JP6135521B2 - Variable capacity swash plate compressor - Google Patents

Description

  The present invention relates to a variable displacement swash plate compressor in which a piston moored to a swash plate reciprocates with a stroke corresponding to the inclination angle of the swash plate.

  As this type, for example, Patent Document 1 discloses a structure in which a movable body capable of changing an inclination angle of a swash plate is connected to the swash plate. The moving body is movable in the axial direction of the rotation shaft by changing the pressure inside the control pressure chamber as the control gas is introduced into the control pressure chamber formed in the housing. . And the inclination angle of a swash plate is changed with the movement to the axial direction of the rotating shaft in this moving body.

  Specifically, when the pressure in the control pressure chamber increases and the pressure in the control pressure chamber approaches the pressure in the discharge pressure region, the moving body moves toward one end in the axial direction of the rotation shaft. The inclination angle of the swash plate increases with the movement of the rotary shaft toward one end in the axial direction of the moving body. When the pressure in the control pressure chamber decreases and the pressure in the control pressure chamber approaches the pressure in the suction pressure region, the moving body moves to the other axial end of the rotating shaft. The inclination angle of the swash plate decreases with the movement of the rotating shaft toward the other end in the axial direction of the moving body. When the inclination angle of the swash plate decreases, the piston stroke decreases and the discharge capacity decreases. When the inclination angle of the swash plate increases, the piston stroke increases and the discharge capacity increases. The variable displacement swash plate compressor includes a displacement control valve, and the pressure of the control pressure chamber is controlled by the displacement control valve.

JP-A-1-190972

  By the way, in such a variable capacity swash plate compressor, when the air conditioner switch of the vehicle air conditioner is turned off and the energization to the electromagnetic solenoid of the capacity control valve is stopped, the swash plate is caused by the fluctuation of the pressure in the suction pressure region. May be maintained in a state where the inclination angle is larger than the minimum inclination angle. In this case, when the air-conditioner switch is turned on and the electromagnetic solenoid is energized again, the load on the variable displacement swash plate compressor increases due to a sudden increase in the discharge capacity. Therefore, when the air conditioner switch is turned off and energization of the electromagnetic solenoid is stopped, it is desirable that the inclination angle of the swash plate is changed to the minimum inclination angle.

  The present invention has been made to solve the above-described problems, and its object is to change the tilt angle of the swash plate to the minimum tilt angle and maintain the minimum tilt angle when the energization to the electromagnetic solenoid is stopped. It is an object of the present invention to provide a variable capacity swash plate compressor capable of achieving the above.

  A variable capacity swash plate compressor that solves the above-mentioned problems is a swash plate that is housed in a housing and rotates by obtaining a driving force from a rotating shaft, and an inclination angle with respect to the rotating shaft is changed, and a mooring to the swash plate A piston that is connected to the swash plate and is capable of changing an inclination angle of the swash plate, and is partitioned by the moving body, and a control gas is introduced to change the internal pressure, thereby changing the pressure. A control pressure chamber for moving the moving body in the axial direction of the rotary shaft; and a capacity control valve for controlling the pressure of the control pressure chamber, wherein the piston reciprocates at a stroke corresponding to an inclination angle of the swash plate. A variable displacement swash plate compressor, wherein the displacement control valve includes a driving force transmission member in which a movable iron core that is attracted to a fixed iron core is fixed by excitation of an electromagnetic solenoid, and a suction pressure region from the control pressure chamber. Of the exhaust passage A second valve body for controlling the degree of opening and a valve seat on which the first valve body is seated, and arranged in parallel with the first valve body in the discharge passage to control the opening degree of the discharge passage. A feeling that controls the valve opening degree of the first valve body by integrating the valve body with the first valve body and expanding and contracting in the moving direction of the first valve body by sensing the pressure in the suction pressure region. A pressure mechanism, a pressure sensing mechanism housing chamber that is disposed between the control pressure chamber and the first valve body and the second valve body, communicates with the control pressure chamber, and houses the pressure sensing mechanism; A communication chamber that is disposed between the suction pressure region and the first valve body and the second valve body and communicates with the suction pressure region, and the second valve body is connected to the electromagnetic solenoid. When energized, it is attracted to the fixed iron core and closed by excitation of the electromagnetic solenoid In addition, when energization to the electromagnetic solenoid is stopped and the pressure in the suction pressure region rises and reaches a threshold value, the first valve body is seated on the valve seat by reducing the pressure-sensitive mechanism, The valve is opened by being pressed by the first valve body.

  When energization of the electromagnetic solenoid is stopped, when the pressure in the suction pressure region rises and reaches a threshold value, the first valve body is closed due to the pressure-sensitive mechanism being contracted by the pressure in the suction pressure region. Thereby, the control gas from the control pressure chamber is not discharged to the suction pressure region through the discharge passage. Here, the first valve body presses the second valve body while sitting on the valve seat. Then, the second valve body is opened, and the pressure-sensitive mechanism accommodation chamber and the communication chamber communicate with each other. As a result, the control gas from the control pressure chamber is discharged to the suction pressure region via the pressure-sensitive mechanism housing chamber and the communication chamber, so that the pressure in the control pressure chamber can be made substantially equal to the pressure in the suction pressure region. . Therefore, even when energization of the electromagnetic solenoid is stopped, even if the pressure in the suction pressure region fluctuates, the inclination angle of the swash plate can be changed to the minimum inclination angle and the minimum inclination angle can be maintained.

  In the variable displacement swash plate compressor, the capacity control valve is a communication member that is formed in the valve member and includes the first valve body and communicates the pressure-sensitive mechanism housing chamber and the communication chamber. And a third valve body that is provided between the driving force transmission member and the valve member and opens and closes the communication passage, and the third valve body is energized to the electromagnetic solenoid. The valve member is closed by being pressed by the driving force transmission member, the energization to the electromagnetic solenoid is stopped, and the pressure in the suction pressure region rises and reaches the threshold value. It is preferable that the valve member is opened by being separated from the driving force transmission member by reducing the pressure-sensitive mechanism.

  According to this, when the energization to the electromagnetic solenoid is stopped, the third valve body is opened when the pressure in the suction pressure region increases and reaches the threshold value. Therefore, in addition to the discharge of the control gas from the control pressure chamber to the suction pressure region via the pressure sensing mechanism accommodating chamber and the communication chamber by opening the second valve body, the control gas from the control pressure chamber is It is discharged to the suction pressure region through the storage chamber, the communication passage, and the communication chamber. As a result, the inclination angle of the swash plate can be changed to the minimum inclination angle, and the minimum inclination angle can be easily maintained.

  In the variable displacement swash plate compressor, the displacement control valve is a stopper member with which an end surface of the second valve body on the valve opening direction side can come into contact when the second valve body moves in the valve opening direction. Is preferably further provided.

  According to this, the excessive movement to the valve opening direction in a 2nd valve body can be controlled by a stopper member. As a result, the electromagnetic force of the electromagnetic solenoid necessary for attracting the second valve body and closing the valve can be minimized.

  In the variable displacement swash plate compressor, the piston is preferably a double-headed piston. A double-headed piston type swash plate compressor employing a double-headed piston is suitable as an application object of the present invention.

In the variable displacement swash plate compressor, it is preferable to obtain the rotational driving force of the rotary shaft from an external drive source through a power transmission mechanism including a clutchless mechanism.
According to this, for example, compared to a configuration in which the rotational drive of the rotary shaft is obtained from the external drive source via the power transmission mechanism including the electromagnetic clutch mechanism only when the electromagnetic solenoid is energized, the variable capacity type diagonal The overall weight of the plate compressor and the power consumption for operating the power transmission mechanism including the electromagnetic clutch mechanism can be suppressed.

  However, when the rotational driving force of the rotary shaft is obtained from an external drive source through a power transmission mechanism including a clutchless mechanism, the rotary shaft is transmitted from the external drive source via the power transmission mechanism even when the electromagnetic solenoid is de-energized. Since the rotational driving force is constantly transmitted, the power of the external driving source is slightly consumed. Therefore, in order to suppress the power consumption of the external drive source as much as possible, in a state where the energization to the electromagnetic solenoid is stopped, it is preferable that the operation is performed with the minimum discharge capacity in which the inclination angle of the swash plate is maintained at the minimum inclination angle. .

  Therefore, when energization to the electromagnetic solenoid is stopped, the valve opening degree of the first valve body is maximized, and the control gas from the control pressure chamber is discharged to the suction pressure region through the discharge passage, thereby controlling the The capacity control valve controls the pressure in the pressure chamber to be substantially equal to the pressure in the suction pressure region and changes the tilt angle of the swash plate to the minimum tilt angle. However, when energization of the electromagnetic solenoid is stopped, when the pressure in the suction pressure region increases and reaches the threshold value, the first valve body is closed due to the pressure-sensitive mechanism being reduced by the pressure in the suction pressure region. There is a case where a malfunction occurs.

  At this time, the first valve body presses the second valve body while sitting on the valve seat. Then, the second valve body is opened, and the pressure-sensitive mechanism accommodation chamber and the communication chamber communicate with each other. As a result, the control gas from the control pressure chamber is discharged to the suction pressure region via the pressure-sensitive mechanism housing chamber and the communication chamber, so that the pressure in the control pressure chamber can be made substantially equal to the pressure in the suction pressure region. . Therefore, even when energization of the electromagnetic solenoid is stopped, even if the pressure in the suction pressure region fluctuates, the inclination angle of the swash plate can be changed to the minimum inclination angle and the minimum inclination angle can be maintained. Therefore, in a configuration in which the rotational driving force of the rotary shaft is obtained from an external drive source through a power transmission mechanism including a clutchless mechanism, even if the energization to the electromagnetic solenoid is stopped, the pressure in the suction pressure region varies. The inclination angle of the swash plate can be changed to the minimum inclination angle and maintained at the minimum inclination angle, and the operation with the minimum discharge capacity can be performed reliably. As a result, power consumption of the external drive source can be suppressed as much as possible.

  According to this invention, when energization to the electromagnetic solenoid is stopped, the inclination angle of the swash plate can be changed to the minimum inclination angle, and the minimum inclination angle can be maintained.

A side sectional view showing a variable capacity type swash plate type compressor in an embodiment. Sectional drawing of a capacity control valve when the inclination angle of a swash plate is the minimum inclination angle. Sectional drawing of a capacity | capacitance control valve when the inclination angle of a swash plate is a maximum inclination angle. The sectional side view which shows a variable capacity | capacitance type swash plate type compressor when the inclination of a swash plate is a maximum inclination. Sectional drawing of a capacity | capacitance control valve when the pressure of a suction chamber is smaller than a 1st predetermined value and is more than a 2nd predetermined value. Sectional drawing of a capacity | capacitance control valve when the pressure of a suction chamber reaches the 1st predetermined value.

Hereinafter, an embodiment embodying a variable displacement swash plate compressor will be described with reference to FIGS. The variable capacity swash plate compressor is used in a vehicle air conditioner.
As shown in FIG. 1, the housing 11 of the variable capacity swash plate compressor 10 includes a first cylinder block 12 and a second cylinder block 13 joined together, and a first cylinder block 12 on the front side (one side). The front housing 14 is joined, and the rear housing 15 is joined to the second cylinder block 13 on the rear side (the other side).

  A first valve / port forming body 16 is interposed between the front housing 14 and the first cylinder block 12. A second valve / port forming body 17 is interposed between the rear housing 15 and the second cylinder block 13.

  A suction chamber 14 a and a discharge chamber 14 b are defined between the front housing 14 and the first valve / port forming body 16. The discharge chamber 14b is disposed on the outer peripheral side of the suction chamber 14a. A suction chamber 15 a and a discharge chamber 15 b are defined between the rear housing 15 and the second valve / port forming body 17. Further, the rear housing 15 is formed with a pressure adjusting chamber 15c. The pressure adjustment chamber 15c is located at the center of the rear housing 15, and the suction chamber 15a is disposed on the outer peripheral side of the pressure adjustment chamber 15c. Further, the discharge chamber 15b is disposed on the outer peripheral side of the suction chamber 15a. The discharge chambers 14b and 15b are connected to each other via a discharge passage (not shown). The discharge passage is connected to an external refrigerant circuit (not shown). Each discharge chamber 14b, 15b is a discharge pressure area.

  The first valve / port forming body 16 is formed with a suction port 16a communicating with the suction chamber 14a and a discharge port 16b communicating with the discharge chamber 14b. The second valve / port forming body 17 is formed with a suction port 17a communicating with the suction chamber 15a and a discharge port 17b communicating with the discharge chamber 15b. Each suction port 16a, 17a is provided with a suction valve mechanism (not shown), and each discharge port 16b, 17b is provided with a discharge valve mechanism (not shown).

  A rotating shaft 21 is rotatably supported in the housing 11. In the rotary shaft 21, one end side along the direction in which the central axis L extends (the axial direction of the rotary shaft 21), and the front end portion side located on the front side (one side) of the housing 11 is connected to the first cylinder block 12. The shaft hole 12h is inserted therethrough. The front end of the rotating shaft 21 is located in the front housing 14. Further, in the rotating shaft 21, the other end side along the direction in which the central axis L extends, and the rear end portion side located on the rear side (the other side) of the housing 11 is provided through the second cylinder block 13. The shaft hole 13h is inserted. The rear end of the rotary shaft 21 is located in the pressure adjustment chamber 15c.

  The rotary shaft 21 has a front end portion rotatably supported by the first cylinder block 12 via the shaft hole 12h and a rear end portion side rotatably supported by the second cylinder block 13 via the shaft hole 13h. ing. A lip seal type shaft seal device 22 is interposed between the front housing 14 and the rotary shaft 21. A vehicle engine E as an external drive source is operatively connected to the front end of the rotating shaft 21 via a power transmission mechanism PT. In the present embodiment, the power transmission mechanism PT is a constant transmission type clutchless mechanism (for example, a combination of a belt and a pulley).

  A crank chamber 24 defined by the first cylinder block 12 and the second cylinder block 13 is formed in the housing 11. The crank chamber 24 accommodates a swash plate 23 that rotates by obtaining a driving force from the rotating shaft 21 and that can tilt in the axial direction with respect to the rotating shaft 21. The swash plate 23 is formed with an insertion hole 23a through which the rotary shaft 21 can be inserted. The swash plate 23 is attached to the rotating shaft 21 by inserting the rotating shaft 21 into the insertion hole 23 a.

  In the first cylinder block 12, a plurality of first cylinder bores 12a penetratingly formed in the axial direction of the first cylinder block 12 are arranged around the rotation shaft 21 (only one first cylinder bore 12a is shown in FIG. 1). . Each first cylinder bore 12a communicates with the suction chamber 14a via the suction port 16a and also communicates with the discharge chamber 14b via the discharge port 16b. In the second cylinder block 13, a plurality of second cylinder bores 13a penetratingly formed in the axial direction of the second cylinder block 13 are arranged around the rotation shaft 21 (only one second cylinder bore 13a is shown in FIG. 1). . Each second cylinder bore 13a communicates with the suction chamber 15a via the suction port 17a and also communicates with the discharge chamber 15b via the discharge port 17b. The 1st cylinder bore 12a and the 2nd cylinder bore 13a are arranged so that it may become a pair in front and back. In the first cylinder bore 12a and the second cylinder bore 13a as a pair, a double-headed piston 25 as a piston is accommodated so as to be able to reciprocate in the front-rear direction. That is, the variable capacity swash plate compressor 10 of this embodiment is a double-headed piston swash plate compressor.

  Each double-headed piston 25 is anchored to the outer peripheral portion of the swash plate 23 via a pair of shoes 26. Then, the rotational motion of the swash plate 23 accompanying the rotation of the rotating shaft 21 is converted into the reciprocating linear motion of the double-headed piston 25 via the shoe 26. A first compression chamber 20a is defined in each first cylinder bore 12a by a double-headed piston 25 and a first valve / port forming body 16. In each second cylinder bore 13a, a second compression chamber 20b is defined by a double-headed piston 25 and a second valve / port forming body 17.

  The first cylinder block 12 is formed with a first large-diameter hole 12b that is continuous with the shaft hole 12h and has a larger diameter than the shaft hole 12h. The first large diameter hole 12 b communicates with the crank chamber 24. The crank chamber 24 and the suction chamber 14a communicate with each other through a suction passage 12c that passes through the first cylinder block 12 and the first valve / port forming body 16.

  The second cylinder block 13 is formed with a second large-diameter hole 13b that is continuous with the shaft hole 13h and has a larger diameter than the shaft hole 13h. The second large diameter hole 13 b communicates with the crank chamber 24. The crank chamber 24 and the suction chamber 15a communicate with each other through a suction passage 13c that passes through the second cylinder block 13 and the second valve / port forming body 17.

  A suction port 13 s is formed in the peripheral wall of the second cylinder block 13. The suction port 13s is connected to an external refrigerant circuit. Then, the refrigerant gas sucked into the crank chamber 24 from the external refrigerant circuit through the suction port 13s is sucked into the suction chambers 14a and 15a through the suction passages 12c and 13c. Therefore, the suction chambers 14a and 15a and the crank chamber 24 are in the suction pressure region, and the pressures are almost equal.

  An annular flange portion 21f disposed in the first large-diameter hole 12b protrudes from the rotary shaft 21. A first thrust bearing 27 a is disposed between the flange portion 21 f and the first cylinder block 12 in the axial direction of the rotary shaft 21. A cylindrical support member 39 is press-fitted on the rear end side of the rotary shaft 21. From the outer peripheral surface of the support member 39, an annular flange portion 39f disposed in the second large-diameter hole 13b is projected. A second thrust bearing 27 b is disposed between the flange portion 39 f and the second cylinder block 13 in the axial direction of the rotary shaft 21.

  An annular fixed body 31 that can rotate integrally with the rotary shaft 21 is fixed to the rear side of the flange portion 21 f of the rotary shaft 21 and to the front side of the swash plate 23. Between the flange portion 21f and the fixed body 31, a bottomed cylindrical moving body 32 that is movable in the axial direction of the rotary shaft 21 with respect to the fixed body 31 is disposed.

  The moving body 32 is formed of an annular bottom portion 32a having an insertion hole 32e through which the rotation shaft 21 is inserted, and a cylindrical portion 32b extending along the axial direction of the rotation shaft 21 from the outer peripheral edge of the bottom portion 32a. The inner peripheral surface of the cylindrical portion 32 b is slidable with respect to the outer peripheral edge of the fixed body 31. Thereby, the moving body 32 can rotate integrally with the rotating shaft 21 via the fixed body 31. The space between the inner peripheral surface of the cylindrical portion 32 b and the outer peripheral edge of the fixed body 31 is sealed with a seal member 33, and the space between the insertion hole 32 e and the rotary shaft 21 is sealed with a seal member 34. A control pressure chamber 35 is defined between the fixed body 31 and the moving body 32.

  A first in-shaft passage 21 a extending along the axial direction of the rotation shaft 21 is formed in the rotation shaft 21. The rear end of the first in-axis passage 21a opens to the pressure adjustment chamber 15c. Further, the rotation shaft 21 is formed with a second in-axis passage 21 b extending along the radial direction of the rotation shaft 21. One end of the second in-shaft passage 21 b communicates with the tip of the first in-shaft passage 21 a, and the other end opens to the control pressure chamber 35. Therefore, the control pressure chamber 35 and the pressure adjustment chamber 15c communicate with each other via the first in-axis passage 21a and the second in-axis passage 21b.

  In the crank chamber 24, a lug arm 40 is disposed between the swash plate 23 and the flange portion 39f. The lug arm 40 is formed in a substantially L shape from one end to the other end. A weight portion 40 a is formed at one end of the lug arm 40. The weight part 40 a passes through the groove part 23 b of the swash plate 23 and is located on the front side of the swash plate 23.

  One end side of the lug arm 40 is connected to the upper end side (the upper side in FIG. 1) of the swash plate 23 by a first pin 41 that traverses the inside of the groove 23b. Thus, one end side of the lug arm 40 is supported so as to be swingable around the first swing center M1 with respect to the swash plate 23 with the axis of the first pin 41 as the first swing center M1. The other end side of the lug arm 40 is connected to the support member 39 by the second pin 42. Thereby, the other end side of the lug arm 40 is supported so as to be swingable around the second swing center M2 with respect to the support member 39 with the axis of the second pin 42 as the second swing center M2.

  A connecting portion 32 c that protrudes toward the swash plate 23 is provided at the tip of the cylindrical portion 32 b of the moving body 32. A moving body side insertion hole 32h into which the third pin 43 can be inserted is formed in the connecting portion 32c. Further, a swash plate side insertion hole 23h through which the third pin 43 can be inserted is formed on the lower end side (lower side in FIG. 1) of the swash plate 23. The connecting portion 32 c is connected to the lower end side of the swash plate 23 by the third pin 43.

  The second valve / port forming body 17 is formed with a throttling portion 36a communicating with the discharge chamber 15b. In addition, a communication portion 36b that communicates the pressure adjustment chamber 15c and the throttle portion 36a is recessed in the end face of the second cylinder block 13 on the second valve / port forming body 17 side. The discharge chamber 15b and the control pressure chamber 35 are communicated with each other through a throttle portion 36a, a communication portion 36b, a pressure adjustment chamber 15c, a first in-axis passage 21a, and a second in-axis passage 21b. Therefore, the throttle portion 36a, the communication portion 36b, the pressure adjusting chamber 15c, the first in-shaft passage 21a, and the second in-shaft passage 21b form a supply passage from the discharge chamber 15b to the control pressure chamber 35. The opening of the supply passage is narrowed by the narrowing portion 36a.

  The pressure in the control pressure chamber 35 is adjusted by introducing the refrigerant gas from the discharge chamber 15b to the control pressure chamber 35 and discharging the refrigerant gas from the control pressure chamber 35 to the suction chamber 15a. Therefore, the refrigerant gas introduced into the control pressure chamber 35 is a control gas that adjusts the pressure of the control pressure chamber 35. The moving body 32 moves in the axial direction of the rotating shaft 21 with respect to the fixed body 31 in accordance with the pressure difference between the control pressure chamber 35 and the crank chamber 24. The rear housing 15 is assembled with an electromagnetic capacity control valve 50 for controlling the pressure in the control pressure chamber 35. The capacity control valve 50 is electrically connected to the control computer 50c. An air conditioner switch 50s is signal-connected to the control computer 50c.

  As shown in FIG. 2, the valve housing 50 h of the capacity control valve 50 includes a cylindrical first housing 51 in which the electromagnetic solenoid 53 is accommodated. The electromagnetic solenoid 53 has a fixed iron core 54 and a movable iron core 55 that is attracted to the fixed iron core 54 based on excitation by current supply to the coil 53c. The electromagnetic force of the electromagnetic solenoid 53 attracts the movable iron core 55 toward the fixed iron core 54. The electromagnetic solenoid 53 receives energization control (duty ratio control) of the control computer 50c. Between the fixed iron core 54 and the movable iron core 55, a spring 56 that urges the movable iron core 55 in a direction in which the movable iron core 55 is separated from the fixed iron core 54 is disposed.

  A columnar driving force transmission member 57 is attached to the movable iron core 55. The driving force transmission member 57 can move integrally with the movable iron core 55. The fixed iron core 54 includes a small-diameter portion 54a located inside the coil 53c, and a large-diameter portion 54b that protrudes from the opening of the first housing 51 opposite to the movable iron core 55 and has a larger diameter than the small-diameter portion 54a. It is configured. A fitting recess 54c is formed on the end surface of the large diameter portion 54b opposite to the small diameter portion 54a. A cylindrical second housing 52 is fitted and fixed in the fitting recess 54c.

  A pressure sensitive mechanism accommodating chamber 59 is formed in the second housing 52. A pressure sensitive mechanism 60 is accommodated in the pressure sensitive mechanism accommodating chamber 59. The pressure sensing mechanism 60 is coupled to a bellows 61, a pressure receiving body 62 that is coupled to one end of the bellows 61 and is press-fitted into an opening of the second housing 52 opposite to the first housing 51, and the other end of the bellows 61. And a spring 64 that urges the pressure receiving body 62 and the connecting body 63 away from each other in the bellows 61.

  In the bellows 61, a stopper 62a is integrally formed with the pressure receiving body 62. Further, the connecting body 63 is formed with a stopper 63 a that protrudes toward the stopper 62 a of the pressure receiving body 62. The stopper 62a of the pressure receiving body 62 and the stopper 63a of the connecting body 63 define the shortest length of the bellows 61.

  A cylindrical valve seat member 65 made of a magnetic material is disposed on the bottom surface side of the fitting recess 54 c in the second housing 52. A valve hole 65 h is formed in the central portion of the valve seat member 65. A recess 541c is formed at the center of the bottom surface of the fitting recess 54c. A communication chamber 58 is defined between the recess 541c and the valve seat member 65. The communication chamber 58 communicates with the pressure-sensitive mechanism accommodation chamber 59 through the valve hole 65h, and is located between the electromagnetic solenoid 53 and the pressure-sensitive mechanism accommodation chamber 59.

  The driving force transmission member 57 passes through the fixed iron core 54 and protrudes into the communication chamber 58. Further, a valve member 68 is accommodated on the valve seat member 65 side of the driving force transmission member 57 in the communication chamber 58. The valve member 68 has a first valve body 68v. The first valve body 68v contacts and separates from the periphery of the valve hole 65h in the valve seat member 65. Therefore, the periphery of the valve hole 65h in the valve seat member 65 is a valve seat 65e on which the first valve body 68v is seated. And the 1st valve body 68v can open and close the valve hole 65h by contacting / separating to the valve seat 65e.

  A columnar protrusion 68 a is provided on the end surface of the valve member 68 on the pressure sensitive mechanism accommodation chamber 59 side. The protruding portion 68 a is connected to the connecting body 63. That is, the valve member 68 (first valve body 68v) is integrated with the pressure-sensitive mechanism 60. The valve member 68 is guided in the moving direction of the driving force transmission member 57 by the inner peripheral surface of the valve seat member 65. Further, a groove 68 b extending in the axial direction of the valve member 68 is formed in a part of the outer peripheral surface of the valve member 68.

  The pressure-sensitive mechanism accommodation chamber 59 communicates with the pressure adjustment chamber 15 c through the passage 71. Therefore, the pressure-sensitive mechanism accommodating chamber 59 is disposed between the control pressure chamber 35 and the first valve body 68v and the valve seat member 65. Further, the communication chamber 58 communicates with the suction chamber 15 a through the passage 72. Therefore, the communication chamber 58 is disposed between the suction chamber 15a, the first valve body 68v, and the valve seat member 65. The second in-shaft passage 21b, the first in-shaft passage 21a, the pressure adjusting chamber 15c, the passage 71, the pressure sensing mechanism accommodating chamber 59, the valve hole 65h, the communication chamber 58, and the passage 72 are connected from the control pressure chamber 35 to the suction chamber. A discharge passage reaching 15a is formed.

  The cross-sectional area of the valve hole 65h opened and closed by the first valve body 68v is the same as the effective pressure receiving area of the bellows 61. Therefore, the pressure-sensitive mechanism 60 is not affected by the pressure in the pressure-sensitive mechanism housing chamber 59 when the first valve body 68v is closed, and the bellows 61 is in the communication chamber 58 within the valve member 68. By sensing the pressure applied to the driving force transmitting member 57, the driving force transmitting member 57 expands and contracts in the moving direction. The expansion and contraction of the bellows 61 is used for positioning the first valve body 68v and contributes to the control of the valve opening degree of the first valve body 68v. The valve opening degree of the first valve body 68v is determined by the balance of the electromagnetic force generated by the electromagnetic solenoid 53, the biasing force of the spring 56, and the biasing force of the pressure-sensitive mechanism 60.

  The first valve body 68v controls the opening degree (passage cross-sectional area) of the discharge passage. The first valve body 68v is in a valve closing state for closing the discharge passage by being seated on the valve seat 65e, and is in a valve opening state for opening the discharge passage by being separated from the valve seat 65e.

  When the electromagnetic solenoid 53 is energized, the valve seat member 65 is attracted to the bottom surface of the fitting recess 54 c by excitation of the electromagnetic solenoid 53 and closes the space between the pressure-sensitive mechanism accommodation chamber 59 and the communication chamber 58. Further, when the energization of the electromagnetic solenoid 53 is stopped, the adsorption action to the bottom surface of the fitting recess 54c with respect to the valve seat member 65 due to the excitation of the electromagnetic solenoid 53 is lost. The valve seat member 65 is separated from the bottom surface of the fitting recess 54c by being pressed by the first valve body 68v while the first valve body 68v is seated on the valve seat 65e. Communication with the communication chamber 58 is allowed.

  The valve seat member 65 is adsorbed on the bottom surface of the fitting recess 54c, thereby closing the space between the pressure-sensitive mechanism housing chamber 59 and the communication chamber 58 and separating from the bottom surface of the fitting recess 54c. As a result, the valve-opening state opens between the pressure-sensitive mechanism housing chamber 59 and the communication chamber 58.

  An annular stopper member 75 in which the valve seat member 65 moves in the valve opening direction and the end surface on the valve opening direction side of the valve seat member 65 can come into contact is accommodated in the pressure sensing mechanism accommodation chamber 59. The stopper member 75 is disposed between the valve seat member 65 and the pressure sensitive mechanism 60 in the pressure sensitive mechanism accommodating chamber 59. The stopper member 75 has a through hole that communicates the space in the pressure-sensitive mechanism housing chamber 59 closer to the pressure-sensitive mechanism 60 than the stopper member 75 and the space outside the valve seat member 65 in the pressure-sensitive mechanism housing chamber 59. 75h is formed. The inside of the stopper member 75 from the through hole 75h is a seat portion with which the end face on the valve opening direction side of the valve seat member 65 abuts. The outer side of the stopper member 75 from the through hole 75 h abuts on a stepped portion 52 e formed on the inner peripheral surface of the second housing 52.

  An urging spring 66 is disposed between the stopper member 75 and the pressure receiving body 62 in the pressure sensitive mechanism accommodating chamber 59. The stopper member 75 is positioned by being pressed against the stepped portion 52e by the biasing spring 66.

  The valve member 68 is formed with a communication passage 73 that connects the pressure-sensitive mechanism housing chamber 59 and the communication chamber 58. The communication passage 73 extends along the axial direction of the valve member 68 and has one end opened to the communication chamber 58 and the other end of the first passage 73a and is orthogonal to the first passage 73a. The second passage 73b extends in the direction and opens into the pressure-sensitive mechanism housing chamber 59.

  The end of the driving force transmission member 57 on the valve member 68 side is a third valve body 74 that opens and closes the communication passage 73 by making contact with and separating from the end of the valve member 68 on the driving force transmission member 57 side. . Therefore, the third valve body 74 is provided between the driving force transmission member 57 and the valve member 68. In the present embodiment, the third valve body 74 is integrated with the driving force transmission member 57. That is, the driving force transmission member 57 has the third valve body 74.

  The third valve body 74 closes the communication path 73 when the air conditioner switch 50s is turned on and energization of the electromagnetic solenoid 53 is performed, and the air conditioner switch 50s is turned off and the energization of the electromagnetic solenoid 53 is stopped. When this is done, the communication passage 73 is opened.

  As shown in FIG. 3, in the variable displacement swash plate compressor 10 having the above-described configuration, when the air conditioner switch 50 s is turned on to energize the electromagnetic solenoid 53, the electromagnetic force of the electromagnetic solenoid 53 is applied to the spring 56. The movable iron core 55 is attracted toward the fixed iron core 54 against the force. Then, the third valve body 74 is pressed against the valve member 68 by the driving force transmission member 57, thereby closing the communication passage 73, and the driving force transmission member 57 pressing the valve member 68. The valve opening degree of the valve body 68v decreases. Then, suction is performed from the control pressure chamber 35 through the second in-shaft passage 21b, the first in-shaft passage 21a, the pressure adjusting chamber 15c, the passage 71, the pressure sensing mechanism accommodating chamber 59, the valve hole 65h, the communication chamber 58, and the passage 72. The flow rate of the refrigerant gas discharged to the chamber 15a is reduced. Then, the refrigerant gas is introduced from the discharge chamber 15b into the control pressure chamber 35 through the throttle portion 36a, the communication portion 36b, the pressure adjustment chamber 15c, the first in-shaft passage 21a, and the second in-shaft passage 21b. The pressure in the pressure chamber 35 approaches the pressure in the discharge chamber 15b.

  As shown in FIG. 4, when the pressure in the control pressure chamber 35 approaches the pressure in the discharge chamber 15b and the pressure difference between the control pressure chamber 35 and the crank chamber 24 increases, the bottom 32a of the moving body 32 is fixed to the fixed body. The moving body 32 moves so as to be separated from 31. Then, the swash plate 23 swings around the first swing center M1. As the swash plate 23 swings around the first swing center M1, both ends of the lug arm 40 swing around the first swing center M1 and the second swing center M2, respectively. It is separated from the flange portion 39f of 39. Thereby, the inclination angle of the swash plate 23 is increased, the stroke of the double-headed piston 25 is increased, and the discharge capacity is increased. The moving body 32 comes into contact with the flange portion 21f when the inclination angle of the swash plate 23 reaches the maximum inclination angle. By the contact between the moving body 32 and the flange portion 21f, the inclination angle of the swash plate 23 is maintained at the maximum inclination angle.

  As shown in FIG. 2, when the valve opening degree of the first valve body 68v increases, the second pressure passage 21b, the first shaft passage 21a, the pressure adjustment chamber 15c, the passage 71, and the pressure sensing mechanism are increased from the control pressure chamber 35. The flow rate of the refrigerant gas discharged to the suction chamber 15a through the storage chamber 59, the valve hole 65h, the communication chamber 58, and the passage 72 increases, and the pressure in the control pressure chamber 35 approaches the pressure in the suction chamber 15a.

  As shown in FIG. 1, when the pressure in the control pressure chamber 35 approaches the pressure in the suction chamber 15a and the pressure difference between the control pressure chamber 35 and the crank chamber 24 is reduced, the bottom 32a of the moving body 32 is fixed to the fixed body. The moving body 32 moves so as to approach 31. Then, the swash plate 23 swings around the first swing center M1 in the direction opposite to the swing direction when the tilt angle of the swash plate 23 is increased. As the swash plate 23 swings around the first swing center M1 in the direction opposite to the swing direction when the tilt angle of the swash plate 23 increases, both ends of the lug arm 40 are moved to the first swing center M1 and the first swing center M1, respectively. 2) The lug arm 40 swings in the direction opposite to the swinging direction when the inclination angle of the swash plate 23 is increased around the swing center M2, and the lug arm 40 approaches the flange portion 39f of the support member 39. Thereby, the inclination angle of the swash plate 23 is reduced, the stroke of the double-headed piston 25 is reduced, and the discharge capacity is reduced. The lug arm 40 comes into contact with the flange portion 39f of the support member 39 when the inclination angle of the swash plate 23 reaches the minimum inclination angle. By the contact between the lug arm 40 and the flange portion 39f, the inclination angle of the swash plate 23 is maintained at the minimum inclination angle.

Next, the operation of this embodiment will be described.
When the air conditioner switch 50 s is turned off and the energization of the electromagnetic solenoid 53 is stopped, the movable iron core 55 is separated from the fixed iron core 54 by the urging force of the spring 56, so that the driving force transmission member 57 moves in the moving direction of the movable iron core 55. Move to. At this time, when the pressure in the suction chamber 15a is less than a second predetermined value which is smaller than the first predetermined value which is a threshold value, the valve member 68 is driven by the biasing force of the spring 64 of the bellows 61 as shown in FIG. It moves in the moving direction of the movable iron core 55 together with the force transmission member 57. And with the movement of the valve member 68, the 1st valve body 68v opens. Since the valve member 68 maintains the state in contact with the driving force transmission member 57, the third valve body 74 maintains the valve closed state.

  Therefore, the refrigerant gas from the control pressure chamber 35 flows into the second in-shaft passage 21b, the first in-shaft passage 21a, the pressure adjustment chamber 15c, the passage 71, the pressure-sensitive mechanism housing chamber 59, the valve hole 65h, the communication chamber 58, and It is discharged to the suction chamber 15a through the passage 72. As a result, when energization to the electromagnetic solenoid 53 is stopped, the pressure in the control pressure chamber 35 becomes substantially equal to the pressure in the suction chamber 15a, and the tilt angle of the swash plate 23 is changed to the minimum tilt angle.

  As shown in FIG. 5, when the pressure in the suction chamber 15a is smaller than the first predetermined value and equal to or higher than the second predetermined value, the valve member 68 is separated from the driving force transmission member 57 by the reduction of the pressure sensing mechanism 60. Thus, the third valve body 74 is opened. As the pressure in the suction chamber 15a approaches the first predetermined value, the opening degree of the first valve body 68v decreases and the opening degree of the third valve body 74 increases. For this reason, the refrigerant gas from the control pressure chamber 35 flows into the second shaft passage 21b, the first shaft passage 21a, the pressure adjustment chamber 15c, the passage 71, the pressure sensing mechanism housing chamber 59, the communication passage 73, the communication chamber 58, and the like. It is discharged to the suction chamber 15a through the passage 72. As a result, when energization to the electromagnetic solenoid 53 is stopped, the pressure in the control pressure chamber 35 becomes substantially equal to the pressure in the suction chamber 15a, and the inclination angle of the swash plate 23 is changed to the minimum inclination angle.

  As shown in FIG. 6, when the pressure in the suction chamber 15a reaches the first predetermined value, the valve member 68 is urged toward the bellows 61 by the pressure in the suction chamber 15a, and the pressure-sensitive mechanism 60 is reduced. The first valve body 68v is closed, the valve member 68 is separated from the driving force transmission member 57, and the third valve body 74 is opened. Here, the first valve body 68v presses the valve seat member 65 while sitting on the valve seat 65e. Since the energization of the electromagnetic solenoid 53 is stopped, the valve seat member 65 is not attracted to the bottom surface of the fitting recess 54c. Therefore, when the first valve body 68v presses the valve seat member 65, the valve seat member 65 is separated from the bottom surface of the fitting recess 54c. Then, the valve seat member 65 is opened, and the pressure-sensitive mechanism accommodation chamber 59 and the communication chamber 58 communicate with each other. Specifically, the space closer to the pressure-sensitive mechanism 60 than the stopper member 75 in the pressure-sensitive mechanism accommodation chamber 59 and the communication chamber 58 are formed through the through hole 75 h and the valve seat member 65 in the pressure-sensitive mechanism accommodation chamber 59. And the space between the valve seat member 65 and the fitting recess 54c. When the valve seat member 65 moves in the valve opening direction, the end surface of the valve seat member 65 on the valve opening direction side contacts the stopper member 75.

  Then, in addition to the discharge of the refrigerant gas from the control pressure chamber 35 to the suction chamber 15a due to the opening of the third valve body 74, the pressure sensing mechanism accommodating chamber 59, the communication chamber 58 and the passage 72 due to the valve seat member 65 being opened. The refrigerant gas is discharged from the control pressure chamber 35 to the suction chamber 15a via the. At this time, the second in-shaft passage 21b, the first in-shaft passage 21a, the pressure adjusting chamber 15c, the passage 71, the pressure-sensitive mechanism accommodating chamber 59, the communication chamber 58, and the passage 72 reach the suction chamber 15a from the control pressure chamber 35. A discharge passage is formed. As a result, when energization to the electromagnetic solenoid 53 is stopped, the pressure in the control pressure chamber 35 becomes substantially equal to the pressure in the suction chamber 15a, and the inclination angle of the swash plate 23 is changed to the minimum inclination angle. That is, the valve seat member 65 is disposed in parallel with the first valve body 68v in the discharge passage, and functions as a second valve body that controls the opening degree of the discharge passage.

  When the air conditioner switch 50s is turned on and the electromagnetic solenoid 53 is energized again, the variable displacement swash plate compressor 10 is operated with the minimum discharge capacity. Therefore, it is avoided that the load on the variable displacement swash plate compressor 10 is increased due to a sudden increase in the discharge capacity.

  When the electromagnetic solenoid 53 is energized, the valve seat member 65 is attracted to the bottom surface of the fitting recess 54 c by the electromagnetic force of the electromagnetic solenoid 53. As a result, the valve seat member 65 is closed, and the space between the pressure-sensitive mechanism accommodation chamber 59 and the communication chamber 58 is closed. Further, the third valve body 74 abuts on the end of the valve member 68 on the driving force transmission member 57 side, closes the communication passage 73, and the driving force transmission member 57 presses the valve member 68, thereby The valve opening degree of the single valve body 68v decreases. Thereby, the inclination angle of the swash plate 23 increases.

  When the rotational drive force of the rotary shaft 21 is obtained from the engine E via the power transmission mechanism PT including the clutchless mechanism, the rotary shaft is rotated from the engine E via the power transmission mechanism PT even when the electromagnetic solenoid 53 is de-energized. Since the rotational driving force 21 is constantly transmitted, the power of the engine E is consumed slightly. Therefore, in order to suppress the power consumption of the engine E as much as possible, when the energization to the electromagnetic solenoid 53 is stopped, there is a state in which the swash plate 23 is operated with the minimum discharge capacity in which the inclination angle is maintained at the minimum inclination angle. preferable.

  Therefore, when energization of the electromagnetic solenoid 53 is stopped, the valve opening degree of the first valve body 68v is maximized and the refrigerant gas from the control pressure chamber 35 is discharged to the suction chamber 15a through the discharge passage. Thus, the capacity control valve 50 controls the pressure of the control pressure chamber 35 to be substantially equal to the pressure of the suction chamber 15a and changes the tilt angle of the swash plate 23 to the minimum tilt angle. However, when energization of the electromagnetic solenoid 53 is stopped, if the pressure in the suction chamber 15a increases and reaches the first predetermined value, the pressure in the communication chamber 58 also increases. There may be a problem that the discharge passage is closed by the pressure of the communication chamber 58.

  However, in the present embodiment, since the first valve body 68v presses the valve seat member 65, the valve seat member 65 is separated from the bottom surface of the fitting recess 54c, and the valve seat member 65 is in the valve open state. The pressure-sensitive mechanism accommodation chamber 59 and the communication chamber 58 communicate with each other, and the refrigerant gas from the control pressure chamber 35 is discharged to the suction chamber 15 a through the pressure-sensitive mechanism accommodation chamber 59, the communication chamber 58 and the passage 72. For this reason, when the energization of the electromagnetic solenoid 53 is stopped, the pressure of the control pressure chamber 35 becomes substantially equal to the pressure of the suction chamber 15a, so that the inclination angle of the swash plate 23 is changed to the minimum inclination angle. Therefore, in the configuration in which the rotational driving force of the rotating shaft 21 is obtained from the engine E via the power transmission mechanism PT that is a clutchless mechanism, the pressure in the suction chamber 15a fluctuates while the energization to the electromagnetic solenoid 53 is stopped. However, the tilt angle of the swash plate 23 is changed to the minimum tilt angle, the minimum tilt angle is maintained, and the operation with the minimum discharge capacity is performed reliably. As a result, power consumption of the engine E is suppressed as much as possible.

In the above embodiment, the following effects can be obtained.
(1) When the electromagnetic solenoid 53 is energized, the valve seat member 65 is attracted to the fixed iron core 54 by the excitation of the electromagnetic solenoid 53 and closes. Further, when the energization to the electromagnetic solenoid 53 is stopped and the pressure in the suction chamber 15a rises and reaches the first predetermined value, the valve seat member 65 is contracted by the pressure sensing mechanism 60 to reduce the first valve body 68v. Is seated on the valve seat 65e and is opened by being pressed by the first valve body 68v. According to this, when energization to the electromagnetic solenoid 53 is stopped, the valve seat member 65 is opened, and the pressure-sensitive mechanism housing chamber 59 and the communication chamber 58 are communicated. Thereby, the refrigerant gas from the control pressure chamber 35 is discharged to the suction chamber 15a through the pressure-sensitive mechanism housing chamber 59, the communication chamber 58, and the passage 72. As a result, the pressure in the control pressure chamber 35 can be made substantially equal to the pressure in the suction chamber 15a. Therefore, even when the electromagnetic solenoid 53 is de-energized, even if the pressure in the suction chamber 15a varies, the swash plate The inclination angle of 23 can be changed to the minimum inclination angle, and the minimum inclination angle can be maintained.

  (2) The third valve body 74 is closed by being pressed against the valve member 68 by the driving force transmission member 57 when the electromagnetic solenoid 53 is energized, and the energization to the electromagnetic solenoid 53 is stopped. When the pressure in the suction chamber 15a increases to reach the first predetermined value, the valve member 68 is separated from the driving force transmission member 57 by the reduction of the pressure-sensitive mechanism 60, thereby opening the valve. According to this, in addition to the discharge of the refrigerant gas from the control pressure chamber 35 to the suction chamber 15a via the pressure sensing mechanism accommodating chamber 59, the communication chamber 58 and the passage 72 by opening the valve seat member 65, the control pressure chamber The refrigerant gas from 35 is discharged to the suction chamber 15a through the pressure-sensitive mechanism housing chamber 59, the communication passage 73, the communication chamber 58, and the passage 72. As a result, the inclination angle of the swash plate 23 can be changed to the minimum inclination angle, and the minimum inclination angle can be easily maintained.

  (3) The capacity control valve 50 includes a stopper member 75 with which the end face of the valve seat member 65 on the valve opening direction side can come into contact when the valve seat member 65 moves in the valve opening direction. According to this, excessive movement of the valve seat member 65 in the valve opening direction can be restricted by the stopper member 75. As a result, the electromagnetic force of the electromagnetic solenoid 53 required when the valve seat member 65 is attracted and is to be closed can be minimized.

  (4) In a double-headed piston type swash plate compressor that employs the double-headed piston 25, the crank chamber 24 is controlled to change the inclination angle of the swash plate 23 as in a variable displacement swash plate type compressor having a single-headed piston. It cannot function as a room. Therefore, in the present embodiment, the inclination angle of the swash plate 23 is changed by changing the pressure of the control pressure chamber 35 partitioned by the moving body 32. Since the control pressure chamber 35 is a smaller space than the crank chamber 24, the amount of refrigerant gas introduced into the control pressure chamber 35 is small, and the responsiveness of changing the tilt angle of the swash plate 23 is good.

  (5) The variable capacity swash plate compressor 10 of the present embodiment obtains the rotational driving force of the rotary shaft 21 from the engine E through the power transmission mechanism PT formed of a clutchless mechanism. According to this, for example, the variable capacity type is compared with the configuration in which the rotational drive of the rotary shaft 21 is obtained from the engine E through the power transmission mechanism including the electromagnetic clutch mechanism only when the electromagnetic solenoid 53 is energized. The overall weight of the swash plate compressor 10 and the power consumption for operating the power transmission mechanism including the electromagnetic clutch mechanism can be suppressed.

  (6) According to the present embodiment, in the configuration in which the rotational driving force of the rotary shaft 21 is obtained from the engine E via the power transmission mechanism PT that is a clutchless mechanism, the suction is performed while the energization of the electromagnetic solenoid 53 is stopped. Even when the pressure in the chamber 15a increases to reach the first predetermined value, the tilt angle of the swash plate 23 can be changed to the minimum tilt angle, and the minimum tilt angle can be maintained. As a result, the operation with the minimum discharge capacity can be reliably performed, and the power consumption of the engine E can be suppressed as much as possible.

  (7) According to the present embodiment, when the energization to the electromagnetic solenoid 53 is stopped, the inclination angle of the swash plate 23 can be changed to the minimum inclination angle. The capacity type swash plate compressor 10 is operated with a minimum discharge capacity. Therefore, it is possible to avoid an increase in the load on the variable displacement swash plate compressor 10 due to a sudden increase in the discharge capacity.

In addition, you may change the said embodiment as follows.
In the embodiment, the driving force transmission member 57 and the valve member 68 may be integrated, or the third valve body 74 may be omitted.

In the embodiment, the stopper member 75 may be deleted.
In the embodiment, the third valve body 74 may be a separate member from the driving force transmission member 57.

  In the embodiment, an interposition member may be interposed between the valve seat member 65 and the bottom surface of the fitting recess 54c. In this case, as long as the valve seat member 65 can be attracted to the fixed iron core 54 by the excitation of the electromagnetic solenoid 53, the interposed member may not be formed of a magnetic material.

In the embodiment, the communication chamber 58 may be communicated with the suction chamber 14a through the passage 72. In short, it is only necessary to form a discharge passage from the control pressure chamber 35 to the suction pressure region.
In the embodiment, the discharge chamber 14b and the control pressure chamber 35 may communicate with each other via the throttle portion 36a, the communication portion 36b, the pressure adjustment chamber 15c, the first in-axis passage 21a, and the second in-axis passage 21b. Good.

In the embodiment, the cross-sectional area of the valve hole 65h and the effective pressure receiving area of the bellows 61 do not have to be completely the same, and may be substantially the same.
In the embodiment, a driving force may be obtained from an external driving source via a clutch.

  In the embodiment, the variable capacity swash plate compressor 10 is a double-headed piston swash plate compressor that employs a double-headed piston 25, but may be a single-headed piston swash plate compressor that employs a single-headed piston. .

  DESCRIPTION OF SYMBOLS 10 ... Variable capacity | capacitance type swash plate type compressor, 11 ... Housing, 14a, 15a ... The suction chamber which is a suction pressure area | region, 14b, 15b ... The discharge chamber which is a discharge pressure area | region, 15c ... The pressure regulation chamber which forms a discharge passage, 21 Rotating shaft, 21a: First in-shaft passage forming a discharge passage, 21b: Second in-shaft passage forming a discharge passage, 23 ... Swash plate, 25 ... Double-headed piston as a piston, 32 ... Moving body, 35 ... Control pressure chamber, 50 ... Capacity control valve, 53 ... Electromagnetic solenoid, 54 ... Fixed iron core, 55 ... Movable iron core, 57 ... Driving force transmission member, 58 ... Communication chamber, 59 ... Pressure-sensitive mechanism accommodating chamber, 60 ... Pressure-sensitive mechanism 65 ... Valve seat member functioning as the second valve body, 65e ... Valve seat, 65h ... Valve hole forming the discharge passage, 68 ... Valve member, 68v ... First valve body, 71, 72 ... Forming the discharge passage Passage, 73 ... Communication passage, 74 ... Third valve body 75 ... stopper member, E ... engine as an external drive source, PT ... power transmission mechanism.

Claims (5)

A swash plate that is housed in a housing and rotates by obtaining a driving force from a rotating shaft, and an inclination angle with respect to the rotating shaft is changed;
A piston moored to the swash plate;
A movable body connected to the swash plate and capable of changing an inclination angle of the swash plate;
A control pressure chamber that is partitioned by the moving body and moves the moving body in the axial direction of the rotating shaft by introducing a control gas and changing an internal pressure;
A capacity control valve for controlling the pressure of the control pressure chamber,
A variable displacement swash plate compressor in which the piston reciprocates at a stroke corresponding to the inclination angle of the swash plate,
The capacity control valve is
A driving force transmission member having a movable iron core fixed to the fixed iron core by the excitation of an electromagnetic solenoid;
A first valve body for controlling the opening degree of the discharge passage from the control pressure chamber to the suction pressure region;
A second valve body that has a valve seat on which the first valve body is seated, and is disposed in parallel with the first valve body in the discharge passage, and controls the opening degree of the discharge passage;
A pressure-sensitive mechanism that is integrated with the first valve body, expands and contracts in the moving direction of the first valve body by sensing the pressure in the suction pressure region, and controls the valve opening of the first valve body;
A pressure-sensitive mechanism housing chamber that is disposed between the control pressure chamber and the first valve body and the second valve body, communicates with the control pressure chamber, and houses the pressure-sensitive mechanism;
A communication chamber that is disposed between the suction pressure region and the first valve body and the second valve body, and communicates with the suction pressure region;
When the electromagnetic solenoid is energized, the second valve body is attracted to the stationary iron core by the excitation of the electromagnetic solenoid and closes the valve, and the energization to the electromagnetic solenoid stops and the suction pressure When the pressure in the region increases and reaches a threshold value, the first valve body is seated on the valve seat by the reduction of the pressure-sensitive mechanism, and the valve is opened by being pressed by the first valve body. A variable capacity swash plate compressor. The capacity control valve is
A valve member having the first valve body;
A communication passage formed in the valve member and communicating the pressure-sensitive mechanism housing chamber and the communication chamber;
A third valve body provided between the driving force transmitting member and the valve member and opening and closing the communication passage;
The third valve body is closed by being pressed against the valve member by the driving force transmission member when the electromagnetic solenoid is energized, the energization to the electromagnetic solenoid is stopped, and the suction is performed. 2. The valve according to claim 1, wherein when the pressure in the pressure region rises and reaches the threshold value, the valve member is separated from the driving force transmission member due to the reduction of the pressure-sensitive mechanism. The variable capacity swash plate compressor described.   The capacity control valve further includes a stopper member with which an end surface of the second valve body on the valve opening direction side can come into contact when the second valve body moves in the valve opening direction. The variable capacity swash plate compressor according to claim 1 or 2.   The variable displacement swash plate compressor according to any one of claims 1 to 3, wherein the piston is a double-headed piston.   The variable capacity swash plate compression according to any one of claims 1 to 4, wherein a rotational driving force of the rotary shaft is obtained from an external drive source through a power transmission mechanism comprising a clutchless mechanism. Machine.