JP2020133548A - Variable displacement compressor - Google Patents

Abstract

To simplify a structure of a cylinder block in a variable displacement compressor.SOLUTION: A first housing hole 401 which houses a first valve body 251 of a check valve 250 and a second housing hole 403 which houses a second valve body 351 of a second control valve 350 are formed within a valve housing 450. The first housing hole 401 and the second housing hole 403 are formed in the valve housing 450 which is a member different from a cylinder block 101.SELECTED DRAWING: Figure 2

Description

The present invention relates to a variable displacement compressor, and more particularly to a variable displacement compressor in which the discharge capacity is controlled by adjusting the pressure in the crank chamber.

This type of variable capacitance compressor is described in Patent Document 1. The variable displacement compressor described in Patent Document 1 includes a first control valve 33 for adjusting the passage cross-sectional area of a supply passage for supplying a refrigerant from a discharge pressure region to a control pressure chamber (crank chamber), and an suction pressure from the crank chamber. A second control valve 34 for adjusting the passage cross-sectional area of the discharge passage for discharging the refrigerant to the region, and a check valve 35 arranged between the first control valve and the crank chamber in the supply passage. , Is equipped. The second control valve 34 is configured to shift from the closed state to the open state when the first control valve 33 shifts from the open state to the closed state.

Japanese Unexamined Patent Publication No. 2011-185138

In the variable displacement compressor described in Patent Document 1, the valve body 55 of the second control valve 34 is housed in a hole (valve storage chamber 53) recessed in the rear end surface of the cylinder block 11 and is not checked. The valve 35 is housed in a hole (accommodation hole 63) recessed in the rear end surface of the cylinder block 11 separately from the valve accommodating chamber 53 for the second control valve 34. As described above, the holes (valve accommodating chamber 53, accommodating hole 63) for accommodating the second control valve 34 (valve body 55) and the check valve 35 are separately formed in the cylinder block 11, and the cylinder block. It is necessary to perform complicated processing on the 11 itself, and the processing time of the cylinder block 11 becomes longer accordingly. For example, the processing of the cylinder block may become a bottleneck process in the manufacturing process.

Therefore, an object of the present invention is to provide a variable displacement compressor having a structure capable of providing a check valve and a second control valve without performing complicated processing on the cylinder block.

According to one aspect of the present invention, the housing, the suction chamber, the compression unit, the discharge chamber, the control pressure chamber, the first control valve, the check valve, the second control valve, and the back pressure relief passage. , And a variable capacitance compressor in which the discharge capacitance changes according to the pressure in the control pressure chamber is provided. The housing includes a cylinder block, a front housing provided on the front end surface side of the cylinder block, and a cylinder head provided on the rear end surface side of the cylinder block. The suction chamber is provided in the cylinder head, and a refrigerant is guided from the outside. The compression unit is provided in the cylinder block and sucks and compresses the refrigerant in the suction chamber. The discharge chamber is provided in the cylinder head and discharges the refrigerant compressed by the compression unit. The control pressure chamber is provided in the front housing. 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 degree of the supply passage. The check valve is provided on the control pressure chamber side of the first control valve in the supply passage, and blocks the flow of the refrigerant from the control pressure chamber to the first control valve. 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 between the valve-to-valve region, which is a region between the first control valve and the check valve in the supply passage, and the suction chamber, and has a throttle portion. The check valve has a first accommodating hole and a first valve body. The first accommodating hole forms a part of the supply passage. The first valve body is housed in the first storage hole and is configured to move according to the differential pressure in the front-rear direction to block the flow of the refrigerant from the control pressure chamber to the first control valve. .. The second control valve has a second accommodating hole and a second valve body. The second accommodating hole has a valve chamber and a back pressure chamber. The valve chamber communicates with the control pressure chamber through the valve hole and also communicates with the suction chamber through the discharge hole to form a part of the discharge passage together with the valve hole and the discharge hole. The back pressure chamber communicates with the intervalve region. The second valve body has a valve portion arranged in the valve chamber and a pressure receiving portion arranged in the back pressure chamber, and moves according to a front-rear differential pressure to open and close the valve hole. It is composed. The variable displacement compressor includes a valve housing in which the first accommodating hole and the second accommodating hole are formed, and a valve unit having the first valve body and the second valve body. The valve unit is a recess recessed in the rear end surface of the cylinder block, and is housed in the recess that communicates with the control pressure chamber through a communication hole opened in the bottom surface of the recess.

In the variable displacement compressor, the first accommodating hole accommodating the first valve body of the check valve and the second accommodating hole accommodating the second valve body of the second control valve are the valve housing. It is formed inside. That is, the first accommodating hole and the second accommodating hole are formed in the valve housing which is a member different from the cylinder block, and the cylinder block includes the valve housing and the first valve body. It suffices to form one recess that accommodates the entire valve unit including the second valve body. Therefore, it is not necessary to perform complicated processing on the cylinder block itself to form the first accommodating hole and the second accommodating hole.

In this way, it is possible to provide a variable displacement compressor having a structure capable of providing a check valve and a second control valve without performing complicated processing on the cylinder block.

It is sectional drawing of the variable capacity compressor which concerns on embodiment of this invention. It is an enlarged sectional view of the main part of the variable capacitance compressor. It is an enlarged sectional view of the main part of the variable capacity compressor of the same part as FIG. 2, and shows the state different from FIG. It is an enlarged sectional view of the main part for demonstrating the modification of the 2nd control valve of the variable capacitance compressor. It is an enlarged sectional view of the main part for demonstrating the modification of the check valve of the variable capacity compressor. It is an enlarged sectional view of the main part for demonstrating the modification of the supply passage of the variable capacity compressor.

[First Embodiment]
Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a cross-sectional view of a variable displacement compressor 100 according to an embodiment of the present invention. FIG. 2 is an enlarged cross-sectional view of a main part of the variable displacement compressor 100, and FIG. 3 is a cross-sectional view of a main part of the same portion as in FIG. 2, showing a state different from that in FIG. The variable displacement compressor 100 is configured as a clutchless compressor mainly applied to an air conditioner system (air conditioner system) for a vehicle. In this embodiment, the case of a swash plate type variable displacement compressor with a variable discharge capacity will be described as an example. The upper side in FIG. 1 is the upper side in the gravity direction when the compressor is installed, and the lower side in FIG. 1 is the lower side in the gravity direction. Similarly, in FIGS. 2 to 6 described later, the vertical relationship in the direction of gravity is shown.

As shown in FIG. 1, the variable displacement compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101a arranged in an annular shape, and a front housing provided on the front end surface side (left side in FIG. 1) of the cylinder block 101. It includes 102 and a cylinder head 104 provided on the rear end surface side (right side in FIG. 1) of the cylinder block 101 via a valve plate 103 or the like. A crank chamber 140 is provided in the front housing 102, and a drive shaft 110 is provided across the inside of the crank chamber 140. In the present embodiment, the crank chamber 140 corresponds to the "control pressure chamber" according to the present invention.

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 connected, and a plurality of throughs are connected. It is fastened by bolts 105 to form the housing of the variable displacement compressor 100. That is, the cylinder gasket 152, the suction valve forming plate 150, the valve plate 103, the discharge valve forming plate 151, and the head gasket 153 are sandwiched between the cylinder block 101 and the cylinder head 104. In this embodiment, the cylinder gasket 152, the suction valve forming plate 150, the valve plate 103, the discharge valve forming plate 151 and the head gasket 153 correspond to the "intervening member" according to the present invention.

A swash plate 111 is arranged 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 the angle (tilt angle of the swash plate 111) of the drive shaft 110 of the swash plate 111 with respect to the axis O can be changed. ing.

The link mechanism 120 rotates with respect to the first arm 112a projecting from the rotor 112, the second arm 111a projecting from the swash plate 111, and one end side with respect to the first arm 112a via the first connecting pin 122. Includes a link arm 121 that is movably connected and whose other end is rotatably connected to the second arm 111a via a second connecting pin 123.

The through hole 111b of the swash plate 111 through which the drive shaft 110 is inserted is formed so that the swash plate 111 can tilt within the range of the maximum tilt angle and the minimum tilt angle. The through hole 111b is formed with a minimum tilt angle regulating portion that comes into contact with the drive shaft 110. When the tilt angle of the swash plate 111 when the swash plate 111 is orthogonal to the axis O of the drive shaft 110 is set to 0 °, the minimum tilt angle restricting portion of the through hole 111b is such that the tilt angle of the swash plate 111 is approximately 0 °. It is formed so as to come into contact with the drive shaft 110 and restrict further tilting of the swash plate 111. When the tilt angle of the swash plate 111 reaches the maximum tilt angle, the swash plate 111 comes into contact with the rotor 112 and further tilting is restricted.

The drive shaft 110 includes a tilt angle reducing spring 114 that urges the swash plate 111 in a direction that reduces the tilt angle of the swash plate 111, and a tilt angle increasing spring 115 that urges the swash plate 111 in a direction that increases the tilt angle of the swash plate 111. And are installed. The tilt angle reducing spring 114 is arranged between the swash plate 111 and the rotor 112, and the tilt angle increasing spring 115 is mounted between the swash plate 111 and the spring support member 116 fixed to the drive shaft 110.

Here, when the tilt angle of the swash plate 111 is the minimum tilt angle, the urging force of the tilt angle increasing spring 115 is set to be larger than the urging force of the tilt angle decreasing spring 114, and the drive shaft 110 is rotating. When not, the swash plate 111 is positioned at a tilt angle in which the urging force of the tilt angle decreasing spring 114 and the urging force of the tilt angle increasing spring 115 are balanced.

One end (the left end in FIG. 1) of the drive shaft 110 penetrates the inside of the boss portion 102a projecting to the outside of the front housing 102 and extends to the outside of the front housing 102. A power transmission device (not shown) is connected to the one end of the drive shaft 110. A shaft sealing device 130 is provided between the drive shaft 110 and the boss portion 102a, and the inside of the crank chamber 140 is shielded from the external space by the shaft sealing device 130.

The connecting body including the drive shaft 110 and the rotor 112 fixed to the drive shaft 110 is supported by bearings 131 and 132 in the radial direction, and is supported by thrust bearings 133 and thrust plates 134 in the thrust direction. The drive shaft 110 is configured to rotate in synchronization with the rotation of the power transmission device by transmitting the power from the external drive source to the power transmission device. The other end of the drive shaft 110, that is, the gap between the end on the thrust plate 134 side and the thrust plate 134 is adjusted to a predetermined gap by the adjusting screw 135.

A piston 136 is arranged in each cylinder bore 101a. An outer peripheral portion of the swash plate 111 and its vicinity are accommodated in an inner space formed in a protruding portion protruding into the crank chamber 140 of the piston 136, and the swash plate 111 is accommodated via a pair of shoes 137. It is configured to work with. Then, the piston 136 reciprocates in the cylinder bore 101a due to the rotation of the swash plate 111 accompanying the rotation of the drive shaft 110.

The cylinder head 104 is divided into a suction chamber 141 arranged at the center and a discharge chamber 142 that circularly surrounds the suction chamber 141. That is, the suction chamber 141 and the discharge chamber 142 are provided in the cylinder head 104. The suction chamber 141 and the cylinder bore 101a communicate with each other through 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 through a discharge valve (not shown) formed in the discharge valve forming plate 151 and a communication hole 103b provided in the valve plate 103.

The cylinder head 104 is formed with a suction passage including a suction port 106 and a suction passage 107. The suction passage extends linearly from the radial outside of the cylinder head 104 so as to cross a part of the discharge chamber 142. The suction chamber 141 is connected to the low pressure side of the refrigerant circuit of the air conditioner system via the suction passage, and the suction chamber 141 is connected to the refrigerant on the low pressure side of the refrigerant circuit of the air conditioner system (that is, the refrigerant before compression from the outside). ) Is derived. The refrigerant in the suction chamber 141 is sucked into the corresponding cylinder bore 101a by the reciprocating motion of each piston 136 and compressed. This compressed refrigerant is discharged to the discharge chamber 142. That is, the reciprocating motion of the piston 136 accompanying the rotation of the drive shaft 110 compresses the refrigerant sucked from the suction chamber 141 into the cylinder bore 101a and discharges it to the discharge chamber 142. A cylinder bore 101a and a piston 136 provided in the cylinder block 101 constitute a compression unit that sucks and compresses the refrigerant in the suction chamber 141.

A muffler is provided on the upper part of the cylinder block 101. The muffler is formed by fastening the lid member 109a on which the discharge port 108 is formed and the muffler forming wall 109b formed on the upper portion of the cylinder block 101 with bolts via a seal member (not shown).

The muffler space 143 surrounded by the lid member 109a and the muffler forming wall 109b communicates with the discharge chamber 142 via the communication passage 144. In the muffler space 143, a discharge check valve 200 is arranged so as to cover the opening end of the communication passage 144 on the muffler space 143 side. The discharge check valve 200 operates in response to the pressure difference between the communication passage 144 (upstream side) and the muffler space 143 (downstream side), and when the pressure difference is smaller than a predetermined value, the communication passage 144 is closed. When the pressure difference is larger than a predetermined value, the communication passage 144 is opened.

The communication passage 144, the discharge check valve 200, the muffler space 143, and the discharge port 108 form a discharge passage of the variable displacement compressor 100, and the discharge chamber 142 is a high pressure of the refrigerant circuit of the air conditioner system via the discharge passage. It is connected to the side. The refrigerant discharged into the discharge chamber 142 is guided to the high pressure side of the refrigerant circuit of the air conditioner system through the discharge passage. Further, the discharge check valve 200 prevents the backflow of the refrigerant (refrigerant gas) from the high pressure side of the refrigerant circuit of the air conditioner system toward the discharge chamber 142.

The cylinder block 101 and the cylinder head 104 are formed with a supply passage 145 for supplying the refrigerant in the discharge chamber 142 to the crank chamber 140. A first control valve 300 is provided in the supply passage 145. The first control valve 300 controls (adjusts) the opening degree (passage cross section) of the supply passage 145, thereby controlling the supply amount of the refrigerant (discharged refrigerant) in the discharge chamber 142 to the crank chamber 140. It is configured in.

The first control valve 300 includes a valve body unit and a drive unit (solenoid) that opens and closes the valve body unit, and is introduced via a communication passage 104a (see FIG. 1) formed in the cylinder head 104. It is configured to control the opening degree of the supply passage 145 in response to the pressure of the suction chamber 141 and the electromagnetic force generated by the current flowing through the solenoid in response to an external signal. Specifically, the coil of the drive unit is connected to a control device (not shown) provided outside the variable capacitance compressor 100 via a signal line or the like. The drive unit generates an electromagnetic force F (I) when a control current I is supplied from the control device to the coil. When the drive unit generates an electromagnetic force F (I), the valve body of the valve body unit moves in the valve closing direction. Further, in the valve body, when the pressure in the suction chamber 141 becomes higher than the set pressure set by the control current I, the opening degree (passage cross-sectional area) of the valve hole (that is, the supply passage 145) is increased in order to increase the discharge capacity. ) Is reduced to reduce the pressure in the crank chamber 140, and when the pressure in the suction chamber 141 is lower than the set pressure, the opening degree of the valve hole (that is, the supply passage 145) is increased in order to reduce the discharge capacity. The pressure in the crank chamber 140 is increased. That is, the first control valve 300 autonomously controls the opening degree of the supply passage 145 so that the pressure in the suction chamber 141 approaches the set pressure. Since the electromagnetic force of the drive unit acts on the valve body in the valve closing direction, the force in the direction of reducing the opening degree of the supply passage 145 (that is, the valve closing direction) increases as the energization amount of the coil increases. Then, the set pressure changes in the direction of decrease. The control device controls energization of the drive unit to the coil by pulse width modulation (PWM control) at a predetermined frequency in the range of, for example, 400 Hz to 500 Hz, so that the current value flowing through the coil becomes a desired value. Change the pulse width (duty ratio). The supply passage 145 will be described in detail later.

A check valve 250 is provided on the crank chamber 140 side (that is, downstream side) of the first control valve 300 in the supply passage 145 to block the flow of the refrigerant from the crank chamber 140 to the first control valve 300. The check valve 250 is configured to open and close the supply passage 145 in conjunction with the opening and closing of the first control valve 300. Specifically, in the present embodiment, the check valve 250 opens when the first control valve 300 opens and opens the supply passage 145, opens the supply passage 145, and opens the first control valve 300. Is configured to close the valve and close the supply passage 145 when the valve closes and closes the supply passage 145. The intervalve region 145a, which is the region between the first control valve 300 and the check valve 250 in the supply passage 145, communicates with the suction chamber 141 via the back pressure relief passage 146 having the throttle portion 146a. That is, the back pressure relief passage 146 is a passage that communicates the intervalve region 145a and the suction chamber 141 and has a throttle portion 146a. The check valve 250 and the back pressure relief passage 146 will be described in detail later.

Further, a discharge passage 147 for discharging the refrigerant in the crank chamber 140 to the suction chamber 141 is provided. A second control valve 350 is provided in the discharge passage 147. The second control valve 350 is configured to control (adjust) the opening degree (passage cross section) of the discharge passage 147. The discharge passage 147 has a throttle portion 147a. The second control valve 350 is configured to secure the minimum passage cross section defined by the throttle portion 147a in the closed state. The discharge passage 147 and the second control valve 350 will be described in detail later.

When the first control valve 300 and the check valve 250 are closed, the second control valve 350 opens to open the discharge passage 147. Therefore, the refrigerant in the crank chamber 140 quickly flows out to the suction chamber 141, and the pressure in the crank chamber 140 becomes equal to the pressure in the suction chamber 141. In this case, the tilt angle of the swash plate 111 is maximized, and the stroke (discharge capacity) of the piston 136 is maximized.

On the other hand, when the first control valve 300 and the check valve 250 are open, the second control valve 350 closes the discharge passage 147, and at this time, the passage cross section of the discharge passage 147 is defined by the throttle portion 147a. It is narrowed down to the minimum passage cross section. Therefore, the outflow of the refrigerant in the crank chamber 140 to the suction chamber 141 is restricted, and the pressure in the crank chamber 140 tends to increase. Therefore, the pressure of the crank chamber 140 rises according to the opening degree of the supply passage 145 by the first control valve 300, and the tilt angle of the swash plate 111 decreases from the maximum, whereby the stroke (discharge capacity) of the piston 136 is variable. Be controlled.

In this way, the variable displacement compressor 100 supplies the refrigerant in the discharge chamber 142 (discharge pressure region) to the crank chamber 140 through the supply passage 145, and sucks the refrigerant in the crank chamber 140 through the discharge passage 147. The pressure in the crank chamber 140 is adjusted by flowing out to the chamber 141 (suction pressure region), and the discharge capacity is controlled by the pressure adjustment in the crank chamber 140. That is, the discharge capacity changes according to the pressure of the crank chamber 140. Lubricating oil is sealed inside the variable displacement compressor 100, and the inside of the variable displacement compressor 100 is caused by the stirring of the oil accompanying the rotation of the drive shaft 110 and the movement of the oil accompanying the movement of the refrigerant gas. Is lubricated.

In the following, the supply passage 145, the check valve 250, the back pressure relief passage 146, the discharge passage 147, and the second control valve 350 will be described in detail.

"Supply passage 145"
When the first control valve 300 is opened, the discharge chamber 142 and the crank chamber 140 communicate with each other through the supply passage 145, and the refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the supply passage 145. In the present embodiment, as shown in FIGS. 1 to 3, the supply passage 145 includes a communication passage 104b (see FIG. 1) formed in the cylinder head 104, a passage in the first control valve 300 (not shown), and The communication passage 104c formed in the cylinder head 104, the through hole 103c penetrating the intervening member (cylinder gasket 152, suction valve forming plate 150, valve plate 103, discharge valve forming plate 151 and head gasket 153), and non-return It is composed of a first accommodating hole 401, which will be described later, which constitutes the valve 250, and a cylindrical passage pipe 148 that is inserted into the communication hole 101b formed in the cylinder block 101. In the present embodiment, the valve-to-valve region 145a, which is the region between the first control valve 300 and the check valve 250 in the supply passage 145, is composed of a region including the communication passage 104c and the through hole 103c.

"Check valve 250"
As described above, FIG. 2 is an enlarged cross-sectional view of a main part of the variable displacement compressor 100, in which the check valve 250 opens the supply passage 145 and the second control valve 350 operates in the valve closing direction to reduce the throttle portion 147a. Indicates a state in which the cross-sectional area of the discharge passage 147 is minimized. FIG. 3 shows a state in which the check valve 250 closes the supply passage 145 and the second control valve 350 is open.

In the present embodiment, the check valve 250 is housed in the first accommodating hole 401 forming a part of the supply passage 145, the suction valve forming plate 150 as a valve seat forming member, and the first accommodating hole 401 before and after. Includes a first valve body 251 configured to move according to the differential pressure and block the flow of refrigerant from the crank chamber 140 to the first control valve 300.

The first accommodating hole 401 is formed in the valve housing 450 and extends parallel to the axis O of the drive shaft 110. The first accommodating hole 401 is formed in a stepped circular hole shape that opens on the rear end surface side of the cylinder block 101. The first accommodating hole 401 has a large-diameter hole portion 401a arranged on the opening side, and a small-diameter hole portion 401b connected to the hole bottom side of the large-diameter hole portion 401a and having a smaller diameter than the large-diameter hole portion 401a. ..

Here, the valve housing 450 is housed in a recess 101c recessed in the rear end surface of the cylinder block 101. The valve housing 450 is formed, for example, in a columnar shape having a circular cross section, and the recess 101c is formed as a circular hole having an inner diameter slightly larger than the outer diameter of the valve housing 450. The first accommodating hole 401 extends from one end surface 451 of the valve housing 450 facing the bottom surface 101c1 of the recess toward the other end surface 452 of the valve housing 450.

One end of the communication hole 101b is opened in the recess bottom surface 101c1 which is the hole bottom of the recess 101c, and the other end of the communication hole 101b is open in the crank chamber 140.

In the present embodiment, the cylindrical passage pipe 148 is inserted into the communication hole 101b opened in the recess bottom surface 101c1. One end of the passage pipe 148 protrudes into the crank chamber 140, and the other end of the passage pipe 148 is connected to the opening of the small diameter hole 401b of the first accommodating hole 401 opposite to the large diameter hole 401a. .. As a result, the first accommodating hole 401 communicates with the crank chamber 140 via the passage pipe 148 and the communication hole 101b, and forms a part of the supply passage 145. Further, the passage pipe 148 serves as a positioning member for determining a position in the radial direction (that is, a direction orthogonal to the moving direction of the first valve body 251 and the second valve body 351 described later) in the recess 101c of the valve housing 450. It also has a function.

Further, a through hole 101d for supporting the drive shaft 110 is opened in the radial center portion of the recess bottom surface 101c1. One end of the through hole 101d opens to the crank chamber 140, and the other end of the through hole 101d opens to the recess bottom surface 101c1. A radial bearing 132 is mounted on one end side of the through hole 101d, a female screw is formed on the other end side of the through hole 101d, and an adjusting screw 135 is screwed into the female screw. The recess 101c is formed from the through hole 135a penetrating the adjusting screw 135 and the thrust plate 134, and the in-axis passage 147b formed in the other end of the drive shaft 110 (that is, the end on the thrust plate 134 side). It communicates with the crank chamber 140 through the communication hole 101e. That is, the recess 101c communicates with the crank chamber 140 through the communication hole 101e opened in the recess bottom surface 101c1. The in-shaft passage 147b is connected to a first passage 147b1 that extends radially from the outer peripheral surface of the drive shaft 110 exposed in the crank chamber 140 and penetrates the drive shaft 110, and one end is connected to the first passage 147b1 in the drive shaft 110. The other end is a second passage 147b2 extending along the axis O to the end surface of the drive shaft 110 on the thrust plate 134 side.

In the present embodiment, the valve housing 450 is provided between one end surface 451 and the concave bottom surface 101c1 and between the inner peripheral surface 101c2 of the concave portion 101c and the outer surface (outer peripheral surface) 453 of the valve housing 450 facing the inner peripheral surface 101c2. They are arranged so as to have a gap between them. An airtight member 500 is provided between the recess 101c and the valve housing 450. The airtight member 500 is formed of, for example, an annular O-ring, and is attached to a groove portion 453a formed on the entire circumference of the outer surface 453 of the valve housing 450 on the one end surface 451 side.

Further, in the present embodiment, an urging member 600 for urging the valve housing 450 toward the opening side of the recess 101c is provided between one end surface 451 of the valve housing 450 and the recess bottom surface 101c1. The urging member 600 is composed of, for example, a compression coil spring, and is provided at a plurality of positions separated in the circumferential direction on the outer edge portion of one end surface 451 of the valve housing 450.

The suction valve forming plate 150 closes (covers) the opening of the first accommodating hole 401 (specifically, the large-diameter hole 401a), and at the same time, the valve seat portion 150a to which the first valve body 251 separates and contacts, and the first valve. It has a first valve hole 150b that is opened and closed by the detachment of the body 251. The first valve hole 150b constitutes an open end of a through hole 103c that penetrates the intervening member (cylinder gasket 152, suction valve forming plate 150, valve plate 103, discharge valve forming plate 151 and head gasket 153).

The first valve body 251 has a stepped cylindrical side wall 251a composed of a large diameter portion 251a1 and a small diameter portion 251a2 having an outer diameter smaller than that of the large diameter portion 251a1, and an opening end of the side wall 251a on the large diameter portion 251a1 side. It has an end wall 251b that closes the wall. In other words, the first valve body 251 is formed in a bottomed stepped cylindrical shape. Further, the first valve body 251 has an internal passage 251c composed of an internal space 251c1 of the side wall 251a and a through hole 251c2 formed in a large diameter portion 251a1 of the side wall 251a. The first valve body 251 is preferably formed of a resin material, but may be formed of another material such as a metal material.

In the first valve body 251, the small diameter portion 251a2 is slidably supported by the small diameter hole portion 401b of the first accommodating hole 401. Further, the space between the large diameter portion 251a1 of the first valve body 251 and the large diameter hole portion 401a of the first accommodating hole 401 forms an annular passage communicating with the internal passage 251c of the first valve body 251. There is.

In the first accommodating hole 401, the first valve body 251 can move in a direction parallel to the axis of the drive shaft 110. When the end wall 251b of the first valve body 251 comes into contact with the valve seat portion 150a of the suction valve forming plate 150, the movement of one of the first valve bodies 251 is restricted, and the small diameter of the large diameter portion 251a1 of the first valve body 251 is restricted. The movement of the other of the first valve body 251 is restricted by the end surface on the side of the portion 251a2 coming into contact with the stepped portion between the small diameter hole portion 401b and the large diameter hole portion 401a of the first accommodating hole 401. Then, when the end wall 251b of the first valve body 251 comes into contact with the valve seat portion 150a, the first valve hole 150b is closed, and when the end wall 251b of the first valve body 251 separates from the valve seat portion 150a, the first valve hole 150b is closed. 150b is released.

The space in the large-diameter hole portion 401a of the first accommodating hole 401 communicates with the valve-to-valve region 145a including the through hole 103c including the first valve hole 150b and the communication passage 104c. Further, as described above, one end of the passage pipe 148 is connected to the small diameter hole portion 401b of the first accommodating hole 401, and the other end of the passage pipe 148 is open in the crank chamber 140. That is, the space in the small-diameter hole portion 401b of the first accommodating hole 401 communicates with the crank chamber 140 via the passage pipe 148.

The pressure Pc'of the supply passage 145 on the upstream side of the check valve 250 and the pressure Pc of the crank chamber 140 on the downstream side of the check valve 250 act on the first valve body 251. Therefore, the first valve body 251 moves in the axial direction of the drive shaft 110 in response to the differential pressure before and after the first valve body 251, that is, the difference (Pc'-Pc) between the upstream side pressure and the downstream side pressure. ..

Further, as described above, the valve-to-valve region 145a between the first control valve 300 and the check valve 250 in the supply passage 145 communicates with the suction chamber 141 via the back pressure relief passage 146 having the throttle portion 146a. ing.

When the first control valve 300 is opened and the supply passage 145 is opened, the refrigerant gas in the discharge chamber 142 reaches the first valve hole 150b of the check valve 250 via the intervalve region 145a in the supply passage 145. .. Therefore, the pressure Pc'on the upstream side of the first valve body 251 rises (Pc'-Pc)> 0, and as shown in FIG. 2, the end wall 251b of the first valve body 251 is the valve seat portion. Separated from 150a, the end surface of the large-diameter portion 251a1 of the first valve body 251 on the small-diameter portion 251a2 side is in contact with the stepped portion of the first accommodating hole 401. Therefore, as shown by the arrows in the figure, the refrigerant gas in the discharge chamber 142 has the large diameter hole 401a, the internal passage 251c, the small diameter hole 401b, and the passage pipe 148 from the first valve hole 150b to the first accommodation hole 401. It is supplied to the crank chamber 140 via.

When the first control valve 300 closes and the supply passage 145 is closed, the refrigerant gas in the discharge chamber 142 is not supplied to the downstream side of the first control valve 300 in the supply passage 145, and the intervalve region 145a Refrigerant gas flows out to the suction chamber 141 via the back pressure relief passage 146. Therefore, (Pc'-Pc) <0, and further, due to the dynamic pressure of the refrigerant flowing back through the internal passage 251c, as shown in FIG. 3, the small diameter portion 251a2 side of the large diameter portion 251a1 of the first valve body 251. The end surface of the first valve body 251 is separated from the stepped portion of the first accommodating hole 401, and the end wall 251b of the first valve body 251 abuts on the valve seat portion 150a to close the first valve hole 150b. As a result, the flow of the refrigerant from the crank chamber 140 to the first control valve 300 is blocked.

As described above, the check valve 250 allows the flow of the refrigerant from the discharge chamber 142 to the crank chamber 140 when the first control valve 300 opens and the supply passage 145 opens, and the first control valve 300 closes. When the supply passage 145 is closed by a valve, the flow of the refrigerant from the crank chamber 140 to the first control valve 300 is blocked. The check valve 250 may have an urging member such as a compression coil spring that urges the first valve body 251 toward the valve seat portion 150a. Further, here, the suction valve forming plate 150 has a valve seat portion 150a and a first valve hole 150b, but the present invention is not limited to this, and for example, the valve plate 103 has a valve seat portion 150a and a first valve hole 150b. May have.

"Back pressure relief passage 146"
One end of the back pressure relief passage 146 opens in the intervalve region 145a, and the other end of the back pressure relief passage 146 is the intervening member (cylinder gasket 152, suction valve forming plate 150, valve plate 103, discharge valve forming plate 151). And the head gasket 153) to open to the suction chamber 141. In the present embodiment, the back pressure relief passage 146 is formed so as to pass through the back pressure chamber 403b of the second accommodating hole 403 described later of the second control valve 350, and the throttle portion 146a penetrates through the intervening member. It is composed of holes 103d. Specifically, one end of the groove 103e formed in the valve plate 103 opens into the through hole 103c penetrating the intervening member, and the other end of the groove 103e communicates between the back pressure chamber 403b and the groove 103e. There is an opening in the through hole 103f that penetrates the cylinder gasket 152 and the suction valve forming plate 150. Therefore, in the present embodiment, the back pressure relief passage 146 is formed by the groove portion 103e, the through hole 103f, the back pressure chamber 403b, and the through hole 103d as the throttle portion 146a.

As described above, when the first control valve 300 closes the supply passage 145, the refrigerant gas is not supplied to the intervalve region 145a in the supply passage 145. Further, the refrigerant gas in the valve-to-valve region 145a in the supply passage 145 flows out (exhausts) to the suction chamber 141 via the back pressure relief passage 146. Therefore, the pressure in the intervalve region 145a in the supply passage 145 approaches the pressure in the suction chamber 141. On the other hand, when the first control valve 300 opens the supply passage 145, the check valve 250 opens and the refrigerant gas in the discharge chamber 142 is supplied to the crank chamber 140. At this time, a part of the refrigerant gas leaks to the suction chamber 141 via the back pressure relief passage 146. Therefore, it is desirable that the passage cross section of the throttle portion 146a of the back pressure relief passage 146 is set as small as possible.

"Discharge passage 147"
The discharge passage 147 is formed as a passage that communicates between the crank chamber 140 and the suction chamber 141, and has a throttle portion 147a. In the present embodiment, the discharge passage 147 is a communication hole 101e composed of an in-shaft passage 147b and a through hole 135a, a gap between one end surface 451 of the valve housing 450 and a recess bottom surface 101c1, and a second valve hole 403a1 described later. Between the throttle portion 147a, the valve chamber 403a of the second accommodating hole 403 described later, the discharge hole 403a2 described later, the inner peripheral surface 101c2 of the recess 101c, and the outer surface 453 of the valve housing 450 facing the inner peripheral surface 101c2. The intervening member (cylinder gasket 152, suction valve forming plate 150, valve plate 103, discharge valve forming plate 151) communicates with the annular gap, a part of the opening end of the annular gap, and the suction chamber 141. And 103g of through holes penetrating the head gasket 153).

"Second control valve 350"
In the present embodiment, the second control valve 350 has a second accommodating hole 403 and a second valve body 351 accommodated in the second accommodating hole 403 and movable in the second accommodating hole 403. .. The second valve body 351 has a valve portion 351a and a pressure receiving portion 351b.

The second accommodating hole 403 is formed in the valve housing 450 and extends parallel to the axis of the drive shaft 110. The second accommodating hole 403 is formed in the shape of a bottomed stepped circular hole that opens to the rear end surface side of the cylinder block 101, and has a small-diameter valve chamber 403a on the hole bottom side and a valve chamber 403a on the opening side. It has a larger diameter back pressure chamber 403b. The second accommodating hole 403 extends from one end surface 451 of the valve housing 450 facing the bottom surface 101c1 of the recess toward the other end surface 452 of the valve housing 450. That is, the first accommodating hole 401 and the second accommodating hole 403 extend in parallel with each other from one end surface 451 of the valve housing 450 toward the other end surface 452, respectively.

A second valve hole 403a1 is opened at the bottom of the valve chamber 403a, and the valve chamber 403a has a second valve hole 403a1 (specifically, a second valve hole 403a1, one end surface 451 of the valve housing 450, and a recessed bottom surface 101c1). It communicates with the crank chamber 140 through the gap between the two and the communication hole 101e). Specifically, one end of the second valve hole 403a1 opens to the bottom of the valve chamber 403a, and the other end of the second valve hole 403a1 opens to one end surface 451 of the valve housing 450. In the present embodiment, the second valve hole 403a1 corresponds to the "valve hole" of the second control valve 350 according to the present invention.

Further, a discharge hole 403a2 is opened in the hole wall of the valve chamber 403a, and the valve chamber 403a has a discharge hole 403a2 (specifically, a discharge hole 403a2, an inner peripheral surface 101c2 of the recess 101c, and an outer surface 453 of the valve housing 450. It communicates with the suction chamber 141 through an annular gap (through hole 103 g) between the two. Specifically, one end of the discharge hole 403a2 opens to the inner wall surface of the valve chamber 403a, and the other end of the discharge hole 403a2 opens to the outer surface 453 (outer peripheral surface) of the valve housing 450. As described above, the valve chamber 403a forms a part of the discharge passage 147 together with the second valve hole 403a1 and the discharge hole 403a2.

In the present embodiment, as described above, the valve housing 450 is provided between one end surface 451 and the recess bottom surface 101c1 and between the inner peripheral surface 101c2 of the recess 101c and the outer surface 453 of the valve housing 450 facing the inner peripheral surface 101c2. , Each is arranged so as to have a gap. An airtight member 500 is provided between the recess 101c and the valve housing 450. Then, the airtight member 500 includes a region in which the second valve hole 403a1 and the first accommodating hole 401 open in the gap and the remaining region in the gap (specifically, the inner peripheral surface 101c2 of the recess 101c and the valve housing 450). The region of the annular gap between the outer surface 453 and the discharge hole 403a2) is airtightly partitioned.

The back pressure chamber 403b forms the open end of the second accommodating hole 403 and is closed by the intervening members (cylinder gasket 152, suction valve forming plate 150, valve plate 103, discharge valve forming plate 151 and head gasket 153). .. The opening of the back pressure chamber 403b is eccentrically expanded toward the first accommodating hole 401. A through hole 103f is connected to the enlarged diameter and eccentric portion. That is, the back pressure chamber 403b communicates with the intervalve region 145a via the through hole 103f and the groove 103e.

The second valve body 351 has a valve portion 351a arranged in the valve chamber 403a and a pressure receiving portion 351b arranged in the back pressure chamber 403b, and moves according to the front-rear differential pressure to move the second valve hole 403a1. Is configured to open and close. In the present embodiment, the second valve hole 403a1 corresponds to the "valve hole" according to the present invention.

The valve portion 351a is slidably supported by the valve chamber 403a (in the figure, the gap between the valve portion 351a and the inner wall of the valve chamber 403a is exaggerated). The valve portion 351a is located in the valve chamber 403a, and an extension portion extending from the valve portion 351a projects into the back pressure chamber 403b. The pressure receiving portion 351b is formed in a cylindrical shape and is press-fitted and fixed to the extension portion extending from the valve portion 351a. As a result, the second valve body 351 including the valve portion 351a and the pressure receiving portion 351b is configured.

In the second accommodating hole 403, the second valve body 351 can move in a direction parallel to the axis of the drive shaft 110. One end surface of the valve portion 351a of the second valve body 351 comes into contact with the valve seat portion 403a3 formed in the hole bottom of the valve chamber 403a, thereby restricting the movement of one of the second valve bodies 351 and the second valve body 351. The movement of the other of the second valve body 351 is restricted by the end surface of the ridge 351b1 projecting in an annular shape from the end surface of the pressure receiving portion 351b on the side of the intervening member in contact with the intervening member. Then, the second valve hole 403a1 is opened and closed when one end surface of the valve portion 351a of the second valve body 351 comes into contact with the valve seat portion 403a3. A notch groove is formed on one end surface of the valve portion 351a, and the notch groove constitutes the throttle portion 147a of the discharge passage 147. In a state where one end surface of the valve portion 351a is in contact with the valve seat portion 403a3, the second valve hole 403a1 is formed between the inner wall surface of the hole of the valve chamber 403a and the valve portion 351a through the notch groove as the throttle portion 147a. It communicates with the gap between the outer peripheral surface. Further, the ridges 351b1 formed in the pressure receiving portion 351b are formed in order to reduce the contact area of the pressure receiving portion 351b with respect to the intervening member. Further, by forming the notch groove 351b2 in the ridge 351b1, the contact area with respect to the intervening member is reduced. As a result, the pressure receiving portion 351b is configured to facilitate the detaching operation with respect to the intervening member.

Here, the operation of the second control valve 350 will be described. First, when the first control valve 300 opens the supply passage 145, the second control valve 350 exerts the pressure acting on the end face of the pressure receiving portion 351b, that is, the pressure Pc'(hereinafter referred to as the pressure Pc'of the valve-to-valve region 145a in the supply passage 145. The second valve body 351 is moved in the valve closing direction by utilizing the increase of (referred to as "back pressure Pc'"), and as shown in FIG. 2, one end surface of the valve portion 351a of the second valve body 351 is a valve seat portion. It is brought into contact with 403a3. As a result, the discharge passage 147 is narrowed down by the throttle portion 147a, and the opening degree (passage cross section) of the discharge passage 147 is minimized.

Next, when the first control valve 300 closes the supply passage 145, the second control valve 350 opens the second valve body 351 by utilizing the decrease in the back pressure Pc'acting on the end face of the pressure receiving portion 351b. As shown in FIG. 3, the end surface of the ridge 351b1 of the pressure receiving portion 351b is brought into contact with the intervening member, and one end surface of the valve portion 351a is separated from the valve seat portion 403a3 to form a discharge passage 147. Open. As a result, the opening degree (passage cross section) of the discharge passage 147 becomes maximum.

In this way, the valve housing 450 in which the first accommodating hole 401 for the first valve body 251 of the check valve 250 and the second accommodating hole 403 for the second control valve 350 are formed, and the first valve body 251. A variable displacement compressor 100 including a valve unit 400 having a second valve body 351 and a second valve body 351 is configured. The valve unit 400 is housed in a recess 101c recessed in the rear end surface of the cylinder block 101.

"Operation of variable capacitance compressor 100"
First, when the variable displacement compressor 100 is stopped, such as when the engine of the vehicle is stopped, the energization of the drive unit of the first control valve 300 to the coil is turned off, and the first control The valve 300 opens the supply passage 145 to the maximum (maximizes the passage cross section). Further, in the check valve 250, the end wall 251b of the first valve body 251 is separated from the valve seat portion 150a, and the end surface of the large diameter portion 251a1 of the first valve body 251 on the small diameter portion 251a2 side is the first accommodating hole 401. The supply passage 145 is in an open state in contact with the stepped portion of the above. Further, in the second control valve 350, one end surface of the valve portion 351a is in contact with the valve seat portion 403a3, and the passage cross section of the discharge passage 147 is minimized.

When the engine of the vehicle starts in the above state and the drive shaft 110 of the variable displacement compressor 100 rotates, the discharge check valve 200 blocks the discharge passage, so that the compressed discharged refrigerant (in the discharge chamber 142) The refrigerant gas) is supplied to the crank chamber 140 via the supply passage 145. Then, the pressure in the crank chamber 140 rises, the tilt angle of the swash plate 111 becomes the minimum, and the stroke (discharge capacity) of the piston 136 becomes the minimum. At this time, the variable capacitance compressor 100 is in a non-operating state. The compressed and discharged refrigerant circulates in the internal circulation path composed of the discharge chamber 142, the supply passage 145, the crank chamber 140, the discharge passage 147, the suction chamber 141, and the cylinder bore 101a.

Next, when the air conditioner system is activated, a current flows through the coil of the drive unit of the first control valve 300, the first control valve 300 is closed, and the supply passage 145 is closed. In this case, the compressed and discharged refrigerant is not supplied to the valve-to-valve region 145a in the supply passage 145, and the refrigerant in the inter-valve region 145a flows to the suction chamber 141 via the back pressure relief passage 146 and Pc. ′ <Pc. Therefore, the check valve 250 closes the supply passage 145. Further, the second control valve 350 opens the discharge passage 147, and the passage cross section of the discharge passage 147 is maximized.

Therefore, the refrigerant in the crank chamber 140 quickly flows out to the suction chamber 141, and the pressure in the crank chamber 140 becomes equal to the pressure in the suction chamber 141. As a result, the tilt angle of the swash plate 111 becomes maximum, and the stroke of the piston 136 (that is, the discharge capacity of the variable displacement compressor 100) becomes maximum. Then, the discharge check valve 200 is opened, the refrigerant circulates in the air conditioner system, and the air conditioner system is put into an operating state.

Then, when the pressure in the suction chamber 141 drops to the set pressure set by the current flowing through the coil of the drive unit, the first control valve 300 is opened, whereby the compressed and discharged refrigerant is in the intervalve region 145a. Is supplied to. Then, Pc'> Pc, the check valve 250 opens the supply passage 145, and the compressed and discharged refrigerant is supplied to the crank chamber 140. Further, the second control valve 350 moves in the valve closing direction to narrow the discharge passage 147, and the passage cross section of the discharge passage 147 is minimized. As a result, the pressure in the crank chamber 140 rises, the tilt angle of the swash plate 111 decreases, the stroke (discharge capacity) of the piston 136 decreases, and the discharge capacity control state is established.

In the variable displacement compressor 100 according to the present embodiment, the first accommodating hole 401 accommodating the first valve body 251 of the check valve 250 and the second accommodating hole 403 accommodating the second valve body 351 of the second control valve 350. Is formed in the valve housing 450. That is, the first accommodating hole 401 and the second accommodating hole 403 are formed in the valve housing 450, which is a member different from the cylinder block 101. Therefore, the cylinder block 101 may be formed with one recess 101c that accommodates the entire valve unit 400 including the valve housing 450, the first valve body 251 and the second valve body 351. Therefore, it is not necessary to perform complicated processing on the cylinder block 101 itself to form the first accommodating hole 401 and the second accommodating hole 403.

In this way, it is possible to provide the variable displacement compressor 100 having a structure capable of providing the check valve 250 and the second control valve 350 without performing complicated processing on the cylinder block 101.

In the present embodiment, the back pressure relief passage 146 is formed so as to pass through the back pressure chamber 403b, and the throttle portion 146a penetrates the intervening member sandwiched between the cylinder block 101 and the cylinder head 104. It is composed of holes 103d. That is, the back pressure relief passage 146 is formed by utilizing the intervening member and the back pressure chamber 403b, and is constructed without processing the cylinder head 104. Thereby, the back pressure relief passage 146 can be easily constructed.

In the present embodiment, the first housing hole 401 communicates with the crank chamber 140 via the passage pipe 148 inserted through the communication hole 101b, and the second housing hole 403 is the second valve hole 403a1 and the recess bottom surface 101c1. It communicates with the crank chamber 140 through a gap between the one end surface 451 of the housing 450 and a communication hole 101e opened in the recess bottom surface 101c1. That is, the first accommodating hole 401 and the second accommodating hole 403 are individually communicated with the crank chamber 140, and the refrigerant gas path is from the first accommodating hole 401 to the crank chamber 140, and then the crank. A one-way route from the chamber 140 to the second accommodating hole 403 is formed. As a result, foreign matter in the crank chamber 140 is easily discharged to the outside of the crank chamber 140.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications and modifications can be made based on the technical idea of the present invention. Some of them are listed below.

The pressure receiving portion 351b of the second valve body 351 is supposed to be in contact with the intervening member, but the present invention is not limited to this. For example, as shown in FIG. 4, an annular second valve body stopper 352 is press-fitted and fixed to a portion of the opening of the back pressure chamber 403b that is eccentrically expanded toward the first accommodating hole 401 side, and this second The annular end face of the pressure receiving portion 351b is configured to be separated from the end face of the peripheral edge of the through hole of the valve body stopper 352. As a result, the contact area of the end surface of the pressure receiving portion 351b can be easily reduced without forming the ridges 351b1 and the notch groove 351b2 on the end surface of the pressure receiving portion 351b, and the shape of the pressure receiving portion 351b is simplified. be able to.

The valve seat portion 150a and the first valve hole 150b to which the first valve body 251 is separated from each other are assumed to be formed on the suction valve forming plate 150, but the present invention is not limited to this. For example, as shown in FIG. 5, an annular check valve stopper 252 is press-fitted and fixed to the opening end side of the large-diameter hole portion 401a of the first accommodating hole 401, and the end surface of the check valve stopper 252 is the valve seat portion. 150a may be formed, and the through hole of the check valve stopper 252 may form the first valve hole 150b.

Further, the back pressure relief passage 146 is formed by the groove portion 103e, the through hole 103f, the back pressure chamber 403b, and the through hole 103d as the throttle portion 146a, but is not limited to this. For example, as shown in FIG. 5, between the opening end of the large-diameter hole 401a of the first accommodating hole 401 and the opening end of the back pressure chamber 403b of the second accommodating hole 403 on the other end surface 452 of the valve housing 450. A groove portion 454 is formed in the housing. As a result, the back pressure relief passage 146 is formed by the groove portion 454, the back pressure chamber 403b, and the through hole 103d as the throttle portion 146a. Although not shown, an enlarged diameter portion is formed by further expanding the opening end portion of the large diameter hole portion 401a of the first valve hole 150b, and one end surface of the check valve stopper 252 is larger than the enlarged diameter portion. A compression coil spring is provided between the other end surface of the check valve stopper 252 and the intervening member while being abutted against a step portion between the diameter hole portion 401a, and the check valve stopper 252 is raised by the compression coil spring. The check valve stopper 252 may be press-fitted and fixed to the enlarged diameter portion while being pressed against the portion. Further, the present invention is not limited to the compression coil spring, and the check valve stopper 252 may be pressed against the step portion to be fixed by a retaining ring, and an O-ring may be attached to the outer periphery of the check valve stopper 252.

Further, in the present embodiment, the airtight member 500 is attached to the groove portion 453a formed on the entire circumference of the outer surface 453 of the valve housing 450 on the one end surface 451 side, but the present invention is not limited to this. Although not shown, the airtight member 500 may be arranged between the bottom surface 101c1 of the recess and one end surface 451 of the valve housing 450. In this case, since the airtight member 500 functions as the urging member 600 for urging the valve housing 450 toward the opening side of the recess 101c, the urging member 600 does not need to be provided separately.

In the present embodiment, the first accommodating hole 401 and the second accommodating hole 403 are individually communicated with the crank chamber 140, but the present invention is not limited to this. For example, as shown in FIG. 6, the first accommodating hole 401 opens in the gap between the recess bottom surface 101c1 and the one end surface 451 of the valve housing 450, and the crank is opened through the communication hole 101e opened in the recess bottom surface 101c1. Both the first accommodating hole 401 and the second accommodating hole 403 may communicate with the crank chamber 140 via the communicating hole 101e so as to communicate with the chamber 140. In this case, the gap between the bottom surface 101c1 of the recess and the one end surface 451 of the valve housing 450 and the passage including the communication hole 101e including the in-shaft passage 147b and the through hole 135a form a part of the discharge passage 147. It forms part of the supply passage 145. Further, in this case, as shown in FIG. 6, as a positioning member for determining the position of the valve housing 450 in the radial direction in the recess 101c, a positioning pin 700 is provided, for example, between the recess bottom surface 101c1 and one end surface 451 of the valve housing 450. Provided in between. Further, not limited to this, although not shown, a flange-shaped flange portion is formed on the outer edge portion of the other end surface 452 of the valve housing 450, and a fitting portion matching the shape of the flange portion is formed at the open end of the recess 101c. The flange portion may be fitted to the fitting portion to determine the radial position of the valve housing 450 in the recess 101c. Although not shown, in the structure shown in FIG. 6, the portion of the small-diameter hole portion 401b of the first accommodating hole 401 on the concave bottom surface 101c1 side may be further reduced in diameter to provide the reduced-diameter portion. In this case, the end surface of the small diameter portion 251a2 of the first valve body 251 abuts on the stepped portion between the small diameter hole portion 401b of the first accommodating hole 401 and the reduced diameter portion, whereby the valve opening direction of the first valve body 251 Configure to regulate the movement of.

The variable capacitance compressor 100 is not limited to the swash plate type clutchless compressor, and may be a variable capacitance compressor equipped with an electromagnetic clutch or a variable capacitance compressor driven by a motor.

100 ... Variable capacity compressor, 101 ... Cylinder block, 101a ... Cylinder bore (compression part), 101c ... Recess, 101c1 ... Recess bottom surface, 101c2 ... Inner peripheral surface, 101e ... Communication hole, 102 ... Front housing, 103 ... Valve plate ( Intervening member), 103d ... Through hole (squeezing part of back pressure relief passage), 104 ... Cylinder head, 136 ... Piston 136 (compressing part), 140 ... Crank chamber (control pressure chamber), 141 ... Suction chamber, 142 ... Discharge Chamber, 145 ... Supply passage, 145a ... Valve area, 146 ... Back pressure relief passage, 146a ... Squeezing part, 147 ... Discharge passage, 148 ... Passage pipe (positioning member), 150 ... Suction valve forming plate (intervening member), 151 ... Discharge valve forming plate (intervening member), 152 ... Cylinder gasket (intervening member), 153 ... Head gasket (intervening member), 250 ... Check valve, 251 ... First valve body, 300 ... First control valve, 350 ... 2nd control valve, 351 ... 2nd valve body, 351a ... valve part, 351b ... pressure receiving part, 400 ... valve unit, 401 ... 1st accommodating hole, 403 ... 2nd accommodating hole, 403a ... valve chamber, 403a1 ... 2 valve holes (valve holes), 403a2 ... discharge holes, 403b ... back pressure chamber, 450 ... valve housing, 451 ... one end surface, 452 ... other end surface, 453 ... outer surface, 500 ... airtight member, 600 ... urging member, 700 ... Positioning pin (positioning member)

Claims (5)

A cylinder block, a front housing provided on the front end surface side of the cylinder block, and a housing including a cylinder head provided on the rear end surface side of the cylinder block.
A suction chamber provided in the cylinder head to which the refrigerant is guided from the outside and
A compression unit provided in the cylinder block that sucks and compresses the refrigerant in the suction chamber,
A discharge chamber provided in the cylinder head to discharge the refrigerant compressed by the compression unit, and
A control pressure chamber provided in the front housing and
A first control valve provided in a supply passage for supplying the refrigerant in the discharge chamber to the control pressure chamber and controlling the opening degree of the supply passage.
A check valve provided on the control pressure chamber side of the supply passage and blocking the flow of the refrigerant from the control pressure chamber to the first control valve.
A second control valve provided in the discharge passage for discharging the refrigerant in the control pressure chamber to the suction chamber and controlling the opening degree of the discharge passage, and
A back pressure relief passage having a throttle portion communicating with the valve-to-valve region, which is a region between the first control valve and the check valve in the supply passage, and the suction chamber.
A variable displacement compressor whose discharge capacity changes according to the pressure in the control pressure chamber.
The check valve is
The first accommodating hole forming a part of the supply passage and
A first valve body that is housed in the first storage hole and is configured to move according to the differential pressure before and after to block the flow of the refrigerant from the control pressure chamber to the first control valve.
Have,
The second control valve is
In the valve chamber which communicates with the control pressure chamber through the valve hole and communicates with the suction chamber through the discharge hole and forms a part of the discharge passage together with the valve hole and the discharge hole, and in the valve-to-valve region. A second accommodating hole having a back pressure chamber that communicates with,
A second valve body having a valve portion arranged in the valve chamber and a pressure receiving portion arranged in the back pressure chamber, and is configured to move according to a differential pressure in the front-rear direction to open and close the valve hole. When,
The configuration has
A valve unit having a valve housing in which the first accommodating hole and the second accommodating hole are formed, the first valve body, and the second valve body.
Prepare
The valve unit is a recess recessed in the rear end surface of the cylinder block, and is housed in the recess that communicates with the control pressure chamber through a communication hole opened in the bottom surface of the recess. Capacity compressor. The back pressure relief passage is formed so as to pass through the back pressure chamber.
The variable displacement compressor according to claim 1, wherein the throttle portion is composed of a through hole penetrating an intervening member sandwiched between the cylinder block and the cylinder head. The first accommodating hole and the second accommodating hole extend in parallel with each other from one end surface of the valve housing facing the bottom surface of the recess toward the other end surface of the valve housing.
The valve housing is arranged so as to have a gap between the one end surface and the bottom surface of the recess, and between the inner peripheral surface of the recess and the outer surface of the valve housing facing the inner peripheral surface of the recess.
The valve hole is opened on the one end surface of the valve housing.
The discharge hole is configured to open to the outer surface of the valve housing.
An airtight member provided between the recess and the valve housing to airtightly partition between the area of the gap where the valve hole and the first accommodating hole open and the remaining area of the gap. The variable displacement compressor according to claim 1 or 2, further comprising. The invention according to any one of claims 1 to 3, further comprising a positioning member for determining the position of the first valve body and the second valve body in the recess of the valve housing in a direction orthogonal to the moving direction of the second valve body. Variable capacity compressor. The variable displacement compressor according to any one of claims 1 to 4, further comprising an urging member for urging the valve housing toward the opening side of the recess.