WO1991019095A1

WO1991019095A1 - Continuously variable capacity type swash plate compressor

Info

Publication number: WO1991019095A1
Application number: PCT/JP1991/000750
Authority: WO
Inventors: Manabu Sugiura; Masafumi Ito; Kazuya Kimura
Original assignee: Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority date: 1990-06-04
Filing date: 1991-05-31
Publication date: 1991-12-12
Also published as: JPH0417183U; EP0489164A4; KR920702467A; EP0489164A1

Abstract

A continuously variable capacity type swash plate compressor of this invention is characterized by being provided with a control valve which selectively introduces discharge pressure and suction pressure into a controlled pressure room formed between the plunger and housing by means of pressure sensitive means in response to suction pressure or discharge pressure, changes an inclination angle of the swash plate through said plunger and slider, and is provided with variable energizing means for varying pressure control point of said pressure sensing means. The pressure control point is varied with variable load applied to pressure sensing means by variable energizing means. Thus, capacity control adaptable to varying conditions is available in addition to a regular one.

Description

Sogetsu ^ Ta β Slanted plate type continuously variable capacitance compressor Technical field

The present invention relates to an improvement of a swash plate type continuous gun variable displacement compressor equipped with a double-headed piston. Background technology

As an oblique type continuously variable capacitance compressor suitable for air conditioning of vehicles, for example, the one disclosed in Japanese Patent Application Laid-Open No. Ί -1 3 8 3 8 2 is known. As shown in Fig. 8, this swash plate type continuously variable capacitance compressor has a double-headed piston 5 3 housed in a plurality of bores 5 2 formed in the cylinder block 5 Ί and is parallel to the bore 5 2. A drive shaft 5 4 is arranged on the axis line, and a slider 5 5 is slidably fitted to the drive shaft 5 4. _c The spherical support portion 5 5 a of the slider 5 5 has a peripheral portion. A swash plate 5 7 that engages a double-headed piston 5 3 via a 5 6 is fitted by a matching spherical portion 5 7 a to a connecting portion 5 7 b stretched in front of the swash plate 5 7. A guide bin 5 8 is attached, and this is guided by a long hole 5 4 b drilled in the front shaft portion 5 4 a of the drive shaft 5 4, so that the swash plate 5 7 slides on the slider 5 5. It is possible to tilt with movement, and the center of tilt is set so that the top dead center position on the Lya side of the double-headed piston 53 does not change. Then, the compressive reaction force of the double-headed screw 5 3 always acts as a momentum: VI in the direction of reducing the tilt angle of the slant 5 7, which moves the plunger 6 0 to the right in the figure via the slider 5 5. Encourage. A control pressure chamber 5 9 is formed between the plunger 60 and the rear housing 50, and the discharge pressure P is provided in the control pressure chamber 5 9 by a control valve 40 (see Fig. 9) described later. Since d and the suction pressure P s are selectively introduced, the plunger 60 is also urged to the left in the figure. Therefore, the tilt angle of the swash plate 57, that is, the discharge capacity of the compressor, is determined via the plunger 60 and the slider 5 5 by the equalization of these opposing urging forces.

Figure 9 shows the general configuration of the control valve 40. A ball valve 4 3 connected to a diaphragm 4 2 is attached to the valve main body 4 1 of the control valve 40 0 through the atmospheric pressure Patm and the urging force of the opposing springs 4 4 and 5 and the swash plate chamber via the pressure detection line a. It is designed to operate based on the pressure fluctuation of the detection pressure chamber 4 6 in which the suction pressure P s is introduced in communication with 6 1 (see Fig. 8). The valve chamber that houses the ball valve 4 3 4 7 is always communicated with the control pressure chamber 5 9 (see Fig. 8) by the supply pipeline b, and the upper chamber 4 8 partitioned by the Ί valve seat 4 8 a of the valve chamber 4 7 is further connected. The lower chamber 4 9 which connects to the discharge chamber 6 2 (see Fig. 8) via the high pressure pipeline c and is also partitioned by the second valve seat 4 9 a becomes the detection pressure chamber 4 6 via the low pressure pipeline d. Similarly, it communicates with the swash plate chamber 6 Ί. Therefore, in this control valve 40, the suction pressure P s introduced into the detection pressure chamber 4 6 through the pressure detection line a is the atmospheric pressure Pat m and the counter spring 4 4, 4 5 When overcoming the urging force of, the diaphragm 4 2 bends downward as shown in the figure, the ball valve 4 3 sits on the second valve seat 4 9 a, and the discharge pressure P d through the high pressure line c is the supply pipe. It is supplied to the control pressure chamber 59 as the activation pressure P c via the path b. On the contrary, when the suction pressure P s introduced into the detection pressure chamber 4 6 defeats the atmospheric pressure Pat m and the urging force of the opposing springs 4 4 and 4 5, the diaphragm 4 2 starts to reverse upward. The ball valve 4 3 gradually opens the second valve seat 4 9 a, and the internal pressure in the control pressure chamber 5 9 passes through the supply line b in the opposite direction, and escapes to the swash plate room 6 Ί through the low pressure line cl. Therefore, the activation pressure P c decreases with _{this c.} Thus, in this compressor, the capacity can be changed according to the change of the suction pressure P s. In the above-mentioned conventional compressor, the opening degree of the ball valve 4 3 in the control valve 40 is controlled by the expansion and contraction of the diaphragm 4 2 in response to the suction pressure P s, and the control is based on the valve opening degree. The tilt angle of the swash plate 5 7 is controlled through the pressure change in the pressure chamber 5 9. In this case, the pressure control point of the diaphragm 4 2 which is the pressure sensitive means is specified by the atmospheric pressure Patm and the spring constants of the opposing springs 4 4 and 45, and as a result, the swash plate is only determined by the suction pressure P s. The tilt angle of 57, that is, the discharge capacity of the compressor is controlled. Therefore, in the above-mentioned conventional compressor, for example, even if a sudden decrease in capacity is requested in order to avoid deterioration of the driving feeling at the time of sudden acceleration of the vehicle, such a request cannot be met. In addition, the vehicle air conditioner including such a compressor is set to be constant so that it can be air-conditioned according to the summer. Also requested that the air conditioning in response to seasonal changes or external environmental changes, under the compressor waiting for changes in the suction pressure P s performing capacity control, _c thus can not meet rapidly to such demands, It is hard to say that conventional compressors are satisfactory not only in terms of driving feeling but also in terms of air conditioning function.

Disclosure of the invention _c.

The swash plate type continuously variable pressure compressor of the present invention has a cylinder block in which double-headed screws are housed in a plurality of bores, a drive shaft arranged on an axis parallel to the bore, and the drive shaft. It is equipped with a slidably fitted slider and a guide bin that is tiltably pivotally supported by the slider and engages with the above-mentioned double-headed screw to fit into a long hole drilled in the drive shaft. The plunger and the housing include a swash plate and a plunger that rotatably supports the slider and changes the tilt angle of the swash plate by axial displacement of the slider, and by a pressure sensitive means that responds to suction pressure or discharge pressure. A slanted continuously variable capacitance equipped with a control valve that selectively introduces discharge pressure and suction pressure into a control pressure chamber formed between the two and changes the tilt angle of the slant plate via the plunger and the slider. Smell of type compressor The control valve can change the pressure control point of the pressure sensitive means. It is a special feature to have a means of change.

The swash plate type continuously variable capacitance compressor of the present invention replaces the control valve of the conventional swash plate type continuous variable capacitance compressor with a control valve having a variable urging means that changes the pressure control point of the pressure sensitive means. It has a structural feature where it is adopted.

Here, the pressure control point of the pressure-sensitive means means a displacement point of the pressure-sensitive means that is in equilibrium with the set suction pressure.

This control valve has an introduction pressure switching valve that selectively introduces discharge pressure and suction pressure into the control pressure chamber, a variable urging means that changes the pressure control point, and a pressure sensitive means that drives the introduction pressure switching valve. The introduction pressure switching valve is a movable valve that adjusts the opening of the valve opening that communicates the suction pressure and the discharge pressure, respectively, in order to introduce the suction pressure, the discharge pressure and the intermediate pressure thereof into the control pressure chamber. The body moves between the two valves mentioned above. As such an introduction pressure switching valve, in the embodiment of the present invention, a movable valve having a ball valve is used, but the valve is not limited to this.

The pressure-sensitive means include a pressure-sensitive part that drives the introduction pressure switching valve in the forward and reverse directions according to the pressure fluctuation of either the suction pressure or the discharge pressure, and a variable urging means that changes the pressure control point. As the pressure sensitive part, a mechanism having an urging means such as a spring that acts on the pressure chamber on one side of the diaphragm and resists the suction pressure or the discharge pressure acting on the pressure chamber can be used. Then, the movement of the diaphragm is transmitted to the movable valve of the introduction pressure switching valve to drive the movable valve. Atmospheric pressure, vacuum, etc. on the other side of the diaphragm A pressure chamber with a predetermined pressure is formed. Instead of the pressure-sensitive diaphragm, a pressure fluid such as a screw can be used.

The variable urging means urges the movable valve in one direction or the opposite direction with a variable urging force while being applied to the pressure sensitive portion. Specifically, an electrically controlled mechanical urging mechanism or fluid pressure can be adopted as the variable urging means. Since this variable urging means controls the capacity according to seasonal changes and changes in the outside environment, it can be controlled by detection command signals such as the steamer outlet temperature and the outside air temperature due to solar radiation. In addition, since capacity control is performed according to the sudden acceleration of the vehicle, it can be controlled by detection command signals such as accelerator opening, engine speed, and vehicle speed.

Since the pressure control point of the pressure-sensitive means changes due to sudden acceleration of the vehicle, seasonal changes, or changes in the outside environment, the swash plate type continuously variable capacitance compressor of the present invention quickly responds to the sudden acceleration of these vehicles. The capacity can be controlled, for example, the capacity of the compressor can be sharply reduced in order to avoid deterioration of the movement feeling when the vehicle is suddenly accelerated. A brief description of the drawing

Figures Ί to 4 relate to the compressor of Example Ί of the present invention, Fig. Ί is a cross-sectional view of the compressor, Fig. 2 is a cross-sectional view of the control valve, and Fig. 3 shows the relationship between time and discharge capacity. The graph shown, Fig. 4, is a graph showing the relationship between the current supplied to the electromagnet and the set suction pressure. Figure 5 and Figure 6 relates to Example ^_ of the compressor, cross-sectional view of Fig. 5 control valve, Figure 6 is a graph showing the relationship between the current and the target suction pressure to be supplied to the electromagnet ..

FIG. 7 is a cross-sectional view of the control valve of the third embodiment.

Fig. 8 and Fig. 9 relate to the conventional compressor, Fig. 8 is a cross-sectional view of the conventional compressor, and Fig. 9 is a cross-sectional view of the control valve. Best Mode for Implementing the Invention Hereinafter, the swash plate type continuously variable capacitance compressor of the present invention will be specifically described with reference to Examples.

[Example Iota

As shown in Fig. 1, the compressor of Example Ί is constructed by joining a pair of front and rear blocks Ί a and 1 b to each other, and a swash plate chamber 2 is formed in the center of the inside. At the same time, the front and rear end faces are connected to the front and rear housings 3 and the rear housing 4. Multiple sets of bores 5 a and 5 are formed in the cylinder block Ί at opposite positions on the front side and the rear side of the swash plate chamber 2, and the double-headed piston 6 can reciprocate in both bores 5 a and 5 b. Housed in _c

In the cylinder block Iota, the drive shaft 7 consisting of the front shaft portion 7 a, the rear shaft portion 7 b, and the flat connecting portion 7 c formed between the two is parallel to the bores 5 a and 5 b. It is rotatably supported on the axis, and a long hole 7d is bored in the connecting part 7c. In the block 1 b on the Lya side, the stalk 8 can be moved along the axis of the drive shaft 7. The drive shaft 7 is arranged so that the front shaft portion 7 a is supported by the front shaft portion 7 a via the bearing 9 a and the front shaft portion 7 b is supported by the front shaft portion 7 b via the bearing 9 b. Fitted with a possible bearing slider Ί 0.

A pair of support shafts 1 1 project in the radial direction at the base of the slider Ί 0 located in the swash plate chamber 2, and the swash plate Ί 2 is supported so as to be tiltable with the support shaft Ί 1 as a pivot axis. The swash plate Ί 2 has a main body Ί 2 a that transmits the rotational swing motion to the double-headed piston 6 as a reciprocating motion via the displacement Ί 3, and a long hole 7 d that extends forward from the main body Ί 2 a. a and _c are formed by the guide bottle 1 5 torque transmission are connected via a portion Ί 2 b, based on the axial displacement of the slider I 0 co dynamic and the sleeve 8, the guide bottles I 5 The tilt angle of the swash plate Ί 2 fluctuates by being guided by the long hole 7 d, and the center of tilt is set so that the top dead center on the Lya side of the double-headed piston 6 does not change.

Valve play boxes 20 and 2 Ί are interposed between the cylinder block Ί and the front and rear housings 3 and 4, and the suction chambers 2 2, 2 3 and the discharge chambers 2 4 and 2 are inside the front and rear housings 3 and 4. 5 is formed, and the discharge chambers 2 4 and 25 are connected to an external cooling circuit via a discharge port (not shown). The Freon suction chamber 2 2 communicating with the swash plate chamber 2 via the Freon suction passage 2 6 communicates with the Freon compression chamber via a suction valve mechanism (not shown) provided in the valve play 20. However, the Freon discharge chamber 2 4 is also communicated with the Freon compression chamber via a discharge valve mechanism (not shown). NS. On the other hand, the rear suction chamber 2 3 communicating with the swash plate chamber 2 via the rear suction passage 2 7 also enters the rear compression chamber via a similar suction valve mechanism (not shown) provided in the valve play box 2. The air discharge chamber 25 is also communicated with the rear compression chamber via a discharge valve mechanism (not shown).

A plunger 3 3 is fitted on the rear side of the rear suction chamber 2 3 so as to be slidable in the axial direction in a state where the plunger 3 3 is in contact with the hakama portion 8 a of the stalk 8. A control pressure chamber 3 2 is formed between them. The activation pressure P c is supplied to the control pressure chamber 3 2 from the control valve 70 shown in Fig. 2. The control valve 70 has a ball valve 73 at one end, a diaphragm 7 2 at the center, and a rod 80 with a movable iron core 8 1 at the other end inside the valve body 7 Iota. 7 3 and the movable iron core 8 1 are pressed by the opposing springs 7 4 and 7 5. The valve chamber 7 7 accommodating the ball valve 7 3 is always communicated with the control pressure chamber 3 2 (see Fig. Ί> by the supply line b, and the Ί valve seat 7 8 a of the same valve chamber 7 7 is further connected. The upper chamber 7 8 partitioned by is connected to the Lya discharge chamber 2 5 <Fig. Iota] via the high-pressure pipe c, and the lower chamber 7 9 also partitioned by the second valve seat 7 9 a is the low-pressure pipe d. It communicates with the swash plate chamber 2 (see Fig. Ί) via. The portion including the ball valve constitutes the introduction pressure switching valve of the present invention.

The first detection pressure chamber 7 6 on the ball valve 7 3 side partitioned by the diaphragm 7 2 communicates with the swash plate chamber 2 through the pressure detection line a, and the suction pressure P s is introduced. _C Diaphragm 7 2 Atmospheric pressure Patm is introduced into the second detection pressure chamber 8 2 on the side of the movable iron core 8 1 partitioned by the opening 8 3. Furthermore, around the movable iron core 8 1, an electromagnet 8 5 having a fixed iron core 8 4 on the second detection chamber 8 2 side of the movable iron core 8 1 is integrally equipped with the valve main body 7 Ί = The electromagnet 8 5 is connected to a control means 8 6 composed of a microcomputer to which a potentiometer (not shown) for detecting the accelerator opening is connected, and a current having a value corresponding to the accelerator opening detected by the potentiometer is energized. _c Note to have been made as a spring 7 4, 7 5, the portion including the diaphragms 7 2 and the Ί sensing chamber 7 6 constituting the main portion of the pressure sensitive portion of the present invention. The portion including the movable iron core 8 1 and the electromagnet 8 5 having the fixed iron core 8 constitutes the main part of the variable urging means of the present invention.

Then, as shown in Fig. Ί, the activation pressure P c supplied into the control pressure chamber 3 2 is transmitted to the swash plate Ί 2 via the plunger 3 3, the stalk 8 and the slider 10, and this is the compression reaction. The force acts against the moment M, which acts in a direction that constantly reduces the tilt angle of the diagonal plate 1 2, and the balance between the two forces determines the tilt angle of the diagonal plate Ί 2, that is, the discharge capacity of the compressor.

When the compressor configured as described above is operated and the drive shaft 7 rotates, the swash plate 2 rotates integrally with the drive shaft 7 and swings, and the double-headed piston 6 is moved through the Shu Ί 3. Moves back and forth within the bores 5 a and 5 b. The return refrigerant gas introduced through the suction pipe is from the entrance to the swash plate chamber 2 as the double-headed screw 6 reciprocates. It is guided to the Freon and Lya suction chambers 2 2 and 2 3 via the Freon suction passage 2 6 and the Lya suction passage 2 7, respectively, and is sucked into the Freon and Lya compression chambers to be compressed. Then, the refrigerant gas discharged from both compression chambers to the discharge chambers 24 and 25 via the discharge valve mechanism (not shown) is sent out to the outer refrigerant gas circuit through the discharge passage.

By the way, for example, during constant speed operation of a vehicle, in the control valve 70 shown in Fig. 2, the electromagnet 85 is energized with a current of a predetermined value according to a predetermined accelerator opening, and below this current value. , The set suction pressure P s 0 that balances the diaphragm 7 2 at various displacement points has been determined.

Then, during constant speed operation of the vehicle, if the cooling load is large and the suction pressure P s introduced through the pressure detection line a shifts to the high pressure side, the suction pressure P s is transferred to the Ί detection pressure chamber 76. The diaphragm 7 2 overcomes the atmospheric pressure Patm of the second detection pressure chamber 8 2 and the urging force of the spring 75 5 and bends downward until it is introduced and balanced at its suction pressure P s. For this reason, the ball valve 7 3 is seated in the second valve seat 7 9 a, and the discharge pressure P el through the high-pressure pipeline c is used as the activation pressure P c in the control pressure chamber 3 2 shown in Fig. 1. It is being supplied. Therefore, the support shaft Ί 1 of the swash plate 1 2 is urged forward through the urging element consisting of the plunger 3 3, the mantle 8 and the slider Ί 0, which resists the moment M due to the compressive reaction force. Hold the swash plate Ί 2 at the maximum tilt angle. At this time, as shown in Fig. 3, the compressor is operated with a capacity of _{Ί 0 0? / 0.} On the contrary, during constant speed operation of the vehicle, the cooling load gradually decreases as the capacity operation continues at Ί 0%, and based on this, the suction pressure P s shifts to the low pressure side. At the valve 70, the pressure drop in the Ί detection pressure chamber 7 6 that balances with the urging force of the spring 7 5 causes the diaphragm 7 2 to flip upwards until balanced with its suction pressure P s, causing the ball valve 7 3 to Ascend from the 2nd valve seat 7 9 a. As a result, a part of the pressure in the control pressure chamber 3 2 (see Fig. 1) escapes to the swash plate chamber 2 side, and the pressure in the control pressure chamber 3 2 decreases. Therefore, the swash plate 1 2 is displaced in the direction of reducing its inclination angle, and the capacity of the compressor is constantly reduced.

If the vehicle is accelerated during such constant speed operation, the current exceeding the value during constant speed operation is energized to the electromagnet 85 of the control valve 70 shown in Fig. 2 due to the increase in the accelerator opening. NS. As a result, eight movable iron cores are attracted to the fixed iron core 8 4 against the downward deflection of the diaphragm 7 2, and the ball valve 7 3 is seated via the rod 80 0 on the second valve seat 7 9 Move from a to the first valve seat 7 8 a. For this reason, the pressure in the control pressure chamber 3 2 (see Fig. Ί> is swiftly moved from the open second valve seat 7 9 a to the lower chamber 7 9, and the low pressure pipeline d to the swash plate chamber 2 side. As it escapes, the pressure in the control pressure chamber 3 2 drops. Therefore, the balance with the above-mentioned Momen VI acting on the swash plate Ί 2 shown in Fig. Ί is lost, and the urging element recedes. In the swash plate Ί 2, the guide pin Ί 5 is guided by the elongated hole 7 d to reduce the tilt angle, and the compressor reduces the capacity.

If the vehicle accelerates rapidly, the accelerator opening will increase. Due to the extreme increase, the electromagnet 85 of the control valve 70 shown in Fig. 2 is energized with a current whose value far exceeds the value during constant speed operation. For this reason, the momentary movement of the movable iron core 8 1 in the control valve 70 causes the tilt angle of the swash plate 1 2 to be reduced momentarily, and the compressor quickly moves as shown in Fig. 3. Reduce capacity.

When the vehicle shifts to constant speed operation at the speed after acceleration, the set suction pressure P so 1 (> P so) that keeps the diaphragm 7 2 in equilibrium is determined by the current value according to the accelerator opening at that time. As a result, the control of the suction pressure P s introduced into the detection pressure chamber 76 is resumed under the set suction pressure P so'. That is, in the compressor of this embodiment, the spring constant of the spring 75 is substantially improved as the current value increases, that is, the accelerator opening increases, and the speed of the vehicle increases, and the set suction pressure is set. This means that P s 0 has changed to the high pressure side. Therefore, in this compressor, as shown in Fig. 4, the current value that energizes the electromagnet 85 is positively proportional to the set suction pressure P s 0. _S

In the above embodiment, the control valve 70 was controlled by detecting the accelerator opening in order to control the capacity according to the vehicle speed including the sudden acceleration of the vehicle. It is also effective to detect the engine speed and directly detect the vehicle speed. In addition, if capacity control is performed according to seasonal changes and changes in the outside environment, for example, the evaporator outlet temperature, solar radiation, outside air temperature, etc. can be detected, and the control valve 70 can be controlled by these detected values. can. As a result, for example, in the case of overcooling, the capacity of the compressor is low. Below, in the case of insufficient cooling, the capacity of the compressor can be increased. For example, in a talented air conditioner, a comfortable air conditioning space can be obtained while avoiding mixed air conditioning of warm air and cold air as much as possible and preventing power loss as much as possible. Is obtained.

[Example 2 2

As shown in Fig. 5, the fixed iron core Ί 8 4 of the electromagnet Ί 8 5 can be provided on the side opposite to the second detection chamber 8 2 side of the movable iron core Ί 8 Ί _c.

In a compressor equipped with such a control valve Ί 70, the spring constant of the spring Ί 75 is substantially reduced, so that the current value and setting for energizing the electromagnet Ί 85 are set as shown in Fig. 6. The suction pressure P s 0 has a negative proportional relationship, and the set suction pressure P s 0 changes to the low pressure side as the current value increases.

[Example 3]

In the control valve 2 70 shown in Fig. 7, a worm 2 8 2 is fixed to the rotating shaft of the servomotor 2 8 Ί controlled by the control means, and the worm 2 8 2 is engaged with the worm 2 8 2 and slid by the valve main body 7 Ί. It is equipped with a nut 2 8 3 that can move but is prevented from rotating, and is equipped with a spring 2 7 5 between the upper surface of this nut 2 8 3 and the lower surface of the diaphragm 7 2. be.

In a compressor equipped with this control valve 2 7 Q, the servomotor 2 8 1 rotates the rotation axis in response to the pulse emitted by the control means, so that the spring 2 8 3 is transmitted via the worm 2 8 2. Pushed up to change the effective spring constant of the spring 2 7 5 Can be done. Therefore, the compressor is capacitively controlled according to the pulse.

In each of the above embodiments, an electromagnet or a server motor was adopted as an electrically controlled mechanical urging means. For example, although not shown, a fluid pressure can be used by using a solenoid valve. _c

As described in detail above, according to the present invention, since the variable urging means changes the pressure control point by applying a variable load to the pressure sensitive means, in addition to the steady capacity control, the capacity is flexible. It can be transformed. Therefore, if this compressor is used in the air conditioner of a vehicle, a good feeling of acceleration can be obtained, and air conditioning can be performed in response to seasonal changes and changes in the outside environment. Can be fully satisfied.

Claims

Compensated claims

[Accepted by the International Bureau on September 30, 1991 (30.09.91); Claims 2 and 3 at the time of the visit were withdrawn; Claims 1, 4 and 6 were amended. Other claims remain unchanged. (Page 2)]

() A cylinder hook that houses a double-headed screw in multiple bores, a drive shaft arranged on an axis parallel to the bore, and a slider that is slidably fitted to the drive shaft. , A swash plate equipped with a guide pin that is pivotally supported by the slider and is engaged with the double-headed piston and fitted with a long hole drilled in the drive shaft, and the slider is rotatably supported. Control formed between the plunger and the housing by a pressure sensitive means that responds to suction pressure or discharge pressure, including a plunger that varies the tilt angle of the swash plate by axial displacement of the slider. In a swash plate type continuously variable capacitance type compressor equipped with a control valve that selectively introduces discharge pressure and suction pressure into the pressure chamber and changes the tilt angle of the swash plate via the plunger and the slider.

The control valve is disposed in the control pressure chamber, a valve chamber having a plurality of passages communicating with the discharge pressure and the suction pressure, and the valve chamber, connected to the pressure sensitive means, and the discharge. A control valve that transfers the valve seat agony formed in the opening of the passage that communicates with the pressure and suction pressure.

A swash plate type continuously variable capacitance compressor comprising a variable urging means for changing the pressure control point of the pressure sensitive means.

(2) (Delete>

(3>(Deleted>

(4) The pressure-sensitive means changes the pressure-sensitive part that drives the introduction pressure switching valve in the forward and reverse directions and the pressure control point according to the pressure fluctuation of either the suction pressure or the discharge pressure force. Claims consisting of means: Compressor according to paragraph L.

(5) The variable urging means is an electromagnetic device that changes the pressure control point by a magnetic force that changes with a change in electric current.

(6) The compressor according to item 1 of the range, wherein the variable urging means is a motor that changes the pressure control point by rotational drive.

Instructions based on Article 19 of the Convention

() In the attached amendment to the scope of claims, the amendment (underlined part) of claim Ί emphasizes the difference between the invention of the present application and the reference described in the international search report.

(2) The second and third claims are deleted by the amendment of the second claim. Therefore, the fourth claim is subordinate to the Ί claim.

(3) In the attached amendment to the scope of claims, the amendment (underlined part) of claim 6 amends the mistake in the type.

(4) Due to the amendment of claim Ί, it is necessary to insert the same wording as inserted in claim Ί after the statement "The control valve is" on the last line of page 4 of the specification. There is.

(5) Due to the amendment of the Iota claim, the same wording that was inserted in the Iota claim before the word "pressure sensitive means" is added to the fifth page and the third line of the specification. Need to enter.