JPH0942149A - Variable displacement type swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure the smooth displacement operation of a swash plate in a simple structure by forming a through hole to permit an inclination displacement of this swash plate extending over the whole control range via a support part which is partially butted to a sleeve at a side to be opposed to a hinge mechanism as holding an axial center between. SOLUTION: In this variable displacement type swash plate compressor, such a moment as making a swash plate 11 be tilted on the basis of compressive reaction or the like, is received by a sleeve 18 being butted to a support part 20a of this swash plate 11, but it follows in the wake of movements of the support part 20a attendant upon the inclination displacement of this swash plate 11, the sleeve 18 is also driven in the same direction on a driving shaft 6, therefore a substantial sliding distance of the support part 20a is contracted to a very little relative displacement to be produced in a gap with the sleeve 18. Accordingly, wear in the driving shaft 6 is effectively prevented by a conversion to a surface contact sliding motion with the sleeve 18, not to mention sliding wear between both of them to be butted, and thus the smooth inclination displacement operation of the swash plate 11 is surely ensured.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity swash plate compressor used in a vehicle air conditioner or the like.

[0002]

2. Description of the Related Art Heretofore, many compressors have been proposed in which a piston stroke is changed by tilting displacement of a swash plate (including a structure for connecting with a swaying plate) to variably control a discharge capacity. ing. For example, Japanese Patent Laid-Open No. Sho 62
The compressor disclosed in Japanese Patent Publication No. 87678 is intended to simplify a swash plate supporting device, and is characterized in that a drive shaft is inserted through a boss portion of the swash plate, Has a structure in which a through hole is formed which partially contacts the drive shaft to regulate the radial position and allows the inclination angle of the swash plate to change. That is, the slider and the pivot pin that have been conventionally used are omitted in order to support the swash plate and give a constant displacement trajectory to the swash plate, and the swash plate 5 has the lower curved surface 55b in the through hole 55. Is guided through local contact with the drive shaft 3 so that a constant displacement trajectory is maintained.

[0003]

However, in the above-mentioned compressor, the supporting mechanism in which the moment acting in the inclination direction of the swash plate 5 based on the compression reaction force includes the elongated hole 43 and the pin 53a. And the lower curved surface 55b in contact with the drive shaft 3, the curved surface 55b receives the load when the swash plate 5 is tilted.
The line will slide within a predetermined range of. In addition, due to the structure of the swash plate 5, a moment based on the compression reaction force also acts in a direction orthogonal to the above-mentioned inclination direction, and this moment is supported by the short diameter portion of the long hole forming the through hole 55. However, the front and rear edges of the short-diameter portion existing at the diagonal position also cause similar sliding contact with the drive shaft 3 when the swash plate 5 is tilted.

Moreover, as seen in the above-mentioned compressor, in the structure in which the support mechanism for the swash plate 5 exists independently, the capacity for receiving the moment is greater than that in the case where the left and right double support mechanisms are provided. It is extremely weak and the sliding surface pressure with the drive shaft 3 inevitably rises. Therefore, if the line contact sliding between the drive shaft 3 and the through hole 55 is repeated with a relatively long sliding distance, local wear progresses on both sides, which impairs accurate and smooth tilt angle displacement of the swash plate 5. It may cause a problem.

SUMMARY OF THE INVENTION The present invention has as its technical subject to ensure a smooth displacement operation of a swash plate with a simple structure.

[0006]

According to a first aspect of the present invention, there is provided a compressor in which a plurality of bores are arranged in parallel to form a compressor outer shell and a crank chamber is formed therein. A front housing that closes the front end of the cylinder block; a drive shaft that is rotatably supported by the cylinder block and the front housing; a rear housing that has a suction chamber and a discharge chamber and closes the rear end of the cylinder block; A rotor fixed to a drive shaft in the crank chamber, a swash plate fitted to the drive shaft through a through hole and connected to the rotor via a hinge mechanism, and a swash plate controlled to be tiltable. In a variable displacement swash plate compressor including a piston that directly moves in the bore in cooperation with the swash plate, a displacement between the through hole and the drive shaft of the swash plate follows the inclination displacement of the swash plate. Drive shaft A sleeve that is driven along the axial direction, and the through hole is provided over the entire control range through a support portion that locally abuts the sleeve on the side facing the hinge mechanism with the axial center interposed therebetween. It is characterized in that it is formed to allow the inclination displacement of the plate.

A compressor according to a second aspect of the invention is characterized in that the sleeve follows the entire displacement range of the tilt angle of the swash plate and follows the drive shaft. The compressor according to claim 3 is characterized in that the sleeve is abutted against the swash plate by the biasing force of a spring. In the compressor according to claim 4, the swash plate is abutted against a flange formed on the sleeve, and the abutting portion with the flange is between the support portion regardless of the inclination displacement of the swash plate. It is characterized in that the axial distance of is formed almost unchanged.

[0008]

In the compressor according to any one of claims 1 to 3, the swash plate connected to the rotor through the hinge mechanism is fitted into the drive shaft through the through hole, and the swash plate is inclined between the through hole and the drive shaft. A sleeve that follows the tilt displacement of the plate and that follows the axial direction of the drive shaft is provided. The through hole is configured to allow the tilt angle displacement of the swash plate over the entire control range around a pivot set over the sleeve on the side facing the hinge mechanism with the axis centered therebetween. A supporting portion that restricts a radial position of the swash plate by a local contact with the bulge, more specifically, a radial position in a plane including the drive shaft center and the top dead center position of the swash plate is arc-shaped about the pivot axis. Is formed in.

Therefore, when the inclination of the swash plate that cooperates with the hinge mechanism is displaced, the support portion in the through hole moves in the axial direction while keeping contact with the sleeve, but with the spring. The sleeve, which is in abutment with the swash plate via a force or the like, also follows the swash plate and similarly follows the drive shaft in the axial direction. As a result, the substantial sliding distance of the support is reduced to the very slight relative displacement that occurs between the abutment of the swash plate against the sleeve and the support. Of course, as in the compressor according to the fourth aspect, the axial distance between the abutting portion and the supporting portion is formed substantially unchanged regardless of the inclination displacement of the swash plate, and the supporting portion and the sleeve are formed. It is sufficiently possible to erase the sliding of the lines to such an extent that they can be substantially ignored.

[0010]

Embodiments of the present invention will be described below with reference to the drawings. In this compressor, as shown in FIG. 1, a front housing 2 is joined to a front end side of a cylinder block 1 and a rear housing 3 is joined to a rear end side thereof via a valve plate 4. A drive shaft 6 extending in the axial direction is accommodated in a crank chamber 5 formed by the cylinder block 1 and the front housing 2, and the drive shaft 6 is rotatably supported by bearings 7a and 7b. A plurality of cylinder bores 8 are formed around the drive shaft 6 in the cylinder block 1, and pistons 9 are fitted in the respective cylinder bores 8.

In the crank chamber 5, a rotor 10 is fixedly attached to a drive shaft 6 and supported by a bearing 19 between the rotor 10 and the front housing 2. A swash plate 11 is provided behind the rotor 10 by a through hole 20. A sleeve 18 is mounted between the through hole 20 and the drive shaft 6 while being fitted. The through hole 20 allows tilt displacement of the swash plate 11 over the entire control range around a pivot Y set across the sleeve 18 on the side facing the hinge mechanism K described later with the drive shaft interposed therebetween. As shown in FIG. 4, the swash plate 11 is locally abutted against the sleeve 18 in the radial direction of the swash plate 11, more specifically, the drive shaft center and the top dead center of the swash plate 11, as shown in FIG. A support portion 20a that restricts a radial position in a plane including a point position is formed in an arc shape around the pivot Y, and a margin inclination angle θ ₁ of 10 to 15 ° is formed on the inner diameter surface 20b on the minimum inclination side of the bending elongated hole. A margin tilt angle θ ₂ of 1 to 2 ° is given to the inner diameter surface 20c on the maximum tilt angle side. A flat regulation surface 20d is formed on both sides of the through hole 20 in association with the formation of the bent elongated hole.

The sleeve 18 is provided with a flange 18a at the front end thereof, and the flange 18a constantly abuts against a refracting abutment portion 11a formed on the front surface of the swash plate 11, so that the sleeve 18 is formed. So as to follow the displacement of the swash plate 11 on the drive shaft 6 and the rotor 10 and the sleeve 18.
A coil spring 12 is interposed between and. And
As shown in FIG. 1, shoes 14, 14 having hemispherical portions as a connecting mechanism are brought into contact with the outer peripheral portion of the swash plate 11, and the hemispherical portions of these shoes 14, 14 engage with the spherical bearing surface of the piston 9. Thus, the plurality of pistons 9 moored to the swash plate 11 are housed in the respective cylinder bores 8 so as to be capable of reciprocating.

On the front side of the swash plate 11, a bracket 15 constituting one side of the hinge mechanism K is provided in a protruding manner. A base end of a guide pin 16 is fixed to the bracket 15, and a spherical portion is attached to the tip. 16a is formed. The rotor 10
A support arm 17, which constitutes the other part of the hinge mechanism K, protrudes along the axial direction so as to face the guide pin 16. A guide hole 17a is formed at the tip of the support arm 17 in parallel with a plane determined by the axis and the top dead center position of the swash plate 11 and inclined backward toward the axis. The center line of the inclined guide hole 17a is set so that the top dead center position of the piston 9 is hardly displaced during the inclination displacement of the swash plate 11 constrained by the spherical portion 16a fitted in the guide hole 17a. It is set.

The inside of the rear housing 3 is divided into a suction chamber 30 and a discharge chamber 31, and a suction port 32 and a discharge port 33 are formed in the valve plate 4 so as to correspond to the cylinder bore 8, and the valve plate 4 and the piston are formed. And a compression chamber formed between the suction chamber 3 and the suction port 3 through the suction port 32 and the discharge port 33.
0 and the discharge chamber 31. Each suction port 32
Is a suction valve that opens and closes the suction port 32 according to the reciprocating movement of the piston 9, and a discharge valve that opens and closes the discharge port 33 according to the reciprocating movement of the piston 9 while being regulated by the retainer 34 ( (Not shown). Further, the rear housing 3 is equipped with a control valve (not shown) for adjusting the pressure of the crank chamber 5.

When the swash plate 11 that cooperates with the drive shaft 6 is rotated when the compressor configured as described above is started, each piston 9 is moved through the shoes 14 and 14 into the cylinder bore 8.
The refrigerant gas is sucked into the compression chamber from the suction chamber 30 by the reciprocating motion of the inside of the suction chamber 30, and the refrigerant gas is compressed.
It is discharged to 1. At this time, the discharge capacity of the refrigerant gas discharged to the discharge chamber 31 is controlled by adjusting the pressure in the crank chamber 5 by the control valve.

That is, in the state of FIG. 2, if the pressure in the crank chamber 5 rises by adjusting the pressure of the control valve, the back pressure acting on the piston 9 rises, and the tilt angle of the swash plate 11 decreases. That is, the spherical portion 16a of the guide pin 16 that constitutes the hinge mechanism K rotates in the guide hole 17a in the counterclockwise direction and slides along the guide hole 17a from the outside toward the axial center side. At the same time, the swash plate 11 rotates and retreats while the supporting portion 20a centering on the pivot Y maintains the abutting contact with the sleeve 18. As a result, the swash plate 1
The tilt angle of No. 1 is reduced to the state of FIG.
The discharge capacity becomes smaller according to the stroke.

On the contrary, in the state of FIG. 3, if the pressure in the crank chamber 5 is lowered by adjusting the pressure of the control valve, the back pressure acting on the piston 9 is lowered, and the inclination angle of the swash plate 11 is increased. That is, the spherical portion 16a of the guide pin 16 rotates in the guide hole 17a in the clockwise direction and slides along the guide hole 17a in a direction away from the axial center from the inside, and at the same time, the swash plate 11 is supported. The portion 20a rotates and advances while maintaining the contact with the sleeve 18. This allows
The inclination angle of the swash plate 11 is enlarged to change to the state of FIG. 2, and the discharge capacity increases according to the stroke of the piston 9.

As described above, the tilt angle of the swash plate 11 is controlled based on the operation of the control valve that detects the heat load, and when the tilt angle of the swash plate 11 is displaced, the supporting portion 20a in the through hole 20 is moved as described above. Although it moves in the axial direction while maintaining the contact with the sleeve 18, the sleeve 18 which is always in abutment with the swash plate 11 by the urging force of the coil spring 12 is attached to the swash plate 11. Similarly, it follows the drive shaft 6 in the axial direction in a follow-up manner. As a result, the substantial sliding distance of the support portion 20a is shown in FIGS. 2 and 3, which is a very small relative displacement between the support portion 20a and the sleeve 18 that abuts against the abutment portion 11a. Difference in axial distance between the abutment portion 11a and the support portion 20a at the maximum and minimum inclination angles (D-d)
Is reduced to.

The swash plate 11 has a minimum tilt angle regulated by the counterbore surface 11b formed at the rear portion of the through hole 20 contacting the circlip 13 locked to the drive shaft 6 (FIG. 3). On the other hand, the maximum tilt angle is restricted by the front end surface 11c formed in a slanted shape in the lower portion of the swash plate 11 coming into contact with the rear end surface 10a of the rotor 10 (FIG. 2). During this time,
As for the displaceable angle of the swash plate 11 with respect to the sleeve 18, the margins of θ ₁ and θ ₂ are given on the minimum and maximum inclination sides, respectively, as described above, but especially the margin inclination angle θ ₁ on the minimum inclination side.
(10 to 15 °) is the spherical portion 16 with respect to the guide hole 17a.
It is easy to insert a, which contributes to the improvement of the assembling property.

The axial distance D between the abutment portion 11a and the support portion 20a at the minimum inclination angle shown in FIG. 3 is made substantially equal to the same distance d at the maximum inclination angle shown in FIG. If design consideration is added to the shape, the support part 2
The sliding between 0a and the sleeve 18 can be erased to a substantially negligible level. In the above embodiment, the sleeve 18 follows the entire range of the tilt displacement of the swash plate 11 and follows the structure on the drive shaft 6. However, for example, by the circlip 13 attached to the drive shaft 6, the sleeve 18 is used. It is also possible to restrict only the retracted position of 18 and to separately restrict the minimum inclination angle of the swash plate 11 by the support portion interposed between the swash plate 11 and the cylinder block 1.

The biasing means (coil spring 12) of the sleeve 18 for following the tilt displacement of the swash plate 11 may be arranged on either side of the front and rear of the sleeve 18, and further on the outer peripheral portion of the sleeve 18. It is also possible to omit the coil spring 12 by attaching a pair of front and rear circlips and appropriately abutting the circlips on the front and rear surfaces of the swash plate 11 to promote the follower movement.

[0022]

As described in detail above, the compressor of the present invention is
Since it has the configuration described in the claims,
It has the following excellent effects. (1) In the compressor of the present invention, although the moment to incline the swash plate based on the compression reaction force or the like is received by the sleeve that abuts the supporting portion of the swash plate, the swash plate is received. Following the movement of the support part due to the inclination displacement of the sleeve, the sleeve also follows the same direction on the drive shaft, and the substantial sliding distance of the support part causes a very small relative displacement between the sleeve and the sleeve. As the sliding wear of the two abutting parts is reduced, the wear of the drive shaft is effectively prevented by conversion to surface contact sliding with the sleeve, and a smooth tilt angle displacement operation of the swash plate is reliably guaranteed. To be done. (2) Moreover, in the compressor adopting the independent hinge mechanism,
Although the moment acting in the direction orthogonal to the inclination direction of the swash plate is considerably large, the relative displacement itself between the swash plate and the sleeve is small, so that it occurs between the side edge of the through hole and the sleeve. Easy wear is likewise prevented.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing the entire structure of a compressor according to an embodiment of the present invention.

FIG. 2 is a sectional view of an essential part showing a maximum inclination state of a swash plate in the compressor.

FIG. 3 is a cross-sectional view of essential parts showing a minimum inclination state of a swash plate in the compressor.

FIG. 4 is an enlarged sectional view showing a main part of a swash plate in the compressor.

[Explanation of symbols]

1 ... Cylinder block 2 ... Front housing 3
… Rear housing 5… Crank chamber 6… Drive shaft 8
… Cylinder bore 9… Piston 10… Rotor 11
… Swash plate 11a… Abutting part 12… Coil spring
14 ... shoe 18 ... sleeve 18a ... flange 2
0 ... Through-hole 20a ... Support part 30 ... Suction chamber
31 ... Discharge chamber K ... Hinge mechanism Y ... Axis

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yoichi Okadome, 2-chome, Toyota-cho, Kariya City, Aichi Stock Company Toyota Industries Corp.

Claims (4)

[Claims] 1. A cylinder block having a plurality of bores arranged side by side to form an outer shell of a compressor, a front housing for closing a front end of the cylinder block by forming a crank chamber therein, and the cylinder block and the front housing. A drive shaft rotatably supported by the rear housing, a rear housing having a suction chamber and a discharge chamber for closing the rear end of the cylinder block,
A rotor fixed to a drive shaft in the crank chamber, a swash plate fitted to the drive shaft through a through hole and connected to the rotor via a hinge mechanism, and a swash plate controlled to be tiltable. In a variable displacement swash plate compressor including a piston that directly moves in the bore in cooperation with the swash plate, a displacement between the through hole and the drive shaft of the swash plate follows the inclination displacement of the swash plate. A sleeve that follows the drive shaft in the axial direction is installed.
The through hole is formed to allow tilt displacement of the swash plate over the entire control range through a support portion that locally abuts the sleeve on the side facing the hinge mechanism with the shaft center interposed therebetween. Variable capacity swash plate type compressor. 2. The variable displacement type swash plate compressor according to claim 1, wherein the sleeve follows the entire range of inclination displacement of the swash plate and follows the drive shaft. 3. The variable displacement type swash plate compressor according to claim 1, wherein the sleeve is abutted against the swash plate by a biasing force of a spring. 4. The swash plate is abutted against a flange formed on the sleeve, and an abutting portion with the flange is an axial distance between the swash plate and the supporting portion regardless of inclination displacement of the swash plate. Are formed substantially unchanged.
Alternatively, the capacity-variable swash plate compressor described in 3.