KR970009845B1 - Clutchless half side piston type variable capacity compressor - Google Patents

Abstract

No content.

Description

Single Side Piston Type Variable Capacity Compressor Without Clutch

1 is a side cross-sectional view of the entire compressor of one embodiment embodying the present invention.

2 is a cross-sectional view taken along the line A-A of FIG.

3 is a cross-sectional view taken along the line B-B in FIG.

4 is a cross-sectional view taken along the line C-C in FIG.

5 is a side cross-sectional view of the entire compressor with the swash plate inclination angle minimized.

6 is an enlarged cross-sectional view of the main portion in the rotary valve open position.

7 is an enlarged cross-sectional view of the main portion in the rotary valve closed position.

8 is an enlarged cross-sectional view of a main portion of the solenoid in an element state;

9 is an enlarged cross-sectional view of a main part showing another example.

10 is an enlarged cross-sectional view of a main portion showing a state in which the blocking body is in the closed position.

11 is an enlarged sectional view of an essential part showing still another example.

12 is an enlarged cross-sectional view of the main portion showing a state where the blocking body is in the closed position.

* Explanation of symbols for main parts of the drawings

2a: crank chamber 3a: discharge chamber

9: rotating shaft 15: swash plate

21,21A, 21B: Block 24,24A, 24B: Rotary Valve

24a: suction refrigerant supply passage 29: suction passage

47: external refrigerant circuit.

Industrial use

The present invention controls the inclination angle of the swash plate by the difference between the pressure in the crank chamber and the suction pressure, and supplies the pressure of the discharge pressure region to the crank chamber and releases the pressure of the crank chamber to the suction pressure region. A clutchless one-sided piston type variable displacement compressor that performs internal pressure adjustment.

Conventional technology

The variable displacement swing swash plate compressor shown in Japanese Patent Laid-Open No. 3-37378 does not use an electromagnetic clutch that connects and interrupts power transmission between an external drive source and a rotary shaft of the compressor. By eliminating the electromagnetic clutch, in particular, in the vehicle-mounted form, it is possible to eliminate the disadvantages of the haptic feeling caused by the on-off shock, reduce the weight of the entire compressor, and reduce the price.

In such a clutchless compressor, there is a problem of a slight discharge capacity when cooling is not required and frost in an evaporator on an external refrigerant circuit. When cooling is not required or when there is a risk of frost generation, the refrigerant circulation on the external refrigerant circuit may be stopped. In the compressor of JP-A-3-37378, the refrigerant circulation stop on the external refrigerant circuit is achieved by stopping the introduction of the refrigerant gas into the suction chamber from the external refrigerant circuit.

When the inlet of the refrigerant gas into the suction chamber in the compressor is stopped by the external refrigerant circuit, the pressure in the suction chamber is lowered and all the capacity control valves in response to the pressure in the suction chamber are opened. By opening all of these, the discharge refrigerant gas of a discharge chamber flows into a crank chamber chamber, and the pressure of a crank chamber rises. In addition, the suction pressure in the cylinder bore is also lowered to reduce the pressure in the suction chamber. Therefore, the difference between the pressure in the crank chamber and the suction pressure in the cylinder bore becomes large, and the swash plate inclination angle shifts to the minimum inclination angle, resulting in the lowest discharge capacity. When the discharge capacity is minimum, the torque in the compressor is minimum, and power loss when cooling is unnecessary can be avoided.

In a conventional piston compressor, a suction port between a compression chamber partitioned in a cylinder bore by a piston and a suction chamber is opened and closed by a flapper valve in the compression chamber. It is opened and closed by a flapper valve in the suction chamber. The refrigerant gas in the suction chamber pushes the flapper valve open by the suction operation of the piston moving from the top dead center to the bottom dead center and flows into the compression chamber. In the discharge stroke in which the piston moves from the bottom dead center side to the top dead center side, the flapper valve closes the suction port, and the refrigerant gas in the compression chamber is discharged from the discharge port to the discharge chamber.

The flapper valve opening and closing operation is based on the pressure difference between the compression chamber and the suction chamber. When the pressure of the suction chamber is higher than the pressure of the suction chamber and the pressure of the compression chamber, the flapper valve is bent and deformed to open the suction port. The pressure higher than the pressure in the suction chamber and the pressure in the compression chamber is at the time of the suction operation of the piston moving from the top dead center side to the bottom dead center side.

Challenges to the Invention

The flexural deformation of the flapper valve, which is an elastic deformation, acts as an elastic resistance, and the flapper valve does not open unless the pressure in the suction chamber is somewhat above the pressure in the pressure chamber. That is, opening of the flapper valve is delayed. Lubricating oil is mixed in the refrigerant gas for lubrication in the compressor, and the lubricant is sent to the necessary lubrication part in the compressor together with the refrigerant gas. This lubricating oil can enter anywhere in the circulation region of the refrigerant gas, and the lubricating oil is attached between the flapper valve closing the suction port and its close surface. This adhesion lubricant increases the close force between the close surface and the flapper valve, and the start of the bending deformation of the flapper valve is further delayed. This delayed start of deformation causes a decrease in the amount of refrigerant gas inflow into the compression chamber, that is, a decrease in volumetric efficiency. In addition, even when the flapper valve is open, the elastic resistance of the flapper valve acts as a suction resistance, thereby reducing the amount of refrigerant gas inflow. Since the lowering of the volumetric efficiency causes the lowering of the cooling capacity, the idler speed in the compressor-mounted vehicle is increased to improve the cooling capacity. However, improving idle speed increases fuel consumption.

The present invention provides a clutchless compressor that improves volumetric efficiency while controlling torque fluctuations in a clutchless one-sided variable displacement compressor using a mechanism that gradually tightens or increases the flow of refrigerant gas from the external refrigerant circuit into the suction chamber. The purpose is to provide.

Means to solve the problem

To this end, in the present invention, a rotating support is mounted on a rotating side in a housing that reciprocally linearly receives the migrating piston in a plurality of cylinder bores arranged around the rotating shaft, and supports the swash plate in such a manner as to allow tilting movement. The angle of inclination of the swash plate is controlled by the difference between the pressure in the crank chamber and the suction pressure through the one-way piston to supply the pressure in the discharge pressure region to the crank chamber, and release the pressure in the crank chamber to the suction pressure region. A clutch-less migraine piston type variable displacement compressor for performing internal pressure is applied. In the invention described in claim 1, a suction refrigerant supply passage for supplying refrigerant gas to a compression chamber partitioned in each cylinder bore by a migraine piston is provided. Formed in the valve and connected to the suction refrigerant supply passage in the external refrigerant circuit. A rotary valve is supported on a rotating shaft so as to sequentially communicate the suction passage for introducing refrigerant gas and the compression chamber in synchronization with the reciprocating motion of the migraine piston, and for communicating and blocking the suction refrigerant supply passage and the suction passage. The blocking body is disposed to be joined to and separated from the rotary valve so that either the rotary valve or the blocking body can be slidably supported in the axial direction of the rotary shaft, and the slide of either the rotary valve or the blocking body is tilted on the swash plate. The inclination angle of the swash plate was kept at the minimum non-zero inclination angle in a state in which the rotary valve and the blocking body were in contact with at least a part of.

In the invention according to claim 2, an open position for communicating with the suction passage and the suction refrigerant supply passage away from the blocking body, and a closed position for blocking communication between the suction passage and the suction refrigerant supply passage in contact with the blocking body. The rotary cylinder supports the rotary valve on the rotary shaft so as to be slide-changeable, and the outlet of the suction refrigerant supply passage when the rotary valve is disposed in the closed position is a circumference connected to the suction port of each compression chamber in accordance with the rotation of the rotary shaft. It's like drawing a trajectory.

In the invention according to claim 3, the refrigerant gas is supplied to the compression chamber partitioned in each cylinder bore by the migraine piston, and the refrigerant gas is formed as a rotary valve in the external refrigerant circuit to the suction refrigerant supply passage. A suction passage for introducing the refrigerant gas supports a rotary valve on the rotating shaft so as to sequentially communicate the compression chamber or the like in synchronization with the reciprocating motion of the migraine piston, and an external refrigerant circuit cannot introduce refrigerant gas into the suction refrigerant supply passage. By arranging the blocker so that the suction passage can be switched to a closed position and an open position which can be closed, the switching operation of the blocker is linked to at least a part of the inclined movement of the swash plate, and when the blocker is in the closed position, The inclination angle of the swash plate was kept at a nonzero minimum inclination angle.

Action

The suction refrigerant passage of the rotary valve sequentially communicates with the plurality of compression chambers in accordance with the rotation of the rotary valve. This communication is performed in synchronization with the suction operation of the migraine piston to the compression chamber. When the suction refrigerant supply passage and the compression chamber are in communication with each other, the pressure of the compression chamber decreases below the pressure of the suction refrigerant supply passage as the piston faces the bottom dead center. By this pressure drop, the refrigerant gas in the suction refrigerant supply passage flows into the compression chamber.

As the swash plate shifts to the minimum inclination angle side by the boosting pressure in the crank chamber, the rotary valve and the blocking body approach in conjunction with the inclined movement of the swash plate. As the rotary valve and the blocking body approach each other, the cross-sectional area of the refrigerant gas flowing into the suction refrigerant supply passage from the external refrigerant circuit is gradually tightened. This tightening action mitigates the reduction of the refrigerant gas inflow amount into the intake refrigerant supply passage in the external refrigerant circuit. Therefore, the amount of refrigerant gas suction in the cylinder bore also slowly decreases in the intake refrigerant supply passage, and the exposure capacity does not suddenly fluctuate to the lowest capacity side. As a result, the torque in the compressor does not fluctuate rapidly in a short time.

As commercial pressure increases at the minimum inclination angle due to pressure drop in the crank chamber, the rotary valve, the blocking body, and the like fall in conjunction with the inclination movement of the swash plate. As the rotary valve, the blocking body, and the like fall, the cross-sectional area of the refrigerant gas gradually increases in the intake refrigerant supply passage in the external refrigerant circuit. This gradually increasing passage cross-sectional area moderates an increase in the amount of refrigerant gas inflow from the external refrigerant circuit into the suction refrigerant supply passage. Therefore, the amount of refrigerant gas suction in the cylinder bore also slowly increases in the suction refrigerant supply passage, and the exposure capacity does not change rapidly on the maximum capacity side. As a result, the torque in the compressor does not fluctuate rapidly in a short time.

When the rotary valve is slide-shifted in conjunction with the inclined movement of the swash plate, the outlet of the suction refrigerant supply passage communicates with the suction port of each compression chamber sequentially even when the rotary valve is in the closed position. When the rotary valve is in the closed position, the refrigerant gas in the discharge pressure region is returned to the discharge pressure region via the crank chamber, the suction refrigerant, the supply passage, and the compression chamber.

In the invention according to claim 3, as the swash plate moves to the minimum inclination angle side by the boosting pressure in the crank chamber, the blocking body approaches the closed position in conjunction with the inclined movement of the swash plate, and flows into the suction refrigerant supply passage from the external refrigerant circuit. Passing cross-sectional area of the refrigerant gas is gradually tightened. This tightening action alleviates the reduction of the refrigerant gas inflow amount into the intake refrigerant supply passage in the external refrigerant circuit. As the commercial inclination angle increases from the minimum inclination angle due to the pressure drop in the crank chamber, the blocking body falls in the closed position in association with the inclination movement of the swash plate, and the cross-sectional area of the refrigerant gas from the external refrigerant circuit to the suction refrigerant supply passage gradually expands. Goes. This gradually increasing passage cross-sectional area alleviates the increase in the amount of refrigerant gas flowing into the suction refrigerant supply passage from the external refrigerant circuit.

Example

A first embodiment of the present invention will be described below with reference to FIGS. 1 to 8.

As shown in FIG. 1, the front housing 2 is joined to the front end of the cylinder block 1 which becomes a part of the housing of the whole compressor. At the rear end of the cylinder block 1, the rear housing 3 is fitted and fixed by sandwiching the valve plate 4, the valve forming plates 5A and 5B and the retainer forming plate 6. A rotating shaft 9 is temporarily supported between the front housing 2 and the cylinder block 1, which are part of the housing and form the crank chamber 2a. The front end of the rotating shaft 9 protrudes outward from the crank chamber 2a, and the driven free 10 is attached to this protruding end. The driven free 10 is operatively connected to the vehicle engine via the belt 11.

At the front end of the front housing 2, the support cylinder 2b is protruded so as to surround the periphery of the protruding end of the rotation shaft 9. The driven free 10 is supported by the support cylinder 2b via the angular baring 7. The support cylinder 2b receives the angular bearing 7 in both the thrust direction load and radial load acting on the driven free 10.

A lip seal 12 is interposed between the front end of the rotating shaft 9 and the front housing 2. The lip seal 12 prevents leakage of pressure in the crank chamber 2a.

The rotary support 9 is attached to the rotary shaft 9, and the spherical swash plate support 14 is slidably supported. The swash plate 15 is supported by the swash plate support body 14 so as to be capable of tilting in the axial direction of the rotation shaft 9.

As shown in FIG. 2, the swash plate 15 is provided with connecting pieces 16 and 17. As shown in FIG. A pair of guide pins 18 and 19 are attached to the connecting pieces 16 and 17. The support arm 8a protrudes from the rotating support 8. The support pin 20 is rotatably supported by the support arm 8a in a direction perpendicular to the rotation axis 9 while being rotatable. The pair of guide pins 18 and 19 are slidably fitted at both ends of the support plate 20. The swash plate 15 is inclined about the swash plate support 14 in the axial direction about the swash plate support 14 by linkage between the support pin 20 on the support arm 8a and the pair of guide plates 18 and 19. It is movable and integrally rotatable with the rotating shaft 9. The inclined movement of the swash plate 15 is guided by the slide guide relationship between the support plate 20 and the guide plates 18, 19, the slide action of the swash plate support 14, and the support action of the swash plate support 14.

As shown in FIG. 1, FIG. 5, and FIG. 6, the rotary valve 24 is rotatably accommodated in the accommodating hole 13 in the center part of the cylinder block 1, and is slidably accommodated. An intake refrigerant supply passage 24a is formed in the rotary valve 24, and an inlet 24b of the intake refrigerant supply passage 24a is formed in the rear end of the rotary valve 24. As shown in FIG. 4, the outlet 24c of the suction refrigerant supply passage 24a is formed in the circumferential surface of the rotary valve 24. As shown in FIG.

The small diameter part of the rear end side of the rotary shaft 9 is drilled in the rotary valve 24, and the rotary valve 24 is slidably supported on the small diameter part of the rotary shaft 9, and is supported by relative rotation. At the rear end of the small diameter portion of the rotating shaft 9, the blocking body 21 is tightened and fixed by the screw 25, and an opening spring 26 is provided between the blocking body 21 and the rotary valve 24. The opening spring 26 adds the blocking body 21 to the swash plate support body 14 side. The end surface of the rotary valve 24 is in contact with the blocking body 21. In the state where the end surface of the rotary valve 24 and the blocking body 21 and the like abut, the inlet 24b of the suction refrigerant supply passage 24a is closed by the blocking body 21.

The transmission cylinder 27 is slidably supported on the rotation shaft 9 between the swash plate support member 14 and the rotary valve 24. One end of the transmission cylinder 27 is in contact with the end face of the swash plate supporter 1, and the other end of the transmission cylinder 27 is in contact with the end face of the rotary valve 24. The transmission cylinder 27 enters in the accommodation hole 13, and the sliding bearing member 28 is interposed between the peripheral wall of the accommodation hole 13 and the transmission cylinder 27. The sliding bearing member 28 receives the radial load on the rotating shaft 9 via the transmission cylinder 27. The sealing member S is interposed between the sliding bearing member 28 and the rotary valve 24. The sealing member S seals between the crank chamber 2a and the receiving hole 13.

As shown in FIG. 6, stepped portions 9a and 9b are formed on the circumferential surface of the rear end of the rotary shaft 9. The stepped portion 9a regulates the movement of the rotary valve 24 toward the swash plate support 14 side, and the stepped portion 9b regulates the movement on the commercial support 14 side of the delivery cylinder 27.

The suction passage 29 is formed at the center of the rear housing 3. The inlet 24b of the suction refrigerant supply passage 24a is opened in the suction passage 29. As the end surface of the rotary valve 24 abuts against the blocking body 21, the rotary valve 24 restricts movement in a direction falling from the swash plate member 14, while the suction passage 29 and the suction refrigerant supply passage ( 24a) is blocked.

When the swash plate support 14 contacts the transfer cylinder 27 as the swash plate support 14 moves toward the blocking body 21 side, the transfer cylinder 27 is joined to the rotary valve 24. The rotary valve 24 abuts against the blocking body 21 against the spring force of the opening spring 26. Therefore, the inclination angle of the swash plate 15 is regulated by the contact between the rotary valve 24 and the blocking body 21. The minimum inclination angle of the swash plate 15 is slightly larger than 0 °. This minimum inclination-angle state occurs when the blocking body 21 is arranged in the closed position which interrupts communication between the suction passage 29 and the suction refrigerant supply passage 24a. The rotary valve 24 is arranged to be shifted in conjunction with the inclination angle movement of the swash plate 15 to the closed position and the open position away from the position.

The maximum inclination angle of the swash plate 15 is regulated by the contact between the inclination angle regulating protrusion 8b of the rotary support 8 and the swash plate 15.

The migraine piston 22 is accommodated in the cylinder bore 1a penetrated to the cylinder block 1 so as to be connected to the crank chamber 2a. The rotational motion of the swash plate 15 is converted to the front and rear rest swing of the migraine piston 22 via the shoe 23, and the migraine piston 22 moves back and forth in the cylinder bore 1a.

As shown in FIG. 1 and FIG. 3, the suction chamber 3a and the discharge chamber 3b are partitioned in the rear housing 3. As shown in FIG. A discharge port 4b is formed on the valve plate 4, and a discharge valve 5a is formed on the valve forming plate 5. The refrigerant gas in the compression chamber P partitioned in the cylinder bore 1a by the migraine piston 22 pushes the discharge valve 5a from the discharge port 4a by the reciprocating motion of the migraine piston 22 to discharge it. It is discharged to the chamber 3b. The opening degree of the discharge valve 5a abuts against the retainer 6a on the retainer forming plate 6 is regulated.

A thrust bearing 53 is interposed between the rotary support 8 and the front housing 2. Thrust bearing 53 acts on rotating support 8 in compression chamber 9 via migraine piston 22, swash plate 15, connecting pieces 16 and 17, guide pins 18 and 19 and support plate 20. To accept compression reaction.

A plurality of suction ports 13a are arranged in the circumferential direction on the circumferential surface of the accommodation hole 13. The suction port 13a and the compression chamber P are in one-to-one communication. The outlet of the intake refrigerant supply passage 24a in the rotary valve 24 even when the rotary valve 24 is disposed in either the open position shown in FIG. 6 and the closed position shown in FIGS. 7 and 8. 24c draws the peripheral periphery which sequentially connects with each suction port 13a according to rotation of the rotary valve 24. As shown in FIG. When the rotary valve 24 is in the open position, the refrigerant gas of the suction passage 29 is sequentially sucked into each compression chamber P via the suction refrigerant supply passage 24a by the reciprocating operation of the migraine piston 22. .

The stroke of the migraine piston 22 changes in response to the differential pressure across the migraine piston 22 between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a. That is, the inclination angle of the swash plate 15 that influences the compression capacity changes. The pressure in the crank chamber 2a is controlled by the capacity control valve 30 mounted in the rear housing 3. The discharge pressure introduction port 31a, the suction pressure introduction port 31b, and the control port 31c are provided in the valve housing 31 constituting the displacement control valve 30. The discharge pressure introduction port 31a communicates with the discharge chamber 3a via the discharge pressure introduction passage 32.

The pressure of the suction pressure detection chamber 35 through the suction pressure introduction port 31b is opposed to the adjustment spring 37 via the diaphragm 36. The spring force of the adjustment spring 37 is transmitted to the valve body 39 via the diaphragm 36 and the rod 38. The valve body 39 which has a spring action in the direction of closing the valve hole 31d by the return spring 40 closes the valve hole 31d against the variation of the suction pressure in the suction pressure detection chamber 35. When the valve hole 31d is closed, communication between the discharge pressure introduction port 31a and the control port 31c and the like is interrupted.

The pressure release passage 41 is formed in the rotating shaft 9. The inlet 41a of the pressure release passage 41 is opened in the crank chamber 2a, and the outlet 41b of the pressure release passage 21 is opened in the step 9a. As shown in FIG. 4, the pressure release clearance 42 is formed between the circumferential surface of the small diameter part of the rear end of the rotating shaft 9, and the rotary valve 24. As shown in FIG. The pressure release gap 42 communicates with the outlet 41b of the pressure release passage 41, the suction refrigerant supply passage 24a, and the like. That is, the crank chamber 2a communicates with the intake refrigerant supply passage 24a via the pressure opening passage 41 and the pressure opening gap 42.

The electronic housing valve 43 is attached to the rear housing 3. The valve body 46 closes the valve hole 43a by the excitation of the solenoid 45, and the valve body 46 opens the valve hole 43a by the element of the solenoid 45. That is, the solenoid valve 43 closes the pressure supply passage 44 connecting the discharge chamber 3a and the crank chamber 2a and the like.

The suction passage 29 for introducing the refrigerant gas into the suction refrigerant supply passage 24a and the discharge port 1b for discharging the refrigerant gas to the discharge chamber 3a are connected to the external refrigerant circuit 47. The condenser 48, the expansion valve 49, and the evaporator 50 are interposed on the external refrigerant circuit 47. The expansion valve 49 controls the refrigerant flow rate in response to the change in the gas pressure at the outlet side of the carburettor 50.

The solenoid 45 is subjected to the excitation control of the control computer C. The control computer C excites the solenoid 45 by turning on the air conditioner operating switch 51 or turning off the excel switch 52 and turning off the activating switch 51 of the air conditioning device or turning on the excel switch 52. The solenoid 45 is demagnetized by this.

The pressure supply passage 44 is closed by the excited state of the solenoid 45 in the state of FIG.

When the solenoid 45 is excited, when the suction pressure is high (the cooling load is large), the valve opening degree of the valve body 39 becomes small. The refrigerant gas in the crank chamber 2a flows out into the suction refrigerant supply passage 24a via the pressure discharge passage 31. Therefore, the valve opening degree of the valve body 39 becomes small and the discharge pressure introduction passage 32, the discharge pressure introduction port 31a, the valve hole 31d, the control port 31c and the control passage in the discharge chamber 3b. The amount of refrigerant gas flowing into the crank chamber 2a via 34 is reduced. Therefore, the pressure in the crank chamber 2a falls. Moreover, since the suction pressure in the cylinder bore 1a is also high, the difference between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a becomes small. Therefore, as shown in FIG. 1 and FIG. 6, the swash plate inclination angle becomes large.

On the contrary, when the suction pressure is low (the cooling load is small), when the valve opening degree of the valve body 39 becomes large, the amount of refrigerant gas flowing into the crank chamber 2a from the discharge chamber 3a becomes large. Therefore, the pressure in the crank chamber 2a rises. Moreover, since the suction pressure in the cylinder bore 1a is low, the difference between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a becomes large. Therefore, the swash plate inclination angle becomes small.

In a state where the suction pressure is considerably low (there is no cooling load), the valve body 39 is close to the maximum opening position as shown in FIG. In a state close to the maximum opening degree as shown in FIG. 7, the refrigerant gas in the discharge chamber 3a rapidly flows into the crank chamber 2a via the control passage 34. Therefore, the boosting pressure in the crank chamber 2a is fast, and the pressure in the crank chamber 2a becomes the highest pressure state, and the inclination angle of the swash plate 15 shifts to the minimum inclination angle side.

As the inclination angle of the swash plate 15 shifts to the minimum inclination angle side, the swash plate support member 14 abuts against the transmission cylinder 27 and presses the transmission cylinder 27 against the rotary valve 24 to join.

When the swash plate support member 14 further moves toward the blocking body 21 in the state where the transmission cylinder 27 is joined to the rotary valve 24, the rotary valve 24 approaches the blocking body 21. By this approach operation, the refrigerant gas passage cross section between the suction passage 29 and the suction refrigerant supply passage 24a is gradually narrowed. This narrowing action gradually reduces the amount of refrigerant gas flowing into the suction refrigerant supply passage 24a from the suction passage 29. Therefore, the amount of refrigerant gas sucked into the compression chamber P from the suction refrigerant supply passage 24a via the suction port 13a also gradually decreases, and the discharge capacity gradually decreases. As a result, the discharge pressure gradually decreases, and the torque in the compressor does not fluctuate largely in a short time.

When the rotary bearing valve 24 is in contact with the blocking body 21, communication between the suction passage 29 and the suction refrigerant supply passage 24a is interrupted, and refrigerant circulation in the external refrigerant circuit 47 is prevented. Therefore, there is no fear of frost generation in the evaporator 50.

The refrigerant gas discharged from the cylinder bore 1a to the discharge chamber 3a passes through the discharge pressure introduction passage 32, the passage within the displacement control valve 30 and the control passage 34, and the pressure release passage. A circulation path referred to as 41, the pressure release gap 42, the suction refrigerant supply passage 24a, and the compression chamber P is formed in the compressor, and the discharge chamber 3a, the crank chamber 2a, and the suction refrigerant supply passage. A pressure difference is generated between the 24a.

In addition, the suction pressure introduction position of the displacement control valve 30 sensitive to the suction pressure is set upstream than the position at which the suction passage 29 is blocked. Therefore, the capacity control valve 30 is significantly sensitive to the suction pressure reflecting the cooling load, and when the cooling load is generated, the swash plate inclination angle is automatically increased at the minimum state.

When the solenoid 45 is demagnetized by turning off the air conditioner operating switch 51 or turning on the excel switch 52, the solenoid valve 43 opens the pressure supply passage 44 as shown in FIG. In this state, the refrigerant gas in the discharge chamber 3a rapidly flows into the crank chamber 2a via the pressure supply passage 44, and the inclination angle of the swash plate 15 shifts to the minimum inclination angle side.

In the state of FIG. 7, when the cooling load increases and the suction pressure rises, the increase in the suction pressure spreads to the suction pressure detection chamber 35 in the suction passage 29 so that the valve body 33 closes the valve hole 31d. do. Alternatively, when the air conditioner operating switch 51 is turned on or the Excel switch 52 is turned off in the state of FIG. 8, the solenoid 45 is excited to block the pressure supply passage 44.

There is a pressure difference between the discharge chamber 3a, the crank chamber 2a, and the suction refrigerant supply passage 24a. Therefore, when the pressure supply passage 44 is in the shut-off state and the valve body 39 closes the valve hole 31d, the pressure in the crank chamber 2a decreases and the swash plate inclination angle increases at the minimum inclination angle. The swash plate support 14 moves in a direction falling from the delivery cylinder 27 by the increase of the inclination angle, but the delivery cylinder 27 and the rotary valve 24 are moved by the spring force of the development spring 26 to allow the swash plate support 14 to move. In accordance with the movement, the rotary valve 24 falls off the blocking body 21. By this dropping operation, the refrigerant gas cylinder and the cross-sectional area between the suction passage 29 and the suction refrigerant supply passage 24a gradually expand. The amount of refrigerant gas flowing into the suction refrigerant supply passage 24a from the passage cross-section suction passage 29 which is gradually performed gradually increases. Therefore, the amount of refrigerant gas sucked into the compression chamber P in the suction refrigerant supply passage 24a gradually increases, and the discharge capacity gradually increases. As a result, the discharge pressure gradually increases, and the torque in the compressor does not fluctuate greatly in a short time.

In the present invention obtained by preventing large torque fluctuations, the rotary valve 24 is employed, and the adoption of the rotary valve 24 brings about an improvement in volume efficiency. In the case of the flapper valve type suction valve, the lubricating oil increases the suction force between the suction valve and its close face, and the opening timing of the suction valve is delayed by the suction force. This delay and the suction resistance due to the elastic resistance of the suction valve lower the volumetric efficiency.

However, when the rotary valve 24 is forcibly rotated, there is no problem of the suction force caused by the lubricating oil and the suction resistance due to the elastic resistance of the suction valve, and the pressure inside the compression chamber P slightly reduces the pressure in the suction refrigerant supply passage 24a. When lowered, the refrigerant gas immediately flows into the pressure chamber P. Therefore, in the case of employing the rotary valve 24, the volumetric efficiency is greatly improved compared to the case of employing the flapper valve type intake valve.

The improvement of the volumetric efficiency calls for the improvement of the cooling capacity. Therefore, in the idling state in the compressor-equipped vehicle, the improvement of the cooling capacity can be achieved without raising the engine speed, and the fuel consumption can be controlled.

The present invention is, of course, not limited to the above embodiment, but can also be implemented in, for example, FIGS. 9 and 10. In this embodiment, the rotary valve 24A is tightened and fixed to the rear end of the rotary shaft 9 by a screw 25, and a blocking member 21A slidably supported on the rotary shaft 9 is sucked in by the rotary valve 24A. It enters in the refrigerant supply passage 24a. The blocking body 24A is interlocked with the inclined movement of the swash plate 15, and an opening spring 26 is interposed between the rotary valve 24A and the blocking body 21A.

As shown in FIG. 9, when the swash plate 15 is at the maximum inclination angle, the blocking member 21A is disposed in an open position away from the inlet 24b of the suction refrigerant supply passage 24a by the spring action of the opening spring 26. do. As shown in FIG. 10, when the swash plate 15 is at the minimum inclination angle, the blocking body 21A is disposed in the closed position to close the inlet 24b of the intake refrigerant supply passage 24a. The pressure releasing hole 21a is formed in the blocking body 21A so as to be connected to the outlet 41a of the pressure releasing passage 41, and the compression chamber P, the discharge chamber 3a, and the crank even when the swash plate inclination angle is minimum. The seal 2a and the suction refrigerant supply passage 24a form a circulation path.

The configuration in which the rotary valve 24A simply rotates without slipping with respect to the receiving hole 13 has a sliding joint circumferential surface of the rotary valve as compared with the configuration in which the rotary valve 24 slides with respect to the receiving hole 13. It is advantageous with regard to the sealability of the.

In addition, in the present invention, as shown in Figs. 11 to 12, an embodiment in which the suction passage 29 is opened and closed by the blocking body 21B is also possible. In the maximum state of the swash plate inclination of FIG. 11, the suction gas is in an open position to introduce the refrigerant gas into the intake refrigerant supply passage 24a in the suction passage 29. In the minimum state of the swash plate inclination of FIG. The refrigerant gas is in the closed position incapable of introducing refrigerant gas into the passage 24a. That is, the blocking body 21B is linked to the inclined movement of the swash plate 15 in the same manner as in the above embodiments.

Also in this embodiment, the rotary valve 24B simply rotates without slipping with respect to the receiving hole 13, and the practicality at the sliding joint surface of the rotary valve 24 is determined by the rotary valve 24 in the receiving hole 13. It is advantageous as compared with the structure which slides with respect to.

As described above, in the present invention, one of the rotary valve and the blocking member is slidably supported in the axial direction of the rotation axis, and the slide of either the rotary valve and the blocking member is at least a part of the inclined movement of the swash plate. In the state that the rotary valve and the shutoff body are connected to each other, the inclination angle of the swash plate is maintained at the minimum inclination angle, not 0, thereby preventing the sudden fluctuation of the discharge pressure, thereby controlling the torque variation and improving the volume efficiency. Achieve an excellent effect that can be obtained.

In the invention which makes the rotary valve slippery, the outlet of the suction refrigerant supply passage when the rotary valve slides in the closed position draws a circumferential rotational position which is sequentially connected to the suction port of each compression chamber in accordance with the rotation of the rotary shaft. Therefore, even when the swash plate inclination angle is minimum, the compression chamber, the discharge chamber, the crank chamber, and the suction refrigerant supply passage form a circulation path to generate a pressure difference, and achieve an excellent effect that can be obtained by automatically performing a capacity recovery at the minimum capacity.

In the invention which makes the blocking body slippery, the sealant at the sliding joint circumferential surface of the rotary valve is improved as compared with the case in which the rotary valve is slipped.

Claims (3)

It accommodates the migraine pistons in the plurality of cylinder bores arranged around the rotation shaft in a reciprocating linear motion, and supports the rotation shaft rotatably in the housing to support the swash plate integrally rotatable and the lightly movable on the rotation shaft. The angle of inclination of the swash plate is controlled by the difference between the pressure in the crank chamber and the suction pressure that has passed, and the discharge pressure and the area pressure are supplied to the crank chamber, and the pressure in the crank chamber is released to the suction pressure region to adjust the adjustment pressure in the crank chamber. A clutchless single-sided piston type variable displacement compressor, comprising: a suction valve supply passage for supplying a coolant gas to a compression chamber partitioned in each cylinder bore by the migraine piston, in a rotary valve, and the suction refrigerant in an external refrigerant circuit. The suction passage for introducing refrigerant gas into the supply passage and the compression chamber A rotary valve is supported on the rotational axis so as to be in downward communication in synchronism with the reciprocating motion of the migraine piston, and a blocking body for communicating and blocking the suction refrigerant supply passage and the suction passage is disposed so as to be joined to the rotary valve. One of the rotary valve and the blocking body is slidably supported in the lateral direction of the rotary shaft, and the rotary valve and the blocking body are in contact with each other by slicing one of the rotary valve and the blocking body with at least a part of the inclined movement of the swash plate. The clutchless one-sided piston variable displacement compressor, characterized in that the inclination angle of the swash plate is maintained at a minimum inclination angle other than zero when there is. 2. The slide according to claim 1, further comprising: an open position that is separated from the blocking body to communicate with the suction passage and the suction refrigerant supply passage, and a closed position that contacts the blocking body to block communication between the suction passage and the suction refrigerant supply passage. The rotary valve is supported on the rotary shaft so as to be convertible, and the outlet of the suction refrigerant supply passage when the rotary valve is slide-positioned in the closed position is sequentially connected to the suction port of each compression chamber in accordance with the rotation of the foremost shaft. A clutchless one-sided piston variable displacement compressor characterized by drawing a circumferential trajectory. Reciprocating grindstones in a plurality of cylinder bores arranged around the rotating shaft (removably receive the reciprocating grindstone, and rotatably support the rotating shaft in the housing to support the rotating shaft integrally rotatable and tiltable movement, the migrating piston The angle of inclination of the swash plate is controlled by the difference between the pressure in the crank chamber and the suction pressure passing through it, and the pressure in the discharge pressure region is supplied to the crank chamber, and the pressure of the crank chamber is released to suction only to adjust the pressure in the crank chamber. A clutchless single-sided piston type variable displacement compressor, comprising: a suction valve supply passage for supplying a refrigerant gas to a compression chamber partitioned in each cylinder bore by the one-headed piston, in a rotary valve, and the suction refrigerant in an external refrigerant circuit. The suction passage for introducing the refrigerant gas into the supply passage and the compression chamber A rotary valve is supported on the rotary shaft so as to sequentially communicate with the reciprocating motion of the migraine piston, and an external refrigerant circuit converts the blocking body into a closed position and an open position in which refrigerant gas cannot be introduced into the suction refrigerant supply passage. And at least a portion of the inclined movement of the swash plate, and when the blocker is in the closed position, the inclination angle of the swash plate is maintained at a minimum non-zero inclination angle.