JP6192365B2 - Variable capacity compressor - Google Patents

Description

  The present invention relates to a variable capacity compressor used in a vehicle air conditioner system and the like, and particularly includes pressure-sensitive means for sensing a control pressure and autonomously adjusting a valve opening so that the control pressure becomes a set pressure. The present invention relates to a variable capacity compressor that adjusts the pressure of a pressure adjusting chamber by a control valve to vary the discharge capacity of a refrigerant.

  An example of this type of variable capacity compressor is described in Patent Document 1. In this variable capacity compressor, a control valve is interposed in a pressure supply passage that connects the discharge chamber and the crank chamber, and the suction pressure is set by the control valve as a control current value (current value that flows through the electromagnetic coil of the control valve). The refrigerant discharge capacity is varied by adjusting the crank chamber pressure by controlling the opening of the pressure supply passage so that the set suction pressure is obtained. The control valve includes pressure sensing means that senses suction pressure and autonomously adjusts the valve opening so that the suction pressure becomes the set suction pressure, and the pressure sensing means includes the sensed suction pressure. When the pressure is higher than the set suction pressure, the valve opening is decreased, and when the detected suction pressure is lower than the set suction pressure, the valve opening is adjusted autonomously so as to increase the valve opening. Therefore, in a variable capacity compressor using such a control valve, the valve opening of the control valve is autonomously controlled by the pressure sensing means so that the suction pressure is maintained at the set suction pressure determined by the control current value. The discharge capacity can be varied.

JP-A-11-170858

  Incidentally, Patent Document 1 discloses a method for estimating the driving torque of a compressor. In this estimation method, the control valve assumes that the control current value and the set suction pressure value have a substantially unambiguous relationship as shown in FIG. The control current value is used as a substitute for the suction pressure value for estimation.

  However, the control valve having the pressure sensing means described above is in a fully closed state from the application of the control current value to the electromagnetic coil until the suction pressure reaches the set pressure value due to the characteristics of the valve. Thus, the compressor is in the maximum discharge capacity state. Thereafter, when the suction pressure decreases and reaches the set pressure value, the control valve opens and the compressor enters the discharge capacity control state. In this discharge capacity control state, the control current value and the set suction pressure value have a substantially unambiguous relationship, and the drive torque of the compressor can be accurately estimated using the control current value as a substitute for the suction pressure. However, when the control valve is in the closed state and the compressor is in the maximum discharge capacity state, since the suction pressure and the control current value are not uniquely related, if the control current value is used as a substitute for the suction pressure, The compressor cannot accurately calculate the driving torque in the maximum discharge capacity operation state. For example, in a vehicle air conditioner system or the like, the engine control of the vehicle may be adversely affected.

  Therefore, in a variable capacity compressor using a control valve provided with pressure sensitive means, it is necessary to know whether the compressor is in a maximum discharge capacity state or a discharge capacity control state in order to accurately calculate the drive torque. In other words, it is necessary to know whether the control valve of the compressor is closed (maximum discharge capacity state) or opened (discharge capacity control state).

  The present invention has been made paying attention to the above problems, and an object of the present invention is to provide a variable capacity compressor capable of easily detecting the open / closed state of a control valve provided with pressure-sensitive means.

For this reason, the present invention provides a control valve having pressure sensing means that senses the control pressure and autonomously adjusts the valve opening so that the control pressure becomes a set pressure set by an external signal. Variable displacement compression that is installed in a pressure supply passage that communicates with the pressure adjustment chamber, adjusts the opening of the pressure supply passage by the control valve, and adjusts the pressure in the pressure adjustment chamber to vary the discharge capacity of the refrigerant. In the machine, the control valve includes a valve hole that constitutes a part of the pressure supply passage and a valve body that opens and closes the valve hole, and the control valve is interlocked with an opening and closing operation of the control valve. A movable body that moves to the first position when the valve is closed and moves to the second position when the valve is opened, the movable body provided separately from the valve body, and the position of the movable body And a valve state detecting means for detecting and outputting an open / closed state detection signal of the control valve. And wherein the door.

According to the variable capacity compressor of the present invention, the movable body interlocking with the opening / closing operation of the control valve having a valve hole constituting a part of the pressure supply passage and a valve body for opening / closing the valve hole , The movable body is provided separately from the valve body, and the movable body moves to the first position when the control valve is closed and moves to the second position when the control valve is opened. Therefore, the control valve is detected by detecting the position of the movable body. The open / closed state of can be detected. As a result, the variable capacity compressor can know the maximum discharge capacity state or the discharge capacity control state, and the driving torque of the variable capacity compressor can be accurately calculated. In addition, the maximum movable stroke of the movable body can be set to be significantly larger than the maximum opening / closing stroke of the valve body of the control valve, and even when the valve body of the control valve is slightly opened, the movable stroke of the movable body is increased. The open state of the control valve can be detected regardless of the opening degree of the valve body of the control valve.

It is sectional drawing which shows 1st Embodiment of the variable capacity compressor of this invention. It is sectional drawing of a non-return valve. The control valve is shown, (a) is an overall cross-sectional view, (b) is an enlarged view of a connecting portion of the valve body and the bellows assembly. It is a control characteristic figure showing the relation between control suction pressure of a control valve, and current value. The valve opening / closing detection part is shown, (a) is a whole sectional view showing a state when the control valve is closed, and (b) is a principal part sectional view showing a state when the control valve is opened. It is a figure which shows the arrangement | positioning relationship of the control valve and valve opening / closing detection part in the cylinder head seen from the valve plate side. It is a figure which shows the cylinder head accommodation cross section of the control valve and valve opening / closing detection part of the arrangement | positioning relationship of FIG. It is sectional drawing which shows 2nd Embodiment of the variable capacity compressor of this invention. It is a figure which shows the arrangement | positioning relationship of the control valve and valve opening / closing detection part in the cylinder head seen from the valve plate side. It is a figure which shows the cylinder head accommodation cross section of the control valve and valve opening / closing detection part of the arrangement | positioning relationship of FIG. The valve opening / closing detection part is shown, (a) is a whole sectional view showing a state when the control valve is closed, and (b) is a principal part sectional view showing a state when the control valve is opened. It is a figure which shows the example of a shape of the outflow hole formed in a 1st housing side wall. It is a block block diagram which shows an example of the drive torque calculating apparatus of the variable capacity compressor of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 shows a schematic configuration of a variable capacity compressor according to a first embodiment of the present invention, which is an example of a clutchless variable capacity compressor used in a vehicle air conditioner system.
In FIG. 1, the variable capacity compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101a, a front housing 102 provided at one end of the cylinder block 101, a valve plate 103 at the other end of the cylinder block 101, and the like. And a cylinder head 104 provided via the cylinder.

  A drive shaft 110 is provided so as to cross the crank chamber 140 formed by the cylinder block 101 and the front housing 102. A swash plate 111 is disposed around an intermediate portion of the drive shaft 110 in the axial direction. The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120 and is supported by the drive shaft 110 so that the tilt angle can be changed.

  The link mechanism 120 includes a first arm 112 a projecting from the rotor 112, a second arm 111 a projecting from the swash plate 111, and one end rotating relative to the first arm 112 a via the first connecting pin 122. A link arm 121 that is movably coupled and has the other end pivotally coupled to the second arm 111a via a second coupling pin 123.

  The through hole 111b of the swash plate 111 is formed in a shape that allows the swash plate 111 to tilt within the range of the maximum tilt angle (θmax) and the minimum tilt angle (θmin), and the through hole 111b has a minimum tilt restriction that abuts the drive shaft 110. And a maximum inclination angle restricting portion are formed. When the inclination angle of the swash plate 111 when the swash plate 111 is orthogonal to the drive shaft 110 is 0 °, the minimum inclination restriction portion of the through hole 111b is formed so that the swash plate 111 can be inclined to approximately 0 °. The maximum inclination restriction part is formed so that the swash plate 111 can be inclined to approximately 20 °.

  Around the drive shaft 110 between the rotor 112 and the swash plate 111, an inclination reduction spring 114 that urges the swash plate 111 toward the minimum inclination angle is mounted. Further, around the drive shaft 110 between the swash plate 111 and the spring support member 116 provided on the drive shaft 110, the inclination angle is increased so that the inclination angle of the swash plate 111 is increased to a predetermined inclination angle smaller than the maximum inclination angle. A spring 115 is attached. The biasing force of the tilt-increasing spring 115 at the minimum tilt angle is set to be larger than the biasing force of the tilt-decreasing spring 114, so that when the drive shaft 110 is not rotating, the swash plate 111 has a biasing force of the tilt-decreasing spring 114. It is positioned at a predetermined tilt angle that balances the biasing force of the tilt angle increasing spring 115.

  One end of the drive shaft 110 extends through the boss portion 102a of the front housing 102 to the outside of the front housing 102, and is connected to a power transmission device (not shown). A shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102a to shut off the crank chamber 140 and the external space.

  The coupling body of the drive shaft 110 and the rotor 112 is supported by bearings 131 and 132 in the radial direction, and supported by the bearing 133 and the thrust plate 134 in the thrust direction, and power from an external drive source (vehicle engine) is transmitted to the power transmission device. The drive shaft 110 rotates in synchronization with the power transmission device. The clearance between the drive shaft 110 and the thrust plate 134 is adjusted to a predetermined clearance by the adjustment screw 135.

  A piston 136 is disposed in the cylinder bore 101a, and an outer peripheral portion of the swash plate 111 is accommodated in an inner space of an end portion of the piston 136 that protrudes toward the crank chamber 140. The swash plate 111 includes a pair of shoes 137. Via the piston 136. Accordingly, the piston 136 reciprocates in the cylinder bore 101a by the rotation of the swash plate 111.

  In the cylinder head 104, a suction chamber 141 defined by an annular partition 104b and a discharge chamber 142 defined by the partition 104b and an outer peripheral wall and surrounding the suction chamber 141 in an annular shape are formed at the center. The suction chamber 141 communicates with the cylinder bore 101a via a suction hole 103a provided in the valve plate 103 and a suction valve (not shown) formed in the suction valve forming body, and a discharge chamber 142 is provided in the valve plate 103. The cylinder bore 101a communicates with the discharge hole 103b and a discharge valve (not shown) formed in the discharge valve forming body.

  The front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 105 through a gasket or the like (not shown) to form a compressor housing.

  A muffler 160 that reduces noise and vibration due to refrigerant pressure pulsation is provided on the cylinder block 101. The muffler 160 is formed by fastening the lid member 106 with a bolt (not shown) via a seal member (not shown) on a forming wall 101b formed in the upper part of the cylinder block 101.

  A connecting portion between the communication path 144 formed across the cylinder head 104, the valve plate 103, and the cylinder block 101 and communicating with the discharge chamber 142 and the muffler space 143 has a refrigerant gas from the discharge side refrigerant circuit to the discharge chamber 142. A check valve 200 for preventing backflow is disposed. The check valve 200 operates in response to a pressure difference between the upstream communication path 144 and the downstream muffler space 143. When the pressure difference is smaller than a predetermined value, the check valve 200 blocks the communication path 144 and the pressure difference is reduced. When it is larger than the predetermined value, the communication path 144 is opened. The discharge chamber 142 is connected to the discharge-side refrigerant circuit of the vehicle air-conditioning system via a discharge passage formed by the communication passage 144, the check valve 200, the muffler space 143, and the discharge port 106a.

  A suction passage 104a is formed in the cylinder head 104 in a straight line so as to cross a part of the discharge chamber 142 from the outside toward the suction chamber 141. The suction chamber 141 is connected to the suction side of the vehicle air conditioner system via the suction passage 104a. Connected to the refrigerant circuit.

  The cylinder head 104 is provided with a control valve 300. The control valve 300 is interposed in a pressure supply passage 145 that connects the discharge chamber 142 and the crank chamber 140 to adjust the opening of the pressure supply passage 145, and the amount of refrigerant gas introduced into the crank chamber 140 from the discharge chamber 142. To control. Further, the refrigerant in the crank chamber 140 flows into the suction chamber 141 via the pressure release passage 146 configured by the communication passage 101 c formed in the cylinder block 101, the space portion 101 d, and the orifice 103 c formed in the valve plate 103. . Therefore, the pressure in the crank chamber 140 can be changed by the control valve 300. Details of the control valve 300 will be described later. Here, the discharge chamber 142 and the crank chamber 140 correspond to a discharge pressure region and a pressure adjustment chamber of the present invention, respectively.

  The angle change operation of the swash plate 111 is caused by the inclination decreasing moment based on the pressure in the crank chamber 140 acting on the surface of the piston 136 on the crank chamber 140 side and the pressure in the cylinder bore 101a acting on the surface of the piston 136 on the cylinder bore 101a side. This is done by breaking the balance with the inclination increasing moment based on it. Therefore, if the pressure in the crank chamber 140 is changed by the control valve 300, the inclination angle of the swash plate 111, that is, the stroke of the piston 136 can be changed, and the discharge capacity of the variable capacity compressor 100 can be variably controlled. .

  A check valve 250 (shown by a broken line in the figure) is interposed in the communication passage 101e that constitutes the pressure supply passage 145 downstream of the control valve 300. As shown in FIG. 2, the check valve 250 is disposed in a valve chamber 101f formed at the end of the communication passage 101e facing the crank chamber 140, receives pressure on the communication passage 101e side at one end, and cranks at the other end. A valve body 251 that opens and closes the communication path 101e under pressure on the chamber 140 side, a compression coil spring 252 that is supported by the valve body 251 at one end side and elastically biases the valve body 251 in a direction to close the communication path 101e, and a compression coil spring And a support member 253 formed with a communication hole 253a that communicates the crank chamber 140 and the valve chamber 101f at the center. When the refrigerant discharged from the discharge chamber 142 flows into the communication passage 101e as the control valve 300 opens, the valve body 251 resists the urging force of the compression coil spring 252 in FIG. The pressure supply passage 145 is moved in the direction to allow the refrigerant to flow into the crank chamber 140, and the discharge refrigerant gas flows into the communication passage 101e from the discharge chamber 142 as the control valve 300 is closed. Is shut off, the valve body 251 operates to close the communication path 101e as shown in FIG. 2 by the urging force of the compression coil spring 252 and prevent the refrigerant from flowing from the crank chamber 140 toward the control valve 300.

  Further, as shown in FIG. 5, the cylinder head 104 includes a movable body accommodating portion 401 that accommodates the movable body 410 and a valve state detecting portion that detects the open / closed state of the control valve 300 by detecting the position of the movable body 410. A valve opening / closing detection unit 400 that is integrated with 402 is provided. Here, the movable body accommodation unit 401 and the valve state detection unit 402 correspond to the movable body accommodation unit and the valve state detection unit of the present invention. Details of the valve opening / closing detection unit 400 will be described later.

Details of the control valve 300 will be described with reference to FIG.
3A and 3B are diagrams showing the configuration of the control valve 300, in which FIG. 3A is an overall cross-sectional view, and FIG. 3B is an enlarged view of a connecting portion between the valve body and the bellows assembly.
The control valve 300 is formed in the valve housing 301, and includes a first pressure sensing chamber 302 that communicates with the crank chamber 140 via the communication hole 301a, a valve chamber 303 that communicates with the discharge chamber 142 via the communication hole 301b, and one end. Is slidable into a valve hole 301c having an opening in the first pressure sensing chamber 302 and the other end opening in the valve chamber 303, and a support hole 301d formed in the valve housing 301 on one end side and in the valve housing 301 on the other end side. The valve body 304 that opens and closes the valve hole 301c, and has a coil spring in a vacuumed interior, one end of which is fixed to the valve housing 301 and disposed in the first pressure sensing chamber 302, and the pressure in the crank chamber 140 is adjusted. The bellows assembly 305 that receives pressure is connected to one end of the bellows assembly 305 so that the other end of the bellows assembly 305 can be contacted and separated, and the other end is fixed to one end of the valve body 304 to displace the bellows assembly 305. A connecting portion 306 for transmitting to the valve body 304, a second pressure sensing chamber 307 in which the other end side of the valve body 304 is disposed and the pressure of the suction chamber 141 is introduced through the communication hole 301e, and the valve body 304 are integrated. The formed solenoid rod 304a is fixedly press-fitted and fixed to the end opposite to the valve body 304 side, and is fixed to the movable core 308 with a predetermined gap between the solenoid rod 304a and the solenoid rod 304a. A core 309, a coil spring 310 that is interposed between the fixed core 309 and the movable core 308 and elastically biases the valve body 304 in the valve opening direction via the movable core 308 and the solenoid rod 304a, and the movable core 308 and the fixed core A cylindrical member 312 made of a non-magnetic material and disposed around the outer periphery of 309 and fixed to the solenoid housing 311; and a solenoid so as to surround the cylindrical member 312. And it is configured to include an electromagnetic coil 313 accommodated in the id housing 311, a. In addition, three O-rings 313 a to 313 c are provided on the outer peripheral portion of the control valve 300.

  In the control valve 300 having such a configuration, the valve body 304 has a cylindrical outer peripheral portion having a single diameter over both ends of the support hole 301d, and one end side is formed around the valve hole 301c when the valve is closed. The seal position of the valve body 304 and the valve seat surface 301f is the valve body outer peripheral end 304b. Accordingly, the pressure receiving area of the crank chamber 140 that the valve body 304 receives from the first pressure sensing chamber 302 side through the valve hole 301c, and the suction chamber 141 side that acts on the valve body 304 via the second pressure sensing chamber 307. The pressure receiving area is substantially the same. Further, the pressure in the discharge chamber 142 acting on the valve chamber 303 does not act in the opening / closing direction of the valve body 304. The electromagnetic force generated by energizing the electromagnetic coil 313 acts in the valve closing direction of the valve body 304.

Accordingly, the pressure receiving area of the crank chamber 140 that the valve body 304 receives from the first pressure sensing chamber 302 side through the valve hole 301c, and the suction chamber 141 side that acts on the valve body 304 via the second pressure sensing chamber 307. If the pressure receiving area and the effective pressure receiving area in the valve body opening / closing direction of the bellows assembly 305 are set to substantially the same pressure receiving area (this is Sv), the force acting on the valve body 304 is expressed by the following equation: It is represented by (1).
Ps = − (1 / Sv) · F (i) + (F + f) / Sv (1)
Here, Ps is the control suction pressure of the suction chamber 141, F (i) is the electromagnetic force, f is the biasing force of the coil spring 310, and F is the biasing force of the bellows assembly 305.
From the above equation (1), the relationship between the control suction pressure Ps of the suction chamber 141 and the current value flowing through the electromagnetic coil 313 is as shown in FIG.

  Therefore, the control valve 300 communicates the discharge chamber 142 and the crank chamber 140 so that the control suction pressure Ps of the suction chamber 141 becomes a set value determined by the energization amount of the electromagnetic coil 313 given as an external signal from the outside. The discharge capacity of the variable capacity compressor 100 is varied by adjusting the opening of the pressure supply passage 145 and controlling the amount of refrigerant gas introduced into the crank chamber 140. The pressure sensing means constituted by the bellows 305, the connecting portion 306, and the valve body 304 reduces the opening of the pressure supply passage 145 to increase the discharge capacity when the pressure in the suction chamber 141 rises above the set value. Thus, the pressure in the crank chamber 140 is decreased, the refrigerant gas suction amount from the suction chamber 141 to the cylinder bore 101a is increased, and the pressure in the suction chamber 141 is decreased. On the other hand, when the pressure in the suction chamber 141 falls below the set value, the opening of the pressure supply passage 145 is increased to reduce the discharge capacity, the pressure in the crank chamber 140 is increased, and the pressure from the suction chamber 141 to the cylinder bore 101a is increased. The refrigerant gas suction amount is decreased to increase the pressure in the suction chamber 141. As described above, the pressure-sensitive means autonomously controls the valve opening so as to maintain the pressure (control pressure) of the suction chamber 141 at a set value determined by the electromagnetic coil energization amount.

5A and 5B are diagrams showing the configuration of the valve opening / closing detection unit 400 described above. FIG. 5A is an overall cross-sectional view showing a state when the control valve 300 is in a closed state, and FIG. The state when the control valve 300 is in the open state is shown.
The valve opening / closing detection unit 400 is configured by integrally assembling a movable body accommodation unit 401 and a valve state detection unit 402, and the valve state detection unit 402 is integrally assembled with a housing 420 of the movable body accommodation unit 401.

  The movable body accommodating portion 401 includes a movable body 410 and a housing 420, and the movable body 410 and the housing 420 are made of, for example, a metal material.

  The movable body 410 has a stepped cylindrical shape having a large-diameter portion 410a and a small-diameter portion 410b, and a magnet 411 is fixed to the end surface on the small-diameter portion 410b side.

  The housing 420 is integrated with the side wall 421 on the other end side opposite to the first end wall 422, a substantially cylindrical side wall 421 having one end opened, a first end wall 422 that is press-fitted and fixed to the opening side end of the side wall 421. And a second end wall 423 formed on the surface. A housing chamber 424 having a stepped portion 421d is formed in the housing 420. The large-diameter portion 421a and the small-diameter portion 421b are formed in accordance with the outer diameters of the large-diameter portion 410a and the small-diameter portion 410b of the movable body. The accommodation chamber 424 accommodates the movable body 410 so as to be movable, and is partitioned by the movable body 410 into a first chamber 424a and a second chamber 424b.

  The first chamber 424a of the storage chamber 424 communicates with the pressure region 104f1 shown in FIG. 7 through a communication hole 422a formed in the first end wall 422 and communicates between the control valve 300 and the check valve 250. The pressure of the passage 101e (pressure supply passage 145) acts. Further, the second chamber 424b of the storage chamber 424 communicates with the pressure region 104f2 shown in FIG. 7 through the communication hole 421c formed in the side wall 421 of the housing 420, and the pressure of the crank chamber 140 acts. As a result, the movable body 410 moves in the accommodation chamber 424 following the pressure difference between the pressure in the first chamber 424a and the pressure in the second chamber 424b.

  The movable body 410 is restricted from moving in the direction of the first end wall 422 when one end surface of the large-diameter portion 410 a abuts against the first end wall 422, and the other end surface of the large-diameter portion 411 a is a step in the storage chamber 424. The movement in the direction of the second end wall 423 is restricted by coming into contact with the portion 421d.

  In the movable body 410, one point of the large-diameter portion 410a contacts the large-diameter portion 421a of the storage chamber 424, one point of the small-diameter portion 410b contacts the small-diameter portion 421b of the storage chamber 424, and two points on the diagonal. Each gap is adjusted to be supported. Thereby, the movable body 410 can slide smoothly in the storage chamber 424 without the movement being hindered.

  The valve state detection unit 402 is disposed so as to face the magnet 411 across the second end wall 423 and detects, for example, a Hall element 431 and an output of the Hall element 431 as a detection element that detects a change in magnetic flux density of the magnet 411. An electronic circuit 432 that outputs a signal and an input / output connector terminal 433 connected to the electronic circuit 432 are insert-molded with resin. The valve state detection unit 402 is housed and fixed in the housing 420 on the second end wall 423 side and integrated with the movable body housing unit 401. In addition, two O-rings 441 a and 441 b are provided on the outer periphery of the housing 420 of the movable body accommodating portion 401.

  The valve state detection unit 402 detects the position of the movable body 410 whose position changes following the pressure difference between the first chamber 424a (upstream) and the second chamber 424b (downstream). Detects closed and open states. Specifically, when the control valve 300 is closed and the pressure in the first chamber 424a is lower than the pressure in the second chamber 424b, the movable body 410 is moved to the first chamber as shown in FIG. The magnet 411 comes into contact with the first end wall 422 which is the end surface of the 424a, and is located farthest from the Hall element 431 (first position). In addition, when the control valve 300 is opened and the pressure in the first chamber 424a is higher than the pressure in the second chamber 424b, the movable body 410 is separated from the first end wall 422 and moves toward the second chamber 424b. As shown in FIG. 5 (b), the magnet 411 moves to a position closest to the Hall element 431 (second position). The electronic circuit 432 receives a position detection signal corresponding to the position of the magnet 411 of the Hall element 431, and outputs a closed state detection signal of the control valve 300 when the movable body 410 contacts the first end wall 422. When the movable body 410 comes into contact with the step portion 421d, a valve open state detection signal of the control valve 300 is output. The maximum movable stroke of the movable body 410 is set to about several mm, which is significantly larger than the maximum opening / closing stroke (about 0.5 mm) of the valve body 304 of the control valve 300. Here, the magnet 411 and the Hall element 431 constitute a position detection unit that detects the position of the movable body 410, and the electronic circuit 432 outputs an open / closed state detection signal of the control valve 300 based on the output signal of the Hall element 431. It corresponds to the output unit.

6 is a diagram showing the arrangement relationship between the control valve 300 and the valve opening / closing detection unit 400 when the cylinder head 104 is viewed from the valve plate 103 side. FIG. 7 is a diagram showing the arrangement relationship between the control valve 300 and the control valve 300 in FIG. FIG. 4 is a view showing a housing cross section in the cylinder head 104 of the valve opening / closing detection unit 400.
The control valve 300 is accommodated in the accommodation hole 104e of FIG. 7 formed in the accommodation area indicated by the broken line in FIG. 6 of the cylinder head 104 with the first pressure-sensitive chamber 302 side as the tip. Further, the valve opening / closing detection unit 400 is housed in the housing hole 104f of FIG. 7 formed in the housing area indicated by the broken line in FIG. 6 of the cylinder head 104 with the communication hole 422a side as the tip. The tip of the accommodation hole 104 f is directed to the pressure region 104 e 3 around the first pressure sensing chamber 302 of the accommodation hole 104 e of the control valve 300.

  The accommodating hole 104e is formed by three O-rings 313a to 313c provided in the control valve 300, a pressure region 104e1 where the pressure of the suction chamber 141 acts, a pressure region 104e2 where the pressure of the discharge chamber 142b acts, and a crank chamber 140 It is partitioned into a pressure region 104e3 where pressure acts. The pressure region 104e1 communicates with the suction chamber 141 through a communication path 104d formed in the bottom wall 104h of the suction chamber 141 as shown in FIG. As shown in FIG. 6, the pressure region 104 e 2 communicates with the discharge chamber 142 through a communication passage 104 c formed in the cylinder head 104 and constituting a pressure supply passage 145 on the discharge chamber 142 side. As shown in FIG. 6, the pressure region 104e3 includes a communication passage 104m formed in one of a plurality of pressing protrusions 104i extending from the bottom wall 104h of the suction chamber 141 toward the valve plate 103, and the communication passage shown in FIG. It communicates with the crank chamber 140 via the control valve side pressure supply passage 101e and the check valve 250. Here, the discharge chamber 142 has a pressure supply passage 145 that passes through the communication passage 104c, the pressure region 104e2 of the accommodation hole 104e, the inside of the control valve 300, the pressure region 104e3, the communication passage 104m, the communication passage 101e, and the check valve 250. Via the crank chamber 140.

  In the housing hole 104f, the pressure of the pressure supply passage 145 (the communication passage 101e and the communication passage 104m) between the control valve 300 and the check valve 250 is controlled by two O-rings 441a and 441b provided in the valve opening / closing detection unit 400. It is divided into a pressure region 104f1 where the pressure acts and a pressure region 104f2 where the pressure in the crank chamber 140 acts. The pressure region 104f1 communicates with the pressure region 104e3 on the control valve 300 side through the communication passage 104g, and the pressure downstream of the control valve 300 is introduced through the pressure region 104e3. As shown in FIG. 6, the pressure region 104f2 passes through a communication path 104j formed in one of a plurality of pressing protrusions 104i extending from the bottom wall 104h of the suction chamber 141 toward the valve plate 103, the valve plate 103, and the like. The space 101 d formed in the cylinder block 101 communicates with the pressure in the crank chamber 140 through the pressure relief passage 146. In addition, when the control valve 300 is closed, in order to allow the refrigerant in the communication passage 101e to quickly flow out into the suction chamber 141, as shown in FIG. 6, a throttle that connects the pressure region 104e3 on the control valve 300 side and the suction chamber 141 is provided. A passage 104k is formed in the bottom wall 104h of the suction chamber 141. Here, the suction chamber 141 corresponds to the suction pressure region of the present invention, and the throttle passage 104k is a communication passage that connects the pressure supply passage 145 between the control valve 300 and the check valve 250 and the suction pressure region. Equivalent to.

Next, the operation of the variable capacity compressor 100 of the present embodiment will be described.
When the drive shaft 110 of the variable capacity compressor 100 is rotating by the driving force from the engine and the air conditioner is in an inactive state (OFF operation), the control valve 300 is opened in a non-energized state and the pressure supply passage 145 is opened. Is released. As a result, the pressure on the upstream side of the check valve 250 is increased. Since the urging force of the compression coil spring 252 is set so that the check valve 250 is surely opened by the discharge suction pressure difference during the OFF operation, the check valve 250 is opened at this time and the discharge chamber 142 The crank chamber 140 communicates with the crank chamber 140 via the pressure supply passage 145, and the discharged refrigerant gas is introduced into the crank chamber 140. Thereby, the variable capacity compressor 100 is operated with the minimum discharge capacity. It should be noted that since the check valve 200 interposed in the discharge passage is set not to open at the discharge suction pressure difference generated at the minimum discharge capacity, the compressed refrigerant is discharged from the discharge chamber 142 and the pressure supply passage. 145, the crank chamber 140, the pressure relief passage 146, and the suction chamber 141 are circulated through an internal path.

  During the minimum discharge capacity operation of the compressor 100, the pressure acting on the first chamber 424a of the movable body accommodating portion 401 is higher than the pressure acting on the second chamber 424b, and the movable body 410 is illustrated in FIG. As described above, it abuts on the stepped portion 421d. As a result, the valve state detection unit 402 outputs a position detection signal indicating that the position of the movable body 410 is the second position from the Hall element 431 to the electronic circuit 432, and the electronic circuit 432 A valve open state detection signal indicating that the valve is open is output to the outside via the input / output connector terminal 433.

  When the control valve 300 is energized with a predetermined control current value set according to the vehicle interior target temperature in order to operate the air conditioner, the control valve 300 is closed and divided by the control valve 300 and the check valve 250. The refrigerant gas in the pressure supply passage 145 (the communication passage 101e and the communication passage 104m) flows out from the throttle passage 104k in FIG. 6 to the suction chamber 141 via the pressure region 104e3, and is upstream of the check valve 250. The pressure in 145 decreases and the check valve 250 closes. As a result, the pressure acting on the first chamber 424a of the movable body accommodating portion 401 becomes lower than the pressure acting on the second chamber 424b, and the movable body 410 is separated from the step portion 421d as shown in FIG. Abuts against the first end wall 422. As a result, the valve state detection unit 402 outputs a position detection signal indicating that the position of the movable body 410 is the first position from the hall element 431 to the electronic circuit 432, and the electronic circuit 432 A valve closing state detection signal indicating the valve closing state is output to the outside via the input / output connector terminal 433.

  When the control valve 300 is closed, the discharged refrigerant gas is not introduced into the crank chamber 140, and only the blow-by gas generated when the piston 136 compresses the intake refrigerant flows into the crank chamber 140. The opening area of the orifice 103 c formed in the valve plate 103 has a necessary and sufficient area for flowing blow-by gas into the suction chamber 141, and the refrigerant gas in the crank chamber 140 is sucked through the pressure release passage 146. The pressure in the crank chamber 140 decreases and becomes equal to the pressure in the suction chamber 141. As a result, the check valve 200 installed in the discharge passage increases from the minimum discharge capacity, and the discharge chamber 142 is connected to the discharge side refrigerant circuit of the vehicle air conditioner system through the discharge passage. Circulates. Due to the pressure drop in the crank chamber 140, the tilt angle of the swash plate 111 increases to the maximum, and the variable displacement compressor 100 operates at the maximum discharge capacity.

  During the maximum discharge capacity operation of the variable capacity compressor 100, the pressure in the suction chamber 141 gradually decreases. When the pressure in the suction chamber 141 decreases to the set pressure set by the control current value of the control valve 300, the bellows of the bellows assembly 305 of the pressure sensing means expands and is connected to the connecting portion 306, and the valve body 304 is The valve hole 301c is opened away from the seating surface 301f, and the control valve 300 is opened. As a result, the pressure in the pressure supply passage (the communication passage 101e and the communication passage 104m) between the control valve 300 and the check valve 250 is increased, and the pressure acting on the first chamber 424a of the movable body accommodating portion 401 is increased. The pressure is higher than the pressure acting on the second chamber 424b, and the movable body 410 is separated from the first end wall 422 and contacts the stepped portion 421d as shown in FIG. 7B. As a result, the valve state detection unit 402 outputs a position detection signal indicating that the position of the movable body 410 is the second position from the hall element 431 to the electronic circuit 432, and the control valve 300 is opened from the electronic circuit 432. A valve open state detection signal indicating the valve state is output to the outside via the input / output connector terminal 433.

  After the control valve 300 is opened, the pressure of the pressure supply passage (the communication passage 101e and the communication passage 104m) on the upstream side of the check valve 250 increases due to the opening of the control valve 300, and the check valve 250 is opened and discharged. The chamber 142 and the crank chamber 140 communicate with each other through the pressure supply passage 145, and the discharged refrigerant gas is introduced into the crank chamber 140. Since the outflow amount of the refrigerant gas flowing out from the crank chamber 140 to the suction chamber 141 via the pressure release passage 146 is limited by the orifice 103c, the pressure in the crank chamber 140 increases. When the pressure difference between the pressure in the crank chamber 140 and the pressure in the suction chamber 141 increases to a predetermined value (ΔPH), the inclination angle of the swash plate 111 decreases and the discharge capacity decreases. When the discharge capacity decreases and the pressure in the suction chamber 141 increases, the bellows of the bellows assembly 305 of the pressure sensing means contracts, the valve body 304 moves in the valve closing direction, and the amount of discharged refrigerant gas introduced into the crank chamber 140 Decreases and the pressure in the crank chamber 140 decreases. When the pressure difference between the pressure in the crank chamber 140 and the pressure in the suction chamber 141 decreases to a predetermined value ΔPL (ΔPL <ΔPH) due to the pressure drop in the crank chamber 140, the inclination angle of the swash plate 111 increases and the discharge capacity increases. Thus, after the control valve 300 is opened, the valve opening degree of the control valve 300 is autonomously adjusted by the pressure sensing means so that the pressure of the suction chamber 141 becomes the set pressure set by the control current value, The variable capacity compressor 100 is operated in a discharge capacity control state in which the control current value and the control suction pressure value are uniquely related.

  That is, in the variable capacity compressor 100 of the present embodiment, when the control valve 300 is closed in the air conditioner operating state, the movable body 410 interlocks and contacts the inner surface side of the first end wall 422 that is the first position. The state detection unit 402 outputs a valve closing state detection signal indicating the valve closing state of the control valve 300. At this time, the variable capacity compressor 100 is in the maximum discharge capacity state. On the other hand, when the control valve 300 is opened, the movable body 410 is interlocked and comes into contact with the stepped portion 421d which is the second position, and the valve state detection unit 402 detects the valve opening state indicating the valve opening state. Output a signal. At this time, the variable capacity compressor 100 is in a discharge capacity control state.

  According to the variable displacement compressor 100 of the present embodiment, the control valve 300 is detected by detecting the position of the movable body 410 that moves between the first position and the second position in conjunction with the opening / closing operation of the control valve 300. Therefore, the maximum discharge capacity state and the discharge capacity control state of the variable capacity compressor 100 can be easily discriminated. Therefore, it is possible to accurately calculate the driving torque in the maximum discharge capacity state of the variable capacity compressor 100 in which the control current value of the control valve 300 does not substitute for the control pressure value of the suction chamber 141.

  Further, the valve opening / closing detection unit 400 has a simple configuration, and the movable body housing unit 401 and the valve state detection unit 402 are assembled together, so that the variable capacity compressor 100 can be easily mounted. The second chamber 424b of the storage chamber 424 in which the magnet 411 is stored is a pressure supply passage 145 (the communication passage 101e and the communication passage 101e) partitioned by the valve body 304 of the control valve 300 and the valve body 251 of the check valve 250. Since the area of the communication path 104m) is partitioned, foreign matter such as wear powder contained in the refrigerant flowing through the pressure supply path 145 (the communication path 101e and the communication path 104m) may enter the second chamber 424b. In addition, the foreign matter does not cause trouble in the valve state detection unit 402.

Next, a second embodiment of the variable capacity compressor of the present invention will be described.
The variable displacement compressor of this embodiment omits the check valve 250 interposed in the pressure supply passage 145 (communication passage 101e) downstream of the control valve in the first embodiment, and the function of this check valve is accommodated in a movable body. It is different from the first embodiment that it is incorporated in the part.

FIG. 8 shows a schematic configuration of the variable capacity compressor in the second embodiment, and is an example of a clutchless variable capacity compressor used in the vehicle air conditioner system similar to the first embodiment. In addition, the same code | symbol is attached | subjected to the same element as 1st Embodiment, and description is abbreviate | omitted.
8, in the variable capacity compressor 100 ′ of the present embodiment, the movable body accommodating portion 501 of the present embodiment, which will be described later, is provided with a check valve function so that the communication path 101e ( The formation position of the pressure supply passage 145 on the downstream side of the control valve 300 is set to the upper side of the communication passage 101c constituting a part of the pressure release passage 146, as indicated by a broken line in the figure.

FIG. 9 is a diagram showing an arrangement relationship between the control valve 300 and the valve opening / closing detection unit 500 when the cylinder head 104 of the present embodiment is viewed from the valve plate 103 side, and FIG. 10 is an arrangement relationship of FIG. It is a figure which shows the accommodation cross section in the cylinder head 104 of the control valve 300 and the valve opening / closing detection part 500. FIG.
The control valve 300 is accommodated in an accommodation hole 104e formed in the cylinder head 104, and the accommodation hole 104e has a pressure region 104e1 in which the pressure of the suction chamber 141 acts by the three O-rings 313a to 313c, and the pressure of the discharge chamber 142b. It is the same as in the first embodiment that it is divided into a pressure region 104e2 where the pressure acts and a pressure region 104e3 where the pressure in the crank chamber 140 acts.

  On the other hand, the valve opening / closing detection unit 500 is housed in the housing hole 104f, and the housing hole 104f is partitioned into two pressure regions 104f1 and 104f2 by two O-rings 561a and 561b. The communication with the pressure region 104e3 on the control valve 300 side via the passage 104g is the same as in the first embodiment. However, in this embodiment, as shown in FIG. 6), the pressure region 104f1 communicates with the pressure region 104f2 via the inside of the movable body accommodating portion 501 of the valve opening / closing detection unit 500, as will be described later, and the pressure region 104f2 is a cylinder head as shown in FIG. The communication path 104j formed in 104 and the communication path 101e formed in the cylinder block 101 via the valve plate 103 and the like communicate with each other. It is.

  Accordingly, the discharge chamber 142 includes the communication path 104c, the pressure area 104e2, the control valve 300, the pressure area 104e3, the communication path 104g, the pressure area 104f1, the movable body storage part 501, the pressure area 104f2, the communication path 104j, and the communication path 101e. Is communicated with the crank chamber 140 via a pressure supply passage 145 passing through. As in the first embodiment, a throttle passage 104k that connects the pressure region 104e3 and the suction chamber 141 is formed in the bottom wall 104h of the suction chamber 141. The throttle passage 104k is connected to the control valve 300 and the movable body. This corresponds to a communication path that connects the pressure supply path 145 between the accommodating portions 501 and the suction pressure region (in this embodiment, the suction chamber 141).

Next, the valve opening / closing detection unit 500 of this embodiment will be described.
11A and 11B are diagrams showing a configuration of the valve opening / closing detection unit 500. FIG. 11A is an overall cross-sectional view showing a state when the control valve 300 is in a closed state, and FIG. 11B is a main part configuration diagram showing a control valve. The state when 300 is in a valve open state is shown.

  The valve opening / closing detection unit 500 is configured by integrally assembling the movable body housing unit 501 having the above-described check valve function and the valve state detection unit 502. In the valve state detection unit 502, the Hall element 551, the electronic circuit 552, and the input / output connector terminal 553 are insert-molded with a resin material and have the same configuration as in the first embodiment. Is omitted. Below, the movable body accommodating part 501 provided with the function of the non-return valve is explained in full detail.

  The movable body accommodating portion 501 includes a movable body 510, a compression coil spring 520, a first housing 530, and a second housing 540. The first housing 530 and the second housing 540 are each formed of a metal material, for example, a brass-based material. Note that the first housing 530 may be formed of a resin material.

  The movable body 510 has a first member 511 formed in a substantially cylindrical shape with one end opening, and a one-end opening having a substantially cylindrical side wall fixed to the inner side of the opening end side of the first member 511 and having a smaller diameter than the first member 511. The second member 512 and the magnet 513 are fixed to the closed end side of the first member 512. An internal space 514 defined by the first member 511 and the second member 512 communicates with the outside of the movable body 510 through a communication hole 512 a formed in the second member 512. The first member 511 and the second member 512 are made of, for example, an aluminum-based metal material. Note that the first member 511 and the second member 512 may be formed of a resin material.

  The first housing 530 is formed in a substantially cylindrical shape with one end opening, and a valve seat 530a is formed on the inner surface side of the closed end side where the O-ring 561b is mounted on the outer peripheral surface. In addition, a refrigerant inflow hole 530b is formed in the central portion of the end wall on the closed end side, and a plurality of outflow holes 530c through which the refrigerant flows out through a first chamber 533a described later are formed in the side wall. In addition, a plurality of communication holes 530d are formed to communicate a second chamber 533b (described later) on the side wall and the pressure region 104f2.

  The second housing 540 has a cylindrical side wall 540a to which the O-ring 561a is attached, an end wall 540b that closes one end of the side wall 540a, and a second wall 540a that protrudes from the side wall 540a opposite to the side wall 540a. And a cylindrical portion 540c that movably supports the closed end side of the two members 512.

  By press-fitting and fixing the opening end side of the first housing 530 to the second housing 540, an accommodation chamber 533 (see FIG. 11B) for accommodating the movable body 510 is formed. The clearance between the outer surface of the first member 511 of the movable body 510 and the inner surface of the first housing 530 is managed to be as small as, for example, about several tens to 200 microns, and the storage chamber 533 is separated from the first chamber 533a by the movable body 510. It is partitioned into a second chamber 533b. The first chamber 533a can communicate with the pressure region 104f1 in the accommodation hole 104f through the inflow hole 530b, and can communicate with the pressure region 104f2 in the accommodation hole 104f through the plurality of outflow holes 530c. The second chamber 533b communicates with the region 104f2 in the accommodation hole 104f through the communication hole 530d. Therefore, the first chamber 533a communicates with the pressure supply passage (the pressure region 104f1, the communication passage 104g, and the pressure region 104e3) on the control valve 300 side, and the second chamber 533b is connected to the crank chamber 140 side pressure supply passage ( The pressure region 104f2, the communication path 104j, and the communication path 101e) communicate with each other. The first chamber 533a and the second chamber 533b communicate with each other through a plurality of outflow holes 530c, a pressure region 104f2, and a communication hole 530d. The outflow holes 530c, the pressure region 104f2, and the communication hole 530d are connected to each other. A communication portion that connects the first chamber 533a and the second chamber 533b is formed. A space portion surrounded by the cylindrical portion 540c of the second housing 540 and the second member 512 of the movable body 510 communicates with the second chamber 533b by a throttle passage 540d formed in the cylindrical portion 540c.

  The compression coil spring 520 is supported between the second housing 540 and the movable body 510 (the end surface of the first member 511) in the second chamber 533b, and urges the movable body 510 toward the valve seat 530a. The movable body 510 has an urging force in a state where the movable body 510 is seated on the valve seat 530a. By adjusting the press-fitting amount of the first housing 530, the urging force of the compression coil spring 520 can be adjusted. The cylindrical portion 540c of the second housing 540 is provided inside the compression coil spring 520 and also serves as a guide member for the compression coil spring 520.

  In the movable body 510, one point of the first member 511 is in contact with the inner surface of the first housing 530, and one point of the second member 512 is in contact with the inner surface of the cylindrical portion 540c of the second housing 540, so that two points diagonally exist. Each gap is adjusted so that it is supported by. Thereby, it can slide smoothly, without the movement of the movable body 510 being inhibited.

  In the movable body accommodating portion 501 having such a configuration, the movable body 510 accommodates the pressure difference between the pressure in the pressure region 104f1 upstream of the movable body 510 and the pressure in the pressure region 104f2 downstream of the movable body 510. It moves in the chamber 533. When the pressure difference is smaller than a predetermined value, the movable body 510 abuts the valve seat 530a to block the upstream side and the downstream side of the movable body 511, and when the pressure difference exceeds a predetermined value, the upstream side and the downstream side of the movable body 511. Open the side. In other words, when the pressure difference is smaller than the predetermined value, the pressure supply passage 145 between the control valve 300 and the crank chamber 140 is closed to prevent the flow of refrigerant from the crank chamber 140 to the control valve 300 side. Exceeds a predetermined value, the pressure supply passage 145 between the control valve 300 and the crank chamber 140 is opened to allow the refrigerant to flow into the crank chamber 140. Therefore, in this embodiment, the movable body accommodating portion 501 has the function of the check valve 250 of the first embodiment, and the movable body 510 functions as a valve body of the check valve. Note that the biasing force of the compression coil spring 420 is extremely small, and the movable body 510 is opened (even if the differential pressure generated when the control valve 300 is turned off and the variable displacement compressor 100 'operates with the minimum discharge capacity). In FIG. 11, it is set to move in the right direction.

  The movable body accommodating portion 501 of the present embodiment can increase the movable stroke of the movable body 510 by weakening the biasing force of the compression coil spring 420 and setting the spring constant small. Thereby, even when the valve body 304 of the control valve 300 is slightly opened, the movable stroke of the movable body 510 of the movable body accommodating portion 501 is increased, and the control valve 300 is independent of the opening degree of the valve body 304 of the control valve 300. The valve open state can be detected. The maximum movable stroke of the movable body 510 is set to about several millimeters, which is significantly larger than the maximum opening / closing stroke (about 0.5 mm) of the valve body 304 of the control valve 300.

  In order to increase the movable stroke of the movable body 510, as shown in FIGS. 12A to 12C, the shape of the outflow hole 530c formed in the side wall of the first housing 530 is such that the apex angle is on the valve seat 530a side. It is desirable to have a substantially triangular shape directed to Thus, the movable stroke of the movable body 510 can be increased even in the low flow rate region of the refrigerant, and the detection accuracy of the valve opening state of the control 300 can be improved.

Next, the operation of the variable capacity compressor 100 ′ of the second embodiment will be described.
In a state where the drive shaft 110 of the variable capacity compressor 100 ′ is rotated by the driving force from the engine, the control valve 300 that is not energized when the air conditioner is in an inactive state (OFF operation) is opened and the pressure supply passage 145 is opened. Is released. As a result, the pressure in the pressure supply passage 145 on the upstream side of the movable body accommodating part 501 of the valve opening / closing detection part 500 is increased. Since the urging force of the compression coil spring 520 is set so that the movable body accommodating portion 501 is reliably opened by the discharge suction pressure difference during the OFF operation, the movable body 510 of the movable body accommodating portion 501 is shown in FIG. ), The discharge chamber 142 and the crank chamber 140 communicate with each other via the pressure supply passage 145, the discharge refrigerant gas is introduced into the crank chamber 140, and the variable capacity compressor 100 'operates with the minimum discharge capacity. Is done. At this time, the check valve 200 does not open, and the compressed refrigerant circulates in an internal path constituted by the discharge chamber 142, the pressure supply passage 145, the crank chamber 140, the pressure release passage 146, and the suction chamber 141. This is the same as in the first embodiment.

  During the minimum discharge capacity operation of the compressor 100 ′, the pressure acting on the first chamber 533 a of the movable body accommodating portion 501 is higher than the pressure acting on the second chamber 533 b, and the level difference of the second member 512 of the movable body 510. As shown in FIG. 11B, the portion 512b contacts the end surface 540e of the cylindrical portion 540c of the second housing 540, and the movement of the movable body 510 is restricted. Thereby, in the valve state detection unit 502, the position detection signal indicating that the position of the movable body 510 is the second position (position where the magnet 513 is closest to the Hall element 551) from the Hall element 551 to the electronic circuit 552. The electronic circuit 552 outputs a valve open state detection signal indicating that the control valve 300 is in a valve open state to the outside via the input / output connector terminal 553.

  When the control valve 300 is energized with a predetermined control current value set according to the vehicle interior target temperature in order to operate the air conditioner, the control valve 300 is closed and partitioned by the control valve 300 and the valve opening / closing detection unit 500. The refrigerant gas in the pressure supply passage 145 (the pressure region 104e3, the communication passage 104g, and the pressure region 104f1) flows out from the throttle passage 104k to the suction chamber 141, and the pressure in the upstream pressure supply passage 145 of the valve opening / closing detection unit 500. Decreases. As a result, the pressure acting on the first chamber 533a of the movable body accommodating portion 501 becomes lower than the pressure acting on the second chamber 533b, and the movable body 510 comes into contact with the valve seat 530a to cause the pressure region 104f1 and the pressure region 104f2. And shut off. As a result, in the valve state detection unit 502, the position detection signal indicating that the position of the movable body 510 is the first position (position where the magnet 513 is farthest from the Hall element 551) from the Hall element 551 to the electronic circuit 552. Is output, and the electronic circuit 552 outputs a closed state detection signal indicating that the control valve 300 is closed to the outside via the input / output connector terminal 553.

  In the state where the control valve 300 is closed, as in the first embodiment, only the blow-by gas generated when the piston 136 compresses the sucked refrigerant flows into the crank chamber 140, and the refrigerant gas in the crank chamber 140 is The pressure is discharged to the suction chamber 141 through the pressure release passage 146, and the pressure in the crank chamber 140 is reduced to be equal to the pressure in the suction chamber 141. As a result, the check valve 200 installed in the discharge passage increases from the minimum discharge capacity, and the discharge chamber 142 is connected to the discharge side refrigerant circuit of the vehicle air conditioner system through the discharge passage. Circulates. Due to the pressure drop in the crank chamber 140, the inclination angle of the swash plate 111 increases to the maximum, and the variable capacity compressor 100 'operates at the maximum discharge capacity.

  During the maximum discharge capacity operation of the variable capacity compressor 100 ′, the pressure in the suction chamber 141 gradually decreases. When the pressure in the suction chamber 141 decreases to the set pressure set by the control current value of the control valve 300, the bellows of the bellows assembly 305 of the pressure sensing means expands and is connected to the connecting portion 306, and the valve body 304 is The valve hole 301c is opened away from the seating surface 301f, and the control valve 300 is opened. As a result, the pressure in the pressure supply passage 145 (the pressure region 104e3, the communication passage 104g, and the pressure region 104f1) on the upstream side of the valve opening / closing detection unit 500 is increased, and the pressure acting on the first chamber 533a of the movable body accommodating portion 501 is increased. The pressure is higher than the pressure acting on the second chamber 533b, and the stepped portion 512b of the second member 512 of the movable body 510 comes into contact with the end surface 540e of the cylindrical portion 540c of the second housing 540 as shown in FIG. As a result, in the valve state detection unit 502, a position detection signal indicating that the position of the movable body 510 is the second position is output from the hall element 551 to the electronic circuit 552, and the control valve 300 is opened from the electronic circuit 552. A valve open state detection signal indicating the valve state is output to the outside via the input / output connector terminal 553.

  After the control valve 300 is opened, the movable body 510 of the movable body accommodating portion 501 is opened, and the discharge chamber 142 and the crank chamber 140 are communicated with each other through the pressure supply passage 145 so that the discharged refrigerant gas is transferred to the control valve 300 and the movable body. It is introduced into the crank chamber 140 via the accommodating portion 501. Since the outflow amount of the refrigerant gas flowing out from the crank chamber 140 to the suction chamber 141 via the pressure release passage 146 is limited by the orifice 103c, the pressure in the crank chamber 140 increases. When the pressure difference between the pressure in the crank chamber 140 and the pressure in the suction chamber 141 increases to a predetermined value (ΔPH), the inclination angle of the swash plate 111 decreases and the discharge capacity decreases. When the discharge capacity decreases and the pressure in the suction chamber 141 increases, the bellows of the bellows assembly 305 of the pressure sensing means contracts, the valve body 304 moves in the valve closing direction, and the amount of discharged refrigerant gas introduced into the crank chamber 140 Decreases and the pressure in the crank chamber 140 decreases. When the pressure difference between the pressure in the crank chamber 140 and the pressure in the suction chamber 141 decreases to a predetermined value ΔPL (ΔPL <ΔPH) due to the pressure drop in the crank chamber 140, the inclination angle of the swash plate 111 increases and the discharge capacity increases. Thus, after the control valve 300 is opened, the valve opening degree of the control valve 300 is autonomously adjusted by the pressure sensing means so that the pressure of the suction chamber 141 becomes the set pressure set by the control current value, The variable capacity compressor 100 ′ is operated in a discharge capacity control state in which the control current value and the control suction pressure value are uniquely related.

  According to the variable capacity compressor 100 ′ of this embodiment, in addition to the function and effect of the first embodiment, the function of the check valve is incorporated in the movable body accommodating portion 501 of the valve opening / closing detection unit 500. There is an advantage that 250 can be omitted and the manufacturing cost can be suppressed.

  In addition, since the magnet 513 is disposed in the space surrounded by the cylindrical portion 540c and the second member 512, the magnet 513 and the Hall element 551 are configured by foreign matter such as wear powder contained in the refrigerant flowing through the pressure supply passage 145. It is possible to prevent problems in position detection by the position detection means. Furthermore, the damper passage 540d formed in the cylindrical portion 540c can have a damper effect on the movement of the movable body 510 in the space surrounded by the cylindrical portion 540c and the second member 512.

Next, an example of the driving torque calculation device of the variable capacity compressors 100 and 100 'of the present invention will be shown and described.
FIG. 13 is a block diagram showing a configuration related to driving torque calculation in air conditioner ECU 600 of the vehicle air conditioner system.
In FIG. 13, an evaporator target temperature setting means 610 sets an evaporator outlet air temperature that is a final target of discharge capacity control based on a vehicle interior temperature setting (not shown) and various external information. The control current setting means 620 calculates the deviation between the target temperature set by the evaporator target temperature setting means 610 and the actual temperature detected by the temperature detection means 630 disposed at the evaporator outlet. A control current value I for energizing the electromagnetic coil 313 of the control valve 300 is set so as to decrease. The driving unit 640 drives the electromagnetic coil 313 so that the current flowing through the electromagnetic coil 313 of the control valve 300 becomes the control current value I set by the control current setting unit 620. The control current is adjusted by changing the duty ratio by PWM (pulse width modulation) at a predetermined drive frequency (for example, 400 to 500 Hz). Therefore, the variable capacity compressor 100 (or 100 ′) adjusts the control current value I so that the actual temperature detected by the temperature detecting means 630 approaches the target temperature set by the evaporator target temperature setting means 610. Thus, the discharge capacity is controlled.

  The drive torque calculation means 650 includes, for example, an output signal Pd from the high pressure detection means 660, an output signal Ne from the engine speed detection means 670, an output signal Vr from the flow rate detection means 680, and an output signal I (control) from the control current setting means 620. Current value I) and an output signal (valve open / closed state detection signal) of the valve open / close detection unit 400 (or 500) are input. The drive torque calculation means 650 calculates the drive torque Tr of the variable capacity compressor 100 (or 100 ') based on these input signals, and outputs it to the engine ECU 700. The high pressure detection means 660 and the flow rate detection means 680 are arranged in a high pressure side refrigerant circuit between the discharge chamber 142 of the variable capacity compressor 100 (or 100 ′) and the condenser (not shown) of the air conditioner system, for example. .

When the valve closing state detection signal is input from the valve opening / closing detection unit 400 (or 500), the drive torque calculating means 650 is in the closed state, that is, the control valve 300 is in the closed state, and the variable capacity compressor 100 (or 100 ') is turned on. When operating at the maximum discharge capacity, the drive torque Tr of the variable capacity compressor 100 (or 100 ') is calculated as a function of, for example, the following four parameters.
Tr = f (Vr, Pd, Ps, Ne)
Here, Ps is the control pressure of the suction chamber 141 and can be easily estimated from other parameters as a fixed value because it is during the maximum discharge capacity operation.

Further, when a valve open state detection signal is input from the valve opening / closing detection unit 400 (or 500), that is, the control valve 300 is in the valve open state, and the variable displacement compressor 100 (or 100 ') is in the discharge capacity control state. When operating, since the control pressure in the suction chamber 141 is equivalent to the set pressure set by the control current value I, the drive torque calculating means 650 uses the control current value I input from the control current setting means 620. Instead of the control pressure Ps of the suction chamber 141, the driving torque Tr of the variable capacity compressor 100 (or 100 ') is calculated as a function of the following four parameters.
Tr = f (Vr, Pd, I, Ne)

  That is, the drive torque calculating means 650 controls the control current of the control valve 300 as the control pressure Ps of the suction chamber 141 for torque calculation only when the variable capacity compressor 100 (or 100 ′) is operating in the discharge capacity control state. Substituting the value I and calculating the drive torque Tr of the variable capacity compressor 100 (or 100 ') using the value estimated from other parameters as the control pressure Ps of the suction chamber 141 in the case of the maximum discharge capacity state. The calculated drive torque Tr does not deviate greatly from the actual torque, and the calculation accuracy of the drive torque of the variable capacity compressor is improved.

  In the movable body accommodating portion 401 of the first embodiment, a throttle passage that communicates the first chamber 424a and the second chamber 424b when the large diameter portion 410a of the movable body 410 abuts on the stepped portion 421d. It is good to provide between the contact surfaces of the large diameter portion 410a and the stepped portion 421d. As a result, when foreign matter enters the first chamber 424a, the foreign matter is easily discharged from the second chamber 424b to the crank chamber 140 via the throttle passage.

  In the movable body accommodating portion 501 of the second embodiment, the main flow of the refrigerant flow flowing from the control valve 300 side flows downstream from the inflow hole 530b via the first chamber 533a and the outflow hole 530c. The portion leaks into the second chamber 533b through a minute gap between the side wall of the first member 511 of the movable body 510 and the inner surface of the first housing 530. There is a possibility that foreign matter may enter the second chamber 533b along this flow. In order to suppress this, an annular groove that guides foreign matter to the outflow hole 530c may be formed in the middle portion of the side wall of the first member 511.

  Moreover, in each embodiment, although movable body accommodating part 401,501 and valve state detection part 402,502 were integrated, you may make it arrange | position separately.

  Moreover, in each embodiment, although the example of the variable capacity compressor provided with the control valve which has the pressure-sensitive means which autonomously controls the pressure of the suction chamber 141 to a predetermined value was shown, two points of the discharge pressure area | region inside a compressor are shown. The present invention is also applied to a variable capacity compressor having a control valve having pressure-sensitive means for autonomously controlling a differential pressure between two points in a suction pressure region, or a differential pressure between a high pressure region and a low pressure region. Applicable.

  Moreover, in each embodiment, although it was set as the clutchless variable capacity compressor, it is good also as a variable capacity compressor with a clutch. Further, if it is a variable capacity compressor provided with a control valve having a pressure sensing means that autonomously adjusts the opening of the pressure supply passage by receiving the pressure inside the compressor, it is not limited to the reciprocating type of this embodiment, Other drive type variable capacity compressors such as vane type and scroll type may be used.

  Further, the open / closed state detection output indicating the control valve open / closed state output from the valve state detection unit can be used for control of each control device such as an evaporator blower fan, an inside / outside air switching damper, an air mix damper, etc. of the air conditioner system. Conceivable.

  DESCRIPTION OF SYMBOLS 100,100 '... Variable capacity compressor, 140 ... Crank chamber, 141 ... Suction chamber, 142 ... Discharge chamber, 145 ... Pressure supply passage, 250 ... Check valve, 300 ... Control valve, 305 ... Bellows, 306 ... Connection part 304, valve body, 400, 500 ... valve opening / closing detection unit, 401, 501 ... movable body housing unit, 402, 502 ... valve state detection unit, 410, 510 ... movable body, 411, 513 ... magnet, 424a, 533a ... First chamber, 424b, 533b ... second chamber, 431, 551 ... Hall element, 432, 552 ... electronic circuit

Claims (8)

A control valve having pressure sensing means that senses the control pressure and autonomously adjusts the valve opening so that the control pressure becomes a set pressure set by an external signal communicates the discharge pressure region and the pressure adjustment chamber. In a variable capacity compressor that is interposed in a pressure supply passage and adjusts the opening of the pressure supply passage by the control valve to adjust the pressure in the pressure adjustment chamber to vary the discharge capacity of the refrigerant,
The control valve includes a valve hole that constitutes a part of the pressure supply passage and a valve body that opens and closes the valve hole.
In conjunction with the opening and closing operation of the control valve, the movable body moves to the first position when the control valve is in the closed state and moves to the second position when the control valve is in the opened state, and is separated from the valve body A movable body provided as a
Valve state detecting means for detecting the position of the movable body and outputting an open / closed state detection signal of the control valve;
A variable capacity compressor characterized by comprising: The pressure supply passage is interposed between the control valve and the pressure regulation chamber, and the pressure supply passage is closed in accordance with the valve closing operation of the control valve so that the refrigerant from the pressure regulation chamber to the control valve side A check valve that prevents flow and opens the pressure supply passage in accordance with the opening operation of the control valve to allow the refrigerant to flow into the pressure adjustment chamber;
A communication path communicating the pressure supply path between the control valve and the check valve and the suction pressure region;
A storage chamber for movably storing the movable body, wherein the storage chamber communicates with the first chamber and the pressure adjustment chamber communicating with the pressure supply passage between the control valve and the check valve; Movable body containing means partitioned by the movable body into the second chamber,
With
The valve state detection means detects when the movable body moves to the end face side of the first chamber as the first position, outputs a valve closing state detection signal of the control valve, The variable capacity compressor according to claim 1, wherein a valve open state detection signal of the control valve is output with the second position as the time of movement toward the end face. Pressure regulation with a first chamber that is movably accommodated in a storage chamber interposed in a pressure supply passage between the control valve and the pressure adjustment chamber, and that communicates the storage chamber with the control valve side pressure supply passage. The movable body that partitions into a second chamber communicating with the chamber-side pressure supply passage, an elastic member that elastically biases the movable body toward the first chamber, the first chamber, and the second chamber A communicating portion that communicates with the control valve, and the movable body closes the communicating portion in accordance with the closing operation of the control valve, and the refrigerant flows from the first chamber to the second chamber side. The movable body opens the communication portion against the urging force of the elastic member in accordance with the opening operation of the control valve, and the refrigerant flows from the first chamber into the second chamber. Movable body containing means having a check valve function that enables
A communication path communicating the pressure supply path and the suction pressure region between the control valve and the movable body housing means;
With
The valve state detection means detects when the movable body moves to the closed side of the communication portion as the first position, outputs a valve closed state detection signal of the control valve, and opens the open side of the communication portion. 2. The variable capacity compressor according to claim 1, wherein a valve open state detection signal of the control valve is output with the second position as a time when moved to an end face side of the second chamber.   The valve state detection unit integrally includes a position detection unit that detects the position of the movable body, and an output unit that outputs an open / closed state detection signal of the control valve based on an output signal of the position detection unit. The variable capacity compressor according to any one of claims 1 to 3. The variable capacity compressor according to claim 2 or 3 , wherein the movable body housing means and the valve state detection means are assembled together.   The position detection unit of the valve state detection unit includes a magnet fixed to one end of the movable body, and a detection element that detects a change in magnetic flux of the magnet due to the movement of the movable body, and the magnet is movable. The variable capacity compressor according to claim 5, which is disposed on the second chamber side of the body housing means.   Reciprocating the piston in the cylinder bore compresses the refrigerant sucked into the cylinder bore from the suction chamber and discharges it to the discharge chamber, and controls the pressure in the crank chamber behind the piston to change the stroke of the piston 7. A reciprocating variable displacement compressor that varies the discharge capacity of the refrigerant, wherein the discharge pressure region is the discharge chamber and the pressure adjustment chamber is the crank chamber. The variable capacity compressor described in 1.   The control valve is configured to sense the pressure in the suction chamber as the control pressure and to autonomously adjust the pressure in the suction chamber with the pressure sensing means so that the pressure in the suction chamber becomes a set pressure set by an external signal. 8. The variable capacity compressor according to 7.