JP2006009627A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor having a hinge mechanism for suppressing the rattling of a cam plate with respect to a lug plate. <P>SOLUTION: In a variable displacement compressor, a lug plate 17 and a swash plate 18 are connected to each other through the medium of a hinge mechanism 19, in which a limiting surface 43 is provided to a first hinge part 19A on the lug plate 17 side and a limited surface 44 opposed to the limiting surface 43 is provided to a second hinge part 19B on the swash plate 18 side. A spring 48 is interposed between the first hinge part 19A and the second hinge part 19B, and biases the first hinge part 19A and the second hinge part 19B in the direction where the limiting surface 43 and the limited surface 44 approach each other. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a variable capacity compressor that changes a discharge capacity by changing an inclination angle of a cam plate.

  For example, in a refrigerant circulation circuit of a vehicle air conditioner, a variable capacity compressor is generally used as a refrigerant compressor. As the variable capacity compressor, there is one constituted by a drive shaft, a lug plate, a swash plate, a hinge mechanism, a piston, and the like. Each component is generally connected as follows. The drive shaft is connected to the output shaft of the engine so as to be rotationally driven by the engine of the vehicle. A lug plate is fixed to the drive shaft so as to be integrally rotatable. A swash plate is supported on the drive shaft. The inclination angle of the swash plate with respect to the drive shaft can be changed. A hinge mechanism is interposed between the lug plate and the swash plate. A piston is connected to the swash plate.

  Since the variable displacement compressor has the above-described configuration, the rotational force of the drive shaft is transmitted to the swash plate via the lug plate and the hinge mechanism, and the piston is reciprocated to compress the refrigerant gas. Is called. Further, the stroke of the piston can be changed by changing the inclination angle of the swash plate by the guidance of the hinge mechanism, whereby the discharge capacity of the variable capacity compressor can be changed.

  In addition, as a variable capacity compressor, a clutch is not provided in the power transmission mechanism between the engine and the drive shaft, and the power from the engine is always transmitted (equipped with a clutchless mechanism). Exists. That is, in the clutchless type variable capacity compressor, the drive shaft is always driven to rotate by the engine when the engine is in operation. Therefore, the vehicle air conditioner minimizes the discharge capacity of the variable capacity compressor and stops the refrigerant circulation in the refrigerant circulation circuit when the cooling is unnecessary. In order to ensure the refrigerant circulation stop of the refrigerant circulation circuit, the clutchless type variable displacement compressor has a minimum discharge capacity of zero or near zero compared to a variable displacement compressor provided with a clutch in the power transmission mechanism, for example. Is set to a very low value.

  As a hinge mechanism used for a variable capacity compressor, for example, a conventional technique as disclosed in Patent Document 1 has been proposed. As shown in FIG. 16, in the hinge mechanism according to this prior art, 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. Further, in this hinge mechanism, a guide groove 102a for guiding each spherical portion 103a is formed on the end surface of the lug plate 102 on the swash plate 101 side.

In the hinge mechanism having such a configuration, the transmission of the rotational force from the lug plate 102 to the swash plate 101 is similarly performed from the inner surface of the guide groove 102a located on the rear side (right side in the drawing) of the rotational direction R of the drive shaft. This is performed to the spherical portion 103a located on the rear side in the rotation direction R. The inclination angle of the swash plate 101 is changed by being guided by the spherical portions 103a of the link pins 103 sliding on the inner surfaces of the respective guide grooves 102a.
JP 2001-289159 A (FIG. 3)

  However, in the hinge mechanism shown in FIG. 16, a gap exists between the spherical portion 103a of the link pin 103 and the inner surface of the guide groove 102a due to manufacturing tolerances and the like. This gap allows relative movement of the swash plate 101 with respect to the lug plate 102 within a certain range (for example, relative rotation or sliding movement in the direction along the axis of the drive shaft).

  Here, for example, when the discharge capacity of the variable capacity compressor is low, the compression reaction force X acting on the swash plate 101 via the piston is small, and the pressing force of the spherical portion 103a against the inner surface of the guide groove 102a is small. Become. In this state, for example, when the drive shaft is affected by the torque fluctuation of the engine or the variable displacement compressor is affected by the running vibration of the vehicle, the gap between the link pin 103 and the guide groove 102a described above. May cause the swash plate 101 to vibrate relative to the lug plate 102 (so-called rattling). The rattling of the swash plate 101 in this way causes, for example, a problem that the spherical portion 103a collides with the inner surface of the guide groove 102a, or noise, vibration, or the like is further generated by this collision. It was pointed out.

  In particular, in a clutchless type variable capacity compressor, when the discharge capacity is minimized, the compression reaction force X acting on the swash plate 101 is extremely small, and therefore there is a very high possibility that the swash plate 101 will rattle. It was high.

  An object of the present invention is to provide a variable displacement compressor having a hinge mechanism that prevents the cam plate from rattling with respect to the lug plate.

  In order to achieve the above object, in the variable capacity compressor according to the present invention, the first hinge portion on the lug plate side is provided with a restriction surface, and the second hinge portion on the cam plate side is restricted to face the restriction surface. A spring is interposed between the first hinge portion and the second hinge portion, and the spring moves the first hinge portion and the second hinge portion in a direction in which the regulating surface and the regulated surface are close to each other. It is characterized by energizing.

  Therefore, the urging force of the spring can bring about a state where the regulating surface and the regulated surface are pressed against each other (at least both surfaces are almost always in contact). Therefore, relative movement of the first hinge portion and the second hinge portion in the direction in which the regulating surface and the regulated surface are separated can be suppressed. Therefore, for example, rattling of the cam plate with respect to the lug plate in the direction in which the regulating surface and the regulated surface come in contact with or away from each other can be suppressed.

  In the variable capacity compressor, the spring is supported by one of the first hinge portion and the second hinge portion, and the one hinge portion is provided with a spring seat surface on which the spring abuts, and A movable member is provided, and the other hinge portion is provided with a spring biasing force receiving surface that receives the biasing force of the spring, and the movable member is disposed between the spring seat surface and the spring biasing force receiving surface. The lug plate or the cam plate provided with one hinge portion is supported so as to be movable toward and away from the spring seat surface. The spring is interposed between the movable member and the spring seat surface. The variable capacity compressor may bias the movable member toward the direction close to the spring biasing force receiving surface.

  That is, the spring is in contact with the spring biasing force receiving surface of the other hinge part via the movable member. Therefore, when the cam plate changes the inclination angle with respect to the drive shaft, the spring does not slide directly with the spring biasing force receiving surface of the other hinge portion. Therefore, it becomes possible to suppress the wear and deterioration of the spring accompanying the change of the inclination angle of the cam plate. In addition, the movable member that does not need to have a spring action has, for example, better sliding contact with the spring biasing force receiving surface compared to a configuration in which the spring is in direct contact with the spring biasing force receiving surface. Easy to design. Therefore, the cam plate inclination angle can be changed smoothly, and the capacity controllability of the variable capacity compressor can be improved.

  In the variable capacity compressor, the regulating surface and the regulated surface, and the spring seat surface and the spring biasing force receiving surface are arranged opposite to each other in the front and rear in the rotation direction of the drive shaft, and the cam plate is changed from the lug plate by the hinge mechanism. The variable capacity compressor may be configured such that the transmission of the rotational force is performed between the spring seat surface and the spring biasing force receiving surface via a movable member and a spring.

  In this way, for example, even if the spring seat surface and the spring biasing force receiving surface are inclined with respect to each other from the initial state (from the set state) for some reason, the spring is deformed following the inclination. Therefore, the movable member supported by the spring can be brought into contact with the spring biasing force receiving surface in a stable posture. Therefore, transmission of the rotational force from the lug plate to the cam plate can be performed stably, and wear and deterioration of the spring biasing force receiving surface and the movable member due to the transmission of the rotational force can be suppressed. Further, since the contact posture of the movable member with respect to the spring biasing force receiving surface is stabilized, the contact sliding property between the spring biasing force receiving surface and the movable member when the cam plate changes the inclination angle with respect to the drive shaft. Can be good. Therefore, for example, it is possible to suppress wear and deterioration of the spring biasing force receiving surface and the movable member.

  In the variable capacity compressor, a link pin is provided at one hinge portion, a movable member is supported at a first end portion of the link pin, and a cam plate is connected to a second end portion of the link pin via a piston. It is good also as a variable capacity compressor provided with the compression reaction force transmission part for transmitting the compression reaction force which acts to the said lug plate.

  If it does in this way, a hinge mechanism does not need to be provided with the member for supporting a movable member, and the member for providing a compression reaction force transmission part separately. Therefore, for example, the configuration of the hinge mechanism can be simplified.

  In the variable capacity compressor, the movable member forms a columnar shape and abuts against a spring biasing force receiving surface at an end surface thereof. When the cam plate changes the inclination angle of the other hinge portion, Variable displacement compression with a cam surface on which the outer peripheral surface slides, and a movable member supported by a lug plate or cam plate provided with one hinge so as to be rotatable about its own cylinder center axis It is good also as a machine.

  In this way, when the cam plate changes the tilt angle with respect to the drive shaft, the movable member rolls on the cam surface, so that the resistance generated between the outer peripheral surface of the movable member and the cam surface is referred to as rolling resistance. can do. Therefore, for example, it is possible to smoothly change the inclination angle of the cam plate. Therefore, for example, the capacity controllability of the variable capacity compressor can be improved, and wear and deterioration of the movable member due to sliding with the cam surface can be reduced.

  According to the said invention, it can suppress that a cam plate rattles with respect to a lug plate. Therefore, for example, it is possible to suppress the generation of abnormal noise and vibration from the variable capacity compressor due to the backlash of the cam plate.

  Hereinafter, the variable capacity compressor of the present invention will be described in detail as a variable capacity compressor used in a refrigerant circulation circuit of a vehicle air conditioner. First, the variable capacity compressor according to the first embodiment will be described.

First Embodiment FIG. 3 is a longitudinal sectional view of a variable capacity compressor (hereinafter simply referred to as “compressor”) 10. As shown in FIG. 3, the housing of the compressor 10 has a cylinder block 11, a front housing 12 joined and fixed to one end (the left end in the drawing) of the cylinder block 11, and a valve at the other end (the right end in the drawing) of the cylinder block 11. A rear housing 14 that is joined and fixed via a port forming body 13 is provided. In FIG. 3, the left side (front housing 12 side) is appropriately described as the front side of the compressor 10, and the right side (rear housing 14 side) is appropriately described as the rear side of the compressor 10.

  A space defined by the inner wall of the front housing 12 and the cylinder block 11 constitutes a crank chamber 15. One end (front end) of the drive shaft 16 is rotatably supported by the front housing 12, and the other end (rear end) is rotatably supported by the cylinder block 11. The drive shaft 16 extends in the front-rear direction of the compressor 10 in the housing of the compressor 10 and is disposed so as to pass through the crank chamber 15.

  The drive shaft 16 is connected to an output shaft (not shown) of an engine (internal combustion engine) E, which is a travel drive source of the vehicle, via a power transmission mechanism PT. The power transmission mechanism PT may be a clutch mechanism (for example, an electromagnetic clutch) capable of selecting transmission / cutoff of power by electric control from the outside, or a constant transmission type clutchless without such a clutch mechanism. It may be a mechanism (for example, a belt / pulley combination). In the present embodiment, a power transmission mechanism PT including a clutchless mechanism is employed. Therefore, when the engine E is in operation, the drive shaft 16 always receives power from the engine E and rotates about the axis T in the direction of the 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. The drive shaft 16 passes through a substantially central portion of the lug plate 17. In the crank chamber 15, a swash plate 18 as a cam plate, which is substantially disk-shaped, is accommodated. The drive shaft 16 is inserted through an insertion hole 18a formed at a substantially central portion of the swash plate 18. The lug plate 17 and the swash plate 18 are connected via a hinge mechanism 19.

  As described above, the swash plate 18 is coupled to the lug plate 17 via the hinge mechanism 19 and is supported by the drive shaft 16 via the insertion hole 18a, and thus is synchronized with the lug plate 17 and the drive shaft 16. Rotate. Further, the swash plate 18 changes the inclination angle with respect to the drive shaft 16 by the fact that the hinge mechanism 19 can exert a hinge action and that the swash plate 18 can move in the direction along the axis T of the drive shaft 16. be able to. The inclination angle of the swash plate 18 with respect to the drive shaft 16 is specifically an angle formed between the swash plate 18 and a virtual plane (not shown) orthogonal to the axis T of the drive shaft 16.

  In the cylinder block 11, a plurality of cylinder bores 27 (only one is shown in the drawing) are formed at substantially equal angular intervals around the axis T of the drive shaft 16. Each cylinder bore 27 penetrates from the end surface (front end surface) on the front housing 12 side to the end surface (rear end surface) on the rear housing 14 side in the cylinder block 11. A part of the single-headed piston 28 (a rear end portion (an end portion on the rear housing 14 side) and a so-called head portion) is accommodated in each cylinder bore 27. Each piston 28 is held by a cylinder bore 27, that is, the cylinder block 11 so as to be slidable in a direction in which the piston 28 is in contact with or separated from the front end surface (end surface on the cylinder block 11 side) of the valve / port forming body 13.

  Both openings of the cylinder bore 27 are closed by the front end face of the valve / port forming body 13 and the piston 28. As described above, there is a closed space in the cylinder bore 27, and this space is particularly referred to as a compression chamber 29. The compression chamber 29 is a closed and partitioned space in the cylinder bore 27 as described above, and its volume changes according to the relative sliding movement of the piston 28 with respect to the cylinder bore 27.

  Each piston 28 is connected to the outer periphery of the swash plate 18 via a pair of hemispherical shoes 30. The pair of shoes 30 has the same curvature center point. The rotational movement of the swash plate 18 is converted into reciprocating movement of the piston 28 (repetition of reciprocating sliding movement) via the shoe 30. That is, when the swash plate 18 is inclined with respect to the axis T of the drive shaft 16, the center of curvature of the shoe 30 held by each piston 28 is the valve / port forming body as the swash plate 18 rotates. The distance from the front end face of 13 varies. Therefore, the piston 28 connected to the swash plate 18 via the shoe 30 also reciprocates in the direction of coming into contact with and separating from the front end face of the valve / port forming body 13, that is, the direction of changing the volume of the compression chamber 29.

  The suction chamber 31 and the discharge chamber 40 are partitioned by the rear end surface of the valve / port forming body 13 and the inner side (inner surface) of the rear housing 14. The valve / port forming body 13 includes a suction port 32 for connecting the compression chamber 29 and the suction chamber 31 so that refrigerant can flow, and a suction valve 33 for opening and closing the suction port 32. Corresponding to the cylinder bores 27 are provided. Further, the valve / port forming body 13 has a discharge port 34 for connecting the compression chamber 29 and the discharge chamber 40 so that the refrigerant can flow, and a discharge valve 35 for opening and closing the discharge port 34. , Provided corresponding to each cylinder bore 27.

  The refrigerant (for example, carbon dioxide) gas in the suction chamber 31 is moved from the top dead center position to the bottom dead center position side of each piston 28 through the suction port 32 and the open suction valve 33 in the open state. Inhaled. The refrigerant gas sucked into the compression chamber 29 is compressed to a predetermined pressure by the movement from the bottom dead center position of the piston 28 to the top dead center position side, and then the discharge port 34 and the discharge valve 35 in the open state are opened. Through the discharge chamber 40.

  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 is a passage that connects the crank chamber 15 and the suction chamber 31 so that the refrigerant can flow. The air supply passage 37 is a passage that connects the discharge chamber 40 and the crank chamber 15 so that refrigerant can flow. A known control valve 38 having an electromagnetic drive configuration, that is, a configuration that can be electrically controlled from the outside, is disposed in the supply passage 37.

  The control valve 38 adjusts the degree of opening so that the amount of refrigerant gas (high-pressure refrigerant gas) in the discharge chamber 40 introduced into the crank chamber 15 via the air supply passage 37 and the crank chamber via the bleed passage 36. The internal pressure of the crank chamber 15 is determined by controlling the balance with the amount of refrigerant gas led out from 15 to the suction chamber 31. 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 according to the internal pressure of the crank chamber 15 thus changed, and the force by which the piston 28 pushes the swash plate 18 Changes, and the inclination angle of the swash plate 18 is changed. As a result, the stroke of the piston 28, that is, the discharge capacity of the compressor 10 is adjusted. Specifically, the discharge capacity of the compressor 10 is controlled as follows.

  When the internal pressure of the crank chamber 15 is reduced, the inclination angle of the swash plate 18 increases, the stroke of the piston 28 increases, and the discharge capacity of the compressor 10 increases. When the internal pressure of the crank chamber 15 is increased, 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. The minimum inclination angle of the swash plate 18 is set to zero or a very small angle near zero (for example, about 0 ° to about 3 °).

Next, the hinge mechanism 19 will be described.
First, the 2nd hinge part 19B by the side of the swash plate 18 which is one hinge part is demonstrated.
As shown in FIGS. 1 to 4, a support portion 20 protrudes toward the lug plate 17 near the top dead center corresponding position TDC on the surface of the swash plate 18 on the lug plate 17 side. The top dead center corresponding position TDC is a portion of the swash plate 18 where the piston 28 is positioned at the top dead center. The top dead center corresponding position TDC can be rephrased as “the center point of curvature of the shoe 30 connecting the piston 28 located at the top dead center to the swash plate 18”.

  As shown in FIGS. 1 and 2, the support portion 20 is provided with a plane (side surface) substantially parallel to the axis T, and the plane forms a spring seat surface 42. The spring seat surface 42 is disposed toward the rear side in the rotation direction R. The support portion 20 is formed in a direction perpendicular to the protruding direction (a plane substantially parallel to the plane on which the spring seat surface 42 exists) (in a plane formed by the lug plate 17 side surface of the swash plate 18 or a straight line on a virtual plane). The insertion hole 20a is penetrated. Therefore, one end of the insertion hole 20 a is provided on the spring seat surface 42.

  A cylindrical link pin 21 is inserted into the insertion hole 20 a by using a method such as press fitting, and thus the link pin 21 is fixed to the support portion 20. One end portion (first end portion) 21 a of the link pin 21 protrudes from the spring seat surface 42 to the outside of the support portion 20. The other end (second end) of the link pin 21 is denoted as “21b”. Further, the end portion is a portion including the end surface, and at least a portion not including the other end portion, generally, a portion of the end surface side portion from the central portion (in this example, the link pin 21). The part or the whole thing.

  A cylindrical roller 22 is rotatably supported on the outer peripheral surface of the second end 21 b of the link pin 21. A bearing 46 is interposed between the inner peripheral surface of the roller 22 and the outer peripheral surface of the second end portion 21 b in the link pin 21. As the bearing 46, a plain bearing (sliding bearing) is used. The bearing 46 makes the rotation of the roller 22 relative to the link pin 21 smooth. A circlip 26 is attached to a portion of the second end 21 b of the link pin 21 that protrudes from the roller 22. The circlip 26 prevents the roller 22 from coming off from the second end 21 b side of the link pin 21.

  In the link pin 21, a movable cylinder 23 as a movable member is supported on the outside of the first end 21 a so as to be able to slide and rotate with respect to the link pin 21 (with a margin of movement). ing. The movable cylinder 23 has a cylindrical hole into which the link pin 21 is inserted, and a bottom (lid) is provided so that the link pin 21 does not penetrate. That is, the movable cylinder 23 has a bottomed (covered) cylindrical shape as a columnar shape. In the support portion 20, the movable cylinder 23 and the roller 22 are disposed across the top dead center corresponding position TDC of the swash plate 18 in the rotational direction R. The movable cylinder 23 has an outer bottom surface 23a (a surface orthogonal to the central axis P of the link pin 21 and a surface not facing the link pin 21 / a bottom surface provided on the outer side) in the rotational direction R. It is arranged in a state facing the rear side. That is, the movable cylinder 23 is provided so as to cover the end surface of the first end 21a of the link pin 21 and part or all of the first end 21a.

  As described above, the movable cylinder 23 is rotatable about the central axis P of the link pin 21 on the first end 21 a side of the link pin 21. That is, the movable cylinder 23 is rotatably supported by the swash plate 18 provided with the second hinge portion 19B via the link pin 21. In addition, the movable cylinder 23 is slidable on the link pin 21 in a direction along the center axis P of the link pin 21 which is its own cylinder center axis. In other words, the movable cylinder 23 is supported by the swash plate 18 provided with the second hinge portion 19 </ b> B so as to be movable toward and away from the spring seat surface 42 via the link pin 21.

As described above, the second hinge portion 19B includes the support portion 20, the link pin 21, the roller 22, the movable cylinder 23, and the like.
Next, the 1st hinge part 19A by the side of the lug plate 17 which is the other hinge part is demonstrated.

  As shown in FIGS. 1 and 4, on the surface of the lug plate 17 on the swash plate 18 side, the movable cylinder 23 is guided (moved in a direction substantially parallel to the central axis P of the link pin 21 (sliding). The first cam portion 24 is provided so as to project. A first cam surface 24a serving as a cam surface is provided on a portion of the base portion of the first cam portion 24 (the connection portion with the lug plate 17 and the vicinity thereof) near the support portion 20 (the side where the link pin 21 is disposed). Is provided toward the swash plate 18 side. A part of the outer peripheral surface 23b of the movable cylinder 23 is in contact with the first cam surface 24a. The first cam surface 24 a is inclined so as to approach the cylinder block 11 as it approaches the drive shaft 16.

  A surface of the first cam portion 24 on the link pin 21 side (a planar side surface facing the front side in the rotation direction R) constitutes a spring biasing force receiving surface 41. The spring biasing force receiving surface 41 and the spring seat surface 42 of the support portion 20 face each other before and after the rotation direction R. An outer bottom surface 23 a of the movable cylinder 23 is in contact with the spring biasing force receiving surface 41.

  On the swash plate 18 side of the lug plate 17, a second cam portion 25 for guiding the roller 22 (for enabling movement (sliding) in a direction substantially parallel to the central axis P of the link pin 21). Is protruding. A surface of the second cam portion 25 facing the swash plate 18 is a second cam surface 25a. A part of the outer peripheral surface 22a of the roller 22 is in contact with the second cam surface 25a. The second cam surface 25 a is inclined so as to approach the cylinder block 11 as it approaches the drive shaft 16.

As described above, the first hinge portion 19A includes the first cam portion 24, the second cam portion 25, and the like.
Next, a connection configuration between the first hinge portion 19A and the second hinge portion 19B will be described.

  At the tip of the support portion 20, a surface forming projection 20 b is projected toward the lug plate 17 at a portion near the roller 22. In the surface forming protrusion 20 b, the side surface (preferably planar) of the second cam portion 25 forms a regulated surface 44. In the second cam portion 25, a side surface (preferably planar) on the support portion 20 side forms a regulating surface 43. That is, the regulating surface 43 and the regulated surface 44 are arranged so as to face each other before and after the rotation direction R. Therefore, the regulating surface 43 and the regulated surface 44 and the above-described spring biasing force receiving surface 41 and the spring seat surface 42 have the following relationship.

  For example, it is assumed that the swash plate 18 rotates relative to the lug plate 17 in the direction opposite to the rotation direction R from the state of FIG. Then, the spring biasing force receiving surface 41 and the spring seat surface 42 are close to each other, and the regulating surface 43 and the regulated surface 44 are separated from each other. It is assumed that the swash plate 18 rotates relative to the lug plate 17 in the rotation direction R from this state. As a result, the spring biasing force receiving surface 41 and the spring seat surface 42 are separated from each other, and the regulating surface 43 and the regulated surface 44 are brought into close contact with each other. When the regulating surface 43 and the regulated surface 44 are in contact with each other, the relative rotation of the lug plate 17 and the swash plate 18 in one direction (the direction in which the regulating surface 43 and the regulated surface 44 are close to each other) is regulated. .

  Now, a spring 48 is interposed between the first hinge part 19A and the second hinge part 19B. More specifically, as shown in FIG. 1 and FIG. 2, the spring 48 is a spring between the spring biasing force receiving surface 41 of the first hinge portion 19A and the spring seat surface 42 of the second hinge portion 19B. It is disposed between the seat surface 42 and the movable cylinder 23. The spring 48 is formed of a coil spring that is wound around the link pin 21 and is disposed so that the end portions thereof are in contact with the spring seat surface 42 and the opening end surface 23 c of the movable cylinder 23. The opening end surface 23c of the movable cylinder 23 is a surface facing the spring seat surface 42, and more specifically, a portion of the surface excluding the hole into which the first end portion 21a of the link pin 21 is inserted. . Thus, the spring 48 is supported by the second hinge portion 19B. That is, when the swash plate 18 changes the inclination angle, the spring 48 moves in a direction in which the spring 48 moves toward and away from the drive shaft 16 together with the second hinge portion 19B.

  The spring 48 has a function of pressing the movable cylinder 23 against the spring biasing force receiving surface 41. In other words, the spring 48 has a function of pushing (urging) the movable cylinder 23 in a direction in which it is separated from the spring seat surface 42. That is, the spring 48 works (biases) so as to separate the movable cylinder 23 and the support portion 20 along the central axis P of the link pin 21. Therefore, the working force (biasing force) of the spring 48 finally acts (acts) on the spring biasing force receiving surface 41 and the spring seat surface 42. As a result, the spring 48 urges the first hinge portion 19A and the second hinge portion 19B in a direction in which the regulating surface 43 and the regulated surface 44 are close to each other (pushing each other).

Next, the operation of the hinge mechanism 19 will be described.
In the hinge mechanism 19, the rotational force is transmitted from the lug plate 17 to the swash plate 18 from the spring biasing force receiving surface 41 of the first cam portion 24 to the outer bottom surface 23 a of the movable cylinder 23. The rotational force transmitted to the movable cylinder 23 is transmitted from the opening end surface 23 c of the movable cylinder 23 to the spring seat surface 42 of the support portion 20 via the spring 48. The swash plate 18 receives a compression reaction force (in FIG. 1, the load center of the compression reaction force is indicated by an arrow X for easy understanding) via a piston 28 in the compression stroke. (A force (compression reaction force) having a different magnitude is applied to each part connected to the piston 28). The compression reaction force X acting on the swash plate 18 is mainly received by the second cam surface 25a of the second cam portion 25 via the roller 22 which is a compression reaction force transmission portion.

  In order to increase the discharge capacity of the compressor 10, it is necessary to increase the inclination angle of the swash plate 18. In this case, the inclination of the swash plate 18 is caused by the movement of the roller 22 and the movable cylinder 23 as follows. An increase in angle is guided. The roller 22 slides (rolls) on the second cam surface 25a in a direction away from the drive shaft 16. The movable cylinder 23 slides (rolls) on the first cam surface 24a in a direction away from the drive shaft 16. By operating in this way, an increase in the inclination angle of the swash plate 18 is guided.

  In order to reduce the discharge capacity of the compressor 10, it is necessary to reduce the inclination angle of the swash plate 18. In this case, the roller 22 and the movable cylinder 23 move as follows, so that the swash plate 18 A decrease in tilt angle is guided. The roller 22 slides (rolls) on the second cam surface 25a in a direction approaching the drive shaft 16. Further, the movable cylinder 23 slides (rolls) on the first cam surface 24a in a direction approaching the drive shaft 16. By operating in this way, a decrease in the inclination angle of the swash plate 18 is guided.

  Here, 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 is pressed against the second cam surface 25a based on the compression reaction force X. The power is reduced. In this state, 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, the swash plate 18 tends to rattle against the lug plate 17. In particular, when stopping the refrigerant circulation in the refrigerant circulation circuit, such as when cooling is not required, the control valve 38 is externally controlled to keep the discharge capacity of the compressor 10 to a minimum, so the compression reaction force X becomes extremely small. For the reasons described above, the swash plate 18 is extremely susceptible to rattling.

  However, the spring 48 interposed between the first hinge portion 19A and the second hinge portion 19B moves the first hinge portion 19A and the second hinge portion 19B in the direction in which the restricting surface 43 and the restricted surface 44 are close to each other. By energizing, the regulation surface 43 and the regulated surface 44 are brought into a state of pressing against each other. Therefore, even if the swash plate 18 is loose, the state in which the regulating surface 43 and the regulated surface 44 are pressed against each other by the urging force of the spring 48 can be maintained. In other words, the state in which the regulating surface 43 and the regulated surface 44 are pressed against each other is maintained by the urging force of the spring 48. In other words, the direction in which the regulating surface 43 and the regulated surface 44 are separated from each other and the regulating surface 43 and the regulated surface 44 are regulated. This means that the biasing force of the spring 48 prevents the swash plate 18 from moving relative to the lug plate 17 in the direction in which the surface 44 slides. Therefore, the swash plate 18 rattles in the direction in which the regulating surface 43 and the regulated surface 44 come into contact with or separate from the lug plate 17, that is, in the front-rear direction of the rotation direction R, or It is possible to prevent rattling in the sliding direction, for example, the front-rear direction in the direction along the axis T of the drive shaft 16, or to make these rattling extremely small.

  In addition, when the discharge capacity of the compressor 10 is high, the rotational force required to drive the compressor 10 increases. In the hinge mechanism 19, the spring 48 may be compressed and deformed between the spring biasing force receiving surface 41 and the spring seat surface 42 by the action of this large rotational force. When the spring 48 is compressed and deformed, the swash plate 18 rotates relative to the lug plate 17 in the direction opposite to the rotation direction R, and the regulating surface 43 and the regulated surface 44 are separated from each other.

  However, when the discharge capacity of the compressor 10 is high, the compression reaction force X acting on the swash plate 18 via the piston 28 increases. Therefore, the pressing force of the roller 22 against the second cam surface 25a based on the large compression reaction force X is large. Therefore, the swash plate 18 hardly rattles against the lug plate 17 even if 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. .

The compressor 10 having the above configuration has the following effects, for example.
(1) In the hinge mechanism 19, a restriction surface 43 is provided on the first hinge portion 19A, and a restricted surface 44 opposite to the restriction surface 43 is provided on the second hinge portion 19B. In addition, a spring 48 is interposed between the first hinge portion 19A and the second hinge portion 19B, and the spring 48 moves in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. The 2 hinge part 19B is urged | biased. Therefore, as described above, the swash plate 18 can be prevented from rattling with respect to the lug plate 17, or the rattling can be made extremely minute. Therefore, generation | occurrence | production of the noise and the vibration from the compressor 10 resulting from the rattling of the swash plate 18 can be suppressed, for example.

  (2) The spring 48 is supported by the second hinge part (one hinge part) 19B. The spring 48 is in contact with the spring biasing force receiving surface 41 provided in the first hinge part (the other hinge part) 19 </ b> A via the movable cylinder (movable member) 23. The movable cylinder 23 is supported by the swash plate 18 provided with the second hinge portion 19 </ b> B so as to be movable in a direction in which it is in contact with and away from the spring seat surface 42. Therefore, when the swash plate 18 changes the inclination angle, the spring 48 does not slide directly with the spring biasing force receiving surface 41 of the first hinge portion 19A. Therefore, it is possible to prevent the spring 48 from being worn or deteriorated due to a change in the inclination angle of the swash plate 18.

  (3) Since the movable cylinder (movable member) 23 does not have to have a spring action, for example, compared to a configuration in which the spring is brought into direct contact with the spring biasing force receiving surface, the spring biasing force receiving surface is The design (for example, selection of a material and selection of a shape) which makes the contact slidability of this good is easy. Therefore, the inclination angle of the swash plate 18 can be changed smoothly, and the capacity controllability of the compressor 10 can be improved.

  (4) The rotational force transmitted from the lug plate 17 to the swash plate (cam plate) 18 by the hinge mechanism 19 is transmitted from the spring biasing force receiving surface 41 via the movable cylinder (movable member) 23 and the spring 48. To the seating surface 42. Therefore, for example, even when the spring biasing force receiving surface 41 and the spring seat surface 42 are inclined with each other for some reason, the movable cylinder 23 supported by the spring 48 is deformed by the follow-up deformation of the spring 48 according to this inclination. The spring biasing force receiving surface 41 can be brought into contact with the spring in a stable posture. Therefore, the transmission of the rotational force from the lug plate 17 to the swash plate 18 can be performed stably. Thereby, for example, it becomes possible to suppress wear and deterioration of the spring biasing force receiving surface 41 and the movable cylinder 23 due to the transmission of the rotational force. Further, since the contact posture of the movable cylinder 23 with respect to the spring biasing force receiving surface 41 is stabilized, the sliding contact between the spring biasing force receiving surface 41 and the movable cylinder 23 when the inclination angle of the swash plate 18 is changed. Therefore, it is possible to suppress wear and deterioration of the spring biasing force receiving surface 41 and the movable cylinder 23.

  (5) A roller (compression reaction force transmitting portion) 22 is provided at the second end 21 b of the link pin 21 opposite to the movable cylinder (movable member) 23. Therefore, the hinge mechanism 19 does not need to include a member for supporting the movable cylinder 23 and a member for providing the roller 22 separately. Therefore, for example, the configuration of the hinge mechanism 19 can be simplified.

  (6) The movable cylinder (movable member) 23 is rotatably supported by the link pin 21. Therefore, when the swash plate 18 changes the inclination angle, the movable cylinder 23 rolls on the first cam surface 24a of the first cam portion 24, so that the outer peripheral surface 23b of the movable cylinder 23 and the first cam surface 24a The resistance generated during the period can be set as rolling resistance. Therefore, the inclination angle of the swash plate 18 can be changed smoothly, and the capacity controllability of the compressor 10 can be improved. It is also possible to reduce wear and deterioration of the movable cylinder 23 due to sliding with the first cam surface 24a.

Second Embodiment FIG. 5 shows a compressor according to a second embodiment which is a modified example of the first embodiment. In the following, only differences from the compressor according to the first embodiment will be described, and the same, equivalent or similar members as those of the compressor according to the first embodiment will be denoted by the same reference numerals, and the description will be made. Omitted.

  In the compressor according to the second embodiment, the first cam surface 24a is deleted from the first cam portion 24 of the first hinge portion 19A in the compressor according to the first embodiment. The movable cylinder 23 is deleted from the second hinge part 19B. Further, the surface forming protrusion 20 b is deleted from the support portion 20. On the other hand, at the front end of the support portion 20, a planar side surface 20 c that faces the front side in the rotation direction R forms the regulated surface 44.

  In the link pin 21, a spherical portion 50 is provided at the tip of the first end 21a. A cam groove 52 is provided in the spring biasing force receiving surface 41 of the first cam portion 24. The change of the inclination angle of the swash plate 18 is guided by the spherical portion 50 of the link pin 21 sliding on the inner surface of the cam groove 52 in the direction of contact with and away from the drive shaft 16 (see FIG. 4). .

  A movable ring 51 as a movable member is interposed between the spring 48 and the spring biasing force receiving surface 41. The movable ring 51 is a thin plate and has an annular shape. The first end 21 a of the link pin 21 is inserted through the substantially central portion of the movable ring 51. In other words, the movable ring 51 is supported by the swash plate 18 so as to be slidable in a direction along the central axis P of the link pin 21, that is, in a direction in which the movable ring 51 contacts and separates from the spring seat surface 42 of the support portion 20.

  The spring 48 biases the movable ring 51 and the support portion 20 along the central axis P of the link pin 21 in a direction in which the movable ring 51 is close to the spring biasing force receiving surface 41 and away from the spring seat surface 42. Then, the biasing force is applied to the spring biasing force receiving surface 41 of the first hinge portion 19A and the spring seating surface 42 of the second hinge portion 19B. That is, the spring 48 biases the first hinge portion 19A and the second hinge portion 19B in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. Therefore, in particular, even when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, the state in which the regulating surface 43 and the regulated surface 44 are pressed against each other by the urging force of the spring 48 can be maintained. Further, rattling of the swash plate 18 can be suppressed.

The compressor having the above configuration has the same effects as (1) to (5) in the first embodiment. In addition, the following effects (7) can be obtained.
(7) The first end portion 21 a of the link pin 21 is provided with a spherical portion 50 that guides the change of the inclination angle of the swash plate 18, separately from the movable ring 51. Accordingly, when the swash plate 18 changes the inclination angle, the sliding between the movable ring 51 and the first hinge portion 19A is performed only between the end surface of the movable ring 51 and the spring biasing force receiving surface 41. Done. Therefore, the sliding environment of the movable ring 51 can be moderated, and a lighter thin plate-like member can be employed as the movable ring 51. The lightweight movable ring 51 contributes to the weight reduction of the compressor 10, and particularly contributes to the weight reduction of the rotating portion of the compressor 10 and can greatly reduce the power loss of the compressor 10.

Third Embodiment FIG. 6 shows a compressor according to a third embodiment which is a modification of the compressor according to the first embodiment. In the following description, only the differences from the compressor according to the first embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the first embodiment will be denoted by the same reference numerals. Omitted. Moreover, since the effect | action which suppresses the rattling of the swash plate 18 is the same as that of the compressor which concerns on 1st Embodiment, the description is also abbreviate | omitted.

  In the compressor according to the third embodiment, the roller 22 and the circlip 26 are deleted from the second hinge portion 19B as compared with the compressor according to the first embodiment. On the other hand, in the link pin 21, a cylindrical disc-shaped flange portion 53 is integrally formed at the tip of the second end portion 21 b. The link pin 21 is pushed forward in the insertion hole 20 a of the support portion 20 until the flange portion 53 comes into contact with the support portion 20. The second cam portion 25 is provided with a surface forming projection 55. The surface forming protrusion 55 is disposed at a position slightly shifted from the second cam surface 25a to the front side in the rotational direction R.

  The surface forming protrusion 20b is deleted from the support portion 20. The support portion 20 is disposed slightly shifted from the top dead center corresponding position TDC to the front side in the rotation direction R. A tip surface 20 d having a convex curved surface shape in the support portion 20 is in contact with the second cam surface 25 a of the second cam portion 25. Accordingly, the compression reaction force X (see FIG. 1) that acts on the swash plate 18 is mainly received by the second cam surface 25a of the second cam portion 25 via the tip surface 20d of the support portion 20. Further, the inclination angle of the swash plate 18 is changed by sliding the front end surface 20 d of the support portion 20 on the second cam surface 25 a of the second cam portion 25 in a direction in which the tip end surface 20 d contacts and separates from the drive shaft 16. Guided.

  In the flange portion 53 of the link pin 21, a planar end surface (a plane orthogonal to the central axis P of the link pin 21) that faces the front side in the rotation direction R forms the regulated surface 44. In the surface forming protrusion 55 of the second cam portion 25, a planar side surface that faces the rear side in the rotation direction R forms a restriction surface 43.

In the present embodiment configured as described above, the same effects as (1) to (4) and (6) in the first embodiment can be obtained. In addition, the effects described in (8) below are also achieved.
(8) The front end surface 20 d of the support portion 20 is in contact with the second cam surface 25 a of the second cam portion 25 and bears transmission of the compression reaction force X in the hinge mechanism 19. Therefore, the roller 22 can be deleted from the link pin 21, and for example, the number of parts constituting the hinge mechanism 19 can be reduced.

Fourth Embodiment FIG. 7 shows a compressor according to a fourth embodiment which is a modification of the compressor according to the third embodiment. In the following, only differences from the compressor according to the third embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the third embodiment will be denoted by the same reference numerals, and the description will be made. Omitted.

  In the compressor according to the fourth embodiment, the spring 48 is deleted from the second hinge portion 19B as compared with the compressor according to the third embodiment. The movable cylinder 23 is not given a role as a movable member. The movable cylinder 23 transmits the rotational force of the lug plate 17 to the swash plate 18 by the opening end surface 23c being in direct contact with the side surface 20e toward the rear side in the rotation direction R in the support portion 20. A side surface facing the rear side in the rotation direction R in the surface forming protrusion 55 forms a spring biasing force receiving surface 41. A flat side surface (a plane perpendicular to the central axis P of the link pin 21) 20 f toward the front side in the rotation direction R in the support portion 20 forms a spring seat surface 42. The outer bottom surface 23 a of the movable cylinder 23 forms a regulated surface 44. A side surface of the first cam portion 24 that faces the front side in the rotation direction R forms a restriction surface 43.

  The link pin 21 is inserted into the insertion hole 20a of the support portion 20 with a margin of movement. Therefore, the link pin 21 can be rotated with respect to the support portion 20 about the center axis P of the link pin 21 and can be slid in a direction along the center axis P of the link pin 21. The flange portion 53 of the link pin 21 forms a movable member. That is, the flange portion 53 is supported by the swash plate 18 so as to be movable in a direction in which the flange portion 53 is in contact with or separated from the spring seat surface 42.

  A spring 56 is interposed between the first hinge portion 19A and the second hinge portion 19B. The spring 56 is a disc spring. The spring 56 is disposed on the outer periphery of the second end portion 21 b of the link pin 21 between the flange portion 53 of the link pin 21 and the spring seat surface 42 of the support portion 20. That is, the end portions of the spring 56 are in contact with the flange portion 53 and the spring seat surface 42, respectively. Thus, the spring 56 is supported by the second hinge portion 19B. That is, when the swash plate 18 changes the inclination angle, the spring 56 moves in a direction in which the spring 56 moves toward and away from the drive shaft 16 (see FIG. 4) together with the second hinge portion 19B.

  The spring 56 biases the flange portion 53 in a direction close to the spring biasing force receiving surface 41 and away from the spring seating surface 42, and this biasing force is applied to the spring biasing force receiving surface 41 and the spring seating surface 42. To act on. That is, the spring 56 biases the first hinge portion 19A and the second hinge portion 19B in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. Therefore, in particular, even when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, the regulated surface 44 of the movable cylinder 23 and the regulating surface 43 of the first cam portion 24 are urged by the biasing force of the spring 56. Can be maintained, and the open end surface 23c of the movable cylinder 23 and the side surface 20e of the support portion 20 can be maintained in a pressed state. As a result, rattling of the swash plate 18 can be suppressed.

  As described above, the compressor having the above configuration has the same effects as (1) to (3) and (8) of the third embodiment in the compressor according to the first embodiment. In addition, the effect described in the following (9) is also achieved.

  (9) The spring 56 is a disc spring. The disc spring is easy to downsize in the direction along the central axis P of the link pin 21 as compared with, for example, a coil spring. The small spring 56 in the direction along the central axis P facilitates an increase in size in the direction along the central axis P of other members (such as the support portion 20 and the movable cylinder 23) in the hinge mechanism 19. For example, an increase in the size of the support portion 20 responsible for transmitting the compression reaction force X leads to an improvement in durability of the support portion 20. Further, the increase in the size of the movable cylinder 23 leads to an increase in the fitting distance with the link pin 21 that supports the movable cylinder 23, and the support of the movable cylinder 23 by the link pin 21 can be stabilized. Become.

Fifth Embodiment FIG. 8 shows a compressor according to a fifth embodiment, which is a modification of the compressor according to the fourth embodiment. In the following, only differences from the compressor according to the fourth embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the fourth embodiment will be denoted by the same reference numerals, and the description will be made. Omitted. Moreover, since the effect | action which suppresses the rattling of the swash plate 18 is the same as that of the compressor which concerns on 4th Embodiment, the description is also abbreviate | omitted.

  A bearing 57 that supports the link pin 21 is disposed in the insertion hole 20 a of the support portion 20. The bearing 57 is a plain bearing. The flange portion 53 of the link pin 21 has a large diameter and is elongated in the axial direction. A compression reaction force X (FIG. 1) acting on the swash plate 18 is caused by the outer peripheral surface 53a of the flange portion 53 but not the front end surface 20d of the support portion 20 being in contact with the second cam surface 25a as the cam surface. Is transmitted to the lug plate 17. When the swash plate 18 changes the inclination angle, the flange portion 53 is rolled while sliding on the second cam surface 25 a of the second cam portion 25.

  In the compressor according to this embodiment having the above-described configuration, the same effects as (1) to (3) and (9) of the fourth embodiment in the compressor according to the first embodiment are obtained. In addition, the following effects (10) and (11) are also achieved.

  (10) In the link pin 21, the outer peripheral surface 53 a of the flange portion 53 is in contact with the second cam surface 25 a of the second cam portion 25 and bears transmission of the compression reaction force X in the hinge mechanism 19. Therefore, the roller 22 can be deleted from the link pin 21. For this reason, for example, the number of parts which constitute hinge mechanism 19 can be reduced.

  (11) The link pin 21 is supported via the bearing 57 in the insertion hole 20 a of the support portion 20. Therefore, the link pin 21 can be smoothly rotated. Further, the link pin 21 can be smoothly slid. Thereby, for example, it becomes possible to suppress wear and deterioration due to sliding with the support portion 20 due to rotation and sliding movement of the link pin 21.

Sixth Embodiment FIG. 9 shows a compressor according to a sixth embodiment, which is a modification of the compressor according to the fifth embodiment. In the following, only differences from the compressor according to the fifth embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the fifth embodiment will be denoted by the same reference numerals, and the description will be made. Omitted.

  In the compressor according to the sixth embodiment, the flange 53 of the link pin 21 is not given a role as a movable member as compared with the compressor according to the fifth embodiment. On the other hand, an accommodation recess 58 is formed on the end surface of the flange portion 53 that faces the front side in the rotation direction R. Part of the spring 56 is housed in the housing recess 58 of the flange portion 53. Therefore, when the swash plate 18 changes the inclination angle, the spring 56 contacts and separates from the drive shaft 16 (see FIG. 4) together with the second hinge portion 19B while being held in the housing recess 58. Move in the direction.

  The spring 56 has an inner bottom surface 58a (a plane orthogonal to the central axis P of the link pin 21) 58a that faces the front side in the rotation direction R in the housing recess 58, and a plane that faces the rear side in the rotation direction R in the surface forming projection 55. Between the side surface 55a. That is, the ends of the springs 56 are in contact with the inner bottom surface 58a of the housing recess 58 and the side surface 55a of the surface forming projection 55, respectively. The spring 56 is firstly arranged in a direction in which the inner bottom surface 58a of the flange portion 53 (accommodating recess 58) and the side surface 55a of the surface forming projection 55 are separated, that is, in a direction in which the regulating surface 43 and the regulated surface 44 are close to each other. The hinge part 19A and the second hinge part 19B are biased.

  Therefore, in particular, even when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, the regulated surface 44 of the movable cylinder 23 and the regulating surface 43 of the first cam portion 24 are urged by the biasing force of the spring 56. Can be maintained in a state where they are pressed against each other. Further, it is possible to maintain a state where the opening end surface 23c of the movable cylinder 23 and the side surface 20e of the support portion 20 are pressed against each other. Thereby, the play of the swash plate 18 can be suppressed.

  The compressor according to the present embodiment having the above configuration includes (1) in the compressor according to the first embodiment, (9) in the compressor according to the fourth embodiment, and the compressor according to the fifth embodiment. The same effects as (10) and (11) are obtained.

FIG. 10 shows a compressor according to a seventh embodiment, which is a modification of the compressor according to the sixth embodiment. In the following, only differences from the compressor according to the sixth embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the sixth embodiment will be denoted by the same reference numerals, and the description will be made. Omitted. Moreover, since the effect | action which suppresses the rattling of the swash plate 18 is the same as that of the compressor which concerns on 6th Embodiment, the description is also abbreviate | omitted.

  In the compressor according to the seventh embodiment, the flange portion 53 is omitted from the link pin 21 as compared with the compressor according to the sixth embodiment. On the other hand, the front end surface 20 d of the support portion 20 is in contact with the second cam surface 25 a of the second cam portion 25. Accordingly, the compression reaction force X (see FIG. 1) that acts on the swash plate 18 is mainly received by the second cam surface 25a of the second cam portion 25 via the tip surface 20d of the support portion 20.

  Further, the bearing 57 is omitted from the support portion 20. On the other hand, the link pin 21 is press-fitted into the insertion hole 20 a of the support portion 20 and is fixed to the support portion 20. The spring 56 is interposed between the side surface 55a of the surface forming protrusion 55 and the side surface 20c facing the front side in the rotation direction R in the support portion 20. That is, the ends of the springs 56 are in contact with the side surface 20c of the support portion 20 and the side surface 55a of the surface forming projection 55, respectively. The second end 21 b of the link pin 21 is inserted through the center of the spring 56.

  The compressor according to the present embodiment having the above configuration includes the effect described in (1) above in the compressor according to the first embodiment, the effect described in (8) above in the compressor according to the third embodiment, and the first. The effect similar to the effect of (9) description in the compressor concerning 4 embodiment is produced.

Eighth Embodiment FIG. 11 shows a compressor according to an eighth embodiment, which is a modification of the compressor according to the fifth embodiment. In the following, only differences from the compressor according to the fifth embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the fifth embodiment will be denoted by the same reference numerals, and the description will be made. Omitted.

  In the compressor according to the eighth embodiment, the bearing 57 is omitted from the support portion 20 as compared with the compressor according to the fifth embodiment. The distal end surface 20d of the support portion 20 is in contact with the second cam surface 25a of the second cam portion 25 and carries the transmission of the compression reaction force X (see FIG. 1). On the other hand, the link pin 21 is press-fitted into the insertion hole 20 a and fixed to the support portion 20. The first end portion 21 a of the link pin 21 does not protrude from the support portion 20. Therefore, the side surface 20 c that faces the rear side in the rotation direction R at the tip of the support portion 20 forms a regulated surface 44 that abuts on the regulation surface 43 of the first cam portion 24.

  The bottom (lid) is removed from the movable cylinder 23 as the movable member. The member number “23a” indicating the outer bottom surface of the movable cylinder 23 indicates the other opening end face (first opening end face) of the movable cylinder 23. One opening end surface 23c is referred to as a “second opening end surface 23c”. The movable cylinder 23 is supported at the second end 21 b of the link pin 21 so as to be rotatable about its own central axis P and slidable in a direction along its own central axis P. A part of the outer peripheral surface 23b of the movable cylinder 23 is in contact with a second cam surface 25a as a cam surface. The flange portion 53 of the link pin 21 prevents the movable cylinder 23 from coming off from the second end portion 21b side of the link pin 21.

  The spring 56 is interposed between the second opening end surface 23 c facing the rear side in the rotation direction R in the movable cylinder 23 and the spring seat surface 42 of the support portion 20. That is, the end portions of the spring 56 are in contact with the second opening end surface 23 c of the movable cylinder 23 and the spring seat surface 42 of the support portion 20. The spring 56 urges the movable cylinder 23 in a direction close to the spring urging force receiving surface 41 and away from the spring seat surface 42, and the first opening end surface 23 a of the movable cylinder 23 is urged by the spring urging force receiving surface. 41, the biasing force is applied to the spring biasing force receiving surface 41 of the first hinge portion 19A and the spring seat surface 42 of the second hinge portion 19B. That is, the spring 48 biases the first hinge portion 19A and the second hinge portion 19B in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other.

  Therefore, in particular, even when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, the regulated surface 44 of the support portion 20 and the regulating surface 43 of the first cam portion 24 are caused by the biasing force of the spring 56. Can be maintained in a state where they are pressed against each other. Thereby, the play of the swash plate 18 can be suppressed.

  The compressor according to the present embodiment having the above-described configuration is the effect described in (1) to (3) in the compressor according to the first embodiment and the description (9) in the compressor according to the fourth embodiment. Has the same effect as the effect. In addition, the following effects (12) and (13) are also achieved.

  (12) The movable cylinder (movable member) 23 is rotatably supported by the link pin 21. Therefore, when the swash plate 18 changes the inclination angle, the movable cylinder 23 rolls on the second cam surface 25a of the second cam portion 25, so that the outer peripheral surface 23b of the movable cylinder 23 and the second cam surface 25a The resistance generated during the period can be set as rolling resistance. Therefore, the inclination angle of the swash plate 18 can be changed smoothly, and the capacity controllability of the compressor 10 can be improved. It is also possible to reduce wear and deterioration of the movable cylinder 23 due to sliding with the second cam surface 25a.

  (13) The front end surface 20 d of the support portion 20 is in contact with the first cam surface 24 a of the first cam portion 24 and bears transmission of the compression reaction force X in the hinge mechanism 19. Therefore, the roller 22 can be deleted from the link pin 21, and for example, the number of parts constituting the hinge mechanism 19 can be reduced.

Ninth Embodiment FIG. 12 shows a compressor according to a ninth embodiment which is a modification of the compressor according to the first embodiment. In the following, only differences from the compressor according to the first embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the first embodiment will be denoted by the same reference numerals, and description will be made. Omitted.

  In the compressor according to the ninth embodiment, the first cam portion 24, the second cam portion 25, and the like are deleted from the first hinge portion 19A of the hinge mechanism 19 as compared with the compressor according to the first embodiment. . Further, the support portion 20, the link pin 21, the roller 22, the movable cylinder 23, the spring 48, and the like are omitted from the second hinge portion 19B.

  The first hinge portion 19 </ b> A includes a first guide arm 61 and a second guide arm 62. The first guide arm 61 and the second guide arm 62 are arranged on the lug plate 17 before and after the rotation direction R. The second hinge portion 19B includes a guide protrusion 63 provided in the vicinity of the top dead center corresponding position TDC in the swash plate 18. The first guide arm 61 and the guide protrusion 63, and the second guide arm 62 and the guide protrusion 63 are connected via an intermediate member 64, respectively. The intermediate member 64 includes a base portion 65 disposed on the lug plate 17 side, and a first intermediate arm 66 and a second intermediate arm 67 that respectively extend from the base portion 65 toward the swash plate 18 side.

  A base 65 of the intermediate member 64 is disposed between the first guide arm 61 and the second guide arm 62 in the lug plate 17. An insertion hole 65 a passes through the base 65. A first link pin 68 is installed between the first guide arm 61 and the second guide arm 62. The intermediate member 64 is rotatably supported by the first guide arm 61 and the second guide arm 62 when the first link pin 68 is inserted into the insertion hole 65a of the base portion 65 with a margin of movement. Yes.

  A guide projection 63 of the swash plate 18 is disposed between the first intermediate arm 66 and the second intermediate arm 67 in the intermediate member 64. An insertion hole 66 a is penetrated through the first intermediate arm 66. An insertion hole 67 a is passed through the second intermediate arm 67. A second link pin 69 is supported on the guide protrusion 63. In the intermediate member 64, one end of the second link pin 69 moves in the insertion hole 66a of the first intermediate arm 66, and the other end of the second link pin 69 moves in the insertion hole 67a of the second intermediate arm 67. It is supported by the guide projection 63 so as to be rotatable.

  In the hinge mechanism 19, rotational force is transmitted from the lug plate 17 to the swash plate 18 from the first guide arm 61 located on the rear side (right side) in the rotation direction R in the drawing, the base portion 65 of the intermediate member 64, and the drawing. Is performed to the guide projection 63 via the first intermediate arm 66 located on the rear side in the rotation direction R. Further, the compression reaction force X (see FIG. 1) biased on the swash plate 18 is transmitted from the guide protrusion 63 via the second link pin 69, the intermediate member 64, and the first link pin 68. 61 and the second guide arm 62. The change of the inclination angle of the swash plate 18 is guided by the intermediate member 64 rotating with respect to the first guide arm 61, the second guide arm 62, and the guide projection 63, respectively.

  Here, the intermediate member 64 is grasped as a part of the first hinge portion 19 </ b> A when attention is paid to the integral connection relationship between the first guide arm 61 and the second guide arm 62 via the first link pin 68. be able to. Based on this grasp, in the present embodiment, in the first intermediate arm 66 of the intermediate member 64, a planar side surface (a plane perpendicular to the central axis of the second link pin 69) toward the front side in the rotation direction R is the restriction surface. 43. In addition, a planar side surface (a plane orthogonal to the central axis of the second link pin 69) that faces the rear side in the rotation direction R in the guide protrusion 63 forms the regulated surface 44.

  A spring 70 made of a disc spring is interposed between the intermediate member 64 (first hinge portion 19A) and the guide projection 63 (second hinge portion 19B). Specifically, the spring 70 has a planar side surface (a plane perpendicular to the central axis of the second link pin 69) 67 b toward the rear side in the rotation direction R in the second intermediate arm 67 and the rotation direction R in the guide protrusion 63. And a planar side surface (a plane orthogonal to the central axis of the second link pin 69) 63a. That is, the end of the spring 70 is in contact with the side surface 67 b of the second intermediate arm 67 and the side surface 63 a of the guide projection 63. A second link pin 69 is inserted through the center of the spring 70.

  The spring 70 biases the intermediate member 64 (first hinge part 19A) and the guide protrusion 63 (second hinge part 19B) in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. Therefore, especially when the discharge capacity of the compressor 10 is low, even if the guide protrusion 63 rattles the intermediate member 64, the regulating surface 43 of the intermediate member 64 and the guide protrusion are urged by the biasing force of the spring 70. It is possible to maintain a state where the 63 regulated surfaces 44 are pressed against each other. Therefore, rattling of the guide protrusion 63, that is, rattling of the swash plate 18 can be suppressed.

  On the other hand, the intermediate member 64 can be grasped as a part of the second hinge portion 19B by paying attention to the integral connection relationship with the guide protrusion 63 via the second link pin 69. Based on this grasp, in the present embodiment, a planar side surface (a plane perpendicular to the central axis of the first link pin 68) that faces the front side in the rotation direction R in the first guide arm 61 forms the regulation surface 43. . In addition, a planar side surface (a plane perpendicular to the central axis of the first link pin 68) toward the rear side in the rotation direction R in the base portion 65 of the intermediate member 64 forms the regulated surface 44.

  A spring 71 made of a disc spring is interposed between the second guide arm 62 (first hinge portion 19A) and the intermediate member 64 (second hinge portion 19B). Specifically, the spring 71 rotates at a planar side surface (a plane perpendicular to the central axis of the first link pin 68) 62a toward the rear side in the rotation direction R in the second guide arm 62 and the base 65 of the intermediate member 64. It is interposed between a planar side surface (a plane perpendicular to the central axis of the first link pin 68) 65b that faces the front side in the direction R. That is, the end portions of the spring 71 are in contact with the side surface 62a of the second guide arm 62 and the side surface 65b of the intermediate member 64, respectively. A first link pin 68 is inserted through the center of the spring 71.

  The spring 71 biases the second guide arm 62 (first hinge part 19A) and the intermediate member 64 (second hinge part 19B) in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. Therefore, especially when the discharge capacity of the compressor 10 is low, even if the intermediate member 64 rattles against the first guide arm 61 and the second guide arm 62, the first guide arm is biased by the biasing force of the spring 71. The state where the regulating surface 43 of 61 and the regulated surface 44 of the intermediate member 64 are pressed against each other can be maintained. Therefore, the play of the intermediate member 64, that is, the play of the swash plate 18 can be suppressed.

  In this embodiment having the above-described configuration, the same effect as the effect described in (1) in the compressor according to the first embodiment and the effect described in (9) in the compressor according to the fourth embodiment are achieved.

10th Embodiment FIG. 13 shows a compressor according to a 10th embodiment which is a modification of the compressor according to the first embodiment. In the following, only differences from the compressor according to the first embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the first embodiment will be denoted by the same reference numerals, and description will be made. Omitted.

  In the compressor according to the tenth embodiment, the first cam portion 24, the second cam portion 25, and the like are deleted from the first hinge portion 19A of the hinge mechanism 19 as compared with the compressor according to the first embodiment. . Further, the support portion 20, the link pin 21, the roller 22, the movable cylinder 23, the spring 48, and the like are omitted from the second hinge portion 19B.

  The first hinge portion 19A of the hinge mechanism 19 includes a first fixed arm 81 located on the rear side in the rotational direction R in the drawing, and a second fixed arm 82 located on the front side in the rotational direction R in the drawing. . The second hinge portion 19B includes a first movable arm 83 located on the rear side in the rotational direction R in the drawing and a second movable arm 84 located on the front side in the rotational direction R in the drawing. The distal end portion of the first movable arm 83 and the distal end portion of the second movable arm 84 are disposed between the first fixed arm 81 and the second fixed arm 82.

  In the first fixed arm 81, the front surface in the rotation direction R, that is, the planar side surface facing the first movable arm 83 forms the regulation surface 43. Further, in the first movable arm 83, the planar side surface facing the rear side in the rotation direction R, that is, the first fixed arm 81 side forms the regulated surface 44. Transmission of the rotational force from the lug plate 17 to the swash plate 18 is performed from the regulating surface 43 of the first fixed arm 81 to the regulated surface 44 of the first movable arm 83 that contacts the regulating surface 43.

  A first cam surface 81a is provided toward the swash plate 18 at a portion near the second fixed arm 82 in the base portion of the first fixed arm 81 (the connection portion with the lug plate 17 and the vicinity thereof). The tip surface 83a of the first movable arm 83 is in contact with the first cam surface 81a. A second cam surface 82 a is provided toward the swash plate 18 at a portion near the first fixed arm 81 in the base portion of the second fixed arm 82. The distal end surface 84a of the second movable arm 84 is in contact with the second cam surface 82a.

  Accordingly, the compression reaction force X (see FIG. 1) acting on the swash plate 18 is caused by the first cam surface 81a of the first fixed arm 81 via the distal end surface 83a of the first movable arm 83 and the second movable arm 84. Are received by the second cam surface 82a of the second fixed arm 82 through the distal end surface 84a. In changing the inclination angle of the swash plate 18, the tip surface 83 a of the first movable arm 83 is on the first cam surface 81 a of the first fixed arm 81, and the tip surface 84 a of the second movable arm 84 is the second fixed arm 82. The second cam surface 82a is guided by sliding in a direction in which the second cam surface 82a contacts and separates from the drive shaft 16 (see FIG. 4).

  An accommodation recess 86 is formed on a side surface of the second movable arm 84 that faces the front side in the rotation direction R. A part of the spring 87 made of a disc spring is housed in the housing recess 86. Therefore, when the swash plate 18 changes the inclination angle, the spring 87 moves in the direction of contact with and away from the drive shaft 16 together with the second hinge portion 19B while being held in the housing recess 86.

  The spring 87 has a planar inner bottom surface 86a that faces the front side in the rotational direction R in the housing recess 86 of the second movable arm 84, and a planar side surface 82b that faces the rear side in the rotational direction R in the second fixed arm 82. It is interposed between That is, the ends of the springs 87 are in contact with the inner bottom surface 86a of the second movable arm 84 (accommodating recess 86) and the side surface 82b of the second fixed arm 82, respectively. The spring 87 is moved in the direction in which the inner bottom surface 86a of the second movable arm 84 (accommodating recess 86) and the side surface 82b of the second fixed arm 82 are separated, that is, in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. The first hinge portion 19A and the second hinge portion 19B are biased.

  Therefore, especially when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, the regulated surface 44 of the swash plate 18 and the regulating surface 43 of the lug plate 17 are pushed by the biasing force of the spring 87. The fit can be maintained. Thereby, the play of the swash plate 18 can be suppressed.

The compressor according to the present embodiment having the above configuration has the same effects as (1) in the compressor according to the first embodiment and (9) in the compressor according to the fourth embodiment.
Eleventh Embodiment FIG. 14 shows a compressor according to an eleventh embodiment which is a modification of the compressor according to the tenth embodiment. In the following, only differences from the compressor according to the tenth embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the first embodiment will be denoted by the same reference numerals, and the description will be made. Omitted.

  Compared with the compressor according to the tenth embodiment, the compressor according to the eleventh embodiment has the spring 87 removed from the hinge mechanism 19 and the housing recess 86 from the second movable arm 84 of the second hinge portion 19B. Has been deleted. In the first movable arm 83, the planar side surface facing the front side in the rotation direction R, that is, the second movable arm 84 side forms a spring seat surface 42. In the second fixed arm 82, a side surface 82 b that faces the rear side in the rotational direction R, that is, the first fixed arm 81 side, forms a spring biasing force receiving surface 41.

  A movable member 88 is supported on the second movable arm 84. The movable member 88 has a large-diameter cylindrical portion 88a, a small-diameter cylindrical portion 88b, and a flange 88c that connects the small-diameter cylindrical portion 88b to the large-diameter cylindrical portion 88a along the central axis Q on the same central axis Q. It is connected to (the left-right direction of the drawing). An insertion hole 82c is passed through the distal end portion of the second movable arm 84 from the side surface located on the first movable arm 83 side to the side surface located on the second fixed arm 82 side. The large-diameter cylindrical portion 88a of the movable member 88 is inserted into the insertion hole 82c with a margin for movement. Therefore, the movable member 88 can rotate about the central axis Q of the movable member 88 with respect to the second movable arm 84 and can slide in the direction along the central axis Q of the movable member 88.

  The movable member 88 is disposed such that the small-diameter cylindrical portion 88b and the flange portion 88c are located between the first movable arm 83 and the second movable arm 84. Therefore, in the movable member 88, one end surface facing the front side in the rotation direction R, that is, the end surface 88 d of the large-diameter cylindrical portion 88 a is opposed to the spring biasing force receiving surface 41 of the second fixed arm 82. The large-diameter cylindrical portion 88 a (at least the end surface 88 d) of the movable member 88 protrudes from the insertion hole 82 c of the second movable arm 84 and is in contact with the spring biasing force receiving surface 41.

  A spring 89 is interposed between the first hinge part 19A and the second hinge part 19B. The spring 89 is a coil spring. A part of the spring 89 is wound around the outer periphery of the small-diameter cylindrical portion 88 b of the movable member 88 between the flange portion 88 c of the movable member 88 and the spring seat surface 42 of the first movable arm 83. The ends of the spring 89 are in contact with the flange portion 88 c of the movable member 88 and the spring seat surface 42 of the first movable arm 83. Thus, the spring 89 is supported by the second hinge portion 19B. That is, when the swash plate 18 changes the inclination angle, the spring 89 moves together with the second hinge portion 19B in a direction in contact with and away from the drive shaft 16 (see FIG. 4).

  The spring 89 urges the movable member 88 in a direction close to the spring biasing force receiving surface 41 and away from the spring seating surface 42, and this biasing force is applied to the spring biasing force receiving surface 41 and the spring seating surface 42. To act on. That is, the spring 89 biases the first hinge portion 19A and the second hinge portion 19B in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. Therefore, especially when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, the regulated surface 44 of the first movable arm 83 and the regulated surface of the first fixed arm 81 are urged by the biasing force of the spring 89. 43 can be kept in a pressed state, and the end surface 88d of the movable member 88 (large-diameter cylindrical portion 88a) and the spring biasing force receiving surface 41 of the second fixed arm 82 are kept in a pressed state. be able to. Thereby, the play of the swash plate 18 can be suppressed.

The compressor which concerns on this embodiment provided with the said structure has an effect similar to (1)-(3) in the compressor which concerns on 1st Embodiment.
FIG. 15 shows a compressor according to a twelfth embodiment, which is a modification of the compressor according to the tenth embodiment. In the following, only differences from the compressor according to the tenth embodiment will be described, and the same, equivalent or similar members as those in the compressor according to the first embodiment will be denoted by the same reference numerals, and the description will be made. Omitted.

  Compared with the compressor according to the tenth embodiment, the compressor according to the twelfth embodiment has the spring 87 removed from the hinge mechanism 19 and the housing recess 86 from the second movable arm 84 of the second hinge portion 19B. Has been deleted. Further, the first cam surface 81 a is deleted from the first fixed arm 81 of the first hinge portion 19 </ b> A, and the second cam surface 82 a is deleted from the second fixed arm 82.

  In the first hinge portion 19 </ b> A as one hinge portion, a link pin 90 is installed between the first fixed arm 81 and the second fixed arm 82. The link pin 90 is supported by the first fixed arm 81 and the second fixed arm 82 so as to be rotatable about its own central axis S and to be slidable in the direction along its own central axis S. A flange portion 90b is provided at an end portion of the link pin 90 on the first fixed arm 81 side. The flange portion 90b makes the sliding movement of the link pin 90 toward the second fixed arm 82 abut against the first fixed arm 81 (specifically, the side surface 81b facing the rear side in the rotation direction R in the first fixed arm 81). To regulate.

  In the second hinge portion 19 </ b> B as the other hinge portion, the distal end surface 83 a of the first movable arm 83 and the distal end surface 84 a of the second movable arm 84 are in contact with the outer peripheral surface 90 a of the link pin 90. Therefore, the compression reaction force X (see FIG. 1) acting on the swash plate 18 is caused by the outer peripheral surface 90a of the link pin 90 via the front end surface 83a of the first movable arm 83 and the front end surface 84a of the second movable arm 84. Accepted. The inclination angle of the swash plate 18 is changed by changing the tip surface 83a of the first movable arm 83 and the tip surface 84a of the second movable arm 84 on the outer peripheral surface 90a of the link pin 90 while the link pin 90 rotates. It is guided by sliding in the direction of contact with and away from the drive shaft 16 (see FIG. 4).

  In the link pin 90, a circlip 91 is mounted (fixed) between a position where the distal end surface 83a of the first movable arm 83 abuts and a position where the distal end surface 84a of the second movable arm 84 abuts. In the link pin 90, between the position where the tip end surface 83a of the first movable arm 83 abuts and the circlip 91, a thin ring-shaped movable ring 92 is supported with a margin of movement. . That is, the movable ring 92 is linked to the lug plate 17 and / or linked in the direction along the center axis S of the link pin 90 by the lug plate 17, that is, in the direction in which the movable ring 92 is in contact with or separated from the distal end of the first movable arm 83. A sliding movement relative to the pin 90 is supported.

  In the circlip 91, the end face toward the rear side in the rotation direction R, that is, toward the first fixed arm 81 forms the spring seat surface 42. At the front end portion of the first movable arm 83, the front side in the rotation direction R, that is, the side surface toward the second movable arm 84 side forms the spring biasing force receiving surface 41. A spring 95 made of a coil spring is wound around the outer periphery of the link pin 90 between the circlip 91 and the movable ring 92. The ends of the springs 95 are in contact with the spring seat surface 42 of the circlip 91 and the end surface of the movable ring 92 facing the spring seat surface 42. Thus, the spring 95 is supported by the first hinge portion 19A, that is, the lug plate 17.

  The spring 95 attaches the movable ring 92 and the circlip 91 (link pin 90) along the central axis S in a direction in which the movable ring 92 is close to the spring biasing force receiving surface 41 and away from the spring seat surface 42. The urging force is applied to the spring urging force receiving surface 41 and the spring seat surface 42. That is, the spring 95 biases the first hinge portion 19A and the second hinge portion 19B in the direction in which the regulating surface 43 and the regulated surface 44 are close to each other. Therefore, especially when the swash plate 18 is loose when the discharge capacity of the compressor 10 is low, it is possible to maintain the state where the regulating surface 43 and the regulated surface 44 are pressed against each other by the biasing force of the spring 95. Moreover, the state where the flange portion 90b of the link pin 90 and the side surface 81b of the first fixed arm 81 are pressed against each other can be maintained. As a result, rattling of the swash plate 18 can be suppressed.

The compressor which concerns on this embodiment provided with the said structure has an effect similar to (1)-(3) in the compressor which concerns on 1st Embodiment. In addition, the effect described in the following (14) is also achieved.
(14) The spring 95 and the movable ring (movable member) 92 are supported by the lug plate 17. Therefore, the swash plate 18 that does not include a spring or a movable member, that is, a heavy object in an eccentric position, is particularly effective in improving the rotation balance around the axis T of the drive shaft 16. If the rotation balance of the swash plate 18 becomes good, it is effective to cause, for example, deterioration of the capacity controllability of the compressor 10 and generation of abnormal noise and vibration due to the unbalance of rotation of the swash plate 18. Can be suppressed.

  The compressors according to the first to twelfth embodiments are merely examples of the present invention and can be modified without departing from the spirit of the present invention. For example, it is possible to modify as described below, and it is also possible to implement each modified example in an appropriate combination within a range that does not contradict each other.

  ○ Use a wave washer that has a shape that undulates in the circumferential direction and exhibits a spring action. The wave washer is easy to downsize in the direction along the central axis P of the link pin 21 as compared with, for example, a coil spring.

In the fifth embodiment and the sixth embodiment, the bearing 57 of the link pin 21 is changed to a rolling bearing such as a ball bearing or a roller bearing.
In the first embodiment and the second embodiment, the bearing 46 of the roller 22 is changed to a rolling bearing such as a ball bearing or a roller bearing.

  In the first embodiment and the third to eighth embodiments, a bearing for smoothly rotating the movable cylinder 23 is provided between the inner peripheral surface of the movable cylinder 23 and the outer peripheral surface of the link pin 21. Intervening. Examples of the bearing include a plain bearing (sliding bearing), and a rolling bearing such as a ball bearing or a roller bearing. A bearing that allows the movable cylinder 23 to slide is adopted as the bearing.

In the first embodiment and the third to eighth embodiments, the movable cylinder 23 is not rotatable with respect to the link pin 21.
In the first embodiment and the third to eighth embodiments, the movable cylinder 23 is formed in a cylindrical shape having both ends opened.

  In each of the above embodiments, the first hinge part having the same configuration as the second hinge part 19B is provided on the lug plate 17 side, and the second hinge part having the same structure as the first hinge part 19A is provided on the swash plate 18 side. To provide.

  ○ By using a spring having a strong spring force, even if the discharge capacity of the compressor 10 is maximum, even if the swash plate 18 rattles, the setting is such that the spring does not compress and deform. In other words, the regulating surface 43 and the regulated surface 44 The setting that does not cancel the state where the and press. In this way, rattling of the swash plate 18 can be reliably suppressed in the entire variable range of the discharge capacity in the compressor 10.

  In each of the above embodiments, the regulating surface 43 and the regulated surface 44, and the spring seat surface 42 and the spring biasing force receiving surface 41 are arranged so as to oppose each other in the front and rear direction along the axis T of the drive shaft 16. thing.

○ The present invention is embodied in other types of variable capacity compressors such as a wobble type.
○ The present invention is embodied in a variable capacity compressor other than a refrigerant compressor such as an air compressor.

The top view which shows the hinge mechanism vicinity in the variable capacity compressor of 1st Embodiment. FIG. 2 is an enlarged view of FIG. The longitudinal cross-sectional view which shows a variable capacity compressor. The side view which shows the hinge mechanism vicinity. The principal part expanded sectional view of the hinge mechanism vicinity in 2nd Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 3rd Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 4th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 5th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 6th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 7th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 8th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 9th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 10th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 11th Embodiment. The principal part expanded sectional view of the hinge mechanism vicinity in 12th Embodiment. The top view of the hinge mechanism vicinity in the variable capacity compressor of a prior art.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Variable capacity compressor, 16 ... Drive shaft, 17 ... Lug plate, 18 ... Swash plate as cam plate, 19 ... Hinge mechanism (A ... 1st hinge part, B ... 2nd hinge part), 21 ... Link pin (A ... first end, b ... second end), 22 ... roller as a compression reaction force transmitting portion, 23 ... movable cylinder (movable member in the first, third and eighth embodiments) (A ... outer bottom surface as an end face, b ... outer peripheral surface), 24a ... first cam surface (can be grasped as a cam surface in the first and third embodiments), 25a ... second cam surface (It can be grasped as a cam surface in the fifth embodiment and the eighth embodiment), 28 ... piston, 41 ... spring biasing force receiving surface, 42 ... spring seat surface, 43 ... regulating surface, 44 ... regulated surface, 48 ... spring, 51 ... movable ring as a movable member, 5 ... Flange portion (can be grasped as a movable member in the fourth and fifth embodiments), 56 ... spring, 70, 71 ... spring, 87 ... spring, 88 ... movable member, 89 ... spring, 92 ... as a movable member , Movable ring, 95... Spring, P... Center axis of the link pin, which is the center axis of the cylinder of the movable member, and R.

Claims (5)

A lug plate is coupled to the drive shaft so as to be integrally rotatable, a cam plate is supported on the drive shaft, the cam plate can change an inclination angle with respect to the drive shaft, and the lug plate and the cam plate A hinge mechanism is interposed therebetween, and the hinge mechanism has a first hinge part provided on the lug plate and a second hinge part provided on the cam plate and connected to the first hinge part. A piston is connected to the cam plate, and the rotational force of the drive shaft is transmitted to the cam plate via the lug plate and the hinge mechanism, so that the piston reciprocates to compress the gas. The stroke of the piston is changed by changing the inclination angle of the cam plate with respect to the drive shaft by the guide by the hinge mechanism. The variable displacement compressor output capacity is changed,
The first hinge part is provided with a restriction surface, the second hinge part is provided with a restricted surface opposite to the restriction surface, and a spring is provided between the first hinge part and the second hinge part. And the spring biases the first hinge part and the second hinge part in a direction in which the regulating surface and the regulated surface are close to each other. The spring is supported by one of the first hinge part and the second hinge part,
The one hinge part is provided with a spring seat surface against which the spring abuts and is provided with a movable member, and the other hinge part is provided with a spring biasing force receiving surface for receiving the biasing force of the spring. And
The movable member is disposed between the spring seat surface and the spring biasing force receiving surface, and is in contact with the spring seat surface by the lug plate or the cam plate provided with the one hinge portion. Supported so as to be movable in the direction of separation,
2. The variable capacity compression according to claim 1, wherein the spring is interposed between the movable member and the spring seat surface and biases the movable member toward a direction close to the spring biasing force receiving surface. Machine. The regulating surface and the regulated surface, and the spring seat surface and the spring biasing force receiving surface are arranged to face each other in the front-rear direction of the rotational direction of the drive shaft,
The transmission of the rotational force from the lug plate to the cam plate by the hinge mechanism is performed between the spring seat surface and the spring biasing force receiving surface via the movable member and the spring. The variable capacity compressor described in 1.   The one hinge part is provided with a link pin, the movable member is supported on the first end of the link pin, and the second end of the link pin is connected to the cam plate via the piston. The variable capacity compressor according to claim 3, wherein a compression reaction force transmission portion for transmitting an acting compression reaction force to the lug plate is provided.   The movable member has a columnar shape and abuts against the spring biasing force receiving surface at an end surface thereof, and the other hinge portion has an outer periphery of the movable member when the cam plate changes an inclination angle. A cam surface on which the surface slides is provided, and the movable member is supported by the lug plate or the cam plate provided with the one hinge portion so as to be rotatable about its own cylinder central axis. The variable capacity compressor according to claim 3 or 4.

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