JPH0617028Y2 - Variable capacity vane rotary compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to improvement of a variable capacity vane rotary compressor used as a refrigerant compressor of an air conditioner for an automobile, for example.

(Prior Art) Generally, in a refrigerant compressor of an air conditioner for an automobile, the amount of discharge is variable in order to always maintain a comfortable environment in the vehicle by changing the circulation amount of the refrigerant gas according to the load of the air conditioner. A variable capacity vane rotary compressor that can be controlled is used.

As a conventional variable capacity vane type rotary compressor of this type,
For example, it is known that a front plate is provided with an arc-shaped bypass port that opens in substantially the entire area of the working chamber, and a movable plate having an arc-shaped bypass opening is provided between the front plate and the cam ring. In this device, the discharge amount is variably controlled by rotating the movable plate by an electric motor provided inside or outside the compressor to change the position of the bypass opening.

By the way, the applicant of the present invention has a structure in which the variable capacity vane type rotary compressor as described above drives the movable plate by an electric motor, so that the fuel efficiency of the engine is deteriorated and the manufacturing cost of the device is increased. In view of the above, a variable capacity vane type rotary compressor in which a movable plate is rotated by suction pressure or discharge pressure of the compressor has already been applied (Japanese Patent Application No. 61-2.
No. 25563).

In the variable displacement vane type rotary compressor of this prior application, the control member is moved by the change of the suction pressure of the compressor to drive the control valve, and the movable plate is rotated by communicating the suction pressure or the discharge pressure with the actuator. As a result, an appropriate compressor discharge amount according to the load of the air conditioner can be automatically secured.

(Problems to be solved by the invention) However, in such a variable capacity vane rotary compressor of the prior application, when the suction pressure of the compressor fluctuates with respect to a preset value, the suction pressure changes. Has a configuration in which the control member drives the control valve to variably control the discharge amount of the compressor so that the set value becomes the set value, and further, there is a mechanism for changing the set value from outside the compressor as necessary. It is not provided, and it is necessary to cope with various load conditions of the air conditioner based on the set value of one suction pressure that is set. For this reason, it has been difficult to ensure proper operation of the air conditioner corresponding to the cooling load. For example, if the intake pressure set value is set to a high value so that the evaporator of the air conditioner does not freeze when the air conditioner has a low load, it will be supplied into the vehicle when the air conditioner has a high load. Since the compressor is controlled so as to reduce the discharge amount before the temperature of the cold air becomes sufficiently low, the cooling capacity of the air conditioner becomes insufficient. In addition, if the set value of suction pressure is set to a low value, sufficient cooling capacity of the air conditioner can be obtained at high load, but troubles such as freezing of the evaporator occur and the air conditioner is suitable for the cooling load. It was difficult to ensure proper operation of the car.

(Object of the Invention) Therefore, the present invention has a drive mechanism that sandwiches the control valve and faces the control member, and drives the pressing member by the drive mechanism to urge the first valve body of the control valve in the valve closing direction. By changing the biasing force of the elastic member, the set value of the suction pressure is changed from the outside of the compressor as needed, and the proper operation of the air conditioner corresponding to the cooling load is ensured.

(Means for Solving Problems) In order to achieve the above object, a variable capacity vane type rotary compressor according to the present invention has a cam ring in which a rotor is housed and a compression chamber is defined by the rotor, and both openings of the cam ring. It is defined by a front plate and a rear plate that seal the ends, a bottomed cylindrical housing that houses the rotor, the cam ring, the front plate and the rear plate, and a head cover and the front plate that seal the open end of the housing. A bypass port, which is formed in the suction chamber and the front plate and opens in the compression chamber to communicate the compression chamber with the suction chamber, is rotatably provided between the front plate and the cam ring to change the opening position of the bypass port. A movable plate having a bypass opening and an actuator for rotating the movable plate are connected to face each other. A first valve body and a second valve body which are connected to each other and whose opening and closing directions are opposite to each other.
A control valve having a valve body for supplying the discharge pressure and the suction pressure of the compressor to the actuator by the first valve body and the second valve body, respectively, to operate the actuator; and engaging a second valve body of the control valve. A control member that drives the control valve according to a change in suction pressure, and when the suction pressure of the compressor fluctuates with respect to a preset set value of suction pressure, the movable plate is rotated to change the suction pressure. In a variable displacement vane type rotary compressor that changes a discharge amount of a compressor so as to be a set value, the control valve is provided so as to face the control member,
The first valve body is interposed between the drive mechanism that engages one end of the pressing member to drive the pressing member toward the control valve, and the other end of the pressing member and the first valve body of the control valve. An elastic member for urging in the valve closing direction is provided, and the pressing member is driven by the drive mechanism to change the urging force for urging the first valve body by the elastic member, and the first valve body discharge pressure of the compressor. And the suction pressure of the compressor is applied to the second valve body to change the set value of the suction pressure.

(Operation) In the present invention, the drive mechanism is provided so as to sandwich the control valve and face the control member, and the pressing member is driven by the drive mechanism to urge the first valve body of the control valve in the valve closing direction. Is changed according to a set value outside the compressor, and the movable plate is rotated by operating the actuator by the discharge pressure or the suction pressure of the compressor. Therefore, the appropriate operation of the air conditioner corresponding to the cooling load is ensured without increasing the power consumption.

(Example) Hereinafter, the present invention will be described with reference to the drawings.

1 to 5 are views showing an embodiment of the present invention. First,
In FIG. 2, reference numeral 1 is a cylindrical cam ring, and a cam surface 1a having a substantially elliptical cross section is formed on the inner circumference of the cam ring 1. A rotor 2 having a support shaft 2a, 2b integrally formed therein is housed in the cam ring 1, and the rotor 2 defines a pair of compression chambers 3 in the cam ring 1. The front side (left side in FIG. 1) and the rear side (first side) of the cam ring 1
A front plate 4 and a rear plate 5 are fixed to each other (right side in the drawing), and both front and rear opening ends of the cam ring 1 are sealed by the front plate 4 and the rear plate 5, respectively. Reference numeral 6 denotes a bottomed cylindrical housing in which a cam ring 1, a rotor 2, a front plate 4 and a rear plate 5 are housed. A head cover 7 is provided on the front side of the housing 6, and the head cover 7 seals the open end of the housing 6 and defines a suction chamber 8 between the head cover 7 and the front plate 4. As shown in FIG. 2, the front plate 4 is formed with a pair of arc-shaped bypass ports 9 that are opened along the outer periphery over substantially the entire area of the compression chamber 3, and the bypass port 9 causes the compression chamber 3 to move into the suction chamber 8. Is in communication with. A circular movable plate 10 is interposed between the front plate 4 and the cam ring 1, and the outer periphery 10a of the movable plate 10 is interposed.
Is slidably in contact with the circular inner periphery 4b of the ring plate 4a provided on the cam ring 1 side of the front plate 4 and the movable plate 10
Is rotatably supported around a support shaft 2a of the rotor 2. A pair of bypass openings 11 formed by cutting out in a fan shape along the outer periphery of the movable plate 10 are formed in the outer peripheral portion of the movable plate 10, and the compression chamber 3 and the suction chamber 8 are separated by the rotation of the movable plate 10. The opening position of the bypass port 9 that communicates is changed. Although not shown, a plurality of vanes are fitted into the cam ring 1 so as to slide in and out so that the tip of the vane is in sliding contact with the cam surface 1a. As shown in FIG. 2, the refrigerant gas introduced into the suction chamber 8 through the inlet 12 penetrates the front plate 4 and the cam ring 1 in the axial direction, and passes through a pair of suction ports 13 which are opened at the cam surface 1a at a plurality of positions. It is supplied to the compression chamber 3. The refrigerant gas supplied to the compression chamber 3 is compressed in the compression chamber 3, introduced into the discharge chamber 14 formed between the rear plate 5 and the housing 6, and further discharged through a discharge port 15 provided in the housing 6 through a discharge port 15 (not shown). Is supplied to the air conditioner. Then, in FIG. 5, when the movable plate 10 rotates in the clockwise direction, the bypass opening
11 moves, the opening position of the bypass port 9 changes, the compression start point of the vane in the compression chamber 3 is delayed, and the flow rate of the refrigerant gas bypassed from the compression chamber 3 to the suction chamber 8 increases, When the movable plate 10 rotates in the counterclockwise direction, the discharge amount of the compressor decreases, the compression start point of the vane becomes faster, and the flow rate of the refrigerant gas bypassed becomes smaller. The amount increases.

In FIG. 1, reference numeral 16 is an actuator which is provided on the head cover 7 and which rotates the movable plate 10 to change the discharge amount of the compressor as described above. As shown in FIG. 5, the actuator 16 is slidably fitted into a cylinder 17 and a cylinder 17 formed in the head cover 7 at right angles to the axis of the rotor 2, and the cylinder 17 is inserted into the first cylinder chamber 17a. , The piston 18 defined in the second cylinder chamber 17b, the first of the cylinder 17
A guide rod 19 protruding from the inner surface 17c on the cylinder chamber 17a side toward the piston 18 and loosely fitted in a guide hole 18a bored axially in the center of the piston 18 and the inner surface 17c of the cylinder 17 and the guide hole of the piston 18. The return spring 20 is interposed between the bottom surface 18b of the 18a and biases the piston 18 toward the second cylinder chamber 17b. Cylinder 17
The open end of the second cylinder chamber 17b is sealed by a flange 17d, and the guide rod 19 has a function of guiding the return spring 20 when the piston 18 moves up and down. A link arm 21 is provided on the front plate 4 side of the piston 18, and a pin 22 provided so as to project from the outer circumference of the head of the piston 18 penetrates one end of the link arm 21 to rotate the link arm 21. The link arm 21 is freely connected to the piston 18, and the other end of the link arm 21 is penetrated by a pin 23 projecting from the outer peripheral portion of the movable plate 10 through one of the bypass ports 9 of the front plate 4. It is rotatably connected to the movable plate 10. Then, the link arm 21 connects the piston 18 and the movable plate 10, and the piston 18
Is moved in the axial direction of the cylinder 17, the movable plate 10 moves to the pin 2
2. It is rotated via the link arm 21 and the pin 23.
Further, a long groove 24 is extended along the cylinder 17 between the cylinder 17 of the head cover 7 and the front plate 4, and
The link arm 21 is fitted in the 24, and the width of the long groove 24 prevents the link arm 21 from freely rotating when the link arm 21 moves by the piston 18 to rotate the movable plate 10. It is formed wide enough so that it does not exist. Further, a guide window 25 is provided between the cylinder 17 and the long groove 24. The pin 22 of the cylinder 18 penetrates the guide window 25 so that the guide window 25 guides the movement of the pin 22 and the cylinder 17 passes through the long groove 24. The first cylinder chamber 17a is communicated with the suction chamber 8, and the suction pressure of the compressor is introduced into the first cylinder chamber 17a.

In FIGS. 3 and 4, reference numeral 26 is a control valve provided across the head cover 7, the front plate 4, the ring plate 4a and the cam ring 1 in parallel with the axis of the rotor 2.
The control valve 26 has a ball valve body 27 as a first valve body and a poppet valve body 28 as a second valve body, which are provided to face each other. The ball valve body 27 is fitted and inserted into a cylindrical ball valve chamber 29 provided in the cam ring 1 in parallel with the axis of the rotor 2, and the ball valve chamber 29 is seated in a communication chamber 30 formed in the ring plate 4a. It communicates via 29a. on the other hand,
The poppet valve body 28 comprises a large diameter portion 28a, a medium diameter portion 28b and a small diameter portion 28c which are integrally formed in order toward the ball valve body 27, and are coaxial with the ball valve chamber 29 across the head cover 7 and the front plate 4. Is inserted into a poppet valve chamber 31 provided in the. The poppet valve chamber 31 is formed in the large diameter portion 31a formed on the head cover 7 and the front plate 4,
Medium-diameter portion 31 that communicates with the large-diameter portion 31a via the poppet valve seat 31b
c and similarly formed on the front plate 4 and has a medium diameter portion 3
The small-diameter portion 31d communicates with 1c. The small-diameter portion 31d opens into the communication chamber 30 of the ring plate 4a, and the poppet valve chamber 31 communicates with the communication chamber 30. The ball valve body 27 and the ball valve chamber 29 form a ball valve 32, and the poppet valve body 28 and the poppet valve chamber 31 form a poppet valve 33. Then, the ball valve body 27 abuts the ball valve seat 29a, the communication between the ball valve chamber 29 and the communication chamber 30 is cut off, and the ball valve 32 is closed, so that the ball valve body 27 causes the small diameter part 28c of the poppet valve body 28c. And pushes the poppet valve body 28. Accordingly, the stepped portion 28d formed between the large diameter portion 28a and the medium diameter portion 28b of the poppet valve body 28 is brought into contact with the poppet valve seat 31b so that the large diameter portion 31a of the poppet valve chamber 31.
The poppet valve body 28, which has blocked the communication between the communication chamber 30 and the communication chamber 30, moves to the large diameter portion 31a side to communicate the large diameter portion 31a with the communication chamber 30, and the poppet valve 33 is opened. On the contrary, the step surface of the poppet valve body 28
When 28d contacts the poppet valve seat 31b to close the poppet valve 33, the poppet valve body 28 presses the ball valve body 27 to open the ball valve 32. That is, the ball valve body 27 and the poppet valve body 28 are connected to each other so that the valve opening and closing directions are opposite to each other.

Reference numeral 34 is a bellows as a control member that engages the poppet valve body 28 of the control valve 26 and drives the control valve 26.

The bellows 34 is formed in the head cover 7 coaxially with the ball valve chamber 29 and the poppet valve chamber 31, and the left end in the drawing is fitted into a cylindrical bellows chamber 35 that opens to the outside of the head cover 7. Has one end fixed to a plate member 36 slidably fitted to the left end of the bellows chamber 35. The step on the right end of the bellows chamber 35 in which the bellows 34 is fitted
35a communicates with the large diameter portion 31a of the poppet valve chamber 31 and the other end of the bellows 34 has a poppet valve body 28 through a ball 37.
The large diameter portion 28 a of the control valve 26 is brought into contact with and engaged with the bellows 34, and the bellows 34 is engaged with the poppet valve body 28 of the control valve 26. In addition, the bellows chamber 35
A back plate 38 is provided outside the plate member 36 at the left end part of the back plate 38, and an adjustment screw 39 that penetrates toward the plate member 36 in the axial direction and is screwed is attached to the back plate 38. . Back plate 38
The outer periphery of the plate member 36 is supported by a snap ring 40 fitted and fixed in a ring-shaped groove 7a formed in the head cover 7 along the inner periphery of the bellows chamber 35, and the adjusting screw 39 abuts the plate member 36 so that the plate member 36 36 is the back plate
It is axially supported by 38. Then, the bellows chamber 35 communicates with the suction chamber 8 through a through hole (not shown), and the suction pressure of the compressor is introduced into the bellows chamber 35. Although not shown, a coil spring for urging the bellows 34 to extend in the axial direction is housed in the bellows 34.
Furthermore, since the pressure inside the bellows 34 is kept constant, the bellows 34 expands and contracts in the axial direction as the suction pressure of the compressor changes, and as described above, the bellows 34 becomes the poppet valve body 28 of the control valve 26. Being engaged, the bellows 34 drives the control valve 26 by a change in suction pressure. The plate member 36
The sealing member 41 is interposed between the bellows chamber 35 and the bellows chamber 35, and the bellows chamber 35 is sealed, and the adjusting screw 39 is further rotated so that the axial position of the plate member 36 in the bellows chamber 35 can be adjusted. Has become.

42 faces the bellows 34 across the control valve 26,
Is a cylindrical solenoid provided coaxially with, and the solenoid 42 is fitted and fixed in a solenoid chamber 43 provided on the rear plate 5 side of the cam ring 1. The solenoid 42 constitutes a drive mechanism. 44 is an axially long pin 45
And a column-shaped block 46, the right end of the pin 45 in the figure is slidably fitted in the hollow part of the solenoid 42, and the left end is in contact with the right end of the block 46. . The block 46 is slidably inserted in the ball valve chamber 29 in which the ball valve body 27 of the control valve 26 is inserted, and a coil as an elastic member is provided between the left end portion of the block 46 and the ball valve body 27. The spring 47 is interposed and the coil spring 47 urges the ball valve body 27 in the valve closing direction. When the solenoid 42 is energized, the pin 45 is driven by the electromagnetic force of the solenoid 42 in a direction projecting from the solenoid 42, and the block 46 also moves in the same direction. The initial coil length 1 of the coil spring 47 is reduced to 1 ', and the urging force for urging the ball valve body 27 increases from the initial F to F'. Further, by changing the value of the current supplied to the solenoid 42, the coil length l'of the coil spring 47 can be changed to adjust the urging force F'of the coil spring 47. That is, the solenoid 42
One end of the pressing member 44 (the right end of the pin 45) is engaged with the solenoid 42, and the solenoid 42 drives the pressing member 44 toward the control valve 26, and the other end of the pressing member 44 (the left end of the block 46). The urging force F of the coil spring 47 interposed between the ball valve element 27 and the ball valve body 27 can be changed. Incidentally, 29b is a stepped portion provided between the ball hole 29c and the through hole 29c through which the left end portion of the pin 45 penetrates, and the right end portion of the block 46 abuts on the stepped portion 29b so that the coil spring 47 has an initial position. The coil length (set length) 1 is set. Also, block 46 and ball valve chamber 29
A seal member 48 is interposed between them to seal the inside of the ball valve chamber 29. Further, 45a is a flange portion formed in an intermediate portion of the pin 45, and has a function of a stopper for inserting the pin 45 into the solenoid 42 for positioning. Further, 42a is a lead wire of the solenoid 42, and penetrates the housing 6 to connect the solenoid 42 to a control circuit (not shown) provided outside the compressor, and the control circuit opens and closes the energization of the solenoid 42. At the same time, the current value during energization can be changed.

On the other hand, the ball valve chamber 29 communicates with the discharge chamber 14 through a passage 49 formed in the cam ring 1 and the rear plate 5, and similarly, the communication chamber 30 forms a passage 50 formed in the front plate 4 and the head cover 7. Through actuator
It communicates with 16 second cylinder chambers 17b. Then, when the suction pressure of the compressor changes and becomes large, a compression force that reduces the bellows 34 in the axial direction is generated due to the differential pressure between the suction pressure inside the bellows chamber 35 and the pressure inside the bellows 34, and the coil spring inside the bellows 34 is generated. Bellows 34 shrinks to overcome the urging force of. Along with this, the ball 37 pressed by the bellows 34, the poppet valve body 28 of the control valve 26, and the ball valve body 27 of the control valve 26 are urged by the coil spring 47 in the contracting direction of the bellows 34 as described above. , The ball valve body 27 is closed, and the poppet valve 33 is opened to allow the second cylinder chamber 17b of the actuator 16 to pass through the passage 50, the communication chamber 30, the poppet valve chamber 31, and the bellows chamber 35. Is communicated with the suction chamber 8 and becomes suction pressure. On the contrary, when the suction pressure of the compressor changes and becomes smaller, the urging force of the coil spring in the bellows 34 overcomes the resultant force of the compressive force and the urging force of the coil spring 47 generated by the above-mentioned differential pressure, and the bellows 34 expands. . Along with this, the poppet valve body 28 is driven, the poppet valve 33 is closed, and the communication between the second cylinder 17b and the suction chamber 8 is cut off. At the same time, the ball valve body 27 opens to open the passage 49 in the second cylinder 17b of the actuator 16.
Discharge chamber 14 through ball valve chamber 29, communication chamber 30 and passage 50
Discharge pressure is supplied. Then, in FIG. 5, when the second cylinder chamber 17b of the actuator 16 communicates with the suction chamber 8, the second cylinder chamber 17b has the same pressure as the first cylinder chamber 17a, and the urging force of the return spring 20 causes the piston 18 to move to the first position. 5 descending in the figure, the movable plate 10 is rotated counterclockwise through the pin 22, the link arm 21 and the pin 23,
As described above, the discharge amount of the compressor increases. When the discharge pressure of the compressor is supplied to the second cylinder chamber 17b of the actuator 16, the piston 18 overcomes the combined force of the downward pressing force generated by the suction pressure and the urging force of the return spring 20 and rises to move the movable plate. The 10 is rotated clockwise, and the discharge amount of the compressor is reduced. That is, the bellows 34 drives the control valve 26 by the change of the suction pressure of the compressor,
The control valve 26 can switch and communicate the second cylinder chamber 17b with the high pressure discharge chamber 14 or the low pressure suction chamber 8 of the compressor by the ball valve body 27 and the poppet valve body 28 to operate the actuator 16.

Next, the operation will be described.

In FIGS. 1 and 2, when the rotor 2 is connected to a drive source such as an engine (not shown) and driven to rotate, the refrigerant gas introduced into the suction chamber 8 through the inlet 12 of the head cover 7 is compressed through the suction port 13. It is supplied to the chamber 3, compressed in the compression chamber 3, introduced into the discharge chamber 14, and further supplied to the air conditioner (not shown) through the discharge port 15. At this time, in FIG. 3, the solenoid 42 is de-energized by a control circuit (not shown) and the coil length of the coil spring 47 is set to l. Corresponding to this, the ball valve element of the coil spring 47 is set.
The urging force that urges 27 in the valve closing direction is set to F.
Then, it is caused by the differential pressure between the suction pressure of the compressor supplied into the bellows chamber 35 and the pressure inside the bellows 34, and the urging force of a coil spring (not shown) housed in the bellows 34,
When the extension force P that extends the bellows 34 in the axial direction balances with the urging force F by the discharge pressure that acts to open the coil spring 47 and the poppet valve 33, the suction pressure of the compressor is the urging force F. Becomes smaller as becomes larger, and is uniquely determined by the urging force F. Such a suction pressure value is set as a set value of the suction pressure at which the bellows 34 starts driving the control valve 26 due to the fluctuation of the suction pressure. When the discharge amount of the compressor is too small with respect to the cooling load of the air conditioner and the suction pressure exceeds the above set value, the bellows 34 contracts in the axial direction and the ball valve body 27 causes the coil spring 47 to move. Is pressed to close the ball valve 32, and at the same time, the poppet valve element 28 is driven to open the poppet valve 33. As a result, in FIG. 5, the second cylinder chamber 17b of the actuator 16 communicates with the suction chamber 8 through the control valve 26, and as described above, the piston 18 descends and the movable plate 10 rotates counterclockwise. As a result, the discharge amount of the compressor increases. On the contrary, when the discharge amount of the compressor is excessive and the suction pressure becomes lower than the set value, the bellows 34 extends axially and the poppet valve body 28 causes the bellows 34 to pass through the ball 37 in FIG. Is pressed to close the poppet valve 33, and at the same time, the ball valve body 27 is driven to open the ball valve 32. As a result, the discharge pressure is supplied to the second cylinder chamber 17b of the actuator 16 in FIG.
Rises, the movable plate 10 rotates in the clockwise direction, and the discharge amount of the compressor decreases.

Therefore, for example, when the air conditioner has a low load, the set value of the suction pressure is set to a high value so that the evaporator of the air conditioner does not freeze. That is, the solenoid 42 is turned off so that the coil length l of the coil spring 47 is set to be long. Next, when the air conditioner has a high load, the discharge amount of the compressor increases and we want to continue the operation with the increased discharge amount.Therefore, the bellows 34 causes the control valve 26 The control circuit (not shown) energizes the solenoid 42 so that the compressor discharge amount is reduced and the cooling capacity of the air conditioner is not insufficient. As shown in FIG. The coil length of the coil spring is reduced to l ', and the biasing force of the coil spring 47 is reduced to F'.
To decrease the set value of suction pressure. As a result, the discharge amount of the compressor can be maintained in a state corresponding to the cooling load of the air conditioner. In this case, the control circuit changes the current value to be supplied to the solenoid 42 according to the cooling condition in the vehicle to adjust the coil length l'of the coil spring 47 and appropriately change the set value of the suction pressure to cool the vehicle. The state can be maintained optimally. In the present embodiment, the drive mechanism of the pressing member 44 is configured by the solenoid 42 that electrically operates, but not limited to this, for example, the pressing member 44 of the compressor by using an actuator such as air pressure or hydraulic pressure. Needless to say, it may be configured to be driven from the outside.

As described above, in the present embodiment, the solenoid 42 is provided so as to face the bellows 34 with the control valve 26 sandwiched therebetween, and one end of the pressing member 44 engages with the solenoid 42 so that the pressing member 44 moves the control valve 26.
Driven towards. And the ball valve body of the control valve 26
The coil spring 1 interposed between the spring 27 and the other end of the pressing member 44 adjusts the coil length 1 of the coil spring 47, and the coil spring 47 urges the ball valve body 27 in the valve closing direction. The actuator 16 is operated by the discharge pressure or the suction pressure of the compressor, and the movable plate 10 is rotated. Therefore, it is possible to ensure the proper operation of the air conditioner corresponding to the cooling load without increasing the power consumption. Further, since the bellows 34 is driven by the change in suction pressure and the control valve 26 is controlled without being affected by external factors, the reliability is improved. Further, when the heat load is high and the discharge pressure is high, the movable plate 10 is rotated by the discharge pressure and the suction pressure is controlled to be lower, so that the cooling performance is improved.

(Effects) According to the present invention, the drive mechanism is provided so as to sandwich the control valve and face the control member, and the drive mechanism drives the pressing member to urge the first valve body of the control valve in the valve closing direction. The urging force of the member changes according to the set value outside the compressor, the actuator operates by the discharge pressure or the suction pressure of the compressor, and the movable plate rotates. Therefore, it is possible to ensure proper operation of the air conditioner corresponding to the cooling load without increasing the power consumption. Further, the control member is driven by the change of the suction pressure and controls the control valve without being affected by external factors, so that the reliability can be improved. Further, when the heat load is high and the discharge pressure is high, the movable plate is rotated by the discharge pressure and the suction pressure is controlled to be lower, so that the cooling performance can be improved.

[Brief description of drawings]

1 to 5 are views showing an embodiment of a variable displacement vane type rotary compressor according to the present invention, and FIG. 1 is a front sectional view thereof.
FIG. 2 is a sectional view taken along the line II-II in FIG. 1, FIGS. 3 and 4 are enlarged sectional views of essential parts showing the configurations of the control member, control valve and drive mechanism, and FIG. It is a block diagram which shows a structure and operation | movement of a movable plate. 1 ... Cam ring, 2 ... Rotor, 3 ... Compression chamber, 4 ... Front plate, 5 ... Rear plate, 6 ... Housing, 7 ... Head cover, 8 ... Suction chamber, 9 ... Bypass port, 10 ... Movable plate, 11 ... Bypass opening, 16 ... Actuator, 26 ... Control valve, 27 ... Ball valve body (first valve body), 28 ... Poppet valve body (second valve body), 34 ... Bellows (control member), 42 ... Solenoid (drive mechanism), 44 ... Pressing member, 47 ... Coil spring (elastic member).

Claims (1)

[Scope of utility model registration request] 1. A cam ring in which a rotor is housed and a compression chamber is defined by the rotor, a front plate and a rear plate for sealing both open ends of the cam ring, a rotor, a cam ring, a front plate and a rear plate. A bottomed cylindrical housing that has been housed, a suction chamber defined by a head cover and a front plate that seal the opening end of the housing, and a suction plate that is formed in the front plate and opens into the compression chamber to turn the compression chamber into the suction chamber. A movable plate having a bypass port that is rotatably provided between the bypass port that communicates with the front plate and the cam ring and that changes the opening position of the bypass port, and an actuator that rotates the movable plate face each other. A first valve body and a second valve body, which are connected to each other and whose valve opening and closing directions are opposite to each other.
A control valve having a valve body for supplying the discharge pressure and the suction pressure of the compressor to the actuator by the first valve body and the second valve body, respectively, to operate the actuator; and engaging a second valve body of the control valve. A control member that drives the control valve according to a change in suction pressure, and when the suction pressure of the compressor fluctuates with respect to a preset set value of suction pressure, the movable plate is rotated to change the suction pressure. In a variable displacement vane type rotary compressor that changes a discharge amount of a compressor so as to be a set value, the control valve is provided so as to face the control member,
The first valve body is interposed between the drive mechanism that engages one end of the pressing member to drive the pressing member toward the control valve, and the other end of the pressing member and the first valve body of the control valve. An elastic member for urging in the valve closing direction is provided, and the pressing member is driven by the drive mechanism to change the urging force for urging the first valve body by the elastic member, and the first valve body discharge pressure of the compressor. And a suction pressure of the compressor is applied to the second valve body to change the set value of the suction pressure.