no influence on the valve body 40 when the valve body 40 is driven. Therefore, capacity control is performed in swift and stable manners.

[0055] On the other hand, in an operating state in which the amount of refrigerant gas discharged is highest, the solenoid 60 (i.e., coil 68) is energized, and the movable iron core 66 and the driving rod 65 move the valve body 40 against the urging force of the coil springs 50 and 67 as shown in FIG. 4. The first valve part 41 is seated on the first valve seat 31a' so as to close the communication path (lead-inpassage) 31a, whereas the second valve part 42 is separated from the second valve seat 32a' so as to open the communication path (lead-out passage) 32a.

[0056] As a result, a fluid (refrigerant gas, blowby gas, etc.) flowing in the control chamber 12 is led out toward the suction chamber 13 through the communication paths (lead-out passages) 31b, 32a, and 32b. The swash plate 21 is controlled to have a largest inclination angle, and the stroke of the piston 22 is maximized. As a result, the amount of refrigerant gas discharged becomes highest.

[0057] Likewise, in this flow control, only the discharge pressure Pd and the suction pressure Ps substantially act on the valve body 40, and the control-chamber pressure Pc exerts no influence on the valve body 40 when the valve body 40 is driven. Therefore, capacity control is performed in swift and stable manners.

[0058] In an operating state in which the amount of refrigerant gas discharged is intermediate between the lowest and the highest, the solenoid 60 (coil 67) is controlled to have a proper amount of energization, and the electro-magnetic driving force (urging force) is varied. In other words, the valve opening amount of the first valve part 41 and the valve opening amount of the second valve part 42 are controlled to have a desired amount of refrigerant gas discharged while properly adjusting the position of the valve body 40 by use of the electro-magnetic driving force.

[0059] Likewise, in this flow control, only the discharge pressure Pd and the suction pressure Ps substantially act on the valve body 40, and the control-chamber pressure Pc exerts no influence on the valve body 40 when the valve body 40 is driven. Therefore, capacity control is performed in swift and stable manners.

[0060] FIG. 5 to FIG. 7 show another embodiment of the capacity control valve according to the present invention. This embodiment is the same as the above-mentioned embodiment except that the valve body is modified and that a pressure-sensitive body is provided. Therefore, in this embodiment, the same reference numeral is given to the same structure as in the above-mentioned embodiment, and a description of the same structure is omitted.

[0061] In the capacity control valve V regarding this embodiment, a regulation plate 38 is connected to the enlarged chamber 35 of the body 30, and the enlarged chamber 35 is formed as a housing chamber in which a pressure-sensitive body 70 is housed as shown in FIG. 5. A communication path 31a serving as a lead-in passage is formed in the sidewall of the regulation plate 38 and the enlarged chamber 35.

[0062] An extension part 45 extending from the first valve part 41 is formed integrally with a valve body 40'. The extension part 45 passes through the communication path 31a, and protrudes into the enlarged chamber 35 used as a housing chamber, and has a tip of the extension part 45 comes into contact with the pressure-sensitive body 70.

[0063] According to an increase in discharge pressure Pd, the pressure-sensitive body 70 is deformed so as to exert an urging force on the valve body 40', i.e., so as to come into contact with the extension part 45 and to exert an urging force thereon, thereby opening the first valve part 41 and closing the second valve part 42. The pressure-sensitive body 70 can employ a bellows structure, a diaphragm structure, or other structures.

[0064] In other words, in the communication path (lead-in passage) 31a, the pressure-sensitive body 70 is disposed in the enlarged chamber (housing chamber) 35 located on the upstream side of the valve chamber 36, and is engaged with the tip of the extension part 45 of the valve body 40', passing through the communication path (lead-in passage) 31a and extending from the valve chamber 36 to the enlarged chamber 35. As a result, according to an increase in discharge pressure Pd, the first valve part 41 is opened, and the second valve part 42 is closed. Therefore, when the pressure-sensitive body 70 senses an increase in discharge pressure Pd in a state in which an electro-magnetic driving force (urging force) is given by the solenoid 60 as shown in FIG. 7, the urging force is exerted on the extension part 45 of the valve body 40' so as to move the valve body 40' quickly in a direction in which the first valve part 41 is opened and the second valve part 42 is closed as shown in FIG. 6.

[0065] As a result, for example, when the discharge pressure Pd is increased by a load change, the pressure-sensitive body 70 performs control so as to quickly reach a stable state having a desired amount of refrigerant gas discharged while working in a direction in which the increase of the discharge pressure Pd is decreased.

[0066] Additionally, the valve chamber 36 in which the first and second valve parts 41 and 42 are disposed, the enlarged chamber 35 in which the pressure-sensitive body 70 is housed, and the valve chamber 37 to which the pressure receiving part 44 is exposed can be easily arranged in the longitudinal direction (reciprocating direction) of the valve body 40' , so that a smooth operation complying with a change in discharge pressure Pd can be obtained, and compaction and structural simplification can be achieved as a whole.

[0067] In the above-mentioned embodiment, the valve chamber 36 is formed in the shape of a single valve chamber allowing the first valve chamber in which the first valve part 41 is disposed and the second valve chamber in which the second valve part 42 is disposed to communicate with each other, and the communication path 31b is formed in the shape of a shared communication path that serves as the lead-in passage leading from the first valve chamber to the control chamber 12 and serves as the lead-out passage leading from the control chamber 12 to the second valve chamber. However, without being limited to this, the first valve chamber and the second valve chamber may be formed independently of each other, and the lead-in passage and the lead-out passage may be formed independently of each other.

[0068] Additionally, in the above-mentioned embodiment, the pressure-sensitive body 70 is formed as a body exerting an urging force on the valve body 40' so as to open the first valve part 41 and so as to close the second valve part 42 according to an increase in discharge pressure Pd. However, without being limited to this, a structure may be employed in which an urging force is exerted on a valve body according to an increase or a decrease in suction pressure Ps.

Industrial Applicability

[0069] As described above, the capacity control valve of the present invention is capable of minimizing the influence of a control-chamber pressure on a valve body, is capable of performing capacity control more stably, and is capable of achieving a reduction in, for example, solenoid size and a reduction in cost while securing a fluid flow obtained when a control chamber and a suction chamber are controlled. Therefore, the capacity control valve of the present invention can, of course, be applied to a capacity-variable compressor used in an air-conditioning system of, for example, an automobile, and is useful as a capacity control valve that performs capacity control in a machine for variably controlling the capacity of other fluids.

Claims

1. A capacity control valve adapted to be applied to a compressor (M) including a discharge chamber (11) for discharging a fluid, a suction chamber (13) for sucking in the fluid and a control chamber (12) for controlling a discharge amount of the fluid, the capacity control valve comprising:

a first communication path (31) through which the discharge chamber (11) and the control chamber (12) are allowed to communicate with each other and through which the fluid is introduced into the control chamber (12);

a second communication path (32) through which the suction chamber (13) and the control chamber (12) are allowed to communicate with each other and through which the fluid is led out from the control chamber (12);

a first valve chamber formed midway of the first communication path (31);

a second valve chamber formed midway of the second communication path (32);

a valve body (40) formed integrally with a first valve part (41) that is disposed in the first valve chamber and opens and closes the first communication path (31), a second valve part (42) that is disposed in the second valve chamber and opens and closes the second communication path (32), and a pressure receiving part (44) disposed at an end on an opposite side of the first valve part (41) with the second valve part (42) placed therebetween;

a guide path (33) for reciprocatably guiding the pressure receiving part (44) of the valve body (40) ;

a solenoid (60) that exerts an electro-magnetic driving force on the pressure receiving part (44) of the valve body (40) via a driving rod (65) that is brought into contact with the pressure receiving part (44); and

a body (30) that defines the first communication path (31), the second communication path (32), the first valve chamber, the second valve chamber, and the guide path (33) and that accommodates the valve body (40);

the capacity control valve being characterized in that:

the valve body (40) is configured to act such that when moving in one direction, the first valve part (41) is separated from a first valve seat (31a') so as to open a lead-in first communication path (31a) extending toward the valve seat (31a') and at the same time, the second valve part (42) is seated on a second valve seat (32a') so as to close a lead-out second communication path (32a) extending from the second valve seat (32a'), and when moving in another direction, the second valve part (42) is separated from the second valve seat (32a') so as to open the lead-out second communication path (32a) and at the same time, the first valve part (41) is seated on the first valve seat (31a') so as to close the lead-in first communication path (31a), and

wherein a pressure receiving area (S3) of the pressure receiving part (44) is formed to become equal to a difference between a pressure receiving area (S2) of the second valve part (42) in the lead-out second communication path (32a) extending from the second valve seat (32a') and a pressure receiving area (S1) of the first valve part (41) in the lead-in first communication path (31a) extending toward the first valve seat (31a') .

2. The capacity control valve according to claim 1, wherein the first valve chamber and the second valve chamber are formed as one valve chamber (36) by which the first valve chamber and the second valve chamber communicate with each other, and
a communication path (31b) which is located on a downstream side of the lead-in first communication path (31a) extending toward the first valve seat (31a') and through which the first valve chamber and the control chamber (12) communicate with each other is formed so as to serve as a lead-out passage that is located on an upstream side of a lead-out second communication path (32b) and leads out the fluid in the control chamber (12) toward the suction chamber (13).

3. The capacity control valve according to claim 1 wherein
the lead-out second communication path (32a) extending from the second valve seat (32a') and the guide path (33) are defined by a partition member (B1) fitted into the body (30) .

4. The capacity control valve according to claim 1, further comprising a third valve chamber (37) to which the pressure receiving part (44) is exposed and which communicates with the control chamber (12), wherein
the driving rod (56) is reciprocatably disposed in the third valve chamber (37).

5. The capacity control valve according to claim 1, further comprising a pressure-sensitive body (70) that exerts an urging force on the valve body (40) according to an increase and a decrease in pressure.

6. The capacity control valve according to claim 2, further comprising a pressure-sensitive body (70) that exerts an urging force on the valve body (40) according to an increase and a decrease in pressure.

7. The capacity control valve according to claim 3, further comprising a pressure-sensitive body (70) that exerts an urging force on the valve body (40) according to an increase and a decrease in pressure.

8. The capacity control valve according to claim 4, further comprising a pressure-sensitive body (70) that exerts an urging force on the valve body (40) according to an increase and a decrease in pressure.

9. The capacity control valve according to claim 5, wherein the lead- in first communication path (31a) is provided with a housing chamber (35) in which the pressure-sensitive body (70) is housed at an upstream side of the first valve chamber;
the valve body (40) has an extension part (45) passing through the lead-in first communication path (31a) and extending from the first valve part (41) to the housing chamber (35); and
the pressure-sensitive body (70) comes into contact with a tip of the extension part (45) in a reciprocating direction of the valve body (40), and opens the first valve part (41) and closes the second valve part (42) according to an increase in discharge pressure.

10. The capacity control valve according to claim 6, wherein the lead-in first communication path (31a) is provided with a housing chamber (35) in which the pressure-sensitive body (70) is housed at an upstream side of the first valve chamber;
the valve body (40) has an extension part (45) passing through the lead-in first communication path (31a) and extending from the first valve part (41) to the housing chamber (35); and
the pressure-sensitive body (70) comes into contact with a tip of the extension part (45) in a reciprocating direction of the valve body (40), and opens the first valve part (41) and closes the second valve part (42) according to an increase in discharge pressure.

11. The capacity control valve according to claim 7, wherein the lead-in first communication path (31a) is provided with a housing chamber (35) in which the pressure-sensitive body (70) is housed at an upstream side of the first valve chamber;
the valve body (40) has an extension part (45) passing through the lead-in first communication path (31a) and extending from the first valve part (41) to the housing chamber (35); and
the pressure-sensitive body (70) comes into contact with a tip of the extension part (45) in a reciprocating direction of the valve body (40), and opens the first valve part (41) and closes the second valve part (42) according to an increase in discharge pressure.

12. The capacity control valve according to claim 8, wherein
the lead-in first communication path (31a) is provided with a housing chamber (35) in which the pressure-sensitive body (70) is housed at an upstream side of the first valve chamber;
the valve body (40) has an extension part (45) passing through the lead-in first communication path (31a) and extending from the first valve part (41) to the housing chamber (35); and
the pressure-sensitive body (70) comes into contact with a tip of the extension part (45) in a reciprocating direction of the valve body (40), and opens the first valve part (41) and closes the second valve part (42) according to an increase in discharge pressure.

Ansprüche

1. Mengenregelventil, angepasst, um an einem Kompressor (M) angebracht zu werden, umfassend eine Ablasskammer (11) zum Ablassen eines Fluids, eine Saugkammer (13) zum Ansaugen des Fluids und eine Steuerkammer (12) zum Steuern einer Ablassmenge des Fluids, wobei das Mengenregelventil umfasst:

einen ersten Kommunikationsweg (31), durch den die Ablasskammer (11) und die Steuerkammer (12) miteinander kommunizieren können, und durch den das Fluid in die Steuerkammer (12) eingeführt wird;

einen zweiten Kommunikationsweg (32), durch den die Saugkammer (13) und die Steuerkammer (12) miteinander kommunizieren können, und durch den das Fluid aus der Steuerkammer (12) herausgeführt wird;

eine erste Ventilkammer, die in der Mitte des ersten Kommunikationswegs (31) gebildet ist;

eine zweite Ventilkammer, die in der Mitte des zweiten Kommunikationswegs (32) gebildet ist;

einen Ventilkörper (40), der als ein Stück mit einem ersten Ventilteil (41), der in der ersten Ventilkammer angeordnet ist, und den ersten Kommunikationsweg (31) öffnet und schließt, einem zweiten Ventilteil (42), der in der zweiten Ventilkammer angeordnet ist und den zweiten Kommunikationsweg (32) öffnet und schließt, und einem druckaufnehmenden Teil (44), der an einem Ende auf einer dem ersten Ventilteil (41) gegenüberliegenden Seite angeordnet ist, wobei der zweite Ventilteil (42) dazwischen angeordnet ist, gebildet ist;

einen Führungsweg (33), um den druckaufnehmenden Teil (44) des Ventilkörpers (40) auf reziproke Weise zu führen;

eine Magnetspule (60), die über eine Pleuelstange (65), die mit dem druckaufnehmendem Teil (44) in Kontakt gebracht wird, eine elektromagnetische Antriebskraft auf den druckaufnehmenden Teil (44) des Ventilkörpers (40) ausübt; und

einen Körper (30), der den ersten Kommunikationsweg (31), den zweiten Kommunikationsweg (32), die erste Ventilkammer, die zweite Ventilkammer und den Führungsweg (33) bestimmt und der den Ventilkörper (40) aufnimmt;

wobei das Mengenregelventil dadurch gekennzeichnet ist, dass:

der Ventilkörper (40) so konfiguriert ist, dass beim Bewegen in eine Richtung der erste Ventilteil (41) von einem ersten Ventilsitz (31a') getrennt wird, sodass ein hereinführender erster Kommunikationsweg (31a), der sich in Richtung des Ventilsitzes (31a') erstreckt, geöffnet wird, und dass zur selben Zeit der zweite Ventilteil (42) auf einem zweiten Ventilsitz (32a') sitzt, sodass ein herausführender zweiter Kommunikationsweg (32a) geschlossen wird, der sich vom zweiten Ventilsitz (32a') aus erstreckt, und dass beim Bewegen in eine andere Richtung der zweite Ventilteil (42) vom zweiten Ventilsitz (32a') getrennt wird, sodass der herausführende zweite Kommunikationsweg (32a) geöffnet wird und zur selben Zeit der erste Ventilteil (41) auf dem ersten Ventilsitz (31a') sitzt, sodass der hereinführende erste Kommunikationsweg (31 a) geschlossen wird, und

wobei ein druckaufnehmender Bereich (S3) des druckaufnehmenden Teils (44) gebildet ist, um gleich einer Differenz zwischen einem druckaufnehmenden Bereich (S2) des zweiten Ventilteils (42) in dem herausführenden zweiten Kommunikationsweg (32a), der sich vom zweiten Ventilsitz (32a') erstreckt, und einem druckaufnehmenden Bereich (S1) des ersten Ventilteils (41) im hereinführenden ersten Kommunikationsweg (31a), der sich in Richtung des ersten Ventilsitzes (31a') erstreckt, zu werden.

2. Mengenregelventil nach Anspruch 1, wobei
die erste Ventilkammer und die zweite Ventilkammer als eine Ventilkammer (36) gebildet sind, durch die die erste Ventilkammer und die zweite Ventilkammer miteinander kommunizieren, und
ein Kommunikationsweg (31b), der an einer nachgelagerten Seite des hereinführenden ersten Kommunikationswegs (31a) angeordnet ist, der sich in Richtung des ersten Ventilsitzes (31a') erstreckt, und durch den die erste Ventilkammer und die Steuerkammer (12) miteinander kommunizieren, so gebildet ist, dass er als Auslass-Passage dient, die sich an einer vorgelagerten Seite eines herausführenden zweiten Kommunikationswegs (32b) befindet, und das Fluid in der Steuerkammer (12) in Richtung der Saugkammer (13) auslässt.

3. Mengenregelventil nach Anspruch 1, wobei
der herausführende zweite Kommunikationsweg (32a), der sich vom zweiten Ventilsitz (32a') erstreckt, und der Führungsweg (33) durch ein in den Körper (30) eingebautes Trennelement (B1) bestimmt werden.

4. Mengenregelventil nach Anspruch 1, überdies umfassend eine dritte Ventilkammer (37), der der druckaufnehmende Teil (44) ausgesetzt ist, und die mit der Steuerkammer (12) kommuniziert, wobei
die Pleuelstange (56) reziprok in der dritten Ventilkammer (37) angeordnet ist.

5. Mengenregelventil 1 nach Anspruch 1, überdies umfassend einen druckempfindlichen Körper (70), der eine Drängkraft auf den Ventilkörper (40) ausübt, entsprechend einer Zunahme und einer Abnahme des Drucks.

6. Mengenregelventil nach Anspruch 2, überdies umfassend einen druckempfindlichen Körper (70), der eine Drängkraft auf den Ventilkörper (40) ausübt, entsprechend einer Zunahme und einer Abnahme des Drucks.

7. Mengenregelventil nach Anspruch 3, überdies umfassend einen druckempfindlichen Körper (70), der eine Drängkraft auf den Ventilkörper (40) ausübt, entsprechend einer Zunahme und einer Abnahme des Drucks.

8. Mengenregelventil nach Anspruch 4, überdies umfassend einen druckempfindlichen Körper (70), der eine Drängkraft auf den Ventilkörper (40) ausübt, entsprechend einer Zunahme und einer Abnahme des Drucks.

9. Mengenregelventil nach Anspruch 5, wobei
der hereinführende erste Kommunikationsweg (31a) mit einer Gehäusekammer (35) versehen ist, in der der druckempfindliche Körper (70) an einer vorgeordneten Seite der ersten Ventilkammer eingepasst ist;
der Ventilkörper (40) ein Verlängerungsteil (45) aufweist, das durch den hereinführenden ersten Kommunikationsweg (31a) hindurch läuft, und sich vom ersten Ventilteil (41) zur Gehäusekammer (35) erstreckt; und
der druckempfindliche Körper (70) mit einer Spitze des Verlängerungsteils (45) in einer reziproken Richtung des Ventilkörpers (40) in Kontakt tritt und den ersten Ventilteil (41) öffnet und den zweiten Ventilteil (42) schließt, entsprechend einer Zunahme des Ablassdrucks.

10. Mengenregelventil nach Anspruch 6, wobei
der hereinführende erste Kommunikationsweg (31a), mit einer Gehäusekammer (35) versehen ist, in der der druckempfindliche Körper (70) an einer vorgeordneten Seite der ersten Ventilkammer eingepasst ist;
der Ventilkörper (40) ein Verlängerungsteil (45) aufweist, das durch den hereinführenden ersten Kommunikationsweg (31 a) hindurch läuft, und sich vom ersten Ventilteil (41) zur Gehäusekammer (35) erstreckt; und
der druckempfindliche Körper (70) mit einer Spitze des Verlängerungsteils (45) in einer reziproken Richtung des Ventilkörpers (40) in Kontakt tritt und den ersten Ventilteil (41) öffnet und den zweiten Ventilteil (42) schließt, entsprechend einer Zunahme des Ablassdrucks.

11. Mengenregelventil nach Anspruch 7, wobei
der hereinführende erste Kommunikationsweg (31a) mit einer Gehäusekammer (35) versehen ist, in der der druckempfindliche Körper (70) an einer vorgeordneten Seite der ersten Ventilkammer eingepasst ist;
der Ventilkörper (40) ein Verlängerungsteil (45) aufweist, das durch den hereinführenden ersten Kommunikationsweg (31 a) hindurch läuft, und sich vom ersten Ventilteil (41) zur Gehäusekammer (35) erstreckt; und
der druckempfindliche Körper (70) mit einer Spitze des Verlängerungsteils (45) in einer reziproken Richtung des Ventilkörpers (40) in Kontakt tritt und den ersten Ventilteil (41) öffnet und den zweiten Ventilteil (42) schließt, entsprechend einer Zunahme des Ablassdrucks.

12. Mengenregelventil nach Anspruch 8, wobei
der hereinführende erste Kommunikationsweg (31a) mit einer Gehäusekammer (35) versehen ist, in der der druckempfindliche Körper (70) an einer vorgelagerten Seite der ersten Ventilkammer eingepasst ist;
der Ventilkörper (40) ein Verlängerungsteil (45) aufweist, das durch den hereinführenden ersten Kommunikationsweg (31 a) hindurch läuft, und sich vom ersten Ventilteil (41) zur Gehäusekammer (35) erstreckt; und
der druckempfindliche Körper (70) mit einer Spitze des Verlängerungsteils (45) in einer reziproken Richtung des Ventilkörpers (40) in Kontakt tritt und den ersten Ventilteil (41) öffnet und den zweiten Ventilteil (42) schließt, entsprechend einer Zunahme des Ablassdrucks.

Revendications

1. Valve de contrôle de capacité, adaptée pour être appliquée à un compresseur (M) incluant une chambre de décharge (11) pour décharger un fluide, une chambre d'aspiration (13) pour aspirer le fluide et une chambre de commande (12) pour commander une quantité de décharge du fluide, la valve de contrôle de capacité comprenant :

un premier passage de communication (31) à travers lequel la chambre de décharge (11) et la chambre de commande (12) peuvent communiquer l'une avec l'autre, et à travers lequel le fluide est introduit dans la chambre de commande (12) ;

un deuxième passage de communication (32) à travers lequel la chambre d'aspiration (13) et la chambre de commande (12) peuvent communiquer l'une avec l'autre, et à travers lequel le fluide est extrait de la chambre de commande (12);

une première chambre de valve formée à mi-chemin du premier passage de communication (31) ;

une deuxième chambre de valve formée à mi-chemin du deuxième passage de communication (32) ;

un corps de valve (40) formé d'une seule pièce avec une première partie de valve (41) qui est disposée dans la première chambre de valve et ouvre et ferme le premier passage de communication (31), une deuxième partie de valve (42) qui est disposée dans la deuxième chambre de valve et ouvre et ferme le deuxième passage de communication (32), et une partie de réception de pression (44) disposée à une extrémité sur un côté opposé de la première partie de valve (41), la deuxième partie de valve (42) étant placée en position intermédiaire ;

un passage de guidage (33) pour guider, en effectuant un mouvement alternatif, la partie de réception de pression (44) du corps de valve (40) ;

un solénoïde (60) qui exerce une force d'entraînement électromagnétique sur la partie de réception de pression (44) du corps de valve (40) via une tige d'entraînement (65) qui est amenée en contact avec la partie de réception de pression (44) ; et

un corps (30) qui définit le premier passage de communication (31), le deuxième passage de communication (32), la première chambre de valve, la deuxième chambre de valve, et le passage de guidage (33), et qui loge le corps de valve (40) ;

la valve de contrôle de capacité étant caractérisée en ce que :

le corps de valve (40) est configuré pour agir de sorte que lors du déplacement dans une direction, la première partie de valve (41) est séparée d'un premier siège de valve (31a') de façon à ouvrir un premier passage de communication (31a) d'entrée s'étendant vers le siège de valve (31a'), et en même temps la deuxième partie de valve (42) est assise sur un deuxième siège de valve (32a') de façon à fermer un deuxième passage de communication (32a) de sortie s'étendant à partir du deuxième siège de valve (32a'), et lors du mouvement dans une autre direction la deuxième partie de valve (42) est séparée du deuxième siège de valve (32a') de façon à ouvrir le deuxième passage de communication (32a) de sortie, et en même temps la première partie de valve (41) est assise sur le premier siège de valve (31a') de façon à fermer le premier passage de communication (31a) d'entrée, et

dans laquelle une zone de réception de pression (S3) de la partie de réception de pression (44) est formée pour devenir égale à une différence entre une zone de réception de pression (S2) de la deuxième partie de valve (42) dans le deuxième passage de communication (32a) de sortie s'étendant à partir du deuxième siège de valve (32a') et une zone de réception de pression (S1) de la première partie de valve (41) dans le premier passage de communication (31a) d'entrée s'étendant vers le premier siège de valve (31a').

2. Valve de contrôle de capacité selon la revendication 1, dans laquelle
la première chambre de valve et la deuxième chambre de valve sont formées comme une seule chambre de valve (36) au moyen de laquelle la première chambre de valve et la deuxième chambre de valve communiquent l'une avec l'autre, et
un passage de communication (31b), qui est situé sur un côté aval du premier passage de communication (31a) d'entrée s'étendant vers le premier siège de valve (31a') et à travers lequel la première chambre de valve et la chambre de commande (12) communiquent l'une avec l'autre, est formé de façon à servir de passage de sortie qui est situé sur un côté amont d'un deuxième passage de communication (32b) de sortie et qui extrait le fluide de chambre de commande (12) vers la chambre d'aspiration (13).

3. Valve de contrôle de capacité selon la revendication 1, dans laquelle le deuxième passage de communication (32a) de sortie s'étendant à partir du deuxième siège de valve (32a') et le passage de guidage (33) sont définis par un élément de cloisonnement (B1) monté dans le corps (30).

4. Valve de contrôle de capacité selon la revendication 1, comprenant également une troisième chambre de valve (37) à laquelle la partie de réception de pression (44) est exposée et qui communique avec la chambre de commande (12), dans laquelle la tige d'entraînement (56) est disposée, en effectuant un mouvement alternatif, dans la troisième chambre de valve (37).

5. Valve de contrôle de capacité selon la revendication 1, comprenant également un corps sensible à la pression (70) qui exerce une force de poussée sur le corps de valve (40) selon une augmentation et une réduction de pression.

6. Valve de contrôle de capacité selon la revendication 2, comprenant également un corps sensible à la pression (70) qui exerce une force de poussée sur le corps de valve (40) selon une augmentation et une réduction de pression.

7. Valve de contrôle de capacité selon la revendication 3, comprenant également un corps sensible à la pression (70) qui exerce une force de poussée sur le corps de valve (40) selon une augmentation et une réduction de pression.

8. Valve de contrôle de capacité selon la revendication 4, comprenant également un corps sensible à la pression (70) qui exerce une force de poussée sur le corps de valve (40) selon une augmentation et une réduction de pression.

9. Valve de contrôle de capacité selon la revendication 5, dans laquelle le premier passage de communication (31a) d'entrée est muni d'une chambre de logement (35) dans laquelle le corps sensible à la pression (70) est logé au niveau d'un côté amont de la première chambre de valve ;
le corps de valve (40) a une partie de prolongement (45) traversant le premier passage de communication (31a) d'entrée et s'étendant à partir de la première partie de valve (41) vers la chambre de logement (35) ; et
le corps sensible à la pression (70) entre en contact avec un bout de la partie de prolongement (45) dans une direction à mouvement alternatif du corps de valve (40), et ouvre la première partie de valve (41) et ferme la deuxième partie de valve (42) en fonction d'une augmentation de la pression de décharge.

10. Valve de contrôle de capacité selon la revendication 6, dans laquelle
le premier passage de communication (31a) d'entrée est muni d'une chambre de logement (35) dans laquelle le corps sensible à la pression (70) est logé au niveau d'un côté amont de la première chambre de valve ;
le corps de valve (40) a une partie de prolongement (45) traversant le premier passage de communication (31a) d'entrée et s'étendant à partir de la première partie de valve (41) vers la chambre de logement (35) ; et
le corps sensible à la pression (70) entre en contact avec un bout de la partie de prolongement (45) dans une direction à mouvement alternatif du corps de valve (40), et ouvre la première partie de valve (41) et ferme la deuxième partie de valve (42) en fonction d'une augmentation de la pression de décharge.

11. Valve de contrôle de capacité selon la revendication 7, dans laquelle
le premier passage de communication (31a) d'entrée est muni d'une chambre de logement (35) dans laquelle le corps sensible à la pression (70) est logé au niveau d'un côté amont de la première chambre de valve ;
le corps de valve (40) a une partie de prolongement (45) traversant le premier passage de communication (31 a) d'entrée et s'étendant à partir de la première partie de valve (41) vers la chambre de logement (35) ; et
le corps sensible à la pression (70) entre en contact avec un bout de la partie de prolongement (45) dans une direction à mouvement alternatif du corps de valve (40), et ouvre la première partie de valve (41) et ferme la deuxième partie de valve (42) en fonction d'une augmentation de la pression de décharge.

12. Valve de contrôle de capacité selon la revendication 8, dans laquelle
le premier passage de communication (31a) d'entrée est muni d'une chambre de logement (35) dans laquelle le corps sensible à la pression (70) est logé au niveau d'un côté amont de la première chambre de valve ;
le corps de valve (40) a une partie de prolongement (45) traversant le premier passage de communication (31a) d'entrée et s'étendant à partir de la première partie de valve (41) vers la chambre de logement (35) ; et
le corps sensible à la pression (70) entre en contact avec un bout de la partie de prolongement (45) dans une direction à mouvement alternatif du corps de valve (40), et ouvre la première partie de valve (41) et ferme la deuxième partie de valve (42) en fonction d'une augmentation de la pression de décharge.

Drawing