WO2001053699A1

WO2001053699A1 - Variable-displacement swash plate type clutchless compressor

Info

Publication number: WO2001053699A1
Application number: PCT/JP2001/000187
Authority: WO
Inventors: Keiichi Matsuda; Yukio Kazahaya; Katsutaka Une; Shoichi Kido
Original assignee: Zexel Valeo Climate Control Corporation
Priority date: 2000-01-21
Filing date: 2001-01-15
Publication date: 2001-07-26
Also published as: JP2001207958A

Abstract

The pressure for opening a spool (30) serving as a suction control valve is obtained not by introducing refrigerant gas from a crank chamber (8) but by leading refrigerant gas, which is present downstream of a control valve (81), directly (rather than via the crank chamber (8)) to the spool valve (30), so that as compared with an arrangement in which a passageway leading from the crank chamber (8) to the spool valve (30) is opened/closed by a hinge ball (90) slidably mounted on a shaft (5), hunting hardly occurs in the suction control valve (30) during the minimum piston stroke operation (minimum-intermediate piston stroke operation) not requiring a large discharge amount, for example, during the low-load, high speed rotation.

Description

Description Variable-capacity swash plate type clutchless compressor technology field

This invention relates to a variable displacement type swash plate type clutch compressor, and in particular, a variable displacement in which the driving force of the engine is constantly transmitted. Related to mold swash plate type clutch compressor. Background technology

As a conventional clipless compressor, there is a variable-capacity swash plate-type clutchless compressor. In this clutchless compressor, the inclination angle of the swash plate changes in response to the suction pressure, and the stroke amount of the piston changes. And the amount of exhalation increases or decreases.

Uses a variable displacement swash plate type clamp compressor with a minimum discharge capacity that does not reach the minimum as a clutchless compressor. If the heat load is reduced (when the clutch with a clutch is equivalent to the clutch off), the cooling medium will cause the evaporator to operate.ー The evening is cooled, frost forms on the surface of the evaporator evening, the evaporator evening freezes and the ventilation becomes difficult, and the cooling function is reduced. May be damaged

As a technology to prevent this, when the heat load is reduced, the coolant is circulated inside the compressor to reduce the heat load. In some cases, the amount of air discharged to the outside of the compressor is used as the outlet (Japanese Patent Laid-Open No. 7-253080).

In this clutchless compressor, the inclination angle of the swash plate decreases with a decrease in the heat load, and the swash plate pushes the transmission cylinder toward the rear side. The transmission cylinder pushes the blocker toward the rear side. When the swash plate is tilted to the maximum, the suction passage is closed by the blocking body, and the inflow of low-pressure refrigerant gas from the evaporator is prevented. On the other hand, the discharge chamber communicates with the crank chamber by the control valve, and the high-pressure refrigerant gas in the discharge chamber flows to the crank chamber, and the refrigerant gas flows into the crank chamber. Hardly flows to the capacitor side. In this way, when the inclination angle of the swash plate is the minimum (at the time of the minimum piston stroke), most of the refrigerant gas circulates inside the compressor. And the ability to cool and freeze can be used. In addition, the sliding part is sufficiently lubricated and cooled because the refrigerant gas circulates internally.

However, since a structure is adopted in which a transmission cylinder and a blocker for closing the suction passage are mounted on the rotating shaft, the cylinder should be placed inside the cylinder head. The discharge chamber must be located outside the suction chamber, and tighter seal management with the outside air will be required.

For example, higher processing accuracy and proper tightening of bolts (bolts for connecting the cylinder head and head) are required. It will be done.

Furthermore, since the blocking body rotates with the rotation of the rotating shaft, a spring for biasing the blocking body is provided together with the blocking body. The screw turned off and the screw was cut off, and the suction passage could not be opened or closed.

This invention provides a variable-capacity swash plate clutch compensator that not only makes it easier to manage the seal against the outside air, but also withstands long-term use. The aim is to provide a lesser. Disclosure of the invention

In order to solve the above-mentioned object, the variable capacity type swash plate type clutch compressor of the present invention accommodates the refrigerant gas discharged from the compression chamber. A discharge chamber, a crank chamber for accommodating a swash plate, and a passage connecting the discharge chamber to each other, and in response to a change in heat load, A variable-capacity swash plate clutch having a pressure control valve that regulates the cross-sectional area of the passage and a suction passage that guides the refrigerant gas from the suction port to the suction chamber. In the compressor, the pressure of the refrigerant gas downstream of the pressure control valve and the urging force of the urging member act in the valve closing direction. When the pressure of the refrigerant gas in the discharge chamber acts in the valve opening direction and the pressure difference between the two drops below a predetermined value. Only a suction control valve for shutting off the suction passage is provided.

At the suction control valve, the pressure of the refrigerant gas downstream of the pressure control valve and the urging force of the urging member act in the valve closing direction, and the refrigerant gas in the discharge chamber is closed. Pressure acts in the valve opening direction. The pressure of the refrigerant gas acting in the valve closing direction and When the difference between the pressure of the refrigerant gas acting in the valve opening direction and the pressure of the refrigerant gas falls below a predetermined value, the suction control valve moves in the valve closing direction to shut off the suction passage. When the aforementioned pressure difference exceeds the specified value, the suction control valve moves in the valve opening direction to open and release the suction passage.

Refrigerant gas is not introduced from the crank chamber as the pressure to open and close the suction control valve, and the refrigerant gas downstream of the pressure control valve is directly (Without passing through the chamber), the suction valve is led to the suction control valve, so the passage from the crank chamber to the suction control valve is slid to the rotating shaft. Compared to a configuration that opens and closes with a slider (for example, a hinge ball) that is movably mounted, a large discharge volume is not required. Small piston stroke □ — Maximum rotation of the pump at the maximum zJ 中 ~ Medium rotation piston stroke □ — During the operation, for example, when the load is low and the rotation is high, the suction control valve turns off. Ching phenomenon is unlikely to occur.

Since there is no need to equip the rotating shaft with a mechanism that opens and closes the suction port, the suction chamber can be located outside the discharge chamber, and seal management with outside air can be achieved. It will be easier. Also, since the spring that urges the blocking body rotates and rotates with the rotation of the rotating shaft, it is difficult to open and close the suction port. Improves the reliability of In addition, the intake control valve hunting during extremely small stroke stroke operation that does not require a large discharge amount, for example, at low load and high rotation. Control phenomena hardly occur, so control is stable

It is preferable that the suction control valve is a spool valve. .

The pressure of the refrigerant gas downstream of the pressure control valve and the urging force of the urging member act on one side of the spool valve in the valve closing direction, and the refrigerant in the discharge chamber on the other side of the spool valve. Gas pressure acts in the valve opening direction. When the operation of the compressor is stopped, the urging force of the urging member acts on one of the spool valves in the valve closing direction, so that the liquid refrigerant intrudes into the compressor through the suction port. Absent .

Preferably, a decompression means is provided downstream of the pressure control valve on the passage and restricts the flow of the refrigerant gas guided to the crank chamber. ing .

When the refrigerant flow rate of the pressure control valve is large, the high-pressure refrigerant is supplied to the suction control valve, whereas the pressure in the crank chamber is reduced by the operation of the pressure reducing means. The supplied refrigerant is supplied. Therefore, the pressure in the crank chamber must not be too high and the suction control valve closes quickly and reliably.

Preferably, the suction control valve is a spool valve, which is provided downstream of the pressure control valve on the passage and guided to the crank chamber. Equipped with decompression means to restrict the flow of the refrigerant gas. Brief explanation of drawings

FIG. 1 is a longitudinal sectional view showing a variable capacity type swash plate type clutch compressor according to one embodiment of the present invention. FIG. 2 is a partially enlarged cross-sectional view of the variable-capacity swash plate type clutch compressor on the rear side, showing a state in which an intake passage is closed. .

FIG. 3 is a diagram showing a state in which the suction passage is open. FIG. 4 is a diagram showing a front end face of the lid head.

FIG. 5 shows a control valve used in the variable capacity type swash plate type clutch compressor of the embodiment shown in FIG. 1 and another component. FIG. 2 is a conceptual diagram showing a mouthpiece.

Fig. 6 is a block diagram of the control device of the control valve. Best mode for carrying out the invention

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view showing a variable capacity type swash plate type compressor according to an embodiment of the present invention, and FIG. 2 is a variable capacity type swash plate type compressor. FIG. 3 is a partially enlarged cross-sectional view of the latch compressor on the ria side, showing a state in which the suction passage is closed; and FIG. 3 shows a state in which the suction passage is open. FIG. 4 and FIG. 4 are diagrams showing the front end face of the rear head.

One end of the cylinder block 1 of this variable capacity type swash plate type clutch compressor is connected via a valve plate 2 to the rear end of the cylinder block 1. Head 3 on the other end Each of the heads 4 is fixed. The cylinder block 1 is provided with a plurality of cylinder pores 6 at predetermined intervals in the circumferential direction around a shaft (rotation axis) 5. It is. A piston 7 is slidably accommodated in each of the cylinder pores 6.

A crank chamber 8 is formed in the front head 4, and a swash plate 10 is accommodated in the crank chamber 8. The sliding surface 10a of the swash plate 10 is provided with a spherical end 11a of the connecting rod 11 so as to rotatably support the spherical end 11a. 0 is held in the retainer 53. A bearing 55 is mounted on the boss portion 10 b of the swash plate 10, and a retainer 53 is mounted on the boss portion 10 b of the swash plate 10 via the bearing 55. The retainer 53 is rotatable relative to the swash plate 10. The bearing 55 is prevented from coming off by a nut 54 screwed to the boss 10b, and is laid. The other end 11 b of the connecting opening 11 is fixed to the piston 7.

The shower 50 is composed of a shower body 51 that supports the tip end surface of the one end portion 11 a of the connection rod 11 so as to be able to relatively roll, and a shower head 50. The rear end face of the one end 11a of the swinging rod 11 is supported by a mesh 52 for supporting the rear end face so as to be able to relatively roll.

A discharge chamber 12 and a suction chamber 13 are formed in the lid head 3. The suction chamber 13 is arranged so as to surround the discharge chamber 12 (see Fig. 4). The lid head 3 is provided with a suction port 3a which is connected to the outlet of Enopore 80.

The refrigerant gas at the inlet 3 a is drawn into the suction chamber 13 via a suction passage 39 formed in the lid 3. A valve accommodation space 13 is provided in the middle of the intake passage 39, and a spool valve is provided in this valve accommodation space 13.

(Suction control valve) 30 is slidably housed. The spool valve 30 has a disk portion 131, a bottomed cylinder portion 132, a center portion of the disk portion 131, and a bottomed cylinder portion.

1 3 2 Bar-shaped connection part connecting the center of the bottom of 1 2 3

3 and are provided. The valve accommodation space 134 is divided into a valve-opening chamber 13a on the front side and a valve-closing chamber 13b on the rear side across the spool valve 30. A spring (biasing member) 32 is accommodated in the bottomed cylindrical portion 13 2. One end of the spring 32 contacts the inner wall surface of the valve-closing chamber 13 3 b, and the other end of the spring 3 2 The end is in contact with the bottom surface of the bottomed cylinder. Refrigerant gas in the discharge chamber 12 is proposed in the valve-opening chamber 13 3 a via a high-pressure inner groove 13 35 formed on the front end face of the lid 3. Within.

The front side of the spool valve 30, that is, the disk

At 131, the pressure of the refrigerant gas in the valve opening chamber 1333a acts in the valve opening direction (the direction in which the valve opening increases). The spool side of the spool valve 30, that is, the bottomed cylinder 1

On the bottom surface of the valve 32, the combined force of the pressure of the refrigerant gas in the valve-closing chamber 13 3 b and the biasing force of the spring 32 is applied in the valve-closing direction (the direction in which the valve opening decreases. ). Spool valve 3 0 Corresponds to the difference between the internal pressure of the valve-opening chamber 13 3 a and the internal pressure of the valve-closing chamber 13 3 a in the fully closed position shown in FIG. 2 (the suction passage 39 is closed). 3) and the fully open position shown in FIG. 3 (the position where the suction passage 39 is opened). When the difference between the internal pressure of the valve-opening chamber 133a and the internal pressure of the valve-closing chamber 133b falls below a predetermined value, the throttle valve 30 is moved to the fully closed position ( Move to the front side), and when the pressure difference exceeds the specified value P, move to the fully open position side (Lear side).

The discharge chamber 12 and the crank chamber 8 communicate with each other via a passage 57. As shown in FIG. 1, the passage 57 is formed with passages 57 a, 5, which are formed on the rear head 3.

7b, a valve accommodation space 57c, a passage 57d formed in the valve plate 2, and a cylindrical block 1 formed along the axial direction. Composed of a passage 57 e

A control valve (pressure control valve) 81 is provided in the middle of the passage 57. When the heat load is small, the current value to the solenoid (not shown) of the control solenoid 81 becomes small, and the valve element 81a is moved. When the passage 57 is opened apart from the seat and the thermal load is large, the current value to the solenoid increases, and the valve 81 a is seated, and the passage 57 is cut off. The current value to the solenoid is controlled by an unillustrated control device. An orifice (decompression means) 62 is provided in the middle of the passage 57 e. A passage 60 is formed in the lid head 3. The passage 60 communicates with the valve closing chamber 1333b from the end A of the knob plate side of the passage 57b. No depressurizing means such as an orifice is provided in the middle of the passage 60, but a depressurizing means may be provided.

The suction chamber 13 and the crank chamber 8 communicate with each other via a passage 58. The passage 58 includes an orifice 58 a formed in the valve plate 2, a passage 58 b formed in the cylindrical opening 1, and a cylinder. It is composed of a bearing housing space 58c formed in the dub mouth 1.

The valve plate 2 includes a discharge port 16 for communicating the compression chamber 82 and the discharge chamber 12, a cylinder bore 6 and a suction chamber 13. The suction ports 15 to be communicated with each other are provided at predetermined intervals in the circumferential direction. The discharge port 16 is opened and closed by the discharge valve 17, and the discharge valve 17 is pressed to the end face of the valve plate 2 on the lid head side 18. Both are fixed by bolt 19. The port 19 is screwed into a thread 1b formed in the center of the cylindrical opening 1

The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is connected between the valve plate 2 and the cylinder block 1. It is arranged. A [Shaft-to-J-91] is mounted on the outer peripheral surface on the rear side of the shaft 5. The radial bearings 25 and thrust bearings 24 support the rear side of the shaft 5, and the front side of the shaft 5 is the radial shaft. It is rotatably supported by the bearing 26.

The thrust flange 40 for transmitting the rotation of the shaft 5 to the swash plate 10 is fixed to the shaft 5, and the thrust is fixed to the thrust plate 40. The flange 40 is supported on the inner wall surface of the front head 4 via a thrust bearing 33. The thrust flange 40 and the swash plate 10 are connected via a link mechanism 41, and the swash plate 10 is a virtual line that intersects the shaft 5 directly. It can be tilted with respect to the surface.

The swash plate 10 is slidably and tiltably mounted on the shaft 5 via a hinge ball 90. In the center hole of the boss portion 10b of the swash plate 10, a hinge pole receiving surface 10d corresponding to the spherical surface portion 90a of the hinge ball 90 is provided. It is set up. The spherical surface portion 90a of the hinge pole 90 is slidably fitted to the hinge pole receiving surface 10d. A winding spring 93 is wound between the hinge pole 90 and the thrust flange 40 so as to be wound around the outer peripheral surface of the shaft 5. It is worn.

In addition, control head is included in rear head 3.

81 A passage 92 (see Fig. 4) is provided so that the bellows (not shown) of 1 can detect the pressure of the inlet 3a. .

Next, this variable capacity type swash plate type clutch Explain the operation of the presser.

The rotating power of the vehicle engine (not shown) is constantly transmitted to the pulley (not shown) and the shaft 5 via a belt (not shown), The torque of the shaft 5 is transmitted to the swash plate 10 via the thrust flange 40 and the link mechanism 41, and the swash plate 10 rotates.

Since the rotation of the swash plate 10 causes the shower 50 to relatively rotate on the sliding surface 10a of the swash plate 10, the rotation force from the swash plate 10 is This is converted to a linear reciprocation of 7 in. The piston 7 reciprocates in the cylinder pore 6, and as a result, the volume of the compression chamber 82 in the cylinder pore 6 changes, and due to this volume change, The suction, compression and discharge of the refrigerant gas are sequentially performed, and the refrigerant gas having a capacity corresponding to the inclination angle of the swash plate 10 is discharged. At the time of suction, the suction valve 21 is opened, and low-pressure refrigerant gas is sucked from the suction chamber 13 into the compression chamber 82 of the cylinder bore 6, and at the time of discharge, the discharge valve is discharged. 17 is opened, and the high-pressure refrigerant gas is discharged from the compression chamber 82 to the discharge chamber 12.

When the thermal load decreases (at the time of the clutch-off of the clutch-equipped compressor), the control knob

The energization of the solenoid 8 1 is stopped, the plunger 8 1 c moves in the valve opening direction, and the valve 8 1 a springs.

8 Move in the valve opening direction against the biasing force of 1b, and

5 7 opens. As a result, the discharge chamber via passage 57

12 High pressure refrigerant gas flows out into the crank chamber 8 from the outlet, the pressure in the crank chamber 8 increases, and the swash plate 10 tilts. The angle becomes smaller (see Fig. 1).

However, since the throttle function of the orifice 62 operates, the crank chamber 8 is supplied with the depressurized coolant gas. The pressure in the crank chamber 8 must not be too high. In addition, the coolant gas flowing out of the suction chamber 13 from eight crank chambers to the suction chamber 13 is throttled by the orifice 58a. Significant pressure drop in room 8 is suppressed

When the control valve 81 is opened, a high-pressure cooling gas downstream of the control □ —Renolbu 81 passes through the passage 60. As a result, the pressure in the valve-closing chamber 33 b introduced into the valve-closing chamber 133 increases, and the pressure difference between the valve-closing chamber 133 b and the valve-opening chamber 133 a is increased. When the value falls below the fixed value P, the spool valve 30 moves in the valve closing direction due to the biasing force of the spring 81b, and the suction passage 39 is shut off. See Figure 2). As a result, the coolant gas is prevented from flowing into the suction chamber 13 from the suction port 3a.

In this embodiment, the coolant gas directly introduced from the control knob 81 into one of the spool valves 30 as suction control valves is provided. To operate the spool valve.

A structure to apply the pressure of the discharge chamber 12 to the other side of 30 is adopted, and the structure related to the position of the swash plate 10 (or piston stroke) is adopted. Regardless, the spool valve 30 can be closed only when the thermal load is at a minimum. Therefore, at the time of the minimum stroke stroke operation (small to medium-sized stroke stroke operation) that does not require a large discharge, For example, when the load is low and the engine speed is high, hunting of the suction control valve can be prevented from being reduced.

At the time of the minimum piston stroke (the state shown in Fig. 2), the cooling gas flows into the suction chamber 13, the compression chamber 82, the discharge chamber 12, the passage 57, and the crank chamber. 8 and the passage 58 sequentially return to the suction chamber 13 again.

When the load increases, the solenoid of the control knob 81 is energized, and the solenoid

81 c moves in the valve closing direction, the valve element 81 a moves in the valve closing direction by the biasing force of the spring 81, and the passage 57 is closed. As a result, the inflow of high-pressure refrigerant gas from the discharge chamber 12 to the crank chamber 8 is prevented. The refrigerant gas in the crank chamber 8 gradually flows out into the suction chamber 13 through the passage 58. Accordingly, the pressure in the crank chamber 8 gradually decreases, the hinge pole 90 moves to the front side, and the inclination angle of the swash plate i0 increases. The degree increases.

Further, when the passage 57 is closed, refrigerant gas is not introduced from the discharge chamber 12 to the valve closed chamber 13 3 b, so that the pressure of the valve closed chamber 13 3 b is reduced. The power drops immediately.

When the pressure difference between the valve-closing chambers 13 3 b and the valve-opening chamber 13 3 a exceeds a predetermined value P (the refrigerant gas in the valve-opening chamber 13 3 a acting on the spool valve 30). When the pressure of the valve overcomes the combined force of the pressure of the refrigerant gas in the valve-closing chamber 13 3 b and the urging force of the spring 32), the spool valve 30 moves in the opening direction. It moves and the suction passage 39 is opened (see Fig. 3). That Result Refrigerant gas flows into the suction chamber 13 from the suction port 3a

Variable-capacity swash plate type clutch of the embodiment of the present invention

The Z1 compressor has the following effects.

Since there is no need to attach a mechanism that opens and closes the suction port to the shaft 5 (conventional transmission tube, blocker, etc.), place the suction chamber 1 in the lid head 3. 3 can be arranged outside the discharge chamber 12, which facilitates seal management with the outside air.

In addition, the spring for biasing the shaft 5 may be turned around each time the shaft 5 is turned, and the inlet 3a may not be opened or closed. Since there is no compressor, the reliability of the compressor is improved.

In addition, one side of the spool valve 30 as a suction control valve (valve closing chamber 1333b) is provided with a refrigerant gas directly introduced from the control valve 81. A configuration is employed in which the pressure is applied to apply the pressure of the discharge chamber 12 to the other side of the spool valve 30.

That is, the same pressure as the pressure of the discharge chamber 12 is introduced into the valve opening chamber 33a, and the pressure of the discharge chamber 12 is controlled. Is introduced into the valve-closing chamber 13 3 b, but the two pressures always have a certain magnitude relationship. Accordingly, a passage (not shown) for guiding the refrigerant gas in the crank chamber 8 to one of the spool valves serving as the suction control valve is provided by the hinge pole 90. Compared to the open / close configuration, extremely low displacement that does not require a large discharge volume During stroke operation (minimum to intermediate piston stroke operation), for example, when the load is low or the motor rotates at a high speed, the hinge 90 is insecure. It is possible to suppress the switching of the spool valve 30 due to the constant operation. Incidentally, a passage (not shown) that leads the coolant gas in the crank chamber 8 to one of the spool valves 30 is opened and closed by the hinge pole 90. In such a configuration, the coolant gas for closing the valve is supplied to one of the spool valves despite the fact that the heat load is not minimal, and the coolant is supplied to the spool valve. This can cause hunting of the valve.

In the above-described embodiment, the case where the spool valve 30 is used as the suction control valve has been described. However, the mouth-tally valve and the like are used. You may.

Fig. 5 is different from the control valve used in the variable capacity swash plate type clutch compressor of the embodiment of Fig. 1. FIG. 3 is a conceptual diagram showing a control valve of FIG. In the figure, P s is the pressure of the coolant gas in the suction pressure area, for example, in the suction port or the suction chamber, and Pc is the control pressure, for example, in the crank chamber. Pd indicates the pressure of the coolant gas in the discharge area, and Pd indicates the pressure of the coolant gas in the discharge pressure area, for example, in the discharge chamber.

This control valve (control valve for a variable displacement type compressor) 28 1 has a discharge pressure area (for example, a discharge chamber) and a control pressure area (for example, a discharge chamber). For example, a valve body 281c that shuts off or opens a passage that communicates with the crank chamber) and a spring receiver 281a are normally provided. Open the valve 2 8 1 c A biasing member 281b (for example, a spring) for biasing the valve in the direction of the valve and an armature 281c 'for driving the valve element 281c are provided as specified. A solenoid 281d that draws the armature 281c 'in the valve-closing direction when current is supplied, and a normal armature 2 A biasing member 281e that urges 81c 'in the valve-closing direction and a pressure sensor (low-pressure sensor) that detects changes in low pressure (for example, suction pressure) Output means) A control device (control means) for controlling the operation of the solenoid 2811d based on the output of the pressure sensor 270 and the pressure sensor 270 ) 27 1 and are provided.

As shown in FIG. 5, the pressure sensor 270 is integrally mounted on the upper part of the housing 281f of the control knob 281. Thus, the control device 27 1 is provided integrally below the housing 28 1 f.

Above the chamber 272 in the housing 281f and the valve element 281c in which the spring receiver 281a and the biasing member 2811b are stored. What is the chamber 2 73 in the housing 28 1 f where the part is housed? The two chambers 27 2 and 27 3 constitute a part of a communication path that connects the discharge chamber and the crank chamber. .

Fig. 6 is a block diagram of the control device of the control valve.

The control device 27 1 includes an amplifier 27 1 a for amplifying an electric signal output from the pressure sensor 27 0, and an amplifier 27 1 Output signal from a and external current setting section

2 7 1 b Input the setting signals and input Signal that outputs a signal proportional to the signal difference (differential amplification circuit) 2 7 1c and the signal 2 7

A drain circuit 271d for driving a solenoid 2881d based on the output of 1c is provided.

The signal value (reference value) set by the external current setting section 27 1 b is applied to one input terminal of the comparator 27 1 c, and the other input terminal is connected to the other input terminal. The detection signal from the pressure sensor 270 amplified by the amplifier 271a is input to the input terminal.

According to the control knob 281, the following effects can be obtained.

(1) A mechanical control valve (connected to the valve body to detect the suction pressure to drive the valve body, and to apply a variable load to the pressure-sensitive means. And a solenoid valve that changes the pressure control point of the pressure-sensitive means), the control accuracy is improved, the response is fast, and there is a danger of mechanical vibration. Less is .

(2) When hunting occurs (a phenomenon in which the pressure inside the compressor fluctuates abnormally), it can return to a normal state by itself.

(3) There is little refrigerant leakage (leakage between PC and? S) inside the control solenoid 281, and the housing 2881f, and control is reduced. Stabilize .

Note that the above-mentioned control device 271 includes an analog circuit, a digital relay circuit, a CPU, and the like. If CPU is used as a circuit for the night of the competition and the driving circuit The detailed operation characteristics can be programmed, and more precise control is possible. When used together with the ECU of the airconsistency system, the complicated control of the compressor can be shared and the entire airconsistment system can be shared. The processing ability of the system is improved. Industrial availability

As described above, in the variable displacement type swash plate type clutch compressor according to the present invention, the driving force of the engine is constantly transmitted. According to the variable-capacity swash plate type clutch compressor, which is useful as a compressor, the seal pipe against the outside air can be used. It will make the process easier and can withstand long-term use.

Claims

The scope of the claims

1. a discharge chamber for containing the cooling gas discharged from the compression chamber;

It is installed in the middle of the passage that connects the crank chamber that houses the swash plate and the discharge chamber described above, and responds to changes in heat load in response to changes in heat load. Variable swash plate type equipped with a pressure control valve that regulates the cross-sectional area of the pump and a suction passage that guides the cooling gas from the suction port to the suction chamber. In the clutchless compressor,

The pressure of the cooling gas downstream of the pressure control valve and the biasing force of the biasing member act in the direction of closing the valve, and the cooling of the discharge chamber The suction control valve that shuts off the suction passage described above only when the pressure of the medium gas acts in the valve opening direction and the pressure difference between the two drops below a predetermined value. A variable capacity type swash plate type clutch compressor characterized by having a swash plate.

2. The scope of the claim that the suction control valve is a spool valve The variable displacement type swash plate type clutchle described in Paragraph 1 of the claim Compressor.

3. A pressure-reducing means that is installed downstream of the pressure control valve on the communication path and that restricts the flow of the cooling gas that is led to the crank chamber. The scope of the claim, which is characterized by the fact that the variable capacity swash plate type clamp compressor described in Paragraph 1 is provided.

4. The suction control valve is a spool valve, Come S one

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