JP2001295755A - Guide pin of variable displacement compressor and variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the crank chamber pressure required for varying capacity during high-speed rotation and reduce power consumption during an OFF operation when using the clutch-less type power transmission, by restraining hunting. SOLUTION: A hinge mechanism 22 comprises two support arms 36 provided to project from the rear face of a lug plate 17, a guide hole 37 formed in each support arm 36, and two guide pins 38 fixed to a swash plate 19. The guide pin 38 has a shank 38a securely fitted into the swash plate 19, and a spherical portion 38b formed at the end of the shank to engage the guide hole 37. The guide pin 38 is formed with a hollow part 38c shaped to be open on the side opposite to the shank 38a of the spherical portion 38b in order to reduce products of inertia about the variable fulcrum (fulcrum of oscillation) of the swash plate 19 including the guide pins 38.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a guide pin and a variable displacement compressor which constitute a hinge mechanism of a variable displacement compressor applied to, for example, a vehicle air conditioner.

[0002]

2. Description of the Related Art Generally, a variable displacement compressor of this type includes a housing including a cylinder block and a drive shaft rotatably provided in the housing. A plurality of cylinder bores are formed in the cylinder block so as to surround the drive shaft, and each bore accommodates a piston so as to be able to reciprocate. On the drive shaft, a swash plate (cam plate) is rotatable synchronously with the drive shaft via a special operation connecting mechanism (hinge mechanism) and slides in the axial direction of the drive shaft with respect to the drive shaft. It is provided to be tiltable. The outer periphery of the swash plate is moored to each piston. When the swash plate, which is inclined with respect to the drive shaft, rotates together with the drive shaft, the rotational motion of the drive shaft is converted into reciprocating linear motion of the piston, and gas is sucked and compressed in each cylinder bore. Then, by controlling the pressure in the crank chamber in which the swash plate is accommodated, the inclination angle of the swash plate is controlled to change the stroke of the piston, thereby changing the discharge capacity.

FIG. 9 shows an example of an operation connection mechanism between a swash plate and a drive shaft disclosed in Japanese Patent Application Laid-Open No. 11-93333.
A rotor (lug plate) 63 is fixed to the drive shaft 61 in the crank chamber 62, and a pair of support arms 64 protrude from the rear surface thereof. The support arm 64 includes
A guide hole 65 that penetrates the arm substantially in the radial direction of the rotor 63 is formed.

A swash plate (cam plate) 66 is disposed in the crank chamber 62 behind the rotor 63 on the drive shaft 61. The swash plate 66 includes a swash plate body 67 made of an aluminum-based metal and a swash plate guide 68 made of an iron-based metal to reduce the weight and prevent seizure with the shoes.
Are press-fitted into the swash plate guide 68. The swash plate main body 67 is connected to the piston 7 via a shoe 69 which is in sliding contact with the outer peripheral sliding surface.
Moored to zero.

The swash plate guide 68 has a pair of guide pins 71.
Are fitted and fixed. The guide pin 71 has a spherical portion 71a at the tip for engaging with the guide hole 65. The support arm 64, the guide hole 65, and the guide pin 71 constitute a hinge mechanism. When the pressure in the crank chamber 62 is changed, the inclination angle of the swash plate 66 is changed so that the stroke amount is changed without changing the top dead center of the piston 70, and the stroke of the piston 70 is changed. You.

[0006]

In the compressor having the hinge mechanism constructed as described above, the swash plate 66 is attached to the swash plate 66.
6 is generated based on the correlation between the moment of the rotational motion caused by the centrifugal force when the cylinder 6 is rotated, the internal pressures of all the cylinder bores in the suction stroke and the compression stroke, and the pressure in the crank chamber 62 (crank pressure Pc). Moments act,
The inclination angle of the swash plate 66 is determined based on the balance.
The mass of the guide pin 71 constituting the hinge mechanism affects the moment caused by the centrifugal force, and acts in the direction in which the inclination angle of the swash plate 66 increases.

The moment generated by the rotation of the swash plate 66 includes the swing shaft of the swash plate 66 and the drive shaft 61.
The origin is defined by the intersection of the plane orthogonal to the axis and the axis.
A rectangular coordinate system (x, y,
and products of inertia I _xy of the swash plate 66 with respect to the xz plane and yz plane at z), it becomes that multiplied by the square of the angular velocity of the drive shaft 61 (e.g., JP-A-7-293429). The product of inertia I _xy is represented by I _xy = ∫xydm.
The y-axis of the rectangular coordinate system coincides with the axis of the drive shaft 61, and the z-axis coincides with the swing axis.

Therefore, if the mass of the guide pin 71 is large, its influence becomes large at the time of high-speed rotation, and the crank pressure P
When control is performed to increase the angle c and decrease the inclination angle of the swash plate 66, the crank pressure Pc variably required increases. As a result, hunting occurs and the wear of the rubber lip due to an increase in the back pressure of the seal member easily proceeds. In addition, when the power transmission to the compressor is of a clutchless type, there is a problem that power consumption increases during an off operation, that is, during a minimum capacity operation.

In the case where the swash plate main body 67 made of aluminum-based metal is fitted to the iron-based swash plate guide 68,
In order to secure the press-fit strength of the swash plate 66, the distance from the swash plate main body 67 to the spherical portion 71a of the guide pin 71, that is, the distance from the xz plane of the orthogonal coordinate system, is such that the entire swash plate 66 is made of an iron-based metal. It is about 20% larger than when formed.
As a result, the influence of the moment becomes greater.

The present invention has been made in view of the above problems, and a first object of the present invention is to reduce the crank chamber pressure necessary for changing the displacement during high-speed rotation.
An object of the present invention is to provide a guide pin of a variable displacement compressor that can suppress occurrence of hunting and reduce power consumption during an off operation when a power transmission is a clutchless type. A second object is to provide a variable displacement compressor provided with the guide pins.

[0011]

According to the first aspect of the present invention, there is provided a housing including a crank chamber, a suction chamber, a discharge chamber, and a cylinder bore communicating with each of the chambers. A piston reciprocally accommodated in the cylinder bore, a drive shaft rotatably supported in the crank chamber, and an actuation of the piston to convert rotational movement of the drive shaft into reciprocal movement of the piston. A cam plate connected to the crankshaft and connected to and penetrated by the drive shaft; a rotation support fixed to the drive shaft so as to be integrally rotatable; the rotation support and the cam plate; And a hinge mechanism interposed between the pistons, and controlling the pressure in the crank chamber to control the tilt angle of the cam plate to thereby control the inclination of the cam plate in accordance with the reciprocation of the piston. In the variable displacement compressor that changes the discharge capacity from the dowel bore to the discharge chamber, the hinge mechanism is configured to transmit the rotational motion of the rotary support to the cam plate side, and the cam plate is mounted on the drive shaft. At least a part of the guide pin that allows the tilt while sliding is made hollow in order to reduce the product of inertia around the variable fulcrum of the cam plate including the guide pin. Note that the tilt angle of the cam plate means an angle formed by a virtual plane orthogonal to the drive shaft and the cam plate.

According to the present invention, the rotation of the drive shaft is transmitted to the cam plate via the rotation support and the hinge mechanism,
The cam plate is rotated integrally with the drive shaft. The cam plate has a moment of rotational motion caused by a centrifugal force during rotation of the cam plate, an internal pressure of all cylinder bores in a suction stroke and a compression stroke, and a pressure in a crank chamber (crank pressure P).
The moment or the like generated based on the correlation with c) acts, and the inclination angle of the cam plate is determined based on the balance. The mass of the guide pin constituting the hinge mechanism affects the moment due to the centrifugal force, and acts in the direction in which the inclination angle of the cam plate increases. If the mass of the guide pin is large, the influence becomes large at the time of high-speed rotation, and when controlling to increase the crank pressure and reduce the inclination angle of the cam plate, the crank pressure variably required increases. However, in the present invention, since at least a part of the guide pin is hollow, the product of inertia around the variable fulcrum of the cam plate including the guide pin is reduced, and the influence on the direction of increasing the inclination angle of the cam plate is reduced. In addition, the crank pressure Pc can be reduced when the displacement is changed during high-speed operation, hunting during control can be suppressed, and the life of the lip seal can be extended. Further, it is possible to reduce power consumption during the off-operation when the power transmission is a clutchless type.

According to a second aspect of the present invention, in the first aspect of the present invention, the hinge mechanism includes a support arm formed on the rotary support so as to extend toward the cam plate, A guide portion formed on the arm, a shaft portion fixed to the cam plate and fitted and fixed to the cam plate, and formed at the tip thereof to engage with the guide portion and have a larger diameter than the shaft portion. And a guide pin having a spherical portion of the above, and at least a part of the spherical portion of the guide pin is made hollow.

According to the present invention, the guide pin constituting the hinge mechanism engages with the guide portion of the support arm at the spherical portion located on the distal end side and tilts. Accordingly, the guide portion can be formed on a simple cylindrical surface, and can smoothly guide the movement when the cam plate tilts while sliding on the drive shaft. And when hollowing a part of the guide pin, in order to hollow a part of the spherical portion located at the tip of the guide pin that has a large effect on the value of the product of inertia,
Even if the weight is the same, the effect is greater than making the base end hollow.

According to a third aspect of the present invention, in the second aspect of the present invention, the guide pin has an open side of the spherical portion opposite to the shaft portion, and extends to a substantially center of the spherical portion. A hollow portion is formed. Therefore, in the present invention, the product of inertia around the variable fulcrum of the cam plate including the guide pin is reduced as compared with the invention described in claim 2, and the crank pressure Pc required at the time of the capacity change during high-speed operation is reduced. Can be reduced, hunting during control can be further suppressed, and the life of the lip seal can be extended.

According to a fourth aspect of the present invention, in the second aspect of the present invention, the guide pin has a hollow portion which is open on a side of the spherical portion opposite to the shaft portion and which reaches the shaft portion. Is formed. Therefore, in the present invention,
The guide pin is further reduced in weight, and the above-described effect is further increased.

According to a fifth aspect of the present invention, in the second aspect of the present invention, the guide pin has an open side of the spherical portion opposite to the shaft portion, and the shaft portion has a position relative to the cam plate. A hollow portion extending to near the fitting portion is formed. Therefore, according to the present invention, the effect is further enhanced as compared with the invention described in claim 4.

According to a sixth aspect of the present invention, in the first aspect of the present invention, the hinge mechanism includes a swing arm provided on the cam plate toward the rotation support, and a hinge provided on the rotation support. A support hole, a guide hole provided in one of the swing arm and the support arm, a mounting hole formed in the other arm, and a projecting portion that penetrates the mounting hole and extends in the guide hole. And an inserted guide pin, and at least a part of the guide pin is made hollow.

Therefore, according to the present invention, the guide pin constituting the hinge mechanism moves along the guide hole, thereby guiding the cam plate to tilt while sliding on the drive shaft. The guide pin may have a simple linear shape, and is easier to manufacture than a case where a spherical portion is formed.

According to a seventh aspect of the present invention, in the sixth aspect of the invention, the guide hole is formed in the support arm, and the mounting hole is formed in the swing arm. Therefore, in the present invention, the structure of the cam plate is simplified as compared with the configuration in which the guide hole is provided in the swing arm.

According to an eighth aspect of the present invention, in the invention of the seventh aspect, a pair of the swing arms are provided so as to sandwich the support arm, and the guide pins are both ends corresponding to mounting holes of the swing arm. The part is formed in a solid state. Therefore, according to the present invention, the strength of both ends corresponding to the mounting hole where the compression reaction force acts greatly on the guide pin is increased, and the life of the guide pin is extended.

According to a ninth aspect of the present invention, in the first aspect of the present invention, the guide pin is formed by forging. Therefore, in the present invention, the strength is increased and the manufacturing cost is reduced as compared with the case where the hollow portion of the guide pin is formed by cutting.

According to a tenth aspect of the present invention, the variable displacement compressor includes the hinge mechanism and the guide pin according to any one of the first to ninth aspects. Therefore, according to the present invention, the same function and effect as the invention described in any one of claims 1 to 9 can be obtained.

[0024]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) Hereinafter, a first embodiment of the present invention applied to a variable displacement compressor of a vehicle air conditioner will be described.
The embodiment will be described with reference to FIGS.

As shown in FIG. 1, a compressor 10 comprises a cylinder block 11, a front housing 12 fixedly joined to the front end thereof, and a valve /
And a rear housing 14 joined and fixed via a port forming body 13. Both housings 12, 14, valves and
The port forming body 13 and the cylinder block 11 are joined and fixed to each other by a plurality of through bolts (only one is shown). The crank chamber 15 is partitioned into a region surrounded by the cylinder block 11 and the front housing 12.

The drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 via bearings so as to pass through the crank chamber 15. A lug plate 17 as a rotation support is fixed to the drive shaft 16 in the crank chamber 15 so as to be integrally rotatable. The lug plate 17 is in contact with the inner wall surface of the front housing 12 via the thrust bearing 18.

The swash plate 19 as a cam plate is made of an aluminum-based swash plate body 20 and an iron-based metal swash plate guide 21 in order to reduce the weight and prevent seizure with the shoe 23a made of an iron-based metal. And the swash plate main body 20 is
1 is press-fitted. The swash plate guide 21 has a through hole 21a
Are formed, and the swash plate 19 is disposed in the crank chamber 15 with the drive shaft 16 penetrating the through hole 21a. The hinge mechanism 22 is interposed between the lug plate 17 and the swash plate 19. Therefore, the swash plate 19 is connected to the hinge mechanism 22.
The hinge connection between the lug plate 17 and the driving shaft 16 via the
6, and can be tilted with respect to the drive shaft 16 with the sliding movement of the drive shaft 16 in the axial direction.

The swash plate guide 21 is formed integrally with a counterweight 21b on the opposite side of the hinge mechanism 22 with respect to the drive shaft 16. A pressing spring 16 a is wound around the drive shaft 16 between the lug plate 17 and the swash plate guide 21. The pressing spring 16a urges the swash plate 19 in a direction approaching the cylinder block 11 (that is, a direction in which the inclination angle decreases).

A plurality of (only one is shown in the drawing) cylinder bores 11a are formed in the cylinder block 11 so as to surround the drive shaft 16 at equal angular intervals. The single-headed piston 23 is reciprocally accommodated in each cylinder bore 11a. The front and rear openings of the cylinder bore 11a are closed by the valve / port forming body 13 and the piston 23, and the piston 23 is provided in the cylinder bore 11a.
A compression chamber 11b whose volume changes according to the reciprocation of the compression chamber 11b is partitioned. The piston 23 is connected to the swash plate 19 via the shoe 23a.
Moored at the periphery. Therefore, the rotational motion of the swash plate 19 accompanying the rotation of the drive shaft 16 is converted to the reciprocating motion of the piston 23 via the shoe 23a.

The drive shaft 16 is operatively connected to an engine 25 via a power transmission mechanism 24. Power transmission mechanism 24
May be a clutch mechanism (for example, an electromagnetic clutch) capable of selecting transmission / disconnection of power by external electric control, or a constant transmission type clutchless mechanism (for example, a belt) having no such clutch mechanism. / Combination of pulleys). In this embodiment, a clutchless type power transmission mechanism 24 is employed.

In the rear housing 14, a suction chamber 26 is provided.
A substantially annular discharge chamber 27 that surrounds the suction chamber 26 is defined. The valve / port forming body 13 is formed with a suction port 28, a suction valve 29 for opening and closing the port 28, a discharge port 30, and a discharge valve 31 for opening and closing the port 30 corresponding to each cylinder bore 11a. The suction chamber 26 and the discharge chamber 27 are connected by an external refrigerant circuit 32.

In the cylinder block 11, the valve / port forming body 13 and the rear housing 14, an air supply passage 33 for communicating the crank chamber 15 with the discharge chamber 27, a crank chamber 15
A bleed passage 34 communicating the suction chamber 26 with the suction chamber 26 is provided. A control valve 35 is provided in the middle of the air supply passage 33. This control valve 35 is disclosed in, for example, Japanese Patent Application Laid-Open No. 9-2689.
The bellows is configured in the same manner as the control valve disclosed in Japanese Patent Publication No. 73, and is displaced by detecting suction pressure, a solenoid capable of generating an electromagnetic force, and opening of the air supply passage 33 by displacement of the bellows and electromagnetic force of the solenoid. A valve mechanism (not shown) for controlling the degree.

In the control valve 35, when the pressure in the suction chamber 26 becomes equal to or lower than a predetermined pressure, the bellows are displaced and the air supply passage 3 is displaced.
3 is opened, and if it is larger than a predetermined pressure, it is kept closed. The discharge capacity of the compressor is variably adjusted by controlling the pressure (crank pressure) Pc of the crank chamber by the control valve 35. That is, when the pressure in the suction chamber 26 is low, the valve opening of the control valve 35 increases, and the crank pressure Pc
, The inclination angle of the swash plate 19 (the angle between the plane orthogonal to the drive shaft 16 and the swash plate 19) is reduced, the stroke of each piston 23 is reduced, and the discharge capacity is reduced. On the other hand, when the pressure in the suction chamber 26 is large, the valve opening is reduced and the crank pressure Pc is induced to be lower, so that the swash plate 19
, The stroke of each piston 23 increases, and the discharge capacity increases.

Next, the hinge mechanism 22 will be described in more detail. The hinge mechanism 22 includes two support arms 36 (only one is shown) projecting from the rear surface of the lug plate 17.
And a guide hole 37 as a guide portion formed in each support arm 36, and two guide pins 38 fixed to the swash plate 19. Each guide hole 37 is formed in a column shape. The two guide pins 38 are arranged side by side with the drive shaft 16 interposed therebetween, and correspond to the support arms 36 respectively. One support arm 36 and one guide pin 38 are combined to form a minimum unit of the hinge mechanism. (One set)
Is configured. The two guide pins 38 are completely equivalent in shape and size, and have symmetry with respect to the drive shaft 16 in the mounting position and direction.

Each guide pin 38 has a shaft 38a fitted and fixed to the swash plate 19, and a guide hole 3 formed at the tip thereof.
7 and a spherical portion 38b to be engaged. Spherical part 38
b is formed to have a larger diameter than the shaft portion 38a, and
The side opposite to 8a is also formed into a shape that is cut into a plane. The guide pin 38 is provided at least in the spherical portion 38.
Part of b is hollow. The guide pin 38 is
For example, it is formed by forging using a header or a former.

The hollow portion 38c of the guide pin 38 is formed in a shape in which the side of the spherical portion 38b opposite to the shaft portion 38a is open. For example, as shown in FIG. 2A, the shape opposite to the opening substantially reaches the center of the spherical portion 38b.
As shown in (b), the shape reaching the shaft portion 38a, FIG.
As shown in (c), the shaft portion 38a is formed so as to extend to near the fitting portion of the swash plate guide 21. That is, the axial mass of the guide pin 38 is as shown in FIG.
(B)> (c). The guide pin 3
The shape of the swash plate 19 including the swash plate 8 includes a plane including the swing axis of the swash plate 19 and orthogonal to the axis of the drive shaft 16, similarly to the one disclosed in Japanese Patent Application Laid-Open No. 7-293429. Xz plane and yz in a rectangular coordinate system (x, y, z) having an origin at a point of intersection with the center and having an axis coincident with the axis
Products of inertia I _xy of the swash plate 19 with respect to plane, to produce a moment M that increases the inclination angle in the direction in which the capacity is increased by the rotation of the self-state inclination is 0 degrees of the swash plate 19 as shown in FIG. 4 Is set.

Next, the operation of the compressor configured as described above will be described. The swash plate 19 rotates integrally with the rotation of the drive shaft 16, and the rotational motion of the swash plate 19 is converted into reciprocating motion of each piston 23 via the shoe 23a. With the continuation of the driving, the suction, compression and discharge of the refrigerant are sequentially repeated in the compression chamber 11b. The refrigerant supplied from the external refrigerant circuit 32 to the suction chamber 26 is supplied to the compression chamber 11 through the suction port 28.
After being sucked by b and receiving a compression action due to the movement of the piston 23, it is discharged to the discharge chamber 27 via the discharge port 30. The refrigerant discharged into the discharge chamber 27 is sent out from the discharge holes to the external refrigerant circuit 32.

Then, the opening of the control valve 35 is adjusted in accordance with the cooling load, and the communication between the discharge chamber 27 and the crank chamber 15 is changed. When the cooling load is high and the pressure in the suction chamber 26 is high, the opening of the control valve 35 is small, the pressure in the crank chamber 15 (crank pressure Pc) is small, and the swash plate 1
9 becomes large. Then, the stroke of the piston 23 increases, and the compressor 10 is operated with a large capacity.
When the cooling load is low and the pressure in the suction chamber 26 is low, the opening of the control valve 35 increases, the crank pressure Pc increases, and the inclination angle of the swash plate 19 decreases. And piston 2
The stroke of No. 3 is reduced, and the compressor 10 is operated with a small capacity.

The swash plate 19 has a moment generated based on the correlation between the internal pressures of all the cylinder bores in the suction stroke and the compression stroke and the pressure in the crank chamber (crank pressure Pc). The moment of the rotational movement caused by the centrifugal force of the above, the urging force of the pressing spring 16a, etc.
The inclination angle of the swash plate 19 is determined based on the balance.

The moment generated by the rotation of the swash plate 19 includes the swing axis S of the swash plate 19 and the drive shaft 1.
6 is defined as the origin O at the intersection of the plane orthogonal to the axis and the axis, and a rectangular coordinate system (x,
swash plate 1 with respect to the xz plane and the yz plane in (y, z)
9 and products of inertia I _xy of, the ones obtained by multiplying the square of the angular velocity ω of the drive shaft 16.

As shown in FIG. 3A, the y axis of the rectangular coordinate system coincides with the axis of the drive shaft 16, the z axis is parallel to the swing axis S, and the x axis is the y axis and z axis. Perpendicular to the axis. Assuming that the x axis is positive on the top dead center side and the y axis is positive on the front side, the product of inertia I _xy is represented by I _xy = ∫xydm. Where dm
Is the minute mass of the swash plate 19 including the guide pins. Therefore, the swash plate 19 has the same diameter, number,
Are the same, the outer diameter of the guide pin 38 is the same, and the rotational speed (angular speed ω) is the same, the moment of the rotational motion is determined by the distance of the guide pin 38 from the plane (xz plane) including the swash plate body 20. different.

The swash plate 19 is made of aluminum-based swash plate main body 20.
Is press-fitted and fixed to the swash plate guide 21 made of an iron-based metal, in order to secure the press-fitting margin, as shown in FIG.
The distance L from the plane is about 20% larger than that of the swash plate 19 made entirely of iron-based metal as shown in FIG. As a result, products of inertia I _xy, even if the shape of the guide pin 38 the same, becomes significantly greater than the iron-based metallic swash plate 19.

The moment M generated by the rotation of the swash plate 19 near the minimum tilt angle acts in a direction in which the tilt angle of the swash plate 19 increases. Therefore, the product of inertia I _xy is large, the influence is increased during high-speed rotation, the crank pressure P
When control is performed to increase c and decrease the inclination angle of the swash plate 19, the crank pressure Pc variably necessary increases. And
Even if the mass of the guide pins 38 are the same, the mass of the partial distance is large from the xy plane, i.e. towards the distal end side of the mass of the guide pin 38 is large inertia product I _xy increases.

In this embodiment, the hollow portion 38 is formed so that the mass of the spherical portion 38b at the tip of the guide pin 38 is reduced.
Since c is formed, products of inertia I _xy becomes smaller as compared with the conventional mass of the guide pin 38 is not formed are the same even hollow portion 38c, also the moment M based on the rotation of the swash plate 19 It becomes smaller than the conventional moment Mo. Thus, the crank pressure Pc required to change the inclination angle of the swash plate 19 is reduced. If the crank pressure Pc required to change the tilt angle is high, the tilt angle is likely to shift with a slight change in the compression load even if the desired tilt angle is adjusted, and hunting is likely to occur. The hunting is less likely to occur due to the lower. This can be understood from the fact that the change rate of the moment M with respect to the inclination angle of the swash plate 19 is smaller than the moment Mo of the conventional swash plate provided with the guide pins as shown in FIG. The reduction in the weight of the guide pin 39 leads to a reduction in the weight of the counterweight portion 21b, and contributes to a reduction in the rate of change of the rotation motor M of the swash plate 19.

This embodiment has the following effects. (1) Since at least a part of the guide pin 38 constituting the hinge mechanism 22 is formed in a hollow shape, the guide which affects the rotational moment accompanying the integral rotation of the swash plate 19 including the guide pin 38 with the drive shaft 16 is provided. The product of inertia at the pin 38 is reduced. As a result, the crank pressure Pc required for changing the capacity during high-speed rotation can be reduced, and the occurrence of hunting can be suppressed. Further, when the power transmission is a clutchless type, the swash plate 1 in the off operation is used.
The inclination of 9 is close to 0 degrees, and power consumption can be reduced. When a check valve is provided downstream of the discharge hole, the valve opening pressure can be reduced, and the performance is improved.

(2) The hinge mechanism 22 is configured such that the spherical portion 38b of the guide pin 38 projecting from the swash plate 19 engages with the guide hole 37 of the support arm 36 projecting from the lug plate 17. ing. Therefore, when the guide hole 37 is simply formed in a cylindrical surface, the movement can be smoothly guided when the swash plate 19 tilts while sliding on the drive shaft 16.

[0047] (3) guide when the hollow of the portion of the pin 38, the products of inertia I guide affects the _xy values is larger pin 38
Since a part of the spherical portion 38b located at the distal end of the hollow portion is hollow, even if the weight is the same, the effect is greater than if the proximal end side is hollow.

(4) The shape of the hollow portion 38c formed in the guide pin 38 is such that the side of the spherical portion 38b opposite to the shaft portion 38a is open, and the depth thereof is changed so that the mass at the tip end side of the guide pin 38 is obtained. Was reduced. Therefore, the hollow part 3
You can change the value of the products of inertia I _xy by changing the depth of 8c. Further, the processing of the hollow portion 38c becomes easy.

(5) Since the shape of the spherical portion 38b of the guide pin 38 is also formed by cutting off the opposite side to the shaft portion 38a, the shape of the spherical portion 38b on the opposite side to the shaft portion 38a is smaller than that of a conventional guide pin having a spherical shape on the opposite side. , the value of the product of inertia I _xy curvature even identical spherical portion 38b is reduced.

(6) The guide pins 38 are formed by forging. Therefore, the strength is higher than when the hollow portion 38c of the guide pin 38 is formed by cutting.
If the guide pins 38 are manufactured with a header or a former, mass productivity can be ensured.

(7) Since the swash plate 19 is composed of the swash plate main body 20 made of aluminum-based metal and the swash plate guide 21 made of iron-based metal, the entire swash plate 19 is made of iron-based metal. In comparison with the case, the entire swash plate 19 becomes lighter, and the compressor can be made lighter.

(8) The swash plate 19 is directly supported on the drive shaft 16 through the through hole 21a. Therefore, between the swash plate 19 and the drive shaft 16, for example, the drive shaft 1
6, there is no need to provide a sleeve slidably disposed on the sleeve 6 and a pivot pin protruding from the sleeve and supporting the swash plate in a tiltable manner, so that the number of parts can be reduced.

(Second Embodiment) Next, a second embodiment will be described with reference to FIGS. In this embodiment, the configuration of the hinge mechanism 22 is different from that of the above-described embodiment, and the other configuration is basically the same as that of the above-described embodiment. Therefore, the same portions are denoted by the same reference numerals and description thereof will be omitted, and only different points will be described.

As shown in FIG. 5, a sleeve 39 is slidably provided on the drive shaft 16, and the swash plate guide 21 is provided via a pair of support shafts 40 (only one is shown) protruding from the sleeve 39. It is supported to be tiltable. The support shaft 40 is the drive shaft 1
6 is provided in a direction orthogonal to the direction.

The hinge mechanism 22 includes a swing arm 4 provided on the swash plate guide 21 toward the lug plate 17.
1 and a support arm 42 provided on the lug plate 17
And a guide pin 43 connecting the arms 41 and 42. A pair of swing arms 41 are provided so as to sandwich the support arm 42, and a guide hole 44 is formed in the support arm 42.
Are formed. A mounting hole 45 is formed in the swing arm 41 and extends in parallel with the support shaft 40.
Is fixedly press-fitted into the mounting hole 45 with the protrusions (both ends) inserted into the guide holes 44. The guide hole 44 is provided so that the top dead center position of the piston 23 does not substantially change even if the inclination angle of the swash plate changes.
It has a long hole shape that extends toward the swash plate 19 from the outside with respect to the axis of the drive shaft 16. The guide pin 43 is formed by a cylindrical pipe, and is entirely hollow.

In the hinge mechanism 22 of this embodiment, the guide pin 43 moves along the guide hole 44, whereby the swash plate 19 rotates integrally with the lug plate 17, and the swash plate 19 moves on the drive shaft 16. You will be guided to tilt while sliding.

Therefore, this embodiment has the following effect in addition to the effects (1) and (7) of the above-described embodiment. (9) The guide pin 43 constituting the hinge mechanism 22 is
By moving along the guide hole 44, the swash plate 19 is guided to tilt while sliding on the drive shaft 16. Therefore, the guide pin 43 may have a simple linear shape, and its manufacture is simpler than when a spherical portion is formed.

(10) The guide hole 44 is provided in the support arm 42
And a mounting hole 45 is formed in the swing arm 41. Therefore, the guide hole 44 is connected to the swing arm 4.
1, the structure of the swash plate 19 is simplified.

The embodiment is not limited to the above, and may be configured as follows, for example. In the configuration using the guide pin 38 having the spherical portion 38b as in the first embodiment, the guide pin 38
The shape of the hollow portion 38 is changed as shown in FIGS.
c may penetrate the guide pin 38. Further, as shown in FIG. 7C, the hollow portion 38c may have a shape penetrating through the guide pin 38, and a split 38d may be formed at the press-fit portion at the tip of the shaft portion 38a. In this case, the outer diameter tolerance of the shaft portion 38a can be increased.

In the second embodiment, the guide pin 43 is not formed in a simple pipe shape, but as shown in FIG. 8A, a hollow portion 43a may be formed on both sides of the guide pin 43. As shown in FIG. 8B, both ends corresponding to the mounting holes 45 of the swing arm 41 may be formed in a solid state. When both ends of the guide pin 43 are formed in a solid state, the strength of both ends corresponding to the mounting hole 45 where the compressive reaction force acts greatly on the guide pin 43 is increased, and the life of the guide pin 43 is extended.

In the first embodiment, the swash plate 19 is provided on a sleeve 39 slidably provided on the drive shaft 16 via a support shaft 40 so as to be swingable as in the second embodiment. Is also good. Further, in the second embodiment, the through holes 21 formed in the swash plate guide 21 are similar to the first embodiment.
a with the drive shaft 16 penetrating the swash plate 19
May be supported. Further, a spherical sleeve may be slidably provided on the drive shaft 16, and a swash plate 19 may be supported on the outer peripheral surface of the spherical sleeve.

The combination of the support arm 36 and the guide pin 38 or the combination of the support arm 42, the swing arm 41, the guide pin 43 and the guide hole 44 constituting the hinge mechanism 22 is not limited to two, but may be one. However, it is preferable that there are two sets in terms of rotational balance and stability of driving force transmission.

The swash plate 19 may be made of only one kind of metal such as an iron-based metal. In this case, since the press-fitting margin can reduce the distance between the guide pin 38 and the xz plane becomes unnecessary, smaller products of inertia I _xy I effect coupled with the hollow forming the guide pin 38. When the material of the swash plate 19 is the same as the material of the shoe 23a, a surface treatment (for example, aluminum spraying) is performed on a sliding portion of the swash plate 19 with the shoe 23a to prevent seizure.

In the hinge mechanism 22 of the second embodiment, the guide hole 44 is provided on the swing arm 41 side,
The mounting hole 45 may be provided on the support arm 42 side. The guide pin 38 may be manufactured by cutting or casting instead of forging.

The present invention may be applied to a wobble type variable displacement compressor. The technical ideas other than those described in the claims, which are understood from the embodiments, will be described below together with their effects.

(1) In the invention according to any one of claims 2 to 5, the shape of the spherical portion is formed so that the side opposite to the shaft portion is also cut off. In this case, smaller values of the products of inertia I _xy by weight of the spherical portion is decreased.

[0067]

As described above in detail, according to the compressor provided with the guide pin according to the first to ninth aspects of the present invention and the invention according to the tenth aspect, the capacity is changed at the time of high-speed rotation. In addition, the crank chamber pressure required for power transmission can be reduced, the occurrence of hunting can be suppressed, and the power consumption during off-operation when the power transmission is a clutchless type can be reduced.

[Brief description of the drawings]

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

FIG. 2 is a sectional view of a guide pin.

FIG. 3 is a schematic cross-sectional view of a swash plate explaining an operation.

FIG. 4 is a graph showing a relationship between a tilt angle of a swash plate and a moment.

FIG. 5 is a partial cross-sectional view illustrating a hinge mechanism according to a second embodiment.

6 is a view taken in the direction of the arrow A in FIG.

7A and 7B are cross-sectional views of another embodiment of the guide pin used in the first embodiment, and FIG. 7C is a perspective view of the same.

8A is a sectional view of another embodiment of a guide pin used in the second embodiment, and FIG. 8B is a perspective view of the same.

FIG. 9 is a partial cross-sectional view of a conventional variable displacement compressor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Compressor, 11 ... Cylinder block which comprises a housing, 11a ... Cylinder bore, 12 ... Front housing, 14 ... Rear housing, 15 ... Crank chamber, 16
... Drive shaft, 17 ... Lug plate as rotary support, 1
9: swash plate as cam plate, 22: hinge mechanism, 2
3 piston, 26 suction chamber, 27 discharge chamber, 36, 4
2. Support arm, 37, 44 Guide hole as guide part, 38 Guide pin, 38a Shaft part, 38b Spherical part, 39c Hollow part, 41 Swing arm, 43 Guide pin, 43a Hollow part , 45 ... mounting holes.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Masanobu Tomita 2-1-1 Toyota-cho, Kariya-shi, Aichi F-term in Toyota Industries Corporation (reference) 3H076 AA06 BB32 BB38 BB43 CC12 CC18 CC19 CC20 CC83

Claims (10)

[Claims] 1. A housing including a crank chamber, a suction chamber, a discharge chamber, and a cylinder bore communicating with each of the chambers; a piston reciprocally housed in the cylinder bore; and a rotatable support in the crank chamber. And a cam plate disposed in the crank chamber while being operatively connected to the piston to convert a rotational movement of the drive shaft into a reciprocating movement of the piston and penetrating the drive shaft. A rotating support fixed to the drive shaft so as to be integrally rotatable; and a hinge mechanism interposed between the rotating support and the cam plate, wherein the cam is controlled by controlling a pressure in the crank chamber. In a variable displacement compressor that controls a tilt angle of a plate to change a discharge capacity from the cylinder bore to the discharge chamber due to reciprocation of the piston. A guide pin that constitutes the hinge mechanism, transmits the rotational motion of the rotary support to the cam plate side, and allows the cam plate to tilt while sliding on the drive shaft; A guide pin for a variable displacement compressor having at least a portion made hollow to reduce a product of inertia around a variable fulcrum of the cam plate. 2. The hinge mechanism is fixed to the cam plate, a support arm formed on the rotary support body so as to extend toward the cam plate, a guide portion formed on the support arm. A shaft portion fitted and fixed to the cam plate, and a guide pin formed at the tip thereof and having a spherical portion having a larger diameter than the shaft portion while being engaged with the guide portion. The guide pin of the variable displacement compressor according to claim 1, wherein at least a part of the spherical portion is hollow. 3. The variable-capacity compression according to claim 2, wherein the guide pin has a hollow portion that is open on a side opposite to the shaft portion of the spherical portion and extends to a substantially center of the spherical portion. Machine guide pin. 4. The guide for a variable displacement compressor according to claim 2, wherein the guide pin has a hollow portion which is open on a side of the spherical portion opposite to the shaft portion and reaches the shaft portion. pin. 5. The guide pin has a hollow portion which is open at a side opposite to the shaft portion of the spherical portion and extends to a vicinity of a fitting portion of the shaft portion to the cam plate. The guide pin of the variable displacement compressor according to [1]. 6. A swing arm provided on the cam plate toward the rotary support, a support arm provided on the rotary support, and one of the swing arm and the support arm. A guide hole provided in the arm, a mounting hole formed in the other arm, and a guide pin penetrating the mounting hole and having a protrusion inserted into the guide hole, at least a part of the guide pin is provided. The guide pin of the variable displacement compressor according to claim 1, wherein the guide pin is hollow. 7. The guide pin of the variable displacement compressor according to claim 6, wherein the guide hole is formed in the support arm, and the mounting hole is formed in the swing arm. 8. The variable according to claim 7, wherein a pair of the swing arms are provided so as to sandwich the support arm, and both ends of the guide pins corresponding to mounting holes of the swing arm are formed in a solid state. Guide pin of capacity compressor. 9. The guide pin of a variable displacement compressor according to claim 1, wherein said guide pin is formed by forging. 10. A variable displacement compressor comprising the hinge mechanism and the guide pin according to claim 1. Description: