WO2018186034A1

WO2018186034A1 - Variable displacement compressor

Info

Publication number: WO2018186034A1
Application number: PCT/JP2018/005606
Authority: WO
Inventors: 田口　幸彦; 崇戸井田; 聖寺内; 井口　智博; 淑恵松嵜
Original assignee: サンデン・オートモーティブコンポーネント株式会社
Priority date: 2017-04-06
Filing date: 2018-02-09
Publication date: 2018-10-11
Also published as: JP2018178792A; JP6830397B2

Abstract

Provided is a variable displacement compressor capable of preventing the intrusion of foreign matter into a second control valve. A variable displacement compressor 100 comprises: a first control valve 300 that controls the opening degree of a supply passage 145; a check valve 350; a second control valve 400 that controls the opening degree of an exhaust passage 146; and a back pressure relief passage 147 that communicates an intermediate supply passage 145b1 and an intake chamber 141. The second control valve 400 includes: a back pressure chamber 410 that communicates with the intermediate supply passage 145b1 via a communication path 104k; a valve chamber 420 where a valve hole 103d and an exhaust hole 431a are open and that constitutes a portion of the exhaust passage 146; a partition member 430 that partitions the back pressure chamber 410 and the valve chamber 420; and a spool 440. A communication path-side connection site 104k1, which extends from at least a connection section 104e of the communication path 104k to the backpressure chamber 410 side, extends out at an acute angle with respect to a communication path 104d which extends from a connection section 104e of the intermediate supply passage 145b1 to the first control valve 300 side.

Description

Variable capacity compressor

The present invention relates to a variable capacity compressor whose discharge capacity changes according to the pressure of a control pressure chamber such as a crank chamber.

As an example of this type of variable capacity compressor, a variable capacity compressor described in Patent Document 1 includes a first control valve that controls the opening of a pressure supply passage that connects a discharge chamber and a crank chamber, a crank chamber, A second control valve for controlling the opening of a pressure release passage communicating with the suction chamber; and the first control valve provided between the first control valve and the crank chamber in the pressure supply passage. And a check valve for preventing the reverse flow of the refrigerant toward the engine, and the discharge capacity is controlled by regulating the pressure in the crank chamber.
Further, the second control valve is partitioned from the back pressure chamber by a back pressure chamber communicating with a region downstream of the first control valve in the pressure supply passage via a communication passage, and a partition member, A valve chamber forming a part of the pressure release passage and having a valve hole communicating with the crank chamber on a wall surface opposite to the back pressure chamber; a pressure receiving portion disposed in the back pressure chamber; And a spool having a shaft portion that extends through the partition member and connects the pressure receiving portion and the valve portion. The second control valve is configured such that a force that moves the spool in a direction approaching the valve hole by the pressure applied to the pressure receiving portion when the first control valve is opened opens the spool by the pressure applied to the valve portion. When the force is greater than the force to move away from the valve hole, the valve portion abuts against the wall surface of the valve chamber to close the valve hole and minimize the opening of the pressure relief passage, and the first control The force that moves the spool in the direction approaching the valve hole due to the pressure applied to the pressure receiving portion when the valve is closed is smaller than the force that moves the spool away from the valve hole due to the pressure applied to the valve portion. In this case, the valve section is configured to open the valve hole away from the wall surface and maximize the opening of the pressure release passage.

JP, 2006-108960, A

In the conventional variable capacity compressor, when the first control valve opens the pressure supply passage, the refrigerant in the downstream region of the pressure supply passage from the first control valve passes through the communication passage. Then, by flowing into the back pressure chamber of the second control valve, the pressure in the back pressure chamber increases. As a result, the spool moves in a direction (a direction approaching the valve hole) that minimizes the opening of the pressure release passage.
Here, in the conventional variable capacity compressor, there is a possibility that minute foreign matter may flow along with the refrigerant through the pressure supply passage. However, since the communication path is open to the end wall of the back pressure chamber, if foreign matter flows along with the refrigerant, the foreign matter easily flows into the back pressure chamber along with the refrigerant flow. When foreign matter flows into the back pressure chamber, there is a risk that the operation of the spool may be hindered.
Accordingly, an object of the present invention is to provide a variable capacity compressor that can prevent or suppress foreign matter from entering the second control valve that controls the opening degree of the discharge passage.

According to one aspect of the present invention, the suction chamber into which the refrigerant is guided, the compression section that sucks and compresses the refrigerant in the suction chamber, the discharge chamber into which the refrigerant compressed by the compression section is discharged, and the control pressure chamber A variable capacity compressor is provided that has a discharge capacity that changes according to the pressure in the control pressure chamber. The variable capacity compressor includes a first control valve, a check valve, a second control valve, and a back pressure relief passage. The first control valve is provided in a supply passage for supplying the refrigerant in the discharge chamber to the control pressure chamber, and controls the opening of the supply passage. The check valve is provided in a downstream supply passage between the first control valve and the control pressure chamber in the supply passage, and prevents reverse flow of the refrigerant from the control pressure chamber toward the first control valve. Operates as follows. The second control valve is provided in a discharge passage for discharging the refrigerant in the control pressure chamber to the suction chamber, and controls the opening degree of the discharge passage. The back pressure relief passage communicates the suction chamber with an intermediate supply passage between the first control valve and the check valve in the downstream supply passage and has a throttle portion. The second control valve includes a back pressure chamber, a valve chamber, a partition member, and a spool. The back pressure chamber communicates with the intermediate supply passage. The valve chamber has a valve hole communicating with an upstream discharge passage between the second control valve and the control pressure chamber in the discharge passage, and a discharge hole communicating with the suction chamber, and the discharge passage Part of The partition member partitions the back pressure chamber and the valve chamber. The spool includes a pressure receiving portion disposed in the back pressure chamber, a valve portion disposed in the valve chamber and contacting and separating from a valve seat around the valve hole, and the pressure receiving portion extending through the partition member. It has a shaft part connecting the valve part. The second control valve moves the spool in accordance with the pressure in the back pressure chamber and the pressure in the upstream discharge passage to bring the valve portion into and out of contact with the valve seat. The opening degree is configured to be controlled. The back pressure chamber communicates with the intermediate supply passage through a communication passage connected to the back pressure chamber and the intermediate supply passage. One end of the communication path is connected to a connection portion provided in the middle of the intermediate supply path. The communication passage side connection portion extending from at least the connection portion of the communication passage toward the back pressure chamber side is an intermediate supply extending from the connection portion of the intermediate supply passage toward the first control valve side. It extends at an acute angle with respect to the passage-side connecting portion.

According to the variable capacity compressor according to the one aspect of the present invention, the check valve is provided in a downstream supply passage between the first control valve and the control pressure chamber in the supply passage, and the second The back pressure chamber of the control valve communicates with the intermediate supply passage between the first control valve and the check valve in the downstream supply passage via the communication passage. And the communicating path side connection site | part extended toward the said back pressure chamber side at least from the said connection part of this communicating path extends toward the said 1st control valve side from the said connecting part of the said intermediate supply passages. It extends at an acute angle with respect to the intermediate supply passage side connection site. Thus, even if minute foreign matter flows through the intermediate supply passage along with the refrigerant, all or most of the foreign matter flows in the connection portion from the first control valve side to the check valve side. Since the fluid flows along the main flow, it is possible to prevent or suppress foreign matter from entering the back pressure chamber. As a result, the spool can be operated satisfactorily even if minute foreign matter is distributed along with the refrigerant. In this way, it is possible to provide a variable capacity compressor capable of preventing or suppressing foreign matter from entering the second control valve.

It is sectional drawing of the variable capacity compressor in one Embodiment of this invention. It is the conceptual diagram which showed the systematic diagram of the channel | path which a refrigerant | coolant distribute | circulates with sectional drawing of the 1st control valve of the said variable capacity compressor. It is a principal part expanded sectional view of the said variable capacity compressor. It is a partial expanded sectional view including a part of discharge passage of the variable capacity compressor. It is a partial expanded sectional view including the back pressure relief passage of the variable capacity compressor. It is a diagram which shows the correlation with the coil energization amount of a said 1st control valve, and setting pressure. It is a partial expanded sectional view containing the non-return valve of the said variable capacity compressor. It is sectional drawing of the 2nd control valve of the said variable capacity compressor. It is sectional drawing which shows the modification of the said 2nd control valve.

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 illustrates a variable capacity clutchless compressor applied to a vehicle air conditioner system (air conditioner system). FIG. 1 shows a state when the variable capacity clutchless compressor is mounted on a vehicle (that is, a compressor installed state). In the drawing, the upper side is the upper side in the direction of gravity and the lower side is the gravity. The direction is on the lower side.
A variable capacity compressor 100 shown in FIG. 1 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, and a valve plate 103 at the other end of the cylinder block 101. And a cylinder head 104 provided. A crank chamber 140 as a control pressure chamber is formed by the cylinder block 101 and the front housing 102, and the drive shaft 110 is provided across the crank chamber 140.
A swash plate 111 is disposed around an intermediate portion in the extending direction of the axis O of the drive shaft 110. The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120, and the tilt angle with respect to the axis O 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 pivotable to the first arm 112 a via the first connecting pin 122. And a link arm 121 having the other end rotatably connected to the second arm 111a via a second connection pin 123.
The through hole 111b of the swash plate 111 is formed in a shape that allows the swash plate 111 to tilt in a range between the maximum inclination angle and the minimum inclination angle, and the minimum inclination angle restricting portion that contacts the drive shaft 110 is formed in the through hole 111b. ing. When the inclination angle of the swash plate 111 when the swash plate 111 is orthogonal to the drive shaft 110 is set to 0 deg, the minimum inclination restriction portion of the through hole 111b is formed so that the swash plate 111 can be inclined to approximately 0 deg. Further, the maximum inclination angle of the swash plate 111 is regulated by the swash plate 111 coming into contact with the rotor 112.
Between the rotor 112 and the swash plate 111, an inclination reduction spring 114 that urges the swash plate 111 in a direction to reduce the inclination angle of the swash plate 111 is mounted. Further, between the swash plate 111 and the spring support member 116 provided on the drive shaft 110, an inclination increasing spring 115 that biases the swash plate 111 in a direction to increase the inclination angle of the swash plate 111 is mounted. Here, the biasing force of the tilt-increasing spring 115 at the minimum tilt angle is set larger than the biasing force of the tilt-decreasing spring 114, and when the drive shaft 110 is not rotating, the swash plate 111 is biased by the tilt-decreasing spring 114. And the urging force of the inclination increasing spring 115 are positioned at an inclination angle that balances.
One end of the drive shaft 110 extends through the boss portion 102a protruding outside 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.
A 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 a bearing 133 and a thrust plate 134 in the thrust direction. The power from the external drive source is transmitted to the power transmission device, and the drive shaft 110 can rotate in synchronization with the rotation of the power transmission device. The gap between the portion of the drive shaft 110 with which the thrust plate 134 abuts and the thrust plate 134 is adjusted to a predetermined gap 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. It is comprised so that it may interlock with piston 136 via. The piston 136 reciprocates in the cylinder bore 101 a by the rotation of the swash plate 111. In the cylinder head 104, a suction chamber 141 is formed at the center, and a discharge chamber 142 that surrounds the radially outer side of the suction chamber 141 in a ring shape is defined.
The suction chamber 141 and the cylinder bore 101a communicate with each other via a communication hole 103a provided in the valve plate 103 and a suction valve (not shown) formed in the suction valve forming plate 150. The discharge chamber 142 and the cylinder bore 101a communicate with each other via a communication hole 103b provided in the valve plate 103 and a discharge valve (not shown) formed in the discharge valve forming plate 151.
In this embodiment, the front housing 102, the center gasket (not shown), the cylinder block 101, the cylinder gasket 152, the suction valve forming plate 150, the valve plate 103, the discharge valve forming plate 151, the head gasket 153, and the cylinder head 104 are sequentially arranged. Connected and fastened by a plurality of through-bolts 105 to form a compressor housing. In the present embodiment, the suction chamber 141 and the discharge chamber 142 are formed in a cylinder head 104 as a housing member constituting one end portion of the compressor housing. Specifically, the suction chamber 141 is disposed on an extension line of the axis O of the drive shaft 110 extending from the other end portion of the compressor housing toward the one end side in the compressor housing, and the discharge chamber 142 is the suction chamber 141. Is formed in an annular shape so as to surround the suction chamber 141 on the radially outer side perpendicular to the axis O. In the present embodiment, the extending direction of the axis O of the drive shaft 110 corresponds to the “center axis extending direction of the compressor housing” according to the present invention.
Further, a muffler is provided on the upper portion of the cylinder block 101 in FIG. The muffler is formed by fastening a lid member 106 where the discharge port 106a is opened and a forming wall 101b formed in the upper part of the cylinder block 101 with a bolt via a seal member (not shown). A discharge check valve 200 is disposed in a muffler space 143 surrounded by the lid member 106 and the forming wall 101b.
The discharge check valve 200 is disposed at a connection portion between the communication path 144 that connects the discharge chamber 142 and the muffler space 143 and the muffler space 143, and is connected to the communication path 144 (upstream side) and the muffler space 143 (downstream side). It operates in response to the pressure difference. When the pressure difference is smaller than the predetermined value, the communication path 144 is shut off, and when the pressure difference is larger than the predetermined value, the communication path 144 is opened. Accordingly, the discharge chamber 142 is connected to the refrigerant circuit (the high-pressure side) of the air conditioner system via the discharge passage formed by the communication passage 144, the discharge check valve 200, the muffler space 143, and the discharge port 106a.
In the cylinder head 104, a suction passage 104a is linearly extended from the outside in the radial direction of the cylinder head 104 so as to cross a part of the discharge chamber 142, and the suction chamber 141 is sucked into the air conditioning system through the suction passage 104a. It is connected to the side refrigerant circuit.
The refrigerant on the low pressure side of the refrigerant circuit of the air conditioning system is guided to the suction chamber 141 through the suction passage 104a. The refrigerant in the suction chamber 141 is sucked into the cylinder bore 101a by the reciprocating motion of the piston 136, compressed, and discharged into the discharge chamber 142. That is, in this embodiment, the cylinder bore 101a and the piston 136 constitute a compression unit that sucks and compresses the refrigerant in the suction chamber 141. Then, the refrigerant discharged to the discharge chamber 142 (refrigerant compressed by the compression unit) is guided to the high-pressure side of the refrigerant circuit of the air conditioner system through the discharge passage.
A supply passage 145 is formed in the cylinder head 104. A first control valve 300 and a check valve 350 are provided in the supply passage 145. A discharge passage 146 is formed in the cylinder block 101 and the cylinder head 104. A second control valve 400 is provided in the discharge passage 146. Further, a back pressure relief passage 147 is provided between the cylinder block 101 and the cylinder head 104.
[Supply passage]
FIG. 2 is a conceptual diagram showing a system diagram of a passage through which the refrigerant flows together with a cross-sectional view of the first control valve 300, and FIG. 3 shows the variable capacity compressor 100 including the check valve 350 and the second control valve 400. FIG. The supply passage 145 is a passage for supplying the refrigerant in the discharge chamber 142 to the crank chamber 140. Here, the passage between the discharge chamber 142 and the first control valve 300 in the supply passage 145 is called an upstream supply passage 145a, and the passage between the first control valve 300 and the crank chamber 140 in the supply passage 145 is downstream. This is referred to as a side supply passage 145b. The supply passage 145 is opened and closed by the first control valve 300 via the first control valve 300 as will be described later. The check valve 350 is provided in the downstream supply passage 145b.
In the present embodiment, the supply passage 145 is a second region S2 (described later) of the communication passage 104b formed in the cylinder head 104 and the accommodation hole 104c of the first control valve 300 formed in the cylinder head 104 (see FIG. 2). ), The inside of the first control valve 300 (see FIG. 2), a third region S3 (see FIG. 2) to be described later in the accommodation hole 104c, a communication path 104d formed in the cylinder head 104, and a cylinder block in the cylinder head 104 101 (head gasket 153), a connecting portion 104e that opens to the connecting end surface 104h, a communication hole of the head gasket 153, a communication hole of the discharge valve forming plate 151, a communication hole 103c formed in the valve plate 103, and a suction valve forming plate 150. Through the valve hole 152a formed in the cylinder gasket 152 and the cylinder block 101. The discharge chamber 142 and the crank chamber 140 are communicated with each other via a communication passage 101e and a second passage 351c2 and a first passage 351c1 (see FIG. 7 described later) of the check valve 350. ing. Therefore, in the present embodiment, the communication passage 104b constitutes the upstream supply passage 145a, the third region S3 (see FIG. 2), the communication passage 104d, the connection portion 104e, the communication hole of the head gasket 153, and the discharge valve forming plate 151. The communication hole, the communication hole 103c, the communication hole of the suction valve forming plate 150, the valve hole 152a of the cylinder gasket 152, the communication path 101e, and the path including the second path 351c2 and the first path 351c1 are connected to the downstream supply path 145b. Constitute.
[Discharge passage]
The discharge passage 146 is a passage for discharging the refrigerant in the crank chamber 140 to the suction chamber 141. In the present embodiment, as shown in FIGS. 1 to 3, the discharge passage 146 is branched into two passages on the suction chamber 141 side, and one of the passages (a first discharge passage 146a described later) is the second passage. Opened and closed by the second control valve 400 via the control valve 400. In the present embodiment, the discharge passage 146 passes through the end surface of the cylinder block 101 on the front housing 102 side and extends to the cylinder head 104 side. The communication passage 101c is connected to the discharge passage 146, and the cylinder head of the cylinder block 101 is connected to the discharge passage 146. There is a space 101d opened at the end face on the 104 side.
FIG. 4 is a partially enlarged view including a part of the discharge passage 146 (second discharge passage 146b described later).
In the present embodiment, the discharge passage 146 branches from the space 101d into a first discharge passage 146a and a second discharge passage 146b as shown in FIGS. From the space 101d, the first discharge passage 146a has a communication hole of the cylinder gasket 152, a communication hole of the suction valve forming plate 150, a valve hole 103d which will be described later penetrating the valve plate 103, and a valve chamber 420 which will be described later of the second control valve 400. , And is formed to open to the suction chamber 141 via the discharge hole 431a. As shown in FIG. 4, the second discharge passage 146 b is formed from the space 101 d to the communication hole formed in the cylinder gasket 152, the groove 150 a as a fixed throttle formed in the suction valve forming plate 150, and the valve plate 103. The communication hole 103e, the communication hole of the discharge valve forming plate 151, and the communication hole of the head gasket 153 are provided to bypass the second control valve 400, and the space 101d and the suction chamber 141 are always in communication with each other. Yes. Further, a passage between the second control valve 400 and the crank chamber 140 in the discharge passage 146 is referred to as an upstream discharge passage 146c (see FIG. 2). The flow passage cross-sectional area of the first discharge passage 146a when opened by the second control valve 400 is set to be larger than the flow passage cross-sectional area of the groove 150a as a fixed throttle of the second discharge passage 146b.
[Back pressure relief passage (throttle passage)]
As shown in FIGS. 2 and 3, the back pressure relief passage 147 communicates the suction chamber 141 with the intermediate supply passage 145b1 between the first control valve 300 and the check valve 350 in the downstream supply passage 145b. This is a passage as a throttle passage having a throttle portion 147a.
FIG. 5 is a partially enlarged view including the back pressure relief passage 147.
In the present embodiment, the throttle portion 147a is composed of a groove portion formed through the discharge valve forming plate 151. The groove portion opens in the connection portion 104e and opens in the communication hole of the head gasket 153. In the present embodiment, the back pressure relief passage 147 is connected to the connecting portion 104e (that is, the intermediate supply passage 145b1) and the suction chamber via the communication hole of the throttle portion 147a and the head gasket 153 formed in the discharge valve forming plate 151. 141 is always in communication.
The intermediate supply passage 145b1 (see FIG. 2) of the downstream supply passage 145b includes a third region S3 (see FIG. 2), a communication passage 104d, a connection portion 104e, a communication hole of the head gasket 153, and a discharge valve forming plate. 151, the communication hole 103c, the communication hole of the suction valve forming plate 150, the valve hole 152a of the cylinder gasket 152, and the passage between the connecting portion 104e and the check valve 350 of the communication passage 101e. ing.
When the first control valve 300 is closed, the refrigerant in the intermediate supply passage 145b1 flows out to the suction chamber 141 through the back pressure relief passage 147. As a result, the pressure in the back pressure chamber 410 (described later) of the intermediate supply passage 145b1 and the second control valve 400 decreases. As a result, as will be described later, the check valve 350 and the spool 440 of the second control valve 400 move.
[Outline of the first control valve]
The first control valve 300 is a valve that controls the opening area (opening degree) of the supply passage 145. Specifically, the first control valve 300 is accommodated in an accommodation hole 104 c formed in the cylinder head 104 as shown in FIGS. 1 and 2. In the present embodiment, O-rings 300a to 300c are mounted on the first control valve 300, and the O-rings 300a to 300c are connected to the suction chamber 141 through the communication passage 104f in the accommodation hole 104c. A first region S1, a second region S2 communicating with the discharge chamber 142 via the communication passage 104b, and a third region communicating with the crank chamber 140 via the communication passage 104d, the connecting portion 104e, the communication passage 101e, and the check valve 350. A region S3 is partitioned. The second region S2 and the third region S3 of the accommodation hole 104c constitute a part of the supply passage 145. The first control valve 300 controls the opening degree of the supply passage 145 in response to the pressure of the suction chamber 141 introduced through the communication passage 104f and the electromagnetic force generated by the current flowing through the solenoid in response to the external signal ( And the discharge gas introduction amount (pressure supply amount) into the crank chamber 140 is controlled.
[Outline of check valve]
The check valve 350 is provided in the downstream supply passage 145b (in other words, the supply passage 145 downstream from the first control valve 300) in the supply passage 145, and prevents reverse flow of the refrigerant from the crank chamber 140 toward the first control valve 300. In addition, the valve operates to allow the flow of the refrigerant from the first control valve 300 toward the crank chamber 140. Specifically, the check valve 350 is formed at an opening end portion on the valve plate 103 side in the communication path 101e of the cylinder block 101, and is accommodated in an accommodation hole 101g constituting a part of the communication path 101e.
[Outline of the second control valve]
The second control valve 400 is a valve that is provided in the discharge passage 146 (the first discharge passage 146a in the present embodiment) and controls the opening degree of the discharge passage 146. Specifically, the second control valve 400 is housed in a housing hole 104g formed in the cylinder head 104 and opened in the suction chamber 141, and opens and closes the first discharge passage 146a of the discharge passage 146. A spool 440 is included. The second control valve 400 includes a pressure in the intermediate supply passage 145b1 between the first control valve 300 and the check valve 350 in the downstream supply passage 145b (specifically, a pressure in a back pressure chamber 410 described later), a crank The spool 440 is moved in accordance with the pressure in the chamber 140 (specifically, the pressure in the upstream discharge passage 146c) to control (adjust) the opening degree of the discharge passage 146, and the refrigerant from the crank chamber 140 to the suction chamber 141 is controlled. Control emissions.
When the first control valve 300 and the check valve 350 are closed, the second control valve 400 opens the first discharge passage 146a. In this case, the discharge passage 146 includes a first discharge passage 146a and a second discharge passage 146b. As a result, the refrigerant in the crank chamber 140 immediately flows into the suction chamber 141, the pressure in the crank chamber 140 is equivalent to the pressure in the suction chamber 141, the inclination angle of the swash plate is maximized, and the piston stroke (discharge capacity) is maximized. It becomes.
In addition, when the first control valve 300 and the check valve 350 are open, the second control valve 400 closes the first discharge passage 146a. In this case, the discharge passage 146 includes only the second discharge passage 146b. As a result, the refrigerant in the crank chamber 140 is restricted from flowing into the suction chamber 141 and the pressure in the crank chamber 140 is likely to increase. As the pressure in the crank chamber 140 increases, the inclination angle of the swash plate 111 decreases from the maximum, and the piston stroke can be variably controlled.
As described above, the variable capacity compressor 100 includes the suction chamber 141, the compression unit, the discharge chamber 142, and the crank chamber 140 as a control pressure chamber, and the discharge capacity changes according to the pressure of the crank chamber 140. In other words, it is a compressor whose discharge capacity is controlled by pressure regulation in the crank chamber 140.
Next, the first control valve 300, the check valve 350, and the second control valve 400 will be described in detail.
[First control valve]
Returning to FIG. 2, the first control valve 300 includes a valve unit and a drive unit (solenoid) that opens and closes the valve unit, and is accommodated in an accommodation hole 104 c formed in the cylinder head 104.
The valve unit of the first control valve 300 includes a cylindrical valve housing 301. Inside the valve housing 301, a first pressure sensing chamber 302, a valve chamber 303, and a second pressure sensing chamber 307 are arranged in the axial direction. They are arranged in order.
The first pressure sensing chamber 302 is connected to the crank chamber via a communication hole 301 a formed in the outer peripheral surface of the valve housing 301, a third region S 3 in the accommodation hole 104 c, and a communication passage 104 d formed in the cylinder head 104. 140.
The second pressure sensing chamber 307 is a suction chamber via a communication hole 301e formed in the outer peripheral surface of the valve housing 301, a first region S1 in the accommodation hole 104c, and a communication passage 104f formed in the cylinder head 104. 141. The valve chamber 303 communicates with the discharge chamber 142 via a communication hole 301 b formed in the outer peripheral surface of the valve housing 301, a second region S <b> 2 of the accommodation hole 104 c, and a communication passage 104 b formed in the cylinder head 104. is doing. The first pressure sensing chamber 302 and the valve chamber 303 can communicate with each other through a valve hole 301c.
A support hole 301 d is formed between the valve chamber 303 and the second pressure sensing chamber 307. A bellows 305 is disposed in the first pressure sensing chamber 302. The bellows 305 has a built-in spring and has a built-in spring. The bellows 305 is disposed so as to be displaceable in the axial direction of the valve housing 301, and serves as a pressure sensing means for receiving the pressure in the first pressure sensing chamber 302, that is, the crank chamber 140. It has a function.
A cylindrical valve body 304 is accommodated in the valve chamber 303. The valve body 304 can slide in the support hole 301 d while the outer peripheral surface is in close contact with the inner peripheral surface of the support hole 301 d, and can move in the axial direction of the valve housing 301. One end of the valve body 304 can open and close the valve hole 301 c, and the other end of the valve body 304 protrudes into the second pressure sensing chamber 307. One end of a rod-shaped connecting portion 306 is fixed to one end of the valve body 304. The other end of the connecting portion 306 is disposed so as to be able to contact the bellows 305 and has a function of transmitting the displacement of the bellows 305 to the valve body 304.
The drive unit of the first control valve 300 has a cylindrical solenoid housing 312 that is coaxially connected to the end of the valve housing 301. The solenoid housing 312 houses a molded coil 314 in which the electromagnetic coil is covered with resin. The solenoid housing 312 houses a cylindrical fixed core 310 coaxially with the mold coil 314, and the fixed core 310 extends from the valve housing 301 to the vicinity of the center of the mold coil 314. The end of the fixed core 310 on the side opposite to the valve housing 301 is surrounded by a cylindrical sleeve 313. The fixed core 310 has an insertion hole 310 a in the center, and one end of the insertion hole 310 a opens into the second pressure sensing chamber 307. A cylindrical movable core 308 is accommodated between the fixed core 310 and the closed end of the sleeve 313.
A solenoid rod 309 is inserted into the insertion hole 310a, and one end of the solenoid rod 309 is fixed to the proximal end side of the valve body 304 by press fitting. The other end of the solenoid rod 309 is press-fitted into a through hole formed in the movable core 308, and the solenoid rod 309 and the movable core 308 are integrated. A release spring 311 is provided between the fixed core 310 and the movable core 308 to urge the movable core 308 in a direction away from the fixed core 310 (valve opening direction).
The movable core 308, the fixed core 310, and the solenoid housing 312 are formed of a magnetic material and constitute a magnetic circuit. The sleeve 313 is made of a nonmagnetic material such as a stainless steel material. The mold coil 314 is connected to a control device provided outside the variable capacity compressor 100 via a signal line. The mold coil 314 generates an electromagnetic force F (i) when the control current I is supplied from the control device. The electromagnetic force F (i) of the mold coil 314 attracts the movable core 308 toward the fixed core 310 and drives the valve body 304 in the valve closing direction.
In addition to the electromagnetic force F (i) by the mold coil 314, the valve body 304 of the first control valve 300 has a biasing force fs by the release spring 311, a force by the pressure in the valve chamber 303 (discharge chamber pressure Pd), A force due to the pressure in the pressure sensing chamber 302 (crank chamber pressure Pc), a force due to the pressure in the second pressure sensing chamber 307 (suction chamber pressure Ps), and a biasing force F due to a spring built in the bellows 305 act.
Here, the effective pressure receiving area Sb in the expansion / contraction direction of the bellows 305, the pressure receiving area Sv of the crank chamber acting on the valve body 304 from the valve hole 301c side, and the cross-sectional area Sr of the cylindrical outer peripheral surface of the valve body 304 are Sb = Sv = Sr. Therefore, the relationship between the forces acting on the valve body 304 is expressed by Equation 1. In Equation 1, “+” indicates the valve closing direction of the valve body 304, and “−” indicates the valve opening direction.

The connecting body of the bellows 305, the connecting portion 306, and the valve body 304 reduces the crank chamber pressure Pc by reducing the opening of the supply passage 145 in order to increase the discharge capacity when the suction chamber pressure Ps becomes higher than the set pressure. When the suction chamber pressure Ps falls below the set pressure, the opening of the supply passage 145 is increased to increase the crank chamber pressure Pc in order to reduce the discharge capacity. That is, the first control valve 300 autonomously controls the opening degree (opening area) of the supply passage 145 so that the suction chamber pressure Ps approaches the set pressure.
FIG. 6 is a diagram showing the correlation between the coil energization amount of the first control valve 300 and the set pressure. Since the electromagnetic force of the mold coil 314 acts on the valve body 304 via the solenoid rod 309 in the valve closing direction, when the energization amount to the mold coil 314 increases, a force in the direction of decreasing the opening of the supply passage 145 is applied. As shown in FIG. 6, the set pressure changes in the decreasing direction. The control device (drive unit) controls energization to the mold coil 314 by pulse width modulation (PWM control) at a predetermined frequency in the range of, for example, 400 Hz to 500 Hz, and the current value flowing through the mold coil 314 becomes a desired value. The pulse width (duty ratio) is changed as follows.
When the air conditioning system is in operation, that is, in the operating state of the variable capacity compressor 100, the energization amount to the mold coil 314 is adjusted by the control device based on the air conditioning setting such as the set temperature and the external environment, and the suction chamber pressure Ps is set to the energization amount. The discharge volume is controlled so that the set pressure corresponds to. Further, when the air conditioner system is not operated, that is, when the variable capacity compressor 100 is not operated, the control device turns off the energization to the mold coil 314. As a result, the supply passage 145 is opened by the release spring 311, and the discharge capacity of the variable capacity compressor 100 is controlled to a minimum state.
[Check valve]
Next, the check valve 350 will be described with reference to FIG. FIG. 7 is a partially enlarged cross-sectional view including the check valve 350 of the variable capacity compressor 100. FIG. 7A shows a state in which the check valve 350 is operated in a direction allowing the refrigerant flow from the first control valve 300 toward the crank chamber 140, and FIG. 7B shows that the check valve 350 is cranked. The state which act | operated in the direction which blocks | prevents the backflow of the refrigerant | coolant which goes to the 1st control valve 300 from the chamber 140 is shown.
The check valve 350 includes a valve body 351, a housing hole 101g for housing the valve body 351, and a cylinder gasket 152 as a valve seat forming member having a valve hole 152a and a valve seat 152b for closing one end of the housing hole 101g. I have. That is, the cylinder gasket 152 is formed with a valve hole 152a and a valve seat 152b.
The valve body 351 includes a substantially cylindrical peripheral wall 351a and an end wall 351b connected to one end of the peripheral wall 351a. The peripheral wall 351a has a large diameter portion 351a1 forming an intermediate portion in the longitudinal direction of the valve body, a connection between the large diameter portion 351a1 and the end wall 351b, a first small diameter portion 351a2 having a smaller diameter than the large diameter portion 351a1, and a large diameter. A second small-diameter portion 351a3 having a smaller diameter than the large-diameter portion 351a1 extending from the end surface opposite to the first small-diameter portion 351a2 in the portion 351a1. An internal passage is formed in the valve body 351. The internal passage passes through the first passage 351c1 formed from the open end of the peripheral wall 351a toward the end wall 351b and the peripheral wall of the first small-diameter portion 351a2, and around the first passage 351c1 and the first small-diameter portion 351a2. The second passage 351c2 communicates with the accommodation hole 101g. The valve body 351 is formed of a resin material, for example, but may be formed of other materials such as a metal material.
The housing hole 101g is formed at an opening end portion on the valve plate 103 side in the communication path 101e of the cylinder block 101 and constitutes a part of the communication path 101e. The housing hole 101g includes a small-diameter portion 101g1 on the crank chamber 140 side and a large-diameter portion 101g2 on the valve plate 103 side that is larger in diameter than the small-diameter portion 101g1. The large diameter portion 351a1 of the valve body 351 is slidably supported by the large diameter portion 101g2, and the second small diameter portion 351a3 of the valve body 351 is slidably supported by the small diameter portion 101g1.
The housing hole 101g is formed so as to be orthogonal to the end face of the cylinder block 101, and the valve body 351 moves in the extending direction of the axis O of the drive shaft 110. When the end wall 351b of the valve body 351 abuts on the valve seat 152b, one movement of the valve body 351 is restricted, and the other end of the peripheral wall 351a abuts on the end surface 101g3 of the accommodation hole 101g so that the valve body 351 The other movement is restricted. When the end wall 351b contacts the valve seat 152b, the valve hole 152a is closed, and when the end wall 351b moves away from the valve seat 152b, the valve hole 152a is opened.
The accommodation hole 101g communicates with the third region S3 in the accommodation hole 104c of the first control valve 300 via the intermediate supply passage 145b1 between the first control valve 300 and the check valve 350 in the downstream supply passage 145b. . The communication passage 101e extends through the end surface of the cylinder block 101 on the front housing 102 side and extends toward the cylinder head 104, passes through the end surface 101g3 of the accommodation hole 101g, and passes through the accommodation hole 101g to the end surface on the cylinder head 104 side. It is open.
Accordingly, the pressure Pm of the intermediate supply passage 145b1 (pressure upstream of the check valve 350) acts on one end of the valve body 351, and the crank chamber pressure Pc (downstream of the check valve 350) acts on the other end of the valve body 351. The valve body 351 moves in the axial direction according to the upstream and downstream pressure difference (Pm−Pc) acting on the valve body 351.
The intermediate supply passage 145b1 communicates with the suction chamber 141 via the back pressure relief passage 147. The back pressure relief passage 147 is provided with a throttle portion 147a. Therefore, in the state where the first control valve 300 opens the valve hole 301c, most of the refrigerant gas in the discharge chamber 142 is communicated with the communication passage 104d, the connection portion 104e, the communication hole of the head gasket 153, and the communication of the discharge valve forming plate 151. It reaches the valve hole 152a of the check valve 350 via the hole, the communication hole 103c, and the communication hole of the suction valve forming plate 150. For this reason, the pressure Pm of the intermediate supply passage 145b1 acting on one end of the valve body 351 increases, and Pm−Pc> 0. Then, due to the pressure difference (Pm−Pc) between the upstream and downstream acting on the valve body 351, the end wall 351b of the valve body 351 is separated from the valve seat 152b, and the other end of the peripheral wall 351a is in contact with the end surface 101g3 of the accommodation hole 101g. It becomes a state. As a result, the refrigerant gas in the discharge chamber 142 passes from the valve hole 152a to the large-diameter portion 101g2 of the accommodation hole 101g, the second passage 351c2, the first passage 351c1, and the communication passage 101e downstream from the check valve 350, and the crank chamber. 140.
When the first control valve 300 closes the valve hole 301c from the state in which the valve hole 301c is opened, the refrigerant gas in the discharge chamber 142 is not supplied to the intermediate supply passage 145b1, and the refrigerant in the intermediate supply passage 145b1. The gas flows into the suction chamber 141 via the back pressure relief passage 147. For this reason, the pressure Pm of the intermediate supply passage 145b1 acting on one end of the valve body 351 is reduced to satisfy Pm−Pc <0. Then, due to the upstream and downstream pressure difference (Pm−Pc) acting on the valve body 351, the other end of the peripheral wall 351a is separated from the end surface 101g3 of the housing hole 101g, and the end wall 351b of the valve body 351 contacts the valve seat 152b. The communication between the communication passage 101e downstream of the check valve 350 and the intermediate supply passage 145b1 is blocked. As a result, the pressure Pm in the intermediate supply passage 145b1 becomes equal to the suction chamber pressure Ps. Thus, the check valve 350 is configured to open and close the supply passage 145 in conjunction with opening and closing of the first control valve 300.
The check valve 350 may be configured to add a biasing means such as a compression coil spring that biases the valve body 351 toward the valve seat 152b. Further, the valve seat forming member is not limited to the cylinder gasket 152, and may be, for example, the suction valve forming plate 150 or the valve plate 103.
[Second control valve]
The second control valve 400 will be described with reference to FIGS. 1 to 3 and FIG. 8 which is a cross-sectional view of the second control valve 400.
The second control valve 400 includes a back pressure chamber 410, a valve chamber 420, a partition member 430, and a spool 440. The second control valve 400 is accommodated in an accommodation hole 104g that is formed in the cylinder head 104 and opens to the suction chamber 141. The
As shown in FIG. 3, the accommodation hole 104 g is formed so as to open to the connection end surface 104 h side of the cylinder head 104 with the cylinder block 101 (head gasket 153). Specifically, the accommodation hole 104g is formed in a stepped columnar shape on a protrusion 104j protruding from the closed end wall 104i of the suction chamber forming wall of the cylinder head 104 toward the valve plate 103 side. Yes. Specifically, the protrusion 104 j is disposed on the extension of the axis O of the drive shaft 110 and is located in the radial center of the suction chamber 141. The protrusion 104j extends from the closed end wall 104i of the cylinder head 104 to a position before the connection end surface 104h so as to have a gap with the head gasket 153. The housing hole 104g has a central axis substantially coincident with the axis O of the drive shaft 110, a large diameter portion on the connection end surface 104h side of the cylinder head 104, a small diameter portion having a smaller diameter than the large diameter portion on the back side, and a large diameter portion. A step portion is formed between the small-diameter portion, the small-diameter portion constitutes the first accommodating chamber 104g1, and the large-diameter portion constitutes the second accommodating chamber 104g2 that accommodates the partition member 430.
The back pressure chamber 410 communicates with the intermediate supply passage 145b1 through the communication passage 104k connected to the back pressure chamber 410 and the intermediate supply passage 145b1. Therefore, the pressure in the back pressure chamber 410 is equal to the pressure Pm in the intermediate supply passage 145b1. In the present embodiment, the back pressure chamber 410 includes the first storage chamber 104g1 partitioned by the partition member 430. The communication path 104k will be described in detail later.
The valve chamber 420 communicates with the valve hole 103 d communicating with the upstream discharge passage 146 c (see FIGS. 2 and 3) between the second control valve 400 and the crank chamber 140 in the discharge passage 146 and the suction chamber 141. The discharge hole 431a is opened and constitutes a part of the discharge passage 146 (specifically, the first discharge passage 146a). In the present embodiment, the discharge hole 431 a is formed in a peripheral wall 431 described later of the partition member 430, and the valve hole 103 d is formed in the valve plate 103.
The partition member 430 is a member that partitions the back pressure chamber 410 and the valve chamber 420, and includes, for example, a cylindrical peripheral wall 431 and a disk-shaped end wall 432. The peripheral wall 431 is provided so as to surround a later-described valve portion 442 of the spool 440. The end wall 432 is connected to one end side of the peripheral wall 431. The end wall 432 has an insertion hole 432a for inserting a shaft portion 443 described later of the spool 440. The first storage chamber 104g1 defined by the end wall 432 constitutes the back pressure chamber 410, and the cylindrical space inside the partition member 430 defined by the peripheral wall 431 and the end wall 432 constitutes the valve chamber 420.
In the present embodiment, the outer diameter of the peripheral wall 431 of the partition member 430 is set smaller than the inner diameter of the peripheral wall of the second storage chamber 104g2, and the peripheral wall 431 is slidably supported on the peripheral wall of the second storage chamber 104g2. In the present embodiment, the radial outer edge of the end wall 432 of the partition member 430 on the side of the one end surface 432b and the connection end surface between the second storage chamber 104g2 and the first storage chamber 104g1 (in other words, the large size of the storage hole 104g). A disc spring 450 as an urging means for urging the partition member 430 is disposed at a step portion between the diameter portion and the small diameter portion. In order to prevent the refrigerant flowing in from the first storage chamber 104g1 from flowing out into the suction chamber 141 through the gap outside the peripheral wall 431, an O-ring 460 is provided between the peripheral wall 431 and the second storage chamber 104g2. It is arranged.
In the present embodiment, the partition member 430 is energized toward the valve plate 103 by the disc spring 450 in a state of being accommodated in the second accommodation chamber 104g2, and thereby the end wall 432 of the peripheral wall 431 and Positioning is made in the second storage chamber 104g2 so that the end surface 431b on the opposite side contacts the valve plate 103 that is the wall surface on the opposite side of the back pressure chamber 410 in the valve chamber 420. In this state, in the partition member 430, the end surface 431b on the opposite side of the end wall 432 of the peripheral wall 431 protrudes toward the valve plate 103 from the protruding end surface 104j1 of the protrusion 104j.
The discharge hole 431a that opens to the valve chamber 420 penetrates the peripheral wall 431 at a plurality of locations spaced in the circumferential direction of the peripheral wall 431. The valve chamber 420 communicates with the suction chamber 141 through the discharge hole 431a. Specifically, a portion of the peripheral wall 431 on the end surface 431b side protrudes toward the valve plate 103 side from the protruding end surface 104j1 of the protrusion 104j so that the discharge hole 431a opens directly to the suction chamber 141. The discharge hole 431a is not limited to a hole, and may be formed as a notch.
A valve hole 103 d that opens into the valve chamber 420 is formed in the valve plate 103 that closes the open end of the partition member 430. A portion of the valve plate 103 around the valve hole 103d constitutes a valve seat 103f with which a valve portion 442 (to be described later) of the spool 440 contacts and separates. The valve chamber 420 communicates with the crank chamber 140 through the valve hole 103d, the communication hole of the suction valve forming plate 150, the communication hole of the cylinder gasket 152, the space 101d, and the communication path 101c. That is, in this embodiment, the upstream discharge passage 146c of the discharge passage 146 is configured by the communication hole of the suction valve forming plate 150, the communication hole of the cylinder gasket 152, the space 101d, and the communication passage 101c. The upstream discharge passage 146c communicates with the valve chamber 420 through the valve hole 103d.
The spool 440 passes through the pressure receiving portion 441 disposed in the back pressure chamber 410, the valve portion 442 disposed in the valve chamber 420 and contacting and separating from the valve seat 103f around the valve hole 103d, and the partition member 430. A shaft portion 443 that connects the extending pressure receiving portion 441 and the valve portion 442 is provided.
In the present embodiment, the pressure receiving portion 441 is accommodated in the first accommodating chamber 104g1 and is slidably supported by the first accommodating chamber 104g1. The valve portion 442 is accommodated in the valve chamber 420 and its one end surface 442a (see FIG. 8) contacts and separates from the valve seat 103f to open and close the valve hole 103d. The shaft portion 443 is formed with a smaller diameter than the pressure receiving portion 441 and the valve portion 442.
In the present embodiment, the shaft portion 443 is formed integrally with the valve portion 442. The spool 440 is configured by press-fitting the pressure receiving portion 441 into the shaft portion 443 in a state where the shaft portion 443 is inserted into the insertion hole 432a (see FIG. 8) of the partition member 430. The pressure receiving portion 441 contacts the end wall 432 of the partition member 430 when the valve portion 442 contacts the valve seat 103f. Specifically, when the one end surface 442a of the valve portion 442 contacts the valve seat 103f, at the same time, the one end surface 441a on the end wall 432 side (the partition member 430 side) of the pressure receiving portion 441 becomes the one end surface 432b of the end wall 432. The press-fit position of the pressure receiving portion 441 in the axial direction with respect to the valve portion 442 and the shaft portion 443 is adjusted so as to come into contact with each other.
Next, the operation of the spool 440 in the second control valve 400 will be described.
The second control valve 400 moves the spool 440 in accordance with the pressure in the back pressure chamber 410 (hereinafter referred to as back pressure) and the pressure in the upstream discharge passage 146c (that is, the crank chamber pressure Pc). The opening degree of the discharge passage 146 is controlled by bringing the portion 442 into and out of contact with the valve seat 103f. As described above, since the back pressure chamber 410 communicates with the intermediate supply passage 145b1 via the communication passage 104k, the pressure (back pressure) in the back pressure chamber 410 is equal to the pressure Pm of the intermediate supply passage 145b1. It is. Further, the pressure in the upstream discharge passage 146c is equal to the crank chamber pressure Pc. Therefore, the second control valve 400 operates the spool 440 according to the back pressure (pressure in the intermediate supply passage 145b1) Pm and the crank chamber pressure Pc.
One end surface of the spool 440 (the other end surface 441b of the pressure receiving portion 441) receives the back pressure Pm, and the other end surface of the spool 440 (the one end surface 442a of the valve portion 442) receives the crank chamber pressure Pc. It moves in the axial direction according to (Pm−Pc). If Pm−Pc> 0, the other end surface of the spool 440 comes into contact with the valve seat 103f, and the second control valve 400 closes the first discharge passage 146a. If Pm−Pc <0, the valve portion 442 contacts the end wall 432 of the partition member 430, and the second control valve 400 opens the first discharge passage 146a to the maximum. The pressure receiving area A1 of the spool 440 in the axial direction for receiving the back pressure Pm and the pressure receiving area A2 of the spool 440 for receiving the crank chamber pressure Pc are set to A1 = A2, for example, but in order to adjust the operation of the spool 440, A1> A2 Or it is good also as A1 <A2.
Specifically, the second control valve 400 is operated by the pressure in the valve closing direction that moves the spool 440 in the direction approaching the valve seat 103f by the pressure (back pressure Pm) acting on the pressure receiving portion 441. When the force in the valve opening direction that moves 440 away from the valve seat 103f is greater, the valve portion 442 comes into contact with the valve seat 103f, thereby blocking the communication between the valve hole 103d and the discharge hole 431a. When the opening degree of 146 is minimized and the force in the valve closing direction is smaller than the force in the valve opening direction, the valve portion 442 is separated from the valve seat 103f, so that the valve hole 103d and the discharge hole 431a communicate with each other. The opening of the discharge passage 146 is configured to be maximized.
Note that a minute gap is formed between the outermost peripheral surface 441c of the pressure receiving portion 441 that is slidably supported on the inner peripheral surface of the first storage chamber 104g1 and the inner peripheral surface of the first storage chamber 104g1. Therefore, in a state where the one end surface 441a of the pressure receiving portion 441 is slightly separated from the end wall 432, the refrigerant gas flowing into the back pressure chamber 410 (first housing chamber 104g1) from the communication path 104k is separated from the outermost peripheral surface 441c. The first chamber 104g1 flows into the valve chamber 420 via a gap between the inner circumferential surface and a gap between the outer circumferential surface of the shaft portion 443 and the inner circumferential surface of the insertion hole 432a. On the other hand, when the one end surface 442a of the valve portion 442 contacts the valve seat 103f, the one end surface 441a of the pressure receiving portion 441 is configured to contact the one end surface 432b of the end wall 432. The refrigerant flow from the back pressure chamber 410 to the valve chamber 420 via the gap between the outer peripheral surface and the inner peripheral surface of the insertion hole 432a is blocked. Therefore, the one end surface 441a of the pressure receiving portion 441 and the one end surface 432b of the end wall 432 constitute valve means.
In other words, in the present embodiment, the pressure receiving portion 441 contacts the end wall 432 facing the back pressure chamber 410 of the partition member 430 in a state where the valve portion 442 is in contact with the valve seat 103f, so that the shaft portion 443 The valve seat side of the valve portion 442 is such that communication between the back pressure chamber 410 and the valve chamber 420 through a gap between the insertion hole 432a formed in the partition member 430 for insertion and the shaft portion 443 is blocked. The distance between the one end surface 442a as the end surface and the one end surface 441a as the partition member side end surface of the pressure receiving portion 441 is set.
Note that the refrigerant gas in the intermediate supply passage 145b1 slightly flows into the suction chamber 141 through the back pressure relief passage 147 in a state where the valve portion 442 is in contact with the valve seat 103f. In the present embodiment, as shown in FIG. 5, the back pressure relief passage 147 opens into the suction chamber 141 via the throttle portion 147a formed in the discharge valve forming plate 151 and the communication hole of the head gasket 153. . Specifically, the back pressure relief passage 147 is provided between the connecting portion 104e1 and the suction chamber 141 in the intermediate supply passage 145b1 and between the cylinder block 101 and the cylinder head 104 (discharge valve forming plate 151, head gasket 153). ) To communicate with each other via a passage formed in (1). Thus, in the present embodiment, the back pressure relief passage 147 is formed so as to bypass the second control valve 400 and directly communicate between the connection portion 104e and the suction chamber 141 in the intermediate supply passage 145b1. Has been.
[Communication passage]
Next, the communication path 104k that communicates between the back pressure chamber 410 and the intermediate supply path 145b1 will be described in detail.
One end of the communication path 104k is connected to a connecting portion 104e provided in the middle of the intermediate supply path 145b1, and the other end of the communication path 104k is connected to the back pressure chamber 410. The communication passage side connection portion 104k1 (see FIG. 3) extending from at least the connection portion 104e of the communication passage 104k toward the back pressure chamber 410 side is connected to the first control valve 300 side from the connection portion 104e of the intermediate supply passage 145b1. It extends at an acute angle with respect to the communication passage 104d as the intermediate supply passage side connection portion extending toward the center. In other words, the communication passage 104k as the intermediate supply passage side connection portion is folded back in the intermediate supply passage 145b1 in the direction opposite to the main flow direction of the refrigerant flow flowing from the first control valve 300 toward the check valve 350. , Branched from the connecting portion 104e in the intermediate supply passage 145b1. The communication passage side connection portion 104k1 is a passage portion near the connection portion 104e in the communication passage 104k.
In the present embodiment, the communication path 104k extends at an acute angle over the entire length of the communication path with respect to the communication path 104d as the intermediate supply path side connection portion. In other words, the communication path 104k extends in one direction opposite to the flow direction of the main flow of the refrigerant flowing through the intermediate supply path 145b1 from the first control valve 300 toward the check valve 350 over the entire length of the communication path. ing. Therefore, the communication path 104k and the communication path 104d extending linearly in one direction form a V-shaped path.
In the present embodiment, the communication passage 104k is formed such that the back pressure chamber side opening end thereof opens to a lower part in the gravity direction on the inner wall surface of the back pressure chamber 410 when the compressor is installed.
In the present embodiment, the connecting portion 104e in the intermediate supply passage 145b1 is disposed so as to be located below the second control valve 400 in the gravitational direction when the compressor is installed. The connecting portion 104e is disposed closer to the valve plate 103 than the back pressure chamber 410. Therefore, the communication path 104k is folded back from the connecting portion 104e and extends obliquely upward to open to the back pressure chamber 410.
In the present embodiment, the first control valve 300 and the second control valve 400 are mutually in the cylinder head 104 with respect to the extending direction of the axis O of the drive shaft 110 (that is, the central axis extending direction of the compressor housing). It is arranged at a position shifted in the orthogonal direction. Specifically, the first control valve 300 is disposed vertically below the second control valve 400. Therefore, the connecting portion 104e, the communication passage 104d as the intermediate supply passage side connection portion, and the second control valve 400 are collectively arranged below the second control valve 400. Further, the second control valve 400 is arranged so that the central axis thereof substantially coincides with the axis O of the drive shaft 110. On the other hand, the first control valve 300 is arranged such that its central axis extends in the horizontal direction and its central axis is orthogonal to the axis O of the drive shaft 110.
[Operation of variable capacity compressor]
Here, the operation of the variable capacity compressor 100 will be described.
When the energization to the mold coil 314 of the first control valve 300 is cut off while the variable capacity compressor 100 is in operation, the first control valve 300 is opened to the maximum. As a result, the back pressure Pm is increased. Therefore, when the check valve 350 closes the supply passage 145 (at the maximum discharge capacity), the check valve 350 opens the supply passage 145 and at the same time the second control valve 400 The first discharge passage 146a is closed. Therefore, the discharge passage 146 is only the second discharge passage 146b, the pressure in the crank chamber 140 is increased, the inclination angle of the swash plate 111 is reduced, and the discharge capacity is maintained at the minimum state.
At substantially the same time, the discharge check valve 200 blocks the discharge passage, and the refrigerant gas discharged with the minimum discharge capacity does not flow to the external refrigerant circuit, but the discharge chamber 142, the supply passage 145, the crank chamber 140, and the second discharge. It circulates in an internal circulation path constituted by the passage 146b, the suction chamber 141, and the cylinder bore 101a. In this state, the refrigerant gas in the region of the supply passage 145 between the first control valve 300 and the check valve 350, that is, the intermediate supply passage 145b1, is released from the back pressure provided around the second control valve 400. It slightly flows out into the suction chamber 141 through the passage 147.
When energizing the mold coil 314 of the first control valve 300 from this state, the first control valve 300 is closed and the supply passage 145 is closed, and the refrigerant gas in the intermediate supply passage 145b1 passes through the back pressure relief passage 147. It flows out to the suction chamber 141. Then, the pressure (back pressure Pm) in the intermediate supply passage 145b1 decreases, the check valve 350 closes the supply passage 145, and the refrigerant gas is prevented from flowing back into the supply passage 145 upstream of the check valve 350. . At the same time, the second control valve 400 opens the first discharge passage 146a.
Accordingly, at this time, the discharge passage 146 is constituted by two of the first discharge passage 146a and the second discharge passage 146b.
The flow passage cross-sectional area in the second control valve 400 is set to be larger than the flow passage cross-sectional area of the groove 150a serving as a fixed throttle, and the refrigerant in the crank chamber 140 quickly flows out into the suction chamber 141. The pressure decreases, and the discharge capacity quickly increases from the minimum state to the maximum discharge capacity. As a result, the pressure in the discharge chamber 142 is rapidly increased, the discharge check valve 200 is opened, the refrigerant circulates through the external refrigerant circuit, and the air conditioner system is activated.
When the air conditioner system is activated and the pressure in the suction chamber 141 decreases and reaches a set pressure set by the current flowing through the mold coil 314, the first control valve 300 is opened. Thereby, when the back pressure Pm is increased, the check valve 350 opens the supply passage 145, and at the same time, the second control valve 400 closes the first discharge passage 146a. Accordingly, at this time, the discharge passage 146 is only the second discharge passage 146b. For this reason, the refrigerant in the crank chamber 140 is restricted from flowing into the suction chamber 141, and the pressure in the crank chamber 140 is easily increased. The opening of the first control valve 300 is adjusted so that the discharge capacity is variably controlled so that the pressure in the suction chamber 141 maintains the set pressure.
According to the variable displacement compressor according to the present embodiment, the check valve 350 is provided in the downstream supply passage 145 b between the first control valve 300 and the crank chamber 140 in the supply passage 145, and The back pressure chamber 410 communicates with the intermediate supply passage 145b1 between the first control valve 300 and the check valve 350 in the downstream supply passage 145b via the communication passage 104k. The communication passage side connection portion 104k1 extending from at least the connection portion 104e of the communication passage 104k toward the back pressure chamber 410 side is directed from the connection portion 104e of the intermediate supply passage 145b1 to the first control valve 300 side. It extends at an acute angle with respect to the communication passage 104d as an intermediate supply passage-side connecting portion that extends. Thereby, even if minute foreign matter flows through the intermediate supply passage 145b1 along with the refrigerant, all or most of the foreign matter becomes the main flow of the refrigerant flowing from the first control valve 300 to the check valve 350 side at the connecting portion 104e. Accordingly, foreign matter can be prevented or suppressed from entering the back pressure chamber 410. As a result, the spool 440 can be operated satisfactorily even if minute foreign matter is distributed along with the refrigerant. In this way, it is possible to provide the variable capacity compressor 100 that can prevent or suppress foreign matter from entering the second control valve 400.
In the present embodiment, the passage between the first control valve 300 and the crank chamber 140 in the supply passage 145 is called a downstream supply passage 145b, and the first control valve 300 and the check valve 350 in the downstream supply passage 145b An intermediate supply passage 145b1 between the two extends substantially linearly as shown in FIG. That is, a bent portion that is greatly bent is not formed in the middle of the intermediate supply passage 145b1. Thereby, in the intermediate supply passage 145b1, it is possible to form a main flow of the refrigerant flow in which the refrigerant linearly flows from the first control valve 300 toward the check valve 350 side. As a result, it is possible to more reliably prevent or suppress the entry of foreign matter into the back pressure chamber 410.
In the present embodiment, the communication path 104k extends at an acute angle over the entire length of the communication path with respect to the communication path 104d as the intermediate supply path side connection portion. As a result, a V-shaped passage is formed in cooperation with the connecting portion 104e and the communication passage 104d, and contamination of foreign matter from the connecting portion 104e to the back pressure chamber 410 can be prevented or suppressed more reliably. .
In the present embodiment, the communication passage 104k is formed such that the back pressure chamber side opening end thereof opens to a lower part in the gravity direction on the inner wall surface of the back pressure chamber 410 when the compressor is installed. Accordingly, when the first control valve 300 closes the supply passage 145 and the refrigerant in the intermediate supply passage 145b1 is discharged to the suction chamber 141 via the back pressure relief passage 147, the back pressure is temporarily set via the communication passage 104k. Even if foreign matter enters the chamber 410, the foreign matter is easily discharged to the connection portion 104e side by gravity through the communication path 104k.
In the present embodiment, the connecting portion 104e in the intermediate supply passage 145b1 is disposed so as to be located below the second control valve 400 in the gravitational direction when the compressor is installed. As a result, the connecting portion 104e is positioned below the back pressure chamber 410 of the second control valve 400 in the gravitational direction, so that it is difficult for foreign matter to enter the back pressure chamber 410 via the communication path 104k. Even if it enters, the foreign matter is easily discharged.
In the present embodiment, the first control valve 300 and the second control valve 400 are mutually in the cylinder head 104 with respect to the extending direction of the axis O of the drive shaft 110 (that is, the central axis extending direction of the compressor housing). It is arranged at a position shifted in the orthogonal direction. Specifically, the first control valve 300 is disposed vertically below the second control valve 400. As a result, the connection portion 104e, the communication passage 104d as the connection passage, and the second control valve 400 can be arranged under the second control valve 400, so that the longitudinal direction of the variable capacity compressor 100 (drive) The length in the extending direction of the axis O of the shaft 110 can be made shorter than before, and as a result, the compressor housing can be downsized.
In the present embodiment, the pressure receiving portion 441 contacts the end wall 432 facing the back pressure chamber 410 of the partition member 430 in a state where the valve portion 442 is in contact with the valve seat 103f, so that the shaft portion 443 is inserted. As a valve seat side end surface of the valve portion 442, the communication between the back pressure chamber 410 and the valve chamber 420 via the gap between the insertion hole 432 a formed in the partition member 430 and the shaft portion 443 is blocked. The distance between the one end surface 442a and the one end surface 441a as the partition member side end surface of the pressure receiving portion 441 is set. The back pressure relief passage 147 is formed so as to bypass the second control valve 400 and directly communicate between the connection portion 104e and the suction chamber 141 in the intermediate supply passage 145b1. Thereby, when the first control valve 300 is opened, there is no or substantially no steady flow of the refrigerant in the back pressure chamber 410, and it is possible to further suppress foreign matter from entering the back pressure chamber 410. it can.
In the present embodiment, the throttle portion 147 a of the back pressure relief passage 147 is formed on the discharge valve forming plate 151. Thereby, the back pressure relief passage 147 including the throttle portion 147a can be easily formed.
[Modification]
In the present embodiment, the back pressure chamber side opening end of the communication passage 104k opens to the inner wall surface of the back pressure chamber 410. However, the present invention is not limited to this, and the end of the first storage chamber 104g1 that constitutes the back pressure chamber 410. You may open to a wall surface (Namely, the end wall surface of the 1st storage chamber 104g1 facing the other end surface 441b of the pressure receiving part 441).
In the present embodiment, the open end of the partition member 430 is closed by the valve plate 103, and the valve plate 103 is used as the valve seat forming member of the second control valve 400. However, the present invention is not limited to this. As the valve seat forming member of the second control valve 400, a member interposed between the cylinder block 101 and the cylinder head 104, for example, the intake valve forming plate 150 or the discharge valve forming plate 151 may be used. Further, as shown in FIG. 9, the second control valve 400 may integrally include a dedicated valve seat forming member 148. Specifically, as shown in FIG. 9, the valve seat forming member 148 is press-fitted and fixed to, for example, the opening on the end surface 431 b side of the peripheral wall 431. If any one of the intake valve forming plate 150, the discharge valve forming plate 151, and the valve plate 103 is used as a valve seat forming member, it is not necessary to add a dedicated valve seat forming member, and flatness accuracy is also improved. Since it is good, it is suitable as a valve seat forming member.
In the present embodiment, the peripheral wall 431 of the partition member 430 is slidably supported by the peripheral wall of the second storage chamber 104g2, but is not limited thereto, and is press-fitted into the second storage chamber 104g2. The cylinder head 104 may be positioned. In this case, the O-ring 460 and the disc spring 450 are not necessary.
In the present embodiment, the back pressure relief passage 147 is formed so as to bypass the second control valve 400 and directly communicate between the connection portion 104e and the suction chamber 141 in the intermediate supply passage 145b1. However, it is not limited to this. The back pressure relief passage 147 may pass through the communication passage 104k that communicates between the back pressure chamber 410 and the intermediate supply passage 145b1. In the case of this modification, a communication hole for communicating the back pressure chamber 410 and the valve chamber 420 is formed in the end wall 432 of the partition member 430 of the second control valve 400. As a result, the communication hole formed in the end wall 432, the valve chamber 420, and the discharge between the communication passage 104k, the back pressure chamber 410, the outermost peripheral surface 441c of the pressure receiving portion 441 and the inner peripheral surface of the first storage chamber 104g1. A back pressure relief passage 147 that opens to the suction chamber 141 is formed via the hole 431a. In the case of this modification, the communication hole that connects the back pressure chamber 410 and the valve chamber 420 is set so that the flow passage cross-sectional area becomes the smallest in the back pressure relief passage 147, and the back pressure relief passage 147 is throttled. Part 147a is configured.
In the present embodiment, the discharge passage 146 is branched from the space 101d into the first discharge passage 146a and the second discharge passage 146b. The first discharge passage 146a is opened and closed by the second control valve 400, and the second discharge passage 146b is opened. Although the minimum opening degree of the discharge passage 146 is ensured when the second control valve 400 is closed by adopting a configuration in which the second control valve 400 is always opened, the present invention is not limited to this. For example, instead of the second discharge passage 146b, a through hole is formed in the peripheral wall of the valve portion 442, or a groove is provided in one end surface 442a of the valve portion 442, thereby ensuring the minimum opening of the discharge passage 146. You may comprise as follows.
In the present embodiment, the shaft portion 443 of the spool 440 is formed integrally with the valve portion 442, but is not limited thereto, and may be formed integrally with the pressure receiving portion 441.
In the present embodiment, the variable capacity compressor 100 is a swash plate type clutchless variable capacity compressor. However, the present invention is not limited thereto, and a variable capacity compressor equipped with an electromagnetic clutch, a variable capacity compressor driven by a motor, can do.
Although the contents of the present invention have been specifically described above with reference to the preferred embodiments, those skilled in the art can further adopt various modifications based on the basic technical idea and teachings of the present invention. It is self-explanatory.

100 ... Variable displacement compressor 101a ... Cylinder bore (compression unit)
103d ... Valve hole (valve hole of the second control valve)
103f ... Valve seat (the seat of the second control valve)
104 ... Cylinder head (housing member)
104d ... Communication passage (intermediate supply passage side connection part)
104e ... Connection part 104k ... Communication path 104k1 ... Communication path side connection part 136 ... Piston (compression part)
140 ... Crank chamber (control pressure chamber)
141 ... suction chamber 142 ... discharge chamber 145 ... supply passage 145b ... downstream supply passage 145b1 ... intermediate supply passage 146 ... discharge passage 146c ... upstream discharge passage 147 ... back pressure relief passage (throttle passage)
147a ... throttle portion 300 ... first control valve 350 ... check valve 400 ... second control valve 410 ... back pressure chamber 420 ... valve chamber 430 ... partition member 431a ... discharge hole 432 ... end wall (to the back pressure chamber of the partition member) Facing end wall)
432a ... Insertion hole 440 for inserting the shaft portion ... Spool 441 ... Pressure receiving portion 442 ... Valve portion 443 ... Shaft portion 442a ... One end surface (end surface on the valve seat side of the valve portion)
441a ... One end surface (the end surface on the partition member side of the pressure receiving portion)
O ... Axis of drive shaft (center axis of compressor housing)

Claims

A suction chamber into which the refrigerant is guided; a compression unit that sucks and compresses the refrigerant in the suction chamber; a discharge chamber into which the refrigerant compressed by the compression unit is discharged; and a control pressure chamber; In variable capacity compressors that change discharge capacity according to pressure,
A first control valve that is provided in a supply passage for supplying the refrigerant in the discharge chamber to the control pressure chamber, and controls the opening of the supply passage;
A check valve that is provided in a downstream supply passage between the first control valve and the control pressure chamber in the supply passage and prevents a reverse flow of refrigerant from the control pressure chamber toward the first control valve;
A second control valve that is provided in a discharge passage for discharging the refrigerant in the control pressure chamber to the suction chamber, and controls the opening degree of the discharge passage;
A throttle passage communicating the intermediate supply passage between the first control valve and the check valve in the downstream supply passage and the suction chamber and having a throttle portion;
With
The second control valve is
A back pressure chamber communicating with the intermediate supply passage;
A valve hole communicating with the upstream discharge passage between the second control valve and the control pressure chamber in the discharge passage and a discharge hole communicating with the suction chamber are opened, and constitutes a part of the discharge passage A valve chamber,
A partition member that partitions the back pressure chamber and the valve chamber;
A pressure receiving portion disposed in the back pressure chamber, a valve portion disposed in the valve chamber and contacting and separating from a valve seat around the valve hole, and the pressure receiving portion and the valve portion extending through the partition member; A spool having a shaft portion for connecting,
And moving the spool in accordance with the pressure in the back pressure chamber and the pressure in the upstream discharge passage to bring the valve portion into contact with and away from the valve seat, thereby opening the opening of the discharge passage. Configured to control,
The back pressure chamber communicates with the intermediate supply passage through a communication passage connected to the back pressure chamber and the intermediate supply passage.
One end of the communication path is connected to a connection portion provided in the middle of the intermediate supply path,
The communication passage side connection portion extending from at least the connection portion of the communication passage toward the back pressure chamber side is an intermediate supply extending from the connection portion of the intermediate supply passage toward the first control valve side. A variable capacity compressor extending at an acute angle with respect to the passage-side connecting portion.
The variable capacity compressor according to claim 1, wherein the communication path extends at an acute angle with respect to the connection portion on the intermediate supply path side over the entire length of the communication path.
The suction chamber and the discharge chamber are formed in a housing member constituting one end portion of the compressor housing,
The said 1st control valve and the said 2nd control valve are arrange | positioned in the position which mutually shifted in the direction orthogonal to the center axis | shaft extending | stretching direction of the said compressor housing in the said housing member. The variable capacity compressor described.
4. The communication passage is formed so that an opening end of the back pressure chamber side opens to a lower portion in the gravity direction on the inner wall surface of the back pressure chamber when the compressor is installed. The variable capacity compressor described in 1.
The variable connection according to any one of claims 1 to 4, wherein the connection portion in the intermediate supply passage is arranged to be located below the second control valve in the gravity direction in a compressor installed state. Capacity compressor.
In the state where the valve portion is in contact with the valve seat, the pressure receiving portion is formed on the partition member for insertion of the shaft portion by contacting the end wall facing the back pressure chamber of the partition member. The valve seat side end surface of the valve portion and the partition member side end surface of the pressure receiving portion so that communication between the back pressure chamber and the valve chamber via a gap between the insertion hole and the shaft portion is blocked. Set the distance between
6. The throttle passage according to claim 1, wherein the throttle passage is formed so as to bypass the second control valve and directly communicate between the connection portion and the suction chamber in the intermediate supply passage. The variable capacity compressor as described in any one.