KR102069600B1 - Variable swash plate compressor - Google Patents

Abstract

In the present invention, the variable swash plate type compressor is a cylinder block having a plurality of cylinder bores 110 formed radially with respect to the center bore 120 and the center bore 120 that are formed through the center to penetrate the drive shaft 400. (100), the piston 130 for compressing the refrigerant while reciprocating along the inner circumferential surface of each cylinder bore 110, and the front coupled to the front of the cylinder block 100 to form a crank chamber 210 therein A rear housing 300 having a suction chamber 310 and a discharge chamber 320 while being coupled to the housing 200, the rear of the cylinder block 100, and the cylinder block 100 and the rear housing 300. The rotor unit 500 is provided between the valve unit 800 and the drive shaft 400 in the crank chamber 210 and the rotor arm 510 is formed on one side thereof, and the inclination angle of the rotor 500 is variable. The swash plate 600 formed to be, and the rotor while being coupled to the swash plate 600 In the variable swash plate type compressor including a hub 700 having a hub arm 710 coupled by a 510 and a hinge pin 720, the rotor 500 is a part of the rotor arm 510. And a slot portion 520 formed through the rotor arm 510 so as to be inclined with respect to the driving shaft 400, wherein the slot portion 520 has a first side surface 523 of the slot portion 520. It relates to a variable swash plate compressor in which the curvature 524 is formed to be curved in the direction of the lower end 522 of the slot 520 in the upper end 521 of the slot 520.

Description

Variable swash plate compressor

The present invention relates to a variable swash plate compressor, and more particularly, a curvature is formed on the first side of the slot to bend from the upper end of the slot to the lower end of the slot, and the piston in a state where the inclination angle of the swash plate is minimized by the curvature. As the gap distance between the valve unit and the valve unit increases the gap distance between the piston and the valve unit in the state where the inclination angle of the swash plate is the maximum, the dead volume is minimized to increase the performance and efficiency of the compressor, and when the air conditioner is turned off, The present invention relates to a variable swash plate compressor capable of reducing hunting noise generated.

In general, a vehicle is provided with an air conditioning (A / C) for indoor air conditioning. Such an air conditioner includes a compressor as a configuration of a cooling system that compresses a low temperature low pressure gaseous refrigerant drawn from an evaporator into a high temperature high pressure gaseous refrigerant and sends it to a condenser.

The compressor has a reciprocating type for compressing the refrigerant by the reciprocating motion of the piston according to the compression method and a rotary type for performing the compression by the rotational motion. The reciprocating type includes a crank type for transferring to a plurality of pistons using a crank and a swash plate for transferring to a rotating shaft provided with a swash plate according to a transmission method of a driving source. Rotary types include rotary rotary shafts and vane rotary using vanes, rotary scrolling and scrolling using fixed scrolls.

Of the above-mentioned reciprocating compressors, the swash plate type compressor is configured to rotate the swash plate while the rotating shaft is rotated by the driving force of the engine, and to compress the refrigerant by causing the piston to reciprocate according to the rotation of the swash plate.

In general, the variable displacement swash plate type compressor refers to a compressor in which the swash plate is configured to change the inclination angle of the swash plate according to the compression capacity.

1 shows a cross-sectional view of a conventional variable swash plate compressor. A schematic configuration of a conventional variable swash plate compressor 1 will be described with reference to FIG. 1.

The appearance of the conventional variable swash plate compressor (1) is the front housing 20 that forms the crank chamber 21 and coupled to the front of the cylinder block 10 and the cylinder block 10 having a plurality of cylinder bores 11 and It is configured to include a rear housing 30 coupled to the rear of the cylinder block 10 and having a suction chamber 31 and a discharge chamber 32.

A center bore 12 is formed in the center of the cylinder block 10 through which the rear side portion of the drive shaft 40 is penetrated, and the cylinder bore 11 is formed through the center bore 12 in a radial position, respectively. . The cylinder block 10 forms part of the appearance and skeleton of the compressor 1. A center bore 12 is formed through the center of the cylinder block. The rotation shaft 40 is rotatably installed in the center bore 12. A plurality of cylinder bores 11 are formed around the center bore 12 to radially penetrate the cylinder block 10. In addition, the piston 13 is installed in the cylinder bore 11 so as to enable linear reciprocating motion, respectively.

Inside the crank chamber 21, a drive unit for reciprocating the piston 13 is provided.

The driving unit is coupled to the driving shaft 40 in the crank chamber 21 and the driving shaft 40 installed through the center of the front housing 20 and the cylinder block 10 and rotates together with the driving shaft 40. And the swash plate 60 which is rotatably coupled to the sleeve 41 and is coupled to the rotor 50 by a hinge pin 72 so that the inclination angle with respect to the rotor 50 is variable, and the rotor 50. 60 is configured to include a pressing spring 42 to elastically press the original position. The rotor 50 has a rotor arm 51 for hinge coupling with the swash plate 60, the rotor arm 51 has a slot 52 having a long hole shape, and the hub 70 at the swash plate 60. Is integrally combined. In addition, since the hub arm 71 hinged by the rotor arm 51 and the hinge pin 72 is formed on the hub 70, the swash plate 60 can be variably inclined with respect to the rotor 50. .

When the drive shaft 40 is rotated by the driving force of the engine transmitted through the pulley 90, the rotor 50 is also rotated together with the drive shaft 40, when the rotation of the rotor 50 is set in the crank chamber 21 The swash plate 60 is reciprocated along the longitudinal direction of the drive shaft 40 by the pressure and the elastic pressing action of the pressure spring 42, and rotates while the inclination angle of the swash plate 60 is changed. The rotation of 60 causes the piston 13 to linearly reciprocate in the cylinder bore 11, thereby compressing the refrigerant in the cylinder bore 11.

The compressed refrigerant is discharged to the discharge 32 of the rear housing 30 through the valve assembly 80 provided between the cylinder block 10 and the rear housing 30 and then discharged to the outside of the compressor.

As shown in FIG. 2, when the piston 13 reciprocates in the variable swash plate compressor, a dead volume exists due to the clearance gap between the piston 13 and the valve assembly 80.

Despite the piston reciprocating motion, uncompressed refrigerant exists in the dead volume, and this uncompressed refrigerant is discharged together with the compressed refrigerant into the discharge chamber, thereby causing a problem of reducing the performance of the compressor.

Conventional variable swash plate type compressor has a problem that the dead volume is increased by forming the slot of the rotor arm in a straight line so that the clearance gap between the piston and the valve assembly is the same when the inclination angle of the swash plate is maximum and minimum.

In addition, the conventional variable swash plate type compressor has a problem that hunting noise is generated by vibration of the driving unit when the air conditioning apparatus is turned off as the volume of the air conditioner increases.

Moreover, the conventional variable swash plate compressor has a problem that the performance of the compressor is reduced as the dead volume increases.

Republic of Korea Patent Publication No. 10-2011-0058017

The present invention is to solve the above problems, an object of the present invention is to form a curvature to be curved in the lower direction of the slot portion from the upper end of the slot portion on the first side of the slot portion, the inclination angle of the swash plate by the curvature portion is minimal As the gap distance between the piston and the valve unit in the state increases the gap distance between the piston and the valve unit in a state where the inclination angle of the swash plate is maximum, the hunting noise generated by the swing of the drive unit when the air conditioner is turned off is reduced. It is to provide a variable swash plate compressor that can increase the performance and efficiency of the compressor by minimizing the dead volume, and improve the reliability of the compressor.

In order to achieve the object of the present invention, the variable swash plate compressor according to the preferred embodiment of the present invention is radially based on the center bore 120 and the center bore 120 formed through the center so that the drive shaft 400 penetrates. A cylinder block 100 having a plurality of cylinder bores 110 formed therein, a piston 130 compressing the refrigerant while reciprocating along the inner circumferential surface of each cylinder bore 110, and in front of the cylinder block 100. A front housing 200 coupled to form a crank chamber 210 therein, a rear housing 300 coupled to the rear of the cylinder block 100 and having a suction chamber 310 and a discharge chamber 320; A rotor 500 having a rotor arm 510 formed at one side thereof while being coupled to the valve unit 800 installed between the cylinder block 100 and the rear housing 300 and the drive shaft 400 in the crank chamber 210. ), And the inclination angle with respect to the rotor 500 is variable To the variable swash plate type compressor comprising a swash plate 600, and a hub 700 is formed and coupled to the swash plate 600, the hub arm 710 is coupled by the rotor arm 510 and the hinge pin 720 The rotor 500 may include a slot 520 formed through a portion of the rotor arm 510 to penetrate the rotor arm 510 so as to be inclined with respect to the drive shaft 400. The curvature 524 is curved such that the first side surface 523 of the slot 520 is curved toward the lower end 522 of the slot 520 from the upper end 521 of the slot 520. It is characterized by being formed.

Further, in another preferred embodiment of the variable swash plate compressor of the present invention, the curvature portion 524 of the first side 523 of the slot portion 520 of the variable swash plate compressor has a minimum inclination angle of the swash plate 600. The gap distance PEC1 between the piston 130 and the valve unit 800 in the state is the gap distance PEC2 between the piston 130 and the valve unit 800 in a state where the inclination angle of the swash plate 600 is maximum. It may be formed to be larger than).

Further, in another preferred embodiment of the variable swash plate compressor of the present invention, the curvature portion 524 of the first side 523 of the slot portion 520 of the variable swash plate compressor has a minimum inclination angle of the swash plate 600. The gap distance PEC1 between the piston 130 and the valve unit 800 in the state is the gap distance PEC2 between the piston 130 and the valve unit 800 in a state where the inclination angle of the swash plate 600 is maximum. It may be formed to be larger than 0.2mm.

Further, in another preferred embodiment of the variable swash plate compressor of the present invention, the curvature portion 524 of the first side 523 of the slot portion 520 of the variable swash plate compressor has a maximum inclination angle of the swash plate 600. Hinge pin 720 in the state where the inclination angle of the straight portion 526 and the swash plate 600 of the first side of the existing slot portion is the maximum hinge pin 720 in the state that the inclination angle of the swash plate 600 is the minimum It may be formed to meet a virtual straight line 527 connecting the.

Further, in another preferred embodiment of the variable swash plate compressor of the present invention, the curvature portion 524 of the first side 523 of the slot portion 520 of the variable swash plate compressor has a maximum inclination angle of the swash plate 600. It may be formed so as to be tangent to the straight portion 526 of the first side of the existing slot portion in the state.

In the variable swash plate compressor according to the present invention, a curvature portion is formed to be bent from the upper end of the slot portion to the lower end of the slot portion on the first side of the slot portion, and the clearance distance between the piston and the valve unit in a state in which the inclination angle of the swash plate is minimized by the curvature portion. As the clearance distance between the piston and the valve unit is increased by a predetermined length in the state where the inclination angle of the swash plate is the maximum, there is an effect of reducing the dead volume.

In addition, the variable swash plate compressor according to the present invention has the effect of minimizing the dead volume to reduce the hunting noise caused by the shaking of the drive unit when the air conditioner off.

Moreover, the variable swash plate compressor according to the present invention has an effect of increasing the reliability of the compressor by improving the cooling performance and efficiency of the compressor as the dead volume is reduced.

1 shows a cross-sectional view of a conventional variable swash plate compressor.
2 is an enlarged view of a portion A of FIG. 1.
3 is a sectional view of a variable swash plate compressor according to the present invention.
Figure 4 shows a side view of the drive shaft coupled to the rotor in the variable swash plate compressor according to the present invention.
5 is a conceptual diagram illustrating the curvature of the curvature of the slot in the preferred embodiment of the present invention.
6 is a graph showing a change state of the gap distance between the piston and the valve unit when the inclination angle of the swash plate changes from the maximum inclination angle to the minimum inclination angle.
7 shows a partial cross-sectional view of the variable swash plate compressor in a state where the inclination angle of the swash plate is the minimum inclination angle.
8 is an enlarged view of a portion B of FIG. 7.
9 is a partial cross-sectional view of the variable swash plate compressor in a state where the inclination angle of the swash plate is the maximum inclination angle.
FIG. 10 is an enlarged view of portion C of FIG. 9.

Preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. First, in adding reference numerals to components of each drawing, the same components are designated by the same reference numerals.

3 shows a cross-sectional view of a variable swash plate compressor according to the present invention. Figure 4 shows a side view of the drive shaft coupled to the rotor in the variable swash plate compressor according to the present invention. 5 is a conceptual diagram illustrating the curvature of the curvature of the slot in the preferred embodiment of the present invention. 6 is a graph showing a change state of the gap distance between the piston and the valve unit when the inclination angle of the swash plate changes from the maximum inclination angle to the minimum inclination angle. 7 shows a partial cross-sectional view of the variable swash plate compressor in a state where the inclination angle of the swash plate is the minimum inclination angle. 8 is an enlarged view of a portion B of FIG. 7. 9 is a partial cross-sectional view of the variable swash plate compressor in a state where the inclination angle of the swash plate is the maximum inclination angle. FIG. 10 is an enlarged view of portion C of FIG. 9.

3 to 6, a variable swash plate compressor according to an embodiment of the present invention will be described.

As shown in FIG. 3, the variable swash plate compressor 1000 according to an embodiment of the present invention includes a cylinder block 100, a front housing 200, a rear housing 300, a rotor 500, and a swash plate 600. , A hub 700, and a valve unit 800.

The cylinder block 100 forms the exterior of the variable swash plate compressor 1000 together with the front housing 200 and the rear housing 300.

The center bore 120 is formed through the center of the cylinder block 100. The rear side portion of the drive shaft 400 is penetrated and supported by the center bore 120 so as to be rotatable through the pulley 900 by the power transmitted from the engine. A plurality of cylinder bores 110 are formed around the center bore 120 to radially penetrate the cylinder block 100. In addition, the piston 130 is installed inside the cylinder bore 110 to enable linear reciprocating motion, respectively. Preferably, the piston 130 is formed in a cylindrical shape, the cylinder bore 110 is formed radially around the center bore 120 in a cylindrical space to correspond to the shape of the piston 130. The piston 130 discharges the refrigerant sucked through the suction chamber 310 to the discharge chamber 320 while linearly reciprocating the inside of the cylinder bore 110.

The front housing 200 is installed at one end of the cylinder block 100. The front housing 20 is recessed to face the cylinder block 100 to form a crank chamber 210 therein together with the cylinder block 100. The crank chamber 210 is kept airtight with the outside.

The pulley 900 is installed on one side of the front housing 200. The pulley 900 receives the driving force of the engine to rotate the drive shaft 400.

The rear housing 300 is installed to face the front housing 200 at the other end of the cylinder block 100, that is, the cylinder block 100. In the rear housing 300, a suction chamber 310 is formed inside by a circular partition wall formed therein. The suction chamber 310 serves to deliver the refrigerant to be compressed into the cylinder bore 110. In addition, the discharge chamber 320 is formed outside the rear housing 300 by a circular partition wall formed therein. The discharge chamber 320 temporarily stores the compressed refrigerant before discharging it to the outside of the variable swash plate compressor.

Inside the crank chamber 210, a drive unit for reciprocating the piston 130 is installed.

The driving unit is coupled to the driving shaft 400 in the driving shaft 400 and the crank chamber 210 installed through the center of the front housing 200 and the cylinder block 100 and rotates together with the driving shaft 400. And the swash plate 600 which is rotatably coupled to the sleeve 410 and is coupled to the rotor 500 by a hinge pin 720 so that the inclination angle of the rotor 500 is variable, and the rotor 500. It is configured to include a restoring spring 420 to elastically press the 600 to the original position.

The rotor 500 is installed in a substantially disk shape, and the rotor 500 has a rotor arm 510 for hinge coupling with the swash plate 600. The rotor arm 510 protrudes from a surface facing the swash plate 600 of the outer wall surface of the disc-shaped rotor 500. A portion of the rotor arm 510 passes through the rotor arm 510 so as to be inclined with respect to the driving shaft, and a slot 520 is formed.

 Hub 700 is integrally coupled to the swash plate 600. It is coupled to the hub 700 in a form surrounding the outer circumferential surface of the hub 700 of the swash plate 600. In addition, the hub arm 710 is formed on one side of the hub 700 so as to protrude on one side of the hub 700 such as the rotor arm 510 to couple the hub 700 to the rotor 500. The hub arm 710 is connected to the rotor arm 510 while the hinge pin 720 is fastened through the slot part 520. By forming the hub arm 710 hinged to the rotor arm 510 by the hinge pin 720, the swash plate 600 can be variably inclined with respect to the rotor 500. That is, the swash plate 600 is to change the inclination angle of the swash plate 600 while the hinge pin 720 moves up and down along the slot portion 520.

When the drive shaft 400 is rotated by the driving force of the engine received through the pulley 900, the rotor 500 is also rotated with the drive shaft 400, when the rotation of the rotor 500 is set in the crank chamber 210 The swash plate 600 reciprocates along the longitudinal direction of the drive shaft 400 by the pressure and the elastic pressing action of the restoring spring 420 and rotates while the inclination angle of the swash plate 600 changes. As such, the piston 130 compresses the refrigerant in the cylinder bore 110 while the piston 130 linearly reciprocates in the cylinder bore 110 due to the rotation of the swash plate 600 whose inclination angle is changed.

The valve unit 800 is installed between the cylinder block 100 and the rear housing 300. The refrigerant compressed by the reciprocating motion of the piston 130 in the cylinder bore 110 is discharged to the discharge chamber 320 of the rear housing 30 through the valve unit 800 and then discharged to the outside of the compressor.

As shown in FIG. 4, the slot portion 520 of the surface rotor 500 according to the exemplary embodiment of the present invention has a first side 523 and a second side with respect to the top 521 and the bottom 522. It is formed through a portion of the rotor arm 510 of the rotor 500 in the form of a long hole to form the 525. The first side surface 523 of the slot part 520 has a curvature part 524 formed to be bent from the upper end 521 of the slot part 520 toward the lower end 522 of the slot part 520. The second side surface 525 of the 520 is formed to form a straight line from the upper end 521 of the slot portion 520 toward the lower end 522 of the slot portion 520.

5 to 10, according to another exemplary embodiment of the present invention, the curvature 524 of the first side surface 523 of the slot 520 has a minimum inclination angle of the swash plate 600. In the gap distance (PEC1) between the piston 130 and the valve unit 800 is formed to be larger than the gap distance (PEC2) between the piston 130 and the valve unit 800 in the state that the inclination angle of the swash plate 600 is the maximum. .

Hereinafter, the existing slot portion means that the slot portion has a state in which the clearance between the piston and the valve unit is the same in a state where the inclination angle of the swash plate is the maximum and the inclination angle of the swash plate is minimum. That is, the first side surface and the second side surface of the slot part mean a state formed in a straight line parallel to each other on the basis of the upper end and the lower end.

As shown in FIG. 6, the curvature 524 of the first side 523 of the slot 520 has a minimum inclination angle of the swash plate 600 in order to reduce the dead volume according to the formation of the curvature 524. In the gap distance (PEC1) between the piston 130 and the valve unit 800 is 0.2mm or more than the gap distance (PEC2) between the piston 130 and the valve unit 800 in the state that the inclination angle of the swash plate 600 is the maximum It is preferable that it is formed to be large. Piston 130 in the state where the inclination angle of the swash plate 600 is the maximum clearance distance (PEC1) between the piston 130 and the valve unit 800 in the state that the curvature 524 is the minimum inclination angle of the swash plate 600 This is because when the gap distance between the valve unit 800 and the valve unit 800 is less than 0.2 mm, the inclination angle of the swash plate is the same as that of the existing slot portion, so that there is no difference in the volume in the state of the maximum and minimum.

As shown in FIG. 5, according to another embodiment of the present invention, the curvature 524 of the first side surface 523 of the slot 520 is the existing slot in the state where the inclination angle of the swash plate 600 is the maximum. Virtual connecting the hinge pins 720 and the hinge pins 720 in a state where the inclination angles of the swash plate 600 are the minimum while the inclination angles of the straight portion 526 and the swash plate 600 of the first side of the negative part are maximum. It is formed to meet the straight line 527. At this time, the curvature 524 of the first side surface 523 of the slot portion 520 is formed to be tangent to the straight portion 526 of the first side of the existing slot portion in the state that the inclination angle of the swash plate 600 is the maximum. It is desirable to be.

As shown in FIGS. 5 and 6, the curvature 524 of the first side surface 523 of the slot 520 has the piston 130 and the valve unit 800 in a state where the inclination angle of the swash plate 600 is minimum. The clearance distance PEC1 is greater than 0.2 mm greater than the clearance distance PEC2 between the piston 130 and the valve unit 800 in a state where the inclination angle of the swash plate 600 is maximum, and the inclination angle of the swash plate 600 is maximum. In the state that the inclination angle of the straight portion 526 and the swash plate 600 of the first side of the existing slot portion is the maximum the hinge pin 720 and the hinge pin 720 in the state that the inclination angle of the swash plate 600 is the minimum When the inclination angle of the swash plate meets the imaginary straight line 527 to be connected to each other and is formed to be tangent to the straight portion 526 of the first side of the existing slot part, the inclination angle of the swash plate is in a state where the inclination angle of the swash plate is maximum. Changing to the minimum state, the gap distance between the piston and the valve unit is changed, thereby reducing the dead volume Done.

It is possible to increase the reliability of the compressor by reducing hunting noise generated by shaking of the drive unit when the air conditioner is turned off due to the reduction of the dead volume and improving the cooling performance and efficiency of the compressor.

The invention is not limited to the embodiments shown in the figures and the embodiments described above, but may be extended to other embodiments falling within the scope of the appended claims.

1: compressor, 10: cylinder block,
11: cylinder bore, 12: center bore,
13: piston, 20: front housing,
21: crankcase, 30: rear housing,
31: suction chamber, 32: discharge chamber,
40: drive shaft, 41: sleeve,
42: pressurized spring, 50: rotor
51: rotor arm, 52: slot,
60: swash plate, 70: hub
71: hub arm, 72: hinge pin,
80: valve assembly, 90: pulley
100: cylinder block, 110: cylinder bore,
120: center bore, 130: piston,
200: front housing, 210: crankcase,
300: rear housing, 310: suction chamber,
320: discharge chamber, 400: drive shaft,
410: sleeve, 420: restoring spring,
500: rotor, 510: rotor arm,
520: slot portion, 521: top,
522: bottom, 523: first side,
524: curvature portion, 525: the second side,
526: a straight portion of the first side of the existing slot portion,
527: straight portion,
528: straight
600: swash plate,
700: herb, 710: herb arm,
720: hinge pin, 800: valve unit,
900: pulley, 1000: variable swash plate compressor,
PEC1: clearance between piston and valve unit with minimum inclination angle of swash plate,
PEC2: Clearance distance between the piston and the valve unit when the inclination angle of the swash plate is maximum.

Claims (5)

Center bore 120 is formed through the center to penetrate the drive shaft 400 and the cylinder block 100 is formed with a plurality of cylinder bores 110 radially with respect to the center bore 120, and each cylinder Piston 130 for compressing the refrigerant while reciprocating along the inner circumferential surface of the bore 110, the front housing 200 is coupled to the front of the cylinder block 100 to form a crank chamber 210 therein, and the cylinder A rear housing 300 coupled to the rear of the block 100 and having a suction chamber 310 and a discharge chamber 320, and a valve unit 800 installed between the cylinder block 100 and the rear housing 300. And, the rotor 500 is coupled to the drive shaft 400 in the crank chamber 210, the rotor arm 510 is formed on one side, the swash plate 600 formed to vary the inclination angle with respect to the rotor 500, and While coupled to the swash plate 600 is coupled by the rotor arm 510 and the hinge pin 720 In the variable swash plate compressor comprising a hub 700 is formed hub hub 710,
The rotor 500 includes a slot portion 520 formed through the rotor arm 510 so as to be inclined with respect to the drive shaft 400 on a portion of the rotor arm 510,
The slot portion 520,
A first side surface 523 formed on the opposite side of the valve unit 800 and a second side surface 525 formed on the valve unit 800 side;
The first side surface 523 has a curvature portion 524 is formed to be curved in the direction of the lower end 522 of the slot portion 520 from the upper end 521 of the slot portion 520 is
The curvature 524,
The clearance distance PEC1 between the piston 130 and the valve unit 800 in the state where the inclination angle of the swash plate 600 is minimum is the piston 130 and the inclined angle of the swash plate 600 in the maximum state. Is formed to be larger than the gap distance (PEC2) between the valve unit 800,
A virtual straight line 527 connecting the hinge pins 720 and the hinge pins 720 in a state where the inclination angle of the swash plate 600 is the minimum while the inclination angle of the swash plate 600 is the maximum.
Variable swash plate type compressor, characterized in that formed between the tangential straight line portion 526 when the inclination angle of the swash plate 600 is the maximum.
delete The method of claim 1,
The curvature 524 of the first side surface 523 of the slot 520,
The clearance distance PEC1 between the piston 130 and the valve unit 800 in a state where the inclination angle of the swash plate 600 is minimum is the inclination angle of the swash plate 600 in the maximum state. Variable swash plate compressor characterized in that formed to be greater than 0.2mm greater than the gap distance (PEC2) between the valve unit (800).
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