KR101501776B1 - swash plate type compressor - Google Patents

Abstract

The present invention relates to a swash plate type compressor. In the present invention, the spline portion 140 'is provided on the rotation shaft 140 which is installed through the center bore 111 and rotates and is coupled with the swash plate 148 and rotated together. The spline portion 140 'is coupled with the spline portion 172 of the hub 170 to receive the driving force of the pulley 160 to rotate the rotary shaft 140. At this time, a guide portion A and a press-fit portion B are continuously provided in the spline portion 140 'along the coupling direction of the rotary shaft 140 and the hub 170, and the width of the guide portion A (W1) and the height (H1) are gradually increased toward the press-in portion (B). The coupling force between the rotating shaft 140 and the hub 170 is maintained at a constant value or less while the coupling force between the rotating shaft 140 and the hub 170 is increased during operation of the compressor 100, Thereby preventing abrasion.

Swash plate, compressor, control valve

Description

A swash plate type compressor

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor, and more particularly, to a swash plate type compressor in which a refrigerant is delivered into a cylinder bore through a rotary valve provided on a rotary shaft and is compressed.

The air conditioning system of a vehicle is briefly described. First, a high-temperature low-pressure gaseous refrigerant is converted into a high-temperature and high-pressure gaseous state by a compressor. The high-temperature high-pressure gaseous refrigerant is brought into a high-temperature and high-pressure liquid state by the condensing action of the condenser through the condenser, and the refrigerant in the high-temperature and high-pressure liquid state passes through the expansion valve to the low- do. The refrigerant in the low-temperature low-pressure liquid state is returned to the high-temperature low-pressure gaseous state through the heat exchanger in the evaporator via the evaporator, and the high-temperature low-pressure gas is again compressed by the compressor to become a high-temperature high-pressure gaseous state. The air conditioning system of the vehicle is operated by repeating this process.

FIG. 1 shows the structure of a conventional variable displacement swash plate type compressor, and FIG. 2 shows a rotating shaft provided in a compressor according to the prior art and a hub connected to the rotary shaft in an exploded perspective view and a cross-sectional view . Accordingly, the swash plate type pressure reducer 10 is provided with the cylinder block 11. The cylinder block 11 forms a part of the skeleton of the outer appearance of the compressor 10. A center bore 12 is formed through the center of the cylinder block 11 and a plurality of cylinder bores 13 are formed so as to penetrate the cylinder block 11 radially around the center bore 12 .

A piston (15) is installed in the cylinder bore (13) so as to reciprocate linearly. The piston 15 has a cylindrical shape, and the cylinder bore 13 is a cylindrical space corresponding to the cylinder bore 13. A connecting portion 17 is formed at one end of the piston 15, that is, a portion protruding outward from the cylinder bore 13. The piston 15 linearly reciprocates in the cylinder bore 13 to compress the refrigerant.

A front housing 20 is installed at one end of the cylinder block 11. The front housing 20 is inserted into the cylinder block 11 so as to form a crank chamber 21 together with the cylinder block 11. The crank chamber 21 is kept airtight with the outside.

A pulley shaft portion 22 is installed on the opposite side of the cylinder block 11 of the front housing 20 so that a pulley (not shown) is rotatably installed. A shaft hole 23 is formed through the center of the pulley shaft 22 and penetrates the front housing 20 forward and backward to the crank chamber 21. The shaft hole 23 is centered with the center bore 12. One end of the rotary shaft (40) is rotatably supported on the shaft hole (23).

And the rear housing 30 is installed at the other end of the cylinder block 11. A discharge chamber 31 is formed in the rear housing 30 so as to selectively communicate with the cylinder bore 13. The discharge chamber 31 is a place where refrigerant compressed in the cylinder bore 13 is discharged and temporarily stays.

A suction chamber (33) is formed in the rear housing (30). The suction chamber (33) is also selectively communicated with the cylinder bore (13). The suction chamber 33 is formed in a region of the rear housing 30 corresponding to the center of the surface facing the cylinder block 11. The suction chamber (33) serves to transfer the refrigerant to be compressed into the cylinder bore (13). The suction port for transferring the refrigerant from the outside to the suction chamber 33 is not shown in this embodiment.

A rotary shaft 40 is installed so as to be rotatable through the center bore 12 of the cylinder block 11 and the shaft hole 23 of the front housing 20. The rotary shaft (40) is rotated by the driving force transmitted from the engine. The rotary shaft (40) is rotatably installed on the front housing (20) by a bearing (42).

The rotation shaft (40) is provided with a hollow portion (41). The hollow portion 41 is an empty space formed along the longitudinal direction inside the rotation shaft 40 and serves to communicate the crank chamber 21 and the cylinder bore 13.

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

A swash plate (48) is installed on the rotating shaft (40). A connecting arm 49 hinged to the hinge arm 46 of the rotor 44 protrudes from the swash plate 48. The connecting arm 49 is connected to the hinge arm 46 at the tip thereof by a hinge structure 49 '. Accordingly, the swash plate 48 is hingedly coupled to the rotor 44 and rotated together.

The swash plate 48 is installed between the swash plate 48 and the rotary shaft 40 so that the angle of the swash plate 48 is orthogonal to the longitudinal direction of the rotary shaft 40 and is inclined at a predetermined angle with respect to the rotary shaft 40 Position.

A valve assembly 53 for controlling the flow of refrigerant between the discharge chamber 31 and the cylinder bore 13 is provided between the cylinder block 11 and the rear housing 30. The valve assembly 53 is constituted by a valve plate 54 and a discharge lead 56 having a discharge hole 54 'to control the refrigerant flow from the cylinder bore 13 to the discharge chamber 31.

Meanwhile, as shown in FIG. 2 (a), the rotary shaft 40 is engaged with the hub H. The hub H serves to transmit the rotational force of the pulley rotated by the engine to the rotary shaft 40. Although not shown, the hub H is coupled to a limiter or the like.

At this time, the rotary shaft (40) and the hub (H) are spline coupled. That is, at least a part of a spline shaft 40 'is provided on the outer circumferential surface of the rotary shaft 40 and a spline portion H' corresponding to the spline shaft 40 'is formed on the inner circumferential surface of the hub H And are coupled to each other.

The state of engagement between the rotary shaft 40 and the hub H is well shown in Fig. 2 (b). As shown in the figure, the spline shaft 40 'of the rotary shaft 40 and the spline portion H' of the hub H are engaged with each other so that the rotary shaft 40 and the hub H do not idle Thereby maintaining a firmly coupled state.

However, the above-described conventional techniques have the following problems.

A clearance G is formed between the spline shaft 40 'of the rotary shaft 40 and the spline H' of the hub H to some extent. This corresponds to a tolerance for preventing the deterioration of assemblability when the coupling force between the rotating shaft 40 and the hub H is too large.

However, when the power of the engine is transmitted to the compressor 10 by the gap G between the rotary shaft 40 and the hub H, wear occurs between the spline shaft 40 'and the spline H' . That is, the sharp edges of the spline shaft 40 'and the spline H' damage the surface of the other side due to the stress generated during the rotation of the rotary shaft 40.

If the rotary shaft 40 and the hub H are idled or worn by such abrasion, the coupling between the hub H and the rotary shaft 40 is released.

Of course, it is possible to minimize the clearance G between the spline shaft 40 'of the rotary shaft 40 and the spline H' of the hub H to prevent such abrasion. However, And the hub (H) is too large, resulting in poor workability.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to solve the problems of the prior art as described above and to solve the problems of the prior art as described above. It is an object of the present invention to provide a compressor To adjust the amount of indentation.

According to an aspect of the present invention, there is provided a cylinder block including a cylinder block having a plurality of cylinder bores formed around a center bore passing through the center thereof, A rotating shaft which is installed through the center bore and rotates together with the swash plate and rotates together and is provided with a spline part on the outer circumferential surface and is coupled to the hub to receive the driving force of the pulley and rotates; And a piston which is received through the swash plate and performs compression of the refrigerant in the cylinder bore, wherein the guide portion and the press-in portion are formed in the spline portion along the direction of joining the rotary shaft and the hub, And the width and height of the guide portion gradually increase toward the press-in portion The greater the.

The height of the tip of the guide portion is formed to be smaller than the height of the press-in portion and the height at which the forced press-fit is performed in the spline portion.

The width of the tip of the guide portion is the width of the press-in portion x 0.1 < the width of the tip of the guide portion < width of the press-

The length of the press-in portion is the length of the spline portion x 0.2 <the length of the press-in portion <the length of the spline portion x 0.9.

In the swash plate type compressor according to the present invention having the above-described structure, the following effects can be obtained.

According to the present invention, in the process of operating the compressor in a state in which the rotating shaft and the hub are assembled while maintaining the coupling force at the time of assembling between the rotating shaft and the hub at a certain level by appropriately adjusting the amount of forced indentation of the spline portion provided in the rotating shaft of the compressor, So that the wear of the spline portion is prevented. Accordingly, both the assembling property and the durability of the compressor can be improved.

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

FIG. 3 is a cross-sectional view of a preferred embodiment of a swash plate type compressor according to the present invention. FIG. 4 is a perspective view of a part of a rotary shaft constituting an embodiment of the present invention. And the spline portion of the rotating shaft constituting the rotating shaft is schematically shown.

According to these drawings, the swash plate type compressor 100 is provided with the cylinder block 110. The cylinder block 110 forms a part of the outer structure and the skeleton of the compressor 100. A center bore 111 is formed through the center of the cylinder block 110. The center bore 111 is a portion in which a rotation shaft 140, which will be described below, is rotatably installed.

A plurality of cylinder bores 113 are formed to penetrate the cylinder block 110 radially around the center bore 111. A communication passage 114 is formed so that the cylinder bore 113 and the center bore 111 are communicated with each other. The communication passage 114 is a passage through which the refrigerant is delivered to the cylinder bore 113.

 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 linearly reciprocates in the cylinder bore 113 to compress the refrigerant.

A front housing 120 is installed at one end of the cylinder block 110. The front housing 120 is recessed toward the cylinder block 110 to form a crank chamber 121 in cooperation with the cylinder block 110. The crank chamber 121 is kept airtight with the outside of the compressor.

A pulley shaft portion 122 is installed on the opposite side of the cylinder block 110 of the front housing 120 to which the pulley 160 is rotatably installed. A shaft hole 123 penetrating the front housing 120 through the center of the pulley shaft portion 122 and extending to the crank chamber 121 is formed. The shaft hole 123 is centered with the center bore 111. One end of the rotation shaft 140 is rotatably supported on the shaft hole 123.

A rear housing 130 is installed at the other end of the cylinder block 110, that is, opposite to the front housing 120. A discharge chamber 131 is formed in the rear housing 130 so as to selectively communicate with the cylinder bore 113. The discharge chamber 131 is formed along an edge of a surface of the rear housing 130 facing the cylinder block 110. The discharge chamber 131 is a place where the refrigerant compressed by the cylinder bore 113 is discharged and temporarily stays.

A suction chamber 133 is formed at a center of a surface of the rear housing 130 facing the cylinder block 110. The suction chamber 133 is also selectively communicated with the cylinder bore 113. The suction chamber 133 serves to transfer the refrigerant to be compressed into the cylinder bore 113. The suction chamber 133 transfers the refrigerant to the communication passage 114 through a rotary valve 141 formed at one end of the rotary shaft 140.

A fastening hole 137 is fastened to the cylinder block 110, the front housing 120, and the rear housing 130 so as to fasten the cylinder block 110, the front housing 120 and the rear housing 130 to each other. A plurality of fastening holes 137 are formed at the edges of the cylinder block 110, the front housing 120, and the rear housing 130, respectively. In the present embodiment, the fastener 137 is a bolt.

A rotating shaft 140 is installed to be rotatable through the center bore 111 of the cylinder block 110 and the shaft hole 123 of the front housing 120. The rotation shaft 140 is rotated by the driving force transmitted from the engine. The rotary shaft 140 is rotatably installed in the front housing 120 and the cylinder block 110.

A spline 140 'is provided at one end of the rotation shaft 140. The spline portion 140 'is for coupling with the spline portion 172 of the hub 170 to be described below and allows the rotation shaft 140 and the hub 170 to be engaged and rotated together.

4 and 5, the spline 140 'of the rotating shaft 140 is well illustrated. As shown in the drawing, the spline portion 140 'is composed of a guide portion A and a press-fitting portion B. The guide portion A is a portion that guides the spline portion 140 'to be inserted into the spline portion 172 of the hub 170 more easily, and the press-fitting portion B is a portion So that the rotary shaft 140 and the hub 172 can be substantially engaged. Of course, press-fitting can be performed even in a part of the guide portion A.

At this time, the ratio of the guide portion A to the press-in portion B with respect to the total length L of the spline portion 140 'needs to be appropriately adjusted. If the length of the press-fitting portion B is too long, the coupling force for coupling the rotation shaft 140 to the hub 170 becomes large. On the contrary, if the size of the press-fitting portion B becomes too small, And the hub 170, the wear of the spline part 140 'is liable to occur during the rotation of the rotation shaft 140.

As shown in FIG. 5, the guide portion A is formed so that the height H1 and the width W1 of the guide portion A gradually increase toward the press-fitting portion B. This is for the purpose of guiding the natural coupling to the press-fitting portion B without generating a large coupling force in the process of engaging the hub 170 with the spline portion 172.

The minimum height H1 of the guide portion A, that is, the height H1 of the tip of the guide portion A is determined from the height H2 of the press-fitting portion B to the height k of the forced press- ) Is preferably smaller than the value obtained by subtracting the thickness This means that the minimum height H1 of the guide portion A should be set so as not to be directly inserted from the tip end of the guide portion A. [

Here, the forced indentation amount D means the volume of the portion where the forced indentation is made between the hub 170 and the rotary shaft 140. If forced indentation is performed only in the press-fitting portion B, the forced indentation amount D can be calculated approximately as D = (W 2 x X) x k.

Hereinafter, with reference to FIG. 6, an appropriate setting of the area (W 2 X) of the press-fitting portion B will be described. FIG. 6 is a graph showing an experiment in which a stress is calculated by changing the ratio of the area (W 2 × X) of the press-fitting portion B to the entire area of the spline portion 140 '. 6 shows experimental data while varying only the area (W2 x X) of the press-fitting portion B while the height H2 of the press fitting portion B is fixed.

As can be seen, the stress generated when the rotary shaft 140 and the hub 170 are engaged increases as the size of the press-fitting portion B increases. The stress generated when the rotary shaft 140 and the hub 170 are coupled is preferably kept small for workability. As shown in FIG. 6, it can be seen that the stress generated when the rotation shaft 140 and the hub 170 are coupled with each other is maintained relatively constant in the section where the ratio of the press-fit portion B is 10% to 90%.

The stress applied to the spline portion 140 'during the operation of the compressor 100 after the rotation shaft 140 and the hub 170 are coupled with each other is reduced to a certain extent as the size of the press-fitting portion B increases . This is because when the compressor 100 is operated, the edges of the spline portion 140 'tend to be worn to offset the stress acting on the spline portion 140'. The gap between the rotation axis 140 and the hub 170 If this is reduced, this will be lost.

Therefore, it can be seen that it is appropriate to maintain the area (W2 x X) of the press-fitting portion B about 10% to 90% with respect to the area of the entire spline portion 140 ' . This means, conversely, that the area of the guide portion A can be maintained at 90% to 10%. Preferably, the width W1 of the tip end of the guide portion A is smaller than the width W2 of the press-in portion B x 0.1 <the width W1 of the tip end of the guide portion A < And the length X of the press-fitting portion B is preferably set such that the length L of the spline portion 140 'x 0.2 is smaller than the length X of the press-fitting portion B, (L) of the spline portion 140 'x 0.9.

A rotary valve 141 is provided at one end of the rotary shaft 140. Although the rotary valve 141 is formed integrally with the rotary shaft 140 in the present embodiment, the rotary valve 141 may be formed separately from the rotary shaft 140 and then coupled to the rotary shaft 140.

A flow passage 142 is formed in the rotary valve 141 to communicate with the suction chamber 133. The flow path 142 is formed to be open to one end of the rotary valve 141. A flow path outlet 142 'is formed on the outer surface of the rotary valve 141 to selectively communicate between the flow path 142 and the communication path 114.

A rotor 146 is installed on the rotating shaft 140. The rotor 146 is installed in the crank chamber 121 so that the rotating shaft 140 passes through the center and is integrally rotated with the rotating shaft 140. The rotor 146 is fixed to the rotating shaft 140 in a substantially disk shape. A hinge arm 147 protrudes from one surface of the rotor 146. The hinge arm 147 is formed with a hinge slot 147 '.

The swash plate 148 is installed on the rotating shaft 140. A connecting arm 149 connected to the hinge arm 147 of the rotor 146 protrudes from the swash plate 148. A hinge pin 149 'is provided at the tip of the connecting arm 149 in a direction perpendicular to the longitudinal direction of the connecting arm 149. The hinge pin 149' In the hinge slot 147 'formed at the distal end of the hinge slot 147'.

The swash plate 148 is hingedly coupled to the rotor 146 and rotated together. The swash plate 148 is installed to vary the angle of the swash plate 148 with respect to the rotation axis 140 and is disposed between the swash plate 148 and the swash plate 148 in a state in which the swash plate 148 is inclined at a predetermined angle with respect to the rotation axis 140 Position.

A semi-inclined spring 150, which is a coil spring, is installed on the rotation shaft 140 so as to surround the rotation shaft 140. The anti-tilt spring 150 exerts an elastic force between the rotor 146 and the swash plate 148. The antireflection spring 150 exerts an elastic force in a direction in which the inclination angle of the swash plate 148 is reduced and absorbs a force acting on the swash plate 148 when the operation of the compressor 100 is stopped do.

The swash plate 148 has its edge connected to the pistons 115 through a shoe 152. That is, the edge of the swash plate 148 is connected to the connecting portion 117 of the piston 115 through the shoe 152 so that the piston 115 is rotated in the cylinder bore 113 by the rotation of the swash plate 148 To make a linear reciprocating motion.

A valve assembly 153 for controlling the flow of the refrigerant between the discharge chamber 131 and the cylinder bore 113 is provided between the cylinder block 110 and the rear housing 130. The valve assembly 153 includes a valve plate 154 and a discharge lead 156 having a discharge hole 154 'to control the refrigerant flow from the cylinder bore 113 to the discharge chamber 131.

A pulley 160 is rotatably mounted on the pulley shaft 122 formed at the front end of the front housing 120. The pulley 160 is selectively connected to the rotary shaft 140 through a clutch 162 to transmit the driving force of the engine to the rotary shaft 140 via the pulley 160 and the clutch 162.

More precisely, a hub 170 is connected to the clutch 162 and a spline portion 172 is provided to the hub 170 to be coupled to the spline portion 140 'of the rotation shaft 140.

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

When the pulley 160 is rotated by the driving force of the engine, the rotational force of the pulley 160 is transmitted to the rotating shaft 140 through the hub 170. The spline 140 ' of the rotary shaft 140 is composed of a guide portion A and a press-fit portion B, and the press-fit portion 140' B) is appropriately set, the stress acting on the spline 140 'during the rotation of the rotating shaft 140 can be minimized.

Meanwhile, in the course of coupling the hub 170 to the rotary shaft 140, the coupling can be guided by the guide portion A. That is, since the width W1 and the height H1 of the guide portion A become smaller toward one end thereof, the coupling with the hub 170 can be naturally guided.

When the rotation shaft 140 rotates, the rotor 146 rotates together, and the swash plate 148 rotates together with the rotor 146. The rotation of the swash plate 148 is transmitted to the piston 115 through the shoe 152.

Accordingly, the piston 115 linearly reciprocates in the cylinder bore 113 to compress the refrigerant. At this time, the stroke distance of the piston 115 is determined according to the angle of the swash plate 148. The angle of the swash plate 148 can be controlled by the pressure of the refrigerant transferred into the crank chamber 121.

On the other hand, the refrigerant is transferred into the cylinder bore 113. The refrigerant transferred from the outside to the suction chamber 133 is transferred to the flow path 142 provided in the rotary valve 141 of the rotary shaft 140. The refrigerant transferred to the oil passage 142 is sequentially communicated through the respective cylinder bores 113 and the respective communication passages 114 in accordance with the rotation of the rotary shaft 140, To the cylinder bore 113 of the cylinder.

The refrigerant transferred to the cylinder bore 113 and compressed by the piston 115 is delivered to the discharge chamber 131 by the valve assembly 153 and is delivered to the outside of the compressor 100. That is, when the refrigerant is compressed and the pressure inside the cylinder bore 113 is increased, the tip of the discharge lead 156 is pushed by the pressure to open the discharge hole 154 ' The refrigerant is discharged to the discharge chamber 131. [

The scope of the present invention is not limited to the embodiments described above, but may be defined by the scope of the claims, and those skilled in the art may make various modifications and alterations within the scope of the claims It is self-evident.

Although the guide portion A and the press-fit portion B are provided on the spline portion 140 'of the rotary shaft 140 in the above-described embodiment, The spline portion 172 may be provided with a guide portion and a press-in portion.

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

Fig. 2 (a) is an exploded perspective view showing a configuration of a rotary shaft and a hub of a swash plate type compressor according to the prior art.

Fig. 2 (b) is a partial cross-sectional view showing a spline coupling structure of a rotating shaft and a hub of a swash plate type compressor according to the related art.

3 is a sectional view showing a configuration of a preferred embodiment of a swash plate type compressor according to the present invention.

4 is a perspective view showing a part of the configuration of a rotary shaft constituting an embodiment of the present invention.

5 is a schematic view showing a configuration of a spline portion of a rotating shaft constituting an embodiment of the present invention.

6 is a graph showing a change in stress according to a ratio of a press-in portion of a spline portion of a rotating shaft constituting an embodiment of the present invention.

Description of the Related Art [0002]

100: compressor 110: cylinder block

111: center bore 113: cylinder bore

115: piston 117:

120: front housing 121: crank chamber

122: pulley shaft part 123:

130: rear housing 131: discharge chamber

133: Suction chamber 135: Control valve

140: rotation axis 140 ': spline portion

147: Hinge arm 147 ': Hinge slot

148: swash plate 149: connecting arm

150: Semi inclined spring 153: Valve assembly

154: valve plate 154 ': discharge hole

156: discharge lead 160: pulley

170: hub 172: spline portion

A: Guide part B:

Claims (4)

A cylinder block 110 in which a plurality of cylinder bores 113 are formed around a center bore 111 passing through the center, A front housing 120 and a rear housing 130 provided at the front and rear ends of the cylinder block 110, And is coupled with the swash plate 148 and rotates together with the swash plate 148. The spline part 140 'is provided on the outer circumferential surface and is coupled with the hub 170 to receive the driving force of the pulley 160 A rotating shaft 140 rotated, And a piston (115) that receives the rotation of the rotary shaft (140) through the swash plate (148) and compresses the refrigerant in the cylinder bore (113) The guide portion A and the press-fit portion B are continuously provided in the spline portion 140 'along the coupling direction of the rotation shaft 140 and the hub 170 and the width W1 And the height H1 gradually increase toward the press-fitting portion B, The height H1 of the tip of the guide portion A is greater than the difference H2-k between the height H2 of the press-fitting portion B and the height k at which the force is applied by the spline portion 140 ' Wherein the compressor is formed in a small size. delete A cylinder block 110 in which a plurality of cylinder bores 113 are formed around a center bore 111 passing through the center, A front housing 120 and a rear housing 130 provided at the front and rear ends of the cylinder block 110, And is coupled with the swash plate 148 and rotates together with the swash plate 148. The spline part 140 'is provided on the outer circumferential surface and is coupled with the hub 170 to receive the driving force of the pulley 160 A rotating shaft 140 rotated, And a piston (115) that receives the rotation of the rotary shaft (140) through the swash plate (148) and compresses the refrigerant in the cylinder bore (113) The guide portion A and the press-fit portion B are continuously provided in the spline portion 140 'along the coupling direction of the rotation shaft 140 and the hub 170 and the width W1 And the height H1 gradually increase toward the press-fitting portion B, The width (W1) of the tip of the guide portion (A) The width W2 of the press-in portion B x 0.1 <the width W1 of the tip end of the guide portion A <the width W2 of the press-fitting portion B x 0.95. A cylinder block 110 in which a plurality of cylinder bores 113 are formed around a center bore 111 passing through the center, A front housing 120 and a rear housing 130 provided at the front and rear ends of the cylinder block 110, And is coupled with the swash plate 148 and rotates together with the swash plate 148. The spline part 140 'is provided on the outer circumferential surface and is coupled with the hub 170 to receive the driving force of the pulley 160 A rotating shaft 140 rotated, And a piston (115) that receives the rotation of the rotary shaft (140) through the swash plate (148) and compresses the refrigerant in the cylinder bore (113) The guide portion A and the press-fit portion B are continuously provided in the spline portion 140 'along the coupling direction of the rotation shaft 140 and the hub 170 and the width W1 And the height H1 gradually increase toward the press-fitting portion B,  The length (X) of the press-fitting portion (B) Wherein the length L of the spline portion 140 'is 0.2 times the length X of the press-fitting portion B and the length L of the spline portion 140' is 0.9.

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