JP3259487B2 - Variable capacity swash plate compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art A conventional variable displacement type swash plate type compressor (hereinafter, referred to as a swash plate type compressor).
It is simply called a compressor. ) Is disclosed in JP-A-4-303184.
Japanese Unexamined Patent Application Publication No. 2000-205,099 is known. In this compressor, a crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connected to these are defined in a housing. In the crank chamber, the rotor is supported by the drive shaft so as to be able to rotate synchronously,
A swash plate is pivotally supported at the top dead center side between the rotor and the drive shaft via a hinge mechanism and via a sleeve between the swash plate and the drive shaft so that the swash plate can be rotated synchronously and tilted. The swash plate is composed of a rotary swash plate having a sliding surface that engages with a piston via each shoe, and a rotary driving body that fixes the rotary swash plate with a tightening ring. The rotary driving body protrudes toward the rotor in a region including the connecting portion of the hinge mechanism formed between the rotor, the fitting portion with the driving shaft via the sleeve, and the bottom dead center, and further projects outward. The counterweight portion that is bent and extends is integrally formed. Each piston is accommodated in each cylinder bore. The housing is provided with a control valve for adjusting the pressure in the crank chamber.

[0003] In this compressor, when the swash plate rotates at a predetermined inclination with the driving of the drive shaft, the piston reciprocates in the cylinder bore. Thereby, the refrigerant gas is sucked into the cylinder bore from the suction chamber, and the refrigerant gas is compressed and then discharged to 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, whereby the discharge capacity of the refrigerant gas discharged to the discharge chamber is controlled.

[0004]

However, in the above-mentioned compressor, a swash plate is constituted by a rotary driving body integrally having a connecting portion, a fitting portion and a counterweight portion, and a rotary swash plate having a sliding surface. Therefore, there is a possibility that the performance may vary. That is, in such a compressor, the inclination 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. However, since the connecting portion and the fitting portion are integrally formed, the inclination angle of the rotary driving body is suitably secured. However, since the rotary swash plate having a sliding surface that determines the positional relationship between the piston and the cylinder bore is separate from the rotary driver, the rotary swash plate is slightly inclined with respect to the rotary driver. If it is fixed, the inclination of the rotary driving body will not be accurately applied to the sliding surface, and the positional relationship between the piston and the cylinder bore will be displaced, causing variations in variable characteristics and compression performance.

On the other hand, if a swash plate having a sliding surface integrally with the connecting portion, the fitting portion and the counterweight portion is constituted, the imbalance during rotation of the swash plate can be effectively absorbed. Therefore, when the counterweight portion is positioned in the radially outward direction from the axis of the drive shaft as much as possible, the counterweight portion covers the sliding surface, and it becomes difficult to process the sliding surface.

An object of the present invention is to effectively absorb imbalance 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 order to solve the above-mentioned problems, a compressor according to the present invention has a housing in which a crank chamber, a suction chamber, a discharge chamber, and cylinder bores connected to these are formed. The piston is housed in a reciprocating manner, and a rotor located in the crank chamber is supported on the drive shaft supported by the housing so as to be able to rotate synchronously, and a hinge mechanism is provided on the top dead center side with the rotor. A swash plate connected through the swash plate is fitted so as to be displaceable at an angle, and a pair of shoes for converting the forward and backward swinging motion of the swash plate into reciprocating motion of each piston is provided between the swash plate and the piston. In the variable displacement swash plate type compressor, which is configured to control the inclination angle of the swash plate by the pressure in the crank chamber to change the discharge capacity, the swash plate is connected to the piston via the respective shoes. Sliding surface is formed to tons engage
Sliding surface, the part of the hinge mechanism configured to be formed between the rotor that, and have the fitting portion fitted to the drive shaft
The swash plate employs a novel configuration in which a separate counterweight is attached to the swash plate .

In the compressor of the present invention, it is preferable that the front end face of the swash plate comes into contact with the rear end face of the rotor to maintain the maximum inclination angle.

[0009]

[Action] In the compressor of the present invention, the swash plate and a connecting portion and the fitting portion and the sliding surface part, separate counterweight against this swash plate is mounted. Also in such a compressor, the inclination 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. By having the joint portion, the inclination angle is suitably secured. In this compressor,
Since the sliding surface that determines the positional relationship between the piston and the cylinder bore is formed on the sliding surface of the swash plate, the inclination angle of the swash plate is accurately given to the sliding surface, and the positional relationship between the piston and the cylinder bore is increased. No deviation occurs. Therefore, there is no variation in variable characteristics and compression performance.

Moreover, counterweight because it is intended to be mounted on the swash plate and a connecting portion and the fitting portion and the sliding surface part, it is possible to mount the counterweight after processing of the sliding surface. For this reason, processing of the sliding surface becomes easy,
At the same time, in order to effectively absorb imbalance during rotation of the swash plate, the swash plate can be positioned radially outward from the axis of the drive shaft as much as the counterweight covers the sliding surface.

When the front end face of the swash plate contacts the rear end face of the rotor to maintain the maximum inclination angle, a gap is provided between the counterweight and the rotor so that the force from the rotor is applied to the counterweight. Since it can be prevented from acting, the counterweight can be mounted by 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 of the cylinder block 1 by a through bolt 21, and the rear housing 3 is joined to the rear end of the cylinder block 1 by the through bolt 21 via a valve plate 4. Have been. 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 provided with a shaft sealing device 7c.
And are rotatably supported by bearings 7a and 7b. The cylinder block 1 is provided with a plurality of cylinder bores 8 at positions surrounding the drive shaft 6, and pistons 9 are respectively fitted into the respective cylinder bores 8.

In the crank chamber 5, a rotor 10 is supported on the drive shaft 6 so as to be able to rotate synchronously with the drive shaft 6 via a bearing 11 between the rotor 10 and the front housing 2, and a swash plate 12 is provided behind the rotor 10. Equipped. And rotor 1
A pressing spring 13 is interposed between 0 and the swash plate 12, and the pressing spring 13 urges the swash plate 12 toward the rear housing 3.

As shown in FIG. 2, the swash plate 12 is formed with a smooth ring-shaped sliding surface 12a on the outer peripheral sides of both end faces.
As shown in FIG. 1, hemispherical shoes 14, 14 are in contact with the sliding surface 12a. These shoes 14, 14
Is engaged with a ball bearing surface of a piston 9, and each piston 9 is accommodated in each cylinder bore 8 so as to be able to reciprocate. The sliding surface 12a corresponds to the sliding surface of the present invention.

As shown in FIG. 1 and FIG.
A pair of brackets 12b, 12b protrude across the top dead center position T of the swash plate 12 with the drive shaft 6 interposed between the upper dead center side of the inner region and the rotor 10 side from the second sliding surface 12a. Has been established. One end of each of the guide pins 12c, 12c is fixed to each of the brackets 12b, 12b.
Ball parts 12d, 12d are fixed to the other ends of c, 12c. Thus, in this compressor, the bracket 12b,
12b, guide pins 12c, 12c , spheres 12d, 12
d and support arms 17, 17 of the rotor 10 which will be described later.
Thus, a hinge mechanism K is configured. And arm 1
7,17 but excluding the connecting portion is formed is a part of the hinge mechanism K configuration. Each bracket 12b, 12
As shown in FIG. 2, a weight reduction portion 12f having a through hole in the center is formed between the portions b.

Further, a through hole 20 is formed in the central area of the swash plate 12 as a fitting portion, and the drive shaft 6 is formed in the through hole 20.
Is inserted. Further, the inner surface of the swash plate 12 is extended radially outward from the axis of the drive shaft 6 at the bottom dead center side and the rotor 10 side to avoid the shoe 14 on the rotor 10 side and slide the sliding surface 12a. Counter weight 1 that is covered and separate from swash plate 12
5 is attached by a rivet 16.

The method for mounting the counterweight 15 on the swash plate 12 was as follows. That is, FIG.
As shown in (B), the swash plate 12 having the sliding surface 12a machined.
Four rivet holes 12e are penetrated in the lower dead center side of the inner region. As shown in FIGS. 3A and 3B, the counterweight 15 is also provided with four rivet holes 15a that match the respective rivet holes 12e. Then, the counter weight 15 is brought into contact with the rivet holes 12e and 15a of the swash plate 12 on the bottom dead center side and the rotor 10 side while aligning the respective rivet holes 12e and 15a, and the rivet 16 is inserted from the rotor 10 side. Thereafter, the swash plate 12 and the counterweight 15 are mounted by caulking the protruding end of the rivet 16 as shown in FIGS. 4A and 4B.

Thus, in this compressor, the swash plate 12 has the sliding surface 12a, the brackets 12b and 12b, the guide pins 12c and 12c, the spherical portions 12d and 12d, and the through hole 20.
The swash plate 12 has a counter weight 15
Is installed. The swash plate 12 has a front end face 12g closer to the through hole 20 than the inner area where the counter weight 15 is mounted.
Abuts on the rear end face 10a of the inner region of the rotor 10 to maintain the maximum inclination angle. On the other hand, the swash plate 12 has a part of the through hole 20 on the cylinder block 1
The minimum inclination angle is maintained by contacting the second angle.

Further, as shown in FIG. 1, the upper portion of the rotor 10, it the remainder of the hinge mechanism K, K constructed as above
Support arms 17 and 17 to a pair is the guide pins 12c,
It protrudes rearward in the axial direction so as to face 12c.
Each tip of each support arm 17, 17 is parallel to a plane determined by the axis of the drive shaft 6 and the top dead center position T of the swash plate 12, and is outside the axis of the drive shaft 6. The guide holes 17a, 17a are linearly provided in the direction approaching from the side. The direction of the center line of these guide holes 17a, 17a is
The top dead center position of the piston 9 is set so that it hardly moves back and forth regardless of the inclination displacement of 2. As shown in FIG. 1, the spherical portions 12d, 12d of the guide pins 12c, 12c are respectively provided in the guide holes 17a, 17a.
Are slidably and slidably inserted. Each support arm 1
Weight reduction portions 17b, 17b are also formed at the base ends of 7, 17.

Further, the inside of the rear housing 3 is provided with a suction chamber 3.
0 and a discharge chamber 31. The valve plate 4 has a suction port 32 and a discharge port 3 corresponding to each cylinder bore 8.
A compression chamber formed between the valve plate 4 and the piston 9 is provided with a suction port 32 and a discharge port 33.
Are communicated with the suction chamber 30 and the discharge chamber 31 through the air passage. Each suction port 32 is provided with a suction valve (not shown) that opens and closes the suction port 32 according to the reciprocating motion of the piston 9. Each discharge port 33 restricts the discharge port 33 to a retainer 34 according to the reciprocating motion of the piston 9. A discharge valve (not shown) that opens and closes while being opened is provided. Further, the rear housing 3 is provided 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 with the driving of the drive shaft 6 shown in FIG. 1, the shoes 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 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, so that the inclination angle of the swash plate 12 becomes smaller. That is, the spherical portions 12d of the swash plate 12 rotate counterclockwise in the guide holes 17a of the hinge mechanism K, and the guide holes 17a, 17a are moved along the center line from the outside toward the axial center. Slide in the direction approaching. Further, the swash plate 12 rotates counterclockwise while the peripheral surface of the drive shaft 6 abuts against the inner surface of the through hole 20, and swashes against the pressing spring 13 and retreats. Thus, the inclination angle of the swash plate 12 is reduced, and the stroke of the piston 9 is reduced, and the discharge capacity is reduced.

Conversely, if the pressure in the crank chamber 5 is reduced by adjusting the pressure of the control valve, the back pressure acting on the piston 9 is reduced, and the inclination angle of the swash plate 12 is increased. That is, the spherical portions 12d, 12d of the swash plate 12 rotate clockwise in the guide holes 17a, 17a of the hinge mechanism K, and move inside the guide holes 17a, 17a along the center line with respect to the axis from the inside. Sliding away. Also, the swash plate 12 is
Rotating clockwise while the peripheral surface of the drive shaft 6 is in contact with the inner surface of the drive shaft 6, it advances forward against the pressing spring 13. Thereby, the inclination angle of the swash plate 12 becomes large, so that the stroke of the piston 9 is extended, and the discharge capacity becomes large.

During this time, in this compressor, the counterweight 15 is tilted together with the swash plate 12, so that a large centrifugal force can be applied to the swash plate 12 during high-speed operation where the cooling capacity is small. Therefore, at this time, even if the pressure in the crank chamber 5 is low, the swash plate 12 attempts to reduce the inclination angle, and the automatic swash plate 12 is automatically varied. Thus, at the time of high-speed operation, while the discharge capacity can be changed, the pressure in the crank chamber 5 can be prevented from excessively increasing while the refrigerant gas having a high discharge pressure is introduced into the crank chamber 5 so much. Since there is no need, it is possible to prevent the inside of the crank chamber 5 from becoming high temperature, and thus it is possible to improve the reliability of the shaft sealing device 7c.

Further, also in such a compressor, the brackets 12b in the hinge mechanism K, 12b etc. and the rotor 1
Since the inclination of the swash plate 12 is determined by the positional relationship of 0 and the positional relationship between the through hole 20 and the drive shaft 6, the swash plate 12 has the brackets 12b, 12b and the like and the through hole 20 integrally. , The inclination angle is suitably secured. In this compressor, the swash plate 12 has a sliding surface 12a for determining the positional relationship between the piston 9 and the cylinder bore 8, so that the inclination angle of the swash plate 12 is accurately given to the sliding surface 12a. ,
There is no deviation in the positional relationship between the piston 9 and the cylinder bore 8. Therefore, the performance can be stabilized without causing variation in the variable characteristics and the compression performance.

Further, in this compressor, since the counter weight 15 is mounted on the swash plate 12 having the sliding surface 12a, the brackets 12b, 12b, etc. and the through hole 20, the counter weight 15 is formed on the sliding surface 12a. Counter weight 1 after processing
5 can be attached. For this reason, 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 and slides on the sliding surface 1.
The longer the swash plate 12 rotates, the more the swash plate 12 rotates.

In addition, in this compressor, since the front end face 12g of the swash plate 12 abuts on the rear end face 10a of the rotor 10, the maximum inclination angle is maintained.
By providing a gap between the rotor and the rotor 10, the force from the rotor 10 can be prevented from acting on the counterweight. For this reason, even when the counter weight 15 is attached with a simple rivet 16, the durability in use can be sufficiently exhibited, and low-cost manufacturing is possible.

Further, in this compressor, since the swash plate 12 and the rotor 10 are formed with the weight loss portions 12f and 17b on the top dead center side, the hinge mechanism K and the brackets 12b and 12b are formed.
Etc. can be reduced. For this reason, even with the small counterweight 15, the balance can be ensured, and the weight of the entire compressor can be reduced.

[0029]

As described in detail above, the compressor of the present invention employs the configuration described in the claims, so that the imbalance during rotation of the swash plate is effectively absorbed, and at the same time, the sliding is performed. Performance and controllability can be stabilized without making working of the moving surface difficult. In addition, when the front end surface of the swash plate abuts on the rear end surface of the rotor to maintain the maximum tilt angle, the swash plate and the counterweight can be mounted by simple mounting means. It becomes possible.

[Brief description of the drawings]

FIG. 1 is a longitudinal 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 of the swash plate taken along line BB in the compressor according to the embodiment.

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

4A is a front view of a swash plate on which a counter weight is mounted, and FIG. 4B is a cross-sectional view of the swash plate on which a counter weight is mounted, taken along line BB.

[Explanation of symbols]

DESCRIPTION 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 surface portion ( sliding surface ) 12b, 12c, 12d ... Connecting portion (12b ... bracket, 12c ... guide pin, 1
2d: ball portion 20: fitting portion (through hole) 15: counter weight 12g: front end surface 10a
... Rear end face 17 ... Support arm which is the rest of the hinge mechanism configuration

Continuation of the front page (72) Inventor Osamu Hiramatsu 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (56) References JP-A-5-52183 (JP, A) JP-A-5-99137 (JP, A) JP-A-5-149245 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04B 27/08

Claims (2)

(57) [Claims] A crank chamber, a suction chamber, a discharge chamber, and cylinder bores connected thereto are formed in a housing, and a piston is reciprocally housed in each of the cylinder bores and supported by the housing. A rotor located in the crank chamber is supported on the drive shaft so as to be able to rotate synchronously, and a swash plate connected to the rotor via a hinge mechanism at the top dead center side is fitted so as to be tiltable and displaceable. Between the plate and the piston, a pair of shoes for converting the forward and backward oscillating motion of the swash plate into reciprocating motion of each piston is interposed, and the inclination angle of the swash plate is controlled by the pressure in the crank chamber. In the variable displacement type swash plate type compressor configured to change the discharge capacity, the swash plate includes a sliding surface portion on which a sliding surface that engages with the piston is formed through each of the shoes. A part of the hinge mechanism configuration formed therebetween, and a fitting part that fits into the drive shaft, and is separate from the swash plate.
A variable displacement type swash plate type compressor equipped with a counter weight of (1). 2. The variable displacement type swash plate compressor according to claim 1, wherein the maximum inclination angle is maintained by the front end surface of the swash plate abutting on the rear end surface of the rotor.