Capacity control valve

Abstract

The object of the present invention is to provide a capacity control valve which can effectively discharge liquid refrigerant regardless of the pressure of the suction chamber and can reduce the driving force of the compressor during the liquid refrigerant discharge operation. The capacity control valve comprises: a valve body (10) having a first communication passage (11), a second communication passage (12), a third communication passage (13) and a main valve seat (15a); a valve body (20) having an intermediate communication passage (29), a main valve portion (21c) and an auxiliary valve portion (23d); a pressure-sensitive body (24) arranged in the valve body (10); a solenoid (30) driving a connecting rod (36); a first force-applying member (43) applying force to the main valve portion (21c) in a valve closing direction; and a second force-applying member (44) applying force to the main valve portion (21c) in a valve opening direction, wherein the connecting rod (36) moves relative to the valve body (20) to press the pressure-sensitive body (24).

Description

[0001] This application is a divisional application of an invention patent application with an application date of November 12, 2018, application number 201880069558.1 (international application number PCT / JP2018 / 041768), and invention name “Capacity control valve and method for controlling capacity control valve”. Technical Field

[0002] The present invention relates to a capacity control valve used to control the flow rate or pressure of a variable capacity compressor and a method for controlling the capacity control valve. Background Art

[0003] As a variable capacity compressor, for example, an inclined plate type variable capacity compressor used in air-conditioning systems of automobiles, etc. comprises: a rotating shaft driven to rotate by the rotational force of the engine; a inclined plate connected to the rotating shaft in a manner that can change the inclination angle; and a compression piston connected to the inclined plate, etc. By changing the inclination angle of the inclined plate, the stroke of the piston is changed, thereby controlling the discharge amount of the refrigerant.

[0004] The inclination angle of the inclined plate can be continuously changed in the following manner, namely, by utilizing the suction pressure of the suction chamber for sucking in refrigerant, the discharge pressure of the discharge chamber for discharging refrigerant pressurized by the piston, and the control chamber pressure of the control chamber (crank chamber) accommodating the inclined plate, and by using a capacity control valve driven to open and close by electromagnetic force to appropriately control the pressure in the control chamber and adjust the balance state of the pressure acting on both sides of the piston.

[0005] An example of such a capacity control valve is shown in Figure 7 middle. The capacity control valve 160 comprises: a valve portion 170 having a second valve chamber 182 communicating with a discharge chamber of the compressor via a second communication passage 173, a first valve chamber 183 communicating with a suction chamber via a first communication passage 171, and a third valve chamber 184 communicating with a control chamber via a third communication passage 174; a pressure-sensitive body 178 disposed in the third valve chamber and expanding and contracting by the surrounding pressure and having a valve seat body 180 having a free end provided in the expansion and contraction direction; a valve body 181 having a second valve portion 176 for opening and closing a valve hole 177 connecting the second valve chamber 182 and the third valve chamber 184, a first valve portion 175 for opening and closing the first communication passage 171 and the flow groove 172, and a third valve portion 179 for opening and closing the third valve chamber 184 and the flow groove 172 by engaging with and disengaging from the valve seat body 180 in the third valve chamber 184; and a solenoid portion 190 for generating an electromagnetic driving force in the valve body 181.

[0006] Furthermore, even if a clutch mechanism is not provided in the variable capacity compressor, in the capacity control valve 160, when there is a need to change the pressure in the control chamber, the discharge chamber and the control chamber can be connected to control the pressure in the control chamber (control chamber pressure) Pc and the suction pressure Ps (suction pressure). (Hereinafter, referred to as "conventional technology". For example, refer to Patent Document 1.)

[0007] Previous technical literature

[0008] Patent Literature

[0009] Patent Document 1: Japanese Patent No. 5167121 Summary of the invention

[0010] Technical issues to be solved by the invention

[0011] In the prior art, when the inclined plate type variable capacity compressor is stopped for a long time, liquid refrigerant (refrigerant that is cooled and liquefied during storage) is accumulated in the control chamber (crank chamber), so even if the compressor is started in this state, the set discharge volume cannot be ensured. Therefore, in order to perform the desired capacity control immediately after starting, it is necessary to discharge the liquid refrigerant in the control chamber (crank chamber) as quickly as possible.

[0012] Therefore, if Figure 8 As shown, in the conventional capacity control valve 160, a liquid refrigerant discharge function is provided in order to discharge the liquid refrigerant in the control chamber (crank chamber) as quickly as possible when starting. That is, when the variable capacity compressor is stopped and left for a long time and is to be started, the high-pressure liquid refrigerant stored in the control chamber (crank chamber) flows from the third communication passage 174 into the third valve chamber 184. Then, the pressure-sensitive body (bellows) 178 contracts and the third valve portion 179 and the valve seat body 180 are opened, so that the liquid refrigerant can be discharged from the control chamber (crank chamber) to the discharge chamber via the suction chamber from the third valve chamber 184 through the auxiliary communication passage 185, the communication passage 186 and the flow groove 172, and the liquid refrigerant is quickly vaporized and set to a cooling operation state in a short time.

[0013] However, in the above-mentioned prior art, at the beginning of the liquid refrigerant discharge process, the pressure in the control chamber is also high, so the opening of the third valve portion 179 is also large, so that the liquid refrigerant can be effectively discharged. However, as the discharge of the liquid refrigerant advances and the pressure in the control chamber decreases, the opening of the third valve portion becomes smaller, so there is a problem that it takes time to discharge the liquid refrigerant.

[0014] Furthermore, in the past, when performing the liquid refrigerant discharge operation, the focus was only on how to complete the discharge of the liquid refrigerant in a short time, so the control to reduce the engine load was not performed during the liquid refrigerant discharge operation. However, if the liquid refrigerant discharge operation is performed when the engine load is high, the engine load is further increased, thereby causing a problem of reducing the overall energy efficiency of the vehicle.

[0015] The present invention is completed in order to solve the problems existing in the above-mentioned prior art, and its purpose is to provide a capacity control valve and a control method of the capacity control valve, which can effectively discharge liquid refrigerant and transfer to refrigeration operation in a short time regardless of the pressure of the suction chamber in a capacity control valve that controls the flow rate or pressure of a variable capacity compressor according to the valve opening of the valve part, and can reduce the driving force of the compressor during the liquid refrigerant discharge operation.

[0016] Means for solving technical problems

[0017] In order to solve the above-mentioned problems, a capacity control valve of the present invention controls the flow rate or pressure of a variable capacity compressor according to the valve opening of a valve portion, and the capacity control valve is characterized in that it has:

[0018] A valve body having a first communication passage for allowing a fluid of a first pressure to flow, a second communication passage arranged adjacent to the first communication passage and allowing a fluid of a second pressure to flow, a third communication passage for allowing a fluid of a third pressure to flow, and a main valve seat arranged in a valve hole connecting the second communication passage and the third communication passage;

[0019] a pressure-sensitive body disposed in the valve body on the third communication passage side and expanding and contracting in response to the surrounding pressure;

[0020] a valve body having an intermediate communication passage connecting the first communication passage and the third communication passage, a main valve portion that is separated from / contacted with the main valve seat to open and close the valve hole, and an auxiliary valve portion that is separated from / contacted with the pressure sensing body to open and close the intermediate communication passage;

[0021] Solenoid, driving the connecting rod;

[0022] a first force applying member for applying force in a valve closing direction of the main valve portion; and

[0023] The second force applying member applies force in the valve opening direction of the main valve portion.

[0024] The connecting rod moves relative to the valve body to press the pressure-sensitive body.

[0025] According to this feature, the auxiliary valve portion can be forcibly opened by moving the connecting rod relative to the valve body to press the pressure-sensitive body. Therefore, the opening of the auxiliary valve portion can be maintained in a fully open state from the start of liquid refrigerant discharge until the liquid refrigerant discharge is completed, thereby effectively discharging the liquid refrigerant.

[0026] The capacity control valve of the present invention is characterized in that:

[0027] The urging force of the second urging member is greater than the urging force of the first urging member.

[0028] According to this feature, even when the biasing force of the pressure sensitive body does not act on the valve body, the biasing force of the second biasing member can open the main valve portion, so that the main valve portion and the auxiliary valve portion can be opened and closed in all combinations.

[0029] The capacity control valve of the present invention is characterized in that:

[0030] The first urging member is disposed between the solenoid and the valve body.

[0031] According to this feature, the first urging member is disposed between the solenoid and the valve body, thereby being able to reliably urge the valve body in the valve closing direction of the main valve portion.

[0032] The capacity control valve of the present invention is characterized in that:

[0033] The second urging member is disposed between the pressure-sensitive body and the link.

[0034] According to this feature, the second urging member is disposed between the pressure-sensitive body and the link, thereby being able to reliably urge the valve body in the valve opening direction of the main valve portion.

[0035] The capacity control valve of the present invention is characterized in that:

[0036] The solenoid further includes a plunger connected to the connecting rod, a magnetic core and an electromagnetic coil arranged between the plunger and the valve body.

[0037] The second urging member is disposed between the plunger and the magnetic core.

[0038] According to this feature, by being disposed between the plunger and the magnetic core, the valve body can be reliably urged in the valve opening direction of the main valve portion when the solenoid is in the "closed" position.

[0039] The capacity control valve of the present invention is characterized in that:

[0040] The link includes a locking portion that is separated from and in contact with the valve body.

[0041] According to this feature, the locking portion provided on the connecting rod contacts the valve body and moves integrally to open and close the main valve portion, and the locking portion separates from the valve body and the connecting rod and the valve body move relative to each other to press the pressure-sensitive body to open the auxiliary valve portion, so that one connecting rod can open and close different valves.

[0042] The capacity control valve of the present invention is characterized in that:

[0043] The link includes a pressing portion that presses the pressure-sensitive body.

[0044] According to this feature, the pressure-sensitive body is reliably pressed by the pressing portion of the connecting rod, and the liquid refrigerant can be effectively discharged regardless of the pressure of the suction chamber, so that the cooling operation state can be set in a short time.

[0045] The capacity control valve of the present invention is characterized in that:

[0046] The first pressure is the suction pressure of the variable capacity compressor, the second pressure is the discharge pressure of the variable capacity compressor, the third pressure is the pressure of the crank chamber of the variable capacity compressor, and

[0047] The first pressure is a pressure of a crank chamber of the variable capacity compressor, the second pressure is a discharge pressure of the variable capacity compressor, and the third pressure is a suction pressure of the variable capacity compressor.

[0048] According to this feature, it is possible to cope with various variable capacity compressors.

[0049] In order to solve the above-mentioned problems, the control method of the capacity control valve of the present invention is characterized by:

[0050] When the auxiliary valve portion is in the open state, the main valve portion is changed from the closed state to the open state.

[0051] According to this feature, when discharging liquid refrigerant, the main valve portion is opened in a state where the force of the pressure sensitive body does not act on the valve body to increase the flow rate from the discharge chamber to the control chamber, thereby reducing the load on the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] Figure 1 It is a front sectional view of the capacity control valve involved in Example 1 of the present invention, showing the control state of the capacity control valve when the solenoid of the third valve chamber is in the "open" state under the low pressure state, the main valve is set to the open state, and the auxiliary valve is set to the closed state.

[0053] Figure 2It is a partially enlarged view of the valve body, valve body and solenoid of the capacity control valve involved in Example 1 of the present invention, showing the liquid refrigerant discharge state in which the solenoid of the third valve chamber is in the "open" state under the high-pressure state, the main valve is set to the closed state, and the auxiliary valve is set to the open state.

[0054] Figure 3 It is a partially enlarged view of the valve body, valve body and solenoid of the capacity control valve involved in Example 1 of the present invention, showing the state when the solenoid is in the "closed" state under the high pressure state of the third valve chamber, and the auxiliary valve part is maintained in the open state and the main valve is set to the open state.

[0055] Figure 4 It is a front cross-sectional view of the capacity control valve involved in Example 2 of the present invention, showing the control state of the capacity control valve when the solenoid of the third valve chamber is in the "open" state under the low pressure state, the main valve is set to the open state, and the auxiliary valve is set to the closed state.

[0056] Figure 5 It is a partially enlarged view of the valve body, valve body and solenoid of the capacity control valve involved in Example 2 of the present invention, showing the liquid refrigerant discharge state in which the solenoid of the third valve chamber is in the "open" state under the high-pressure state, the main valve is set to the closed state, and the auxiliary valve is set to the open state.

[0057] Figure 6 It is a partially enlarged view of the valve body, valve body and solenoid of the capacity control valve involved in Example 2 of the present invention, showing the state when the solenoid is in the "closed" state under the high pressure state of the third valve chamber, and the auxiliary valve portion is maintained in the open state and the main valve is set to the open state.

[0058] Figure 7 It is a front cross-sectional view showing a conventional capacity control valve.

[0059] Figure 8 This is a conventional capacity control valve, and shows the state of the capacity control valve when liquid refrigerant is discharged. DETAILED DESCRIPTION

[0060] Hereinafter, the method for implementing the present invention will be illustratively described according to the embodiments with reference to the accompanying drawings. The dimensions, materials, shapes and relative positions of the components described in the embodiments are not limited to these dimensions, materials, shapes and relative positions unless otherwise specified.

[0061] Example 1

[0062] refer to Figures 1 to 3 , the capacity control valve involved in the first embodiment of the present invention is described. Figure 1In the figure, reference numeral 1 denotes a capacity control valve. The capacity control valve 1 is mainly composed of a valve body 10 , a valve body 20 , a pressure sensing body 24 , and a solenoid 30 .

[0063] Below, reference Figure 1 and Figure 2 The structures constituting the capacity control valve 1 are described. The valve body 10 is made of metal such as brass, iron, aluminum, stainless steel, or synthetic resin material. The valve body 10 is a hollow cylindrical member having a through hole penetrating in the axial direction, and a first valve chamber 14, a second valve chamber 15 adjacent to the first valve chamber 14, and a third valve chamber 16 adjacent to the second valve chamber 15 are continuously arranged in the region of the through hole.

[0064] The second valve chamber 15 is connected to the second communication passage 12. The second communication passage 12 is connected to the discharge chamber (not shown) of the variable capacity compressor, and the fluid at the discharge pressure Pd (the second pressure involved in the present invention) can flow from the second valve chamber 15 into the third valve chamber 16 by opening and closing the capacity control valve 1.

[0065] The third valve chamber 16 is connected with the third communication passage 13. The third communication passage 13 is connected to the control chamber (not shown) of the variable capacity compressor, and through the opening and closing of the capacity control valve 1, the fluid of the discharge pressure Pd flowing from the second valve chamber 15 into the third valve chamber 16 flows out to the control chamber (crank chamber) of the variable capacity compressor, or the fluid of the control chamber pressure Pc (the third pressure involved in the present invention) flowing into the third valve chamber 16 flows out to the suction chamber of the variable capacity compressor through the intermediate communication passage 29 described later and the first valve chamber 14.

[0066] Furthermore, a first communication passage 11 is connected to the first valve chamber 14. The first communication passage 11 guides the fluid of the suction pressure Ps (the first pressure involved in the present invention) from the suction chamber of the variable capacity compressor to the pressure sensing body 24 via the intermediate communication passage 29 described later, thereby controlling the suction pressure of the compressor to a set value.

[0067] A hole portion 18 having a smaller diameter than the diameters of these chambers is continuously formed between the first valve chamber 14 and the second valve chamber 15, and the hole portion 18 slides with a labyrinth portion 21f described later to form a sealing portion that seals the first valve chamber 14 and the second valve chamber 15. In addition, a valve hole 17 having a smaller diameter than the diameters of these chambers is continuously provided between the second valve chamber 15 and the third valve chamber 16, and a main valve seat 15a is formed around the valve hole 17 on the side of the second valve chamber 15. The main valve seat 15a is separated from / contacted with a main valve portion 21c described later to control the communication between the second valve chamber 15 and the third valve chamber 16 by opening and closing.

[0068] A pressure-sensitive body 24 is arranged in the third valve chamber 16. In the pressure-sensitive body 24, one end of a metal bellows 24a is sealed and connected to a separation adjustment portion 24f. The bellows 24a is made of phosphor bronze, stainless steel, etc., but its spring constant is designed to be a specified value. The internal space of the pressure-sensitive body 24 is a vacuum or there is air. Moreover, the pressure-sensitive body 24 is configured so that pressure acts on the effective pressure-bearing area of ​​the bellows 24a of the pressure-sensitive body 24 to cause the pressure-sensitive body 24 to expand and contract. A head 24c is arranged on the free end side of the pressure-sensitive body 24, and an auxiliary valve seat 24d is formed on the head 24c. The auxiliary valve seat 24d contacts and separates with the auxiliary valve portion 23d described later to control the opening and closing of the connection between the third valve chamber 16 and the intermediate connecting passage 29.

[0069] Furthermore, a flange portion 24h pressed by a connecting rod 36 of the solenoid 30 described later is formed at the head portion 24c of the pressure-sensitive body 24. The pressure-sensitive body 24 is directly pressed by the connecting rod 36 to expand and contract, thereby opening and closing the auxiliary valve portion 23d. As described later, the pressure-sensitive body 24 expands and contracts according to the suction pressure Ps guided by the pressure-sensitive body 24 through the intermediate communication passage 29, and expands and contracts by the pressing force of the connecting rod 36.

[0070] The separation adjustment portion 24f of the pressure sensing body 24 is sealed and fixed in a manner to block the third valve chamber 16 of the valve body 10. In addition, if the separation adjustment portion 24f is screwed in and fixed by a set screw (not shown), the compression spring arranged in parallel in the bellows 24a or the spring force of the bellows 24a can be adjusted in the axial direction.

[0071] In addition, the first communication passage 11, the second communication passage 12, and the third communication passage 13 penetrate the circumferential surface of the valve body 10 in, for example, 2 to 6 equal parts. Moreover, three O-ring mounting grooves are provided in the axial direction on the outer circumferential surface of the valve body 10. Moreover, O-rings 47, 48, 49 for sealing between the valve body 10 and the mounting hole (not shown) of the housing fitted with the valve body 10 are installed in each of the mounting grooves, and each flow path of the first communication passage 11, the second communication passage 12, and the third communication passage 13 is constituted as an independent flow path.

[0072] Next, the valve body 20 will be described. The valve body 20 is mainly composed of a main valve body 21 including a hollow cylindrical component and a connector 23. First, the main valve body 21 will be described. The main valve body 21 is a hollow cylindrical component, and a labyrinth portion 21f is formed in the approximately central portion of the axial direction of its outer peripheral portion. The labyrinth portion 21f slides with the hole portion 18 formed between the first valve chamber 14 side and the second valve chamber 15 side to form a sealing portion that seals the first valve chamber 14 and the second valve chamber 15. As a result, the first valve chamber 14 and the second valve chamber 15 are configured as independent valve chambers.

[0073] The main valve body 21 is arranged on the first valve chamber 14 side and the second valve chamber 15 side with the labyrinth portion 21f interposed therebetween. A main valve portion 21c is formed at the end of the main valve body 21 arranged in the second valve chamber 15. The main valve portion 21c is separated from / contacted with the main valve seat 15a to control the opening and closing of the valve hole 17 connecting the second valve chamber 15 and the third valve chamber 16. The main valve portion 21c and the main valve seat 15a constitute the main valve 27. In addition, a shutoff valve portion 21a is formed at the end of the main valve body 21 arranged in the first valve chamber 14. The shutoff valve portion 21a contacts the end 32c of the magnetic core 32 when the solenoid 30 described later is "closed" to shut off the communication between the intermediate communication path 29 and the first valve chamber 14. The shutoff valve portion 21a and the end 32c of the magnetic core 32 constitute the shutoff valve 26. The shutoff valve portion 21 a and the main valve portion 21 c of the valve body 20 are formed so as to perform opening and closing operations in opposite directions to each other.

[0074] Next, the adapter 23 constituting the valve body 20 will be described. The adapter 23 is mainly composed of a large diameter portion 23c formed as a hollow cylindrical member and a large diameter, and a cylinder portion 23e formed with a smaller diameter than the large diameter portion 23c. The cylinder portion 23e is fitted with the open end portion on the main valve portion 21c side of the main valve body 21 and constitutes the valve body 20. As a result, an intermediate communication passage 29 penetrating in the axial direction is formed inside the main valve body 21 and the adapter 23, that is, inside the valve body 20. In addition, an auxiliary valve portion 23d is formed in the large diameter portion 23c of the adapter 23, and the auxiliary valve portion 23d contacts and separates from the auxiliary valve seat 24d formed on the head portion 24c of the pressure-sensitive body 24 to open and close the communication between the third valve chamber 16 and the intermediate communication passage 29. The auxiliary valve portion 23d and the auxiliary valve seat 24d constitute the auxiliary valve 28.

[0075] Next, the solenoid 30 will be described. The solenoid 30 includes a connecting rod 36, a plunger cylinder 38, an electromagnetic coil 31, a magnetic core 32 composed of a center column 32a and a base 32b, a plunger 35, a thin plate 34, and a solenoid housing 33. The plunger cylinder 38 is a hollow cylindrical member with a bottom and one side open. The plunger 35 is arranged to be movable in the axial direction relative to the plunger cylinder 38 between the plunger cylinder 38 and the center column 32a arranged inside the plunger cylinder 38. The magnetic core 32 is fitted with the valve body 10 and arranged between the plunger 35 and the valve body 10. The connecting rod 36 is arranged to penetrate the center column 32a of the magnetic core 32 and the valve body 20 arranged in the valve body 10, and the connecting rod 36 has a gap with the through hole 32e of the center column 32a of the magnetic core 32 and the intermediate communication path 29 of the valve body 20, and can move relative to the magnetic core 32 and the valve body 20. Furthermore, one end 36e of the connecting rod 36 is connected to the plunger 35, and the pressing portion 36d of the other end contacts the flange portion 24h of the head portion 24c of the pressure-sensitive body 24. Thus, the connecting rod 36 is driven by the electromagnetic force generated between the magnetic core 32 and the plunger 35, and the connecting rod 36 directly presses the pressure-sensitive body 24 to cause the pressure-sensitive body 24 to expand and contract.

[0076] Furthermore, the open end of the plunger cylinder 38 is sealed and fixed to the inner periphery of the base 32b of the magnetic core 32, and the solenoid housing 33 is sealed and fixed to the outer periphery of the base 32b. Furthermore, the electromagnetic coil 31 is arranged in a space surrounded by the plunger cylinder 38, the base 32b of the magnetic core 32, and the solenoid housing 33 without contacting the refrigerant, thereby preventing a decrease in insulation resistance.

[0077] Next, the spacer 41 constituting a part of the valve body 20 will be described. The spacer 41 is a cylindrical member having a base 41e and a collar 41c extending axially from the base 41e, and is fitted and fixed to the inner diameter portion of the valve body 20. The collar 41c is arranged to contact the step 21b formed between the isolation valve portion 21a and the main valve portion 21c in the inner diameter portion of the valve body 20, and a gap is formed between the step 21b and the spacer 41. A retaining ring 42 (the locking portion involved in the present invention) fixed to the connecting rod 36 is arranged in the gap. In addition, a flow hole 41d through which the refrigerant flows is formed in the spacer 41.

[0078] The retaining ring 42 fixed to the connecting rod 36 contacts the main valve portion side end surface 41b of the base 41e of the spacer 41 fixed to the valve body 20, so that the driving force of the connecting rod 36 of the solenoid 30 acts on the valve body 20 as a force in the valve opening direction of the main valve portion 21c. Conversely, the retaining ring 42 fixed to the connecting rod 36 contacts the step portion 21b of the valve body 20, so that the driving force of the solenoid 30 acts on the valve body 20 as a force in the valve closing direction of the main valve portion 21c.

[0079] Next, the spring 43 (the first urging member involved in the present invention) and the spring 44 (the second urging member involved in the present invention) disposed with the retaining ring 42 interposed therebetween will be described. The spring 43 is disposed between the magnetic core 32 and the spacer 41 of the valve body 20. Specifically, one end of the spring 43 contacts the magnetic core 32, and the other end contacts the cutoff valve portion side end surface 41a of the base 41e of the spacer 41 provided on the valve body 20. Thus, the urging force of the spring 43 acts on the valve body 20 in the valve closing direction of the main valve portion 21c.

[0080] On the other hand, the spring 44 is disposed between the pressure-sensitive body 24 and the connecting rod 36. Specifically, one end of the spring 44 contacts the step portion 36f formed on the connecting rod 36 between the pressing portion 36d of the connecting rod 36 and the retaining ring 42, and the other end contacts the flange portion 24h of the head portion 24c of the pressure-sensitive body 24. Thus, the force of the spring 44 acts on the valve body 20 in the valve opening direction of the main valve portion 21c via the retaining ring 42 and the spacer 41. In addition, the spring constant of the spring 44 is set to be greater than the spring constant of the spring 43, so that the force of the spring 44 is greater than the force of the spring 43.

[0081] The operation of the displacement control valve 1 having the above-described structure will be described. In addition, the flow path from the third valve chamber 16 to the first valve chamber 14 through the intermediate communication passage 29 will be referred to as a "Pc-Ps flow path" hereinafter. Also, the flow path from the second valve chamber 15 to the third valve chamber 16 through the valve hole 17 will be referred to as a "Pd-Pc flow path" hereinafter.

[0082] First, the stop state of the connecting rod 36, the movement of the connecting rod, and the movement of each valve when the connecting rod is stopped are described. First, when the solenoid 30 is not energized, the combined force of the force of the pressure-sensitive body 24 and the force of the spring 44 exceeds the force of the spring 43, so that the connecting rod 36 is pushed toward the spring 43 side, the retaining ring 42 contacts the spacer 41, and the valve body 20 moves in the valve opening direction of the main valve portion 21c, the main valve portion 21c is fully opened, and the isolation valve portion 21a contacts the end 32c of the magnetic core 32, and the isolation valve portion 21a becomes fully closed (refer to Figure 3 ).

[0083] Next, when the solenoid 30 is energized from the non-energized state, the connecting rod 36 is gradually driven in the forward direction (the direction in which the connecting rod 36 protrudes from the end 32c of the magnetic core 32 to the outside). At this time, the spacer 41 is pressed downward by the spring 43, and the retaining ring 42 fixed to the connecting rod 36 and the spacer 41 fixed to the valve body 20 move in a contacting state, and the connecting rod 36 and the valve body 20 move integrally. As a result, the isolation valve portion 21a opens from the fully closed state, and the main valve portion 21c is gradually tightened from the fully open state (refer to Figure 1 ).

[0084] If the connecting rod 36 is further driven in the forward direction, the isolation valve portion 21a becomes fully open, and the main valve portion 21c contacts the main valve seat 15a and becomes fully closed, so that the movement of the valve body 20 stops. If the connecting rod 36 is further driven in the forward direction from this state, the retaining ring 42 separates from the spacer 41, and the connecting rod 36 moves relative to the main valve body 21, and the pressing portion 36d of the connecting rod 36 presses the flange portion 24h of the pressure-sensitive body 24 to shrink the pressure-sensitive body 24, thereby forcibly opening the auxiliary valve portion 23d (refer to Figure 2 After the auxiliary valve portion 23d is opened, if the connecting rod 36 is further driven in the forward direction, the connecting rod 36 stops because the stopper ring 42 contacts the step portion 21b of the valve body 20.

[0085] Next, according to Figure 1The control state of the capacity control valve 1 is described. The control state is a state controlled in the following manner, that is, when the auxiliary valve portion 23d is closed, the main valve portion 21c is set to a predetermined opening by the solenoid 30, so that the pressure of the suction chamber of the variable capacity compressor becomes the set value Pset. In this state, the fluid of the suction pressure Ps flowing from the suction chamber of the variable capacity compressor through the first communication passage 11 into the first valve chamber 14 passes through the intermediate communication passage 29 and acts on the pressure-sensitive body 24. The main valve portion 21c stops at a position where the force of the spring 43 in the valve closing direction, the force of the spring 44 in the valve opening direction, the force of the solenoid 30, and the force of the pressure-sensitive body 24 that expands and contracts according to the suction pressure Ps reach a balance. However, the suction pressure Ps sometimes changes due to external disturbances, etc. For example, if the pressure Ps of the suction chamber becomes higher than the set value Pset, the pressure-sensitive body 24 contracts and the opening of the main valve portion 21c becomes smaller. As a result, the Pd-Pc flow path becomes narrower, so the amount of refrigerant of the discharge pressure Pd flowing from the discharge chamber into the crank chamber decreases and the pressure in the crank chamber decreases. As a result, the inclination angle of the compressor inclined plate becomes larger, the discharge capacity of the compressor increases, and the discharge pressure decreases. On the contrary, if the pressure Ps in the suction chamber becomes lower than the set value Pset, the pressure-sensitive body 24 extends and the opening of the main valve portion 21c becomes larger. As a result, the Pd-Pc flow path expands, so the amount of refrigerant of the discharge pressure Pd flowing from the discharge chamber into the crank chamber increases and the pressure in the crank chamber increases. As a result, the inclination angle of the compressor inclined plate becomes smaller, the compressor reduces the discharge capacity, and the discharge pressure increases. In this way, the capacity control valve 1 can be used to control the pressure of the suction chamber of the variable capacity compressor to the set value Pset.

[0086] Next, according to Figure 2The liquid refrigerant discharge state of the capacity control valve 1 is described. After the compressor is stopped for a long time, liquid refrigerant (refrigerant that is cooled and liquefied during storage) is accumulated in the crank chamber. Therefore, in order to ensure the specified discharge pressure and discharge flow rate from the start of the compressor, the liquid refrigerant needs to be discharged as quickly as possible. When the liquid refrigerant is discharged, the pressure of the third valve chamber 16 connected to the crank chamber becomes high pressure and the suction pressure Ps also becomes high pressure. As a result, the pressure-sensitive body 24 contracts, and the valve body 20 is pressed downward by the spring 43, so that the main valve part 21c becomes a closed valve state and the auxiliary valve part 23d becomes an open valve state. In this state, the liquid refrigerant can also be discharged from the crank chamber to the suction chamber through the Pc-Ps flow path. However, as the discharge of the liquid refrigerant progresses, the pressure of the third valve chamber 16 and the suction pressure Ps gradually decrease, so the opening of the auxiliary valve part 23d gradually becomes smaller, resulting in a longer time until the discharge of the liquid refrigerant is completed. Then, the solenoid 30 is driven in the forward direction to press the pressure-sensitive body 24 through the connecting rod 36, so that the auxiliary valve portion 23d is forcibly set to the fully open state. As a result, the auxiliary valve portion 23d is kept in the fully open state, so that the opening degree of the auxiliary valve portion 23d does not change from the start of liquid refrigerant discharge to the completion of liquid refrigerant discharge, and the liquid refrigerant can be discharged from the crank chamber to the suction chamber via the Pc-Ps flow path in a short time.

[0087] Furthermore, in the previous liquid refrigerant discharge operation, only the aspect of how to complete the discharge of the liquid refrigerant in a short time regardless of the engine load was focused on. However, sometimes, even when the liquid refrigerant is discharged, when the engine output is high, it is desirable to reduce the load on the load compressor. Furthermore, when the liquid refrigerant is discharged, the auxiliary valve portion 23d is in an open valve state, so the force from the pressure-sensitive body 24 does not act on the valve body 20, and thus there is also a problem that it is difficult to quickly drive the valve body 20. The capacity control valve 1 involved in the present invention can easily drive the valve body 20 even when the liquid refrigerant is discharged.

[0088] Below, according to Figure 3The operation of the capacity control valve 1 when the engine load is reduced when the liquid refrigerant is discharged is described. When the engine load is reduced when the liquid refrigerant is discharged, the solenoid 30 is set to "closed", and the magnetic attraction Fsol between the magnetic core 32 and the plunger 35 becomes zero. At this time, the upward pressure and the downward pressure acting on the valve body 20 are set to maintain balance, so the main force acting on the valve body 20 becomes the force of the spring 44 and the spring 43. Here, the force of the spring 44 is set to be greater than the force of the spring 43, so the connecting rod 36 is pushed up by the force of the spring 44, the retaining ring 42 contacts the spacer 41, and the valve body 20 is driven, so that the main valve part 21c becomes fully open. If the main valve part 21c becomes fully open, the amount of refrigerant flowing into the crank chamber from the discharge chamber of the compressor through the Pd-Pc flow path increases, the pressure Pc in the crank chamber becomes higher, and the compressor operates at the minimum capacity. In this way, when discharging liquid refrigerant, when the auxiliary valve portion 23d is in an open state, even if force does not act on the valve body 20 from the pressure-sensitive body 24, the load on the compressor can be reduced by setting the main valve portion 21c from a fully closed state to a fully open state, thereby reducing the load on the engine when discharging liquid refrigerant.

[0089] Furthermore, in an operating state in which the pressure of the suction chamber of the compressor is controlled to be a set value Pset by the capacity control valve 1, even when it is necessary to reduce the load on the engine, the load on the engine can be reduced by setting the solenoid 30 to a non-energized state and the main valve portion 21c to a fully open state, as described above.

[0090] Thus, during the period from the fully open state to the fully closed state of the main valve portion 21c, the connecting rod 36 moves integrally with the valve body 20, and after the main valve portion 21c is fully closed, the connecting rod 36 moves relative to the valve body 20 to press the pressure-sensitive body 24, thereby enabling the auxiliary valve portion 23d to be opened. That is, one connecting rod 36 can open and close different main valve portions 21c and auxiliary valve portions 23d. Furthermore, the spring constant of the spring 44 is set to be greater than the spring constant of the spring 43, so that the force of the spring 44 is greater than the force of the spring 43, and thus the opening and closing states of the main valve portion 21c and the auxiliary valve portion 23d can be opened and closed in all combinations. That is, it can be set to open with respect to the main valve portion 21c and the auxiliary valve portion 23d is open, open with respect to the main valve portion 21c and the auxiliary valve portion 23d is closed, closed with respect to the main valve portion 21c and the auxiliary valve portion 23d is open, and closed with respect to the main valve portion 21c and the auxiliary valve portion 23d is closed.

[0091] Example 2

[0092] refer to Figures 4 to 6 , the capacity control valve involved in the second embodiment of the present invention is described. Figure 4In FIG. 1 , reference numeral 100 denotes a capacity control valve. The capacity control valve 100 is mainly composed of a valve body 110 , a valve body 120 , a pressure sensing body 124 , and a solenoid 130 .

[0093] Below, reference Figure 4 and Figure 5 The components constituting the displacement control valve 100 will be described. The displacement control valve 100 is mainly composed of a valve body 110 , a valve body 120 , a pressure sensing body 124 , and a solenoid 130 .

[0094] The valve body 110 is made of metal such as brass, iron, aluminum, stainless steel, or synthetic resin material, etc. The valve body 110 is a hollow cylindrical member having a through hole extending therethrough in the axial direction, and a first valve chamber 114, a second valve chamber 115 adjacent to the first valve chamber 114, and a third valve chamber 116 adjacent to the second valve chamber 115 are continuously arranged in the region of the through hole.

[0095] The second valve chamber 115 is connected to the second communication passage 112. The second communication passage 112 is connected to the discharge chamber (not shown) of the variable capacity compressor, and the fluid at the discharge pressure Pd can flow from the second valve chamber 115 into the third valve chamber 116 by opening and closing the capacity control valve 100.

[0096] The third valve chamber 116 is connected with a third communication passage 113. The third communication passage 113 is connected to a control chamber (not shown) of the variable capacity compressor, and through the opening and closing of the capacity control valve 100, the fluid of the discharge pressure Pd flowing from the second valve chamber 115 into the third valve chamber 116 flows out to the control chamber (crank chamber) of the variable capacity compressor, or the fluid of the control chamber pressure Pc flowing into the third valve chamber 116 flows out to the suction chamber of the variable capacity compressor through the intermediate communication passage 129 described later and the first valve chamber 114.

[0097] The first valve chamber 114 is connected to a first communication passage 111. In the first communication passage 111, fluid at a suction pressure Ps from a suction chamber of the variable displacement compressor is guided to the pressure sensing body 124 via an intermediate communication passage 129 to be described later, thereby controlling the suction pressure of the compressor to a set value.

[0098] A hole portion 118 having a smaller diameter than the diameters of the first valve chamber 114 and the second valve chamber 115 is continuously formed between the first valve chamber 114 and the second valve chamber 115, and the hole portion 118 slides with a labyrinth portion 121f described later to form a sealing portion that seals the first valve chamber 114 and the second valve chamber 115. In addition, a valve hole 117 having a smaller diameter than the diameters of the second valve chamber 115 and the third valve chamber 116 is continuously provided between the second valve chamber 115 and the third valve chamber 116, and a main valve seat 115a is formed around the valve hole 117 on the side of the second valve chamber 115. The main valve seat 115a is separated from / contacted with a main valve portion 121c described later to control the opening and closing of the communication between the second valve chamber 115 and the third valve chamber 116.

[0099] A pressure-sensitive body 124 is arranged in the third valve chamber 116. In the pressure-sensitive body 124, one end of a metal bellows 124a is sealed and connected to a separation adjustment portion 124f. The bellows 124a is made of phosphor bronze, stainless steel, etc., but its spring constant is designed to be a specified value. The internal space of the pressure-sensitive body 124 is a vacuum or there is air. Moreover, the pressure-sensitive body 124 is configured so that pressure acts on the effective pressure-bearing area of ​​the bellows 124a of the pressure-sensitive body 124 to cause the pressure-sensitive body 124 to expand and contract. A head 124c is arranged on the free end side of the pressure-sensitive body 124, and an auxiliary valve seat 124d is formed on the head 124c. The auxiliary valve seat 124d contacts and separates with the auxiliary valve portion 123d described later to control the opening and closing of the connection between the third valve chamber 116 and the intermediate connecting passage 129.

[0100] The head 124c of the pressure sensing body 124 is compressed by the connecting rod 136 of the solenoid 130, and opens and closes the auxiliary valve portion 123d. As described later, the pressure sensing body 124 expands and contracts according to the suction pressure Ps guided by the pressure sensing body 124 through the intermediate communication passage 129, and expands and contracts due to the pressing force of the connecting rod 136.

[0101] The separation adjustment portion 124f of the pressure sensing body 124 is sealed and fixed in a manner to block the third valve chamber 116 of the valve body 110. In addition, if the separation adjustment portion 124f is screwed in and fixed by a set screw (not shown), the compression spring arranged in parallel in the bellows 124a or the spring force of the bellows 124a can be adjusted in the axial direction.

[0102] In addition, the first communication passage 111, the second communication passage 112, and the third communication passage 113 penetrate the circumference of the valve body 110 in, for example, 2 to 6 equal parts. Moreover, three O-ring mounting grooves are provided in the axial direction on the outer circumference of the valve body 110. Moreover, O-rings 147, 148, 149 are installed in each mounting groove to seal the valve body 110 and the mounting hole (not shown) of the housing in which the valve body 110 is fitted, and each flow path of the first communication passage 111, the second communication passage 112, and the third communication passage 113 is configured as an independent flow path.

[0103] Next, the valve body 120 will be described. The valve body 120 is mainly composed of a main valve body 121 including a hollow cylindrical component and a connector 123. First, the main valve body 121 will be described. The main valve body 121 is a hollow cylindrical component, and a labyrinth portion 121f is formed in the approximately central portion of the axial direction of its outer peripheral portion. The labyrinth portion 121f slides with the hole portion 118 formed between the first valve chamber 114 side and the second valve chamber 115 side to form a sealing portion that seals the first valve chamber 114 and the second valve chamber 115. As a result, the first valve chamber 114 and the second valve chamber 115 are configured as independent valve chambers.

[0104] The main valve body 121 is arranged on the first valve chamber 114 side and the second valve chamber 115 side with the labyrinth portion 121f interposed therebetween. A main valve portion 121c is formed at the end of the main valve body 121 arranged in the second valve chamber 115. The main valve portion 121c is separated from / contacted with the main valve seat 115a to control the opening and closing of the valve hole 117 connecting the second valve chamber 115 and the third valve chamber 116. The main valve portion 121c and the main valve seat 115a constitute a main valve 127. In addition, a shutoff valve portion 121a is formed at the end of the main valve body 121 arranged in the first valve chamber 114. The shutoff valve portion 121a contacts the end 132c of the magnetic core 132 when the solenoid 130 described later is "closed" to shut off the communication between the intermediate communication path 129 and the first valve chamber 114. The shutoff valve portion 121a and the end portion 132c of the magnetic core 132 constitute the shutoff valve 126. The shutoff valve portion 121a and the main valve portion 121c are formed so as to perform opening and closing operations in opposite directions to each other.

[0105] Next, the adapter 123 constituting the valve body 120 will be described. The adapter 123 is mainly composed of a large diameter portion 123c which is a hollow cylindrical member and is formed with a large diameter, and a cylinder portion 123e which is formed with a smaller diameter than the large diameter portion 123c. The cylinder portion 123e is fitted with the open end portion on the main valve portion 121c side of the main valve body 121 and constitutes the valve body 120. Thus, an intermediate communication passage 129 penetrating in the axial direction is formed inside the main valve body 121 and the adapter 123, that is, inside the valve body 120. In addition, an auxiliary valve portion 123d is formed at the front end portion of the large diameter portion 123c, and the auxiliary valve portion 123d contacts and separates from the auxiliary valve seat 124d of the pressure sensing body 124 to open and close the communication between the third valve chamber 116 and the intermediate communication passage 129. The auxiliary valve portion 123d and the auxiliary valve seat 124d constitute an auxiliary valve 128.

[0106] Next, the solenoid 130 is described. The solenoid 130 includes a connecting rod 136, a plunger cylinder 138, an electromagnetic coil 131, a magnetic core 132 composed of a center column 132a and a base 132b, a plunger 135, a thin plate 134, and a solenoid housing 133. The plunger cylinder 138 is a hollow cylindrical member with a bottom and one side open. The plunger 135 is arranged between the plunger cylinder 138 and the center column 132a arranged inside the plunger cylinder 138 so as to be movable in the axial direction relative to the plunger cylinder 138. The magnetic core 132 is fitted with the valve body 110 and is arranged between the plunger 135 and the valve body 110. The connecting rod 136 is arranged to penetrate the central column 132a of the magnetic core 132 and the valve body 120 arranged in the valve body 110, and the connecting rod 136 has a gap with the through hole 132e of the central column 132a of the magnetic core 132 and the intermediate communication path 129 of the valve body 120, and can move relative to the magnetic core 132 and the valve body 120. In addition, one end 136e of the connecting rod 136 is connected to the plunger 135, and the pressing part 136d of the other end is in contact with the head 124c of the pressure-sensitive body 124. Thus, the connecting rod 136 is driven by the electromagnetic force generated between the magnetic core 132 and the plunger 135, and the connecting rod 136 directly presses the pressure-sensitive body 124 to cause the pressure-sensitive body 124 to expand and contract.

[0107] A spring 137 (second urging member of the present invention) is disposed between the core 132 and the plunger 135 to urge the plunger 135 away from the core 132. Thus, the urging force of the spring 137 acts in a direction to open the main valve portion 121c of the valve body 120.

[0108] Furthermore, the open end of the plunger cylinder 138 is sealed and fixed to the inner periphery of the base 132b of the magnetic core 132, and the solenoid housing 133 is sealed and fixed to the outer periphery of the base 132b. Furthermore, the electromagnetic coil 131 is arranged in a space surrounded by the plunger cylinder 138, the base 132b of the magnetic core 132, and the solenoid housing 133 without contacting the refrigerant, thereby preventing a decrease in insulation resistance.

[0109] Next, the retaining ring 142 (the locking portion involved in the present invention) constituting a part of the connecting rod 136 is described. A connecting passage is formed in the retaining ring 142 in a manner that does not hinder the connection between the third valve chamber 116 and the intermediate connecting passage 129. The retaining ring 142 is a disc-shaped component, and is fitted and fixed to the connecting rod 136 in a manner that is located between the connector 123 and the head 124c of the pressure-sensitive body 124. The retaining ring 142 contacts the connector 123 of the valve body 120, whereby the driving force of the connecting rod 136 of the solenoid 130 acts on the valve body 120 as a force in the valve opening direction of the main valve portion 121c. On the contrary, the retaining ring 142 fixed to the connecting rod 136 contacts the head 124c of the pressure-sensitive body 124, and the driving force of the connecting rod 136 of the solenoid 130 directly presses the pressure-sensitive body 124 to cause the pressure-sensitive body 124 to expand and contract.

[0110] Here, a convex portion 124h is formed at the center of the head portion 124c of the pressure-sensitive body 124, and a convex portion (not shown) is also formed at the center of the separation adjustment portion 124f of the pressure-sensitive body 124 that faces the auxiliary valve seat 124d. Furthermore, the pressure-sensitive body 124 is compressed by the contact of the retaining ring 142 fixed to the connecting rod 136 with the head portion 124c of the pressure-sensitive body 124. When the pressure-sensitive body 124 contracts by a predetermined amount, the convex portion 124h contacts the convex portion of the separation adjustment portion 124f to restrict the deformation of the pressure-sensitive body 124, and the movement of the connecting rod 136 is also restricted.

[0111] Next, the spring 143 (the first biasing member involved in the present invention) is described. The spring 143 is disposed between the solenoid 130 and the valve body 120. Specifically, one end of the spring 143 contacts the magnetic core 132, and the other end contacts the step portion 121b formed between the isolation valve portion 121a and the labyrinth portion 121f of the valve body 120. Thus, the biasing force of the spring 143 acts in the direction of closing the main valve portion 121c of the valve body 120.

[0112] The spring constant of the spring 137 (second urging member) provided between the magnetic core 132 and the plunger 135 is set larger than the spring constant of the spring 143 (first urging member), so that the urging force of the spring 137 is larger than the urging force of the spring 143 .

[0113] The operation of the connecting rod 136 and the operation of each valve portion of the displacement control valve 100 having the above-described structure will be described. In addition, hereinafter, the flow path from the third valve chamber 116 to the first valve chamber 114 through the intermediate communication passage 129 will be referred to as a "Pc-Ps flow path". Also, hereinafter, the flow path from the second valve chamber 115 to the third valve chamber 116 through the valve hole 117 will be referred to as a "Pd-Pc flow path".

[0114] First, refer to Figure 6The stop state of the connecting rod 136, the operation of the connecting rod 136, and the operation of each valve when the connecting rod 136 is stopped are described. First, in the non-energized state of the solenoid 130, the force of the pressure-sensitive body 124 and the spring 137 ( Figure 4 ) exceeds the force of the spring 143, so the connecting rod 136 is pushed upward, the retaining ring 142 contacts the connector 123, the connector 123 is pressed and the main valve portion 121c is fully opened, the isolating valve portion 121a contacts the end 132c of the magnetic core 132 and the isolating valve portion 121a becomes fully closed.

[0115] Next, if the solenoid 130 is energized from the non-energized state, the connecting rod 136 is gradually driven in the forward direction (the direction in which the connecting rod 136 protrudes outward from the end 132c of the magnetic core 132). At this time, the valve body 120 is pressed downward by the spring 143, and the retaining ring 142 fixed to the connecting rod 136 and the adapter 123 of the valve body 120 move in a contact state, and the connecting rod 136 and the valve body 120 also move integrally. As a result, the isolation valve portion 121a opens from the fully closed state, and the opening of the main valve portion 121c is gradually tightened (refer to Figure 4 ).

[0116] If the connecting rod 136 is further driven in the forward direction, Figure 5 As shown, the shutoff valve portion 121a becomes fully open, and the main valve portion 121c contacts the main valve seat 115a and becomes fully closed, so that the movement of the main valve body 121 stops. If the connecting rod 136 is driven further in the forward direction from this state, the connecting rod 136 moves relative to the main valve body 121, and the retaining ring 142 separates from the connector 123. If the connecting rod 136 is further driven, the retaining ring 142 of the connecting rod 136 contacts the head 124c of the pressure-sensitive body 124, and presses the head 124c to shrink the pressure-sensitive body 124, thereby forcibly opening the auxiliary valve portion 123d. Moreover, if the pressure-sensitive body 124 shrinks a specified amount, the convex portion 124h contacts the convex portion (not shown) of the partition adjustment portion 124f to limit the deformation of the pressure-sensitive body 124, and the movement of the connecting rod 136 also stops (refer to Figure 5 In addition, instead of pressing the head 124c of the pressure-sensitive body 124 by the retaining ring 142 to cause the pressure-sensitive body 124 to contract, the pressing portion 136d of the connecting rod 136 may press the head 124c of the pressure-sensitive body 124 to cause the pressure-sensitive body 124 to contract and force the auxiliary valve portion 123d to open.

[0117] Next, according to Figure 4The control state of the capacity control valve 100 is described. The control state is a state controlled in the following manner, that is, when the auxiliary valve portion 123d is closed, the main valve portion 121c is set to a predetermined opening by the solenoid 130, so that the pressure of the suction chamber of the variable capacity compressor becomes the set value Pset. In this state, the fluid of the suction pressure Ps flowing from the suction chamber of the variable capacity compressor through the first communication path 111 into the first valve chamber 114 acts on the pressure-sensitive body 124 through the intermediate communication path 129. As a result, the main valve portion 121c stops at a position where the force of the spring 143 in the valve closing direction, the force of the spring 137 in the valve opening direction, the force of the solenoid 130, and the force of the pressure-sensitive body 124 that expands and contracts according to the suction pressure Ps reach a balance. However, sometimes the pressure Ps of the suction chamber becomes higher than the set value Pset due to disturbances or the like. For example, if the pressure Ps in the suction chamber becomes higher than the set value Pset due to disturbance or the like, the pressure-sensitive body 124 contracts and the opening of the main valve portion 121c becomes smaller. As a result, the Pd-Pc flow path becomes narrower, so the amount of refrigerant of the discharge pressure Pd flowing from the discharge chamber into the crank chamber decreases and the pressure in the crank chamber decreases. As a result, the inclination angle of the compressor inclined plate becomes larger, the discharge capacity of the compressor increases, and the discharge pressure decreases. On the contrary, if the pressure Ps in the suction chamber becomes lower than the set value Pset, the pressure-sensitive body 124 extends and the opening of the main valve portion 121c becomes larger. As a result, the Pd-Pc flow path becomes larger, so the amount of refrigerant of the discharge pressure Pd flowing from the discharge chamber into the crank chamber increases and the pressure in the crank chamber increases. As a result, the inclination angle of the compressor inclined plate becomes smaller, the discharge capacity decreases, and the discharge pressure increases. In this way, the pressure of the suction chamber of the variable capacity compressor can be controlled to the set value Pset by the capacity control valve 100.

[0118] Next, according to Figure 5The operation of the capacity control valve 100 when discharging liquid refrigerant (refrigerant liquefied by cooling during storage) after the compressor is stopped for a long time and the liquid refrigerant is accumulated in the crank chamber is described. When discharging the liquid refrigerant, the pressure of the third valve chamber 116 connected to the crank chamber becomes high pressure, and the suction pressure Ps also becomes high pressure, so the pressure-sensitive body 124 contracts due to the high-pressure suction pressure Ps, and the auxiliary valve portion 123d becomes an open valve state. The solenoid 130 is driven in the forward direction, the main valve portion 121c becomes a fully closed state, and the retaining ring 142 of the connecting rod 136 presses the pressure-sensitive body 124 to force the auxiliary valve portion 123d to open, so that the auxiliary valve portion 123d becomes a fully open state. The pressure-sensitive body 124 is pressed by the connecting rod 136 and the auxiliary valve portion 123d is kept in a fully open state. Therefore, the opening degree of the auxiliary valve portion 123d does not change from the start of liquid refrigerant discharge to the completion of liquid refrigerant discharge, and can be kept in a fully open state, so that liquid refrigerant can be discharged from the crank chamber to the suction chamber via the Pc-Ps flow path in a short time. In contrast, when the auxiliary valve portion 123d is forcibly opened without pressing the pressure-sensitive body 124 by the connecting rod 136 of the solenoid 130, the pressure of the third valve chamber 116 and the suction pressure Ps decrease as the discharge of liquid refrigerant advances, so the opening degree of the auxiliary valve portion 123d gradually decreases, thereby prolonging the time until the discharge of liquid refrigerant is completed, and therefore the set discharge amount cannot be ensured in a short time.

[0119] Furthermore, when performing the conventional liquid refrigerant discharge operation, attention was only paid to how to complete the discharge of the liquid refrigerant in a short time, and therefore, no control was performed to reduce the engine load during the liquid refrigerant discharge operation. Furthermore, on the other hand, when discharging the liquid refrigerant, the auxiliary valve portion 123d is in an open valve state, so that the force does not act from the pressure sensing body 124 on the valve body 120, and thus it is difficult to quickly drive the valve body 120. The capacity control valve 100 according to the present invention can easily drive the valve body 120 even when discharging the liquid refrigerant.

[0120] according to Figure 6The operation of the capacity control valve 100 when the engine load is reduced when the liquid refrigerant is discharged is described. When the engine load is reduced when the liquid refrigerant is discharged, the solenoid 130 is "closed" and the magnetic attraction Fsol between the magnetic core 132 and the plunger 135 becomes zero. At this time, the upward pressure and the downward pressure acting on the valve body 120 are set to maintain balance, so the main force acting on the valve body 120 is the force of the spring 137 and the spring 143, and the force of the spring 137 is set to be greater than the force of the spring 143. Therefore, the connecting rod 136 is pushed up by the force of the spring 137, the retaining ring 142 contacts the adapter 123, and the valve body 120 is driven, and the main valve part 121c becomes fully open. If the main valve part 121c becomes fully open, the amount of refrigerant flowing into the crank chamber from the discharge chamber of the compressor through the Pd-Pc flow path increases, the pressure Pc in the crank chamber becomes higher, and the compressor operates at the minimum capacity. In this way, when liquid refrigerant is discharged, when the auxiliary valve portion 123d is in the open valve state, even when force does not act on the valve body 120 from the pressure-sensitive body 124, the load on the compressor can be reduced by setting the main valve portion 121c from the fully closed state to the fully open state, thereby reducing the engine load even when liquid refrigerant is discharged.

[0121] Furthermore, when the load on the engine is to be reduced while the pressure in the suction chamber of the compressor is controlled to be a set value Pset by the capacity control valve 100, the solenoid 130 is set to a non-energized state, the main valve portion 121c is set to a fully open state, and the amount of refrigerant at a Pd pressure flowing from the discharge chamber of the compressor into the crank chamber through the Pd-Pc flow path is increased, as described above, and the compressor is operated at a minimum capacity, thereby enabling operation to reduce the load on the engine.

[0122] Thus, during the period from when the main valve portion 121c changes from a fully open state to a fully closed state, the connecting rod 136 moves integrally with the valve body 120. After the main valve portion 121c is fully closed, the connecting rod 136 moves relative to the valve body 120 and presses the pressure-sensitive body 124, thereby opening the auxiliary valve portion 123d. That is, one connecting rod 136 can open and close different main valve portions 121c and auxiliary valve portions 123d. Furthermore, the spring constant of the spring 137 is set to be greater than the spring constant of the spring 143, so that the acting force of the spring 137 is greater than the acting force of the spring 143, and thus the opening and closing states of the main valve portion 121c and the auxiliary valve portion 123d can be opened and closed in all states. That is, the auxiliary valve portion 123d can be opened relative to the main valve portion 121c, opened relative to the main valve portion 121c and closed, opened relative to the main valve portion 121c and closed, and closed relative to the main valve portion 121c and closed.

[0123] As mentioned above, although the embodiment of the present invention is described based on the drawings, the specific structure is not limited to these embodiments, and even if there are changes and additions within the scope that does not depart from the gist of the present invention, they are also included in the present invention.

[0124] For example, in the second embodiment, the spring 143 is arranged on the outer peripheral side of the main valve body 121 in the first valve chamber 114, but the present invention is not limited thereto. For example, the spring 143 may be arranged on the inner peripheral side of the main valve body 121 in the first valve chamber 114, with one end in contact with the magnetic core 132 and the other end in contact with the valve body 120.

[0125] Furthermore, in the above-mentioned embodiment, the first pressure of the first valve chamber 14 (114) is set to the suction pressure Ps of the variable capacity compressor, the second pressure of the second valve chamber 15 (115) is set to the discharge pressure Pd of the variable capacity compressor, and the third pressure of the third valve chamber 16 (116) is set to the pressure Pc of the crank chamber of the variable capacity compressor, but it is not limited to this. The first pressure of the first valve chamber 14 (114) can be set to the pressure Pc of the crank chamber of the variable capacity compressor, the second pressure of the second valve chamber 15 (115) can be set to the discharge pressure Pd of the variable capacity compressor, and the third pressure of the third valve chamber 16 (116) can be set to the suction pressure Ps of the variable capacity compressor to cope with various variable capacity compressors.

[0126] Explanation of symbols

[0127] 1-capacity control valve, 10-valve body, 11-first communication passage, 12-second communication passage, 13-third communication passage, 14-first valve chamber, 15-second valve chamber, 15a-main valve seat, 16-third valve chamber, 17-valve hole, 20-valve body, 21-main valve body, 21a-blocking valve part, 21c-main valve part, 23-adapter, 23d-auxiliary valve part, 24-pressure sensing body, 24a-bellows, 24d-auxiliary valve seat, 27-main valve, 28 - auxiliary valve, 29 - intermediate communication passage, 30 - solenoid portion, 31 - electromagnetic coil, 32 - magnetic core, 33 - solenoid housing, 35 - plunger, 36 - connecting rod, 38 - plunger cylinder, 41 - spacer, 42 - retaining ring (locking portion), 43 - spring (first force applying member), 44 - spring (second force applying member), 100 - capacity control valve, 110 - valve body, 111 - first communication passage, 112 - second communication passage, 113 - third communication passage, 1 14-1st valve chamber, 115-2nd valve chamber, 115a-main valve seat, 116-3rd valve chamber, 117-valve hole, 120-valve body, 121-main valve body, 121a-blocking valve part, 121c-main valve part, 123-adapter, 123d-auxiliary valve part, 124-pressure sensing body, 124a-bellows, 124d-auxiliary valve seat, 127-main valve, 128-auxiliary valve, 129-intermediate connecting passage, 130-solenoid, 131- Electromagnetic coil, 132-magnetic core, 133-solenoid housing, 135-plunger, 136-connecting rod, 137-spring (second force-applying component), 138-plunger cylinder, 142-retaining ring (locking component), 143-spring (first force-applying component), Fsol-magnetic attraction force, Ps-suction pressure (first pressure) (third pressure), Pd-discharge pressure, Pc-control chamber pressure (third pressure) (first pressure), Pset-suction pressure setting value.

Claims

1. A capacity control valve for controlling a flow rate or a pressure of a variable capacity compressor according to a valve opening of a valve portion, wherein the capacity control valve comprises: A valve body having a first communication passage for allowing a fluid of a first pressure to flow, a second communication passage arranged adjacent to the first communication passage and allowing a fluid of a second pressure to flow, a third communication passage for allowing a fluid of a third pressure to flow, and a main valve seat arranged in a valve hole connecting the second communication passage and the third communication passage; a pressure-sensitive body disposed in the valve body on the third communication passage side and expanding and contracting in response to the surrounding pressure; A solenoid comprising a connecting rod having a locking portion at one end and a plunger at the other end, a magnetic core disposed between the plunger and the valve body, and a second urging member disposed between the magnetic core and the plunger; a valve body having an intermediate communication passage connecting the first communication passage and the third communication passage, a main valve portion that is separated from / contacted with the main valve seat to open and close the valve hole, an auxiliary valve portion that is separated from / contacted with the pressure-sensitive body to open and close the communication between the third communication passage and the intermediate communication passage, and a shutoff valve portion that is separated from / contacted with the magnetic core of the solenoid to open and close the communication between the first communication passage and the intermediate communication passage; and A first force applying member is disposed between the magnetic core and the valve body. The locking portion of the link moves in a first direction to contact the valve body to open the main valve portion, and moves relative to the valve body in a direction opposite to the first direction when the main valve portion is closed to press the pressure sensitive body.

2. The capacity control valve according to claim 1, characterized in that: The urging force of the second urging member urging the main valve portion in the valve opening direction is greater than the urging force of the first urging member urging the main valve portion in the valve closing direction.

3. The capacity control valve according to claim 1 or 2, characterized in that: The first pressure is a suction pressure of the variable capacity compressor, the second pressure is a discharge pressure of the variable capacity compressor, and the third pressure is a pressure of a crank chamber of the variable capacity compressor.

4. The capacity control valve according to claim 1 or 2, characterized in that: The first pressure is a pressure of a crank chamber of the variable capacity compressor, the second pressure is a discharge pressure of the variable capacity compressor, and the third pressure is a suction pressure of the variable capacity compressor.

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