JP2001123944A - Variable displacement type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain occurrence of striking noises and abnormal vibrations caused by collision by buffering the collision generated in each operation connecting portion inside a compressor. SOLUTION: In a guide hole 33 on a side of rotary supporting body 24 constituting a hinge mechanism 30, a first shock absorbing portion 60 is provided for buffering the collision of a spherical portion 34 of a guide pin 32 with respect to an inner peripheral surface 33a of the hinge mechanism 30. The first shock absorbing portion 60 comprises a tubular body 61 made of a metal forming the inner peripheral surface 33a of the guide hole 33, and an elastic body 62 for supporting the tubular body 61 with respect to the rotary supporting body 24. On the outside of the driving shaft 17 passes through a through-hole 29 of a swash plate 26, a second shock absorbing portion 63 is disposed for buffering collision of the inner peripheral surface 29a of the through-hole 29 with respect to the outer peripheral surface 17a of the driving shaft 17. The second shock absorbing portion 63 comprises a tubular body 64 constituting the outer peripheral surface 17a of the driving shaft 17, and an elastic body 65 for elastically supporting the tubular body 64.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a positive displacement, reciprocating variable displacement compressor.

[0002]

2. Description of the Related Art Conventionally, in a swash plate type (swash type) compressor, which is one type of a variable displacement compressor of a positive displacement type and a reciprocating type, a plurality of pistons form a shoe on a swash plate which is swung by rotation of a drive shaft. The pistons reciprocate with a stroke having a magnitude corresponding to the inclination angle of the swash plate with respect to the drive shaft. Then, the displacement of the compressor is changed by adjusting the inclination angle of the swash plate and changing the stroke of each piston.

[0003] The swash plate is connected to the drive shaft so as to be integrally rotatable and to be adjustable in inclination. To elaborate,
The swash plate adjusts the stroke by changing the bottom dead center position without changing the top dead center position of each piston, so that the axial top dead center position in the swing range of the swash plate does not change as much as possible. Operatively connected to the drive shaft.

As a connection structure for connecting the swash plate to the drive shaft as described above, for example, a connection structure proposed by the present applicant and employed in, for example, a variable displacement compressor disclosed in Japanese Patent Application Laid-Open No. Hei 7-91366. is there.

In this connection structure, as shown in FIG. 8, a swash plate 92 is fixed to a rotating support 91 fixed to a drive shaft 90.
Are operatively connected by a hinge mechanism 93. Further, in the swash plate 92, the inner peripheral surface 94 a of the through hole 94 through which the drive shaft 90 is inserted is in contact with the outer peripheral surface 90 a of the drive shaft 90.

The hinge mechanism 93 includes a pair of support arms 95 provided on the rotation support body 91 and a pair of guide pins 96 provided on the swash plate 92 so as to face each support arm 95. Each support arm 95 is provided with a guide hole 97 for connecting a guide pin 96.
Each guide hole 97 is provided so that its axis is parallel to each other and parallel to the tilting surface of the swash plate 92, and is inclined at a predetermined inclination angle with respect to a plane orthogonal to the axis of the drive shaft 90. It is provided to be. Further, a spherical portion 98 is provided at the tip of each guide pin 96 so as to be accommodated in the guide hole 97 of the support arm 95 facing thereto and held movably in the axial direction of the guide hole 97. The swash plate 92 moves relative to the rotation support 91 so that the spherical portion 98 of each guide pin 96 is movably connected along each guide hole 97 so as to be integrally rotatable in a state where the inclination angle can be changed. It is operatively connected.

The inclination angle of the swash plate 92 is changed by the hinge mechanism 93 in a state where the inner peripheral surface 94 a of the through hole 94 is in contact with the outer peripheral surface 90 a of the drive shaft 90. As a result, the swash plate 92
The tilt angle is adjusted without changing the top dead center position.

During operation of the compressor, a compression reaction force received by each piston 99 from the refrigerant gas acts on the inner peripheral surface 97 a of the guide hole 97 from the spherical portion 98 of each guide pin 96. Then, since each guide hole 97 is provided so as to be further away from the swash plate 92 toward the outer peripheral side of the drive shaft 90, the drive shaft 90 extends from the inner peripheral surface 97 a of the guide hole 97 to the spherical portion 98.
An outward reaction force acts in the radial direction. As a result, during operation of the compressor, the swash plate 92 is
a is constantly pressed against the outer peripheral surface 90 a of the drive shaft 90.

[0009]

A clearance is provided between the inner peripheral surface 97a of each guide hole 97 and the spherical portion 98 of each guide pin 96. This consists of a clearance for allowing a dimensional tolerance of the inner diameter of the guide hole 97 and the outer diameter of the spherical portion 98, and a clearance in consideration of heat shrinkage. For the same reason, a clearance is also provided between the through hole 94 of the swash plate 92 and the drive shaft 90. Therefore, the swash plate 92 and the rotary support 9
There is backlash in the hinge mechanism 93 between 1 and
There is play between the swash plate 92 and the drive shaft 90 in the through hole 94.

During operation of the compressor, as described above, the spherical portion 98 of each guide pin 96 is formed inside the guide hole 97 on the side of the rotary support 91 by the compression reaction force of the refrigerant gas compressed by each piston 99. The swash plate 92 is pressed against the outer peripheral surface 90 a of the drive shaft 90 while being pressed against the peripheral surface. Therefore, even if vibration of the engine or the like is externally applied to the operating compressor, the swash plate 92 is
Guide hole 97 on the side and guide pin 96 on the rotation support 91 side
There is no rattling and collision, or the swash plate 92 and the drive shaft 90 do not collide in the through hole 94.

However, when the discharge capacity of the compressor is adjusted to a minimum or a value close to the minimum and the compressor is operated at a low rotation speed, the compression pressure received by each piston 99 from the refrigerant gas becomes small, A state in which the force by which the spherical portion 98 is pressed against the inner peripheral surface 97a of the guide hole 97 and the force by which the swash plate 92 is pressed against the drive shaft 90 may be insufficient. As a result, it is conceivable that vibrations received from the outside of the compressor cause the members to rattle and collide in the hinge mechanism 93 or the through-hole 94, resulting in hitting sound and abnormal vibration due to the collision.

In particular, the clutchless compressor operates with a minimum discharge capacity even when compression of the refrigerant gas is not required, such as during non-cooling, so that the occurrence of hammering noise and abnormal vibration is a problem. Becomes

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to buffer and reduce a collision generated at each operation connection portion in a compressor by acceleration applied to the compressor from the outside. An object of the present invention is to provide a variable displacement compressor that can suppress generation of noise, abnormal vibration, and the like.

[0014]

SUMMARY OF THE INVENTION In order to solve the above problems, an invention according to claim 1 includes a housing having a cylinder bore and a crank chamber, a drive shaft rotatably supported by the housing, In the crank chamber, a rotation support provided so as to be integrally rotatable with the drive shaft, and provided such that the drive shaft is inserted in the crank chamber,
A swash plate connected to the rotary support so as to be swingable around the drive shaft by the rotation of the drive shaft; and a swash plate having a central axis line with respect to a rotation axis line of the drive shaft. A hinge mechanism configured to be able to change the tilt angle to be formed and to be integrally rotatable with respect to the rotation support member; and a hinge mechanism disposed in the cylinder bore so as to reciprocate in the cylinder bore by swinging of the swash plate. A piston operatively connected to the plate, wherein the swash plate has a variable capacity whose inclination angle is changed by the hinge mechanism in a state where an inner surface of a through hole through which the drive shaft is inserted is in contact with an outer peripheral surface of the drive shaft. The compressor is a variable displacement compressor provided with a buffering portion for buffering a collision between the swash plate side member and the rotary support side member constituting the hinge mechanism.

According to a second aspect of the present invention, in the first aspect of the present invention, the hinge mechanism includes a guide portion serving as the rotating support member and a swash plate side member. And a guide pin movable along the guide, and the buffer is provided on the guide.

According to a third aspect of the present invention, in the second aspect of the present invention, the buffer portion is formed of a rigid body and forms an inner peripheral surface of the guide portion, and an outer peripheral surface of the inner wall member. And an elastic portion provided on the side to elastically support the inner wall body with respect to the rotary support.

According to a fourth aspect of the present invention, in the third aspect of the present invention, the buffer portion includes a partial area of an inner peripheral surface of the guide portion with which the guide pin contacts when the compressor has a minimum capacity. The guide portion is provided in a region of the inner peripheral surface except for a partial region of the inner peripheral surface of the guide portion with which the guide pin abuts when the compressor has the maximum capacity.

According to a fifth aspect of the present invention, there is provided a housing provided with a cylinder bore and a crank chamber, a drive shaft rotatably supported by the housing, and a rotatably provided integrally with the drive shaft in the crank chamber. And a swash plate provided so that the drive shaft is inserted in the crank chamber, and connected to the rotary support so as to be swingable around the drive shaft by rotation of the drive shaft. A hinge mechanism for connecting the swash plate to the rotary support so as to be able to change an inclination angle formed by a center axis of the swash plate with respect to a rotation axis of the drive shaft, and to be integrally rotatable; And a piston operatively connected to the swash plate so as to be reciprocally movable within the cylinder bore by swinging of the swash plate, wherein the swash plate has an inner peripheral surface of a through hole through which the drive shaft is inserted. Is the drive A variable displacement compressor whose inclination angle is changed by the hinge mechanism in a state of contacting the outer peripheral surface of the variable displacement compressor, wherein the variable displacement compressor is provided with a buffer for buffering a collision between the swash plate and the drive shaft in the through hole. is there.

According to a sixth aspect of the present invention, in the fifth aspect of the invention, the buffer is provided on the drive shaft. According to a seventh aspect of the present invention, in the invention of the sixth aspect, the shock-absorbing portion is formed of a rigid body and forms an outer peripheral surface of the drive shaft, and is provided on an inner peripheral side of the outer wall. And an elastic portion for elastically supporting the outer wall with respect to the drive shaft.

According to an eighth aspect of the present invention, in the invention according to the seventh aspect, the buffer portion is a portion of the outer peripheral surface of the drive shaft with which the inner peripheral surface of the through hole contacts when the compressor has a minimum capacity. The drive shaft is provided in a region of the outer peripheral surface excluding a partial region of the outer peripheral surface of the drive shaft with which the inner peripheral surface of the through hole comes into contact when the compressor has the maximum capacity.

According to a ninth aspect of the present invention, there is provided a housing having a cylinder bore and a crank chamber, a drive shaft rotatably supported by the housing, and a rotatable integrally provided with the drive shaft in the crank chamber. And a swash plate that is provided so that the drive shaft is inserted in the crank chamber, and that is connected to the rotary support so as to swing around the drive shaft by rotation of the drive shaft. A hinge mechanism for connecting the swash plate to the rotary support so as to be able to change an inclination angle formed by a center axis of the swash plate with respect to a rotation axis of the drive shaft, and to be integrally rotatable; And a piston operatively connected to the swash plate so as to be reciprocally movable within the cylinder bore by swinging of the swash plate, wherein the swash plate has an inner surface of a through hole through which the drive shaft is inserted. The drive A variable displacement compressor in which the tilt angle is changed by the hinge mechanism in a state of contacting the outer peripheral surface of the swash plate side member and the rotary support side member constituting the hinge mechanism; The variable displacement compressor is provided with a second buffer unit that buffers a collision between the swash plate and a drive shaft in the through hole.

According to a tenth aspect of the present invention, the variable displacement compressor according to any one of the first to ninth aspects is a clutchless type compressor. (Function) According to the first aspect of the invention, when the inclination angle of the swash plate is adjusted to be small and the discharge capacity is controlled to the minimum side, the stroke of the piston is small and the compression reaction force received from the gas compressed by the piston is small. Since the swash plate is not large enough, the urging force applied to the swash plate in the direction of the axis of the drive shaft toward the rotary support is not sufficiently large. Here, when a swash plate side member and a rotary support side member that move relative to each other constitute a hinge mechanism, when there is a backlash between the compressor and an externally applied acceleration to the compressor, the swash plate side member is rotated. The member and the rotating support side member collide. The collision between the two members is buffered by the buffer. Therefore, even if there is backlash between the swash plate side member and the rotation support member side that constitute the hinge mechanism, when an acceleration is externally applied to the compressor whose discharge capacity is controlled to be small, the hinge is not moved. The two members do not collide violently in the mechanism.

According to the invention described in claim 2, according to claim 1
In addition to the operation of the invention described in (1), a collision in a hinge mechanism having a guide portion provided on the rotary support side and a guide pin provided on the swash plate side is buffered by the buffer portion provided on the guide portion. .

According to the invention of claim 3, according to claim 2,
In addition to the operation of the invention described in the above, when the swash plate is tilted, in the hinge mechanism, the guide pin, which is the member on the swash plate side, is caused by the compressive reaction force to the inner peripheral surface of the guide portion, which is the member on the rotary support side. Slides when pressed. At this time,
Since the guide pin is made of a rigid body and slides on the inner wall body forming the inner peripheral surface of the guide portion, the guide pin moves smoothly along the guide portion even when strongly pressed against the inner peripheral surface. Further, in a state in which the inclination angle of the swash plate is controlled to be small and the discharge capacity is controlled to the minimum side, when the guide pin collides with the inner wall body forming the inner peripheral surface of the guide portion by acceleration applied to the compressor from the outside, The collision is buffered by the elastic deformation of the elastic part supporting the inner wall body on the rotating support.

According to the invention described in claim 4, according to claim 3,
In addition to the effect of the invention described in the above, in the state where the inclination angle of the swash plate is large and the discharge capacity is controlled to the maximum, the compression reaction force received by the piston from the gas is maximum, so the force acting on the guide portion from the guide pin is Will be the largest. At this time, the compression reaction force acts on the guide portion from the guide pin without passing through the buffer portion. On the other hand, when the discharge capacity is controlled to the minimum, the guide pin comes into contact with the guide section via the buffer section. Therefore, at the time of the minimum capacity, the collision between the guide pin and the guide portion is buffered by the buffer portion.

According to the fifth aspect of the invention, when the discharge capacity is controlled to the minimum side and the compression reaction force applied to the swash plate is not sufficiently large, the swash plate-side member in the hinge mechanism is connected to the rotary support member. Due to the reaction force received from the member, the magnitude of the force with which the inner peripheral surface of the through hole of the swash plate is pressed against the outer peripheral surface of the drive shaft is not sufficiently large. Here, if there is play between the inner peripheral surface of the through hole and the outer peripheral surface of the drive shaft, when acceleration is applied to the compressor from the outside, the inner peripheral surface of the through hole and the drive shaft are displaced. The outer peripheral surface collides. The collision between the swash plate and the drive shaft is buffered by the buffer. Therefore, even if acceleration is externally applied to the compressor in a state where the discharge capacity is controlled to be small, the swash plate and the rotary support do not collide violently.

According to the invention described in claim 6, according to claim 5,
In addition to the operation of the invention described in the above, the collision between the swash plate and the drive shaft in the through hole is buffered by the buffer provided on the drive shaft.

According to the invention described in claim 7, according to claim 6,
In addition to the operation of the invention described in the above, when the swash plate is tilted, the swash plate moves on the outer peripheral surface of the drive shaft while the inner peripheral surface of the through hole is pressed against the outer peripheral surface of the drive shaft. At this time, the inner peripheral surface of the through hole slides with respect to the outer wall body which is formed of a rigid body and forms the outer peripheral surface of the drive shaft. Move smoothly along. or,
When the inner peripheral surface of the through-hole collides with the outer wall forming the outer peripheral surface of the drive shaft in a state where the discharge capacity is controlled to the minimum side, the collision occurs due to the elastic deformation of the elastic portion supporting the outer wall to the drive shaft. Is buffered.

According to the invention described in claim 8, according to claim 7,
In addition to the operation of the invention described in the above, in the state where the inclination angle of the swash plate is large and the discharge capacity is controlled to the maximum, the compression reaction force received by the piston from the gas becomes maximum, so that the drive shaft The force acting on the outer peripheral surface is also maximum. At this time, the inner peripheral surface of the swash plate abuts on the outer peripheral surface of the drive shaft without any intervening buffer. On the other hand, when the discharge capacity is controlled to the minimum, the inner peripheral surface of the swash plate comes into contact with the outer peripheral surface of the drive shaft via the buffer. Therefore, at the time of the minimum capacity, the collision between the two members is buffered.

According to the ninth aspect of the present invention, the first aspect is provided.
And the operation of each invention described in claim 5. According to the tenth aspect of the present invention, there is provided a clutchless compressor that is operated with a minimum discharge capacity even during a compression stop.
The operation according to any one of claims to 9 is provided.

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) A first embodiment in which the present invention is embodied in a swash plate type variable displacement compressor will be described below with reference to FIGS. For convenience of explanation,
The left side in FIG. 1 is the front side, and the right side is the rear side.

As shown in FIG. 1, a swash plate type variable displacement compressor (hereinafter simply referred to as a compressor) 10 has a housing composed of a front housing 11, a cylinder block 12, and a rear housing 13. A valve plate 14 is interposed between the cylinder block 12 and the rear housing 13. Inside the front housing 11, a crank chamber 15 partitioned by a cylinder block 12 is provided. The cylinder block 12 is provided with a plurality of cylinder bores 16 which are defined by a valve plate 14 and open to the crank chamber 15.

A drive shaft 17 is rotatably supported by the housing. The drive shaft 17 includes the front housing 1
1 and the cylinder block 12 are supported in a state of being disposed in the crank chamber 15, and a front end thereof extends from the front housing 11 to the outside.

The front side of the drive shaft 17 is rotatably supported by a radial bearing 11a provided on the front housing 11. The rear end of the drive shaft 17 is inserted into a hole 20 provided at the center of the cylinder block 12, and the radial bearing 2 fixed to the front of the hole 20.
1 rotatably supported by the housing. The drive shaft 17 is urged in a direction from the rear side to the front side in the axial direction by a compression coil spring 22 and a thrust bearing 23 provided at a rear portion of the hole 20.

At the front end of the front housing 11, a support portion 1 formed so as to surround a drive shaft 17 extending to the outside.
1b is provided, and a pulley 19 is rotatably supported on the outer peripheral side of the support portion 11b via an angular bearing 18. The pulley 19 is fixed to a front end of the drive shaft 17 and is operatively connected to a crankshaft of the vehicle engine E by a belt V.

A rotation support 24 is fixed to the drive shaft 17 so as to be integrally rotatable in the crank chamber 15. The front surface of the rotary support 24 is rotatably abutted on the front housing 11 via a thrust bearing 25.
The rotation support 24 is provided so that the drive shaft 17 is inserted into the crank chamber 15, and a swash plate 26 is connected to the rotation support 24 so as to be swingable around the drive shaft 17 as the drive shaft 17 rotates.

The swash plate 26 has a substantially disk-shaped body 27 forming a central portion, and a ring-shaped sliding part 28 provided on the periphery of the body 27. At the center of the body 27, a through hole 29 through which the drive shaft 17 is inserted is provided. The swash plate 26 is connected to the rotary support 24 by a hinge mechanism 30 provided on the front side of the body 27 in a state where the drive shaft 17 is inserted through the through hole 29. The hinge mechanism 30 connects the swash plate 26 to the rotation support 24 so that the inclination angle θ of the center axis L2 of the swash plate 26 with respect to the center axis L1 of the drive shaft 17 can be changed and can be integrally rotated. . The central axis L2 of the swash plate 26 is the central axis of the annular plate-shaped sliding portion 28, and the shoe 3
9 is an axis orthogonal to the sliding surface. On the front side of the body 27, a counter weight 27a is provided.

The hinge mechanism 30 includes a pair of support arms 31 provided on the rear side of the rotary support 24 as a rotary support side member, and a pair of support arms 31 provided on the front side of the swash plate 26 as a swash plate side member. The guide pin 32 is used. Each support arm 31 has a guide hole 33 as a guide portion.
have. The guide pin 32 has a spherical portion 34 housed along the guide hole 33 so as to be movable in the axial direction. And, the hinge mechanism 30 includes the guide pins 3
By moving the second spherical portion 34 along the guide hole 33, the swash plate 26 can be integrally rotated so that the tilt angle θ can be changed.
Are connected to the rotary support 24.

Further, the hinge mechanism 30 is provided to adjust the inclination angle θ of the swash plate 26.
Is changed, the swash plate 26 is tilted with the inner peripheral surface 29a of the through hole 29 in contact with the outer peripheral surface 17a of the drive shaft 17. At this time, even if the tilt angle θ changes, the hinge mechanism 30 moves to the rearmost position of the swing range in the axial direction of the swash plate 26 that swings with the rotation of the drive shaft 17, that is, the top dead end of the swash plate 26. The swash plate 26 is tilted so that the point position hardly changes.

The drive shaft 17 has a rotating support 24 and a swash plate 2.
A compression coil spring 35 that abuts on the front surface of the swash plate 26 and urges it rearward is fitted between the swash plate 26 and the swash plate 26. Also, the drive shaft 17
The retaining ring 36 at the front end position of the cylinder block 12
Is fixed, and the torso 2 of the swash plate 26 is
A compression coil spring 37 that can be brought into contact with the rear surface of the outer sleeve 7 is telescopically fitted to the outside.

As shown in FIG. 1, the swash plate 26 is in the maximum tilt state when the counter weight portion 27a contacts the rotary support 24 and the tilting of the swash plate 26 to the direction where the tilt angle θ is increased is restricted. Further, as shown in FIG.
When the rear surface is in contact with the retaining ring 36 via the compression coil spring 37, and the tilting of the tilting angle θ is reduced, the tilting state is set to the minimum tilting state. The tilt angle θ in the minimum tilt state is:
The value is larger than 0 °. This is the compressor 10
This is because the refrigerant gas is internally circulated in the compressor 10 even in the idle state.

In each of the cylinder bores 16 provided in the cylinder block 12, a single-headed piston 38 is accommodated so as to be able to reciprocate in the axial direction. Each piston 38
The connecting portion 38a provided at the front end is moored to the sliding portion 28 of the swash plate 26 via the shoe 39, and is operatively connected to the swash plate 26. Each piston 38
At the top dead center position of the swash plate 26, the cylinder bore 16
Is located at the top dead center position of the piston 38, which is the last position of the reciprocating operation range.

In the rear housing 13, a suction chamber 40 located at the center thereof and an annular discharge chamber 41 located around the suction chamber 40 are defined by the valve plate 14. The suction chamber 40 is connected via a suction passage 42 to an evaporator of an external refrigerant circuit (not shown).
It is also connected to the condenser via a check valve (not shown).

The valve plate 14 is provided with a suction port 43 and a suction valve 44 for introducing refrigerant gas from the suction chamber 40 into the cylinder bore 16 for each cylinder bore 16. The valve plate 14 has a cylinder bore 16.
A discharge port 45 and a discharge valve 46 for discharging the compressed refrigerant gas to the discharge chamber 41 are provided for each cylinder bore 16.

Cylinder block 12 and valve plate 14
Is provided with a bleed passage (not shown) for constantly communicating the crank chamber 15 with the suction chamber 40 and reducing the crank pressure.

The cylinder block 12 and the rear housing 13 have an air supply passage (not shown) for communicating the discharge chamber 41 with the crank chamber 15. The rear housing 13 is provided with a capacity control valve 50 for controlling the amount of refrigerant gas introduced from the discharge chamber 41 to the crank chamber 15 through the air supply passage.

The capacity control valve 50 is a single-acting solenoid spring return type solenoid valve, which opens the air supply passage when not energized, shuts off the air supply passage when a predetermined energization is performed, and supplies the air in accordance with the energized amount. Adjust the flow path opening amount of the air passage.
The displacement control valve 50 controls the crank pressure by controlling the supply amount of the refrigerant gas to be supplied to the crank chamber 15 from which the refrigerant gas is discharged through the bleed passage, and the inclination angle θ of the swash plate 26
And an external control valve capable of controlling the discharge capacity.

Next, the first shock-absorbing part 60 provided on the hinge mechanism 30 and the drive shaft 17 which are characteristic features of the present invention.
A description will be given of the second buffer unit 63 provided in the first embodiment. Each of the support arms 31 has a first buffer portion 6 for buffering a collision between the guide pin 32 constituting the hinge mechanism 30 and the support arm 31.
0 is provided. The first buffer portion 60 is provided over the entire length of the guide hole 33, and the guide pin 32 is connected to the first buffer portion 6 when the compressor 10 has the maximum capacity to the minimum capacity.
It comes into contact with the guide hole 33 through the “0”.

As shown in FIG. 3, the first buffer portion 60 is made of a rigid metal material, and has a cylindrical body 61 as an inner side wall forming the inner peripheral surface 33a of the guide hole 33; An elastic body 62 is provided on the outer peripheral side and serves as an elastic part for elastically supporting the cylindrical body 61. The cylinder 61 is, for example,
It is formed by extrusion, cutting, or the like. The elastic body 62 is formed, for example, externally, and then the guide hole 33 is formed.
And is made of a synthetic resin, synthetic rubber, or the like, which has high elasticity with a high shock absorbing effect and excellent heat resistance and oil resistance. First buffer section 60
Is assembled by press-fitting and bonding into the guide hole 33, for example.

Also, as shown in FIG.
Second buffer 6 for buffering collision between swash plate 26 and drive shaft 17
3 are provided. The second buffer 63 is provided on the outer peripheral surface 17a of the drive shaft 17 so as to include a contact area with the swash plate 26 from the maximum inclination to the minimum inclination.

As shown in FIG. 3, the second buffer portion 63 is provided at a portion where the inner peripheral surface 29a of the through hole 29 of the swash plate 26 contacts, and is made of a metal material to form the outer peripheral surface 17a of the drive shaft 17. A cylindrical body 64 as an outer wall body to be formed, and an elastic body 65 as an elastic portion provided on the inner peripheral side of the cylindrical body 64 and elastically supporting the cylindrical body 64. The cylindrical body 64 is formed by, for example, extrusion, cutting, or the like. Elastic body 65
Is, for example, molded outside and assembled to the outside of the drive shaft 17 and has a high shock absorbing effect and a high degree of elasticity, as well as a synthetic resin having excellent heat resistance and oil resistance.
It is made of synthetic rubber or the like. The second buffer portion 63 is assembled, for example, by being bonded to a concave portion provided outside the drive shaft 17 in a state of being divided into two in the circumferential direction.

Next, the operation of the variable displacement compressor configured as described above will be described. When the displacement control valve 50 is controlled such that the amount of high-pressure refrigerant gas introduced from the discharge chamber 41 into the crank chamber 15 is reduced during the operation of the engine to increase the cooling capacity of the external refrigerant circuit, the crank pressure is reduced. The inclination angle θ of the swash plate 26 increases and the displacement of the compressor 10 increases.

Conversely, when the displacement control valve 50 is controlled so that the amount of high-pressure refrigerant gas introduced from the discharge chamber 41 into the crank chamber 15 is increased in order to reduce the cooling capacity of the external refrigerant circuit, the crank pressure is reduced. Rise, the inclination angle θ of the swash plate 26 decreases, and the discharge capacity of the compressor 10 decreases.

When the inclination angle θ of the swash plate 26 is adjusted to be large, the stroke of each piston 38 is large, and the compression pressure received by each piston 38 from the refrigerant gas becomes high.
The urging force applied to the swash plate 26 in the axial direction of the drive shaft 17 increases. In this case, the spherical portion 34 of the guide pin 32 provided on the swash plate 26 is strongly pressed against the first buffer portion 60 forming the inner peripheral surface 33 a of the guide hole 33. At this time, since the cylindrical body 61 forming the inner peripheral surface 33 a is formed of a rigid metal, the spherical portion 34 moves smoothly along the guide hole 33 when the swash plate 26 is tilted.

Further, the spherical portion 34 pressed against the inner peripheral surface 33a of the guide hole 33 has a radially outward component with respect to the axis received from the inner peripheral surface 33a.
9 a is strongly pressed against the second buffer 63 forming the outer peripheral surface 17 a of the drive shaft 17. Accordingly, the swash plate 26 moves in a state where the inner peripheral surface 29 a of the through hole 29 is strongly pressed against the outer peripheral surface 17 a of the drive shaft 17. At this time, the outer peripheral surface 1
When the swash plate 26 is tilted, the inner peripheral surface 2 of the through hole 29 is formed because the cylindrical body 64 forming the metal 7a is formed of a rigid metal.
9a slides smoothly on the outer peripheral surface 17a of the drive shaft 17.

When the energization of the capacity control valve 50 is stopped when the cooling of the external refrigerant circuit is stopped, or when the vehicle is accelerated, the high pressure refrigerant gas is introduced from the discharge chamber 41 to the maximum. Rises to a high value, the swash plate 26 enters the minimum inclination state, and the discharge capacity becomes minimum.

In this state, the compression pressure applied to each piston 38 is minimized, and the urging force applied to the swash plate 26 in the direction toward the rotary support 24 in the axial direction is not sufficiently large. The portion 34 is not strongly pressed forward in the axial direction against the inner peripheral surface 33 a of the guide hole 33. Also at this time, since the inner peripheral surface 29a is formed by the cylindrical body 61 made of metal, the spherical portion 34 moves smoothly along the guide hole 33.

Here, if there is backlash between the guide hole 33 and the spherical portion 34 due to dimensional tolerance or the like, the compressor 10
The swash plate 26 and the pistons 38 cause the drive shaft 1
7, the spherical portion 34 of the guide pin 32 vibrates in the axial direction.
Repeatedly collides with the inner peripheral surface 33 a of the guide hole 33. The collision of the spherical portion 34 with the inner peripheral surface 33 a
It is buffered by the elastic deformation of the elastic body 62 which elastically supports the cylindrical body 61 forming 3a. As a result, even if acceleration is applied from the outside to the compressor 10 whose discharge capacity is controlled to the minimum, the rotating support 24 and the swash plate 26 do not violently collide with the hinge mechanism 30.

Also, since the spherical portions 34 cannot be pressed strongly against the inner peripheral surface 33a of the guide hole 33, the swash plate 26
The inner peripheral surface 29a of the through hole 29 is
a. Also at this time, since the outer peripheral surface 17 a is formed by the cylindrical body 64 made of a metal material, the swash plate 26 is smoothly moved while the inner peripheral surface 29 a of the through hole 29 slides on the outer peripheral surface 17 a of the drive shaft 17. To tilt.

If there is a looseness between the inner peripheral surface 29a of the through hole 29 and the outer peripheral surface 17a of the drive shaft 17 based on dimensional tolerances or the like, vibrations applied to the compressor 10 from the outside cause The inner peripheral surface 29a of the through hole 29 and the outer peripheral surface 17a of the drive shaft 17 collide. Inner peripheral surface 29a of this through hole 29
The collision between the shaft and the outer peripheral surface 17a of the drive shaft 17 is buffered by the elastic deformation of the elastic body 65 that elastically supports the cylindrical body 64. As a result, the swash plate 26 and the drive shaft 17 do not violently collide with each other in the through hole 29 even when an external acceleration is applied to the compressor 10 whose discharge capacity is controlled to the minimum.

According to the present embodiment described in detail above, the following effects can be obtained. (1) When the inclination angle θ of the swash plate 26 is controlled to be close to the minimum and the compression reaction force received by the pistons 38 from the refrigerant gas is not sufficiently large, the guide hole 33 of the hinge mechanism 30 on the rotating support 24 side and the swash plate The collision of the guide pin 32 on the 26 side with the spherical portion 34 is buffered by the first buffer portion 60 provided inside the guide hole 33.

Accordingly, the guide hole 33 of the support arm 31 constituting the hinge mechanism 30 and the spherical portion 34 of the guide pin 32
Even if there is play due to dimensional tolerance or the like, the support arm 31 and the guide pin 32 do not collide violently when vibration is externally applied to the compressor 10 in a state where the discharge capacity is controlled to be small. In addition, occurrence of a tapping sound and occurrence of abnormal vibration can be suppressed.

(2) Connect the hinge mechanism 30 to the rotary support 2
The first buffer portion 60 is constituted by a guide pin 32 provided with a guide hole 33 on the fourth side and a spherical portion 34 on the swash plate 26 side. Body 61
62 that elastically supports the rotation support 24 with respect to the rotation support 24.
It consisted of:

Accordingly, the cylindrical body 61 and the elastic body are provided inside the guide hole 33 without basically changing each part of the hinge mechanism 30 having a simple structure without a rotating shaft for tilting the swash plate 26. Since only two parts 62 need to be provided, it can be easily implemented.

(3) The through hole 2 of the swash plate 26 in a state where the biasing force received by the swash plate 26 from the refrigerant gas is not sufficiently large.
The collision between the inner peripheral surface 29 a of the drive shaft 9 and the outer peripheral surface 17 a of the drive shaft 17 is buffered by the second buffer 63 provided outside the drive shaft 17.

Accordingly, the inner peripheral surface 2 of the through hole 29 of the swash plate 26
Even if there is play due to dimensional tolerances or the like between the drive shaft 9a and the outer peripheral surface 17a of the drive shaft 17, when vibration is externally applied to the compressor 10 whose discharge capacity is controlled to be small, the swash plate 26 and the drive shaft 17 does not collide violently, so that it is possible to suppress occurrence of a tapping sound and occurrence of abnormal vibration due to the collision.

(4) Inner peripheral surface 2 of through hole 29 of swash plate 26
9a, a second buffering portion 63 for buffering a collision with the outer peripheral surface 17a of the drive shaft 17, a cylindrical body 64 forming the outer peripheral surface 17a of the drive shaft 17, and an elastic body 65 for elastically supporting the cylindrical body 64.
It consisted of:

Therefore, it is only necessary to provide two parts, the cylindrical body 64 and the elastic body 65, on the outer peripheral side of the conventional drive shaft 17, so that it can be easily implemented. (5) Since the test was performed on the clutchless compressor 10,
When the cooling operation is stopped with the minimum discharge capacity, the collision generated at each connection portion in the compressor can be buffered, and the hitting sound and the abnormal vibration due to the collision can be suppressed.

(Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG. still,
This embodiment is similar to the hinge mechanism 3 of the first embodiment.
The only feature is that the compressor provided with the hinge mechanism 70 instead of the zero is provided with the second buffer 63 of the first embodiment. Therefore, only the hinge mechanism 70 will be described in detail.

The hinge mechanism 70 moves the swash plate 26 with respect to the rotary support 24 and the swash plate 26 with respect to the center axis of the drive shaft 17.
Are connected so that the inclination angle θ of the center axis of the center line can be changed and can be integrally rotated.

More specifically, the hinge mechanism 70 includes a pair of support arms 71 provided on the rear side of the rotary support 24 as a rotary support side member, and a swash plate side member provided on the front side of the swash plate 26. And one arm 72.

Each support arm 71 has a guide hole 73 as a guide portion. Each guide hole 73 is provided with a drive shaft 1
7 has a long hole shape extending in the direction from the outer peripheral side toward the inner peripheral side and in the direction from the rotary support 24 toward the cylinder block 12 side.

The arm 72 is formed so as to extend from the front surface of the swash plate 26 toward the rotary support 24, and has a front end 74 thereof.
Is formed so as to be sandwiched between both support arms 71. A support pin 75 is fixed to the tip 74.
Each end of the support pin 75 is movably engaged with a guide hole 73 of each support arm 71 along each guide hole 73. At each end of the support pin 75,
A washer 76 interposed between the distal end 74 and each support arm 71 is fitted.

The hinge mechanism 70 includes a support pin 75
Are moved along each guide hole 73,
The swash plate 26 is connected to the rotation support 24 so as to be integrally rotatable in a state where the inclination angle θ can be changed.

The hinge mechanism 70 controls the inclination angle θ of the swash plate 26.
Is changed, the swash plate 26 is tilted while the inner peripheral surface 29a of the through hole 29 is in contact with the outer peripheral surface 17a of the drive shaft 17. At this time, even if the tilt angle θ changes, the hinge mechanism 70 moves the swash plate 26 that swings with the rotation of the drive shaft 17 at the rearmost position of the swing range in the axial direction, that is, the swash plate 26.
The swash plate 26 is tilted so that the top dead center position hardly changes.

Also in the variable displacement compressor configured as described above, the second buffer 63 has the function of the first embodiment. Therefore, according to the present embodiment described in detail above, the effects described in (3) and (4) in the first embodiment can be obtained.

(Third Embodiment) Next, a third embodiment of the present invention will be described with reference to FIGS. This embodiment is different from the first embodiment only in that the arrangement areas of the first buffer section 60 and the second buffer section 63 are changed. The description is omitted.

The first buffer section 60 is, like the first buffer section 60 in the first embodiment, such that the spherical sections 34 of the guide pins 32 come into contact regardless of the discharge capacity of the compressor 10. Is not provided. The first buffer unit 60 is configured as shown in FIG.
As shown in the figure, the inner peripheral surface 33 of the guide hole 33 with which the spherical portion 34 of each guide pin 32 contacts when the compressor 10 has the minimum capacity.
It is provided in the area of the inner peripheral surface 33a including the partial area a. As shown in FIG. 6, the first buffer portion 60 has an inner peripheral surface excluding a partial area of the inner peripheral surface 33a of the guide hole 33 with which the spherical portion 34 of each guide pin 32 contacts when the compressor 10 has the maximum capacity. 33a. That is, the compressor 10
At the maximum capacity, the spherical portion 34 of each guide pin 32 is not connected to the inner peripheral surface 3 of the guide hole 33 without the intervention of the first buffer portion 60.
Contact 3a.

Further, like the second buffering section 63 in the first embodiment, the second buffering section 63 has an inner peripheral surface 29a of the through hole 29 of the swash plate 26 regardless of the discharge capacity of the compressor 10.
Are not provided to abut. Second buffer 63
As shown in FIG. 5, the outer peripheral surface 1 of the drive shaft 17 against which the inner peripheral surface 29a of the through hole 29 contacts when the compressor 10 has the minimum capacity.
It is provided in the area of the outer peripheral surface 17a including the partial area 7a. As shown in FIG. 6, the second buffering portion 63 is provided on the outer peripheral surface 17 a except for a partial region of the outer peripheral surface 17 a of the drive shaft 17 with which the inner peripheral surface 29 a of the through hole 29 contacts when the compressor 10 has the maximum capacity. Provided in the area. That is, when the compressor 10 has the maximum capacity, the through hole 29 of the swash plate 26 is
Directly in contact with the outer peripheral surface 17a of the drive shaft 17 without going through.

Next, the operation of the variable displacement compressor configured as described above will be described. When the discharge capacity of the compressor 10 is controlled to be close to the maximum, the spherical portion 34 of each guide pin 32 is strongly pressed against the inner peripheral surface 33 a of the guide hole 33. At this time, the inner peripheral surface 33a is pressed against the inner peripheral surface 33a formed by the support arm 31 itself, not the inner peripheral surface 33a formed by the cylindrical body 61 of the first buffer portion 60. Does not apply great force to When the swash plate 26 is tilted, the spherical portion 34 moves smoothly along the guide hole 33.

When the discharge capacity is controlled to be close to the maximum, the inner peripheral surface 29 a of the through hole 29 of the swash plate 26 is strongly pressed against the outer peripheral surface 17 a of the drive shaft 17. At this time, the inner peripheral surface 29a is pressed against the outer peripheral surface 17a formed by the drive shaft 17 itself, instead of the outer peripheral surface 17a formed by the cylindrical body 64 of the second buffer portion 63. Does not join. Further, when the swash plate 26 is tilted, the through hole 29 moves smoothly with respect to the drive shaft 17.

On the other hand, when the discharge capacity of the compressor 10 is controlled to be close to the minimum, the spherical portion 34 of each guide pin 32
However, the force pressed against the inner peripheral surface 33a of the guide hole 33 is weakened, and the spherical portion 34 collides with the inner peripheral surface 33a due to vibration applied to the compressor 10 from the outside. At this time,
Each spherical portion 34 collides with the inner peripheral surface 33 a formed by the cylindrical body 61 of the first buffer portion 60, and the collision is buffered by the first buffer portion 60. Further, when the swash plate 26 is tilted, the spherical portion 34 slidably in contact with the cylindrical body 61 moves smoothly along the guide hole 33.

When the discharge capacity is controlled to be close to the minimum, the inner peripheral surface 29a of the through hole 29 of the swash plate 26 is
7, the force pressed strongly against the outer peripheral surface 17a becomes weaker, and the inner peripheral surface 29a collides with the outer peripheral surface 17a of the drive shaft 17 due to vibration applied to the compressor 10 from the outside. At this time, the inner peripheral surface 29a collides with the outer peripheral surface 17a formed by the cylindrical body 64 of the second buffer 63, and the collision is buffered by the second buffer 63. When the swash plate 26 is tilted, the cylinder 64
The through hole 29 that slides on the drive shaft 17 smoothly moves.

Therefore, according to the present embodiment described in detail above, each effect described in (3) and (4) in the first embodiment and each effect described below can be obtained. . (6) The first shock-absorbing portion 60 provided on the support arm 31 includes a partial area of the inner peripheral surface 33a where the spherical portion 34 of the guide pin 32 contacts when the compressor 10 has the minimum capacity, and the spherical portion 34 has the spherical capacity 34 when the compressor 10 has the maximum capacity. It is provided in the region of the inner peripheral surface 33a excluding the partial region of the inner peripheral surface 33a that comes into contact.

Therefore, in the event of a collision, the collision is buffered by the first buffering section 60 and the guide pin 32 is not strongly pressed against the first buffering section 60, so that the spherical portion 34 of the guide pin 32 is strongly pressed. The deterioration of the elastic body 62 due to the above can be suppressed, and the decrease in the buffer capacity can be suppressed.

In this configuration, since the spherical portion 34 is not strongly pressed against the first buffer portion 60,
The material of the cylinder 61 is made of a metal material having lower hardness, or
It is also possible to use engineering plastics.

(7) The second buffer 6 provided on the drive shaft 17
3 is the inner peripheral surface 2 of the through hole 29 when the compressor 10 has the minimum capacity.
9a includes a partial area of the outer peripheral surface 17a with which the inner peripheral surface 29a of the through hole 29 contacts at the maximum capacity.
It is provided in the area of the outer peripheral surface 17a excluding the partial area of a.

Therefore, at the time of a collision, the collision is buffered by the second buffer 63, and the deterioration of the elastic body 65 due to the guide pin 32 being strongly pressed against the second buffer 63 is suppressed, and the reduction of the buffering capacity is suppressed. can do.

In this configuration, since the through hole 29 is not strongly pressed against the second buffer 63,
The material of the cylinder 64 is made of a metal material having lower hardness, or
It is also possible to use engineering plastics.

Hereinafter, embodiments other than the above-described embodiment embodying the present invention will be listed as other examples. In the first embodiment, as shown in FIG. 7, at least a buffer provided in the guide hole 33 of the hinge mechanism 30
The buffer portion 80 may be provided in a region of the inner peripheral surface 33a excluding a partial region in the circumferential direction of the inner peripheral surface 33a against which the spherical portion 34 is pressed by the compression reaction force received by each piston 38.
In this case, the spherical portion 34 is attached to the inner wall 8 of the buffer 80.
1 does not slide, and collides with the inner wall body 81 supported by the elastic body 82 as an elastic part only when acceleration is applied to the compressor 10 from the outside. Accordingly, it is possible to suppress a decrease in the buffering capacity of the buffering section 80, and it is also possible to use a metal material having a lower hardness, an engineering plastic, or the like as the material of the inner wall body 81.

In the first embodiment, as shown in FIG. 7, the buffer provided on the drive shaft 17 is provided at least with the through-hole 29 of the swash plate 26 by the compression reaction force received by each piston 38.
The cushioning portion 83 may be provided in a region of the outer peripheral surface 17a except for a partial region in the peripheral direction of the outer peripheral surface 17a against which the outer peripheral surface 17a is pressed. In this case, the through hole 29 does not slide with respect to the outer wall 84 of the buffer portion 83, and the elastic body 85 as an elastic portion is formed only when acceleration is externally applied to the compressor 10.
Collides with the outer wall 84 supported by the outer wall. Therefore,
A reduction in the buffer capacity of the buffer unit 83 can be suppressed,
It is also possible to use a metal material having a lower hardness or an engineering plastic as the material of the outer wall 84.

In the first embodiment, the inner peripheral surface 3 of the guide hole 33 is replaced with the elastic body 62 of the first buffer portion 60.
The elastic portion may be directly formed of synthetic rubber or the like in the concave portion provided in 3a.

Similarly, in the first and second embodiments, the drive shaft 17 is replaced with the elastic body 65 of the second buffer 63.
An elastic portion may be directly formed of synthetic rubber or the like in a concave portion provided outside the above.

○ In the first embodiment, the driving shaft 1
7 is a rotary support member side member in a hinge mechanism 30 of the compressor, in which a swash plate 26 is tiltably connected to a support pin provided on the sleeve. May be provided with a first buffer section 60. Also in this case, the swash plate 2 in the hinge mechanism 30 is used.
The collision between the rotating support 6 and the rotating support 24 can be buffered.

The method of adjusting the crank pressure of the compressor 10 is not limited to the external control valve of the inlet side control as in the above embodiment, but the external control valve of the outlet side control, and the external side control valve of the inlet side or the outlet side control. It may be an internal control valve. Further, a control valve whose set pressure is adjusted by external control may be used. Further, a three-way valve may be used in which the internal control valve section for the withdrawal control and the external control valve section for the entry control are operated in cooperation with each other.

The present invention is not limited to the clutchless type compressor, but is applied to a clutch type compressor. In this case, it is possible to buffer a collision generated in the through hole 29 of the hinge mechanism or the swash plate 26 when the discharge capacity is operated near the minimum.

The compressor embodying the present invention may be any positive displacement, reciprocating type variable displacement compressor in which a swinging part is operatively connected to a drive shaft. The swash plate (swash type) compressor 10 The compressor is not limited to a wobble type compressor. In the case of a wobble type compressor, a rotating support side member constituting a hinge mechanism for operatively connecting a rotating support fixed to a drive shaft and a wobble plate (swash plate) connected to the rotating support and driving each piston. And a buffer portion for buffering a collision between the shaft member and the wobble plate side member.

Hereinafter, in addition to the inventions described in the claims, the technical ideas grasped from the above embodiments will be described together with their effects. (1) In the invention according to claim 3, the buffer portion excludes at least a partial region in a circumferential direction of an inner peripheral surface of the guide portion on which the guide pin is pressed by a compression reaction force received by the piston. It is provided in the area of the inner peripheral surface. According to such a configuration, the buffer capacity can be maintained for a long period of time.

(2) In the invention according to claim 7,
The buffer portion is provided at least in a region of the outer peripheral surface excluding a partial region in a circumferential direction of an outer peripheral surface of the drive shaft against which an inner peripheral surface of the through hole of the swash plate is pressed by a compression reaction force received by the piston. Is provided. According to such a configuration, the buffer capacity can be maintained for a long period of time.

[0100]

According to the first to tenth aspects of the present invention, a collision generated at each operation connection portion in the compressor due to an acceleration applied to the compressor from the outside is buffered, and a noise such as a tapping sound, an abnormal vibration and the like is reduced. The occurrence of defects can be suppressed. Further, in the clutchless type compressor, it is possible to suppress occurrence of a tapping sound, abnormal vibration, and the like when the cooling operation is stopped with the minimum discharge capacity.

According to the first to fourth or ninth and tenth aspects of the present invention, it is possible to buffer a collision at the hinge mechanism for operatively connecting the rotary support and the swash plate. According to the third, fourth, or tenth aspect of the present invention, the elastic member and the cylindrical body are simply newly provided in the guide portion of the conventional hinge mechanism, so that the present invention can be easily implemented.

According to the fifth to tenth aspects of the present invention, it is possible to buffer a collision that occurs between the operatively connected drive shaft and the swash plate. Claim 7, 8 or Claim 10
According to the invention described in (1), since the elastic portion and the tubular body are simply newly provided outside the conventional drive shaft, it can be easily implemented.

[Brief description of the drawings]

FIG. 1 is a sectional view of a variable displacement compressor according to a first embodiment.

FIG. 2 is a sectional view of the same variable displacement compressor.

FIG. 3 is a sectional view of a main part of the compressor.

FIG. 4 is a sectional view of a main part of a variable displacement compressor according to a second embodiment.

FIG. 5 is a sectional view of a main part of a third embodiment.

FIG. 6 is a sectional view of an essential part of the same.

FIG. 7 is a sectional view of a main part of another example of a compressor.

FIG. 8 is a sectional view of a conventional variable displacement compressor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Compressor, 11 ... Front housing which comprises a housing, 12 ... Same cylinder block, 13 ... Same rear housing, 15 ... Crank chamber, 16 ... Cylinder bore, 17 ... Drive shaft, 24 ... Rotation support, 26 ... Swash plate ,
Reference numeral 30 indicates a hinge mechanism, 31 indicates a support arm as a rotating support member constituting the hinge mechanism according to the first and third embodiments, 32 indicates a guide pin as a swash plate side member also constituting a hinge mechanism, 33. A guide hole as a guide portion, 33a inner peripheral surface, 34 spherical portion, 38 piston, 60 first buffer portion, 61 cylindrical body as inner wall body,
62 ... elastic body as elastic part, 63 ... second buffer part, 64
········································································································· 72 An arm as a swash plate side member constituting the mechanism; 73 a guide hole as a guide portion;
0: buffer part, 81: inner wall body, 82: elastic body as elastic part, 83: buffer part, 84: outer wall body, 85: elastic body as elastic part, L1: central axis of drive shaft, L2 ... The center axis of the swash plate, θ ... the inclination angle.

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Masahiro Kawaguchi 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside the Toyota Industries Corporation (72) Inventor Kazuya Kimura 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Shares Inside Toyota Industries Corporation (72) Inventor Takeshi Imanishi 2-1-1 Toyota-machi, Kariya-shi, Aichi F-term inside Toyota Industries Corporation (Reference) 3H076 AA06 BB01 BB32 CC12 CC17 CC20 CC32 CC37 CC39

Claims (10)

[Claims] A housing provided with a cylinder bore and a crank chamber; a drive shaft rotatably supported by the housing; and a rotation support member integrally rotatable with the drive shaft in the crank chamber. A swash plate that is provided so that the drive shaft is inserted in the crank chamber, and that is connected to the rotary support so as to be swingable around the drive shaft by rotation of the drive shaft; A hinge mechanism configured to be able to change a tilt angle formed by a center axis of the swash plate with respect to a rotation axis of the drive shaft, and to be connected to the rotation support so as to be integrally rotatable; A piston operatively connected to the swash plate so as to be reciprocally movable within the cylinder bore by swinging the plate, wherein the swash plate has an inner surface of a through hole through which the drive shaft is inserted, and an outer surface of the drive shaft. Abut A variable displacement compressor in which a tilt angle is changed by the hinge mechanism in a state, wherein a shock absorber is provided for damping a collision between a swash plate side member and a rotary support side member constituting the hinge mechanism. 2. The hinge mechanism according to claim 1, wherein the hinge mechanism includes a guide portion serving as the rotary support member and a guide pin movable along the guide portion serving as the swash plate member. The variable displacement compressor according to claim 1, wherein the compressor is provided in a guide portion. 3. The buffer section is made of a rigid body and forms an inner peripheral surface of the guide section, and is provided on an outer peripheral side of the inner wall body to move the inner wall body relative to the rotary support. 3. The variable displacement compressor according to claim 2, further comprising an elastic portion for elastically supporting the compressor. 4. The buffer section includes a partial area of an inner peripheral surface of the guide section where the guide pin contacts when the compressor has a minimum capacity, and the guide section contacts the guide pin when the compressor has a maximum capacity. 4. The variable displacement compressor according to claim 2, wherein the compressor is provided in a region of the inner peripheral surface except for a partial region of the inner peripheral surface of the variable displacement compressor. 5. 5. A housing having a cylinder bore and a crank chamber, a drive shaft rotatably supported by the housing, and a rotation support member provided integrally with the drive shaft in the crank chamber. A swash plate that is provided so that the drive shaft is inserted in the crank chamber, and that is connected to the rotary support so as to be swingable around the drive shaft by rotation of the drive shaft; A hinge mechanism configured to be able to change a tilt angle formed by a center axis of the swash plate with respect to a rotation axis of the drive shaft, and to be connected to the rotation support so as to be integrally rotatable; A piston operatively connected to the swash plate so as to reciprocate in the cylinder bore by swinging the plate, wherein the swash plate has an inner peripheral surface of a through hole through which the drive shaft is inserted, and an outer peripheral surface of the drive shaft. Abut A variable displacement compressor in which a tilt angle is changed by the hinge mechanism in a state, wherein a buffer portion for buffering a collision between the swash plate and the drive shaft in the through hole is provided. 6. The variable displacement compressor according to claim 5, wherein the buffer is provided on the drive shaft. 7. An outer wall body made of a rigid body and forming an outer peripheral surface of the drive shaft, and the shock-absorbing portion is provided on an inner peripheral side of the outer wall body, and the outer wall body is provided with respect to the drive shaft. 7. The variable displacement compressor according to claim 6, comprising an elastic portion that elastically supports. 8. The buffer portion includes a partial area of an outer peripheral surface of the drive shaft with which an inner peripheral surface of the through hole abuts when the compressor has a minimum capacity, and an inner peripheral portion of the through hole when the compressor has a maximum capacity. 8. The variable displacement compressor according to claim 6, wherein the compressor is provided in a region of the outer peripheral surface excluding a partial region of the outer peripheral surface of the drive shaft with which a surface abuts. 9. A housing having a cylinder bore and a crank chamber, a drive shaft rotatably supported by the housing, and a rotation support member provided integrally with the drive shaft in the crank chamber. A swash plate that is provided so that the drive shaft is inserted in the crank chamber, and that is connected to the rotary support so as to be swingable around the drive shaft by rotation of the drive shaft; A hinge mechanism configured to be able to change a tilt angle formed by a center axis of the swash plate with respect to a rotation axis of the drive shaft, and to be connected to the rotation support so as to be integrally rotatable; A piston operatively connected to the swash plate so as to be reciprocally movable within the cylinder bore by swinging the plate, wherein the swash plate has an inner surface of a through hole through which the drive shaft is inserted, and an outer surface of the drive shaft. Abut In the variable displacement compressor, the inclination angle of which is changed by the hinge mechanism in a state, a first buffering part that buffers a collision between a swash plate-side member and a rotary support member that constitute the hinge mechanism; A variable displacement compressor provided with a second shock absorber for damping collision between the plate and the drive shaft. 10. The variable displacement compressor according to claim 1, wherein the compressor is a clutchless type compressor.