JP3084976B2 - Lubrication structure for one-sided piston variable displacement compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a crankcase, a suction chamber,
A discharge chamber and a cylinder bore connecting these chambers are defined, and a plurality of cylinder bores are arranged around a rotation axis, and a single-headed piston is slidable on a rotation shaft in a housing that accommodates a single-headed piston in a reciprocating linear motion within the cylinder bore. In addition to supporting the swash plate so as to be tiltable, the swash plate is linked to the rotating support on the rotating shaft so as to be tiltable, and the tilt angle of the swash plate is controlled by the difference between the pressure in the crank chamber and the suction pressure through a single-ended piston. The present invention relates to a lubricating structure in a one-side piston type variable displacement compressor.

[0002]

2. Description of the Related Art In this type of variable displacement compressor, when the pressure in the crank chamber is increased, the inclination of the swash plate is reduced and the discharge capacity is reduced. When the pressure in the crank chamber is reduced, the inclination of the swash plate is increased and the discharge capacity is increased. Increase. That is, the crank chamber is a control pressure chamber,
The pressure in the crank chamber is controlled by introducing refrigerant gas in the discharge pressure region. Therefore, a lip seal is interposed between the housing and the rotating shaft to prevent the leakage of the refrigerant gas in the crank chamber along the peripheral surface of the rotating shaft protruding from the housing to the outside.

[0003] Oil is mixed in the refrigerant gas, and this oil is used for lubrication of a portion of the compressor that requires lubrication. The lip seal for preventing refrigerant gas leakage from the crank chamber is also lubricated by oil in the refrigerant gas. However, when the discharge capacity is small, the circulation amount of the refrigerant gas is small, and lubrication of the lip seal is insufficient with only oil in the refrigerant gas.

Japanese Patent Laid-Open Publication No. Sho 55-176492 discloses a configuration in which oil stored in the bottom of a crank chamber is supplied to a sliding portion of a ball that determines the center of oscillation of a swash plate. An oil deflector is provided on a peripheral wall of the crank chamber, and an oil passage is provided from the oil deflector to a sliding portion of the ball. The oil that has been scraped up along the peripheral wall of the crankcase by the rotation of the rotor is collected by the oil deflector to the inlet of the oil passage, and the oil introduced into the oil passage is supplied to the sliding portion of the ball.

[0005]

The oil which has been lifted up to the oil deflector is guided to the inlet of the oil passage by the wind pressure accompanying the rotation of the rotor, but thereafter only flows down in the oil passage by its own weight. The oil passage is provided in a radial direction of the rotating shaft, and an inlet thereof is directed in a direction orthogonal to the circumferential direction. Therefore, the wind pressure acts as a negative pressure at the inlet of the oil passage, and it is difficult to introduce oil into the oil passage.

SUMMARY OF THE INVENTION An object of the present invention is to provide a lubricating structure in a one-sided piston type variable displacement compressor which can efficiently supply oil accumulated at the bottom of a crankcase to a portion requiring lubrication.

[0007]

According to the present invention, there is provided:
A crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connecting these chambers are formed.A plurality of cylinder bores are arranged around a rotation axis, and a single-sided piston is accommodated in the cylinder bore so as to reciprocate linearly. While supporting the swash plate so as to be slidable and tiltable on the rotating shaft, the swash plate is linked to the rotating support on the rotating shaft in a tiltable manner,
Intended for a one-sided piston type variable displacement compressor that controls the tilt angle of a swash plate by a difference between a pressure in a crank chamber and a suction pressure through a single-headed piston, and an oil scraping section is provided on a peripheral side of the rotary support, Providing an oil introduction passage in the rotating support, providing an introduction port of the oil introduction passage in the oil scraping section, and directing the introduction port in the rotation direction of the rotating support,
A portion requiring lubrication in the compressor and the oil introduction passage were connected by a lubrication passage.

[0008]

The oil-raising section lifts up the stored oil at the bottom of the crankcase as the rotary support rotates. The oil scooped up by the oil scooping section enters the oil introduction passage from an inlet on the oil scooping section. Since the inlet rotates around the rotation direction of the rotary support, the refrigerant gas in the crank chamber flows into the inlet. This inflow action of the refrigerant gas acts as a pushing pressure on the oil in the oil introduction passage. Therefore, the oil in the oil introduction passage is sent to the portion requiring lubrication in the compressor through the lubrication passage by the pushing pressure.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will now be described with reference to FIGS.
Explanation will be given based on FIG. As shown in FIG. 1, a front housing 2 is joined to a front end of a cylinder block 1 which is a part of a housing of the entire compressor. The rear housing 3 is joined and fixed to the rear end of the cylinder block 1 via a valve plate 16, valve forming plates 17A and 17B, and a retainer forming plate. An angular bearing 4 is mounted in the front housing 2. A disk-shaped rotary support 5 is supported on the angular bearing 4, and a rotary shaft 6 is fixed to the rotary support 5. The angular bearing 4 receives both the load in the thrust direction and the load in the radial direction acting on the rotary shaft 6 via the rotary support 5.

As shown in FIGS. 2 and 3, a support arm 5a, an inclination regulating protrusion 5b and an oil scraping protrusion 5c are provided on the front surface of the rotary support 5. An oil introduction passage 42A and a lubrication passage 42B are provided in the rotary support 5.
The oil introduction passage 42A extends from the lifting end face 5d of the oil lifting protrusion 5c to the back surface of the rotary support 5. The lubrication passage 42B branches off from the middle of the oil introduction passage 42A and extends to the front end surface of the inclination restricting projection 5b. Inclination restriction projection 5
The front end surface of the b oil-escape groove 5b ₁ are recessed. Lubricating passageway 42B is connected on the groove 5b ₁ missed oil.

The end face 5d of the oil scraping projection 5c is
The rotation support 5 rotates in the direction of arrow P in FIG. Therefore, the introduction port 42a of the oil introduction passage 42A faces in the rotation direction of the rotary support 5. Further, the outer edge 5d ₁ end face 5d of the oil scraped up projection 5c is in close proximity to the inner peripheral wall of the front housing 2.

The front end of the rotating shaft 6 projects outside from the crank chamber 2a via the front housing 2, and a pulley 7 is screwed to the projecting end. The pulley 7 is operatively connected to a vehicle engine via a belt 7a. A lip seal 53 is interposed between the front end of the rotating shaft 6 and the front housing 2. The lip seal 53 prevents pressure leakage in the crank chamber 2a.

An annular lubrication passage 43 is provided at a position where the lip seal 53 is mounted, and an oil introduction passage 42A is connected to the lubrication passage 43. Further, a lubrication passage 44 is connected to the lubrication passage 43. The lubrication passage 44 is for lubrication of the angular bearing 4.

A spool 8 is fitted and accommodated in the center of the cylinder block 1 so as to be slidable in the axial direction of the rotating shaft 6. The spool 8 includes a large-diameter cylindrical portion 8a and a small-diameter cylindrical portion 8b, and the rear end of the rotating shaft 6 protrudes into the large-diameter cylindrical portion 8a. This protruding end is rotatably supported by a spool 8 via a radial bearing 9. The radial bearing 9 is slidable with respect to the rotating shaft 6. A return spring 2 is provided between the inner end of the small-diameter cylindrical portion 8b and the rear end of the rotary shaft 6.
The spool 8 is always pressed against the valve plate 16 by the spring action of the return spring 21. When the spool 8 is in contact with the valve plate 16, the end surface of the large-diameter cylindrical portion 8 a coincides with the end surface of the cylinder block 1.

The rear housing 3 accommodates an electromagnetic solenoid 36 for returning the tilt angle. The movable iron core 38 which is attracted to the fixed iron core 37 side by the excitation of the tilt angle returning electromagnetic solenoid 36 separates the spool 8 in contact with the valve plate 16 from the valve plate 16. When the spool 8 is separated from the valve plate 16, the end surface of the large-diameter cylindrical portion 8a projects from the end surface of the cylinder block 1 to the crank chamber 2a.

A swash plate support 10 having a spherical shape is slidably supported on the rotating shaft 6, and a swash plate 11 is supported on the swash plate support 10 so as to be tiltable in the axial direction of the rotating shaft 6. . Connecting pieces 12A and 12B are fixed to the swash plate 11. As shown in FIG. 2, a pair of guide pins 13 and 14 are fixed to the connecting pieces 12A and 12B, respectively.
A support pin 15 is rotatably supported by a.

The pair of guide pins 13 and 14 are slidably fitted to both protruding ends of a support pin 15 protruding from the support arm 5a to both right and left sides. The swash plate 11 can be tilted and rotated about the swash plate support 10 in the axial direction of the rotation shaft 6 by the cooperation of the support pin 15 rotatably supported on the support arm 5a and the pair of guide pins 13 and 14. It can rotate integrally with the shaft 6. The tilt of the swash plate 11 is determined by the slide guide relationship between the support pin 15 and the guide pins 13 and 14,
The guide is guided by the sliding action of the swash plate support 10 and the support action of the swash plate support 10.

The maximum inclination angle of the swash plate 11 is regulated by the contact between the inclination regulating protrusion 5b of the rotary support 5 and the swash plate 11.
The minimum inclination angle of the swash plate 11 is determined by the spool 8 and the swash plate support 10.
Is regulated by abutment. The minimum inclination angle of the swash plate 11 when the spool 8 is in contact with the valve plate 16 is 0.
°.

A plurality of cylinder bores 1a are provided in the cylinder block 1 so as to be connected to the crank chamber 2a, and a single-headed piston 19 is accommodated in each cylinder bore 1a. A pair of shoes 20 is fitted into the neck 19 a of the single-headed piston 19. The peripheral portion of the swash plate 11 enters between the two shoes 20, and the end surfaces of the two shoes 20 contact both surfaces of the swash plate 11. Therefore, the rotational movement of the swash plate 11 is converted into a reciprocating swing of the single-headed piston 19 via the shoe 20, and the single-headed piston 19 moves back and forth in the cylinder bore 1a.

As shown in FIGS. 1 and 5, a suction chamber 3a and a discharge chamber 3b are defined in the rear housing 3. A suction port 16a and a discharge port 16b are formed on the valve plate 16, and the valve forming plate 17
A suction valve 17a and a discharge valve 17b are formed on A and 17B. The refrigerant gas in the suction chamber 3a is a single-headed piston 1
9 moves from the suction port 16a to the suction port 1
7a is pushed back and flows into the cylinder bore 1a. The refrigerant gas flowing into the cylinder bore 1a is
As a result, the discharge valve 17b is pushed out of the discharge port 16b and discharged to the discharge chamber 3b. The opening of the discharge valve 17b is regulated by contacting the retainer 18a on the retainer forming plate 18.

As shown in FIGS. 1, 5 and 6, a discharge flange 39 is formed on the upper surface of the cylinder block 1, and a discharge port 1c is provided in the discharge flange 39. The outlet 1c is connected to the inlet 1d via an external refrigerant circuit.

An oil separation hole 39a is formed in the outlet 1c. The oil separation hole 39a has a circular cross section. The oil separation hole 39a is connected to the discharge chamber 3b through the discharge passage 40.
And the refrigerant gas in the discharge chamber 3b
9a is discharged and sprayed. The discharge passage 40 is directed to the eccentric position of the oil separation hole 39a having a circular cross section.
The refrigerant gas discharged from the outer peripheral wall 39 of the oil separation hole 39a
It is sprayed on the oil separation hole 39a along the line c.

Mist oil is mixed in the refrigerant gas, and the oil is separated from the refrigerant gas by spraying the refrigerant gas onto the oil separation hole 39a. The refrigerant gas discharged from the discharge passage 40 to the oil separation hole 39a turns along the circumferential wall surface 39c of the oil separation hole 39a, and the oil in the refrigerant gas is centrifugally separated. The bottom 39b of the oil separation hole 39a is located below the outlet of the discharge passage 40, and the oil centrifugally separated from the refrigerant gas accumulates in the bottom 39b. That is, the bottom 39b is in the oil storage chamber 39.
b. The discharged refrigerant gas flows out from the outlet 36b to the external refrigerant circuit, and the separated oil stays in the oil separation hole 39a.

The stroke of the single-headed piston 19 changes according to the pressure difference between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a through the single-headed piston 19. That is, the inclination angle of the swash plate 11 that affects the compression capacity changes. The crank chamber 2a communicates with the suction chamber 3a via a throttle passage 1b, and the refrigerant gas in the crank chamber 2a flows out to the suction chamber 3a via the throttle passage 1b. The pressure in the crank chamber 2a is controlled by a control valve 22 mounted on the lower wall of the cylinder block 1 and the front housing 2.

The internal structure of the control valve 22 will be described with reference to FIG. The solenoid housing 23 has a solenoid 24
The fixed iron core 25 is accommodated and fixed. Fixed iron core 25
A guide rod 26 is slidably supported through a center axis of the guide rod 26. A movable iron core 27 is provided on the guide rod 26.
Are fixed, and can be moved toward and away from the fixed iron core 25 by the guide action of the guide rod 26. Movable iron core 27
The moving range of the fixed iron core 25 and the solenoid housing 23
And the spring receiver 23a. Guide rod 2
A spring receiver 26 a is formed at one end of the valve 6, and a valve opening forcing spring 49 is interposed between the spring receiver 26 a and the end wall 23 b of the solenoid housing 23. The movable iron core 27 is urged in a direction away from the fixed iron core 25 by a spring action of a valve opening forcing spring 49.

A valve housing 28 is fixedly connected to the solenoid housing 23.
A spherical valve body 29 is accommodated in the inside 8. The valve housing 28 is provided with a discharge pressure introduction port 28a, a suction pressure introduction port 28b, and a control port 28c. The discharge pressure introduction port 28a communicates with the discharge chamber 3b via the discharge pressure introduction passage 30, and the suction pressure introduction port 28b communicates with the suction chamber 3a via the suction pressure introduction passage 31.
The control port 28c is connected to the crank chamber 2 through the control passage 32.
a.

A return spring 33 is interposed between the end wall of the valve housing 28 and the valve body 29, and the valve body 29 receives the spring action of the return spring 33 in a direction to close the valve hole 28d. When the valve hole 28d is closed, the discharge pressure introduction port 28
a is disconnected from the control port 28c.

A diaphragm 34 is interposed between the solenoid housing 23 and the valve housing 28. A pressure rod 35 is slidably housed in the valve housing 28 so as to always shut off the suction pressure introduction port 28b and the control port 28c. Press rod 3
One end of 5 is fixed to the diaphragm 34. A pressing spring 50 is interposed between the spring receiver 23a and the diaphragm 34. The pressure spring 50 opposes the suction pressure via the diaphragm 34. The pressing rod 35 is a pressing spring 5
It is always in contact with the valve body 29 by the spring action of zero.

As shown in FIG. 4, when the valve element 29 closes the valve hole 28d and the movable iron core 27 is in contact with the fixed iron core 25, the guide rod 26
Slightly away from When the solenoid 24 is demagnetized, the movable iron core 27 comes into contact with the spring receiver 23 a by the spring action of the valve opening forcing spring 49. In this contact state, the guide rod 26 pushes the pressing rod 35 toward the valve body 29, and the valve opening of the valve body 29 is maximized as shown by the chain line in FIG.

The oil storage chamber 39b communicates with the discharge pressure introduction port 28a via the oil recovery passage 41. A region in the control valve 22 from the discharge pressure introduction port 28a to the valve hole 28d is a discharge pressure region, and the oil storage chamber 39b communicates with the discharge pressure region via an oil recovery passage 41.

In the state shown in FIG. 1, both the solenoid 24 and the tilt return electromagnetic solenoid 36 are in the excited state. When the solenoid 24 is excited, the movable iron core 27 is
5, and the guide rod 26 is separated from the diaphragm 34. Under this separated state, the diaphragm 34 is displaced in accordance with the fluctuation of the suction pressure introduced from the suction pressure introduction port 28b, and this displacement is
Is transmitted to the valve body 29 through When the suction pressure is high (the cooling load is high), the diaphragm 34 bends and deforms toward the guide rod 26 against the spring action of the pressing spring 50, and the valve opening of the valve body 29 decreases. When the pressure in the crank chamber 2a is higher than the suction pressure, the refrigerant gas in the crank chamber 2a flows out to the suction chamber 3a via the throttle passage 1b. Therefore, if the valve opening of the valve body 29 becomes small, the flow rate of the high-pressure refrigerant gas from the discharge chamber 3b through the discharge pressure introduction passage 30 becomes small or zero. Therefore, the pressure in the crank chamber 2a decreases, and the swash plate inclination angle increases. vice versa,
When the suction pressure is low (the cooling load is small), the diaphragm 34 is actuated by the spring
The valve body 29 is bent and deformed to the side, and the valve opening of the valve body 29 increases. As the valve opening of the valve body 29 increases, the flow rate of the high-pressure refrigerant gas from the discharge chamber 3b through the discharge pressure introduction passage 30 increases. Therefore, the pressure in the crank chamber 2a increases, and the swash plate inclination angle decreases.

The oil separation chamber 39a is a discharge pressure area, and a discharge pressure is applied to the oil surface stored in the oil storage chamber 39b. Therefore, when the flow rate of the refrigerant passing through the valve hole 28d is increased, the oil stored in the oil storage chamber 39b is also removed from the oil recovery passage 41.
, Flows down into the discharge pressure introduction port 28a, and flows into the crank chamber 2a through the valve hole 28d.

The rotary support 5 rotates in the direction of arrow P in FIG. When the amount of stored oil at the bottom of the crank chamber 2a is large, the inlet 42a of the oil introduction passage 42A rushes into the stored oil, and the stored oil enters the oil introduction passage 42A. The introduction port 42a repeatedly enters into the stored oil with the rotation of the rotary support 5, and a pressure is generated in the oil in the oil introduction passage 42A every time the introduction port 42a enters. Therefore, the oil in the oil introduction passage 42A is sent to the lubrication passage 43 and the lubrication passage 42B by the pushing pressure. The oil sent to the lubrication passage 43 lubricates the lip seal 53 and the angular bearing 4. The oil sent to the lubricating passage 42 </ b> B
b leaks out to the front end face. The oil was fed into the lubricating passage 42B is refluxed through the groove 5b ₁ missed oil to the crank chamber 2a when the swash plate 11 and the inclination angle restricting protrusion 5b abuts.

Even when the amount of stored oil is so small that the inlet 42a cannot enter the stored oil at the bottom of the crank chamber 2a, the raised end face 5d of the oil lifting protrusion 5c also lifts the stored oil. Outer edges 5d ₁ oyster raised edge 5d orbits close to the inner peripheral wall surface of the front housing 2. Therefore, the percentage fall leakage from between the inner peripheral wall surface of the oil scraping up edge scooping oil was by 5d outer edge 5d ₁ and the front housing 2 is reduced, inlet 42a correspondingly
The amount of oil introduced into the tank increases. Since the introduction port 42a rotates in the rotation direction P of the rotary support 5, the refrigerant gas in the crank chamber 2a flows into the oil introduction passage 42A.
The oil introduced into the introduction port 42a is pushed into the oil introduction passage 42A by the inflow action of the refrigerant gas.

Accordingly, the oil stored at the bottom of the crank chamber 2a is efficiently used for lubricating the front end surfaces of the lip seal 53, the angular bearing 4, and the inclination restricting projection 5b by the action of the oil raising projection 5c.

When the inclination of the swash plate is controlled in accordance with the fluctuation of the suction pressure, the contact between the swash plate 11 and the inclination regulating protrusion 5b is repeated. Rotary support 5 to reduce the weight of the compressor
When the swash plate 11 is made of aluminum, the contact portion is worn due to repeated contact between the swash plate 11 and the inclination restricting projection 5b. When this abrasion occurs, the maximum discharge capacity changes. The oil supplied to the front end face of the inclination restricting projection 5b prevents this wear and prevents a change in the maximum discharge capacity.

When the solenoid 24 is demagnetized, the movable iron core 27
Is separated from the fixed iron core 25 by the spring action of the valve opening forcing spring 49 and contacts the spring receiver 23a. This movable iron core 2
7, the valve opening of the valve body 29 is maximized, and the pressure in the crank chamber 2a is rapidly increased. When the tilt-return electromagnetic solenoid 36 is demagnetized, the spool 8 moves and abuts on the valve plate 16 by the spring action of the return spring 21. The end surface of the large-diameter cylindrical portion 8 a coincides with the end surface of the cylinder block 1 by this moving contact. Therefore, the crankcase 2
The inclination of the swash plate 11 immediately becomes 0 ° due to the rapid pressure increase in the position a and the movement of the spool 8. Accordingly, the discharge capacity becomes zero, and the same state as the compressor no-load state when the clutch is disconnected in the clutch mounted type compressor is obtained. This compressor no-load state directs the full output of the vehicle engine to drive the vehicle.

The transition to the compressor no-load state is performed when the air conditioner is turned off, the vehicle is accelerated, and the like. In such a compressor having a clutchless structure, the use condition of the lip seal 53 for preventing the leakage of the refrigerant gas from the crank chamber 2a along the peripheral surface of the rotating shaft 6 is severe. That is, as long as the vehicle engine is driven, the rotary shaft 6 is rotating. In such a long-term continuous rotation, the shortage of the oil accelerates the deterioration of the lip seal 53 due to the sliding contact with the rotary shaft 6. In particular, when the inclination angle of the swash plate is reduced to zero, the inside of the crank chamber 2a is rapidly increased to a level corresponding to the discharge pressure.
Results in a relative decrease in sealing performance.

In the present embodiment, the oil scraped up by the rotation of the rotary support 5 is constantly supplied to the lip seal 53, so that the sealing performance of the lip seal 53 is greatly improved. Therefore, even when the inside of the crank chamber 2a is rapidly increased to the discharge pressure in order to reduce the inclination angle of the swash plate to zero, the high-pressure refrigerant gas in the crank chamber 2a keeps the gap between the peripheral surface of the rotating shaft 6 and the lip seal 53. Does not leak. Also, the rotating shaft 6
Also in the clutchless structure of this embodiment in which the state in which the rotation continues for a long period of time is normal, the deterioration of the lip seal 53 due to the sliding contact with the rotating shaft 6 is suppressed, and the durability of the lip seal 53 is extended.

Although the discharge capacity has become zero, if the rolling resistance in the angular bearing 4 is large, the compressor load remains, and the power loss in the zero discharge capacity state increases. In this embodiment, when the inclination angle of the swash plate becomes zero, the control valve 2
The second valve hole 28d has the maximum opening degree, and the pressure in the crank chamber 2a rises sharply to the discharge pressure. Since the maximum opening degree of the valve hole 28d continues for a while, all the stored oil in the oil storage chamber 39b is recovered to the crank chamber 2a. The oil thus recovered is used for lubrication of the angular bearing 4 and is used to suppress the rolling resistance in the angular bearing 4.
Therefore, the presence of the oil separation hole 39a contributes to approaching the compressor load state at the swash plate inclination of zero to the compressor no-load state when the clutch is disengaged in the clutch-mounted compressor, and at the time of the discharge capacity zero state. Power loss is suppressed.

Even if the compressor is operated with the inclination angle of the swash plate 11 at 0 °, the discharge capacity becomes zero, so that the refrigerant gas pressure in the compressor and in the external refrigerant circuit becomes uniform. for that reason,
The swash plate 11 cannot be tilted by reducing the pressure in the crank chamber 2a. In the present embodiment, the swash plate 11 is tilted by exciting the tilt-return electromagnetic solenoid 36.

The present invention is, of course, not limited to the above embodiment, but can be applied to, for example, a one-sided piston type variable displacement compressor having a clutch.

[0043]

As described above in detail, according to the present invention, the stored oil at the bottom of the crank chamber is scraped by the oil scraping section with the rotation of the rotary support, and the oil is lifted from the inlet directed to the rotation direction of the rotary support. Since the oil is introduced into the oil introduction passage, there is an excellent effect that the stored oil at the bottom of the crankcase can be efficiently supplied to the portion of the compressor that requires lubrication.

[Brief description of the drawings]

FIG. 1 is a side sectional view of an entire compressor according to one embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a perspective view of a rotary support.

FIG. 4 is a side sectional view of a control valve.

FIG. 5 is a sectional view taken along line BB of FIG. 1;

FIG. 6 is a sectional view taken along line CC of FIG. 1;

[Description of References] 2a: crank chamber, 5: rotating support, 5c: oil scraping protrusion, 11: swash plate, 42A: oil introduction passage, 42a: introduction port, 42B, 43, 44 ... lubrication passage.

Continuation of the front page (72) Inventor Tomohiko Yokono 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (58) Field surveyed (Int. Cl. ⁷ , DB name) F04B 27/08

Claims (1)

(57) [Claims] 1. A crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connecting these chambers are defined, a plurality of cylinder bores are arranged around a rotation axis, and a single-headed piston can reciprocate linearly in the cylinder bore. A swash plate is slidably and tiltably supported on a rotating shaft in a housing to be accommodated, and the swash plate is linked to a rotating support on the rotating shaft so as to be capable of tilting. A one-side piston type variable displacement compressor that controls the inclination angle of the swash plate by a difference through the oil pump, wherein an oil scraping section is provided on the peripheral side of the rotary support, and an oil introduction passage is provided in the rotary support, An inlet for the oil introduction passage is provided in the raising portion, and the introduction port is oriented in the rotation direction of the rotary support, and a portion requiring lubrication in the compressor and the oil introduction passage are connected by a lubrication passage. Lubrication structure for a one-sided piston type variable displacement compressor.