KR101456714B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate type compressor. In the present invention, the rotor 144 is installed to rotate together with the driving shaft 140 which is rotated by receiving external driving force. The swash plate 148 is hinged to the rotor 144, the angle of which varies depending on the discharge capacity. A hinge arm 146 having a hinge slot 147 is formed on either the rotor 144 or the swash plate 148 for the hinge coupling. A connecting arm 152 connected to the hinge arm 146 is formed on the swash plate 148 or the rotor 144 opposite to the rotor 144 or the swash plate 148 on which the hinge arm 146 is formed . A hinge pin 154 is provided at the tip of the connection arm 152 and a coupling hole 147 'is formed at the other side of the hinge arm 146 opposite to the position where the hinge slot 147 is formed. Inside the engagement hole 147 ', a spring fixing member 160 having a return spring S is installed. According to the present invention having the above-described structure, since the spring fixing member 160 having the return spring S exerting an elastic force in the direction of increasing the inclination angle of the swash plate 148 toward the hinge pin 154 is provided, The swash plate 148 can always maintain the minimum inclination angle without consuming the power of the external driving source.

Swash plate compressor, swash plate, variable capacity, spring

Description

[0001] The present invention relates to a variable displacement swash plate type compressor,

BACKGROUND OF THE INVENTION 1. Field of the Invention [0002] The present invention relates to a variable displacement swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor in which a displacement amount varies depending on a load.

FIG. 1 is a partial cross-sectional view of an internal structure of a variable capacity swash plate type compressor according to the prior art.

As shown in the drawing, the center bore 11 is formed through the center of the cylinder 10. A plurality of cylinder bores 13 are formed through the cylinder 10 radially surrounding the center bore 11. A piston (15) is movably installed in the cylinder bore (13). The piston 15 has a cylindrical shape, and the cylinder bore 13 has a cylindrical shape corresponding thereto. A connecting portion 17 is formed at one end of the piston 15, that is, at a portion protruding outward from the cylinder bore 13. The piston 15 compresses the refrigerant in the cylinder bore 13.

A front housing (20) is installed at one end of the cylinder (10). The front housing 20 cooperates with the cylinder 10 to form a crank chamber 21 therein. The crankcase 21 is kept airtight with the outside. A shaft hole (23) is formed through the front housing (20).

A rear housing 30 is provided at the other end of the cylinder 10, that is, opposite to the front housing 20. A suction chamber (not shown) is formed in the rear housing 30 to selectively communicate with the cylinder bore 13. The suction chamber is formed in a region of the rear housing 30 corresponding to the center of the surface facing the cylinder 10. The suction chamber serves to transfer the refrigerant to be compressed into the cylinder bore 13 .

A discharge chamber (33) is formed in the rear housing (30). The discharge chamber (33) is also selectively communicated with the cylinder bore (13). The discharge chamber (33) is formed at a position adjacent to the edge of the rear housing (30) facing the cylinder (10). The discharge chamber (33) is a place where refrigerant compressed in the cylinder bore (13) is discharged and temporarily stays. A control valve (not shown) is provided at one side of the rear housing 30. The control valve is a configuration for adjusting the angle of the swash plate 48, which will be described below.

The bolts 37 are fastened through the cylinder 10, the front housing 20, and the rear housing 30 to each other. A plurality of bolts 37 pass through the edges of the cylinder 10, the front housing 20, and the rear housing 30 at the same time.

A drive shaft 40 is installed to be rotatable through the center bore 11 of the cylinder 10 and the shaft hole 23 of the front housing 20. The driving shaft 40 is rotated by the driving force transmitted from the engine. The drive shaft 40 is rotatably supported by the cylinder 10 and the front housing 20 by means of bearings 42.

A rotor 44 is provided in the crank chamber 21 so that the drive shaft 40 passes through the center and is integrally rotated with the drive shaft 40. The rotor 44 is fixed to the drive shaft 40 in a substantially disc shape. A hinge arm (46) protrudes from a surface of the rotor (44).

A swash plate (48) is hingedly coupled to the rotor (44) to rotate together with the drive shaft (40). The swash plate 48 is installed at a variable angle with respect to the drive shaft 40 according to the discharge capacity of the compressor. That is, the driving shaft 40 is perpendicular to the longitudinal direction of the driving shaft 40 or inclined at a predetermined angle with respect to the driving shaft 40. The swash plate 48 has its edge connected to the pistons 15 via a shoe 50. That is, the edge of the swash plate 48 is connected to the connecting portion 17 of the piston 15 through the shoe 50 so that the piston 15 is rotated in the cylinder bore 13 by the rotation of the swash plate 48 Make a linear reciprocating motion.

A connecting arm 52 connected to the hinge arm 46 of the rotor 44 protrudes from the swash plate 48. A hinge pin 54 is provided at the tip of the connecting arm 52 in a direction perpendicular to the longitudinal direction of the connecting arm 52. The hinge pin 54 is connected to the hinge arm 46 of the rotor 44 And is movably engaged with the slot 47 formed at the tip.

A semi-inclined spring 56 is provided to exert an elastic force between the rotor 44 and the swash plate 48. The anti-tilt spring 56 is installed around the outer surface of the drive shaft 40 and exerts an elastic force in a direction in which the inclination angle of the swash plate 48 is reduced.

A swab stopper (not shown) protrudes from a surface of the swash plate 48. The swash plate stopper (not shown) is formed on a surface facing the rotor 44 and is provided on the opposite side of the connecting arm 52 with respect to the driving shaft 40. The swash plate stopper (not shown) regulates a degree of inclination of the swash plate 48 with respect to the driving shaft 40.

An axial stopper (60) is provided at one end of the drive shaft (40). The shaft stopper 60 is provided around the outer surface of the drive shaft 40 and functions to regulate the mounting position of the swash plate 48 when the swash plate 48 is set in a direction orthogonal to the longitudinal direction of the drive shaft 40 .

A valve assembly 70 is provided between the cylinder 10 and the rear housing 30 for controlling the flow of the refrigerant between the suction chamber and the discharge chamber 33 and the cylinder bore 13. That is, the valve assembly 70 controls the refrigerant flow from the suction chamber to the cylinder bore 13 and from the cylinder bore 13 to the discharge chamber 33.

The operation of the variable displacement swash plate type compressor having such a structure will be described. The swash plate 48 is rotated together with the driving shaft 40 as the driving shaft 40 rotates by the driving force transmitted from the outside. When the swash plate 48 rotates, the piston 15, to which the connecting portion 17 is connected, linearly reciprocates in the cylinder bore 13 with the shoe 50 interposed at the edge of the swash plate 48. The refrigerant is compressed in the cylinder bore (13) by the linear reciprocating motion of the piston (15). When the refrigerant is transferred to the cylinder bore 13, the piston 15 of the corresponding cylinder bore 13 moves in the direction of the valve assembly 70 and compression of the refrigerant occurs.

Thus, when the refrigerant is compressed in the cylinder bore 13, the pressure inside the cylinder bore 13 becomes relatively high, and the refrigerant is transferred to the discharge chamber 33. In this state, when the inclination angle of the swash plate 48 is varied by the control valve, the amount of the refrigerant compressed in the cylinder bore 13 varies, so that the discharge amount of the refrigerant is varied.

However, the conventional variable capacity swash plate type compressor as described above has the following problems.

The angle of the swash plate 48 is controlled by the control valve so that when the refrigerant in the discharge chamber 33 is transferred to the crank chamber 21 through the control valve, The angle of the swash plate 48 is adjusted. That is, the swash plate 48 is erected perpendicularly to the drive shaft 40, so that the moving stroke of the piston 15 is shortened, and the discharge capacity of the refrigerant is reduced.

When the pressure of the crank chamber 21 is relatively lowered by the control valve, the swash plate 48 is inclined at a predetermined angle with respect to the drive shaft 40, The stroke becomes long and the discharge capacity of the refrigerant increases.

In order to return the swash plate 48 to the state having the minimum inclination angle (the state shown in FIG. 1) at the maximum inclination angle, when the pressure of the crank chamber 21 is lowered, It is necessary to perform the inclination toward the maximum inclination angle from the maximum inclination angle.

However, in the compressor, when the minimum inclination angle is set to about 0 deg., The compression operation is not practically performed, and since the discharge reaction force can not be obtained, the angle of the swash plate 48 can not be restored. In order to solve such a problem, the minimum inclination angle of the swash plate 48 is set to about 3 to 5 degrees. Thus, even when the swash plate 48 has a minimum inclination angle, the compression operation of the compressor is slightly maintained, so that the discharge reaction force can be used for returning the swash plate 48 to the angle.

However, even if the inclination angle of the swash plate 48 is adjusted to the minimum inclination angle, the compressor continues the compression operation at the minimum discharge capacity so that the discharge reaction force always acts on the swash plate 48, There is a problem of consuming inama.

Therefore, in order to reduce the consumption of the power at the minimum discharge capacity and to return the angle of the swash plate 48 by the discharge reaction force, the minimum discharge capacity (the minimum inclination angle of the swash plate ) Needs to be highly precisely adjusted.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a variable displacement swash plate type compressor in which a return spring is further provided to maintain the swash plate at a minimum inclination angle.

According to an aspect of the present invention, there is provided a driving apparatus comprising: a driving shaft rotatably receiving an external driving force; A rotor installed to rotate together with the drive shaft; A swash plate hinged to the rotor and having an angle varying according to a discharge capacity; A hinge arm formed to protrude from one of the rotor and the swash plate for hinge connection and formed with a hinge slot; and a hinge arm protruding from the swash plate or the rotor opposite to the rotor or swash plate having the hinge arm, And a connecting arm connected to the arm, wherein a hinge pin is provided at a tip of the connecting arm in a direction perpendicular to the longitudinal direction of the connecting arm, and the hinge slot is formed And a return spring is provided on the inside of the engaging hole so that the return spring can return to the hinge pin when the inclination angle of the swash plate is increased toward the hinge pin Direction.

The outer circumferential surface of the spring fixing member and the inner surface of the coupling hole of the hinge arm are formed with threaded portions and coupled to each other.

The return spring exerts an elastic force of 5N to 150N.

The hinge arm of the rotor connected to the connecting arm of the swash plate is provided with the spring fastener having the connecting arm of the swash plate and the return spring exerting an elastic force toward the hinge pin movably movably in the hinge arm of the rotor, The swash plate is elastically supported in a direction opposite to the elastic force of the semi-slant spring. Therefore, the swash plate can always maintain the minimum inclination angle without consuming the power of the external driving source, and the capacity can be easily changed at the minimum capacity, thereby improving the performance of the compressor.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of a variable displacement swash plate compressor according to the present invention will be described in detail with reference to the accompanying drawings.

FIG. 2 is a cross-sectional view of a preferred embodiment of a variable displacement swash plate type compressor according to the present invention, and FIG. 3 is a perspective view showing the structure of a spring fixing member constituting an embodiment of the present invention.

As shown in these drawings, the appearance and skeleton of the compressor 100 are formed by the cylinder 110. A center bore 111 is formed through the center of the cylinder 110. The center bore 111 is a portion in which the drive shaft 140, which will be described below, is rotatably installed.

A plurality of cylinder bores 113 are formed to penetrate the cylinder 110 radially around the center bore 111. A piston (115) is installed in the cylinder bore (113) so as to reciprocate linearly. The piston 115 has a cylindrical shape, and the cylinder bore 113 has a cylindrical shape corresponding thereto. A connecting portion 117 is formed at one end of the piston 115, that is, a portion protruding outward from the cylinder bore 113. The piston 115 is linearly reciprocated in the cylinder bore 113 to compress the refrigerant.

A front housing 120 is installed at one end of the cylinder 110. The front housing 120 is inserted into a side facing the cylinder 110 to form a crank chamber 121 in cooperation with the cylinder 110. The crank chamber 121 is kept airtight with the outside.

A pulley shaft portion 122 ', on which a pulley 122 is rotatably mounted to receive rotation of the engine, is protruded from the front housing 120 opposite to the cylinder 110. An axial hole 123 is formed through the center of the pulley shaft portion 122 'to penetrate the front housing 120 forward and backward to the crank chamber 121. One end of the drive shaft 140 is rotatably supported by the shaft hole 123.

A rear housing 130 is installed at the other end of the cylinder 110, that is, opposite to the front housing 120. A suction chamber (not shown) is formed in the rear housing 130 to selectively communicate with the cylinder bores 113. The suction chamber is formed in a region of the rear housing 130 corresponding to the center of the surface facing the cylinder 110. The suction chamber serves to transmit a working fluid to be compressed into the cylinder bore 113.

A discharge chamber 133 is formed in the rear housing 130. The discharge chamber 133 also communicates with the cylinder bore 113 selectively. The discharge chamber 133 is formed along the edge of the rear housing 130 facing the cylinder 110. The discharge chamber 133 is a place where the working fluid compressed by the cylinder bore 113 is discharged and temporarily stays. A control valve (not shown) is provided at one side of the rear housing 130. The control valve is a configuration for adjusting the angle of the swash plate 148, which will be described below.

A bolt 137 is fastened through the cylinder 110, the front housing 120, and the rear housing 130 to each other. A plurality of bolts 137 pass through the edges of the cylinder 110, the front housing 120, and the rear housing 130 to perform a tightening action.

A drive shaft 140 is installed to be rotatable through the center bore 111 of the cylinder 110 and the shaft hole 123 of the front housing 120. The driving shaft 140 is rotated by the driving force transmitted from the engine. The driving shaft 140 is rotatably supported by the cylinder 110 and the front housing 120 by a bearing 142.

A rotor 144 is installed in the crank chamber 121 so that the drive shaft 140 passes through the center and is integrally rotated with the drive shaft 140. The rotor 144 is fixed to the drive shaft 140 in a substantially disc shape.

A hinge arm 146 protrudes from a surface of the rotor 144. A hinge slot 147 is formed in the hinge arm 146. The hinge slot 147 is open at one end to one side edge of the hinge arm 146. [ The hinge slot 147 is a portion into which the hinge pin 154 to be described below is inserted.

An engaging hole 147 'is formed in the other side of the hinge arm 146 opposite to the direction in which the hinge slot 147 is opened. One side of the engagement hole 147 'is shielded by the hinge pin 154 and the other side is opened to the edge of the hinge arm 146. The engagement hole 147 'is a portion into which the spring fixing member 160 to be described below is inserted. The inner diameter of the engagement hole 147 'is formed to be slightly smaller than the outer diameter of the spring fixing hole 160. This is to prevent the spring fixing member 160 from being separated from the engaging hole 147 'by an external force in a state where the spring fixing member 160 is inserted into the engaging hole 147'.

A swash plate 148 is hingedly coupled to the rotor 144 to rotate together with the drive shaft 140. The swash plate 148 is installed to vary the angle of the driving shaft 140 so that the swash plate 148 is positioned between the driving shaft 140 and the driving shaft 140 at a predetermined angle. do. The swash plate 148 has its edge connected to the pistons 115 through a shoe 150. That is, the edge of the swash plate 148 is connected to the connecting portion 117 of the piston 115 through the shoe 150 so that the piston 115 is rotated in the cylinder bore 113 by the rotation of the swash plate 148 Make a linear reciprocating motion.

A connecting arm 152 connected to the hinge arm 146 of the rotor 144 protrudes from the swash plate 148. A hinge pin 154 is provided at the tip of the connecting arm 152 in a direction perpendicular to the longitudinal direction of the connecting arm 152. The hinge pin 154 is connected to the hinge arm 146 of the rotor 144, And is hinged to the hinge slot 147 formed in the hinge slot.

The engagement hole 147 'is provided with a spring fixture 160. The spring fixture 160 is installed with a return spring S to be described below and is engaged with the engagement hole 147 '. 3, the spring fixing member 160 includes a fixing portion 161 and a shielding portion 162. The shielding portion 162 is relatively in contact with the outer diameter of the fixing portion 161 It has a large dimension.

The fixing portion 161 is formed in a substantially cylindrical shape and is inserted into the engaging hole 147 '. The outer diameter of the fixing portion 161 is formed to be slightly larger than the inner diameter of the coupling hole 147 'so that the outer surface thereof is in close contact with the inner surface of the coupling hole 147'.

An insertion space 161 'in which a return spring S is installed is formed inside the fixing portion 161. [ A guide protrusion 163 protrudes from the bottom surface of the insertion space 161 '. The guide protrusion 163 serves to guide the return spring S in a direction in which it is elastically deformed.

The shielding portion 162 is formed orthogonally from the fixing portion 161. The shielding portion 162 may be formed in the coupling hole 147 'of the hinge arm 146 corresponding to the entrance of the coupling hole 147' so that the spring fixing hole 160 is not excessively inserted into the coupling hole 147 ' 147 ').

A return spring S is installed in the insertion space 161 'of the spring fixing member 160. The return spring S is installed so as to surround the outer surface of the guide protrusion 163 of the spring fixture 160. The return spring S exerts an elastic force to push the hinge pin 154 toward the front housing 120. That is, the swash plate 148 connected to the hinge pin 154 exerts an elastic force to push the swash plate 148 toward the front housing 120. In other words, the swash plate 148 exerts an elastic force in a direction in which the inclination angle of the swash plate 148 increases, so that the minimum inclination angle of the swash plate 148 is approximately 0 degrees.

The return spring is a cylindrical coil spring. It is preferable that the return spring S exerts an elastic force of 5N to 150N. When the elastic force is less than 5N, it is difficult to exert an elastic force in a direction in which the inclination angle of the swash plate 148 is increased. When the elastic force is more than 150N, the elastic force of the anti- This is because it is difficult to maintain the inclination angle of the swash plate 148 because it exerts a greater force.

A semi-inclined spring 170 is installed to exert an elastic force between the rotor 144 and the swash plate 148. The antireflection spring 170 is installed to surround the outer surface of the drive shaft 140 and exerts an elastic force in a direction in which the inclination angle of the swash plate 148 is reduced.

An axial stopper 172 is provided at one end of the driving shaft 140. The shaft stopper 172 is provided around the outer surface of the drive shaft 140 and regulates its installation position when the swash plate 148 is erected in a direction orthogonal to the longitudinal direction of the drive shaft 140 do.

A washer 175 is installed at one end of the driving shaft 140 positioned at the center bore 111 of the cylinder 110. A shaft elastic member 177 is supported on the washer 175. The shaft elastic member 177 exerts an elastic force to push the driving shaft 140 toward the front housing 120 by a cylindrical coil spring so as to prevent the driving shaft 140 from being pushed toward the rear housing 130 And supports the drive shaft 140 at the same time.

A valve assembly 180 is provided between the cylinder 110 and the rear housing 130 to control the flow of refrigerant between the suction chamber and the discharge chamber 133 and the cylinder bore 113. That is, the valve assembly 180 controls the refrigerant flow from the suction chamber to the cylinder bore 113 and from the cylinder bore 113 to the discharge chamber 133.

Hereinafter, the operation of the variable displacement swash plate type compressor according to the present invention will be described in detail.

The compressor 100 of the present invention is rotated by receiving a driving force transmitted from an engine. When the driving shaft 140 is rotated, the rotor 144 rotates together. The rotation of the rotor 144 produces rotation of the swash plate 148 connected to the hinge arm 146 and the connecting arm 152.

When the swash plate 148 rotates, the piston 115 connected to the connecting portion 117 is reciprocated linearly in the cylinder bore 113 with the shoe 150 interposed at the edge of the swash plate 148. The refrigerant is compressed in the cylinder bore (113) by the linear reciprocating motion of the piston (115). The refrigerant in the suction chamber is sucked into the cylinder bore 113 under the control of the valve assembly 180. The refrigerant compressed in the cylinder bore 113 is discharged to the discharge chamber 133 under the control of the valve assembly 180 and is delivered to the outside of the compressor 100.

On the other hand, the angle of the swash plate 148 is controlled by the control valve. When the refrigerant in the discharge chamber 133 is transferred to the crank chamber 121 through the control valve, the pressure of the crank chamber 121 is adjusted to the angle of the swash plate 148. That is, the swash plate 148 is erected perpendicularly to the drive shaft 140, so that the moving stroke of the piston 115 is shortened, and the discharge capacity is reduced.

When the pressure of the crank chamber 121 is relatively lowered by the control valve, the swash plate 148 is inclined at a predetermined angle with respect to the driving shaft 140, The stroke becomes longer, and the discharge capacity increases.

In this state, the anti-tilt spring 170 is maximally extended in the longitudinal direction in a state where the swash plate 148 has the minimum inclination angle (the state shown in FIG. 2). At this time, since the return spring S exerts an elastic force toward the hinge pin 154, the swash plate 48 has a minimum inclination angle of approximately 0 degrees.

In this state, when the swash plate 148 begins to be inclined, the swash plate 148 is compressed in the longitudinal direction by the swash plate 148. At this time, since the swash plate 148 maintains a certain minimum inclination angle, the swash plate 148 can be inclined smoothly with respect to the driving shaft 140.

When the inclined angle of the swash plate 148 gradually increases as the semi-inclined spring 170 is compressed, the swash plate 148 has the maximum inclination angle.

In this state, when the refrigerant is compressed in the cylinder bore 113, the pressure inside the cylinder bore 113 becomes relatively high, and the refrigerant is delivered to the discharge chamber 133.

It is to be understood that the scope of the present invention is defined by the appended claims rather than by the foregoing description and that various changes and modifications may be made without departing from the spirit and scope of the invention as defined by the appended claims. It is self-evident.

In the illustrated embodiment, the spring fixture 160 is coupled in an interference fit to the engagement hole 147 'of the hinge arm 146, but is not necessarily limited thereto. For example, the spring fixing member 160 may be fixed by forming threads on the outer circumferential surface of the spring fixing member 160 and the inner surface of the fitting hole 147 'of the hinge arm 146, respectively.

The spring fixture 160 may be fixed to the hinge arm 146 by, for example, riveting the spring fixture 160 on the engagement hole 147 'of the hinge arm 146. [

The spring fixture 160 may be fixed to the hinge arm 146 by welding while the spring fixture 160 is inserted into the engagement hole 147 'of the hinge arm 146.

In the illustrated embodiment, the hinge arm 146 protrudes from one surface of the rotor 144, and the connecting arm 152 protrudes from the swash plate 148, but the present invention is not limited thereto. For example, the connecting arm 152 may protrude from one surface of the rotor 144, and the hinge arm 146 may protrude from the swash plate 148.

An auxiliary return spring 174 may be additionally provided between the swash plate 148 and the shaft stopper 172.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial cross-sectional view showing an internal configuration of a variable capacity swash plate type compressor according to the prior art; FIG.

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a variable displacement swash plate type compressor.

3 is a perspective view showing a structure of a spring fixing member constituting an embodiment of the present invention.

Description of the Related Art [0002]

100: compressor 110: cylinder

111: center bore 113: cylinder bore

115: piston 117:

120: front housing 121: crank chamber

122: pulley 122 ': pulley shaft

123: shaft hole 130: rear housing

133: Discharge chamber 137: Bolt

140: drive shaft 142: bearing

144: Rotor 146: Hinge arm

147: Hinge slot 147 ': Coupling hole

148: swash plate 152: connecting arm

154: hinge pin 160: spring retainer

161: Fixing portion 161 ': Insertion space

162: shielding portion 163: guide projection

170: Semi inclined spring 172: Axial stopper

175: Washer 177: Axial elastic member

180: valve assembly S: return spring

Claims (3)

A front housing 120 and a rear housing 130; A driving shaft 140 provided in an inner space formed by the front housing 120 and the rear housing 130 to rotate by receiving an external driving force; A rotor 144 installed to rotate together with the driving shaft 140; A swash plate hinge-coupled to the rotor 144 and having an angle varying according to a discharge capacity; And A hinge arm 146 protruding from one of the rotor 144 and the swash plate 148 to form a hinge slot 147 for the hinge coupling and the hinge arm 146 formed with the hinge arm 146, And a connection arm 152 protruding from the swash plate 148 or the rotor 144 opposite to the rotor 144 or the swash plate 148 and connected to the hinge arm 146. [ In a capacitive swash plate type compressor, The compressor includes a semi-inclined spring 170 that exerts an elastic force between the rotor 144 and the swash plate 148 in a direction in which the inclination angle of the swash plate 148 is reduced. A hinge pin 154 is provided at a front end of the connecting arm 152 in a direction orthogonal to the longitudinal direction of the connecting arm 152 and at the other side of the hinge arm 146 opposite to a position where the hinge slot 147 is formed, A spring fixture 160 having a return spring S is provided in the coupling hole 147 'so that the return spring S can be inserted into the hinge pin 154, So that an inclination angle of the swash plate (148) is increased by exerting an elastic force in a direction of pushing the swash plate (148) toward the front housing (120). delete The method according to claim 1, Wherein the return spring (S) exerts an elastic force of 5N to 150N.

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