JPH02181078A - Actuator - Google Patents

Abstract

PURPOSE:To make an actuator for an electromagnetic value for capacity control in a cooling medium compressor of a changeable capacity type compact and its cost low by composing it to drive a subject part by displacing a pressure- based follower member by thermal expansion or heat shrinkage of enclosed gas. CONSTITUTION:For a capacity-changeable compressor 1, an inclined plate 35 is rotated through a shaft 15, a wobble 31 by drive rotation of a pulley 11 to reciprocate a piston 39 through a connecting rod 37 in a cylinder 13, so cooling medium sucked from a suction chamber 61 into a cylinder chamber is compressed and discharged from a discharge chamber 63. In this case, an actuator 200 is provided for control by capacity control of a stroke of the piston 39, or a pressure in a pressure chamber 25. This actuator 200 energizes a thermoelectric element 204, and cool and condense the cooling medium in a bellow phragm 203 to shrink the bellow phragm 203 and close a ball valve 202, setting the side of the bellow phragm 203 for a heat suction part, and the side of a heat exchanger 26 for a heat radiation part.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a compressor used in a refrigeration cycle, and specifically relates to a variable capacity refrigerant compressor.

(Prior Art) In recent years, the compression capacity of compressors used in vehicle air conditioners has become variable in order to save power and improve drivability.

For example, a wobble-type reciprocating variable capacity compressor uses a pressure regulator to control the pressure in the crankcase on the back side of the piston according to the pressure in the low-pressure chamber, etc., thereby changing the effective stroke of the piston and increasing the capacity. There is something to control.

(Problems to be Solved by the Invention) Capacity control of such a variable capacity compressor involves controlling the pressure inside the crankcase, and conventionally, this pressure inside the crankcase has been controlled by a pressure regulator.

In this case, if a solenoid valve is used as a control means instead of a pressure regulator, the capacity of the compressor can be adjusted in a responsive manner by freely opening and closing the solenoid valve using an external electric signal depending on the vehicle's driving conditions. Variable control is possible, making it possible to realize an even better air conditioning system.

However, in this case, in order to sensitively control the pressure inside the crankcase using the solenoid valve, duty control using a high-frequency pulse current of several Hz is required, which causes vibration durability problems due to the repeated opening and closing of the solenoid valve, and is complicated. New problems arise, such as the need for expensive electrical circuits to perform accurate duty control.

Also, as a method to vary the compressor capacity with good response without using this duty control, for example, a method of directly driving the valve body with a servo motor etc. can be considered.
In this case, since a large driving force is required, an increase in the size of the device is unavoidable.

The present invention was made to solve these problems, and provides a compact actuator with a large driving force that can quickly control opening and closing of minute openings without using solenoid valves, servo motors, etc. The object of the present invention is to provide a variable capacity compressor using a mounting structure and this actuator.

(Means for Solving the Problems) For this purpose, the actuator in the first aspect of the present invention includes a telescopic pressure-responsive member that drives a driven portion;
The pressure-responsive member includes a sealed gas and a thermal control means for heating or cooling the sealed gas, and the driven part is displaced by displacing the pressure-responsive member by thermal expansion or contraction of the sealed gas. It is characterized by being driven.

In the actuator mounting structure according to the second aspect of the present invention, the heat control means utilizes the Peltier effect, and the heat absorbing part of the heating element is provided on the sealed gas side, and the heat radiating part of the heating element is kept at a low temperature. It is characterized by being set in the environment.

The actuator according to the third aspect of the present invention includes a low pressure chamber into which suction fluid is introduced, a working chamber which sucks fluid from the low pressure chamber and compresses and discharges the fluid, and a working chamber through which the fluid is discharged from the working chamber. An actuator used in a compressor having a high-pressure chamber and a variable capacity means for varying the discharge capacity of the working chamber, the actuator including a telescopic pressure-responsive member that drives the variable-capacity means, and the pressure-responsive member. and a heat control means for heating or cooling the sealed gas, and the pressure responsive member is displaced by thermal expansion or contraction of the sealed gas to drive the capacity variable means. Features.

(Function) According to the actuator of the first invention, the sealed gas is heated or cooled by the thermal control means so that the sealed gas is thermally expanded or contracted, and the bellow flam is expanded or contracted to drive the valve body. The valve opening area of the passageway in which the body is provided is varied.

According to the actuator mounting structure of the second invention, since the heat control means utilizes the Peltier effect,
When the heat dissipation section of the heat control means is exposed to a low-temperature environment during cooling of the sealed gas, the heat absorption performance is improved. As a result, the time required for the sealed gas to reach a low temperature can be shortened, and the temperature itself can also be lowered. Therefore, the response time and displacement amount of the valve can be increased.

According to the variable capacity compressor of the third invention, the sealed gas in the bellow flammable gas expands or contracts in volume by the thermal control means, thereby changing the amount of displacement of the bellow flaming and changing the valve opening area. The actuator enables minute control of opening and closing of the valve, and by controlling the flow rate of the bypass passage, variable control of the fluid pumping capacity can be performed appropriately.

(Example) Embodiments of the present invention will be described based on the drawings.

1 to 3 show a first embodiment in which the present invention is applied to a reciprocating type swash plate type variable capacity compressor for an air conditioner mounted on a vehicle.

As shown in FIG. 3, this air conditioner has a configuration in which refrigerant is circulated in the order of a variable capacity compressor 1, a condenser 2, a liquid receiver 3, an expansion valve 4, and an evaporator 5.

That is, the refrigerant vaporized in the evaporator 5 becomes vapor, passes through the superheat detection section 6, enters the compressor I, becomes high temperature and high pressure in the compression stroke, and is led to the condenser 2. The refrigerant is cooled by air and condensed to become a liquid refrigerant, which is transferred to the liquid receiver 3.
can be accepted. The liquid refrigerant received in the liquid receiver 3 passes through the expansion valve 4 and becomes a gas-liquid mixture at a low temperature and low pressure, and is transferred to the evaporator 5.
sent to. The refrigerant that is evaporated by removing heat from the air ventilated in the direction of the arrow in the evaporator 5 becomes a gaseous refrigerant, and after being sucked into the compressor 1, the above-mentioned refrigeration cycle is repeated.

In the variable displacement compressor 1, when the air conditioning switch 8 is turned on, the electromagnetic clutch 93 is activated by the power supply 9 and the control device 10.
is turned on, the engine's driving force is transmitted, and the engine is driven. The control device 10 detects the temperature of the air blown from the evaporator 5 using the thermistor 12, and when the temperature of the air blown from the evaporator 5 is, for example, 4°.
Figures 1 and 2 are connected by signal lines a and b so that
The voltage applied to the thermoelectric element 204 of the actuator 200 shown in the figure is controlled, and the pressure chamber (crankcase) 2 of the compressor 1 is controlled.
Control the pressure within 5.

Next, the structure of the variable capacity compressor 1 will be explained.

A plurality of cylinders 13 are formed in parallel to each other inside a housing 14 made of aluminum alloy.

A pressure chamber housing 15 is arranged on the side surface of the housing 14, and a shaft 17 is rotatably supported by the pressure chamber housing 15 and the housing 14. That is, a bearing 9 is press-fitted into the housing 14, and the shaft 17 is rotatably supported by the bearing 19. The other end of the shaft 17 is rotatably supported by a bearing 21.

Further, a shaft seal 23 is arranged between the shaft 17 and the pressure chamber housing 15, and this shaft seal 23 prevents the refrigerant and lubricating oil in the pressure chamber 25 from leaking outside along the outer circumference of the shaft 17. is prevented. A pin guide 27 is fixed to the shaft 17, and the pin guide 27 rotates together with the shaft 17. A pin 29 is connected to this pin guide 27, and the wobble 31 is connected to the bin guide 27 by this pin 29. Therefore, the wobble 31 rotates together with the shaft 17. A hair ring 33 is disposed on the - side of the wobble 3, and a swash plate 35 is connected to the wobble plate 35 via this bearing 33.
is held in a rotatable state. Therefore, the rotational movement of the wobble 31 due to the rotation of the shaft 17 is released by the bearing 33, and the swash plate 35 performs only a swinging movement within the pressure chamber 25. Swash plate 3
The rocking motion of 5 is caused by the piston 39 via the connecting rod 37.
transmitted to.

The piston 39 is disposed within the cylinder 13 so as to be able to slide back and forth, and a connecting recess 41 is formed on the back surface of the piston 39 . Connecting rod 37 is inserted into this recess 41.
A ball 43 at the tip is provided for free spherical movement.
3 is held by a holding plate 45 fixed to the inner peripheral wall of the piston.

A ball 47 is also formed at the other end of the connecting rod 37, and this ball 47 is rotatably held by the swash plate 35 via a holding plate 49.

Here, since the wobble 31 is connected by the pin 29, the wobble 31 can be tilted with respect to the shaft 17. Therefore, the inclination angle of the swash plate 35 is also made variable according to the change in the inclination angle of the wobble 31. A change in the inclination angle of the swash plate 35 results in a change in the reciprocating stroke of the piston 39. Note that a support rod 51 is disposed between the housing 14 and the pressure chamber housing 15 so that the swash plate 35 only performs a swinging motion and not a rotational motion. This support rod 51 is slidably engaged with a connecting portion 53 of the swash plate 35, so that the swash plate 35 only moves along the support rod 51.

Note that connection holes 55 are formed in the outer peripheral surfaces of the housing 14 and the pressure chamber housing 15, respectively, and the compressor l is directly fixed to the vehicle engine via the connection holes 55.

A side housing 59 is disposed outside the side bullet 57 disposed at one end of the housing 14 . A suction chamber 61 that receives refrigerant from the evaporator 5 and a discharge chamber 63 that supplies refrigerant to the condenser 2 are formed within the side housing 59. The suction chamber 61 communicates with the cylinder 13 via a suction hole 65 formed in the side plate 57. A suction valve 6 is provided on the cylinder 13 side of the suction hole 65.
6 is disposed to allow the refrigerant to flow only from the suction chamber 61 to the side of the cylinder 13. The discharge chamber 63 is connected to the cylinder 1 through a discharge hole 67 formed in the side plate 57.
It communicates with 3. A discharge valve 69 is disposed on the discharge chamber 63 side of the discharge hole 67, and allows the refrigerant to flow only from the cylinder 13 toward the discharge chamber 63.

The above-mentioned discharge chamber 63 communicates with the relay chamber 87 from the passage 85 via the passage 212 of the actuator main body 201 and the actuator chamber 71 from the passage 7o. The relay room 87 is
It opens into the pressure chamber 25 through through holes 73, 74 formed in the shaft 17. A communication hole 91 communicating with the pressure chamber 25 communicates with the low pressure chamber side. An actuator 200 that opens and closes the passage 75 is connected to the side housing 5.
9 is attached to the actuator chamber 71.

In the actuator 200, an actuator body 201 is housed in an actuator chamber 71 of a side housing 59, and this actuator body 201 is fitted with an O ring 25.
1 and fixed to the side housing 59 by a circlip 252. As shown in FIG. 2, inside the actuator chamber 201, there is a ball valve 202 that opens and closes a passage 211 communicating with the passage 70, and a valve ram 203 that operates the ball valve 202 via a rod 208. The stay 205 to which one end of the bellow frame 203 is bonded, and the bellow frame 20 of the stay bottom plate 205a
Thermoelectric element 204 connected to the opposite side of Thermoelectric element 2
Heat exchanger 206 fixed to the surface of 04 and heat exchanger 2
A refrigerant chamber 2+6 that accommodates the refrigerant chamber 216 and a cap 207 that isolates the refrigerant chamber 216 from the outside world are provided.

A gas-liquid mixed phase refrigerant in a saturated state is sealed in the bellow flamm 203, and a collar 221 is provided inside the bellow flamm 203 to prevent the liquid refrigerant contained therein from scattering. Stay bottom plate 20 to which thermoelectric element 204 is attached
5a is made of resin with high thermal conductivity, and a copper print as an electrode is applied to the side surface of the thermoelectric element of the stay bottom plate 205a. Thermoelectric elements are electrically connected to this electrode in a series arrangement. Both ends of the electrodes are electrically connected to external terminals 209 and 220, respectively.

Bellow frame storage chamber 2 where bellow frame 203 is provided
13 communicates with the first gutter 215 from the passage 214, and
The side groove 215 further communicates with the suction chamber 61. Furthermore, the refrigerant chamber 216 in which the thermoelectric element 204 is arranged is connected to a passage 217.
, 218 to the second side groove 219. Second
The side gutter 219 is connected to the suction chamber 61.

Next, the operation of the variable displacement compressor l provided with the actuator 200 will be explained.

When the electromagnetic clutch 93 is connected by an external signal, the rotational driving force of the engine is transmitted to the shaft 17 via the electromagnetic clutch 93. As the shaft 17 rotates, the wobble 31 rotates and swings, and the swash plate 35 swings. The rocking motion of the swash plate 35 is transmitted to the piston 39 via the connecting rod 37, and the piston 39 reciprocates within the cylinder 13.

As the piston reciprocates, during the suction stroke of the piston 39, the low-pressure refrigerant in the suction chamber 61 pushes open the suction valve 66 and is sucked into the cylinder 13 through the suction hole 65. Further, in the compression stroke of the piston 39, the refrigerant in the cylinder 13 is compressed, and when the pressure reaches a predetermined pressure or higher, the refrigerant pushes open the discharge valve 69 and is discharged from the discharge hole 67 into the discharge chamber 63.

The high-pressure refrigerant discharged into the discharge chamber 63 is fed under pressure to the condenser 2.

The discharge capacity of the compressor I is made variable by changing the inclination angle of the swash plate 35. This angle of inclination varies depending on the pressure within the pressure chamber 25. That is, as the pressure inside the pressure chamber 25 increases, the pressure applied to the back surface of the piston 39 also increases.
As a result, the piston 39 does not retreat much from the top dead center. If the pressure inside the pressure chamber 25 increases in this way,
The angle of inclination of the swash plate 35 becomes smaller, and the reciprocating stroke of the piston 39 also becomes smaller.

The actuator 200 controls the pressure in the pressure chamber 25 to make the stroke variable. That is, in FIG. 3, the temperature of the air blown from the evaporator 5 is detected by the thermistor 12.

The control device 10 commands the terminals 209.
The voltage applied to the thermoelectric element 204 input to the thermoelectric element 220 is controlled, and the pressure inside the pressure chamber 25 is controlled as described later.

For example, if the blowing air temperature exceeds 4.5°C, the control device 1
According to the command 0, the signal line a is set to one pole and the signal line b is set to ten poles, and a voltage is applied to the thermoelectric element 204 from the terminals 209 and 220. Then, in the thermoelectric element 204, the bellow flamm 203 side (upper side in FIG. 2) becomes a heat absorbing part, and the heat exchanger 206 side (lower side in FIG. 2) becomes a heat radiating part. As a result, bellow flam 20
3 cools and condenses, the pressure inside the bellow flamm 203 decreases and the bellow flamm 203 contracts, so the ball valve 202 descends via the rod 208 and the passage 21
Reduce the opening area of 1. As a result, the communication area between the discharge chamber 63 and the pressure chamber 25 is reduced, the pressure within the pressure chamber 25 is reduced, the effective stroke of the piston 39 is increased as described above, and the capacity of the compressor 1 is increased. At this time, the heat radiation part of the thermoelectric element 204 is exposed to a relatively low-temperature low-pressure refrigerant via the heat exchanger 206, so the coefficient of performance of the thermoelectric element 204 is improved due to the Peltier effect, and the actuator 200 is made smaller. , improving responsiveness when opening and closing the valve.

Conversely, when the temperature of the blown air becomes, for example, 3.5° C. or lower, the signal line a is switched to ten poles and the signal line b to poles, contrary to the above. When the voltage applied to the thermoelectric element 204 is reversed, the thermoelectric element 20
The bellow flamm 203 side of No. 4 becomes a heat dissipation part and the refrigerant temperature inside the bellow flammable rises, and as a result, the refrigerant pressure increases and the bellow flamm 203 expands.Contrary to the above-mentioned operation, the ball valve 202 rises and the opening area of the passage 211 increases. increase. As a result, the high pressure in the discharge chamber 63 is guided to the pressure chamber 25, the pressure in the pressure chamber 25 increases, and the piston 3
The effective stroke of 9 is reduced and the capacity of compressor 1 is reduced.

FIG. 4 shows a second embodiment in which the present invention is applied to a reciprocating swash plate type variable capacity compressor.

The variable displacement compressor 400 is configured such that its discharge capacity is variable according to the inclination angle of a swash plate 403 that is slidably attached to a spherical surface 402a of a pivot 402 fixed to a shaft 401. The inclination angle of the swash plate 403 is the same as that of the pivot 4.
A cylindrical piston 40 that is slidable in the axial direction via a thrust bearing 407 that abuts the flange 406 of 02 in the axial direction.
It is controlled by the displacement of 8. The state shown in FIG. 4 shows a state in which the piston 408 is at the leftmost position in FIG. 4, and the swash plate 403 is at the maximum tilt angle position, indicating the maximum pumping capacity position. A plurality of actuators 4]0 drive the position of the piston 408.

As in the first embodiment, the actuator 410 drives the piston 408 by expanding and contracting the resin bellow flamm 412 by controlling the pressure in the hellofram chamber 411 using a thermoelectric element. Inside the bellow flamm chamber 4]1 defined by the bellow flamm 412, there is an activated carbon fixing case 413.
, a thermoelectric element 4 fixed to the bottom surface of the case, and a radiation fin 4 formed on the surface to which this thermoelectric element 414 is fixed.
It consists of 15 mag.

When the activated carbon fixing case 413 side of the thermoelectric element 414 becomes a heat absorbing part due to an external signal, the activated carbon fixing case 413
The heat of the activated carbon inside is taken away. As a result, activated carbon refrigerant (
R12) Bellow frame chamber 411 increases adsorption performance.
It adsorbs the refrigerant (R]2) inside. As a result, the pressure inside the bellows flamm chamber 411 decreases, the bellows flamm 412 contracts, the piston 408 moves rightward from the position shown in FIG. 4, and the pivot 402 is installed as shown in FIG. The plate 403 rises in a direction perpendicular to the shaft 401 and reduces the effective stroke of the piston 418 via a ball 417 provided at the tip of the swash plate 403, thereby reducing the capacity within the cylinder 420.

When the piston 418 moves to the left from the state shown in FIG.
The refrigerant enters the cylinder chamber 420 from the suction chamber 424 defined by 22 through the passage 426, and then when the piston 418 moves to the right, the refrigerant in the cylinder 420 is discharged from the passage 428 into the discharge chamber 430. Similarly, the housing 42
Similar suction and discharge actions are performed in a suction chamber 423 and a discharge chamber 432 that are defined by the side housing 421 on the opposite side.

Note that the bellow flamm chamber 440 in which the bellow flamm 412 is housed is connected to the suction chamber 424 through a passage 442 and to a heat radiation chamber 448 through passages 444 and 446. Further, side housings 421 and 422 are fixed to housing 419 with bolts 450.

The housing 419 is fixed to the engine body through a connecting hole 452 with a bolt (not shown).

With this configuration, by alternating the voltage applied to the thermoelectric element 414, the adsorption force of the activated carbon in the activated carbon case 413 is controlled by temperature, thereby making it possible to vary the pressure in the bellow flamm chamber 4]1. The expansion and contraction of the compressor allows for flexible control of the compressor capacity.

5 and 6 show a third embodiment of the present invention, in which the present invention is applied to a rotary vane type variable capacity compressor.

In the variable displacement compressor 500, a shaft 510 is rotatably provided in a compression chamber 504 defined in a housing 502 via bearings 506 and 508.
A rotor 512 fixed at zero is rotatably provided at an eccentric position in the compression chamber 504. A plurality of vanes 514 are supported in a radially slidable manner within a plurality of slits formed in the radial direction of the rotor 512 .

When the electromagnetic clutch 516 is connected, the driving force of the engine is transmitted to the pulley 518, the driving force is transmitted to the shaft 10 via the pulley 518, and the rotor 512 is rotated. When the rotor 512 is rotated, the refrigerant is guided from the suction port 522 of the side housing 520 to the compression chamber 504, and by the pumping action of the vane 514, from the discharge chamber 528, through the through hole 530, through the oil separator 532, and into the condenser 2. be pumped.

An actuator 534 that changes the capacity of the compression chamber 504 is provided in the site housing 520.

In the actuator 534, bypass holes 540 and 542 are opened in the cylinder chamber 536 in a direction perpendicular to the longitudinal direction, and these bypass holes 540 and 542 communicate with the low pressure chamber 524 and the compression chamber 504, respectively. A plunger 544 slidably provided in the cylinder chamber 536 freely changes the opening area of the bypass holes 540 and 542, thereby controlling the compressor capacity. Plunger 544
is biased by a spring 548 that abuts against a stopper 546 in a direction that increases the opening area of the bypass holes 540 and 542. The other end of the plunger 544 is biased by a bellows flam 550 in a direction in which the bypass holes 540, 542 are closed. A refrigerant is sealed inside the bellow frame 550, and this refrigerant is supplied to the communication path 5.
52 to the temperature sensing section 556.

The temperature sensing unit case 558 is filled with a saturated refrigerant having a gas phase and a liquid phase, and is fixed to a low pressure pipe 562 by a C-shaped clip 564 via a thermoelectric element 560 on the outside of the case. Although not shown in the figure, a heat insulating material is wrapped around the temperature sensing portion 556 and constant pressure piping 562. in this case,
Since one side of the thermoelectric element 560 is in contact with the low-pressure pipe 562, the Peltier effect when cooling or heating the temperature sensing part case 558 when electricity is applied is well exhibited on the opposite side of the thermoelectric element 560, and the actuator E) 34 responsiveness is improved.

In alternating the voltage applied to the thermoelectric element 560,
Control the refrigerant pressure inside the temperature sensing part case 558,
1, FIG. 7 and FIG. 8 show that the position of the plunger 544 is made variable by controlling the pressure in the bellow flamm 550 via the communication passage 552, and the opening area of the bypass hole 540, 542 is changed to control the compressor capacity. This shows a fourth embodiment of the present invention, and the temperature sensing section 556 of the third embodiment
This is a modification of the heating and cooling means.

A temperature sensing part case 704 of a temperature sensing part 702 is filled with a saturated refrigerant that is mostly in a liquid phase.6 Temperature sensing part case 7
The outer periphery of 04 is covered with a stay 7 made of copper, for example, which has good thermal conductivity.
06 and is closely fixed with a rehet 708. The stay 706 tightly fixes the PTC heater 710, further wraps around the low pressure pipe 562, and has the other end 706a tightly fixed with a rivet 712. Lead wires 716 and 718 are connected to the PTC heater 710, the lead wire 718 is grounded, and the lead wire 716 is connected to a control device. The compressor 500 is similar to the third embodiment shown in FIG. 5, so the same components are denoted by the same reference numerals and the explanation thereof will be omitted.

In the fourth embodiment, as in the first embodiment shown in FIG. 3, the PTC heater 710 is turned on and off in order to control the compressor capacity according to the temperature of the air blown from the evaporator 5. That is, when the PTC heater 710 is energized, the heater heat is transmitted to the temperature sensing part case 704 by the stay 706, and the refrigerant temperature in the temperature sensing part case 704 increases. Conversely, when the PTC heater 710 is in a non-energized state, heat is taken from the temperature sensing part case 740 to the low pressure pipe 562 via the stay 706, and the temperature of the refrigerant in the temperature sensing part case 704 decreases. In this way, by repeating energization and de-energization of the PTC heater 710, the temperature of the temperature sensing section 702 is controlled, and the refrigerant flowing from the temperature sensing section case 704 through the bellows frame 550 shown in FIG. 6 via the communication path 552 is controlled. The pressure is controlled, and the compressor capacity is controlled by expanding and contracting the bellows frame 550 as described above.

(Effects of the Invention) As explained above, according to the actuator of the present invention, the pressure in the bellow flammable gas containing the sealed gas is controlled by the thermal control means, and the valve opening/closing operation is performed by the relative displacement of the valve body as the bellow flammable expands and contracts. The effect is that it can be carried out effectively.

Furthermore, the actuator body can be made smaller and its durability can be improved.

According to the actuator mounting structure of the present invention, one end surface of the thermoelectric element is connected to the bellow flamm side, and the other end surface is maintained in a low-temperature atmosphere. can be efficiently cooled, and the valve opening/closing operation efficiency of the actuator can be increased.

According to the variable capacity compressor of the present invention, a valve driving actuator is incorporated in the bypass passage connecting the high pressure chamber and the low pressure chamber, and this actuator is driven by thermal expansion or thermal contraction of the sealed gas. The effect is that the discharge volume can be variably controlled to an appropriate discharge volume in a smooth and responsive manner.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing a variable displacement compressor showing a first embodiment of the present invention, FIG. 2 is an enlarged view of the actuator portion shown in FIG. 1, and FIG. FIG. 4 is a sectional view showing a compressor according to a second embodiment of the present invention, and FIG. 5 is a diagram showing a vane type compressor according to a third embodiment of the present invention. A cross-sectional view, FIG. 6 is a cross-sectional view taken along the line ■-■ shown in FIG. 5, and FIG.
FIG. 8 is a cross-sectional view taken along the line ■--■, which is not shown in FIG. 7. 1... Variable capacity compressor, 5... Pressure chamber (bypass passage), 9... Piston, 1... Suction chamber (low pressure chamber), 3... Discharge chamber (high pressure chamber), 0. 85.91... Passage (bypass passage), 0... Actuator (valve drive actuator), 2... Ball valve (driven part), 3... Bellow flam (pressure responsive member), 4... Thermoelectric element (thermal control means).

Claims (3)

[Claims] (1) A telescoping pressure-responsive member that drives the driven part;
The pressure-responsive member includes a sealed gas and a thermal control means for heating or cooling the sealed gas, and the driven part is displaced by displacing the pressure-responsive member by thermal expansion or contraction of the sealed gas. An actuator characterized by driving. (2) The heat control means utilizes the Peltier effect, and the heat absorption part of the heating element is provided on the side of the sealed gas,
2. The actuator mounting structure according to claim 1, wherein the heat radiation part of the heating element is provided in a low temperature environment. (3) It has a low pressure chamber into which suction fluid is introduced, a working chamber which sucks fluid from this low pressure chamber and compresses and discharges the fluid, and a high pressure chamber from which fluid is discharged from this working chamber, and An actuator used in a compressor including a capacity variable means for varying the discharge capacity of a working chamber, the actuator comprising: a telescopic pressure-responsive member for driving the capacity-variable means; and a sealed gas sealed in the pressure-responsive member. An actuator comprising a thermal control means for heating or cooling the sealed gas, and for driving the capacity variable means by displacing the pressure-responsive member by thermal expansion or contraction of the sealed gas.