JPH06213151A - Clutch-less rocking swash plate variable-capacity compressor - Google Patents

Abstract

PURPOSE:To start a compression action by easily returning a swash plate to the tilt position from the 0-capacity state. CONSTITUTION:A swash plate 13 is fitted reciprocatively tiltably in the longitudinal direction to a rotation supporter 9 fixed to a rotary shaft via a hinge mechanism K1. A spool 24 returning the swash plate 13 from 0 deg. to the tilt position is provided on the rotary shaft. The control oil pressure is fed to a pressure chamber 26 from an oil feed pump 27 when a compressor is started, the spool 24 is advanced, a sleeve 12 having a spherical surface 12a supporting the swash plate 13 is moved along the rotary shaft, and the swash plate 13 is returned to the tilt position to start the compression operation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutchless rocking swash plate type variable displacement compressor used in, for example, an air conditioner for automobiles.

[0002]

2. Description of the Related Art Generally, a variable displacement compressor for an automobile has
When the electromagnetic clutch that connects and disconnects the power of the engine is installed, the temperature inside the vehicle compartment is high, and the electromagnetic clutch is activated by turning on a switch of an air conditioner (hereinafter referred to as an air conditioner), the rotational movement of the engine causes the belt transmission mechanism and the electromagnetic transmission. It is transmitted to the compressor via the clutch. For this reason, the compressor is started and stopped with a large capacity each time the air conditioner switch is turned on and off, and its durability is reduced due to frequent repetitions of electromagnetic clutch engagement and disengagement. The machine is large and heavy, and it is difficult to install due to the installation space in the engine room.

In order to solve the above problems, a clutchless rocking swash plate type variable displacement compressor has been proposed. As this compressor, there is a compressor disclosed in JP-A-3-143725. In this compressor, the maximum stroke of the piston is variable by continuously changing the inclination angle of the swash plate by controlling the differential pressure between the crank chamber in which the swash plate is housed and the working chamber in the cylinder bore during the intake stroke. Further, this compressor is provided with a hydraulic actuator that pushes the swash plate from the zero degree position and holds the tilted position greater than zero degree in response to an ON signal of the air conditioner switch.

[0004]

However, in the conventional compressor, the assist plunger of the hydraulic actuator rotates integrally with the rotary shaft, and when the assist plunger moves forward, the rotary drive plate tilts. Since the plate is moved from the zero degree position to the inclined position together with the plate, there is a problem that the pushing operation is not smoothly performed and the capacity cannot be quickly restored.

Further, a compressor having a swash plate supporting structure has been proposed, in which a sleeve having a spherical surface on a rotating shaft is rotatably supported, and a swash plate is rotatably supported on the spherical surface of the sleeve. Since the sleeve of the compressor cannot be pushed by the above-mentioned assist plunger, a smooth capacity restoring operation cannot be performed.

An object of the present invention is to solve the above problems existing in the prior art, and to allow the swash plate to be easily returned from the zero capacity state to the inclined position to start the compression operation. It is to provide a variable capacity compressor.

[0007]

In order to achieve the above object, a clutchless rocking swash plate type variable displacement compressor controls a tilt angle of the swash plate by an off signal from an external signal generator. And a fluid pressure drive means for returning the inclination angle of the swash plate from zero degrees to an inclined position in response to an ON signal from an external signal generator. The fluid pump for sucking and discharging the fluid in the compressor, the pressure chamber for guiding the fluid discharged from the fluid pump, and the pressurized fluid supplied to the pressure chamber to advance the means for supporting the swash plate. The spool includes a spool that pushes the sleeve having the spherical surface to return the swash plate from a zero degree position to an inclined position, and an oil discharge path that discharges oil from the pressure chamber to the crank chamber after the spool is operated.

According to a second aspect of the present invention, in the first aspect, the spool is formed in a cylindrical shape, and the spool has an outer peripheral surface of a rotating shaft and an inner peripheral surface of a center hole of a cylinder block through which the rotating shaft is inserted. And a seal ring between the outer peripheral surface of the spool and the inner peripheral surface of the center hole, and between the inner peripheral surface of the spool and the outer peripheral surface of the rotating shaft. Intervenes.

[0009]

According to the first aspect of the invention, the swash plate is held at the zero degree position by the inclination changing means when the compressor is stopped. When the compressor is started in this stopped state, the swash plate is rotated by the rotating shaft, but since the tilt angle of the swash plate is zero, the zero capacity operation in the clutchless state is performed.

When the ON signal is output from the external signal generator to the fluid pressure driving means, the fluid is sucked up from the crank chamber by the fluid pump and supplied to the pressure chamber, and the spool moves forward to push the sleeve. Therefore, the swash plate is displaced from the zero degree position to the inclined position. Therefore, the compressor is shifted from the zero capacity operation to the compression operation.

Further, when the off signal is output from the external signal generator to the fluid pressure driving means, the supply of the pressurized fluid from the fluid pump to the pressure chamber is stopped and the spool becomes inoperative. In synchronization with this, the tilt angle changing means is operated by the OFF signal from the external signal generator, the tilt angle of the swash plate is returned from the tilt state to zero degree, and the zero capacity operation in the clutchless state is performed again.

According to the first aspect of the invention, since the sleeve supporting the swash plate is pushed by the spool to incline the swash plate, the capacity restoring operation can be performed smoothly and the capacity control characteristic can be improved. .

Further, according to the second aspect of the invention, since the leakage of the fluid from the pressure chamber to the crank chamber is suppressed by the seal ring, the swash plate can be tilted more reliably.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment embodying the present invention will be described below with reference to FIGS. As shown in FIG. 2, a front housing 2 forming a crank chamber 2a is joined and fixed to a front end surface of a cylinder block 1 having a plurality of cylinder bores 1a. At the rear end of the cylinder block 1, a rear housing 3 that defines and forms a suction chamber 3a and a discharge chamber 3b is joined and fixed. A rotary shaft 4 is rotatably supported by the cylinder block 1 and the front housing 2 via radial bearings 5 and 6 so as to be located in the crank chamber 2a. A pulley 7 is fixed to the outer end of the rotary shaft 4, and the rotational movement of the engine is directly transmitted by a belt 8.

A rotary support 9 is fitted and fixed to the rotary shaft 4, and a thrust bearing 10 for supporting a thrust load during compression is interposed between the support 9 and the inner wall of the front housing 2. A support arm 11 having an insertion hole 11a is integrally formed with the rotary support 9. On the other hand, the sleeve 1 having the spherical surface 12a on the rotating shaft 4
2 is supported along the outer peripheral surface of the rotary shaft 4 so as to be capable of reciprocating in the front-rear direction, and the swash plate 13 is provided on the sleeve 12 with a spherical surface 1.
It is supported so as to be tiltable in the front-back direction along 2a. A support pin 14 is rotatably supported in the insertion hole 11a of the support arm 11 in a direction orthogonal to the rotary shaft 4 as shown in FIG. 3, and is formed at both left and right ends of the support pin 14. A pair of left and right guide pins 1 are provided in the holes 14a, 14a.
The upper ends of the reference numerals 5 and 16 are slidably guided and penetrated in parallel with each other. Further, the lower end portions of the both guide pins 15 and 16 are integrally formed on the back surface of the swash plate 13 to form a bearing portion 13.
It is press-fitted and fixed in the mounting holes 13b and 13b of a and 13a. In this embodiment, the support arm 11 and the sleeve 1 are
2, the guide pins 15 and 16, the bearings 13a and 13a, and the like constitute a hinge mechanism K1 that allows the swash plate 13 to reciprocate in the front-rear direction.

As shown in FIG. 2, the swash plate 13 is inserted into a recess formed at the base end of a plurality of one-sided pistons 17 housed in the cylinder bore 1a, and a pair of front and rear shoes 18, 18 are interposed therebetween. Moored. On the outer circumference of the rotary shaft 4, the inclination angle of the swash plate 13 is zero degrees, that is, the sleeve 12
A stopper 19 for restricting the position of the piston 17 to make the stroke of the piston 17 zero is attached. In addition, swash plate 1
The maximum inclination angle of 3 is regulated by the bearing portion 13a coming into contact with the rotary support 9.

A valve plate 20 having a suction hole 20a and a discharge hole 20b is interposed between the rear end surface of the cylinder block 1 and the front end surface of the rear housing 3, as shown in FIG. In addition, a suction valve plate 21 having a suction valve 21a formed on the front surface of the valve plate 20.
However, a discharge valve plate 22 having a discharge valve 22a is joined to the rear surface thereof. The discharge valve 22 is provided on the rear surface of the discharge valve plate 22.
A retainer plate 23 having a retainer 23a that regulates the open position of a is joined.

Next, the swash plate tilt return oil (fluid) pressure driving means K2 for returning the swash plate 13 from the tilt angle zero degree position to the tilt position will be described. As shown in FIGS. 1 and 2, a cylindrical spool 24, which is slidably guided by the outer peripheral surface of the rotary shaft 4 and reciprocates in the front-rear direction, is housed in the center hole 1b of the cylinder block 1. A lip seal 25 is provided between the rear radial bearing 6 and the spool 24, and the position of the lip seal 25 is regulated by a stop ring 34. The outer peripheral surface of the large-diameter cylindrical portion 24a formed at the tip of the spool 24 is slidably contacted with the inner peripheral surface of the central hole 1b, and the pressure chamber 26 is provided between the outer peripheral surface of the small-diameter cylindrical portion 24b and the central hole 1b. Are formed. And the spool 24
When the control hydraulic pressure is supplied to the pressure chamber 26 with the tip of the large-diameter cylindrical portion 24a of the sleeve 1 in contact with the rear end surface of the sleeve 12, the spool 24 is guided by the rotating shaft 4 and the sleeve 1
2 is pushed forward, and the swash plate 13 is returned to the inclined position from zero degree.

As shown in FIG.
As shown in FIG. 4, a trochoidal type oil supply pump 27 driven by the rotary shaft 4 is housed. This refueling pump 2
7 is an outer tooth body 27a and an inner tooth body 27b as shown in FIG.
Consists of. When the outer tooth body 27a is rotated by the rotating shaft 4, the inner tooth body 27b rotates in the same direction at a slower speed than the outer tooth body 27a. The space V between the tooth bodies 27a and 27b moves in the rotating direction of the tooth bodies 27a and 27b while increasing and decreasing in volume due to the difference in rotational speed between the tooth bodies 27a and 27b. Oil is sucked into the space V from the arc-shaped suction port 28a, and oil sucked into the space V is discharged from the arc-shaped discharge port 29a. As shown in FIG. 2, an oil suction passage 28 communicating with the bottom of the crank chamber 2a is connected to the suction port 28a of the oil supply pump 27. Further, the discharge port 29a of the oil supply pump 27 is connected to the rear side opening of the oil passage 30 formed at the center of the rotary shaft 4 by the oil discharge passage 29. And
In the oil passage 30, branch oil passages 30a are formed at a plurality of points,
Lubricating oil can be supplied to the bearings 5 and 6, the crank chamber 2a, the sleeve 12, and the like.

Further, as shown in FIGS. 1 and 2, a first electromagnetic on-off valve 31 is provided in the oil discharge passage 29, and the oil discharge passage 2 between the on-off valve 31 and the oil supply pump 27 is provided.
Reference numeral 9 denotes the pressure chamber 2 via an oil supply passage 32 for returning the tilt angle of the swash plate formed in the cylinder block 1 and the rear housing 3.
Connected to 6. When the oil discharge passage 29 is closed by the first electromagnetic opening / closing valve 31, the oil supply to the oil passage 30 is cut off, and the swash plate tilt angle from the oil supply pump 27 through the oil supply passage 32 to the pressure chamber 26 is increased. The control hydraulic pressure for return is supplied.

Therefore, the structure of the first electromagnetic on-off valve 31 will be described with reference to FIGS. As shown in FIG. 6, a valve chamber 37 is formed in the valve case 36, and a cylindrical valve body 38 is accommodated in the chamber 37. The valve case 3
An electromagnetic solenoid 39 is attached to the upper part of the coil 6, and a fixed iron core 41 and a movable iron core 42 are housed inside the coil 40. The base end portion of the first operating rod 43 is inserted and fixed to the movable iron core 42, and the intermediate portion thereof is loosely penetrated through the insertion hole formed at the center of the fixed iron core 41 and fixedly penetrated through the valve body 38. There is.

Therefore, when the coil 40 is demagnetized, the valve body 38 is held at a position where the oil discharge passage 29 is opened, as shown in FIG. Therefore, the lubricating oil is supplied to the oil passage 30 through the oil discharge passage 29, and the sliding portions inside the crank chamber 2a are lubricated. On the contrary, when the coil 40 is in the excited state, the movable iron core 42 is moved to the fixed iron core 41 as shown in FIG.
And the valve element 38 is moved to the closed position by the first operating rod 43. Therefore, the control oil pressure discharged from the oil supply pump 27 is not supplied to the oil passage 30 in the rotating shaft 4 but is supplied from the tilt return oil supply passage 32 into the pressure chamber 26, so that the spool 24 is pushed forward. And sleeve 1
2 is moved in the same direction, and the swash plate 13 is returned from the zero degree to the inclined position.

An oil discharge passage 30b which connects the pressure chamber 26 and the oil passage 30 is formed in the rotary shaft 4, and the spool 2
When 4 is moved to the forward end abutting the stopper 19, the oil discharge passage 30b is opened and the control oil pressure supplied from the oil supply pump 27 to the pressure chamber 26 through the oil supply passage 32 is transferred from the oil discharge passage 30b. The oil is guided to the oil passage 30.

Next, referring to FIGS. 2, 6 and 7, the swash plate 1 will be described.
While the compressor 3 is in the tilt position and the compression operation of the compressor is being performed, a tilt angle changing means K3 for returning the tilt angle of the swash plate 13 to zero by the control device 57 of an external control method described later.
Will be described.

As shown in FIG. 2, the rear housing 3 and the cylinder block 1 are provided with an air supply passage 44 which communicates the discharge chamber 3b with the crank chamber 2a, and an extraction passage 45 which communicates the crank chamber 2a with the suction chamber 3a. Has been formed. A second electromagnetic on-off valve 46 is provided in the air supply passage 44. The electromagnetic solenoid of the second electromagnetic opening / closing valve 46 shares the electromagnetic sonoid 39 of the first electromagnetic opening / closing valve 31.

As shown in FIG. 6, the second solenoid on-off valve 46 has a spherical valve body 49 inside a valve chamber 48 formed in a valve case 47. The valve body 49 is always biased by a return spring 50 in a direction to close the air supply passage 44.
A second operating rod 51 is coaxially connected to the upper end of the movable iron core 42 of the electromagnetic solenoid 39, and the upper end of the operating rod 51 is in contact with the lower surface of the valve body 49. When the electromagnetic solenoid 39 is demagnetized, the movable iron core 42 is urged by the bellows 56 having a spring 56a, which will be described later, against the urging force of the return spring 50 to open the valve bodies 49, 38. In this way, the tilt angle changing means K3 of the swash plate 13 is configured.

Therefore, as shown in FIG. 7, when the electromagnetic solenoid 39 is excited, the second operating rod 51 is moved by the movable iron core 42 in the direction away from the valve body 49, and the valve body 4 is moved.
9 is held by the return spring 50 so as to close the air supply passage 44. Then, as shown in FIG. 8, when the electromagnetic solenoid 39 is demagnetized in a state where the swash plate 13 is in the inclined position and the compressor is being compressed, the bellows 56 in FIG.
Accordingly, the valve body 38, the first operating rod 43, the movable iron core 42
The second actuating rod 51 is moved upward, and the actuating rod 51 moves the valve body 49 to a position where the air supply passage 44 is opened against the biasing force of the return spring 50. For this reason,
High-pressure refrigerant gas is supplied from the discharge chamber 3b to the crank chamber 2a through the air supply passage 44, and the differential pressure Δp between the crank chamber pressure Pc acting on the piston 17 and the suction pressure Ps (hereinafter,
The differential pressure Δp) is increased and the swash plate 13 is forcibly returned from the inclined position to the zero degree position.

By the way, during the compression operation of the compressor, the capacity variable control is automatically performed according to the cooling load. That is,
The differential pressure Δp acting on the piston 17 is adjusted by adjusting the opening degree of the bleed passage 45 that connects the crank chamber 2a and the suction chamber 3a according to the suction pressure Ps that is proportional to the cooling load. ing. The pressure control valve 52 for controlling this discharge capacity will be described below.

As shown in FIG. 6, in the valve case 47, a storage chamber 47a is located below the valve chamber 48.
A valve body 53 having a cylindrical shape with a lid for opening and closing the extraction passage 45 is accommodated in the accommodation chamber 47a. The valve body 53 is always urged in the valve closing direction by the return spring 54. A pressure sensitive chamber 55 is formed on the upper side of the head of the valve body 53, and the chamber 55 senses the suction pressure Ps in the suction chamber 3a through the bleed passage 45 on the downstream side of the valve body 53. And
The opening degree of the extraction passage 45 by the valve body 53 is adjusted by the fluctuation of the suction pressure Ps detected by the pressure sensing chamber 55 and the biasing force of the return spring 54. Further, the pressure-sensitive chamber 55 is connected to a chamber 47b formed between the inner peripheral surface of the valve body 53 and the bellows 56 by a communication passage 53a formed in the head of the valve body 53. An insertion hole 53b is formed in the valve body 53 so as to slidably pass through the second operating rod 51.

Therefore, the cooling load is large and the suction pressure Ps
Is large, the pressure in the pressure-sensitive chamber 55 is large and the valve body 53 is opened, so that the extraction passage 4 from the crank chamber 2a is opened.
A large amount of gas flows into the suction chamber 3a through 5, so that the differential pressure Δp acting on the piston 17 decreases, the stroke of the piston 17 increases, and the compressor operates with a large capacity. On the contrary, when the cooling load decreases and the suction pressure Ps decreases, the pressure in the pressure sensing chamber 55 also decreases, and the valve body 53 decreases the opening degree of the extraction passage 45. Therefore, the differential pressure Δp increases and the piston 17 decreases. Stroke is reduced and the compressor operates at a smaller capacity.

As shown in FIG. 2, the cylinder block 1 and the valve plate 20 are provided with a bleed passage 45A having a fixed throttle for communicating the crank chamber 2a with the suction chamber 3a, and the inner peripheral surface of the cylinder bore 1a during the compression stroke of the piston 17. The refrigerant gas blow-by to the crank chamber 2a is circulated to the suction chamber 3a through the clearance between the outer peripheral surface of the piston and the crank chamber 2a.

As shown in FIG. 6, the electromagnetic solenoid 3
A control device 57 including a microcomputer is connected to the coil 40 of No. 9. An air conditioner switch 58 as an external signal generator is connected to the control device 57. Further, although not shown, various commands and detection signals for the discharge temperature detector, the vehicle interior temperature detector, the suction pressure detector, the discharge pressure detector, etc. are input to the control device 57.

Next, the operation of the variable displacement compressor configured as described above will be described. When the compressor is stopped, the pressure Pc in the crank chamber, the pressure Ps in the suction chamber 3a and the pressure Pd in the discharge chamber 3b are the same as shown in FIG. The swash plate 13 is moved rearward, and the swash plate 13 is stopped and held at the zero degree position. Further, the hydraulic drive means K2 is stopped, and the valve body 49 of the second electromagnetic opening / closing valve 46 is held at a position where the air supply passage 44 is opened.

When the engine (not shown) is started in this state, the rotation of the engine is directly transmitted to the rotary shaft 4 via the belt 8 and the pulley 7, and the support arm 1 of the rotary support 9 is supported.
1 revolves around the axis of rotation 4. Therefore, the hinge mechanism K1 rotates the swash plate 13 at the zero degree position, and the zero capacity operation in the clutchless state is started.

Next, when the temperature inside the vehicle compartment increases and the cooling load increases, and the air conditioner switch 58 is turned on, the electromagnetic solenoid 3 is activated by the operation signal output from the controller 57.
9 is excited. For this reason, the valve body 38 closes the oil discharge passage 29 as shown in FIG. Is supplied with pressure oil. Therefore, as shown in FIG. 8, the spool 24 moves forward, the swash plate 13 is displaced from the zero degree position to the inclined position, and the compression operation is started. And the piston 17 is the cylinder bore 1.
The refrigerant gas reciprocated in a and sucked into the cylinder bore 1a from the suction chamber 3a is compressed and then discharged into the discharge chamber 3b.

The second operating rod 51 is moved downward in FIG. 6 together with the movable iron core 42 by the excitation of the electromagnetic solenoid 39, and the valve body 49 of the second electromagnetic on-off valve 46 is returned as shown in FIG. It is moved to a position where the air supply passage 44 is closed by the spring 50, and is moved from the discharge chamber 3b to the crank chamber 2a.
Supply of the refrigerant gas to the is stopped.

Although the spool 24 is stopped by the stopper 19 by supplying the control oil pressure to the pressure chamber 26,
After that, the control oil pressure is returned to the crank chamber 2a because the oil discharge passage 30b provided on the rotary shaft 4 is opened by the forward movement of the spool 24.

By the way, when the temperature in the vehicle compartment is low and the cooling load is small during the compression operation, the suction pressure Ps is low, so the valve body 53 of the pressure control valve 52 shown in FIG. As a result, the differential pressure Δp acting on the piston 17 is kept large, and the swash plate 13 is held at a small tilt angle for small capacity operation. On the contrary, since the suction pressure Ps is large when the cooling load is large, the pressure control valve 52
The valve body 53 increases the opening of the bleed passage 45, which reduces the differential pressure Δp and causes the swash plate 13 to move to the spool 2
It moves away from 4 and shifts to the maximum tilt angle. As described above, during the steady operation, the opening degree of the extraction passage 45 is adjusted by the pressure control valve 52 according to the variation of the suction pressure Ps proportional to the cooling load,
The differential pressure Δp acting on the piston 17 is adjusted, the tilt angle of the swash plate 13 is changed according to the cooling load, and the discharge capacity is adjusted.

When the air conditioner switch 58 is turned off by reducing the cooling load, the electromagnetic solenoid 39 is demagnetized in FIG. 7, and the first electromagnetic on-off valve 3 is demagnetized as shown in FIG.
Since the valve body 38 of No. 1 opens the discharge passage 29, the pressure chamber 2
The supply of the pressure oil to 6 is stopped, and the spool 24 becomes free. Further, since the second operating rod 51 opens the valve body 49 of the second electromagnetic opening / closing valve 46 against the biasing force of the return spring 50 and opens the air supply passage 44, the discharge chamber 3b to the crank chamber 2a. A high-pressure refrigerant gas is supplied therein, the swash plate 13 is forcibly returned to the zero degree position due to an increase in the differential pressure Δp acting on the piston 17, and the compressor is switched to the zero capacity operation.

Further, when the engine is stopped, the compressor is also stopped. In this stopped state, each chamber in the compressor has the same pressure, so that the swash plate 13 is held at the zero degree position as shown in FIG. When the compressor is restarted, the swash plate 13 rotates at the zero degree position. Therefore, the position of the center of gravity is set so that the swash plate 13 does not tilt due to the centrifugal force generated by this rotation.

In the first embodiment, as described above, the sleeve 12 having the spherical surface 12a is pushed by the spool 24 fitted to the rotary shaft 4 to return the swash plate 13 from the zero degree position to the inclined position. Therefore, the pushing operation of the sleeve 12 is smoothly performed, the swash plate 13 is smoothly switched from the zero degree position to the inclined position, and the capacity control characteristic can be improved.

A second embodiment of the present invention will be described with reference to FIG. In this embodiment, annular seal grooves are formed on the outer peripheral surface and the inner peripheral surface of the spool 24, and the seal rings 35 and 35A are engaged with both the seal grooves. Further, the sealing property in the pressure chamber 26 is improved so that the forward movement of the spool 24 can be performed more reliably when the control oil pressure is supplied from the oil supply pump 27 to the pressure chamber 26. The other structures and operations are the same as those in the first embodiment.

In this embodiment, the swash plate 13 is regulated to zero degree in order to bring the compressor into the zero capacity state, but the swash plate 13 is regulated to a slightly inclined position within a range where compression work is not performed. However, in the claims, the zero degree of the swash plate includes this point.

The present invention is not limited to the above embodiment, but can be embodied as follows. (1) As shown in FIG. 10, the spool 24 is housed in, for example, a cylindrical or arcuate spool housing chamber 1c formed in the cylinder block 1, and the end surface of the sleeve 12 is pushed by the spool 24. . 24c
Is a locking piece that is locked by the stopper 19 and prevents the spool 24 from being separated from the spool housing chamber 1c when the spool 24 moves to the forward end.

(2) The tilt angle changing means K3 is composed of an electromagnetic solenoid (not shown). (3) The oil supply pump 27 is used in the above embodiment, but a fluid pump that supplies the refrigerant gas in the crank chamber 2a or the suction chamber 3a to the pressure chamber is used.

(4) In the above embodiment, the refueling pump 27 is driven by the rotary shaft 4, but the refueling pump 27 is separated from the rotary shaft 4 and the refueling pump 27 is turned on only when the air conditioner switch 58 is turned on. For example, it is driven by an electric motor (not shown) to supply the lubricating oil to the pressure chamber 26. In this case, a separate mechanism is used to lubricate the sliding parts in the crank chamber 2a.

(5) When the spool 24 moves to the forward end and the pressure in the pressure chamber 26 exceeds the set value, the valve body 38 of the first electromagnetic opening / closing valve 31 opens the oil discharge passage 29 and the oil is discharged. A structure for supplying lubricating oil to the passage 30.

(6) Utilizing the clearance between the spool 24 and the cylinder block 1 as the oil discharge path.

[0049]

As described above in detail, according to the present invention, the fluid pump for sucking and discharging the fluid in the compressor, the pressure chamber for guiding the fluid discharged from the fluid pump, and the pressure chamber are provided. Since the swash plate is configured to have a spool that moves forward by the pressurized fluid and pushes the sleeve having the spherical surface for supporting the swash plate to return the swash plate from the zero degree position to the tilt position, the swash plate is easily tilted from the zero capacity state. There is an effect that the compression operation can be started by returning to.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a main part showing a first embodiment in which the present invention is embodied in a swash plate type variable displacement compressor.

FIG. 2 is a vertical cross-sectional view showing the entire swash plate type variable displacement compressor in a zero displacement state.

FIG. 3 is a cross-sectional view of the vicinity of a hinge mechanism.

4 is a cross-sectional view taken along the line AA of FIG.

FIG. 5 is a sectional view of an oil supply pump.

FIG. 6 is a vertical sectional view showing an electromagnetic opening / closing valve, an electromagnetic opening / closing valve, and a pressure control valve.

FIG. 7 is a vertical sectional view showing an electromagnetic opening / closing valve, an electromagnetic opening / closing valve, and a pressure control valve.

FIG. 8 is a cross-sectional view near a swash plate in an inclined position.

FIG. 9 is a cross-sectional view near a swash plate showing a second embodiment of the present invention.

FIG. 10 is a sectional view near a swash plate showing another example of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cylinder block, 1a ... Cylinder bore, 2 ... Front housing, 2a ... Crank chamber, 3 ... Rear housing, 3a ... Suction chamber, 3b ... Discharge chamber, 4 ... Rotation shaft, 9 ... Rotation support body, 11 ... Support arm, 12 ... Sleeve, 12a
... spherical surface, 13 ... swash plate, 13a ... bearing portion, 14 ... support pin, 17 ... piston, 24 ... spool, 26 ... pressure chamber,
27 ... Oil supply pump, 31 ... First electromagnetic opening / closing valve, 32 ... Inclination return oil supply passage, 39 ... Electromagnetic solenoid, 44 ... Air supply passage, 46 ... Second electromagnetic opening / closing valve, K1 ... Hinge mechanism, K2 ...
Hydraulic pressure (fluid pressure) driving means, K3 ... Inclination changing means.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Ken Mizuto 2-1-1 Toyota-cho, Kariya city, Aichi stock company Toyota Industries Corp.

Claims (2)

[Claims] 1. A cylinder block in which a plurality of cylinder bores for accommodating a one-sided piston are formed in parallel to each other is provided in a housing, and a crank chamber is provided in one of the housings to support a rotary shaft, and the rotary shaft is provided in the rotary shaft. The rotary support is fixed and a sleeve having a spherical surface is supported so as to be capable of reciprocating in the front-rear direction, a swash plate is rotatably supported on the spherical surface of the sleeve, and the rotary support is supported by a hinge mechanism. A swash plate is mounted so as to be capable of reciprocal tilting in the front-rear direction, and the swash plate is rocked back and forth by the rotation of the rotary shaft to reciprocate the one-side piston in the cylinder bore, so that the refrigerant gas sucked from the suction chamber is transferred to the cylinder bore. It is compressed inside and discharged to the discharge chamber, and the tilt angle of the swash plate is changed by the differential pressure between the crank chamber pressure acting on the back side of the piston and the suction pressure acting on the front side. In the clutchless rocking swash plate type variable displacement compressor configured to adjust the discharge capacity by changing the reciprocating stroke of the piston, the tilt angle of the swash plate is tilted by an off signal from an external signal generator. And a fluid pressure drive means for returning the inclination angle of the swash plate from zero degree to an inclined position in response to an ON signal from an external signal generator. Is a fluid pump that sucks and discharges the fluid in the compressor, a pressure chamber that guides the fluid discharged from the fluid pump, and a pressurized fluid that is supplied to the pressure chamber to move forward to support the swash plate. It is composed of a spool that pushes a sleeve having a spherical surface to return the swash plate from a zero degree position to an inclined position, and an oil discharge path that discharges oil from the pressure chamber to the crank chamber after the spool is operated. Clutchless rocking swash plate type variable displacement compressor. 2. The spool according to claim 1, wherein the spool is formed in a cylindrical shape, and the spool reciprocates in a front-rear direction between an outer peripheral surface of a rotating shaft and an inner peripheral surface of a center hole of a cylinder block that passes through the rotating shaft. Clutchless rocking, which is movably fitted and has a seal ring between the outer peripheral surface of the spool and the inner peripheral surface of the center hole and between the inner peripheral surface of the spool and the outer peripheral surface of the rotating shaft. Swash plate type variable capacity compressor.