JP2005207287A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor having a hinge mechanism which can alleviate a shocking collision between a first hinge part and a second hinge part even in the presence of looseness of a cam plate. <P>SOLUTION: Between a lug plate 17 integrally and rotatably coupled to a drive shaft 16 and a swash plate 18 on which a piston is retained, interposed is a hinge mechanism 19 which couples both the plates. The hinge mechanism 19 comprises a first hinge part 19A on the lug plate 17 side, comprising a cam face 25a and the like, and a second hinge part 19B on the swash plate 18 side, comprising a roller 22 and the like. The roller 22 of the second hinge part 19B is rolled on the cam face 25a of the first hinge part 19A in accordance with the tilting of the swash plate 18. A rubber ring 41 for alleviating a shocking collision of the roller 22 against the cam face 25a when the swash plate 18 is loose is attached to an outer peripheral face 22a a part of which is opposite to the cam face 25a in the roller 22. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a variable capacity compressor used in a refrigeration circuit of a vehicle air conditioner, for example.

  In this type of variable capacity compressor, a cylinder bore is formed in a housing and a drive shaft is rotatably supported. A lug plate is fixed to the drive shaft so as to be integrally rotatable, and a swash plate is supported to be tiltable. A hinge mechanism is interposed between the lug plate and the swash plate. The piston accommodated in the cylinder bore so as to be able to reciprocate is anchored to the outer peripheral portion of the swash plate.

  The drive shaft is rotationally driven by a vehicle engine. The rotation of the drive shaft is transmitted to the swash plate through the lug plate and the hinge mechanism, whereby the piston is reciprocated to compress the refrigerant gas. Moreover, the stroke of the piston is changed by changing the inclination angle of the swash plate by the guidance of the hinge mechanism, so that the discharge capacity can be changed.

As the hinge mechanism, there is one disclosed in Patent Document 1, for example. That is, as shown in FIG. 8, link pins 103 having spherical portions 103a at both ends are provided on the end surface of the swash plate 101 on the lug plate (thrust flange) 102 side. In the lug plate 102, guide grooves 102a for guiding the spherical portions 103a are formed on the end surface of the swash plate 101 side. The change of the inclination angle of the swash plate 101 is guided by the spherical portion 103a of the link pin 103 sliding on the inner surface of the guide groove 102a.
JP 2001-289159 A (FIG. 3)

  However, in the hinge mechanism, due to manufacturing tolerances or the like, the front and rear in the rotational direction of the drive shaft (between the spherical portion 103a of the link pin 103 and the inner surface of the guide groove 102a into which the spherical portion 103a is fitted ( There is a gap between the front and rear (the vertical direction of the drawing) in the direction along the axis of the drive shaft and the axis of the drive shaft. Here, for example, when the discharge capacity of the variable capacity compressor is low and the compression reaction force acting on the swash plate 101 via the piston is small, the pressing force of the spherical portion 103a against the inner surface of the guide groove 102a is small. .

  In this state, for example, when the drive shaft is affected by engine torque fluctuations or the variable capacity compressor is affected by vehicle running vibration, the drive shaft is rotated in the direction of rotation of the drive shaft and / or the axis of the drive shaft. The swash plate 101 will rattle with respect to the lug plate 102 in the longitudinal direction. Accordingly, the spherical portion 103a is repeatedly impacted against the inner surface of the guide groove 102a, and there is a problem that the variable capacity compressor generates abnormal noise and vibration.

  An object of the present invention is to provide a variable capacity compressor having a hinge mechanism that can alleviate an impact collision between a first hinge part and a second hinge part even if the cam plate is rattled. is there.

  In order to achieve the above object, a variable capacity compressor according to a first aspect of the present invention includes a first hinge portion provided on the lug plate and a second hinge portion provided on the cam plate and connected to the first hinge portion. A buffer member is interposed between the opposing surfaces. Therefore, even when the cam plate rattles against the lug plate, the shocking collision between the first hinge portion and the second hinge portion can be mitigated by the buffering action of the buffer member.

  According to a second aspect of the present invention, in the first aspect of the present invention, the buffer member is interposed between opposing surfaces disposed between the first hinge portion and the second hinge portion in the front and rear direction along the axis of the drive shaft. Yes. Therefore, even when the cam plate rattles back and forth in the direction along the axis of the drive shaft, the impact collision between the first hinge portion and the second hinge portion can be mitigated by the buffering action of the buffer member. .

  The invention of claim 3 refers to a preferred embodiment of the hinge mechanism and the buffer member in claim 2. That is, the second hinge part is a support part protruding from the end face of the cam plate on the lug plate side, a spherical part protruding from the support part in the rotational direction of the drive shaft, and a drive at the support part. And a rolling element rotatably supported by a shaft portion protruding on the front side in the rotation direction of the shaft. The first hinge portion is provided on the end surface of the lug plate on the cam plate side, and is provided on the first groove-shaped first cam portion that guides the spherical portion, and the same end surface as the first cam portion, and the rolling element is rolled. And a second cam portion having a cam surface.

  An annular buffer member is mounted on the outer peripheral surface of the rolling element that partially faces the cam surface. Therefore, even when the cam plate is rattled back and forth in the direction along the axis of the drive shaft, the shock collision between the cam surface of the first hinge portion and the rolling element of the second hinge portion is caused by the buffering action of the buffer member. Can be relaxed.

  In the variable capacity compressor employing the hinge mechanism having such a configuration, the cam plate largely rattles (turns) in the direction in which the rolling element is in contact with and away from the cam surface with the spherical portion as the center. There is. In other words, in a variable capacity compressor that employs a hinge mechanism that tends to increase backlash of the cam plate, it is particularly possible to incorporate a buffer member in the hinge mechanism to alleviate the impact collision between the rolling element and the cam surface. It can be said that it is effective.

Moreover, it can be said that the said buffer member which makes | forms an annular | circular shape has comprised the shape convenient for mounting | wearing on the outer peripheral surface with respect to the rolling element which rolls on a cam surface.
According to a fourth aspect of the present invention, in the first aspect, the buffer member is interposed between the opposing surfaces disposed in the front and rear directions in the rotational direction of the drive shaft between the first hinge portion and the second hinge portion. Therefore, even when the cam plate rattles back and forth in the rotation direction of the drive shaft, the shocking collision between the first hinge portion and the second hinge portion can be mitigated by the buffering action of the buffer member.

  According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the shock-absorbing member is mounted on one opposing surface of the first hinge portion and the second hinge portion, and from the opposing surface to the other. It protrudes toward the facing surface. A receiving groove into which the buffer member enters is formed on the other facing surface. Therefore, even when the cam plate rattles back and forth in the direction along the axis of the drive shaft, the impact collision between the first hinge portion and the second hinge portion can be mitigated by the buffering action of the buffer member. . Further, even when the cam plate rattles back and forth in the rotational direction of the drive shaft, the shocking collision between the first hinge portion and the second hinge portion can be mitigated by the buffering action of the buffer member.

  According to the first to fifth aspects of the present invention, even when the cam plate is loose, the shocking collision between the first hinge portion and the second hinge portion can be mitigated by the buffering action of the buffer member. it can. Therefore, it is possible to prevent the generation of abnormal noise and vibration from the variable capacity compressor due to the impact collision between the first hinge portion and the second hinge portion.

  Hereinafter, the first to fourth embodiments in which the present invention is embodied in a variable capacity compressor used in a refrigeration circuit of a vehicle air conditioner will be described. In the second to fourth embodiments, only differences from the first embodiment will be described, and the same or corresponding members will be denoted by the same reference numerals and description thereof will be omitted.

First Embodiment FIG. 1 is a longitudinal sectional view of a variable capacity compressor (hereinafter simply referred to as a compressor) 10. In FIG. 1, the left side is the front of the compressor 10, and the right side is the rear of the compressor 10. As shown in FIG. 1, the housing of the compressor 10 includes a cylinder block 11, a front housing 12 joined and fixed to the front end of the cylinder block 11, and a valve / port forming body 13 at the rear end of the cylinder block 11. And a rear housing 14 joined and fixed.

  A crank chamber 15 is defined between the cylinder block 11 and the front housing 12 in the housing. A drive shaft 16 is rotatably supported between the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15. The drive shaft 16 is operatively connected to an engine E that is a travel drive source of the vehicle. The drive shaft 16 receives power from the engine E and rotates about the axis T in the direction of arrow R.

  A lug plate 17 having a substantially disk shape is fixed to the drive shaft 16 in the crank chamber 15 so as to be integrally rotatable. A swash plate 18 as a cam plate is accommodated in the crank chamber 15. A drive shaft 16 is inserted into an insertion hole 18 a formed in the center of the swash plate 18. A hinge mechanism 19 is interposed between the lug plate 17 and the swash plate 18. The swash plate 18 can be rotated synchronously with the lug plate 17 and the drive shaft 16 by the hinge connection with the lug plate 17 via the hinge mechanism 19 and the support of the drive shaft 16 via the insertion hole 18a. The drive shaft 16 can be tilted with respect to the drive shaft 16 while being slid in the axis T direction.

  In the cylinder block 11, a plurality of cylinder bores 27 (only one is shown in the drawing) are formed around the axis T of the drive shaft 16 so as to penetrate in the front-rear direction (left-right direction in the drawing) at equal angular intervals. The single-headed piston 28 is accommodated in each cylinder bore 27 so as to be movable in the front-rear direction. The front and rear openings of the cylinder bore 27 are closed by the front end face of the valve / port forming body 13 and the piston 28, and a compression chamber 29 whose volume changes in accordance with the movement of the piston 28 in the front and rear direction is defined in the cylinder bore 27. Has been.

  The piston 28 is anchored to the outer periphery of the swash plate 18 via a pair of shoes 30. The rotational movement of the swash plate 18 is converted into the reciprocating movement of the piston 28 via the shoe 30. A suction chamber 31 and a discharge chamber 40 are defined between the valve / port forming body 13 and the rear housing 14 in the housing. The valve / port forming body 13 is formed with a suction port 32 and a suction valve 33 so as to be positioned between the compression chamber 29 and the suction chamber 31. The valve / port forming body 13 is formed with a discharge port 34 and a discharge valve 35 so as to be positioned between the compression chamber 29 and the discharge chamber 40.

  The refrigerant in the suction chamber 31 (carbon dioxide is used in the present embodiment) moves from the top dead center position to the bottom dead center position side of each piston 28, thereby causing a suction port 32 and a suction valve 33. Through the compression chamber 29. The refrigerant gas sucked into the compression chamber 29 is compressed to a predetermined pressure by the movement from the bottom dead center position to the top dead center position side of the piston 28, and enters the discharge chamber 40 through the discharge port 34 and the discharge valve 35. And discharged.

  In the housing of the compressor 10, an extraction passage 36, an air supply passage 37, and a control valve 38 are provided. The extraction passage 36 connects the crank chamber 15 and the suction chamber 31. The air supply passage 37 connects the discharge chamber 40 and the crank chamber 15. In the middle of the air supply passage 37, a known control valve 38 made of an electromagnetic valve is disposed.

  By adjusting the opening of the control valve 38, the amount of high-pressure discharge gas introduced into the crank chamber 15 via the air supply passage 37 and the amount of gas discharged from the crank chamber 15 via the bleed passage 36 are obtained. The balance is controlled and the internal pressure of the crank chamber 15 is determined. In accordance with the change in the internal pressure of the crank chamber 15, the difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 29 via the piston 28 is changed, and the inclination angle of the swash plate 18 (perpendicular to the axis T of the drive shaft 16). As a result, the stroke of the piston 28, that is, the discharge capacity of the compressor 10 is adjusted.

  For example, when the internal pressure of the crank chamber 15 is reduced, the inclination angle of the swash plate 18 is increased, the stroke of the piston 28 is increased, and the discharge capacity of the compressor 10 is increased. Conversely, when the internal pressure of the crank chamber 15 increases, the inclination angle of the swash plate 18 decreases, the stroke of the piston 28 decreases, and the discharge capacity of the compressor 10 decreases.

Next, the hinge mechanism 19 will be described.
First, the second hinge portion 19B on the swash plate 18 side constituting the hinge mechanism 19 will be described. As shown in FIGS. 1 to 3, the end surface of the swash plate 18 on the lug plate 17 side corresponds to the top dead center. In the vicinity of the position TDC (the part where the piston 28 is positioned at the top dead center in the swash plate 18), the support portion 20 protrudes toward the lug plate 17 side. An insertion hole 20a is passed through the support portion 20 in a direction orthogonal to the protruding direction. A link pin 21 is press-fitted and fixed in the insertion hole 20 a of the support portion 20. The link pin 21 has a first end portion (right end portion in FIG. 3) 21a protruding from the support portion 20 to the rear side in the rotation direction R, and a second end portion (left end portion in FIG. 3) 21b supported. Projecting from the portion 20 to the front side in the rotational direction R.

  A cylindrical roller 22 is rotatably supported on the second end portion 21b of the link pin 21 by using the second end portion 21b as a shaft portion. The roller 22 is a second guide protrusion and forms a rolling element. A circlip 26 that prevents the roller 22 from coming off from the link pin 21 is attached to the tip of the second end 21 b of the link pin 21 that protrudes from the roller 22. A spherical portion 23 as a first guide projection is integrally provided at the first end 21 a of the link pin 21. The roller 22 and the spherical portion 23 are disposed across the top dead center corresponding position TDC of the swash plate 18 in the rotation direction R.

  Next, the first hinge portion 19A on the lug plate 17 side that constitutes the hinge mechanism 19 will be described. On the end surface on the swash plate 18 side of the lug plate 17, a long groove-shaped first cam portion that guides the spherical portion 23 is described. 24 is provided. The inner surface 24 a of the first cam portion 24 is inclined so as to be separated from the disk portion of the lug plate 17 as it approaches the drive shaft 16.

  On the end surface of the lug plate 17 on the swash plate 18 side, a second cam portion 25 having a cam surface 25 a for guiding the roller 22 is provided on the front side in the rotation direction R with respect to the first cam portion 24. . The cam surface 25 a of the second cam portion 25 is inclined so as to be separated from the disk portion of the lug plate 17 as it approaches the drive shaft 16. And the 2nd cam part 25 does not have the wall which faces the roller 22 except the part which provides the cam surface 25a. That is, it can be said that the 2nd cam part 25 has the shape which open | releases the roller 22 to the front side of the rotation direction R, and the swash plate 18 side.

  In the hinge mechanism 19, the rotational force is transmitted from the lug plate 17 to the swash plate 18 from the inner surface 24 a of the first cam portion 24 to the spherical surface 23 a of the spherical portion 23 (particularly in the vicinity of the tip). A compression reaction force (the center of load of the reaction force is indicated by an arrow X) biased on the swash plate 18 via the piston 28 is received mainly by the cam surface 25a of the second cam portion 25 via the roller 22. .

  The tilting of the swash plate 18 when the discharge capacity of the compressor 10 is increased is changed while the roller 22 slides while rolling on the cam surface 25a of the second cam portion 25 in a direction away from the drive shaft 16. The spherical portion 23 is guided by sliding on the inner surface 24 a of the first cam portion 24 in a direction away from the drive shaft 16. On the contrary, when the discharge capacity of the compressor 10 is decreased, the swash plate 18 tilts while the roller 22 rolls on the cam surface 25a of the second cam portion 25 in a direction approaching the drive shaft 16. At the same time, the spherical portion 23 is guided by sliding on the inner surface 24 a of the first cam portion 24 in the contact / separation direction approaching the drive shaft 16.

  As shown in FIGS. 3 and 4, in the roller 22, an annular holding groove 22b is formed in the circumferential direction at the center of the outer peripheral surface 22a. An annular rubber ring 41 as a buffer member is fitted into the holding groove 22b. That is, a part of the rubber ring 41 is between the opposing surfaces (the outer peripheral surface of the roller 22) disposed between the first hinge portion 19 </ b> A and the second hinge portion 19 </ b> B in the front-rear direction in the direction along the axis T of the drive shaft 16. 22a and a part of the cam surface 25a of the second cam portion 25).

  The outer diameter of the rubber ring 41 is larger than the outer diameter of the roller 22 in a state where the compression reaction force X is not applied to the roller 22. When a certain amount of compression reaction force X acts on the roller 22, a part of the rubber ring 41 is crushed, and the outer peripheral surface 22a of the roller 22 and the cam surface 25a of the second cam portion 25 are brought together. Direct contact.

  Here, for example, when the discharge capacity of the compressor 10 is low and the compression reaction force X acting on the swash plate 18 via the piston 28 is small, the roller 22 against the cam surface 25a of the second cam portion 25 The pressing force is reduced. The 2nd cam part 25 does not have the wall which faces the roller 22 except the part which provides the cam surface 25a. That is, the 2nd cam part 25 does not have a wall which contact-controls the displacement of the roller 22 to the direction away from the cam surface 25a. Further, due to manufacturing tolerances and the like, the front and rear in the direction along the axis T of the drive shaft 16 is between the spherical portion 23 of the link pin 21 and the inner surface 24a of the first cam portion 24 into which the spherical portion 23 is fitted. There is a gap to.

  Accordingly, when the drive shaft 16 is affected by the torque fluctuation of the engine E and the compressor 10 is affected by the running vibration of the vehicle while the discharge capacity of the compressor 10 is low, the swash plate 18 is moved to the lug plate. 17 is rattling. Specifically, the swash plate 18 rattles the lug plate 17 back and forth in the direction along the axis T of the drive shaft 16, and the roller 22 is centered on the spherical portion 23 of the link pin 21 and the cam surface 25a. In the direction of contact and separation (indicated by an arrow Z in FIG. 4), the lug plate 17 is largely rattled (turned).

  However, a rubber ring 41 is mounted on the outer peripheral surface 22 a of the roller 22. Accordingly, when the roller 22 is about to come into contact with the cam surface 25a when the swash plate 18 is rattled, the rubber ring 41 exerts a buffering action due to its elastic deformation, and the roller 22 and the cam surface 25a. Shocking collisions with the Therefore, it is possible to prevent the generation of abnormal noise and vibration from the compressor 10 due to the impact collision between the roller 22 and the cam surface 25a.

The first embodiment having the above-described configuration also has the following effects.
(1) The hinge mechanism 19 transmits the rotational force from the lug plate 17 to the swash plate 18 from the first cam portion 24 to the spherical portion 23, and also compresses the swash plate 18 via the piston 28. The reaction force is configured to be received by the cam surface 25 a of the second cam portion 25 mainly through the roller 22. In the compressor 10 that employs the hinge mechanism 19 having such a configuration, the swash plate 18 has a large backlash in the direction in which the roller 22 contacts and separates from the cam surface 25a with the spherical portion 23 of the link pin 21 as the center. Easy to turn (turn). In other words, in the compressor 10 that employs the hinge mechanism 19 that tends to increase the backlash of the swash plate 18, the first hinge portion 19 </ b> A and the second hinge portion are assembled by incorporating a buffer member (rubber ring 41) into the hinge mechanism 19. It can be said that the ability to alleviate the impact collision with 19B is particularly effective in preventing the generation of abnormal noise and vibration from the compressor 10.

(2) The annular rubber ring 41 is a buffer member having a shape that is convenient for mounting on the outer peripheral surface 22a of the roller 22 rolling on the cam surface 25a.
Second Embodiment As shown in FIG. 5, in the hinge mechanism 19, a housing groove 25 b is formed on the cam surface 25 a of the second cam portion 25. The housing groove 25 b is in a single line extending along the rolling direction of the roller 22. In the rubber ring 41 of the roller 22, a part of the outer peripheral portion that protrudes from the outer peripheral surface 22 a toward the cam surface 25 a enters the accommodation groove 25 b.

  The depth of the receiving groove 25b is such that the rubber ring 41 is compressed and deformed when the outer peripheral surface 22a of the roller 22 is in contact with the cam surface 25a. It is set shallow so that the rubber ring 41 can mitigate the collision. Therefore, when the roller 22 rolls on the cam surface 25a, the rubber ring 41 rolls while partially compressing and deforming the inner surface of the receiving groove 25b.

In the present embodiment, the same operational effects as in the first embodiment are obtained. In addition, the following effects can be obtained.
That is, in the hinge mechanism 19, due to manufacturing tolerances and the like, between the spherical portion 23 of the link pin 21 and the inner surface 24a of the first cam portion 24 into which the spherical portion 23 is fitted (see FIG. 3), There is a gap before and after the rotation direction R. Therefore, for example, when the drive shaft 16 is affected by the torque fluctuation of the engine E or the compressor 10 is affected by the running vibration of the vehicle while the discharge capacity of the compressor 10 is low, The swash plate 18 will be largely rattled.

  However, the rubber ring 41 of the roller 22 enters the receiving groove 25 b of the second cam portion 25. Accordingly, when the roller 22 moves relative to the cam surface 25a in the front-rear direction of the rotation direction R due to the backlash of the swash plate 18 in the front-rear direction of the rotation direction R, the rubber that has entered the receiving groove 25b. The ring 41 has a buffering action due to its elastic deformation. Therefore, the impact of the spherical portion 23 of the link pin 21 against the inner surface 24a of the first cam portion 24 can be reduced. As a result, it is possible to prevent the compressor 10 from generating abnormal noise and vibration due to the impact collision between the spherical portion 23 and the inner surface 24a of the first cam portion 24.

Third Embodiment As shown in FIG. 6, a holding recess 23 b is formed at the tip of the spherical portion 23. A columnar rubber piece 45 as a buffer member is fitted in the holding recess 23b. That is, the rubber piece 45 is interposed in a region located before and after the rotation direction R between the opposing surfaces of the spherical surface 23 a of the spherical portion 23 and the inner surface 24 a of the first cam portion 24. Also in the present embodiment, the effect similar to that of the second embodiment (the spherical portion 23 and the first cam portion when the swash plate 18 rattles back and forth in the rotational direction R) is obtained by the buffer action by the elastic deformation of the rubber piece 45. 24) to mitigate a shocking collision with the inner surface 24a of 24.

  The configuration of this embodiment (attaching the rubber piece 45 to the spherical portion 23 of the hinge mechanism 19) is the same as the configuration of the first or second embodiment (attaching the rubber ring 41 to the roller 22 of the hinge mechanism 19). The rubber ring 41 may be deleted from the first or second embodiment and applied to the hinge mechanism 19 alone.

Fourth Embodiment As shown in FIG. 7, between the side surface 20b facing the rear side in the rotation direction R in the support portion 20 and the side surface 24b heading the front side in the rotation direction R in the first cam portion 24, A buffer spring 48 made of a coil spring as a buffer member is interposed. In other words, the buffer spring 48 is located between the opposing surfaces arranged in the front and rear in the rotation direction R between the first hinge portion 19A and the second hinge portion 19B (the side surface 20b of the support portion 20 and the side surface of the first cam portion 24). 24b).

  Also in this embodiment, the effect similar to that of the second embodiment (the spherical portion 23 and the first cam when the swash plate 18 rattles back and forth in the rotational direction R) is obtained by the buffer action by the elastic deformation of the buffer spring 48. The impact collision with the inner surface 24a of the portion 24 is mitigated).

  In the present embodiment, the buffer spring 48 is disposed between the side surface 20 b of the support portion 20 and the side surface 24 b of the first cam portion 24 so as to surround the first end portion 21 a of the link pin 21. . In other words, the first end 21 a of the link pin 21 is inserted through the space of the spiral center portion of the buffer spring 48. Therefore, the arrangement of the buffer spring 48 between the side surface 20 b of the support portion 20 and the side surface 24 b of the first cam portion 24 is stabilized by the support by the first end portion 21 a of the link pin 21. Therefore, the buffering action by the buffer spring 48 can be stably achieved. Further, the space at the center of the spiral of the buffer spring 48 is effectively used as the space for disposing the first end 21 a of the link pin 21, so that the buffer spring 48 can be disposed in a space-saving manner and hence the hinge mechanism 19 can be downsized. it can.

  The configuration of the present embodiment (the hinge mechanism 19 includes the buffer spring 48) is the same as the configuration of the first to third embodiments (the hinge mechanism 19 includes the rubber ring 41 and / or the rubber piece 45). The rubber ring 41 and / or the rubber piece 45 may be deleted from the first to third embodiments and applied to the hinge mechanism 19.

For example, the following embodiments can be implemented without departing from the spirit of the present invention.
-Change the rubber ring 41 of the said 1st or 2nd embodiment into the ring member which consists of spring materials, for example. That is, instead of the rubber ring 41, for example, an annular spring material formed by connecting one end of a coil spring to the other end is used. That is, the rubber ring 41 is changed to an elastic member having a ring shape other than rubber.

Change the rubber piece 45 of the third embodiment to a spring material such as a coil spring or a leaf spring. That is, changing the rubber piece 45 to an elastic member other than rubber.
○ The buffer spring 48 of the fourth embodiment is changed to, for example, a rubber buffer member. That is, the buffer spring 48 is changed to an elastic member other than the spring.

The buffer member may be other than an elastic member as long as it has a buffering action.
○ The third embodiment is changed, and the rubber pieces 45 are positioned in front and rear in the direction along the axis T of the drive shaft 16 between the opposing surfaces of the spherical surface 23a of the spherical portion 23 and the inner surface 24a of the first cam portion 24. To intervene in the area to be. In this way, the inner surface of the spherical portion 23 and the first cam portion 24 when the swash plate 18 rattles back and forth in the direction along the axis T of the drive shaft 16 due to the buffering action caused by the elastic deformation of the rubber piece 45. Impact collision with 24a can be mitigated.

  In the third embodiment, an accommodation groove similar to that of the second embodiment for accommodating the tip of the rubber piece 45 is formed on the inner surface 24a of the first cam portion 24. The accommodation groove is formed in a single line extending along the moving direction of the spherical portion 23. In this way, impact collision between the spherical portion 23 and the inner surface 24a of the first cam portion 24 when the swash plate 18 rattles back and forth in the direction along the axis T of the drive shaft 16 can be reduced. Can do.

  ○ The spherical portion 23 is rotatably supported by the link pin 21, and the spherical portion 23 is slid on the inner surface 24 a of the first cam portion 24 when the inclination angle of the swash plate 18 is changed. That is, let the first guide protrusion be a rolling element.

  In each of the above embodiments, the rolling element (roller 22) is used as the second guide protrusion of the hinge mechanism 19. This is changed, and the second guide protrusion is fixed to the support portion so as not to rotate.

  ○ Apply the present invention to a variable capacity compressor provided with a hinge mechanism having the same configuration as that of Patent Document 1. That is, the hinge mechanism is constituted by a pair of spherical portions that are one of the first hinge portion and the second hinge portion, and a pair of guide grooves that are the other of the first hinge portion and the second hinge portion.

○ The present invention is embodied in a wobble type variable capacity compressor.
○ The present invention is embodied in a variable capacity compressor used in a refrigeration circuit employing a chlorofluorocarbon refrigerant.

A technical idea that can be grasped from the embodiment or another example will be described.
(1) The variable capacity compressor according to claim 3, wherein the cam plate is rotatable about the spherical portion and in a direction in which the rolling element contacts and separates from the cam surface.

  (2) One of the first hinge part and the second hinge part is provided with a rolling element, and the other is provided with a cam surface on which the rolling element is rolled. The variable capacity compressor according to claim 1, wherein the buffer member having an annular shape is mounted on an outer peripheral surface partially facing the outer peripheral surface.

The longitudinal cross-sectional view which shows the variable capacity compressor in 1st Embodiment. The side view which shows the hinge mechanism vicinity. The top view which shows the hinge mechanism vicinity. The expanded sectional view of the contact part vicinity of a roller and a cam surface. The expanded sectional view of the contact part vicinity of the roller and cam surface in 2nd Embodiment. The enlarged view of the engagement part vicinity of the 1st cam part and spherical part in 3rd Embodiment. The enlarged view of the engaging part vicinity of the 1st cam part and spherical part in 4th Embodiment. The top view of the hinge mechanism vicinity which shows a prior art.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Variable capacity compressor, 11 ... Cylinder block which comprises housing, 12 ... Similarly front housing, 14 ... Similarly rear housing, 16 ... Drive shaft, 17 ... Lug plate, 18 ... Swash plate as cam plate, 19 ... Hinge Mechanism (A ... first hinge part, B ... second hinge part), 20 ... support part constituting the second hinge part (b ... side surface (which forms the opposing surface in the fourth embodiment)), 21 ... same link pin (B: second end portion as a shaft portion), 22: roller as a rolling element (a ... outer peripheral surface as an opposing surface), 23 ... a spherical portion (a ... spherical surface (in the third embodiment, forming an opposing surface) ), 24... First cam portion constituting the first hinge portion (a... Inner surface (forms a facing surface in the third embodiment), b... Side surface (forms a facing surface in the fourth embodiment)), 25. 2nd cam part (a ... as an opposing surface B, housing groove (second embodiment), 27 ... cylinder bore, 28 ... piston, 41 ... rubber ring as buffer member, 45 ... rubber piece as buffer member (third embodiment), 48 ... buffer Buffer spring (fourth embodiment) as a member, R: rotational direction of drive shaft, T: axis of drive shaft.

Claims (5)

A cylinder bore is formed in the housing and a drive shaft is rotatably supported. A lug plate is connected to the drive shaft so as to be integrally rotatable, and a cam plate is supported to be tiltable. A hinge mechanism is interposed between the cam plate, the hinge mechanism including a first hinge portion provided on the lug plate and a second hinge provided on the cam plate and connected to the first hinge portion. And a piston accommodated in the cylinder bore so as to reciprocate is moored to the cam plate, and the rotation of the drive shaft is transmitted to the cam plate via the lug plate and the hinge mechanism. As a result, the piston is reciprocated to compress the gas, and the cam plate is moved by the guidance of the hinge mechanism. By changing the oblique angle, the changeable variable displacement compressor discharge capacity stroke of the piston is changed,
A variable capacity compressor characterized in that a buffer member is interposed between opposing surfaces of the first hinge part and the second hinge part.   The said buffer member is interposed between the said opposing surfaces arrange | positioned in the direction along the axis line of the said drive shaft between the said 1st hinge part and the said 2nd hinge part. Variable capacity compressor. The second hinge part includes a support part protruding from an end face of the cam plate on the lug plate side, a spherical part protruding from the support part at the rear side in the rotation direction of the drive shaft, and the support A rolling element that is rotatably supported by a shaft portion that projects from the front side in the rotational direction of the drive shaft in the portion,
The first hinge portion is provided on an end surface of the lug plate on the cam plate side, and is provided on the same end surface as the first cam portion, and a long groove-shaped first cam portion that guides the spherical portion, A second cam portion having a cam surface on which the rolling element rolls,
The variable capacity compressor according to claim 2, wherein the buffer member having an annular shape is attached to an outer peripheral surface of the rolling element that partially faces the cam surface.   2. The variable capacitor according to claim 1, wherein the buffer member is interposed between the opposing surfaces arranged before and after the drive shaft in the rotation direction between the first hinge portion and the second hinge portion. Compressor.   The buffer member is mounted on one opposing surface of the first hinge portion and the second hinge portion, and protrudes from the opposing surface toward the other opposing surface, and on the other opposing surface The variable capacity compressor according to any one of claims 1 to 4, wherein an accommodation groove into which the buffer member enters is formed.

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