JPH07158560A - Variable displacement swash plate type compressor - Google Patents

Abstract

PURPOSE:To absorb the unbalance of a swash plate in the rotating time effectively, and to stabilize the performance and the controllability without making the working of the sliding surface difficult. CONSTITUTION:To a swash plate 12, a sliding surface 12a engaged with a piston 9 through shoes 14 and 14, brackets 12b and 12b of hinge mechanisms K and K formed between a rotor 10, and a through hole 20 with a driving shaft 6, are formed integrally. A counter weight 15 projecting to the rotor 10 side in the area including its bottom dead center, and bending and extending further to the outer side, is installed to the swash plate 12.

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 A conventional variable capacity swash plate compressor (hereinafter referred to as
Simply called a compressor. ), JP-A-4-303184
The one described in Japanese Patent Publication is known. In this compressor, a crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connected to these are defined in the housing. In the crank chamber, the rotor is supported on the drive shaft so that it can rotate synchronously,
A swash plate is pivotally supported between the rotor and the drive shaft via a hinge mechanism at the top dead center side and via a sleeve between the rotor and the drive shaft so as to be synchronously rotatable and tiltable. This swash plate is composed of a rotary swash plate having a sliding surface that engages with a piston through each shoe, and a rotary drive body that fixes the rotary swash plate with a tightening ring. The rotary drive body projects to the rotor side in a region including a hinge mechanism connecting portion formed between the rotor and the drive shaft, a drive shaft fitting portion via a sleeve, and bottom dead center, and further faces outward. A counterweight portion that bends and extends is integrally formed. Each piston is housed in each cylinder bore. Further, the housing is equipped with a control valve for adjusting the pressure in the crank chamber.

In this compressor, the piston is reciprocated in the cylinder bore when the swash plate rotates at a predetermined inclination angle as the drive shaft is driven. As a result, the refrigerant gas is sucked into the cylinder bore from the suction chamber, compressed, and then discharged into the discharge chamber. Then, the tilt angle of the swash plate is displaced by adjusting the pressure in the crank chamber by the control valve, and thereby the discharge capacity of the refrigerant gas discharged into the discharge chamber is controlled.

[0004]

However, in the above-mentioned compressor, the swash plate is composed of the rotary driving body integrally including the connecting portion, the fitting portion, and the counter weight portion, and the rotary swash plate having the sliding surface. Therefore, there is a possibility that the performance may vary. That is, in such a compressor, since the tilt angle of the swash plate is determined by the positional relationship between the connecting portion and the rotor via the hinge mechanism and the positional relationship between the fitting portion and the drive shaft via the sleeve, the rotary drive unit By having the connecting portion and the fitting portion integrally with each other, the inclination angle of the rotary drive body is preferably secured. However, since the rotary swash plate that has a sliding surface that determines the positional relationship between the piston and the cylinder bore is separate from this rotary drive body, the rotary swash plate is slightly inclined with respect to the rotary drive body. If fixed, the tilt angle of the rotary drive member is not accurately applied to the sliding surface, and the positional relationship between the piston and the cylinder bore shifts, causing variations in variable characteristics and compression performance.

On the other hand, if the swash plate having the sliding surface integrally with the connecting portion, the fitting portion and the counterweight portion is constructed, the imbalance during rotation of the swash plate is effectively absorbed. Therefore, when the counterweight portion is located as radially as possible from the axis of the drive shaft, the counterweight portion covers the sliding surface, which makes it difficult to machine the sliding surface.

An object of the present invention is to effectively absorb unbalance during rotation of a swash plate, and at the same time, to stabilize performance and controllability without making machining of a sliding surface difficult. .

[0007]

In the compressor of the present invention, in order to solve the above-mentioned problems, a crank chamber, a suction chamber, a discharge chamber, and cylinder bores connected to these are defined and formed in the housing, and each of the cylinder bores is formed. A piston is housed in each of the housings so that the pistons can reciprocate, and a rotor positioned in the crank chamber is rotatably supported by a drive shaft supported by the housing, and a hinge mechanism is provided at the top dead center side with the rotor. A swash plate connected via the swash plate is fitted so as to be tiltable, and a pair of shoes for converting the rocking motion of the swash plate into the reciprocating motion of each piston is interposed between the swash plate and the piston. In a variable displacement type swash plate compressor configured to control the tilt angle of the swash plate by the pressure in the crank chamber to change the discharge capacity, the swash plate is provided with the piston through the shoes. The sliding surface that engages with the tongue, the connecting portion of the hinge mechanism that is formed between the rotor and the rotor, and the fitting portion that engages with the drive shaft are integrally formed, and the region includes the bottom dead center thereof. In addition, a new structure is adopted in which a counter weight that projects toward the rotor side and is bent outwardly is attached.

In the compressor of the present invention, it is preferable that the front end face of the swash plate contacts the rear end face of the rotor to maintain the maximum tilt angle.

[0009]

In the compressor of the present invention, the swash plate integrally has the sliding surface, the connecting portion and the fitting portion, and the counter weight is attached to the swash plate. Even in such a compressor, since the tilt angle of the swash plate is determined by the positional relationship between the connecting portion and the rotor via the hinge mechanism and the positional relationship between the fitting portion and the drive shaft, the swash plate is fitted to the connecting portion. By having the joint part integrally, the tilt angle is suitably secured. Also, with this compressor,
Since the sliding surface that determines the positional relationship between the piston and the cylinder bore is formed on this swash plate, the inclination angle of the swash plate is accurately applied to the sliding surface, and the positional relationship between the piston and the cylinder bore may shift. There is no. Therefore, there is no variation in variable characteristics and compression performance.

Further, since the counterweight is mounted on the swash plate integrally having the sliding surface, the connecting portion and the fitting portion, it is possible to mount the counterweight after processing the sliding surface. . For this reason, machining of the sliding surface becomes easy,
At the same time, in order to effectively absorb the imbalance during rotation of the swash plate, the counterweight can be positioned as radially outward as possible from the axial center of the drive shaft so as to cover the sliding surface.

When the maximum inclination angle is maintained by the front end surface of the swash plate contacting the rear end surface of the rotor, a force is applied from the rotor to the counter weight by providing a gap between the counter weight and the rotor. Since it can be prevented from acting, the counterweight can be mounted by a simple mounting means.

[0012]

Embodiments of the present invention will be described below with reference to the drawings. In this compressor, as shown in FIG. 1, the front housing 2 is joined to the front end side of the cylinder block 1 with a through bolt 21 and the rear housing 3 is joined to the rear end side with a through bolt 21 via a valve plate 4. Has been done. A drive shaft 6 extending in the axial direction is housed in a crank chamber 5 formed by the cylinder block 1 and the front housing 2, and the drive shaft 6 is a shaft sealing device 7c.
And rotatably supported by bearings 7a and 7b. A plurality of cylinder bores 8 are formed in the cylinder block 1 at positions surrounding the drive shaft 6, and pistons 9 are inserted into the respective cylinder bores 8.

In the crank chamber 5, a rotor 10 is supported by a drive shaft 6 between the drive shaft 6 and a front housing 2 via a bearing 11 so as to be rotatable in synchronization with the drive shaft 6, and a swash plate 12 is provided behind the rotor 10. Equipped. And the rotor 1
0 and the swash plate 12 have a pressing spring 13 interposed therebetween, and the pressing spring 13 biases the swash plate 12 toward the rear housing 3.

As shown in FIG. 2, the swash plate 12 has smooth ring-shaped sliding surfaces 12a formed on the outer peripheral sides of both end surfaces.
As shown in FIG. 1, hemispherical shoes 14, 14 are in contact with the sliding surface 12a. These shoes 14, 14
The outer peripheral surface of is engaged with the ball bearing surface of the piston 9, and each piston 9 is housed in each cylinder bore 8 so as to be capable of reciprocating.

As shown in FIGS. 1 and 2, the swash plate 1
A pair of brackets 12b and 12b project across the top dead center position T of the swash plate 12 with the drive shaft 6 interposed between the slide surface 12a and the rotor 10 near the top dead center. It is set up. One end of each guide pin 12c, 12c is fixed to each bracket 12b, 12b.
Spheres 12d and 12d are fixed to the other ends of c and 12c. Thus, in this compressor, the bracket 12b,
12b, guide pins 12c, 12c and spheres 12d, 1
The connecting portion, which is a part of the hinge mechanism K described later, is configured by 2d. As shown in FIG. 2, between the brackets 12b and 12b, there is a weight reducing portion 12 having a through hole in the center.
f is formed.

Further, a through hole 20 is provided as a fitting portion in the central region of the swash plate 12, and the drive shaft 6 is provided in the through hole 20.
Has been inserted. Further, on the bottom dead center side and the rotor 10 side in the inner region of the swash plate 12, a radial surface is extended from the axial center of the drive shaft 6, and the sliding surface 12a is provided while avoiding the shoe 14 on the rotor 10 side. The counterweight 15 is covered and attached by rivets 16.

The method of mounting the counterweight 15 on the swash plate 12 was as follows. That is, in FIG.
As shown in (B), the swash plate 12 with the sliding surface 12a processed
Four rivet holes 12e are formed at the bottom dead center side of the inner region of the. Further, as shown in FIGS. 3A and 3B, the counterweight 15 is also provided with four rivet holes 15a aligned with the rivet holes 12e. Then, on the side of the bottom dead center of the swash plate 12 and on the side of the rotor 10, the counterweight 15 is brought into contact with the rivet holes 12e and 15a in alignment with each other, and the rivet 16 is inserted from the side of the rotor 10. After that, the protruding end of the rivet 16 is caulked to mount the swash plate 12 and the counterweight 15 as shown in FIGS. 4 (A) and 4 (B).

Thus, in this compressor, the swash plate 12 has the sliding surface 12a, the brackets 12b and 12b, the guide pins 12c and 12c and the spherical portions 12d and 12d, and the through hole 20.
And a counterweight 15 on the swash plate 12.
Is installed. The swash plate 12 has a front end surface 12g closer to the through hole 20 than the inner area where the counterweight 15 is attached.
The maximum inclination angle is maintained by abutting the rear end face 10a of the inner region of the rotor 10. On the other hand, in the swash plate 12, a part of the through hole 20 on the cylinder block 1 side has a circlip 2
By abutting with 2, the minimum tilt angle is maintained.

Further, as shown in FIG. 1, a pair of support arms 17, 17 forming the rest of the hinge mechanism K, K are provided on the upper portion of the rotor 10 so as to face the guide pins 12c, 12c. It projects to the rear in the axial direction. The tip end of each support arm 17, 17 has a shaft center of the drive shaft 6 and a swash plate 1.
2 is parallel to the plane determined by the top dead center position T of 2 and in the direction approaching the axis of the drive shaft 6 from the outside.
a and 17a are linearly provided. The directions of the center lines of the guide holes 17a, 17a are set so that the top dead center position of the piston 9 is hardly displaced back and forth regardless of the tilt displacement of the swash plate 12. These guide holes 17
As shown in FIG. 1, spherical portions 12d and 12d of the guide pins 12c and 12c are rotatably and slidably inserted into the a and 17a, respectively. Weight-reducing portions 17b and 17b are also formed at the base ends of the support arms 17 and 17, respectively.

Further, inside the rear housing 3, the suction chamber 3
It is divided into 0 and the discharge chamber 31. The valve plate 4 has a suction port 32 and a discharge port 3 corresponding to each cylinder bore 8.
3 is formed as an opening, and the compression chamber formed between the valve plate 4 and the piston 9 is a suction port 32 and a discharge port 33.
It is communicated with the suction chamber 30 and the discharge chamber 31 via. Each suction port 32 is provided with a suction valve (not shown) that opens and closes the suction port 32 according to the reciprocating movement of the piston 9, and each discharge port 33 restricts the discharge port 33 to the retainer 34 according to the reciprocating movement of the piston 9. A discharge valve (not shown) that opens and closes while being opened is provided. Further, the rear housing 3 is equipped with a control valve (not shown) for adjusting the pressure of the crank chamber 5.

In the compressor configured as described above,
When the swash plate 12 rotates in accordance with the drive of the drive shaft 6 shown in FIG. 1, the shoes 14 and 14 move back and forth while sliding on the sliding surface 12 a of the swash plate 12. Therefore, each piston 9 reciprocates in the cylinder bore 8, whereby the refrigerant gas is sucked from the suction chamber 30 into the compression chamber, and the refrigerant gas is compressed and then discharged to the discharge chamber 31. 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, 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 12 decreases. That is, the spheres 12d and 12d of the swash plate 12 rotate counterclockwise in the guide holes 17a and 17a of the hinge mechanism K, and the guide holes 17a and 17a from the outside toward the axial center along the center line. Slide in the direction toward. Further, the swash plate 12 rotates counterclockwise while bringing the peripheral surface of the drive shaft 6 into contact with the inner surface of the through hole 20, and bends to the pressing spring 13 and retracts. As a result, the inclination angle of the swash plate 12 becomes smaller, so that the stroke of the piston 9 becomes smaller and the discharge capacity becomes smaller.

On the contrary, 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 12 is increased. That is, the spheres 12d, 12d of the swash plate 12 rotate in the guide holes 17a, 17a of the hinge mechanism K in the clockwise direction, and the insides of the guide holes 17a, 17a along the center line from the inside toward the axis. It slides away. Further, the swash plate 12 has the through hole 2
While rotating the drive shaft 6 in the clockwise direction while bringing the peripheral surface of the drive shaft 6 into contact with the inner surface of 0, it moves forward against the pressing spring 13. As a result, the inclination angle of the swash plate 12 is increased, so that the stroke of the piston 9 is extended and the discharge capacity is increased.

In the meantime, in this compressor, the counterweight 15 tilts together with the swash plate 12, so that a large centrifugal force can be applied to the swash plate 12 during high-speed operation, which requires only a small cooling capacity. For this reason, at this time, even if the pressure in the crank chamber 5 is low, the swash plate 12 tries to reduce the inclination angle, and automatic adjustment is performed. As a result, during high-speed operation, the discharge capacity can be changed, but an excessive increase in the pressure of the crank chamber 5 can be prevented, and a refrigerant gas having a high discharge pressure is introduced into the crank chamber 5 to a large extent. Since it is not necessary, it is possible to prevent the temperature inside the crank chamber 5 from rising, so that the reliability of the shaft sealing device 7c can be improved.

Also in such a compressor, the brackets 12b, 12b, etc. and the rotor 1 via the hinge mechanism K are used.
Since the inclination angle of the swash plate 12 is determined by the positional relationship of 0 and the positional relationship of the through hole 20 and the drive shaft 6, the swash plate 12 has the brackets 12b, 12b, etc. and the through hole 20 integrally. , The tilt angle is preferably secured. In this compressor, since the sliding surface 12a that determines the positional relationship between the piston 9 and the cylinder bore 8 is formed on the swash plate 12, the inclination angle of the swash plate 12 is accurately applied to the sliding surface 12a. ,
There is no deviation in the positional relationship between the piston 9 and the cylinder bore 8. Therefore, the variable characteristics and the compression performance do not vary and the performance can be stabilized.

Further, in this compressor, since the counterweight 15 is mounted on the swash plate 12 having the sliding surface 12a, the brackets 12b, 12b, etc., and the through hole 20 as one body, the counterweight 15 of the sliding surface 12a. Counterweight 1 after processing
5 can be attached. Therefore, the sliding surface 12
Processing of a becomes easy. At the same time, the counterweight 15 avoids the shoe 14 on the rotor 10 side to avoid the sliding surface 1.
Since it extends radially outward from the axis of the drive shaft 6 as it covers 2a, the imbalance during rotation of the swash plate 12 can be effectively absorbed.

In addition, in this compressor, since the front end face 12g of the swash plate 12 contacts the rear end face 10a of the rotor 10, the maximum inclination angle is maintained, so that the counterweight 15
By providing a gap between the rotor 10 and the rotor 10, it is possible to prevent the force from the rotor 10 from acting on the counter weight. Therefore, even when the counterweight 15 is attached by the simple rivet 16, the durability in use can be sufficiently exhibited, and the manufacturing can be performed at low cost.

Further, in this compressor, since the weight reducing portions 12f and 17b are formed on the top dead center side of the swash plate 12 and the rotor 10, the hinge mechanism K and the brackets 12b and 12b.
It is possible to reduce the increase in weight of the above. Therefore, balance can be ensured even with a small counterweight 15, and the weight of the entire compressor can be reduced.

[0029]

As described above in detail, since the compressor of the present invention employs the structure described in the claims, it effectively absorbs the imbalance during rotation of the swash plate and, at the same time, slides. The performance and controllability can be stabilized without making the working of the moving surface difficult. Further, when the maximum inclination angle is maintained by the front end surface of the swash plate contacting the rear end surface of the rotor, the swash plate and the counterweight can be mounted by a simple mounting means, and thus inexpensive manufacturing is possible. It will be possible.

[Brief description of drawings]

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

2A is a front view of a swash plate, and FIG. 2B is a cross-sectional view taken along the line BB of the swash plate.

FIG. 3 is a front view of a counterweight, and FIG. 3B is a cross-sectional view taken along the line BB of the counterweight according to the compressor of the embodiment.

FIG. 4 is a front view of a swash plate equipped with a counter weight, and FIG. 4 (B) is a sectional view taken along line BB of the swash plate equipped with a counter weight according to the compressor of the embodiment.

[Explanation of symbols]

1 ... Cylinder block 2 ... Front housing 3 ... Rear housing 5 ... Crank chamber 30 ...
Suction chamber 31 ... Discharge chamber 8 ... Cylinder bore 9 ... Piston 6 ... Drive shaft 10 ... Rotor K ... Hinge mechanism 12 ... Swash plate 14 ... Shoe 12a
... Sliding surfaces 12b, 12c, 12d ... Connecting portion (12b ... Bracket, 12c ... Guide pin, 12d ... Ball portion) 20 ... Fitting portion (through hole) 15
... Counter weight 12g ... Front end face 10a ... Rear end face

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Osamu Hiramatsu 2-chome, Toyota-cho, Kariya city, Aichi stock company Toyota Industries Corp.

Claims (2)

[Claims] 1. A crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connected to these are defined and formed in a housing, and a piston is reciprocally housed in each cylinder bore and supported by the housing. A rotor located in the crank chamber is rotatably supported on the drive shaft in a synchronous manner, and a swash plate connected to the rotor via a hinge mechanism at the top dead center side is fitted to the drive shaft in a tiltable manner. Between the plate and the piston, a pair of shoes for converting the back-and-forth swinging motion of the swash plate into the reciprocating motion of each piston is interposed, and the tilt angle of the swash plate is controlled by the pressure in the crank chamber. In a variable displacement swash plate compressor configured to change a discharge capacity, the swash plate is a sliding surface that engages with the piston via each of the shoes, and the heat sink formed between the rotor and the rotor. The counter that is integrally formed with the connecting portion of the locking mechanism and the drive shaft and that protrudes toward the rotor side in a region including the bottom dead center thereof and further extends outwardly. A variable capacity swash plate compressor that is equipped with weights. 2. The variable displacement swash plate compressor according to claim 1, wherein the maximum inclination angle is maintained by the front end surface of the swash plate contacting the rear end surface of the rotor.