JPH07189899A - Variable displacement compressor - Google Patents

Abstract

PURPOSE:To provide a variable displacement compressor to prevent the propagation of a large load torque on a vehicle engine under small driving force. CONSTITUTION:An electromagnetic opening/closing valve 41 opens and closes a pressure feeding path 44 for connecting a delivery chamber 3b to a crank case 2a. Also a control computer C controls the energizing and deenergizing of the electromagnetic opening/closing valve 41 based on the detection information from a deceleration detection means 51. When the deceleration detection means 51 detects the abrupt decelerating condition of a compressor, the control computer C deenergizes the electromagnetic opening/closing valve 41. By this deenergization, high-pressure refrigerant gas in a delivery chamber 3b flows into the crank case 2a, and the pressure in the crank case 2a is increased. Thus the inclination angle of a swash plate 15 is moved to the minimum inclined angle.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity compressor for supplying pressure in a discharge pressure region to a crank chamber and releasing pressure in the crank chamber to a suction pressure region for adjusting pressure in the crank chamber. is there.

[0002]

2. Description of the Related Art In a one-sided piston type variable displacement type swash plate compressor disclosed in Japanese Patent Laid-Open No. 3-37378, connection and disconnection of power transmission between an external drive source and a rotary shaft of the compressor are performed. Do not use the electromagnetic clutch. If the electromagnetic clutch is removed, it will be ON-OF especially in the vehicle mounting form.
It is possible to eliminate the disadvantage of poor feeling in feeling due to the shock of F, and to reduce the weight and cost of the entire compressor.

Since the difference between the maximum value and the minimum value of the load torque is large in the one-sided piston variable displacement compressor, engine stall in a vehicle equipped with the one-sided piston variable displacement compressor becomes a problem. The cause of the engine stall is the load on the power steering mechanism. Therefore, the idle-speed controller is used. The idle-speed-controller auxiliary adjusts the air supply amount to the engine based on the load detection information of the power steering mechanism.

[0004]

In a vehicle equipped with a variable displacement compressor, the load fluctuation of the compressor has a great influence on the engine stall. For example, when the brake is suddenly applied while the vehicle is traveling, the rotation speed of the vehicle engine sharply decreases and the driving force of the vehicle engine sharply decreases. In such a state, if the displacement of the variable displacement compressor is large, that is, the load is large, the vehicle engine will stop. Therefore, it is necessary to detect the discharge capacity of the variable capacity compressor that reflects the load torque of the variable capacity compressor and control the air supply amount adjustment of the idle-speed controller. In order to detect the discharge capacity of the one-sided piston type variable displacement compressor, it is necessary to detect the tilt angle of the swash plate, but this tilt angle detection is very difficult and accurate discharge capacity detection cannot be expected.

An object of the present invention is to prevent a large load torque ripple to a vehicle engine in a small driving force state without depending on detection of a displacement of a variable displacement compressor.

[0006]

Therefore, according to the present invention,
A rotary support is fixedly attached to a rotary shaft in a housing that accommodates a single-headed piston in a cylinder bore for reciprocating linear movement, and a swash plate is tiltably supported on the rotary support to adjust the pressure and suction pressure in the crank chamber. The variable capacity that controls the tilt angle of the swash plate by the difference via the single-headed piston, supplies the pressure in the discharge pressure area to the crank chamber, and releases the pressure in the crank chamber to the suction pressure area to regulate the pressure in the crank chamber. A variable target of a compressor, including deceleration detection means for detecting a deceleration state of the compressor, and tilt angle forced change means for forcibly changing the tilt angle of the swash plate to the minimum tilt angle when the deceleration detection means detects a specific state. A capacity compressor was constructed.

According to the second aspect of the present invention, the pressure supply passage connecting the discharge pressure region and the crank chamber, and the opening degree of the pressure supply passage are changed when the deceleration detecting means detects a specific state. The tilt angle compulsory changing means is constituted by an on-off valve for increasing the pressure in the crank chamber. A solenoid valve is desirable as the on-off valve.

According to the third aspect of the invention, a pressure detector for detecting the pressure in the discharge pressure region is used as the deceleration detecting means. In the invention according to claim 4, as the deceleration detecting means, a rotation speed detector for detecting the rotation speed of the rotation of the compressor or the rotation device rotating in synchronization therewith is used.

[0009]

According to the first aspect of the invention, when the deceleration detecting means detects a specific state in which the rotational speed of the compressor sharply decreases, the inclination angle changing means forcibly changes the swash plate inclination angle to the minimum inclination angle. . That is, in the case where the vehicle equipped with the compressor is suddenly braked, the discharge pressure of the installed compressor sharply decreases, and the load torque of the compressor immediately decreases. Therefore, the large load torque of the compressor does not spread to the vehicle engine in the small driving force state due to the sudden braking, and the problem of engine stall is avoided.

According to the second aspect of the present invention, when the deceleration detecting means detects a specific state in which the rotation speed of the compressor sharply decreases, the opening / closing valve opens the pressure supply passage, and the refrigerant gas in the discharge pressure region is opened. Flows into the crank chamber through the pressure supply passage. Therefore, the pressure in the crank chamber suddenly rises, and the swash plate tilt angle quickly shifts to the minimum tilt angle. That is, when the vehicle is suddenly braked, the discharge pressure of the compressor mounted on the vehicle is drastically reduced, and the load torque of the compressor is immediately reduced.

In the third aspect of the invention, the pressure detector detects a decrease in the discharge pressure due to a rapid decrease in the rotation speed of the compressor. By this specific pressure detection, the inclination angle changing means forcibly changes the inclination angle of the swash plate to the minimum inclination angle. That is, in the case where the vehicle equipped with the compressor is suddenly braked, the discharge pressure of the installed compressor sharply decreases, and the load torque of the compressor immediately decreases.

In a fourth aspect of the present invention, a specific state in which the rotation speed of the compressor is directly detected or the rotation speed of a rotating device that rotates in synchronization with the compressor, for example, the rotation speed of the engine is directly detected, and the rotation speed sharply decreases If detected, the tilt angle forced change means forcibly changes the swash plate tilt angle to the minimum tilt angle.

[0013]

【Example】

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a clutchless compressor will be described below with reference to FIGS.

As shown in FIG. 1, a front housing 2 is joined to the front end of a cylinder block 1 which is a part of the housing of the entire compressor. A rear housing 3 is joined and fixed to the rear end of the cylinder block 1 via a valve plate 4, valve forming plates 5A and 5B, and a retainer forming plate 6. A rotary shaft 9 is rotatably supported between the front housing 2 that forms a part of the housing and forms the crank chamber 2a, and the cylinder block 1. The front end of the rotary shaft 9 projects outward from the crank chamber 2a, and the driven pulley 10 is fastened and fixed to the projecting end. The driven pulley 10 is operatively connected to the vehicle engine via a belt 11.

At the front end of the front housing 2, a support cylinder 2 is provided.
b is provided so as to surround the periphery of the protruding end of the rotary shaft 9. The driven pulley 10 is supported by the support cylinder 2b via an angular bearing 7. The support cylinder 2b receives both the thrust load and the radial load acting on the driven pulley 10 via the angular bearing 7. A lip seal 12 is interposed between the front end of the rotary shaft 9 and the front housing 2. The lip seal 12 prevents pressure leakage in the crank chamber 2a.

A spherical swash plate support 14 is slidably supported on the rotary shaft 9, and a swash plate 15 is supported on the swash plate support 14 so as to be tiltable in the axial direction of the rotary shaft 9. . Connecting pieces 16 and 17 are fixed to the swash plate 15.
As shown in FIG. 2, a pair of guide pins 18, 19 are fixedly attached to the connecting pieces 16, 17. A disc-shaped rotary support 8 is fixed to the rotary shaft 9, and a support arm 8a is provided on the rotary support 8 so as to project therefrom. A support pin 20 is rotatably supported by the support arm 8a in a direction perpendicular to the rotary shaft 9. A pair of guide pins 18, 19
Are slidably fitted into both ends of the support pin 20. The support pin 20 on the support arm 8a and the pair of guide pins 18 and 19 are linked to each other, so that the swash plate 15 can move the swash plate support 14
Can be tilted in the axial direction of the rotary shaft 9 and rotatable integrally with the rotary shaft 9. The tilt of the swash plate 15 is due to the slide guide relationship between the support pin 20 and the guide pins 18 and 19,
It is guided by the sliding action of the swash plate support 14 and the supporting action of the swash plate support 14.

As shown in FIGS. 1, 4 and 5, a housing hole 13 is formed in the center of the cylinder block 1 so as to penetrate in the axial direction of the rotary shaft 9, and the housing hole 13 has a cylindrical block. Body 2
1 is slidably accommodated. The blocking body 21 includes a large diameter portion 21a and a small diameter portion 21b, and a capacity return spring 24 is provided between the step portion between the large diameter portion 21a and the small diameter portion 21b and the flange portion 13a on the inner peripheral surface of the accommodation hole 13. Is intervening. The capacity return spring 24 urges the blocking body 21 toward the swash plate support 14 side.

The rear end of the rotary shaft 9 is inserted into the blocking body 21. A deep groove ball bearing member 25 is interposed between the rear end of the rotary shaft 9 and the inner peripheral surface of the large diameter portion 21a. The rear end of the rotary shaft 9 is supported by the inner peripheral surface of the housing hole 13 via the deep groove ball bearing member 25 and the blocking body 21. The outer ring 25a of the deep groove ball bearing member 25 is fixed to the inner peripheral surface of the large diameter portion 21a, and the inner ring 25b is slidable on the peripheral surface of the rotating shaft 9. As shown in FIG. 5, a step portion 9a is formed on the peripheral surface of the rear end portion of the rotating shaft 9, and the inner ring 25b is provided with the step portion 9a.
Thus, the movement toward the swash plate support 14 side is restricted. That is,
The deep groove ball bearing member 25 has the step portion 9a so that the swash plate support 1
Movement to the 4th side is blocked. Therefore, when the deep groove ball bearing member 25 contacts the step portion 9a, the blocking body 21 is prevented from moving toward the swash plate support body 14 side.

At the center of the rear housing 3, the suction passage 2 is provided.
6 is formed. The suction passage 26 communicates with the accommodation hole 13, and a positioning surface 27 is formed around the opening of the suction passage 26 on the accommodation hole 13 side. The tip of the small diameter portion 21b of the blocking body 21 can contact the positioning surface 27. When the tip of the small-diameter portion 21b contacts the positioning surface 27, the blocking body 21 is restricted from moving in the direction away from the swash plate support 14, and the communication between the suction passage 26 and the housing hole 13 is blocked. .

A transmission cylinder 28 is slidably mounted on the rotary shaft 9 between the swash plate support 14 and the deep groove ball bearing member 25. One end of the transmission cylinder 28 can contact the end face of the swash plate support 14, and the other end of the transmission cylinder 28 can contact only the inner ring 25b of the deep groove ball bearing member 25 without contacting the outer ring 25a.

As the swash plate support 14 moves to the blocking body 21 side, the blocking body 21 comes into contact with the transmission cylinder 28, and the transmission cylinder 28 is contacted.
Is pressed against the inner ring 25b of the deep groove ball bearing member 25. The deep groove ball bearing member 25 receives a load not only in the radial direction of the rotating shaft 9 but also in the thrust direction. Therefore, the blocking body 2
1 is urged toward the positioning surface 27 side against the spring force of the capacity return spring 24 by the pressing action of the transmission cylinder 28, and the small diameter portion 21
The tip of b contacts the positioning surface 27. Therefore, the swash plate 1
The minimum inclination angle of 5 is regulated by the contact between the tip of the small diameter portion 21b of the blocking body 21 and the positioning surface 27. That is, the blocking body 21, the deep groove ball bearing member 25, the positioning surface 27, and the transmission cylinder 28 constitute the minimum tilt angle defining means.

The minimum inclination angle of the swash plate 15 is slightly larger than 0 °. This minimum tilt angle state is brought about when the blocking body 21 is arranged in the closed position that blocks the communication between the suction passage 26 and the accommodation hole 13, and the blocking body 21 is in the closed position and the open position separated from this position. The swash plate support 14 is interlocked with and arranged. The maximum inclination angle of the swash plate 15 is regulated by the contact between the inclination regulation projection 8b of the rotary support 8 and the swash plate 15 as shown in FIG.

A single-head piston 22 is housed in a cylinder bore 1a penetrating the cylinder block 1 so as to be connected to the crank chamber 2a. The rotational movement of the swash plate 15 is converted into forward and backward reciprocating swing of the one-headed piston 22 via the shoe 23, and the one-headed piston 22 moves back and forth in the cylinder bore 1a.

As shown in FIGS. 1 and 3, the rear housing 3 has a suction chamber 3a and a discharge chamber 3b defined therein. An intake port 4a and a discharge port 4b are formed on the valve plate 4. A suction valve 5a is formed on the valve forming plate 5A, and a discharge valve 5b is formed on the valve forming plate 5B. The refrigerant gas in the suction chamber 3a is sucked into the suction port 4a by the returning movement of the single-headed piston 22.
The suction valve 5a is pushed away from the inside to flow into the cylinder bore 1a. The refrigerant gas flowing into the cylinder bore 1a is discharged from the discharge port 4b to the discharge chamber 3b by pushing the discharge valve 5b away from the discharge port 4b by the forward movement of the single-headed piston 22. Discharge valve 5b
Is brought into contact with the retainer 6a on the retainer forming plate 6 to regulate the opening.

The suction chamber 3a has a housing hole 13 through a through hole 4c.
Is in communication with. When the blocking body 21 is arranged in the closed position, the passage 4c is blocked from the suction passage 26. The suction passage 26 is an inlet for introducing the refrigerant gas into the compressor, and the position where the blocking body 21 shuts on the passage from the suction passage 26 to the suction chamber 3a is on the downstream side of the suction passage 26.

A pressure release passage 29 is formed in the rotary shaft 9. The inlet 29a of the pressure release passage 29 is open to the crank chamber 2a, and the outlet 29b of the pressure release passage 29 is open to the inside of the tubular blocking body 21. As shown in FIGS. 1, 4 and 5, a pressure release port 21c is formed through the peripheral surface of the blocking body 21, and a passage 13b is cut out in the flange portion 13a. As shown in FIG. 7, when the swash plate tilt angle is the maximum tilt angle, the pressure release port 21c communicates the accommodation hole 13 with the inside of the blocking body 21. As shown in FIGS. 6 and 7, when the swash plate tilt angle is on the minimum tilt side, the pressure release port 21c is the blocking member 21.
The interior of the and the communication port 4c are communicated. That is, when the tilt angle of the swash plate is the maximum tilt angle, the crank chamber 2a has the pressure release passage 29, the inside of the blocking body 21, the pressure release passage 21c, the accommodation hole 13, and the passage 13b.
Through the suction chamber 3a. When the swash plate tilt angle is on the minimum tilt side, the crank chamber 2a communicates with the suction chamber 3a via the pressure release passage 29, the inside of the blocking body 21, and the pressure release passage 21c. In any case, from the crank chamber 2a to the suction chamber 3a
The refrigerant gas flowing to is subjected to the throttling action at the pressure release port 21c.

The stroke of the single-headed piston 22 changes depending on 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 22. That is, the tilt angle of the swash plate 15 that affects the compression capacity changes. The pressure in the crank chamber 2a is controlled by a capacity control valve 30 attached to the rear housing 3. The valve housing 31 that constitutes the displacement control valve 30 has a discharge pressure introducing port 31a,
An intake pressure introducing port 31b and a control port 31c are provided. The discharge pressure introducing port 31a is provided in the discharge pressure introducing passage 3
2 to communicate with the discharge chamber 3a. The suction pressure introducing port 31b communicates with the suction passage 26 through the suction pressure introducing passage 33, and the control port 31c communicates with the crank chamber 2a through the control passage 34.

The pressure of the suction pressure detection chamber 35 communicating with the suction pressure introducing port 31b is adjusted by the adjusting spring 3 through the diaphragm 36.
Oppose 7. The spring force of the adjusting spring 37 is the diaphragm 3
6 and the rod 38 to the valve element 39. The valve body 39, which is subjected to a spring action in the direction of closing the valve hole 31d by the return spring 40, opens and closes the valve hole 31d according to the fluctuation of the suction pressure in the suction pressure detection chamber 35. When the valve hole 31d is closed, the communication between the discharge pressure introducing port 31a and the control port 31c is cut off.

An electromagnetic opening / closing valve 41 is attached to the rear housing 3. Excitation of solenoid 42 causes valve body 4
3 closes the valve hole 41a, and the demagnetization of the solenoid 42 causes the valve body 43 to open the valve hole 41a. That is, the solenoid on-off valve 4
Reference numeral 1 opens and closes a pressure supply passage 44 that connects the discharge chamber 3a and the crank chamber 2a. The electromagnetic opening / closing valve 41 and the pressure supply passage 44 constitute a tilt angle forced change means.

A suction passage 26 for introducing the refrigerant gas into the suction chamber 3a and a discharge port 1 for discharging the refrigerant gas from the discharge chamber 3b.
It is connected to b by an external refrigerant circuit 45. A condenser 46, an expansion valve 47 and an evaporator 48 are provided on the external refrigerant circuit 45. The expansion valve 47 controls the refrigerant flow rate according to the fluctuation of the gas pressure on the outlet side of the evaporator 48.

The solenoid 42 receives the excitation / demagnetization control of the control computer C. The control computer C turns on the air conditioner operation switch 49 or turns on the accelerator switch 50.
The solenoid 42 is excited by the FF to turn off the air conditioner operation switch 49 or turn off the accelerator switch 50.
The solenoid 42 is demagnetized by N.

Further, the control computer C uses the deceleration detecting means 5
Excitation / demagnetization control of the solenoid 42 is performed based on the detection information from 1. The deceleration detecting means 51 includes a pressure detector that detects the pressure in the discharge chamber 3b or the pressure in the crank chamber 2a, a rotation speed detector that detects the rotation speed of the compressor or the rotation speed of the vehicle engine, and the torque of the compressor. For example, a torque sensor that detects a torque, a vehicle acceleration sensor, or a hydraulic pressure sensor that detects a brake hydraulic pressure is used.

When the solenoid 42 is excited, the pressure supply passage 4
When 4 is closed, when the suction pressure is high (the cooling load is large), the valve opening degree of the valve body 39 becomes small. Refrigerant gas in the crank chamber 2a passes through the pressure release passage 29 and is sucked into the suction chamber 3
It is flowing to a. Therefore, if the valve opening degree of the valve element 39 becomes smaller, it flows into the crank chamber 2a from the discharge chamber 3b via the discharge pressure introducing passage 33, the discharge pressure introducing port 31a, the valve hole 31d, the control port 31c and the control passage 34. The amount of refrigerant gas decreases. Therefore, the pressure in the crank chamber 2a decreases. Further, since the suction pressure in the cylinder bore 1a is also high, the difference between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a becomes small. Therefore, the swash plate tilt angle becomes large as shown in FIG.

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

When the suction pressure becomes extremely low (no cooling load), the valve element 39 approaches the maximum opening position as shown in FIG. The solenoid 42 is turned on by turning off the air conditioner operation switch 49 or turning on the accelerator switch 50.
Is demagnetized, as shown in FIG. 9, the valve body 43 is closed by the valve hole 41a.
Is opened and the pressure supply passage 44 is opened. 8 or 9
In the state shown in FIG. 3, the refrigerant gas in the discharge chamber 3b is in the crank chamber 2a.
Suddenly flows into. Therefore, the pressure in the crank chamber 2a is rapidly increased, the pressure in the crank chamber 2a becomes high, and the inclination angle of the swash plate 15 shifts to the minimum inclination side.

As the inclination angle of the swash plate 15 shifts to the minimum inclination side, the blocking body 21 is pushed toward the positioning surface 27 side,
The tip of the small diameter portion 21b of the blocking body 21 approaches the positioning surface 27. By this approaching operation, the cross-sectional area of the refrigerant gas passage from the suction passage 26 to the suction chamber 3a is gradually reduced. Therefore, the amount of the refrigerant gas sucked from the suction chamber 3a into the cylinder bore 1a also gradually decreases, and the discharge capacity gradually decreases. As a result, the discharge pressure gradually decreases, and the torque in the compressor does not change greatly in a short time. That is, impact avoidance, which is the main purpose of the clutchless compressor, is achieved.

When the tip of the small-diameter portion 21b of the blocking body 21 comes into contact with the positioning surface 27, the external refrigerant circuit 45 causes the suction chamber 3 to move.
Refrigerant gas inflow to a is stopped. That is, the blocking body 21 constitutes a refrigerant circulation blocking means for stopping the refrigerant circulation in the external refrigerant circuit 45 in the minimum capacity state. Minimum swash plate inclination is 0 °
Therefore, the discharge from the discharge cylinder bore 1a to the discharge chamber 3b is performed even in the state where the swash plate inclination angle is minimum. Therefore, there is a pressure difference between the discharge chamber 3b, the crank chamber 2a, and the suction chamber 3a even when the swash plate tilt angle is at a minimum. Further, the refrigerant gas in the compressor does not flow out to the external refrigerant circuit 45, and there is no fear of frost generation in the evaporator 48.

When the cooling load increases from the state of FIG. 6 and the suction pressure rises, this rise in suction pressure propagates from the suction passage 26 to the suction pressure detection chamber 35, and the valve element 39 closes the valve hole 31d. . Alternatively, when the air conditioner operation switch 49 is turned on or the accelerator switch 50 is turned on from the state of FIG. 7, the solenoid 42 is excited and the pressure supply passage 44 is shut off.

Discharge chamber 3b, crank chamber 2a and suction chamber 3
There is a pressure difference between a. Therefore, when the supply of the refrigerant gas from the discharge chamber 3b to the crank chamber 2a is stopped, the pressure in the crank chamber 2a approaches the suction pressure, and the swash plate tilt angle increases from the minimum tilt angle, that is, the capacity returns. This capacity return is performed by the pressure increase in the crank chamber 2a and the spring action of the capacity return spring 24. The blocking body 21 is gradually separated from the positioning surface 27, and the refrigerant gas passage cross-sectional area between the suction passage 26 and the suction chamber 3a gradually increases. Therefore, the suction chamber 3
The amount of the refrigerant gas sucked into the cylinder bore 1a from a also gradually increases, and the discharge capacity gradually increases. As a result, the discharge pressure gradually increases, and the torque in the compressor does not greatly change in a short time.

When the vehicle is suddenly braked, the engine speed drops sharply and the compressor speed also drops sharply. When the rotation speed of the compressor drops sharply, the discharge pressure drops sharply. When a pressure detector that detects the pressure in the discharge chamber 3b is used as the deceleration detection means 51, this pressure detector detects the pressure state in the discharge chamber 3b, and the control computer C based on the pressure detection information. Grasp the sudden drop in pressure in the discharge chamber 3b. The control computer C degausses the solenoid 42 based on the understanding of the step-down fluctuation in this specific state, and the degaussing opens the pressure supply passage 44. By opening the pressure supply passage 44, the high-pressure refrigerant gas in the discharge chamber 3b flows into the crank chamber 2a, and the pressure in the crank chamber 2a rises. Therefore, the swash plate 15 that is not at the minimum tilt angle quickly shifts to the minimum tilt angle state.
In the case where the vehicle is suddenly braked, the discharge pressure of the installed compressor drops sharply, and the load torque of the compressor immediately drops. Therefore, the large load torque of the compressor does not spread to the vehicle engine in the small driving force state due to the sudden braking, and the problem of engine stall is avoided. That is, the electromagnetic on-off valve 41 and the pressure supply passage 44 constitute a tilt angle forced change means.

When the rapid pressure fluctuation state in the discharge chamber 3b has subsided, the control computer C excites the solenoid 42,
Discharge chamber 3b and crank chamber 2a via pressure supply passage 44
Communication with is cut off. Therefore, the swash plate 15 returns to the tilt position before the sudden braking.

When the vehicle is suddenly braked, the rotation speed of the compressor is drastically reduced and the suction pressure is increased. Therefore, the opening degree of the capacity control valve 30 is increased, and the pressure in the crank chamber 2a is rapidly increased. Crank chamber 2 as deceleration detection means 51
When a pressure detector for detecting the pressure in a is used, the control computer C grasps the specific state of the rapid pressure change state in the crank chamber 2a based on the pressure information from this pressure detector, and controls the solenoid 42. Degauss. Therefore, the pressure in the crank chamber 2a suddenly rises, the swash plate inclination rapidly changes to the minimum inclination, and a large load torque of the compressor due to the sudden braking is applied to the vehicle engine in the small driving force state. There is no.

When a rotation speed detector for detecting the rotation speed of the compressor or the rotation speed of the vehicle engine is used as the deceleration detecting means 51, the control computer C determines the vehicle speed based on the rotation speed information from the rotation speed detector. Understand a specific state of sudden deceleration. The control computer C demagnetizes the solenoid 42 based on the grasp of this specific state, and the swash plate tilt angle quickly shifts to the minimum tilt angle. A rotation speed detector for detecting the rotation speed of a vehicle engine is generally used, and if this rotation speed detector is used as a deceleration detection means, there is an advantage that a dedicated deceleration detection means becomes unnecessary.

Of course, the present invention is not limited to the above-mentioned embodiment, and the swash plate support 14 of the above-mentioned embodiment can be moved in the direction of decreasing the tilt angle by using, for example, a hydraulic pump and an electromagnetic directional control valve. Other embodiments are also possible. That is, a hydraulic pump and an electromagnetic directional control valve can be used as the tilt angle forced change means.

The present invention can also be applied to a variable displacement compressor with a clutch. Also in this case, the tilt angle forced changing means as in the above embodiment may be used.

[0047]

As described above in detail, according to the present invention, when the deceleration detecting means for detecting the deceleration state of the compressor detects the specific state, the inclination angle changing means forcibly changes the inclination angle of the swash plate to the minimum inclination angle. Therefore, it is possible to prevent a large load torque ripple to the vehicle engine in the small driving force state and avoid the engine stall without depending on the detection of the displacement of the variable displacement compressor.

[Brief description of drawings]

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

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

FIG. 3 is a sectional view taken along line BB of FIG.

FIG. 4 is a side sectional view of the entire compressor in a state where the swash plate tilt angle is at a minimum.

FIG. 5 is an enlarged sectional view of an essential part in which the swash plate inclination angle is at a maximum.

FIG. 6 is an enlarged cross-sectional view of an essential part in which the electromagnetic on-off valve is in a closed state and the swash plate inclination angle is in a minimum state.

FIG. 7 is an enlarged cross-sectional view of an essential part in which the electromagnetic on-off valve is in an open state and the swash plate inclination angle is in a minimum state.

[Explanation of symbols]

2a ... Crank chamber, 3a ... Suction chamber serving as suction pressure region, 3
b ... Discharge chamber serving as discharge pressure region, 15 ... Swash plate, 41 ... Electromagnetic on-off valve serving as tilt angle forced change means, 44 ... Pressure supply passage serving as tilt angle forced change means, 51 ... Deceleration detection means.

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[Procedure amendment]

[Submission date] January 20, 1994

[Procedure Amendment 1]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 3

[Correction method] Change

[Correction content]

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0008

[Correction method] Change

[Correction content]

In the invention according to claim 3, a pressure detector for detecting the pressure in the discharge pressure region is used as the deceleration detecting means. In the invention according to claim 4, as the deceleration detecting means, a rotation speed detector for detecting the rotation speed of the rotation of the compressor or the rotation device rotating in synchronization therewith is used.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0013

[Correction method] Delete

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tomohiko Yokono 2-chome, Toyota-cho, Kariya city, Aichi Stock company Toyota Industries Corp.

Claims (4)

[Claims] 1. A rotary support is fixedly attached to a rotary shaft in a housing for accommodating a single-headed piston in a cylinder bore so as to be capable of reciprocating linear movement, and a swash plate is tiltably supported on the rotary support so that a swash plate can be tilted. The tilt angle of the swash plate is controlled by the difference between the pressure and the suction pressure via the single-headed piston, and the pressure in the discharge pressure region is supplied to the crank chamber, and the pressure in the crank chamber is discharged to the suction pressure region to adjust the inside of the crank chamber. In a variable displacement compressor that performs pressure, a deceleration detection unit that detects a deceleration state of the compressor and a tilt angle forced change unit that forcibly changes the tilt angle of the swash plate to a minimum tilt angle when the deceleration detection unit detects a specific state. Variable capacity compressor equipped. 2. The tilt angle forced changing means changes the opening of the pressure supply passage connecting the discharge pressure region and the crank chamber and the opening of the pressure supply passage when the deceleration detecting means detects a specific state. The variable capacity compressor according to claim 1, comprising an on-off valve for increasing the pressure in the crank chamber. 3. The variable displacement compressor according to claim 1, wherein the deceleration detection means is a pressure detector that detects the pressure in the discharge pressure region. 4. The variable displacement compression according to claim 1, wherein the deceleration detection means is a rotation speed detector that detects the rotation speed of a compressor or a rotation device that rotates in synchronization with the rotation speed of the compressor. Machine.