JP2008184920A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To sufficiently absorb compression reaction force transmitted from a piston to a swash plate, on a swash plate receiving face of a rotor. <P>SOLUTION: In this variable displacement compressor, the rotor 21 is fixed to a drive shaft S, and a swash plate part 24 is mounted to the drive shaft S so as to be movable and tiltable to the axial direction. One portion of the swash plate part 24 is connected to one portion of the rotor 21, and the piston 29 is reciprocated by the rotating motion of the swash plate part 24. When a pressure inside a crank chamber 5 storing the rotor 21 and the swash plate part 24 becomes below a predetermined value, the other portion of the swash plate part 24 abuts on the swash plate receiving face 59 (not shown in Fig. 1) provided in the other portion of the rotor 21. When the pressure inside the crank chamber 5 exceeds the predetermined value, the other portion of the swash plate part 24 is separated from the swash plate receiving face 59 of the rotor 21. A rotor side cushioning material 53 and swash plate side cushioning material 54, comprising rubber materials are fixed to the swash plate receiving face 59 of the rotor 21, and the other portion of the swash plate part 24 abutting on the swash plate receiving face 59, by using fixation pins 61, 63, respectively. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a variable capacity compressor in which a piston is reciprocated by swinging of an inclination angle varying member accompanying rotation of a drive shaft.

  An example of a conventional variable capacity compressor is described in Patent Document 1 below. In this variable capacity compressor, a drive hub that is axially movable and rotatable with the drive shaft is provided on the outer periphery of the drive shaft, and the inclination angle of the swinging plate provided on the drive hub varies depending on the pressure in the crank chamber. The change in the inclination angle changes the stroke of the piston provided on the outer peripheral side of the swing plate, thereby changing the refrigerant discharge capacity.

  A thrust flange that rotates with the drive shaft is fixed to the outer periphery of the drive shaft, and one end of the thrust flange and one end of the drive hub are connected to each other.

Here, when the refrigerant discharge amount increases so that the pressure in the crank chamber is less than a predetermined value, the inclination angle of the swing plate increases, and the other end of the drive hub is brought into contact with the drive hub receiving surface provided at the other end of the thrust flange. On the other hand, when the refrigerant discharge amount decreases so that the pressure in the crank chamber becomes equal to or higher than a predetermined value, the inclination angle of the swing plate becomes small and the other end portion of the drive hub separates from the drive hub receiving surface of the thrust flange.
JP 2001-323873 A

  By the way, in the conventional variable capacity compressor described above, the drive hub receiving surface of the thrust flange is made substantially perpendicular to the drive shaft so that the other end of the drive hub is thrust when the maximum discharge amount is reached. Since the flange is almost perpendicular to the drive hub receiving surface, the load is not applied to the drive shaft in a direction perpendicular to the axis of the drive shaft to prevent elastic deformation of the drive shaft, and it is transmitted from the piston to the drive hub. The vibration of the drive hub is damped by absorbing the compression reaction force at the drive hub receiving surface of the thrust flange.

  However, since the contact surface between the other end of the drive hub and the drive hub receiving surface of the thrust flange is a metal surface, the reaction force transmitted from the piston to the drive hub is sufficiently absorbed by the drive hub receiving surface of the thrust flange. This is not possible, and the vibration attenuating effect of the drive hub is insufficient and abnormal noise is generated.

  Accordingly, an object of the present invention is to enable a rotating member (thrust flange) to sufficiently absorb a compression reaction force transmitted from a piston to an inclination angle varying member (oscillating plate).

  According to the present invention, the rotation member is fixed to the drive shaft, and the tilt variation member is attached to the drive shaft so as to be movable and tiltable in the axial direction, and one portion of the tilt variation member is connected to one portion of the rotation member. When the piston is reciprocated by the rotation operation of the tilt variation member and the pressure in the crank chamber that houses the rotation member and the tilt variation member becomes less than a predetermined value, the other portions of the tilt variation member While contacting the inclination varying member receiving surface provided in another part, when the pressure in the crank chamber exceeds a predetermined value, the other part of the inclination varying member is separated from the inclination varying member receiving surface of the rotating member. In the capacity compressor, at least one of the tilt angle varying member receiving surface of the rotating member and the other portion of the tilt angle varying member in contact with the tilt angle varying member receiving surface is provided with an impact absorbing member. The most important feature that is provided.

  According to the variable capacity type compressor of the present invention, when the other portion of the tilt variation member comes into contact with the tilt variation member receiving surface of the rotation member in the maximum discharge amount state, the tilt variation member reception surface of the rotation member The compression reaction force transmitted from the piston to the tilt variation member is sufficiently absorbed by the tilt variation member receiving surface of the rotation member by the shock absorbing member provided at least one of the other portions of the tilt variation member and the tilt variation member. Vibration can be effectively attenuated, abnormal noise can be prevented, and elastic deformation of the rotating member and the tilt angle varying member can be suppressed.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[Overall structure of variable capacity compressor]
FIG. 1 is an overall sectional view of a variable capacity compressor according to a first embodiment of the present invention. However, the rotor 21 serving as the rotating member and the swash plate portion 24 serving as the tilt angle varying member are not shown in cross section but are shown in a front view.

  As shown in FIG. 1, the compressor 1 of this embodiment is a swash plate type variable capacity compressor, and is used for a refrigeration cycle of a vehicle air conditioner mounted on a vehicle such as an automobile, for example. The variable capacity compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 arranged at equal intervals in the circumferential direction, and a cylinder block 2 joined to the left front end surface of the cylinder block 2 in FIG. A front housing 4 that forms a crank chamber 5 therebetween, and a rear housing 6 that is joined to a rear end surface of the cylinder block 2 via a valve plate 9 to form a suction chamber 7 and a discharge chamber 8 are provided. The cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by a plurality of through bolts B.

  The valve plate 9 includes a suction hole (not shown) that allows the cylinder bore 3 and the suction chamber 7 to communicate with each other, and a discharge hole 12 that allows the cylinder bore 3 and the discharge chamber 8 to communicate with each other.

  A valve mechanism (not shown) for opening and closing the suction hole is provided on the cylinder block 2 side of the valve plate 9, while a valve mechanism (not shown) for opening and closing the discharge hole 12 is provided on the rear housing 6 side of the valve plate 9. Is provided. A gasket 14 is interposed between the valve plate 9 and the rear housing 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained.

  A drive shaft S is pivotally supported via bearings 17 and 18 in the support holes 19 and 20 in the center of the cylinder block 2 and the front housing 4, and the drive shaft S is rotatable in the crank chamber 5.

  In the crank chamber 5, a rotor 21 as a rotating member fixed to the drive shaft S, a hinge ball 22 slidably mounted on the drive shaft S, and a tilt ball mounted on the hinge ball 22. And a swash plate portion 24 as an inclination angle varying member. The swash plate portion 24 includes a hub 25 attached to the hinge ball 22 so as to be tiltable and rotatable, and a swash plate body 26 fixed to a boss portion 25 a of the hub 25.

  A piston 29 is slidably accommodated in each cylinder bore 3, and the piston 29 is connected to the swash plate body 26 via a pair of hemispherical piston shoes 30,30.

  A link mechanism 40 is interposed between a part of the rotor 21 as the rotating member and a part of the hub 25 of the swash plate part 24 as the tilt angle varying member. The rotational torque of the rotor 21 is transmitted to the swash plate portion 24 while allowing the tilt angle to vary.

  The link mechanism 40 protrudes from the rotor 21 toward the hub 25 and is opposed to the rotational torque transmission direction, and is opposed to the rotational torque transmission direction. The link mechanism 40 projects from the hub 25 toward the rotor 21 and is in the rotational torque transmission direction. A pair of arms 43, 43 facing each other, and a link 45 inserted between the pair of arms 41, 41 of the rotor 21 and the pair of arms 43, 43 of the hub 25 that face each other. I have.

  One end of the link 45 is rotatably connected to the pair of arms 41 and 41 of the rotor 21 by a first connecting pin 46 extending in the rotational torque direction, and the other end of the link 45 extends in the rotational torque direction. The second connecting pin 47 is rotatably connected to the pair of arms 43 and 43 of the hub 25.

  The inclination angle of the swash plate portion 24 decreases as the hinge ball 22 moves closer to the cylinder block 2, and increases as the hinge ball 22 moves away from the cylinder block 2.

  When the drive shaft S rotates, the rotor 21 rotates integrally with the drive shaft S, and the rotation of the rotor 21 is transmitted to the swash plate portion 24 via the link mechanism 40. The rotation of the swash plate portion 24 is converted into a reciprocating motion of the piston 29 by the pair of piston shoes 30, 30, and the piston 29 reciprocates in the cylinder bore 3. By the reciprocating motion of the piston 29, the refrigerant in the suction chamber 7 is sucked into the cylinder bore 3 through a suction hole (not shown) of the valve plate 9 and then compressed, and discharged into the discharge chamber 8 through the discharge hole 12 of the valve plate 9. Is done.

[Control of variable capacity]
Here, the inclination angle of the swash plate portion 24 can be changed. When the swash plate portion 24 moves close to the cylinder block 2 against the return spring 52 provided on the piston 29 side, the inclination angle decreases, while on the rotor 21 side. If it moves in the direction away from the cylinder block 2 against the provided return spring 51, the inclination angle increases.

  In order to change the refrigerant discharge capacity, the piston stroke is changed by changing the inclination angle of the swash plate portion 24. More specifically, the piston stroke is changed by changing the inclination angle of the swash plate portion 24 by the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear surface side of the piston 29 and the suction chamber pressure Ps on the front surface side of the piston 29. Change.

  For this reason, the variable capacity compressor includes an extraction passage (not shown) that connects the crank chamber 5 and the suction chamber 7, an air supply passage (not shown) that connects the crank chamber 5 and the discharge chamber 8, and A pressure control mechanism having a control valve 33 provided in the middle of the air supply passage for controlling opening and closing of the air supply passage is provided.

  1 shows a state in which the inclination angle of the swash plate portion 24 is maximized at the time of a full stroke, and FIG. 2 shows an enlarged main part in that state. FIG. 3 shows a state at the time of destroke, that is, a state where the inclination angle of the swash plate portion 24 becomes the smallest.

[Shock absorbing member]
Next, the impact absorbing member provided between the other part of the rotor 21 as the rotating member and the other part of the swash plate portion 24 as the tilt angle varying member will be described.

  Here, a rubber material using acrylic rubber having heat resistance and oil resistance as an impact absorbing member is used. The shock absorbing member made of a rubber material is attached to the rotor-side cushioning material 53 attached to the rotor 21 and the hub 25 of the swash plate portion 24 as shown in FIG. The rotor-side cushioning material 53 and the swashplate-side cushioning material 54 face each other.

  The rotor-side cushioning material 53 and the swash plate-side cushioning material 54 are set at two locations on both sides of the drive shaft S perpendicular to the paper surface in FIG.

  FIG. 5 is a perspective view of the rotor 21 as viewed from the side facing the hub 25, and FIG. 6 is a perspective view of the hub 25 as viewed from the side facing the rotor 21. At other portions of the hub 25 of the swash plate portion 24, two projecting portions 55 and 56 are provided so as to project toward the rotor 21 along the axis of the drive shaft S. The swash plate-side cushioning material 54 is provided on the front end surfaces 57 and 58 of the projecting portions 55 and 56, and the rotor is provided on the swash plate receiving surface 59 that serves as the inclination varying member receiving surface of the rotor 21 that faces the front end surfaces 57 and 58. A side cushioning material 53 is provided.

  The swash plate receiving surface 59 of the rotor 21 is substantially perpendicular to the axis of the drive shaft S, and the front end surfaces 57 and 58 on the hub 25 side are swash plate receiving of the rotor 21 during the full stroke shown in FIG. It is almost parallel to the surface 59.

  The rotor-side cushioning material 53 shown in FIG. 5 has a disk shape as shown in an enlarged view in FIG. 7, has a pin insertion hole 53a at the center, and a stepped portion on the surface side around the pin insertion hole 53a. 53b is formed. On the other hand, the swash plate receiving surface 59 is formed with a circular recess 59a into which the rotor-side cushioning material 53 is fitted, and a pin press-fitting hole 59b is provided at the center of the recess 59a.

  Then, by pressing the shaft portion 61a of the press-fit pin 61 as a fixture composed of an iron-based metal material into the press-fit hole 59b of the rotor 21 while being inserted into the pin insertion hole 53a of the rotor-side cushioning material 53, As shown in FIG. 4, the rotor-side cushioning material 53 is attached to the recess 59 a of the rotor 21.

  At this time, the thickness dimension of the rotor-side cushioning material 53 is larger than the depth dimension of the recess 59a. Therefore, the rotor-side cushioning material 53 slightly protrudes from the swash plate receiving surface 59 in the attached state of FIG. Furthermore, in the mounting state described above, the head portion 61b of the press-fit pin 61 enters the stepped portion 53b of the rotor side cushioning material 53. At this time, the depth dimension of the stepped portion 53b is larger than the thickness dimension of the head portion 61b. 4, the surface of the head 61 b does not protrude from the surface of the rotor-side cushioning material 53, and forms a concave surface with respect to the surface of the rotor-side cushioning material 53.

  The swash plate-side cushioning material 54 shown in FIG. 6 is also provided with a pin insertion hole 54a and a stepped portion 54b, respectively, similarly to the rotor-side cushioning material 53 described above. A circular recess 57a (58a) into which the material 54 is fitted is provided, and a pin press-fit hole 57b (58b) is provided at the center of the recess 57a (58a).

  Then, the swash plate-side cushioning material 54 is attached to the distal end surface 57 (58) by a press-fit pin 63 having a shaft portion 63a and a head portion 63b. At this time, similarly to the rotor-side cushioning material 53, the swash plate-side cushioning material 54 slightly protrudes from the tip end surface 57 (58) as shown in FIG. 4 and the surface of the head 63b of the press-fit pin 63. Does not protrude from the surface of the swash plate-side cushioning material 54, but forms a concave surface with respect to the surface of the swash plate-side cushioning material 54.

  Therefore, when the hub 25 of the swash plate portion 24 is in contact with the rotor 21 as in the full stroke of FIG. 2, the press-fit pins 61 and 63 do not contact each other as shown in FIG. The buffer material 53 and the swash plate side buffer material 54 come into contact with each other.

[Operation of variable capacity compressor]
When the rotational power of an in-vehicle engine (not shown) is transmitted to the drive shaft S, the rotor 21 and the swash plate portion 24 rotate with the drive shaft S, the rotation causes the swash plate portion 24 to swing, and the swing causes the piston 29 to rotate. Reciprocates in the cylinder bore 3. As a result, the volume in the cylinder bore 3 changes, and the suction, compression, and discharge of the refrigerant are sequentially performed by this volume change, and the refrigerant having a capacity corresponding to the inclination angle of the swash plate portion 24 is discharged.

  The heat load of the vehicle air conditioner using this variable capacity compressor is reduced, the control valve 33 opens the air supply passage, the refrigerant flows from the discharge chamber 8 to the crank chamber 5, and the pressure in the crank chamber 5 is reduced. When it increases, the inclination angle of the swash plate portion 24 becomes smaller as shown in FIG. 3 with respect to the state of FIG. 2, and as a result, the stroke of the piston 29 becomes smaller and the refrigerant discharge capacity decreases.

  On the other hand, when the heat load increases from the state of FIG. 3 and the control valve 33 closes the air supply passage and the pressure in the crank chamber 5 decreases and becomes less than a predetermined value, as in the full stroke of FIG. The inclination angle of the swash plate portion 24 increases, and as a result, the stroke of the piston 29 increases and the refrigerant discharge capacity increases.

  2, other portions of the hub 25 on the swash plate portion 24 side come into contact with the swash plate receiving surface 59 of the rotor 21, and the swash plate side cushioning material 54 and The rotor side cushioning material 53 is provided, and these abut against each other.

  Since the rotor-side cushioning material 53 and the swash plate-side cushioning material 54 are made of a rubber material, at the time of the above-mentioned contact, unlike the conventional contact between the metal surfaces, the piston 29 to the swash plate portion 24 are used. The compression reaction force transmitted to the rotor 21 is sufficiently absorbed by the swash plate receiving surface 59 of the rotor 21 so that the vibration of the swash plate portion 24 can be effectively attenuated, and abnormal noise can be prevented, and the rotor 21 and the swash plate portion can be prevented. 24 elastic deformation can be suppressed.

  In addition, when the rubber materials are in contact with each other, the swash plate receiving surface 59 of the rotor 21 is perpendicular to the axis of the drive shaft S, so that it is possible to avoid applying a load in a direction perpendicular to the drive shaft S, and Elastic deformation of the shaft S can be suppressed.

  Further, since the rotor-side cushioning material 53 and the swash plate-side cushioning material 54 are fixed by press-fitting using the press-fit pins 61 and 63, the attached state is stabilized and the detachment due to vibration can be prevented.

[Second Embodiment]
8 and 9 are perspective views corresponding to FIGS. 5 and 6 of the rotor 21A and the hub 25A according to the second embodiment of the present invention. In the first embodiment described above, the rotor-side cushioning material 53 and the swash plate-side cushioning material 54 are provided at two locations on the rotor 21 and the hub 25, respectively. The swash plate side cushioning material 54 is provided in one place.

  That is, in the second embodiment, the protruding portion 65 provided at the other portion of the hub 25A on the swash plate portion 24 side shown in FIG. 9 is formed by integrating the two protruding portions 57 and 58 in FIG. Correspondingly, the swash plate-side cushioning material 54 is attached to the central portion of the front end surface 66 of the protruding portion 65 using the press-fit pin 63 as in the first embodiment.

  Correspondingly, one rotor-side cushioning material 53 is attached to the swash plate receiving surface 67 of the rotor 21A shown in FIG.

  Note that the tip surface 66 is also in parallel with the swash plate receiving surface 67 that serves as the tilt varying member receiving surface of the rotor 21A during the full stroke shown in FIG. 10, similarly to the tip surfaces 57 and 58 in the first embodiment. ing. The swash plate receiving surface 67 is substantially perpendicular to the drive shaft S, like the swash plate receiving surface 59 of FIG.

  Also in the second embodiment, when the pressure in the crank chamber 5 decreases and becomes less than a predetermined value, and the inclination angle of the swash plate portion 24 increases as shown in FIG. Other portions of the hub 25A abut against the swash plate receiving surface 67 of the rotor 21A, and the swash plate-side cushioning material 54 and the rotor-side cushioning material 53 are provided on the respective abutting surfaces, respectively. They will be in contact with each other.

  For this reason, the compression reaction force transmitted from the piston 29 to the swash plate portion 24 can be sufficiently absorbed by the swash plate receiving surface 67 of the rotor 21A, and the vibration of the swash plate portion 24 can be effectively attenuated, and abnormal noise is generated. While being able to prevent, the elastic deformation of the rotor 21A and the swash plate portion 24 can be suppressed, and the same effects as in the first embodiment can be obtained.

  A plurality of rotor-side cushioning materials 53 and swashplate-side cushioning materials 54 may be provided on the swash plate receiving surface 67 of the rotor 21A and the tip surface 66 of the protrusion 65 of the hub 25A in the second embodiment. In this case, for example, the rotor-side cushioning material 53 and the swash plate-side cushioning material 54 are provided at the two attachment positions in the first embodiment in addition to the positions of FIGS. Alternatively, it is conceivable to provide only two attachment positions in the first embodiment without providing them in the positions of FIGS. 9 and 10, but this does not specify the attachment positions or the number of attachments.

  Thus, by providing two or a plurality of rotor side cushioning materials 53 and swash plate side cushioning materials 54, the impact force transmitted from the hub 25 to the rotor 21 can be dispersed. Compared with the case where one each of the side buffer materials 54 is provided, the vibration of the swash plate portion 24 can be more effectively damped, and abnormal noise can be prevented more reliably, and the elasticity of the rotor 21 and the swash plate portion 24 can be prevented. Deformation can be further suppressed.

  Further, by providing two or more rotor-side cushioning materials 53 and swash plate-side cushioning materials 54, the impact at the time of contact is dispersed compared to the case of one, so that each of the cushioning materials 53 and 54 is provided. It can also increase the lifespan. In addition, since there are a plurality of contact portions, the posture of the hub 25 at the time of a full stroke is stabilized and it becomes easy to suppress the play, and the reliability can be improved.

  In each of the embodiments described above, the rotor-side cushioning material 53 and the swash plate-side cushioning material 54 are attached to both the rotor 21 (21A) and the hub 25 (hub 25A) as rubber materials. A rubber material may be provided only in the case.

  In this way, when attaching either the rotor-side cushioning material 53 or the swash plate-side cushioning material 54, it is more stable to attach the rubber material to the rotor 21 (21A) that does not move or swing in the axial direction. In addition, it is preferable because the processing on the mounting portion is performed on a wide surface (swash plate receiving surfaces 59 and 67) and becomes easy.

  Further, the rotor-side buffer material 53 and the swash plate-side buffer material 54 are fixed to the swash plate receiving surfaces 59 and 67 of the rotor 21 and the hubs 25 and 25A of the swash plate portion 24 by fixing screws instead of the press-fit pins 61 and 63. These may be attached by screwing and fastening to thread portions provided on the front end surfaces 57, 58 and 66, respectively. By using the fixing screw, the attachment work of the rotor side cushioning material 53 and the swash plate side cushioning material 54 becomes easy.

  Further, as shown in FIG. 11, the shock absorbing member is formed on the swash plate receiving surfaces 59 and 67 of the rotor 21 or the front end surfaces 57, 58 and 66 of the hubs 25 and 25A of the swash plate portion 24 without using a fixture. The cushioning material 69 made of a rubber material may be directly attached to the provided fitting hole 68. The cushioning material 69 is formed by fitting the fitting protrusion 69a at the tip into the fitting hole 68, so that the flat head portion 69b is attached to the swash plate receiving surfaces 59 and 67 of the rotor 21 or the tip surfaces of the hubs 25 and 25A. It will be exposed while projecting from 57, 58, 66.

  In this way, by adopting a configuration in which the cushioning material 69 is directly attached, the number of parts can be reduced and the cost can be reduced as compared with the case of using a fixture.

1 is an overall cross-sectional view of a variable capacity compressor according to a first embodiment of the present invention. It is a front view explaining the full stroke state of the swash plate of the variable capacity compressor of FIG. It is a front view explaining the destroke state of the swash plate of the variable capacity compressor of FIG. It is sectional drawing to which the A section of FIG. 2 was expanded. It is the perspective view seen from the side which opposes the hub of the rotor in the variable capacity compressor of FIG. It is the perspective view seen from the side which opposes the rotor of the hub in the variable capacity compressor of FIG. It is the perspective view to which the principal part of FIG. 5 was expanded. It is a perspective view corresponding to FIG. 5 of the rotor concerning the 2nd Embodiment of this invention. It is a perspective view corresponding to FIG. 6 of the hub concerning the 2nd Embodiment of this invention. It is a front view which shows the state (full stroke state) which the hub of the swash plate in 2nd Embodiment contact | abutted to the swash plate receiving surface of the rotor. It is a fragmentary perspective view which shows the form which fits and fixes the shock absorbing material which consists of rubber materials directly to a rotor or a hub as an impact-absorbing member.

Explanation of symbols

S drive shaft 5 crank chamber 21, 21A rotor (rotating member)
24 Swash plate part (inclination variable member)
29 Piston 53 Rotor side shock absorbing material (Shock absorbing member)
54 Swash plate cushioning material (shock absorbing member)
59,67 Swash plate receiving surface (inclination variable member receiving surface)
57b, 58b, 59b Pin press-fit holes (press-fit holes)
61,63 Press-fit pin (fixing tool)
68 Mating hole 69 Cushioning material (shock absorbing member)
69a Mating protrusion

Claims (6)

  A rotation member (21) is fixed to the drive shaft (S), and an inclination angle varying member (24) is attached to the drive shaft (S) so as to be movable and tiltable in the axial direction, and a part of the rotation member (21) A part of the tilt variation member (24) is connected to the piston, and the piston (29) is reciprocated by the rotational operation of the tilt variation member (24), so that the rotation member (21) and the tilt variation member (24) are moved. When the pressure in the accommodated crank chamber (5) becomes less than a predetermined value, the other part of the inclination changing member (24) is inclined to the inclination changing member receiving surface (59) provided at the other part of the rotating member (21). When the pressure in the crank chamber (5) reaches a predetermined value or more, the other part of the inclination changing member (24) separates from the inclination changing member receiving surface (59) of the rotating member (21). In the variable capacity compressor, An impact absorbing member is provided on at least one of the tilt angle varying member receiving surface (59) of the rolling member (21) and another part of the tilt angle varying member (24) in contact with the tilt angle varying member receiving surface (59). A variable capacity compressor provided with (53, 54).   The impact absorbing member (53, 54) is at least one of the tilt varying member receiving surface (59) of the rotating member (21) and another portion of the tilt varying member (24) by the fixture (61, 63). The variable capacity compressor according to claim 1, wherein the variable capacity compressor is fixed to one of them.   The fixture (61, 63) is a press-fitting hole (59b) provided in at least one of the tilt angle varying member receiving surface (59) of the rotating member (21) and the other part of the tilt angle varying member (24). , 58b). The variable capacity compressor according to claim 2, characterized in that it is a press-fit pin (61, 63) that press-fits into the press-fit pin.   The fixture (61, 63) is screwed into a threaded portion provided on at least one of the tilt varying member receiving surface (59) of the rotating member (21) and another portion of the tilt varying member (24). The variable capacity compressor according to claim 2, wherein the variable capacity compressor is a fixing screw that is fastened together.   The shock absorbing member (69) includes a fitting protrusion (69a), and the fitting protrusion (69a) is provided on the inclination varying member receiving surface (59) of the rotating member (21) and the inclination varying member (24). The variable capacity compressor according to claim 1, wherein the compressor is fitted and fixed in a fitting hole (68) provided in at least one of the other parts.   The variable capacity compression according to any one of claims 1 to 5, wherein the tilt angle changing member receiving surface (59) of the rotating member (21) is perpendicular to the drive shaft (S). Machine.

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