JP2001349274A - Variable displacement swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor capable of restricting the worsening of static unbalance without increasing the weight of a swash plate and superior in high speed controllability. SOLUTION: The variable displacement swash plate compressor comprises a thrust flange 40 fixed to a shaft 5 for rotating integrally with the shaft 5, the swash plate 10 connected to the thrust flange 40 via a link arm 42 for rotating integrally with the rotation of the thrust flange 40, a hinge ball 9 slidably mounted on the shaft 5 for restricting the inclination of the swash plate 10 to the shaft 5, and a piston 7 connected to the swash plate 10 via a shoe 11 to be relatively rotated on the sliding surface of the swash plate 10 for linearly reciprocating in a cylinder bore 6 with the rotation of the swash plate 10. The inclination of the swash plate 10 is changed with the pressure change of a crank room 8 storing the swash plate 10 and the stroke of the piston 7 is also changed. A center O1 of the hinge ball 9 is located at the front side of a center O2 of a plate portion 10a of the swash plate 10.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement type swash plate type compressor in which the displacement of a piston changes according to the inclination angle of the swash plate to change the displacement.

[0002]

2. Description of the Related Art FIG. 6 is a cross-sectional view showing the periphery of a shaft of a conventional variable displacement swash plate type compressor.

The shaft 105 has a thrust flange 1
40 is fixed, and a swash plate 110 is attached via a hinge ball 109.

The hinge ball 109 is slidably mounted along the shaft 105 and regulates the inclination of the swash plate 110 with respect to the shaft 105.

[0005] The thrust flange 140 and the swash plate 110 are connected by a link mechanism 142, and the rotation of the shaft 105 is controlled by the thrust flange 140 via the link mechanism 142.
To the swash plate 110.

[0006] The piston 107 is connected to a swash plate 11 through a pair of shoes 111 which relatively rotate a sliding surface of the swash plate 110.
0 and linearly reciprocates in a cylinder bore (not shown) as the swash plate 110 rotates.

In this variable displacement type swash plate compressor, the swash plate 11
The inclination angle of the swash plate 110 changes in accordance with the change in the pressure of the crank chamber 108 containing 0, and the stroke amount of the piston 107 changes.

The swash plate 110 is located at the center O of the hinge ball 109.
Since the swash plate 110 is tilted about 1, the position of the center of gravity O3 of the swash plate 110 also changes with respect to the shaft 105.

FIG. 7 is a view for explaining static imbalance with respect to the swash plate inclination angle.

The rotating body (swash plate 110 and thrust flange 140) rotating about the shaft 105 has a static imbalance. The static imbalance amount is represented by the product (Kg · cm) of the mass (Kg) of the swash plate 110 (thrust flange 140) and the distance (cm) from the shaft 105 to the center of gravity of the swash plate 110 (thrust flange 140). .

In FIG. 7, a is the static imbalance of the thrust flange, b is the static imbalance of the entire rotating body, and c is the center of the hinge ball located on the front side of the center of the swash plate. D represents static imbalance at the center of the hinge ball, and e represents static imbalance of the swash plate.

Since the inclination angle of the thrust flange 140 does not change, the thrust flange 140 has a certain amount of unbalance (see a straight line a).

On the other hand, since the swash plate angle of the swash plate 110 changes, the swash plate 110 has an unbalance amount that changes at a constant rate (see a straight line e).

The sum of the unbalance amounts of the two becomes the overall static unbalance amount (see the straight line b).

[0015] When the static imbalance amount is large, primary rotational vibrations in which the compressor itself vibrates are generated and appear as vehicle vibrations and sounds. This vibration is low frequency noise in the audible range of 400 Hz or less, and gives an uncomfortable feeling to the boarding vehicle.

[0016]

FIG. 8 is a diagram for explaining the position of the center of gravity of the swash plate.

In FIG. 8, A1, A2, B1, and B2 indicate the positions of the centers of gravity, Amax is the amount of shift of the center of gravity of the swash plate in the Y-axis direction during the maximum stroke, and Amin is the center of gravity of the swash plate during the minimum stroke. Bmax is the amount of displacement of the center of gravity of the swash plate in the Y-axis direction during the maximum stroke when weight is added to the rear side, and Bmin is the amount of displacement in the Y-axis direction when weight is added to the rear side. It shows the amount of displacement of the center of gravity of the swash plate at the time of the minimum stroke in the Y-axis direction.

In recent years, there has been an increasing demand for smaller and faster compressors.

When the speed of the compressor is increased, the piston 107
Since the inertia force of the swash plate 110 increases in accordance with the rotational speed, it is necessary to make the swash plate 110 thicker or heavier in order to balance with the inertia force.

In this variable displacement type swash plate type compressor, the swash plate 1
Weights are added to the front side of No. 10 to balance the inertial force. This weight increases as the degree of speeding up increases.

However, if the weight to be added is increased, the front side of the swash plate 110 becomes heavier, and the distance from the center O1 of the hinge ball 109 to the center of gravity O3 of the swash plate 110 becomes longer. The unbalance amount increases).

The inclination angle of the swash plate 110 with respect to the inclination angle of the swash plate 110
When the position of the center of gravity O3 changes and the distance from the center O1 of the hinge ball 109 to the center of gravity O3 of the swash plate 110 is no longer long, the difference in the amount of static imbalance between the maximum stroke and the minimum stroke increases, and the thrust increases. Flange 1
Variations in the static imbalance of the entire rotating body including 40 are increased (see the straight line b in FIG. 7).

Therefore, when a weight is added to the front side of the swash plate 110, it is possible to cope with high-speed rotation. However, since the primary vibration of rotation increases and the vibration and noise generated in the car increase, the conventional swash plate is used. Weights 112 were also added to the rear side of the swash plate 110 to bring the center of gravity of the swash plate 110 closer to the center O1 of the hinge ball (see FIG. 6).

As a result, the mass of the swash plate 110 increases, and the mass of the thrust flange 140 increases in order to balance the entire compressor. Therefore, there is a problem that the compressor becomes heavy.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and a problem thereof is that a variable capacity swash plate type excellent in high-speed controllability capable of suppressing deterioration of static imbalance without making the swash plate heavy. It is to provide a compressor.

[0026]

According to a first aspect of the present invention, there is provided a rotary member fixed to a shaft and connected to the rotary member via a link mechanism. An inclined rotating plate that integrally rotates with the rotation of the rotating member, an angle regulating member that is slidably attached to the shaft and regulates an angle of the inclined rotating plate with respect to the shaft, and a slide of the inclined rotating plate. A piston that is connected to the inclined rotating plate via a shoe that relatively rotates a moving surface, and a piston that linearly reciprocates in a cylinder bore as the inclined rotating plate rotates, and a crank chamber in which the inclined rotating plate is housed. In the variable displacement swash plate type compressor, in which the inclination angle of the inclined rotary plate changes according to the pressure change and the stroke amount of the piston changes, the center of the angle regulating member is changed. Characterized in that is positioned in front of the center of the plate portion of the inclined rotary plate.

Since the center of the angle regulating member is located on the front side of the center of the plate portion of the inclined rotating plate, the center of the angle regulating member approaches the center of gravity of the swash plate, and the center of gravity of the swash plate moves from the center of the angle regulating member. The distance to is shorter.

According to a second aspect of the present invention, in the variable displacement swash plate type compressor according to the first aspect, the center of the angle regulating member is made to coincide with the center of gravity of the inclined rotating plate.

Since the center of the angle regulating member coincides with the center of gravity of the inclined rotating plate, the static imbalance amount becomes zero.

According to a third aspect of the present invention, there is provided a rotating member fixed to a shaft and rotating integrally with the shaft, and an inclined member connected to the rotating member via a link mechanism and integrally rotating as the rotating member rotates. A rotating plate, a shaft insertion center hole formed in the inclined rotating plate, penetrating the shaft and regulating an angle of the inclined rotating plate with respect to the shaft, and relatively rotating a sliding surface of the inclined rotating plate. A piston that is connected to the inclined rotating plate via a shoe and that linearly reciprocates in a cylinder bore as the inclined rotating plate rotates, wherein the inclined rotation is performed according to a pressure change in a crank chamber in which the inclined rotating plate is housed. In the variable displacement type swash plate compressor in which the inclination angle of the plate changes and the stroke amount of the piston changes, the center of the circle formed by the ridge line of the shaft insertion center hole is changed. Characterized in that is positioned in front of the center of the plate portion of the inclined rotary plate.

Since the center of the circle formed by the ridge line of the shaft insertion center hole is located on the front side with respect to the center of the plate portion of the inclined rotating plate, the center of the angle regulating member approaches the center of gravity of the swash plate, and The distance from the center of the swash plate to the center of gravity of the swash plate becomes shorter.

According to a fourth aspect of the present invention, in the variable displacement swash plate compressor according to the third aspect, the center of a circle formed by the ridge of the shaft insertion center hole is made to coincide with the center of gravity of the inclined rotary plate. It is characterized by the following.

Since the center of the circle formed by the ridge line of the shaft insertion center hole is made coincident with the center of gravity of the inclined rotating plate, the static imbalance amount becomes zero.

[0034]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional view of a variable displacement type swash plate type compressor according to a first embodiment of the present invention, and FIG. 2 is a view for explaining the position of the center of gravity of the swash plate.

In FIG. 2, A1, A2, D1, and D2 indicate the positions of the centers of gravity, Amax is the amount of displacement of the center of gravity of the swash plate in the Y-axis direction during the maximum stroke, and Amin is the center of gravity of the swash plate during the minimum stroke. The amount of displacement of the position in the Y-axis direction, Dmax, is determined by centering the center O1 of the hinge ball 9 on the swash plate 10.
Dmin is the amount of displacement of the center of gravity of the swash plate in the Y-axis direction at the time of the maximum stroke when D is located on the front side of the center O2 of the plate portion 10c, and Dmin is the center O1 of the hinge ball 9.
Is the amount of displacement of the center of gravity of the swash plate 10 in the Y-axis direction at the time of the minimum stroke when is positioned on the front side of the center O2 of the plate portion 10c of the swash plate 10.

A rear head 3 is fixed to one end surface of a cylinder block 1 of the variable displacement type swash plate type compressor via a valve plate 2, and a front head 4 is fixed to the other end surface.

The cylinder block 1 is provided with a plurality of cylinder bores 6 at predetermined intervals in the circumferential direction around the shaft 5.

A piston 7 is accommodated in each of the cylinder bores 6.

A pair of shoes 11 is rotatably supported at one end of the piston 7. The peripheral portion of the swash plate 10 enters between the two shoes 11, and the sliding surfaces 10a, 10
The plane part of both shoes 11 contacts b.

The rotational movement of the swash plate 10 is converted into a linear reciprocating movement of the piston 7 via the shoe 11, and the piston 7 slides in the cylinder bore 6.

A crank chamber 8 is provided in the front head 4.
A swash plate (inclined rotating plate) 10 that rotates around a hinge ball (angle regulating member) 9 in conjunction with the rotation of the shaft 5 is accommodated in the crank chamber 8.

The hinge ball 9 is slidably mounted on the shaft 5 and regulates the inclination angle of the swash plate 10 with respect to the shaft 5.

The center O1 of the hinge ball is located on the front side of the center O2 of the plate portion 10c of the swash plate 10. At this time, Amax, Amin, Bmax, Bmi
n, Dmax and Dmin, (Amax−Ami
n)>(Bmax-Bmin)> (Dmax-Dmi)
n) (see FIGS. 2 and 7).

In the rear head 3, a discharge chamber 12 is provided.
A suction chamber 13 located around the discharge chamber 12 is formed.

The valve plate 2 has a discharge port 16 for communicating the compression chamber 6 a of the cylinder bore 6 with the discharge chamber 12.
And a suction port 15 for communicating the compression chamber 6a of the cylinder bore 6 with the suction chamber 13 are provided at predetermined intervals in the circumferential direction.

The discharge port 16 is opened and closed by a discharge valve 17. The discharge valve 17 is fixed to a rear end surface of the valve plate 2 by a bolt 19 together with a valve retainer 18.

The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is disposed on the front end face of the valve plate 2.

The rear end of the shaft 5 is the radial bearing 2
4 and a thrust bearing 25, and a front end of the shaft 5 is supported by a radial bearing 26.

Further, the pressure in the discharge chamber 12 and the pressure in the crank chamber 8 are adjusted by a pressure regulating valve 32 provided in the communication passage 31 for communicating the discharge chamber 12 with the crank chamber 8.

A thrust flange (rotating member) 40 is fixed to the shaft 5, and a swash plate 10 is attached via a hinge ball 9. The hinge ball 9 is slidably mounted on the shaft 5.

The thrust flange 40 and the swash plate 10 are connected by a link mechanism 42, and the rotation of the shaft 5 is transmitted from the thrust flange 40 to the swash plate 10 via the link mechanism 42.

A coil spring 51 is mounted between the hinge ball 9 and the thrust flange 40.

The coil spring 51 urges the hinge ball 9 toward the cylinder block 1 so that the inclination angle of the swash plate 10 becomes small.

Next, the operation of the variable displacement type swash plate type compressor will be described.

When the rotational power of the vehicle engine (not shown) is transmitted to the shaft 5, the rotational force of the shaft 5 is transmitted to the thrust flange 40.

The swash plate 10 is rotated about the hinge ball 9 as the thrust flange 40 rotates.
Rotate with 0.

The rotational movement of the swash plate 10 is transmitted to the piston 7 via the shoe 11, and is converted into a linear reciprocating movement of the piston 7.

As a result, the volume of the compression chamber in the cylinder bore 6 changes, and the suction, compression, and discharge of the refrigerant gas are sequentially performed by the change in volume, and the refrigerant gas having a capacity corresponding to the inclination angle of the swash plate 10 is discharged. You.

At the time of suction, the suction valve 21 is opened, and low-pressure refrigerant gas is sucked from the suction chamber 21 into the compression chamber 6 a in the cylinder bore 6.

At the time of discharge, the discharge valve 17 is opened, and high-pressure refrigerant gas is discharged from the compression chamber 6a to the discharge chamber 12.

When the cooling load decreases and the pressure in the crank chamber 8 increases, the inclination angle of the swash plate 10 decreases, the stroke of the piston 7 decreases, and the discharge capacity decreases.

When the cooling load increases and the pressure in the crank chamber 8 decreases, the inclination angle of the swash plate 10 increases.

When the inclination angle of the swash plate 10 increases, the stroke amount of the piston 7 increases, and the discharge capacity increases.

According to the variable displacement type swash plate type compressor of this embodiment, the center O 1 of the hinge ball 9 is positioned at the center of gravity O of the swash plate 10.
3, the amount of static imbalance is small, and the swash plate 10
It is possible to suppress the generation of vehicle vibration and noise during high-speed rotation without making the (compressor) heavy, and to add weight to the rear side to make the center of gravity of the swash plate closer to the center of the hinge ball. The balance can be easily adjusted.

Also, (Amax−Amin)> (Bma
x-Bmin)> (Dmax-Dmin), so the difference in the amount of static imbalance between the maximum stroke and the minimum stroke is small, and the variation in the static imbalance of the entire rotating body including the thrust flange 40 is small. Can be reduced (see the straight line c in FIG. 7).

FIG. 3 is a view for explaining the position of the center of gravity of the swash plate.

This figure shows a case where the center of the hinge ball 9 coincides with the center of gravity of the swash plate 10 when the center O 1 of the hinge ball is located on the front side of the center O 2 of the plate portion 10 c of the swash plate 10. Is shown.

At this time, since the static imbalance amount becomes zero, the mass of the thrust flange 40 can be reduced, and the weight of the variable displacement type swash plate compressor can be further reduced.

In the above embodiment, the present invention is applied to the variable displacement type swash plate type compressor using the hinge ball 9, but can also be applied to the variable displacement type swash plate type compressor not using the hinge ball 9.

FIG. 4 is a longitudinal sectional view of a variable displacement type swash plate type compressor according to a second embodiment of the present invention, and the same parts as those in the first embodiment are denoted by the same reference numerals and description thereof will be omitted.

This embodiment is different from the first embodiment in that an angle regulating member is constituted by a slider 59 slidable on the shaft 5 in the axial direction and a pin 58 perpendicular to the axial direction of the slider 59.

The inclination angle of the swash plate 60 is made variable by a slider 59 and a pin 58, and the inclination angle with respect to the shaft 5 is regulated by a through hole 61.

The center O1 of the slider 59 is located on the front side of the center O2 of the plate portion 60a of the swash plate 60.

According to this embodiment, the same effects as in the first embodiment can be obtained.

FIG. 5 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a third embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof will be omitted.

This embodiment differs from the first embodiment in that an angle regulating member is formed by a shaft insertion center hole 81 formed in a swash plate 80.

The shaft insertion center hole 81 regulates the inclination angle of the swash plate 80 with respect to the shaft 5.

The shaft insertion center hole 81 narrows the center of the plate portion 80a of the swash plate 80, and has a larger diameter toward the front side and the rear side.

The ridge line 81a of the shaft insertion center hole 81
Is located on the front side of the center O2 of the plate portion 80a of the swash plate 80.

According to this embodiment, the same effects as in the first embodiment can be obtained.

The ridge 81 of the shaft insertion center hole 81
By making the center of the circle formed by a coincide with the center of gravity of the swash plate 80, the amount of static imbalance can be made zero and the mass of the thrust flange 40 can be reduced, and the weight of the variable displacement swash plate compressor can be further reduced. Can be achieved.

In the above embodiment, the variable displacement type swash plate type compressor in which the swash plates 10, 60 and 80 rotate integrally with the shaft 5 has been described as an example of the variable displacement type swash plate type compressor. For example, the present invention can be applied to a rocking plate compressor. In this case, the rocking plate corresponds to the inclined rotating plate of the present invention.

[0084]

As described above, according to the variable displacement type swash plate type compressor according to the first or third aspect of the present invention, the center of the angle regulating member approaches the center of gravity of the inclined rotary plate, and the amount of static imbalance is reduced. Becomes smaller. Also, when the center of gravity of the swash plate changes with respect to the inclination angle of the swash plate, the difference between the amount of static imbalance between the maximum stroke and the minimum stroke is small, so that the static imbalance of the entire rotating body including the rotating member is reduced. Variations are reduced.

According to the variable displacement type swash plate type compressor according to the second or fourth aspect of the present invention, the mass of the rotating member can be reduced.
It is possible to further reduce the weight of the compressor.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a first embodiment of the present invention.

FIG. 2 is a diagram illustrating the position of the center of gravity of a swash plate.

FIG. 3 is a diagram illustrating the position of the center of gravity of a swash plate.

FIG. 4 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a second embodiment of the present invention.

FIG. 5 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a third embodiment of the present invention.

FIG. 6 is a sectional view showing the periphery of a shaft of a conventional variable displacement swash plate type compressor.

FIG. 7 is a diagram illustrating static imbalance with respect to a swash plate inclination angle.

FIG. 8 is a diagram illustrating the position of the center of gravity of the swash plate.

[Explanation of symbols]

 Reference Signs List 5 shaft 7 piston 8 crank chamber 9 hinge ball (angle restricting member) 10 swash plate (inclined rotating plate) 10c plate portion 11 shoe 40 thrust flange (rotating member) 42 link mechanism 59 slider (angle restricting member) 58 pin (angle restricting) 81) Shaft insertion center hole (angle regulating member)

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[Procedure amendment]

[Submission date] February 27, 2001 (2001.2.2)
7)

[Procedure amendment 1]

[Document name to be amended] Drawing

[Correction target item name] Fig. 7

[Correction method] Change

[Correction contents]

FIG. 7

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Hiromichi Tanabe 39, Higashihara, Chiyo-ji, Onan-gun, Osato-gun, Saitama F-term (reference) 3H076 AA06 BB01 BB38 CC20 CC40

Claims (4)

[Claims] A rotating member fixed to a shaft and rotating integrally with the shaft; an inclined rotating plate connected to the rotating member via a link mechanism and rotating integrally with the rotation of the rotating member; An angle regulating member that is slidably attached to the shaft and that regulates an angle of the inclined rotating plate with respect to the shaft; and is connected to the inclined rotating plate via a shoe that relatively rotates a sliding surface of the inclined rotating plate. A piston that linearly reciprocates in a cylinder bore as the tilted rotary plate rotates, wherein the tilt angle of the tilted rotary plate changes according to a pressure change in a crank chamber in which the tilted rotary plate is housed, In the variable displacement type swash plate type compressor having a variable stroke amount, the center of the angle regulating member is located on the front side of the center of the plate portion of the inclined rotary plate. Variable capacity swash plate type compressor according to claim. 2. The variable displacement type swash plate compressor according to claim 1, wherein the center of said angle regulating member is made coincident with the center of gravity of said inclined rotary plate. 3. A rotating member fixed to a shaft and rotating integrally with the shaft, an inclined rotating plate connected to the rotating member via a link mechanism, and integrally rotating with the rotation of the rotating member; A shaft insertion center hole formed in a rotating plate, through which the shaft penetrates, and restricting an angle of the inclined rotating plate with respect to the shaft; and a shoe that relatively rotates a sliding surface of the inclined rotating plate. A piston connected to the rotating plate and reciprocating linearly in a cylinder bore as the inclined rotating plate rotates, wherein the inclination angle of the inclined rotating plate changes according to a pressure change of a crank chamber in which the inclined rotating plate is housed. In the variable displacement type swash plate type compressor in which the stroke amount of the piston changes, a center of a circle formed by a ridge line of the shaft insertion center hole is defined by the inclination rotation plate. Variable capacity swash plate type compressor is characterized in that is positioned in front of the center of the part. 4. The variable displacement type swash plate type compressor according to claim 3, wherein the center of a circle formed by the ridge line of the shaft insertion center hole coincides with the center of gravity of the inclined rotating plate.