WO2020004166A1

WO2020004166A1 - Variable-capacity compressor

Info

Publication number: WO2020004166A1
Application number: PCT/JP2019/024241
Authority: WO
Inventors: 田口　幸彦; 清人菊池
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: 2018-06-27
Filing date: 2019-06-19
Publication date: 2020-01-02
Also published as: JP2020002837A; JP7052964B2

Abstract

[Problem] To provide a variable-capacity compressor that makes it possible to curb any increase in size in a direction running along an axial direction of a drive shaft. [Solution] A variable-capacity compressor (1) where opening degree adjustment of a first control valve (9) for changing the opening degree of a supply channel (7) changes the pressure of a crankcase (30), thus adjusting the stroke of a piston (23), wherein a second control valve (10) includes: a valve chamber (100) arranged, out of a center bore (22), between one end of a drive shaft (6) and a valve plate (4), and a valve element (110) accommodated so as to be moveable along an axial direction of the drive shaft (6) to the valve chamber (100); and the valve element (110) moves between a first wall surface (101) where a first port (P1) opens and a second wall surface (102) where a second port (P2) and a third port (P3) open, in accordance with the difference between the pressure of a region between the first control valve (9) and a check valve (75) in the supply channel (7), and the pressure of the crankcase (30).

Description

Variable capacity compressor

The present invention relates to a variable displacement compressor used for, for example, an air conditioner for a vehicle.

As a variable displacement compressor which is provided with a displacement control valve and whose discharge displacement is controlled by regulating the pressure in a crank chamber, there is, for example, one having a configuration described in Patent Document 1.
In the variable displacement compressor described in Patent Literature 1, a second control valve that adjusts an opening degree of a pressure release passage that discharges a refrigerant in a crank chamber to a suction chamber includes a valve chamber that receives pressure in the crank chamber and a pressure supply. A partition member for partitioning the back pressure chamber receiving the pressure of the passage; The partition member has a side wall provided so as to surround the valve portion of the spool, and an end wall connected to one end of the side wall and through which a shaft portion of the spool passes. In the second control valve, the end surface of the partition member opposite to the end wall of the partition member abuts against the wall surface of the valve chamber opposite to the back pressure chamber, and the valve portion of the spool is opposite to the back pressure chamber of the valve chamber. When it comes into contact with the wall surface, the pressure receiving portion of the spool comes into contact with the end wall of the partition member.

JP 2016-108960 A

In the variable displacement compressor described in Patent Literature 1, the configuration of the second control valve is such that a back pressure chamber that receives the pressure of the pressure supply passage and a valve chamber that receives the pressure of the crank chamber are partitioned. The pressure receiving section is provided in the chamber, and the valve section is provided in the valve chamber. For this reason, the length of the second control valve along the axial direction of the drive shaft becomes longer, and it is necessary to provide a dedicated storage chamber for disposing the second control valve inside the variable displacement compressor. There is a problem that the length of the variable displacement compressor along the axial direction of the shaft becomes long.
The present invention has been made in view of the above problems, and has an object to provide a variable displacement compressor that can suppress an increase in size in a direction along an axial direction of a drive shaft. I do.

In order to solve the above-described problem, one embodiment of the present invention is to change the pressure in the crank chamber by adjusting the opening degree of a first control valve that changes the opening degree of a supply passage that supplies the refrigerant in the discharge chamber to the crank chamber. Then, the stroke of the piston is adjusted by changing the inclination angle of the swash plate. Further, the compressor is a variable displacement compressor that compresses the refrigerant sucked from the suction chamber into the cylinder bore by the stroke-adjusted piston and discharges the refrigerant to the discharge chamber. Further, the variable capacity compressor is arranged on a side closer to the crank chamber than the first control valve in the supply passage, the second control valve for adjusting the opening degree of the discharge passage that connects the crank chamber and the suction chamber, In addition, a check valve for preventing the refrigerant from moving from the crank chamber to the first control valve is provided. In addition, the variable displacement compressor includes a throttle passage that communicates a supply passage between the first control valve and the check valve with the suction chamber. Further, the second control valve has a valve chamber disposed between one end of the drive shaft and the valve plate in the center bore, and a valve body accommodated in the valve chamber so as to be movable in the axial direction of the drive shaft. . The valve chamber has a first wall arranged on one side in the moving direction of the valve body, a second wall arranged on the other side in the moving direction of the valve body, and a first wall in the supply passage which is opened on the first wall. It has a first port communicating with the area between the control valve and the check valve. In addition to this, the valve chamber opens to the second wall surface and communicates with the crank chamber through a part of the discharge passage, and the suction chamber opens to the second wall surface and communicates through a part of the discharge passage. A third port that communicates with the The valve body has a first pressure receiving surface that is a surface facing the first wall surface, and a second pressure receiving surface that is a surface facing the second wall surface, and is provided between the first control valve and the check valve in the supply passage. It moves between the first wall surface and the second wall surface according to the difference between the pressure in the region and the pressure in the crankcase. When the pressure in the region between the first control valve and the check valve in the supply passage is higher than the pressure in the crank chamber, the valve body contacts the second wall surface to close the second port and the third port. By doing so, the opening degree of the discharge passage is minimized. On the other hand, when the pressure in the area between the first control valve and the check valve in the supply passage is lower than the pressure in the crank chamber, the valve body separates from the second wall surface and opens the second port and the third port. By doing so, the opening degree of the discharge passage is maximized.

According to one aspect of the present invention, a portion of the center bore between one end of the drive shaft and the valve plate is a valve chamber, and the valve chamber has a pressure in a region between the first control valve and the check valve in the supply passage. And a valve element that moves according to the difference between the pressure and the pressure in the crank chamber.
This eliminates the need to provide a dedicated storage chamber for disposing the second control valve inside the variable displacement compressor. For this reason, it is possible to provide a variable displacement compressor that can suppress an increase in the size of the drive shaft in the axial direction.

It is a sectional view showing the composition of the variable displacement compressor in a first embodiment of the present invention. FIG. 2 is an enlarged view of a range surrounded by a line II in FIG. 1. It is a figure showing the structure of a valve room. FIG. 4 is a sectional view taken along line IV-IV of FIG. 3. It is a figure showing the structure of a valve element. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the operation which the variable capacity compressor of a first embodiment performs. It is a figure showing the modification of a 1st embodiment.

A first embodiment of the present invention will be described below with reference to the drawings. In the description of the drawings referred to in the following description, the same or similar portions are denoted by the same or similar reference numerals. However, it should be noted that the drawings are schematic, and the relationship between the thickness and the plane dimension, the ratio of the thickness of each layer, and the like are different from actual ones. Therefore, specific thicknesses and dimensions should be determined in consideration of the following description. In addition, it is needless to say that dimensional relationships and ratios are different between drawings.

Furthermore, the first embodiment described below exemplifies a configuration for embodying the technical idea of the present invention, and the technical idea of the present invention is based on the materials of components, their shapes, The structure, arrangement, etc. are not specified as follows. The technical idea of the present invention can be variously modified within the technical scope defined by the claims described in the claims. Further, the directions “left and right” and “up and down” in the following description are simply definitions for convenience of description, and do not limit the technical idea of the present invention. Therefore, for example, if the paper is rotated 90 degrees, "left and right" and "up and down" are read interchangeably, and if the paper is rotated 180 degrees, "left" becomes "right" and "right" becomes "left". Of course.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
(Constitution)
The configuration of the first embodiment will be described with reference to FIGS.
(Variable capacity compressor)
As shown in FIG. 1, the variable displacement compressor 1 includes a cylinder block 2, a front housing 3, a valve plate 4, a cylinder head 5, a drive shaft 6, a supply passage 7, a discharge passage 8, A first control valve 9 and a second control valve 10 are provided. Note that the upper side in FIG. 1 is the upper side in the vertical direction. Similarly, the lower part in FIG. 1 is the lower part in the vertical direction.
In the first embodiment, as an example, a case will be described in which the variable displacement compressor 1 is configured as a clutchless variable displacement compressor applied to an air conditioner system (air conditioner system) for a vehicle (vehicle). I do.
The cylinder block 2, the front housing 3, the valve plate 4, and the cylinder head 5 are fastened by through bolts 11 via a gasket (not shown) to form a housing of the variable displacement compressor 1.

(Cylinder block)
A plurality of cylinder bores 21 and one center bore 22 are defined in the cylinder block 2.
The plurality of cylinder bores 21 are arranged annularly.
A piston 23 is housed inside the cylinder bore 21.
The center bore 22 is arranged radially inside the plurality of annularly arranged cylinder bores 21 at the center, and is a space penetrating the cylinder block 2.

(Front housing)
The front housing 3 closes one end side (front side; left side in FIG. 1) of the cylinder block 2. The front housing 3 defines a crank chamber 30 together with the cylinder block 2.
The crank chamber 30 is a space formed by the front housing 3 and the cylinder block 2, and has a swash plate 31 disposed therein. The drive shaft 6 is disposed inside the crank chamber 30 so that the axial direction thereof is horizontal.

The swash plate 31 is formed in an annular shape and surrounds the drive shaft 6 from the radial direction.
The swash plate 31 is connected to a rotor 32 fixed to the drive shaft 6 via a link mechanism 33, and rotates together with the drive shaft 6. That is, the rotor 32 is fixed to the drive shaft 6 and rotates integrally with the drive shaft 6.
Further, the swash plate 31 can change the inclination angle (inclination angle) with respect to the axis of the drive shaft 6.
The link mechanism 33 includes a first arm 33a, a second arm 33b, and a link arm 33c.
The first arm 33a protrudes from a surface of the rotor 32 facing the swash plate 31. The second arm 33b protrudes from a surface of the swash plate 31 facing the rotor 32. One end of the link arm 33c is rotatably connected to the first arm 33a via a first connection pin 33d. The other end of the link arm 33c is rotatably connected to the second arm 33b via a second connection pin 33e.

貫通 Further, the swash plate 31 is formed with a through hole 34 in such a shape that the swash plate 31 can be tilted within the range of the maximum tilt angle and the minimum tilt angle. The through-hole 34 is formed with a minimum inclination restricting portion (not shown) that contacts the drive shaft 6. When the inclination angle of the swash plate 31 when the swash plate 31 is perpendicular to the drive shaft 6 is 0 [°], the minimum inclination restricting unit can displace the swash plate 31 by approximately 0 [°]. It is formed to be possible. Also, when the inclination angle of the swash plate 31 is maximized, the swash plate 31 comes into contact with the rotor 32 and the increase of the inclination angle is restricted.

Between the rotor 32 and the swash plate 31 is mounted an inclination-reducing spring 35 that urges the swash plate 31 in the direction of decreasing the inclination until the swash plate 31 has the minimum inclination. Further, between the swash plate 31 and the spring support member 36, a tilt-increase spring 37 that urges the swash plate 31 in a direction to increase the tilt angle is mounted.
The urging force of the inclination increasing spring 37 at the minimum inclination is set to be larger than the urging force of the inclination decreasing spring 35. Therefore, when the drive shaft 6 is not rotating, the inclination angle of the swash plate 31 is an angle at which the urging force of the inclination decreasing spring 35 and the urging force of the inclination increasing spring 37 are balanced.

The outer peripheral portion of the swash plate 31 is accommodated in an inner space formed at an end of the piston 23 that protrudes toward the crank chamber 30 side. Thus, the swash plate 31 is configured to interlock with the piston 23 via the pair of shoes 38. Accordingly, the rotation of the swash plate 31 accompanying the rotation of the drive shaft 6 causes each piston 23 to reciprocate inside the accommodated cylinder bore 21. That is, the swash plate 31 and the shoe 38 form a conversion mechanism that converts the rotation of the drive shaft 6 into a reciprocating motion of the piston 23. Further, the piston 23 is disposed in each of the plurality of cylinder bores 21 and reciprocates in the axial direction of the drive shaft 6. The swash plate 31 is connected to the rotor 32 and is slidably attached to the drive shaft 6 such that the swash plate 31 rotates in synchronization with the rotor 32 and has a variable inclination angle with respect to the axis of the drive shaft 6.

(Valve plate)
The valve plate 4 is provided between the cylinder block 2 and the cylinder head 5. One surface of the valve plate 4 closes the other end side (the right side in FIG. 1) of the cylinder block 2 so that each cylinder bore 21 is closed. It is closed.
Further, a discharge hole 41 and a suction hole 42 are formed in the valve plate 4.
The discharge hole 41 and the suction hole 42 communicate with the respective cylinder bores 21.
That is, the valve plate 4 closes the other end side (rear side, right side in FIG. 1) of the cylinder block 2, and has a discharge hole 41 and a suction hole 42 communicating with the cylinder bore 21.

(cylinder head)
The cylinder head 5 is provided to face the cylinder block 2 with the valve plate 4 interposed therebetween. That is, the cylinder head 5 is provided on the other end side of the cylinder block 2 via the valve plate 4.
Further, the cylinder head 5 is formed with a suction chamber 51 and a discharge chamber 52 partitioned inside the cylinder head 5. The suction chamber 51 and the discharge chamber 52 are closed by the other surface of the valve plate 4.
The suction chamber 51 is disposed at the center of the cylinder head 5 when viewed from the axial direction of the drive shaft 6.
In addition, the suction chamber 51 is connected to a suction side external refrigerant circuit of the air conditioner system via a suction port 53 and a suction passage 54, and a low pressure side refrigerant (refrigerant gas) from the suction side external refrigerant circuit. Inhalation.

Further, the suction chamber 51 communicates with each cylinder bore 21 via a suction hole 42 provided in the valve plate 4 and a suction valve (not shown).
The discharge chamber 52 is disposed at a position surrounding the suction chamber 51 in a ring shape when viewed from the axial direction of the drive shaft 6. That is, the discharge chamber 52 is annularly arranged outside the suction chamber 51.
The discharge chamber 52 communicates with each cylinder bore 21 via a discharge valve (not shown) and a discharge hole 41 provided in the valve plate 4.

Therefore, the low-pressure side refrigerant drawn into the suction chamber 51 from the suction-side external refrigerant circuit is drawn into the cylinder bore 21 containing the piston 23 by the reciprocating motion of the piston 23. Then, the reciprocating motion of the piston 23 causes the piston 23 to be compressed to a high pressure and discharged to the discharge chamber 52. That is, the cylinder bore 21 and the piston 23 form a compression unit that compresses the refrigerant drawn into the suction chamber 51.
Further, the discharge chamber 52 is connected to a discharge-side external refrigerant circuit of the air conditioning system via a discharge passage 55 and a discharge port 56. Accordingly, the refrigerant discharged into the discharge chamber 52 and compressed by the compression unit is discharged as a high-pressure refrigerant (refrigerant gas) to the external refrigerant circuit on the discharge side via the discharge passage 55 and the discharge port 56. .

A discharge check valve 57 is arranged between the discharge chamber 52 and the discharge passage 55.
The discharge check valve 57 operates in response to a pressure difference between the discharge chamber 52 (upstream) and the discharge passage 55 (downstream). When the pressure difference is smaller than a preset threshold pressure, the discharge check valve 57 shuts off the space between the discharge chamber 52 and the discharge passage 55, and the refrigerant flows from the discharge passage 55 to the discharge chamber 52. Prevent movement. On the other hand, when the pressure difference is larger than the threshold pressure, the discharge check valve 57 makes the discharge chamber 52 and the discharge passage 55 communicate with each other.
Therefore, the high-pressure side refrigerant discharged from the discharge chamber 52 to the discharge-side external refrigerant circuit through the discharge passage 55 and the discharge port 56 is prevented from flowing backward by the discharge check valve 57.

(Drive shaft)
The drive shaft 6 is disposed inside the front housing 3 and the cylinder block 2, and both ends are rotatably supported by the front housing 3 and the cylinder block 2.
One end of the drive shaft 6 is inserted into the center bore 22. A first slide bearing 61 is arranged between the drive shaft 6 and the center bore 22.
An end surface of the drive shaft 6 on the side facing the valve plate 4 is supported by an annular thrust plate 62.
The contact state (gap) between the drive shaft 6 and the thrust plate 62 is adjusted by the attachment state of the adjustment screw 63 to the cylinder block 2.
The adjusting screw 63 is formed in an annular shape, and has a male screw (not shown) formed on an outer diameter surface. On the surface of the center bore 22 that faces the outer diameter surface of the adjustment screw 63, a female screw (not shown) that fits with a male screw formed on the adjustment screw 63 is formed.

Therefore, the adjusting screw 63 is disposed inside the center bore 22 at a position closer to the valve plate 4 than the drive shaft 6 by fitting a male screw to the female screw of the center bore 22.
Further, as shown in FIG. 4, the gap portion of the adjustment screw 63 is formed in a hexagonal shape.
The adjusting screw 63 is formed with a screw-side passage 63 a that allows a surface of the adjusting screw 63 facing the drive shaft 6 to communicate with an outer diameter surface of the adjusting screw 63.
The screw-side passage 63a is formed in a shape in which a part of a surface of the adjusting screw 63 facing the drive shaft 6 is cut away when viewed from the axial direction of the drive shaft 6. Therefore, a portion of the surface of the adjusting screw 63 facing the drive shaft 6 where the screw side passage 63 a is not formed is in contact with the thrust plate 62.

A part of the other end of the drive shaft 6 projects outside the front housing 3 and is connected to a power transmission device (not shown). The power transmission device is connected to a driving force generating source (not shown) such as an engine via a belt. Therefore, when the driving force generated by the driving force generation source is transmitted to the power transmission device, the drive shaft 6 can rotate in synchronization with the rotation of the power transmission device.
A second sliding bearing 64 and a shaft sealing device 65 are arranged between the drive shaft 6 and the front housing 3. The second sliding bearing 64 supports the drive shaft 6 rotatably in the radial direction. Further, a load in the thrust direction toward the other end of the drive shaft 6 is supported by a thrust bearing 66 via the rotor 32.

Therefore, the connected body formed by the drive shaft 6 and the rotor 32 is supported by the first sliding bearing 61 and the second sliding bearing 64 so as to be rotatable in the radial direction, and the thrust plate 62 and the thrust bearing 66 provide thrust. It is supported so that it can rotate in the direction. One end (rear side) of the drive shaft 6 is inserted into the center bore 22 and supported by the cylinder block 2, and the other end (front side) of the drive shaft 6 is supported by the front housing 3.
The shaft sealing device 65 blocks the inside of the crank chamber 30 from the external space.
Note that lubricating oil (not shown) is sealed inside the variable capacity compressor 1 and the oil is stirred when the drive shaft 6 rotates. When the refrigerant moves inside the variable displacement compressor 1, oil moves together with the refrigerant, and the inside of the variable displacement compressor 1 is lubricated.

(Supply passage)
The supply passage 7 communicates the discharge chamber 52 with the crank chamber 30 and is a path for supplying the refrigerant in the discharge chamber 52 to the crank chamber 30.
2, the supply passage 7 includes a head-side supply passage forming portion 71, a plate-side supply passage forming portion 72, and a block-side supply passage forming portion 73.
The head-side supply passage forming portion 71 is a passage formed in the cylinder head 5 in the supply passage 7, and a portion of the supply passage 7 for discharging the refrigerant supplied from the discharge chamber 52 and a plate-side supply passage formation portion. The section 72 is communicated with the section 72.
The plate-side supply passage forming portion 72 is a portion of the supply passage 7 formed in the valve plate 4, and communicates the head-side supply passage forming portion 71 with the valve chamber 100. In the valve plate 4, a throttle passage 74 that connects the plate-side supply passage forming portion 72 of the supply passage 7 with the suction chamber 51 is formed. A detailed description of the valve chamber 100 will be described later.

The block-side supply passage forming portion 73 is a passage formed in the cylinder block 2 in the supply passage 7 and communicates the plate-side supply passage forming portion 72 with the crank chamber 30. Further, a part of the block-side supply passage forming portion 73 communicates with the center bore 22.
A check valve 75 is disposed at an end of the block-side supply passage forming portion 73 on the side of the crank chamber 30. That is, the throttle passage 74 allows the supply passage between the first control valve 9 and the check valve 75 to communicate with the suction chamber 51.

The check valve 75 operates in response to a pressure difference between the supply passage between the first control valve 9 (upstream side) and the check valve 75 and the crank chamber 30 (downstream side). When the pressure in the supply passage between the first control valve 9 and the check valve 75 becomes lower than the pressure in the crank chamber 30, the check valve 75 establishes a connection between the crank chamber 30 and the first control valve 9. It shuts off and prevents the movement of the refrigerant from the crank chamber 30 to the first control valve 9. On the other hand, when the pressure in the crank chamber 30 becomes lower than the pressure in the supply passage between the first control valve 9 and the check valve 75, the check valve 75 establishes a connection between the first control valve 9 and the crank chamber 30. Communicate.
That is, the check valve 75 is disposed closer to the crank chamber 30 than the first control valve 9 in the supply passage 7 and prevents the refrigerant from moving from the crank chamber 30 to the first control valve 9.

(Discharge passage)
The discharge passage 8 connects the crank chamber 30 and the suction chamber 51 and is a path for discharging the refrigerant in the crank chamber 30 to the suction chamber 51.
Further, the discharge passage 8 includes an in-shaft passage 81, a block-side discharge passage forming portion 82, and a plate-side discharge passage forming portion 83.
The in-shaft passage 81 is a passage formed in the drive shaft 6 in the discharge passage 8. That is, a part of the discharge passage 8 is formed inside the drive shaft 6.
One end of the in-shaft passage 81 is open to the side surface of the drive shaft 6 and communicates with the crank chamber 30. The other end of the in-shaft passage 81 is open at the end face of the drive shaft 6 on the side facing the valve plate 4, and communicates with a part of the center bore 22 via a screw-side passage 63 a, and has an adjusting screw 63. It communicates with a part of the valve chamber 100 via the gap. Therefore, the discharge passage 8 includes a part of the valve chamber 100.

Therefore, the shaft passage 81 communicates the crank chamber 30 with the region of the center bore 22 on the valve plate 4 side.
The block-side discharge passage forming portion 82 is a passage formed in the cylinder block 2 of the discharge passage 8, and includes a throttle 82a, an expansion portion 82b, and a discharge portion 82c.
The throttle 82a is formed in a shape in which a part of the surface of the cylinder block 2 that faces the valve plate 4 is cut away, and always communicates the in-shaft passage 81 and the expansion portion 82b.

The extension portion 82b is a passage formed between the cylinder bore 21 and the center bore 22 in the cylinder block 2, and communicates the throttle 82a with the discharge portion 82c.
That is, the expansion portion 82b of the discharge passage 8 is provided at a position closer to the crank chamber 30 than the valve chamber 100, communicates with the third port P3, and has a larger flow path cross-sectional area than the third port P3. . The description of the third port P3 will be described later.
The discharge portion 82c is a passage formed in the cylinder block 2 at a position farther from the crank chamber 30 than the expansion portion 82b, and communicates the expansion portion 82b with the plate-side discharge passage formation portion 83.

That is, the discharge portion 82c of the discharge passage 8 is disposed outside of the valve chamber 100 in the radial direction (radial direction of the drive shaft 6) as viewed from the axial direction of the drive shaft 6, and the expansion portion 82b and the suction chamber 51 And the cross-sectional area of the flow path is smaller than that of the expanded portion 82b.
The block-side discharge passage forming portion 82 is formed, for example, by closing an opening of the expansion portion 82b on the crank chamber 30 side with the closing member 84 in the center bore 22.
The plate-side discharge passage forming portion 83 is an opening formed in the valve plate 4 of the discharge passage 8 and communicates the discharge portion 82 c with the suction chamber 51.

(First control valve)
The first control valve 9 connects the discharge chamber 52 and the crank chamber 30 inside the cylinder head 5, and is disposed in the supply passage 7.
Further, the first control valve 9 can adjust the opening degree (cross-sectional area) of the supply passage 7.
By adjusting the opening degree of the supply passage 7 by the first control valve 9, it is possible to control the amount of refrigerant introduced from the discharge chamber 52 to the crank chamber 30. Therefore, by adjusting the opening degree of the supply passage 7 by the first control valve 9 to change the pressure of the crank chamber 30 and change the inclination angle of the swash plate 31, the stroke of the piston 23 can be changed. It becomes. When the stroke of the piston 23 is changed, the discharge capacity (flow rate of the discharged refrigerant) of the variable displacement compressor 1 can be variably controlled.

That is, the variable displacement compressor 1 changes the inclination of the swash plate 31 by changing the pressure of the crank chamber 30 by adjusting the opening of the first control valve 9, and adjusts the stroke of the piston 23. Further, the variable displacement compressor 1 compresses the refrigerant drawn into the cylinder bore 21 from the suction chamber 51 by the piston 23 whose stroke has been adjusted, and discharges the compressed refrigerant to the discharge chamber 52.
For example, when the air conditioner is operating, that is, when the variable displacement compressor 1 is operating, the energization amount of the solenoid built in the first control valve 9 is adjusted based on a signal received from outside. You. Thus, the discharge displacement of the variable displacement compressor 1 is variably controlled so that the pressure in the suction chamber 51 becomes a predetermined value. At this time, the first control valve 9 can control the suction pressure to an optimum value according to the external environment.
Also, for example, when the air conditioner is not operating, that is, when the variable displacement compressor 1 is not operating, the supply passage 7 is forcibly opened by not energizing the solenoid built in the first control valve 9. Then, the discharge displacement of the variable displacement compressor 1 is controlled to a minimum.

(Second control valve)
The second control valve 10 is housed in the center bore 22 between the one end of the drive shaft 6 and the valve plate 4, and is movably accommodated in the valve room 100 along the axial direction of the drive shaft 6. The valve element 110 is provided.
(Valve room)
The valve chamber 100 is formed by a part of the center bore 22 on the side closer to the valve plate 4.
Further, the valve chamber 100 is a space disposed between the one end of the drive shaft 6 and the valve plate 4 in the center bore 22 as shown in FIG. One end of the drive shaft 6 is an end on the side facing the valve plate 4.
Further, the valve chamber 100 has a first wall surface 101, a second wall surface 102, a peripheral wall surface 103, a first port P1, a second port P2, and a third port P3. Communicates with the other end.

Further, a passage is formed between the valve chamber 100 and the in-shaft passage 81 by a gap part of the thrust plate 62 and a gap part of the adjustment screw 63. The inner diameter of the gap portion of the thrust plate 62 is larger than the inner diameter of the axial passage 81. The inner diameter of the gap of the adjusting screw 63 is larger than the inner diameter of the gap of the thrust plate 62.
The first wall surface 101 is a wall surface on the side closer to the valve plate 4 in the valve chamber 100, and constitutes a wall surface arranged on one side (rear side) in the moving direction of the valve body 110.

In the first embodiment, as an example, a case in which the first wall surface 101 is formed by a suction valve forming plate 104 on which a suction valve (not shown) is formed will be described. The suction valve forming plate 104 is a plate-shaped member arranged between the cylinder block 2 and the valve plate 4.
The second wall surface 102 is a wall surface facing the first wall surface 101 in the axial direction of the drive shaft 6, and constitutes a wall surface arranged on the other side (front side) in the moving direction of the valve element 110.
The first port P 1 is an opening that opens to the first wall surface 101 and communicates a region between the first control valve 9 and the check valve 75 in the supply passage 7 with the valve chamber 100. That is, the first port P 1 opens to the first wall surface 101 and communicates with a region in the supply passage 7 between the first control valve 9 and the check valve 75.

The second port P 2 is an opening that opens to the second wall surface 102, and communicates the gap of the adjustment screw 63 with the valve chamber 100. That is, the second port P 2 is an opening communicating with the crank chamber 30 through a part of the discharge passage 8. The second port P2 communicates with the crank chamber 30 via the shaft passage 81.
In addition, as shown in FIG. 4, the second port P 2 includes a region of the center bore 22 where the drive shaft 6 is arranged, when viewed from the axial direction of the drive shaft 6.

The third port P3 is an opening that opens to the second wall surface 102 and that allows the expansion portion 82b to communicate with the valve chamber 100. That is, the third port P3 is an opening communicating with the suction chamber 51 via a part of the discharge passage 8.
As shown in FIG. 4, the third port P 3 is disposed outside the area of the center bore 22 where the drive shaft 6 is disposed, when viewed from the axial direction of the drive shaft 6.
The peripheral wall surface 103 is a wall surface that connects the first wall surface 101 and the second wall surface 102, and is formed in an annular shape when viewed from the axial direction of the drive shaft 6.

A part of the peripheral wall surface 103 communicates with the block-side supply passage forming portion 73.
As described above, the supply passage 7 is formed in the cylinder block 2 through a path different from the valve chamber 100 and the center bore 22, and has a block-side supply path connected to the crank chamber 30 and the valve chamber 100. In addition, the supply passage 7 is formed on the first wall surface 101 and connected to the plate-side supply passage connected to the valve chamber 100 via the first port P1, and to the plate-side supply passage and the first control valve 9. It has a head side supply passage.

(Valve)
The valve body 110 is formed in a disk shape.
In addition, the valve chamber 100 can be formed using a necessary space, for example, in the operation of disposing the drive shaft 6 and the thrust plate 62 in the center bore 22 and attaching the adjusting screw 63 to the cylinder block 2. . For this reason, the valve chamber 100 is provided in the variable displacement compressor 1 instead of a space formed as a dedicated storage chamber for disposing the second control valve 10 (valve element 110) inside the variable displacement compressor 1. This is a configuration that can be formed using an existing configuration.
As a material for forming the valve body 110, for example, a metal material or a resin material can be used. However, in order to reduce the weight of the valve body 110, a resin material is used as a material for forming the valve body 110. Is preferred. When the valve body 110 is formed of a resin material, for example, a polyphenylene sulfide resin, a nylon (polyamide) resin, or the like can be used as the resin material.

The thickness direction of the valve body 110 is parallel to the axial direction of the drive shaft 6.
The thickness of the valve body 110 (the length in the left-right direction in FIGS. 1 and 5) is the length along the axial direction of the drive shaft 6 of the valve chamber 100 (the left-right direction in FIGS. 1 and 5). Length).
Further, as shown in FIG. 5, the valve body 110 includes a large diameter portion 110a and a small diameter portion 110b.
The large diameter portion 110a is located closer to the drive shaft 6 than the small diameter portion 110b.
The outer diameter of the large diameter portion 110a is smaller than the inner diameter of the peripheral wall surface 103.
In the large-diameter portion 110a, a second concave portion 112a is formed on a second pressure receiving surface 112 which is a surface facing the drive shaft 6.
The bottom surface of the second concave portion 112a faces the axial passage 81 when viewed from the axial direction of the drive shaft 6.
A part of the second pressure receiving surface 112 where the second concave portion 112a is not formed faces the third port P3 and the throttle 82a when viewed from the axial direction of the drive shaft 6.
Therefore, the second pressure receiving surface 112 is a surface facing the second wall surface 102.

The small diameter portion 110b is continuous with the large diameter portion 110a, and is disposed closer to the valve plate 4 than the large diameter portion 110a.
The outer diameter of the small diameter portion 110b is smaller than the outer diameter of the large diameter portion 110a. The center of the circle formed by the small diameter portion 110b and the center of the circle formed by the large diameter portion 110a overlap when viewed from the axial direction of the drive shaft 6.
Of the small diameter portion 110b, a first concave portion 111a is formed on a first pressure receiving surface 111 which is a surface facing the valve plate 4.
The bottom surface of the first recess 111a faces the first port P1 when viewed from the axial direction of the drive shaft 6.
Therefore, the first pressure receiving surface 111 is a surface facing the first wall surface 101.
As described above, the valve element 110 includes the first pressure receiving surface 111 which is a surface facing the first wall surface 101 and the second pressure receiving surface 112 which is a surface facing the second wall surface 102.

(Operation / action)
An example of the operation performed by the variable displacement compressor 1 of the first embodiment and the operation will be described with reference to FIGS. 1 to 5 and FIGS. 6 to 8.
When the variable displacement compressor 1 is used, when the rotor 32 and the swash plate 31 rotate by the rotation of the drive shaft 6, the rotation of the drive shaft 6 is converted into reciprocating motion of the piston 23 by the swash plate 31 and the shoe 38, and the cylinder bore 21 Compresses the refrigerant supplied to the inside.
The stroke of the piston 23 inside the cylinder bore 21 is changed by adjusting the opening degree of the supply passage 7 by the first control valve 9.
Here, in the configuration of the first embodiment, a valve body in which the first pressure receiving surface 111 faces the first wall surface 101 and the second pressure receiving surface 112 faces the second wall surface 102 in the valve chamber 100 provided in the cylinder block 2. 110 are accommodated.

When the opening of the supply passage 7 is controlled, when the first control valve 9 opens the supply passage 7, the first control valve 9 passes through the first port P 1 that is applied to the first pressure receiving surface 111 including the first concave portion 111 a and passes through the valve chamber 100. The pressure of the refrigerant moving to increases.
For this reason, the valve element 110 is pressed by the pressure of the refrigerant moving to the valve chamber 100 through the first port P 1, and the valve element 110 moves in a direction away from the valve plate 4.
Thereby, as shown in FIG. 6, the first pressure receiving surface 111 is separated from the first wall surface 101, and the second pressure receiving surface 112 is in contact with the second wall surface 102. In FIG. 6, the flow of the refrigerant is indicated by broken arrows.

When the second pressure receiving surface 112 abuts on the second wall surface 102, the third port P3 is closed by the valve body 110, so that the crank chamber 30 and the suction chamber 51 communicate with each other via the throttle 82a of the discharge passage 8. Thereby, the opening degree of the discharge passage 8 is minimized.
That is, when the first control valve 9 opens the supply passage 7, the pressure of the refrigerant moving to the valve chamber 100 through the first port P 1 is higher than the pressure of the refrigerant in the second port P 2. When it is raised, it contacts the second wall surface 102. Thereby, the in-shaft passage 81 and the expansion portion 82b are communicated only by the throttle 82a, and the opening of the discharge passage 8 is set to the minimum opening larger than zero.

Therefore, when the pressure in the area between the first control valve 9 and the check valve 75 in the supply passage 7 is higher than the pressure in the crank chamber 30, the valve body 110 contacts the second wall surface 102 and the second port By closing P2 and the third port P3, the opening degree of the discharge passage 8 is minimized.
The throttle 82a provided in the discharge passage 8 always connects the second port P2 and the third port P3.
When the first pressure receiving surface 111 is separated from the first wall surface 101, the refrigerant flows from the valve chamber 100 to the check valve 75 through the supply passage 7, and the pressure on the inlet side of the check valve 75 increases. Therefore, the check valve 75 opens the supply passage 7, and the refrigerant is supplied to the crank chamber 30.

When the first control valve 9 closes the supply passage 7, immediately after the first control valve 9 closes the supply passage 7, the supply passage 7 exists between the first control valve 9 and the check valve 75. The refrigerant is discharged into the suction chamber 51 via the throttle passage 74. In addition, the refrigerant existing in the crank chamber 30 flows backward to press the check valve 75, and the check valve 75 closes the supply passage 7, as shown in FIG. Note that, in FIG. 7, similarly to FIG. 6, the flow of the refrigerant is indicated by dashed arrows.
When the check valve 75 closes the supply passage 7, the pressure in the valve chamber 100 becomes equal to the pressure Ps in the suction chamber 51, the pressure in the suction chamber 51 acts on the first pressure receiving face 111, and the pressure in the second pressure receiving face 112. The pressure Pc of the crank chamber 30 acts. As a result, a differential pressure (Pc−Ps) between the pressure Pc of the crank chamber 30 and the pressure Ps of the suction chamber 51 acts on the valve body 110.

After the first control valve 9 closes the supply passage 7, when the differential pressure (Pc−Ps) acting on the valve body 110 exceeds a preset threshold pressure, the valve body 110 is moved by the pressure Pc of the crank chamber 30. The second pressure receiving surface 112 is pushed away from the second wall surface 102 as shown in FIG. Note that, in FIG. 8, the flow of the refrigerant is indicated by broken-line arrows as in FIG.
When the first pressure receiving surface 111 abuts on the first wall surface 101, the second port P2 and the third port P3 communicate with each other through the valve body 110 and the second wall surface 102 of the valve chamber 100. , The first port P1 is disconnected from the second port P2 and the third port P3. Thereby, the opening degree of the discharge passage 8 is maximized.

That is, when the first control valve 9 closes the supply passage 7 and the pressure of the refrigerant at the first port P1 becomes lower than the pressure of the refrigerant at the second port P2, the valve body 110 opens the second wall surface. Move away from 102. Thereby, the opening degree of the discharge passage 8 is maximized by setting the interval between the valve body 110 and the second wall surface 102 to the maximum value.
Therefore, when the pressure in the area between the first control valve 9 and the check valve 75 in the supply passage 7 is lower than the pressure in the crank chamber 30, the valve body 110 separates from the second wall surface 102 and By opening P2 and the third port P3, the opening degree of the discharge passage 8 is maximized.

When pressure is applied to the second pressure receiving surface 112 including the second concave portion 112a, the valve body 110 moves in a direction away from the drive shaft 6. When pressure is applied to the first pressure receiving surface 111 including the first concave portion 111a, the valve body 110 moves in a direction away from the valve plate 4.
As described above, the valve body 110 is configured such that the first wall surface 101 and the second wall surface correspond to the difference between the pressure in the region between the first control valve 9 and the check valve 75 in the supply passage 7 and the pressure in the crank chamber 30. 102 along the axial direction of the drive shaft 6. Further, the outer peripheral surface of the large diameter portion 110a forms a guide surface when the valve element 110 moves inside the valve chamber 100.
That is, the second control valve 10 is arranged in the discharge passage 8, and adjusts the opening degree of the discharge passage 8 according to a change in the pressure of the supply passage 7.
Note that the above-described first embodiment is an example of the present invention, and the present invention is not limited to the above-described first embodiment. Various changes can be made according to the design and the like within a range not departing from the technical idea.

(Effects of the first embodiment)
With the variable capacity compressor 1 of the first embodiment, the following effects can be obtained.
(1) A second control valve 10 for adjusting the opening degree of the discharge passage 8 includes a valve chamber 100 disposed between one end of the drive shaft 6 and the valve plate 4 in the center bore, and a drive shaft 6 connected to the valve chamber 100. The valve body 110 is accommodated so as to be movable along the axial direction. In addition, when the pressure in the region between the first control valve 9 and the check valve 75 in the supply passage 7 is higher than the pressure in the crank chamber 30, the valve body 110 comes into contact with the second wall surface 102 and By closing the second port P2 and the third port P3, the opening degree of the discharge passage 8 is minimized. On the other hand, when the pressure in the area between the first control valve 9 and the check valve 75 in the supply passage 7 is lower than the pressure in the crank chamber 30, the valve body 110 separates from the second wall surface 102 and the second By opening the port P2 and the third port P3, the opening degree of the discharge passage 8 is maximized.
For this reason, the space between one end of the drive shaft 6 and the valve plate 4 in the center bore is defined as a valve chamber 100, and the valve body 110 is accommodated in the valve chamber 100, so that the second control unit is provided inside the variable displacement compressor 1. It is not necessary to provide a dedicated storage chamber for disposing the valve 10.
As a result, it is possible to provide the variable displacement compressor 1 capable of suppressing an increase in the size of the drive shaft 6 in the axial direction.

(2) The supply passage 7 is formed in the cylinder block 2 by a path different from the valve chamber 100 and the center bore 22, and has a block-side supply passage connected to the crank chamber 30 and the valve chamber 100. In addition, the supply passage 7 is formed in the first wall surface 101 and connected to the plate-side supply passage connected to the valve chamber 100 via the first port P1, and to the plate-side supply passage and the first control valve 9. It has a head side supply passage.
As a result, the cylinder block 2, the valve plate 4, and the cylinder head 5, which are the existing configurations of the variable displacement compressor 1, are processed to supply the variable displacement compressor 1 without adding a new configuration. The passage 7 can be formed.

(3) A part of the discharge passage 8 is formed inside the drive shaft 6.
As a result, the discharge passage 8 can be formed using the drive shaft 6 having the existing configuration in the variable displacement compressor 1.
(4) The second port P2 includes an area of the center bore 22 where the drive shaft 6 is disposed, as viewed from the axial direction of the drive shaft 6. In addition, the third port P 3 is disposed outside the area of the center bore 22 where the drive shaft 6 is disposed, as viewed from the axial direction of the drive shaft 6.
As a result, the second port P2 and the third port P3 can be easily provided on the second wall surface 102.

(5) The discharge passage 8 is provided at a position closer to the crank chamber 30 than the valve chamber 100, communicates with the third port P3, and has an expanded portion 82b having a larger flow path cross-sectional area than the third port P3. In addition, the discharge passage 8 is disposed radially outside the valve chamber 100 when viewed from the axial direction of the drive shaft 6 to communicate the extended portion 82b and the suction chamber 51, and to flow more than the extended portion 82b. It has the discharge part 82c with a small road cross-sectional area. Further, the discharge portion 82c is provided at a position farther from the crank chamber 30 than the extension portion 82b.
As a result, even when the third port P3 is provided at a position near the cylinder bore 21 in the center bore 22, the provision of the extension portion 82b allows the third port P3 to be easily connected to the suction chamber 51. It becomes possible.
In addition, in the expansion portion 82b, the flow velocity of the refrigerant moving from the crank chamber 30 to the suction chamber 51 decreases, and the direction in which the refrigerant moves reverses, so that the oil contained in the refrigerant flows out to the suction chamber 51. Can be suppressed.

(6) The discharge passage 8 is provided with a throttle 82a that constantly connects the second port P2 and the third port P3.
As a result, the oil contained in the refrigerant can be supplied between the center bore 22 and the drive shaft 6 regardless of whether the first control valve 9 opens or closes the supply passage 7. 6 can be smoothly performed.
When the second pressure receiving surface 112 of the valve body 110 is in contact with the second wall surface 102, the flow of the refrigerant discharged from the crank chamber 30 to the suction chamber 51 acts on the second pressure receiving surface 112. The two-port P2 is larger than the area of the center bore 22 through which the drive shaft 6 is inserted. For this reason, the flow velocity of the refrigerant discharged from the crank chamber 30 to the suction chamber 51 becomes extremely low, and the force of the flow of the refrigerant pressing the second pressure receiving surface 112 becomes small. It is possible to suppress inadvertent separation from the second wall surface 102.

(7) The second port P2 communicates with the crank chamber 30 via an in-shaft passage 81 that opens on a surface of the drive shaft 6 facing the valve element 110.
As a result, the second port P2 and the crank chamber 30 can be easily communicated.
(8) The valve element 110 includes a second concave portion 112a which is a concave portion formed on the second pressure receiving surface 112, and the bottom surface of the second concave portion 112a faces the axial passage 81.
As a result, the pressure of the refrigerant moving to the valve chamber 100 through the second port P2 can be efficiently received by the second concave portion 112a, and the valve body 110 can be efficiently moved away from the drive shaft 6. Can be moved.

(9) The valve body 110 includes a first concave portion 111a which is a concave portion formed on the first pressure receiving surface 111, and the bottom surface of the first concave portion 111a faces the first port P1.
As a result, the pressure of the refrigerant that moves to the valve chamber 100 through the first port P1 can be efficiently received by the first recess 111a, and the valve body 110 can be efficiently moved away from the valve plate 4. Can be moved.

(Modification of First Embodiment)
(1) In the first embodiment, a part of the discharge passage 8 is formed by the in-shaft passage 81 formed inside the drive shaft 6. However, the present invention is not limited to this. For example, as shown in FIG. Alternatively, the drive shaft 6 may not be provided with the in-shaft passage 81.
In this case, a part of the discharge passage 8 is, for example, a gap formed between the drive shaft 6 and the first sliding bearing 61 (a gap secured for rotating the drive shaft 6) and a cylinder block. 2 may be formed by the block side discharge passage 85 formed.
The block-side discharge passage 85 is a passage that allows the center bore 22 to communicate with the expansion portion 82b.
Note that, in FIG. 9, the flow of the refrigerant is indicated by broken-line arrows as in FIG.

DESCRIPTION OF SYMBOLS 1 ... Variable capacity compressor, 2 ... Cylinder block, 3 ... Front housing, 4 ... Valve plate, 5 ... Cylinder head, 6 ... Drive shaft, 7 ... Supply passage, 8 ... Discharge passage, 9 ... First control valve, 10 ... second control valve, 11 ... through bolt, 21 ... cylinder bore, 22 ... center bore, 23 ... piston, 30 ... crank chamber, 31 ... swash plate, 32 ... rotor, 33 ... link mechanism, 33a ... first arm, 33b ... Second arm, 33c link arm, 33d first connection pin, 33e second connection pin, 34 through hole, 35 inclination decreasing spring, 36 spring supporting member, 37 inclination increasing spring, 38 shoe 41 ... discharge hole, 42 ... suction hole, 51 ... suction chamber, 52 ... discharge chamber, 53 ... suction port, 54 ... suction passage, 55 ... discharge passage, 56 ... discharge port, 57 ... discharge check valve, 61 ... One slip Receiver, 62: thrust plate, 63: adjusting screw, 63a, 64: second sliding bearing, 65: shaft sealing device, 66: thrust bearing, 71: head side supply passage forming part, 72: plate side supply passage forming part 73, block-side supply passage forming portion, 74, throttle passage, 75, check valve, 81, axial passage, 82, block-side discharge passage forming portion, 82a, throttle, 82b, expansion portion, 82c, discharge portion, 83: plate side discharge passage forming portion, 84: closing member, 85 ... block side discharge passage, 100 ... valve chamber, 101 ... first wall surface, 102 ... second wall surface, 103 ... peripheral wall surface, 104 ... suction valve forming plate, 110: valve element, 110a: large diameter portion, 110b: small diameter portion, 111: first pressure receiving surface, 111a: first concave portion, 112: second pressure receiving surface, 112a: second concave portion, P1: first port, P2 ... Second port, P3 ... No. Port

Claims

A plurality of cylinder bores arranged in a ring, a center bore disposed inside the plurality of cylinder bores, and a cylinder block in which a partition is formed;
A valve plate that closes one end of the cylinder block and has a discharge hole and a suction hole that communicate with the cylinder bore;
A front housing that closes the other end of the cylinder block and defines a crank chamber together with the cylinder block;
A cylinder head having a suction chamber provided opposite to the cylinder block with the valve plate interposed therebetween and having a suction chamber disposed at the center, and a discharge chamber disposed annularly outside the suction chamber; ,
A drive shaft having one end inserted into the center bore and supported by the cylinder block, and the other end supported by the front housing;
A piston disposed in each of the plurality of cylinder bores and reciprocating in the axial direction of the drive shaft;
A rotor fixed to the drive shaft and rotating integrally with the drive shaft,
A swash plate connected to the rotor, and slidably attached to the drive shaft such that the tilt angle with respect to the axis of the drive shaft is variable by rotating synchronously with the rotor;
A conversion mechanism for converting the rotation of the swash plate into a reciprocating motion of the piston,
A supply passage for communicating the discharge chamber and the crank chamber,
A first control valve arranged in the supply passage, and adjusting an opening degree of the supply passage;
A discharge passage communicating the crank chamber and the suction chamber,
A second control valve arranged in the discharge passage and adjusting an opening degree of the discharge passage;
A check valve disposed on the side closer to the crank chamber than the first control valve in the supply passage, and preventing movement of refrigerant from the crank chamber to the first control valve;
A throttle passage that communicates a supply passage between the first control valve and the check valve with the suction chamber, wherein the pressure in the crank chamber is changed by adjusting an opening of the first control valve. Changing the inclination angle of the swash plate to adjust the stroke of the piston, and further compressing the refrigerant drawn from the suction chamber into the cylinder bore by the piston whose stroke has been adjusted, and discharging the compressed refrigerant to the discharge chamber. A capacity compressor,
The second control valve includes a valve chamber disposed between the one end of the drive shaft and the valve plate in the center bore, and is housed in the valve chamber so as to be movable in an axial direction of the drive shaft. And a valve body,
The valve chamber is a first wall disposed on one side in the moving direction of the valve body, a second wall disposed on the other side in the moving direction of the valve body, and opened to the first wall. A first port communicating with a region between the first control valve and the check valve in a supply passage, and a first port opening to the second wall surface and communicating with the crank chamber through a part of the discharge passage. A second port, and a third port that opens to the second wall surface and communicates with the suction chamber through a part of the discharge passage,
The valve body includes a first pressure receiving surface that is a surface facing the first wall surface, and a second pressure receiving surface that is a surface facing the second wall surface, and the first control valve in the supply passage. Move between the first wall surface and the second wall surface according to the difference between the pressure in the area between the check valve and the pressure in the crank chamber,
When the pressure in a region between the first control valve and the check valve in the supply passage is higher than the pressure of the crank chamber, the valve body contacts the second wall surface and the second port and By closing the third port to minimize the opening of the discharge passage,
When the pressure in the region between the first control valve and the check valve in the supply passage is lower than the pressure of the crank chamber, the valve body is separated from the second wall surface and the second port and A variable displacement compressor wherein the opening of the discharge passage is maximized by opening the third port.
The supply passage, the valve chamber, is formed in the cylinder block in a different path from the center bore, and a block-side supply passage connected to the crank chamber and the valve chamber, formed in the first wall surface, And a plate-side supply passage connected to the valve chamber via the first port, and a head-side supply passage connected to the plate-side supply passage and the first control valve. The variable displacement compressor according to claim 1.
The second port, when viewed from the axial direction of the drive shaft, includes an area of the center bore where the drive shaft is disposed,
The said 3rd port is arrange | positioned outside the area | region where the said drive shaft is arrange | positioned among the said center bores, when seen from the axial direction of the said drive shaft, The Claim 1 or Claim 2 characterized by the above-mentioned. The variable capacity compressor described.
The discharge passage is provided at a position closer to the crank chamber than the valve chamber, communicates with the third port, and has an expanded portion having a larger flow path cross-sectional area than the third port, and an axis of the drive shaft. A discharge section disposed radially outward of the valve chamber when viewed from the direction to communicate the expansion section and the suction chamber, and having a smaller flow path cross-sectional area than the expansion section;
The variable displacement compressor according to any one of claims 1 to 3, wherein the discharge unit is provided at a position farther from the crank chamber than the expansion unit.
The variable displacement compressor according to any one of claims 1 to 4, wherein the discharge passage includes a throttle that communicates the second port and the third port.
The said 2nd port is communicating with the said crank chamber via the axial passage which opens in the surface which opposes the said valve body of the said drive shaft, The Claim 1 characterized by the above-mentioned. 2. The variable displacement compressor according to claim 1.
The second pressure receiving surface is opposed to the drive shaft,
The valve body includes a second concave portion that is a concave portion formed on the second pressure receiving surface,
7. The variable displacement compressor according to claim 6, wherein a bottom surface of the second concave portion faces the axial passage.
The first pressure receiving surface faces the valve plate,
The valve body includes a first concave portion that is a concave portion formed on the first pressure receiving surface,
The variable displacement compressor according to any one of claims 1 to 7, wherein a bottom surface of the first concave portion faces the first port.