KR0125495B1 - Wobbling swash plate type compressor - Google Patents

Abstract

The lubricity of each sliding part in the crank chamber in the zero-capacity state in which the inclination angle of the inclination plate is operated at zero is improved.

The rotary support 9 is fitted and fixed to the rotary shaft 4, and the rotary support 9 is mounted to the rotary support 9 via a hinge mechanism K1 so as to reciprocate inclined in the front-rear direction. By rotating the inclined plate 13 back and forth by the rotation of), the migraine piston is reciprocated in the cylinder bore, and the refrigerant gas sucked from the suction chamber is compressed in the cylinder bore to be discharged into the discharge chamber. The inclination plate inclination angle zero forced change mechanism K2 which returns the inclination angle of the inclination plate 13 to zero degree is provided. At the start of the compressor, a control device 57 is provided which operates the inclined plate inclination angle return drive mechanism K2 for a predetermined time by the timer 59 and temporarily maintains the inclined plate 13 in an inclined state at zero degrees.

Description

Oscillating Inclined Plate Variable Capacity Compressor

1 is a longitudinal sectional view of an essential part showing an embodiment in which the present invention is embodied as an inclined plate type variable displacement compressor.

2 is a longitudinal sectional view of a zero displacement state showing the entire gradient plate type variable displacement compressor.

3 is a cross sectional view near the hinge mechanism.

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

5 is a sectional view of an oil supply pump.

6 is a longitudinal sectional view showing an electromagnetic directional valve, an electromagnetic on-off valve and a pressure control valve.

FIG. 7 is a longitudinal sectional view showing an electromagnetic directional valve, an electromagnetic on-off valve and a pressure control valve. FIG.

8 is a longitudinal cross-sectional view showing a large capacity state of the inclined plate type variable displacement compressor.

9 is a sectional view of the vicinity of an inclined plate showing another example of the present invention.

* Description of the symbols for the main parts of the drawings *

1: cylinder block, 1a: cylinder bore,

2: front housing, 2a: crankcase,

3: rear housing, 3a: suction chamber,

3b: discharge chamber, 4: rotating shaft,

a: rotation support, 11: support arm,

13: inclined plate, 13a: bearing part,

14: support pin, 17: piston,

24: spool, 26: pressure chamber,

27: oil supply pump, 31: electromagnetic directional valve,

32: oil supply passage for inclination angle return, 39: electronic solenoid,

44: air supply passage, 46: solenoid valve,

K1: hinge mechanism, K2: inclination plate inclination return mechanism,

K3: Force change mechanism of the inclined plate inclination.

Industrial use

The present invention relates to a swinging gradient plate type variable displacement compressor, for example, used in an air conditioner of an automobile.

Conventional technology

In general, a variable displacement compressor for automobiles is equipped with an electromagnetic clutch that cuts off and connects the power of the engine. Rotational movement is transmitted to the compressor via the belt transmission mechanism and the electromagnetic clutch. As a result, the compressor starts and stops with a large capacity each time the air conditioner switch is turned on and off, and the durability of the compressor decreases due to frequent repetition of the electromagnetic clutch and the joint. It is difficult to install because of the installation space in the engine room.

In order to solve this problem, a rocking inclination plate type compressor having a clutch mechanism has been proposed. As this compressor, there is one specified in Japanese Patent Laid-Open No. 3-37378. The compressor controls the pressure difference between the crank chamber in which the inclined plate is accommodated and the operating chamber in the cylinder bore of the suction stroke, thereby continuously changing the inclination angle of the inclined plate to vary the maximum stroke of the piston. In addition, the compressor is provided with a passage opening and closing device at the inlet to the suction chamber or the suction chamber connected to the suction chamber, and the crank chamber and the suction chamber are always in communication with the tightened narrow tube, and the discharge chamber and the crank chamber have a pressure below the predetermined value of the suction chamber. It is provided with the pressure control valve which opens when it turns into.

When the discharge from the compressor is unnecessary, the passage opening / closing valve is closed and the pressure of the suction chamber is lowered. The pressure control valve is opened to allow the high pressure gas to flow into the crank chamber, thereby increasing the pressure of the crank chamber, The angle of inclination shifts in the direction of the minimum value. Because of this, the stroke of the piston is at its minimum and the required torque is at a very small value. In addition, the inside of the compressor is reciprocated by a very small piston required to generate a gas flow flowing from the discharge chamber to the crank chamber through each sliding part, and then through the outflow hole, which is the throttle part (throttle part), to the suction chamber. It is lubricated.

Challenges to the Invention

In the conventional compressor, when discharge from the compressor is unnecessary, a small amount of refrigerant gas is circulated inside the compressor for lubrication of each sliding part in a state in which the suction pipe is closed by the on / off valve. However, since the refrigerant gas is circulated only inside the compressor, there arises a problem that, in particular, each sliding part in the crankcase becomes poor in lubrication. In other words, when the compressor is stopped during large-capacity operation, the high pressure refrigerant gas is supplied from the discharge chamber into the crank chamber to increase the differential pressure acting on the piston and displace the inclined plate at the minimum inclination angle. A large amount of refrigerant gas liquefies and accumulates in the crank chamber. Even if the compressor is started in the state where liquid refrigerant is present and operation continues at the minimum capacity, the liquid refrigerant is difficult to gasify, so the oil attached to each sliding part is washed off by the circulation of the liquid refrigerant inside the compressor, thereby degrading lubricity. It also increases power loss.

The applicant of the present application has recently proposed a variable capacity compressor of a method of operating in a zero capacity state by setting the inclination angle of the inclined plate to zero to further reduce power loss in the clutchless state of the compressor. The problem of one lack of lubrication likewise occurs.

SUMMARY OF THE INVENTION An object of the present invention is to provide a rocking inclination plate type variable capacity compressor which can solve the problems of the prior art and improve the lubricity of each sliding part in the compressor in a zero capacity state in which the inclination angle of the inclination plate is operated at about zero degrees. To provide.

Means to solve the problem

In order to achieve the above object, the present invention provides a cylinder block in which a plurality of cylinder bores for accommodating a migrating piston in a housing are formed in parallel with each other, and a crank chamber is installed in the housing to support a rotating shaft, and a rotating support on the rotating shaft. And swivel the swash plate forward and backward by the rotation of the rotating shaft while mounting the slop plate in the forward and backward direction via a hinge mechanism to the rotating support and reciprocating the migrating piston in the cylinder bore. The refrigerant gas sucked from the gas is compressed in the cylinder bore to be discharged into the discharge chamber, and the inclination angle of the inclined plate is changed by the pressure difference between the crankcase pressure acting on the back of the piston and the bore pressure acting on the front. The reciprocating stroke of the In the rocking inclination plate type variable capacity compressor configured to adjust the discharge capacity, the inclination angle forcibly changing mechanism of the inclination plate for changing the inclination angle of the inclination plate to the non-operational position, and returning the inclination angle of the inclination plate from the non-moving position to the movable position A control device for releasing the inclination plate inclination angle forcibly changing mechanism in the inoperative operation state of the inclination plate inclination angle return mechanism and the compressor, and temporarily operating the inclination plate inclination angle return mechanism for a predetermined time to temporarily hold the inclination plate in the non-operation position in a compressed state. Equipped with. Here, the non-moving position indicates the inclination plate inclination angle at which the compressor stops functioning as the compressor without substantially discharging, and for example, the inclination angle of the inclination plate can be set to zero.

Action

In the present invention, the inclination plate inclination angle return means is temporarily operated by the control device in the zero-capacity operation state of the compressor in which the inclination plate is maintained at the non-operational inclination angle, so that the inclination plate is kept in the inclination state in the non-operation position. For this reason, the compression operation of the compressor is performed, and the liquid refrigerant existing in the compressor is discharged from the discharge chamber to the external refrigerant gas discharge tube, and the refrigerant gas is sucked into the suction chamber from the external refrigerant gas suction tube, and this refrigerant gas is discharged from the cylinder bore. After being compressed, it is discharged to the discharge chamber. In the cylinder bore operating chamber, refrigerant gas containing lubricating oil leaks into the crank chamber through the gap between the outer circumferential surface of the piston and the inner circumferential surface of the cylinder bore, and the liquid refrigerant in the crank chamber is lost. For this reason, the inclined plate inclination angle return mechanism is stopped, and the inclined plate is displaced by the inclined plate inclination angle change mechanism. It is lubricated.

Example

EMBODIMENT OF THE INVENTION Hereinafter, one Example which actualized this invention is described based on drawing.

2, the front housing 2 which forms the crank chamber 2a is joined and fixed to the front side end surface of the cylinder block 1 in which the several cylinder bore 1a was formed. The rear housing 3 which partitions the suction chamber 3a and the discharge chamber 3b is joined and fixed to the rear end. The cylinder block 1 and the front housing 2 are located in the crank chamber 2a so that the rotation shaft 4 is rotatably supported via the radial bearings 5 and 6. The pulley 7 is fixed to the outer end of the rotary shaft 4, and the rotational motion of the engine, which is the driving source, is directly transmitted by the belt 8.

A rotary bearing 9 is fitted and fixed to the rotary shaft 4, and a thrust bearing 10 for supporting a thrust load during the compression operation is interposed between the support 9 and the inner wall of the front housing 2. The support arm 11 which has the insertion hole 11a is integrally formed in this rotating support body 9. On the other hand, the inclined plate support 12 having the spherical surface 12a is supported on the rotating shaft 4 so as to reciprocate in the front-rear direction along the outer circumferential surface of the rotary shaft 4, and the inclined plate support 12 is spherical on the inclined plate support 12. It is supported along the 12a so that tilting movement is possible in the front-back direction. In the insertion hole 11a of the support arm 11, the support pin 14 is rotatable and penetrated in a direction orthogonal to the rotation axis 4 as shown in FIG. One end of the pair of left and right guide pins 15 and 16 is guided and slides in the guide holes 14a formed at both ends, and is supported through and parallel to each other. In addition, pressure is fixed to the other end of both guide pins 15 and 16 in the attachment hole 13b of the bearing part 13a integrally formed in the back surface of the said inclination plate 13. In this embodiment, the hinge mechanism K1 that allows the reciprocating inclined movement in the front and rear directions of the inclined plate 13 by the support arm 11, the inclined plate support 12, the guide pins 15 and 16 and the bearing portion 13a. ).

As shown in FIG. 2, the inclined plate 13 mooring a pair of shoes before and after the pair of shoes 18 before and after entering into a recess formed in the proximal end of the plurality of migraine pistons 17 accommodated in the cylinder bore 1a. Doing. A stopper 19 is attached to the outer periphery of the rotary shaft 4 to control the inclination angle of the inclined plate 13 to zero, that is, the inclined plate support 12 and to prevent the compressor from discharging. In addition, the maximum inclination angle of the inclined plate 13 is regulated as the inclined plate support 12 contacts the stepped portion 4a formed on the rotation shaft 4.

Between the rear end face of the said cylinder block 1 and the front end face of the rear housing 3, the valve plate 20 which provided the suction hole 2a and the discharge hole 20b is interposed. Moreover, the suction valve plate 21 in which the suction valve 21a was formed is connected to the front surface of the said valve plate 20, and the discharge valve plate 22 in which the discharge valve 22a was formed is joined to the back surface. A retainer plate 23 having a retainer 23a for regulating the open position of the discharge 22a is joined to the rear surface of the discharge valve plate 22.

Next, the inclination plate inclination-angle return mechanism K2 for returning the inclination plate 13 from the non-moving position to the movable position will be described.

As shown in FIG. 1 and FIG. 2, in the center hole 1b of the cylinder block 1, a cylindrical spool 24, which is slid to the outer circumferential surface of the rotating shaft 4, is guided and reciprocated in the front and rear directions, is accommodated. It is. A lip seal 25 is provided between the rear radial bearing 6 and the spool 24. The outer circumferential surface of the large diameter cylindrical portion 24a formed at the tip of the spool 24 is joined to the inner circumferential surface of the central hole 1b by sliding between the outer circumferential surface of the small diameter cylindrical portion 24b and the center hole 1b. The pressure chamber 26 is formed in the chamber. Then, when the control hydraulic pressure is supplied to the pressure chamber 26 while the front end portion of the large diameter cylindrical portion 24a of the spool 24 is in contact with the rear wall surface of the inclined plate support 12, the spool 24 rotates with the rotation shaft 4. ), The inclined plate support 12 is pushed forward to move the inclined plate 13 back to the inclined state at zero degrees.

In the center of the rear housing 3, a trocoid oil supply pump 27 driven by the rotating shaft 4, as shown in Figs. 2 and 4, is housed. This oil supply pump 27 consists of the outer gear body 27a and the inner gear body 27b, as shown in FIG. When the outer gear body 27a is rotated by the rotation shaft 4, the inner gear body 27b rotates in the same direction at a speed later than that of the outer gear body 27a. As shown in FIG. 5, the space V between the reference numerals 27a and 27b is moved in the rotational direction of both gear bodies 27a and 27b while increasing and decreasing the volume V by the rotation speed difference between the two gear bodies 27a and 27b. do. Oil is sucked into the cavity V at the arc-shaped suction port 28a, and oil sucked into the supply V is discharged from the arc-shaped discharge port 29a. 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 as shown in FIG. In addition, the discharge port 29a of the oil feed pump 27 is connected to the rear opening of the oil passage 30 formed in the center of the rotation shaft 4 by the oil discharge passage 29. Branch oil passages 30a are formed in plural places in the oil passages 30, and lubricating oil can be supplied to the bearings 5, 6, the crank chamber 2a, the inclined plate support 12, and the like.

In addition, as illustrated in FIGS. 1 and 2, an electromagnetic directional valve 31 is provided in the middle of the oil discharge passage 29, and the switching valve 31 is provided in the cylinder block 1 and the rear housing 3. It is connected to the said pressure chamber 26 via the lubrication plate inclination-angle return oil supply passage 32 which formed. Moreover, the direction switching valve 31 can perform a selective switching operation between the 1st port 31a which communicates with the said flow path 30, and the 2nd port 31b which communicates with the said oil supply passage 32. As shown in FIG.

Therefore, the structure of the said electromagnetic direction switching valve 31 is demonstrated based on FIG. 6, FIG.

As shown in FIG. 6, the valve case 33 is provided with first and second valve chambers 34 and 35, in which the first cylindrical valve body 36 and the second cylindrical valve body 37 are spherical. ) Is received, and the second valve body 37 is normally biased by the return spring 38 in the direction of closing the inclined plate inclined angle return oil supply passage 32 (second port 31b). An electromagnetic solenoid 39 is attached to an upper portion of the valve case 33, and a fixed iron core 41 and a movable iron core 42 are housed inside the coil 40. The proximal end of the first actuating rod 43 is inserted into and fixed to the movable iron core 42, and the middle portion thereof gently penetrates the insertion hole formed in the center of the fixed iron core 41 and penetrates the first valve body 36. It is fixed. The tip of the first actuating rod 43 is in contact with the second valve body 37.

Therefore, in the self-releasing state of the coil 40, as shown in FIG. 6, the second valve body 37 opens the inclined plate inclined angle return oil supply passage 32 (second port 31b) by the return spring 38. As shown in FIG. The first valve body 36 is held in a position to open the oil discharge passage 29 (first port 31a) while being held in the closed position. For this reason, lubricating oil is supplied to the oil passage 30 by the oil discharge passage 29, and lubrication of each sliding part in the compressor is performed. On the contrary, in the working state of the coil 40, as shown in FIG. 7, the movable iron core 42 is absorbed and moved to the fixed iron core 41 against the biasing force of the return spring 38, and is applied to the first operating rod 43. As a result, the first valve body 36 is switched to the closed position, and the second valve body 37 is switched to the position at which the inclined plate inclined angle return oil supply passage 32 is opened. For this reason, the control hydraulic pressure discharged from the oil supply pump 27 is not supplied to the oil passage 30 in the rotation shaft 4, but is supplied into the pressure chamber 26 from the oil supply passage 32 for inclination angle return, so that the spool 24 is moved forward. The inclined plate support 12 is moved in the same direction so that the inclined plate 13 is returned to the inclined state at zero degrees.

Next, when the compression operation of the compressor is performed with the inclined plate 13 in an inclined state according to FIGS. 2, 6, and 7, the inclined plate 13 is controlled by the control device 57 of the external control method described later. The inclination plate inclination-angle forced change mechanism K3 for returning an inclination angle to zero is demonstrated.

As shown in FIG. 2, in the rear housing 3 and the cylinder block 1, an air supply passage 44 communicating with the discharge chamber 3b and the crank chamber 2a is formed, and the crank chamber 2a and the suction chamber ( An exhaust passage 45 communicating with 3a) is formed. The solenoid valve 46 is provided in the middle of the air supply passage 44. The solenoid of the solenoid valve 46 is shared with the solenoid 39 of the solenoid valve 31.

The solenoid valve 46 is provided with a spherical valve body 49 in the valve chamber 48 formed in the valve case 47 as shown in FIG. The valve body 49 is normally biased by the return spring 50 in the direction of closing the air supply passage 44. In addition, a second actuating rod 51 is connected to the upper end of the movable iron core 42 of the electromagnetic solenoid 39 on the same axis, and an upper end of the actuating lot 51 abuts against a lower surface of the valve body 49. have. In this way, the inclination-angle forced change mechanism K3 of the inclined plate 13 is configured.

Therefore, as shown in FIG. 7, in the working state of the electromagnetic solenoid 39, the second operation rod 51 is moved in the direction away from the valve body 49 by the movable iron core 42, and the valve body 49 is moved. The position at which the air supply passage 44 is closed by the return spring 50, that is, the inclination angle forced change mechanism K3 is maintained in an inoperative state.

Then, as shown in FIG. 8, when the solenoid 39 is self-released in the state in which the compressor is compressed and operated in the inclined state of the inclined plate 13, the return spring 38 on the electromagnetic direction switching valve 31 side is applied. The second operating rod 51 is pushed upward through the second valve body 37, the first operating rod 43, and the movable iron core 42.

For this reason, the difference between the crank chamber pressure Pc and the suction pressure Ps which supply high-pressure refrigerant gas to the crank chamber 2a through the air supply passage 44 from the discharge chamber 3b, and acts on the piston 17 The pressure DELTA p (hereinafter referred to simply as differential pressure p) is increased and the inclined plate 13 is forcibly returned from the inclined state to the zero position.

By the way, during the compression operation of the compressor, the variable capacity control is automatically performed in accordance with the cooling load. That is, the difference acting on the piston 17 by adjusting the opening degree of the exhaust passage 45 communicating the crank chamber 2a and the suction chamber 3a in accordance with the suction pressure Ps proportional to the cooling unit. The pressure p is to be adjusted. The pressure control valve 52 for controlling this discharge capacity is demonstrated below.

As shown in FIG. 6, an accommodating type 47a is formed in the valve case 47 to be positioned below the valve chamber 48, and a lid for opening and closing the exhaust passage 45 in the accommodating type 47a. The valve body 53 is formed to have a cylindrical shape. This valve body 53 is normally biased in the closing direction by the return spring 54. In addition, a pressure reducing chamber 55 is formed above the head of the valve body 53, and the chamber 55 receives suction pressure in the suction chamber 3a through an exhaust passage 45 downstream of the valve body 53. (Ps) is detected. The opening degree of the exhaust passage 45 by the valve body 53 is adjusted by the fluctuation of the suction pressure Ps sensed by the decompression chamber 55 and the force of the return spring 54. Moreover, this pressure reduction chamber 55 communicates with the chamber 47b formed between the inner peripheral surface of the valve body 53 and the bellows 56 by the communication path 53a formed in the head part of the valve body 53. have. The valve body 53 is formed with an insertion tube 53b which slides through the second operation rod 51 so as to be movable.

Therefore, when the cooling load is large and the suction pressure Ps is large, the pressure in the decompression chamber 55 is large and the valve body 53 is opened. Therefore, the crank chamber 2a is moved from the crank chamber 2a to the suction chamber 3a through the exhaust passage 45. There is a lot of gas flowing and because of this, the differential pressure p acting on the piston 17 is reduced so that the stroke of the piston 17 is increased and the compressor is operated at a large capacity. On the contrary, when the cooling load is allowed and the suction pressure Ps decreases, the pressure in the decompression chamber 55 also decreases and the valve body 53 decreases the opening of the exhaust passage 45. Increasing, the stroke of the piston 17 is reduced and the compressor is operated at a small capacity.

In addition, the cylinder block 1 and the valve plate 20 are provided with an exhaust passage (not shown) having a fixed throttle communicating with the crank chamber 2a and the suction chamber 3a, and during the compression stroke of the piston 17. The refrigerant gas leaking into the crank chamber 2a is returned to the suction chamber 3a through a gap between the inner circumferential surface of the cylinder bore 1a and the outer circumferential surface of the piston.

Next, a control device which is a main part of the present invention will be described.

In the present embodiment, as shown in FIGS. 1, 2, and 6, the inclined plate inclination angle returns when the compressor starts up, while the inclined plate 13 held at zero by the inclined plate inclination angle forcibly changing mechanism K3 in the stopped state of the compressor. The control device 57 is provided to operate the mechanism K2 only for a predetermined time, temporarily hold it in an inclined state, and perform a compression operation.

As shown in FIG. 6, the control device 57 is connected to the coil 40 of the electromagnetic solenoid 39, and inside thereof, a central processing circuit (CPU) 58 and the electronic solenoid 39 are connected. The timer 59, the input unit 60, and the instructing part 61 which can set an energization time are provided. In addition, the control device 57 includes an engine start switch 62, an air conditioner switch 63, a discharge temperature detector 64, a vehicle interior temperature detector 65, a suction pressure detector and a discharge pressure detector, although not shown. Various commands and detection signals are input. In addition, the central processing circuit 58 includes a memory 66 to store a set time, a set temperature, a set pressure, and the like. When the start switch 62 of the engine is turned on, the timer 59 energizes the electronic solenoid 39 by the timer 59 only for a predetermined time and temporarily turns the inclined plate 13 at the start of the compressor. For example, change the angle of inclination of 10 degrees.

Next, the operation of the variable displacement compressor configured as described above will be described.

In the state where the compressor is stopped, as shown in FIG. 2, the inclined plate 13 is held at zero by the inclined plate inclination angle change mechanism K3 of the inclined plate 13, and the inclined plate inclination angle return mechanism K2 is stopped. have. When the engine (not shown) is started in this state, the rotation of the engine is directly transmitted to the rotating shaft 4 via the belt 8 and the pulley 7, and the support arm 11 of the rotating support 9 is rotated by the rotating shaft 4. Is rotated by For this reason, the inclination plate 13 starts rotation in the state of zero degree by the hinge mechanism K1.

The on signal of the start switch 62 of the engine is transmitted to the control device 57 in FIGS. 1 and 6, and the electronic solenoid (for 10 minutes) is set for a predetermined time set by the CPU 58 and the timer 59. 39) is a woman. For this reason, in FIG. 6, since the 1st valve body 36 closes the 1st port 31a, and the 2nd valve body 37 opens the 2nd port 31b, the oil passage by the oil supply pump 27 Supply of lubricating oil to 30 is stopped, and pressure oil is supplied to the pressure chamber 26 from the oil supply passage 32 for inclination angle return. For this reason, the spool 24 is advanced so that the inclined plate 13 shifts from the zero position shown by the solid line in FIG. 1 to the inclined position shown by the dashed line in the figure, and the piston 17 reciprocates in the cylinder bore 1a. The refrigerant gas that has been moved and sucked into the cylinder bore 1a from the suction chamber 3a is compressed and then discharged to the discharge chamber 3b. Further, the second actuating rod 51 along with the movable iron core 42 is moved downward in FIG. 6 by the excitation of the electromagnetic solenoid 39 so that the solenoid valve 46 of FIG. The valve body 49 is moved to the position where the oil supply passage 44 is closed by the return spring 50, and the supply of the refrigerant gas from the discharge chamber 3b to the crank chamber 2a is stopped.

The spool 24 is stopped by the stopper 19 by the supply of the control oil pressure to the pressure chamber 26. After that, the control oil pressure is the pressure chamber 26 and the crank chamber 2a installed on the rotary shaft 4. The flow path (not shown) which communicates with is opened by the movement of the spool 24, so that it is supplied to the crank chamber 2a.

When the operation at the intermediate capacity of the compressor has elapsed for a predetermined time, the electronic solenoid 39 is demagnetized in FIG. 7 due to the time-up of the timer 59, and as shown in FIG. Since the valve body 36 opens the discharge passage 29 and the second valve body 37 is closed by the return spring 38, the supply of pressure oil to the pressure chamber 26 is stopped and the spool 24 is in a free state. It becomes In addition, since the second actuating rod 51 opens the valve body 49 of the solenoid valve 46 against the force of the return spring 50 to open the air supply passage 44, the discharge chamber 3b. The high-pressure refrigerant gas is supplied into the crank chamber 2a from above, and the inclined plate 13 increases the differential pressure Δp acting on the piston 17, and the inclined plate 13 is forcibly returned to the zero position and the compressor is zero. Switch to capacity operation.

In this manner, the compressor is temporarily operated at an intermediate capacity (for example, 10%) when the compressor is started. For this reason, even if liquid refrigerant exists in the compressor, the liquid refrigerant is discharged from the discharge chamber 3b to the external refrigerant gas discharge line, and the refrigerant gas containing the lubricant oil in the condenser and the evaporator is sucked through the suction refrigerant gas suction line 3a. Inflow). As a result, after the lubricant outside the compressor returns to the compressor together with the refrigerant gas and the compressor is switched to the zero capacity operation, the lubricity of each sliding part in the crank chamber 2a is improved.

By the way, the magnitude | size of the cooling load in the inclination-angle vehicle compartment of the inclination plate 13 by the said spool 24 differs. When the temperature in the vehicle compartment is low and the cooling load is small, the inlet pressure Ps is low, so that the opening of the bleed passage 45 is reduced by the valve body 53 of the pressure control valve 52, which causes the piston 17 The differential pressure DELTA p acting on the < RTI ID = 0.0 >) is largely maintained and the inclined plate 13 is maintained at a minimum inclination angle for 10% capacity operation. On the contrary, when the cooling load is large, since the suction pressure Ps is large, the opening degree of the bleeding passage 45 is increased by the valve body 53 of the pressure control valve 52. Therefore, the differential pressure Δp is increased. Becomes smaller, and the inclined plate 13 is spaced apart from the spool 24 to shift to the maximum inclination angle. However, when the cooling load is large, since the switch 63 of the air conditioner is normally turned on, the compressor continues normal compression operation at the same time as the engine is started. That is, the control device 57 continues the working state of the solenoid 39 as shown in FIG. 7 by turning on the air conditioner switch 63 and supplies lubricant oil from the oil supply pump 27 to the pressure chamber 26. Keep feeding. In addition, the spool 24 is maintained as it is, and the inclined plate 13 swings in an inclined state with its inclination angle changed according to the cooling load, and the opening degree of the exhaust passage 45 is opened by the reciprocating motion of the piston 17. The inclination angle of the inclined plate 13 is changed in accordance with the variation in the suction pressure ps proportional to the discharge capacity ps.

In the case where the air conditioner switch 63 is turned off while the cooling load is large, the inclination angle of the inclined plate 13 is the maximum, and the compression operation of the compressor is performed only for a predetermined time.

In addition, this invention is not limited to the said Example, It can also be actualized as follows.

(1) In the above embodiment, the inclined plate 13 is rotated from zero degrees to inclined state only for a predetermined time when the compressor is started by the engine. Instead, the compressor is started at zero capacity by the control device 57 so that the predetermined time is increased. After the elapse of time or each time a predetermined time elapses, the inclination plate 13 may be temporarily inclined by the timer 59 to perform compression operation. In this case, it is conceivable that the predetermined time is set after, for example, 10 to 30 seconds before the liquid refrigerant present in the compressor is heated and the lubricity of each sliding portion becomes a problem.

Moreover, when the compressor detects the temperature in the crank chamber 2a by the detector while the compressor is operating at zero capacity, and the detected temperature exceeds the set value, the inclination plate 13 is temporarily inclined by the control device 57. The compressor may be operated at medium capacity.

In addition, when the rotation speed of the rotating shaft 4 reaches the predetermined value, or every predetermined number of times, the inclination plate 13 may be temporarily inclined by the control device 57 and the compressor may be driven at an intermediate capacity.

In the case of each of these separate examples, the lubricating oil is introduced together with the refrigerant gas from the external refrigerant gas suction pipe inside the compressor, thereby improving the lubricity of each sliding part in the crank chamber.

(2) The control device 57 may temporarily perform the compression operation of the intermediate capacity after the initial start of the compressor and after a predetermined time has elapsed.

(3) The inclination plate inclination-angle forced change mechanism K3 of the inclination plate 13 may be constituted by a coiled return spring (not shown) provided between the rotary support 9 and the inclined plate support 12.

(4) As the inclined plate inclination angle return mechanism K2 of the inclined plate 13, the inclined plate support 12 is pushed in place of the oil supply pump 27 and the spool 24, for example, an electronic solenoid (not shown) can be used. It may be.

(5) The time for operating the inclined plate inclination angle return mechanism K2 by the CPU 58 and the timer 59 of the control device 57 according to the magnitude of the cooling load may be changed and adjusted.

(6) As shown in FIG. 9, in the pressure chamber 26, the spool 24 is moved forward to keep the inclined plate 13 in the stopped state of the compressor, and the inclined plate inclined position is maintained at the intermediate capacity position. The bias spring 133 as a means may be accommodated.

In this case, in the rotational state of the engine (rotational state of the compressor), the inclination plate inclination angle is controlled in the same state as in the first embodiment. In the stationary state of the engine (the stationary state of the compressor), since the chambers in the compressor become the same pressure, the inclined plate 13 is returned to the intermediate inclined angle by the biasing spring 133. Therefore, in this embodiment, since the operation of the compressor is immediately started in the intermediate position state at the start of the engine, it is possible to further improve the lubricity of each sliding part of the crankcase during engine operation.

(7) Moreover, although the valve 53 which opens and closes the said exhaust passage opens and closes by depressurizing inhalation pressure, and adjusts the opening degree of an exhaust passage, you may open and close with an external signal instead of a solenoid valve. In this case, by opening and closing the solenoid valve, the pressure of the crankcase is converted into two types of high pressure and low pressure, and the capacity of the compressor changes into two types, the maximum capacity and the zero capacity, correspondingly.

As described above, the present invention provides a control apparatus for releasing the inclined plate inclination angle forcibly changing mechanism in the zero-capacity operation state of the compressor, and also for operating the inclined plate inclination angle return mechanism for a predetermined time and temporarily maintaining the inclined plate in the inclined state in the non-operating position. Since the compressor is operated at zero capacity, it is possible to improve the lubricity of each sliding part of the crankcase and to increase the durability of the compressor.

Claims (2)

A cylinder block 1 having a plurality of cylinder bores 1a for accommodating a migraine piston in a housing is provided in parallel with each other, a crank chamber 2a is provided in the housing to support a rotating shaft, and a hinge to the rotating shaft. The inclined plate is mounted to be reciprocally inclined forward and backward through a mechanism, and the inclined plate is oscillated back and forth by the rotation of the rotary shaft 4 to reciprocate the migraine piston in the cylinder bore, and the refrigerant sucked from the suction chamber. The gas is compressed in the cylinder bore to be discharged to the discharge chamber, and the inclination angle of the inclined plate is changed by the pressure difference between the crankcase pressure acting on the rear surface of the piston and the bore pressure acting on the front surface, and the reciprocating stroke of the piston The swing ramp variable displacement compressor configured to adjust the discharge capacity by changing the The inclination plate inclination angle forcibly changing mechanism K3 for changing the inclination angle of the inclination plate to the non-operational position, the inclination plate inclination angle return mechanism K2 for returning the inclination angle of the inclination plate from the non-operational position to the movable position, Command of each part for releasing the said inclination plate inclination-angle forced change mechanism K3 in a non-operational operation state, and also operating the said inclination plate inclination-angle return mechanism K2 for a predetermined time, and temporarily holding a inclination plate in a compressed state from a non-operation position. And a control device including a detection signal unit and an input unit, and an arithmetic processing unit 58 according to the oscillation inclination plate type variable displacement compressor. The swing-inclined plate type variable displacement compressor according to claim 1, wherein the inclined plate is held in an inclined position in a stationary state of the compressor and provided with an inclined plate inclined position holding means.