WO2001094785A1

WO2001094785A1 - Variable displacement swash plate type compressor

Info

Publication number: WO2001094785A1
Application number: PCT/JP2001/003927
Authority: WO
Inventors: Hiroyuki Ishida; Takeo Mizushima; Hiromichi Tanabe
Original assignee: Zexel Valeo Climate Control Corporation
Priority date: 2000-06-07
Filing date: 2001-05-11
Publication date: 2001-12-13
Also published as: EP1291522A1; EP1291522A4; JP2001349274A; US20030136256A1; JP4565367B2

Abstract

A variable displacement swash plate type compressor, comprising a thrust flange (40) fixed to a shaft (5) and rotated integrally with the shaft (5), a swash plate (10) connected to the thrust flange (40) through a link mechanism (42) and rotated integrally with the thrust flange according to the rotation of the thrust flange (40), a hinge ball (9) installed slidably on the shaft (5) and restricting the angle of the swash plate (10) relative to the shaft (5), and pistons (7) connected to the swash plate (10) through shoes (11) rotated on the sliding surfaces (10a, 10b) of the swash plate (10) relative to each other and performing a linear reciprocating motion in the cylinder bores (6) according to the rotation of the swash plate (10), wherein the inclination angle of the swash plate (10) varies according to a pressure variation in a crank chamber (8) for storing the swash plate (10) so as to vary the amount of stroke of the pistons (7), and the center (O1) of the hinge ball (9) is positioned on the front side of the center (O2) of the plate part (10c) of the swash plate (10).

Description

Description Variable capacity swash plate compressor Technical field

The present invention relates to a variable displacement type swash plate type compressor in which a stroke amount of a piston changes according to an inclination angle of a swash plate to change a discharge capacity. Background art

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

The thrust flange 140 is fixed to the shaft 105, and the swash plate 110 is attached to the shaft 105 via the hinge port 109. I have.

The hinge pole 109 is slidably mounted along the shaft 105 to restrict the inclination of the slope 110 with respect to the shaft 105.

The thrust flange 140 and the swash plate 110 are connected by a link mechanism 142, and the rotation of the shaft 105 is thrust via the link mechanism 144. It is transmitted from the flange 140 to the swash plate 110.

The piston 107 is connected to the swash plate 110 via a pair of shafts 111 that relatively rotate the sliding surface of the swash plate 110, and the swash plate 110 As it rotates, it reciprocates linearly in a cylinder pore (not shown). In the variable displacement type swash plate compressor, the inclination angle of the swash plate 110 changes according to the change in the pressure of the crank chamber 108 accommodating the swash plate 110, and the piston 107 The stroke amount changes.

Since the swash plate 110 is inclined around the center O 1 of the hinge 109, the position of the center of gravity O 3 of the swash plate 110 also changes with respect to the shaft 105.

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

A rotating body (swash plate 110 or thrust flange 140) rotating about the shaft 105 has a static imbalance. The amount of static imbalance is swash plate 1 1 0 (thrust flange 1

It is expressed by the product (kg · cm) of the quality g) of the 40) and the distance (cm) from the shaft 105 to the center of gravity of the swash plate 110 (thrust flange 140). Be done

In Fig. 7, .a is the static imbalance of the thrust flange, b is the static imbalance of the whole rotating body, and c is the center of the hinge pole with the swash plate. D is the static imbalance at the front of the center of the hinge pole, d is the static imbalance at the center of the hinge pole, and e is the static imbalance of the swash plate. Show

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

Since the inclination angle of the swash plate 1 1 0 changes, the swash plate 1

0 has an unbalanced amount that changes at a fixed rate. See line e).

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

If this static imbalance increases, the compressor itself vibrates, generating primary rotational vibration, which appears as vehicle vibration and noise. This vibration is a low-frequency noise in the audible range of 400 Hz or less and gives discomfort to the boarding vehicle.

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

In FIG. 8, A 1, A 2, Β 1, and Β 2 indicate the positions of the centers of gravity, A max is the displacement of the center of gravity of the swash plate at the maximum stroke in the Y-axis direction, and A min is the minimum. The displacement of the center of gravity of the swash plate in the Y-axis direction during a stroke, and B max is the maximum position of the center of gravity of the swash plate during a stroke when a weight is added to the rear side. The amount of displacement in the Y-axis direction, Bmin, indicates the amount of displacement of the center of gravity of the swash plate in the Y-axis direction during the minimum stroke when weight is added to the rear side. The demand for higher speed is increasing.

When the speed of the compressor is increased, the inertia of piston 107 increases according to the rotation speed, so that the swash plate 110 is made thicker or heavier to balance the inertia. Need to be done.

In this variable capacity swash plate compressor, weight is added to the front side of the swash plate 110 to balance the inertial force. This weight grows as the speed increases. However, when the weight to be added is increased, the front side of the swash plate 110 becomes heavier, and the center of gravity of the swash plate 110 from the center O 1 of the hinge pole 109 becomes 〇 3 Since the distance to is longer, the static imbalance becomes worse (the static imbalance increases).

The position of the center of gravity O 3 of the swash plate 110 changes with respect to the inclination angle of the swash plate 110, and the distance from the center 〇 1 force of the hinge pole 109 to the center of gravity 0 3 of the swash plate 110. When the stroke becomes longer, the difference in the amount of static imbalance between the maximum stroke and the minimum stroke increases, and thrust flange 140 Variations in the static imbalance of the entire rotating body including the rotation become large (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, but the rotation primary vibration becomes large, and it occurs in the car. Conventionally, weights 11 and 12 are also applied to the rear side of the swash plate 110 to reduce the vibration and noise, so that the center of gravity of the swash plate 110 approaches the center O 1 of the hinge pole. (See Figure 6).

Therefore, as the mass of the swash plate 110 increases, the mass of the thrust flange 140 also increases in order to balance static imbalance of the entire compressor. The problem is that the compressor gets too heavy.

An object of the present invention is to provide a variable capacity type swash plate compressor excellent in high-speed controllability which can suppress deterioration of static imbalance without making the swash plate heavy. . Disclosure of the invention

In order to solve the above-mentioned object, the present invention provides a rotating member fixed to a shaft and rotating integrally with the shaft, a rotating member connected to the rotating member via a link mechanism, An inclined rotating plate that rotates together with the rotation of the shaft, and 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. A piston that is connected to the inclined rotating plate via a shoe that relatively rotates a sliding surface of the inclined rotating plate, and that linearly reciprocates in a cylinder pore as the inclined rotating plate rotates. A variable displacement type swash plate type compression in which the inclination angle of the inclination rotation plate changes according to a change in the pressure of the crank chamber in which the inclination rotation plate is housed, and the stroke amount of the piston changes. In the machine, of the angle regulating member The mind Ri by the center of the plate portion of the inclined rotary plate was positioned off B down Bok side.

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 swash plate is moved from the center of the angle regulating member. The distance to the center of gravity becomes shorter. Therefore, the center of the angle regulating member approaches the center of gravity of the inclined rotating plate, and the static imbalance amount is reduced. In addition, when the center of gravity of the swash plate changes with respect to the inclination angle of the swash plate, the difference in static imbalance between the maximum stroke and the minimum stroke is small. The noise of the imbalance of the whole body is reduced.

Preferably, the center of the angle regulating member is made coincident with the center of gravity of the inclined rotating plate. Since the center of the angle regulating member is aligned with the center of gravity of the inclined rotating plate, the amount of static imbalance is zero. Therefore, the weight of the rotating member can be reduced, and the compressor can be further reduced in weight.

The present invention provides a rotating member fixed to a shaft and rotating integrally with the shaft, an inclined member connected to the rotating member via a link mechanism, and integrally rotating as the rotating member rotates. A rotary plate, a shaft insertion center hole formed in the tilted rotary plate, through which the shaft penetrates, and for regulating an angle of the tilted rotary plate with respect to the shaft; A piston which is connected to the inclined rotating plate via a shoe which relatively rotates a sliding surface, and which linearly reciprocates in a cylinder pore as the inclined rotating plate rotates. In the variable displacement type swash plate type compressor, the inclination angle of the inclined rotating plate changes according to a pressure change of a crank chamber in which the plate is accommodated, and a stroke amount of the piston changes. Ridge line of center hole for entry The center of the circle formed even Ri by the center of the plate portion of the front Symbol inclined rotary plate was positioned off B down-up side.

The center of the circle formed by the ridge line of the shaft insertion center hole is inclined. The distance from the center of the angle regulating member to the center of gravity of the swash plate becomes shorter. Therefore, the center of the angle regulating member approaches the center of gravity of the inclined rotating plate, and the amount of static imbalance is reduced. Also, when the center of gravity of the swash plate changes with respect to the inclination angle of the swash plate, the maximum stroke and the maximum Since the difference in the amount of static imbalance during a small stroke is small, the variation in the static imbalance of the entire rotating body including the rotating member is reduced.

Preferably, the center of the circle formed by the ridge line of the shaft insertion center hole coincides with the center of gravity of the inclined rotating plate.

Since the center of the circle formed by the ridge line of the shaft insertion center hole is matched with the center of gravity of the inclined rotating plate, the static imbalance amount is zero. Therefore, the weight of the rotating member can be reduced, and the compressor can be further reduced in weight. BRIEF DESCRIPTION OF THE FIGURES

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

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

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

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

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

FIG. 8 is a diagram for explaining the position of the center of gravity of the swash plate. BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings.

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

In FIG. 2, A 1, A 2, D 1, and D 2 indicate the position of the center of gravity, A max is the amount of displacement of the center of gravity of the swash plate in the Y-axis direction during the maximum stroke, and A min is The amount of displacement of the center of gravity of the swash plate in the Y-axis direction at the time of the stop stroke, D max is such that the center 〇 1 of the hinge pole 9 is larger than the center O 2 of the plate portion 10 c of the swash plate 10. The amount of deviation of the center of gravity of the swash plate in the Y-axis direction at the maximum stroke when it is positioned on the front side, and D min is the position of the swash plate at the center O 1 of the hinge pole 9. This 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 the plate portion 10c is located on the front side of the center O2 of the swash plate 10c.

In this variable displacement swash plate type compressor, cylinder head 1 has one end fixed to rear head 3 via pulsating plate 2 and the other end fixed to front head 4. A plurality of cylinder pores 6 are arranged at predetermined intervals in the circumferential direction around the shaft 5 in the cylinder hole 1 that is provided.

A piston 7 is accommodated in each of these cylinder pores 6.

A pair of showers 11 are rotatably supported at one end of the piston 7. The edge of the swash plate 10 is between the two The sliding surfaces 10a and 10b of the swash plate 10 come into contact with the flat portions of the two showers 11.

Rotational movement of the swash plate 10 is converted into linear reciprocating movement of the piston 7 via the sleeve 11, and the piston 7 slides in the cylinder pore 6.

A crank chamber 8 is formed in the front head 4. In the crank chamber 8, a hinge pole (angle restricting member) 9 is centered in conjunction with the rotation of the shaft 5. A rotating swash plate (tilt rotating plate) 10 is accommodated.

The hinge pole 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 O 1 of the hinge pole 9 is located on the front side of the center O 2 of the plate 10 c of the swash plate 10. At this time, A max, A min, B max, B min, D max, and D min must satisfy (A max — A min)> (B max-B min)> (D max-D min). There is a relationship (see Figures 2 and 7). '

A discharge chamber 12 and a suction chamber 13 located around the discharge chamber 12 are formed in the rear head 3.

The nozzle plate 2 communicates between the discharge port 16 that connects the compression chamber 6 a of the cylinder pore 6 and the discharge chamber 12, and the compression chamber 6 a of the cylinder pore 6 and the suction chamber 13. The suction ports 15 are provided at predetermined intervals in the circumferential direction.

Discharge port 16 is opened and closed by discharge valve 17 and discharge valve

17 is the valve retainer 18 on the rear end face of the valve plate 2. Both are fixed by port 19.

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

The rear end of the shaft 5 is supported by radial bearings 24 and thrust bearings 25, and the front end of the shaft 5 is supported by radial bearings 26. Have been.

Further, a pressure regulating valve 32 provided in the middle of a communication path 31 communicating between the discharge chamber 12 and the crank chamber 8 allows the pressure chamber 32 to communicate between the discharge chamber 12 and the-crank chamber 8. Pressure adjustment is performed.

A thrust flange (rotating member) 40 is fixed to the shaft 5, and a swash plate 10 is attached to the shaft 5 via a hinge pole 9. Hinge pole 9 is slidably mounted on 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 controlled by the thrust flange 40 via the link mechanism 42. From the swash plate 10 to the swash plate 10.

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

The coil spring 51 urges the hinge pole 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 swash plate type compressor will be described. When the rotational power of the vehicle engine (not shown) is transmitted to the shaft 5, the rotating power of the shaft 5 is changed to the thrust flange 4 Propagated to 0.

The swash plate 10 rotates integrally with the thrust flange 40 about the hinge 9 as the thrust flange 40 rotates.

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

As a result, the volume of the compression chamber in the cylinder pore 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 obtained. Is discharged.

At the time of suction, the suction valve 21 is opened, and low-pressure refrigerant gas is sucked from the suction chamber 13 into the compression chamber 6 a in the cylinder pore 6.

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

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

As 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 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, since the center 01 of the hinge 9 is close to the center of gravity O 3 of the swash plate 10, the static imbalance amount is small, Without increasing the weight of the swash plate 10 (compressor), it is possible to suppress the generation of vehicle vibration and noise during high-speed rotation. By adjusting the center of gravity of the swash plate closer to the center of the hinge pole, the amount of static imbalance can be easily adjusted.

Also, (. A max — A min)> (B max — B min)

> (D max-D min), the difference in the amount of static imbalance between the maximum stroke and the minimum stroke is reduced, and the thrust flange is reduced. The noise of the static imbalance of the entire rotating body including 40 can be reduced (see the straight line c in Fig. 7).

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

In this figure, when the center 01 of the hinge pole 9 is located more frontward than the center 02 of the plate portion 10c of the swash plate 10, the center 〇1 of the hinge pole 9 is This shows the case when the center of gravity O 3 of the swash plate 10 is matched.

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 swash plate compressor can be further reduced. Can be.

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

FIG. 4 is a longitudinal sectional view of a variable displacement type swash plate 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 is omitted.

This embodiment is different from the first embodiment in that the shaft 5 has a slider 59 that can slide in the axial direction and a pin 58 that is perpendicular to the axial direction of the slider 59 to form an angle regulating member. Different from the first embodiment You.

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 〇 1 of the slider 59 is located on the front side of the center 〇 2 of the plate portion 60 a 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, and the same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is 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 large diameter toward the front side and the rear side.

The center 0 1 of the circle formed by the ridge line 8 1 a of the shaft insertion center hole 81 is located on the front side of the center 0 2 of the plate portion 80 a of the swash plate 80. ing.

According to this embodiment, effects similar to those of the first embodiment can be obtained.

Also, the center of the circle formed by the ridge line 81a of the shaft insertion center hole 81 is made to coincide with the center of gravity of the swash plate 80. By setting the static unbalance amount to zero, the mass of the thrust flange 40 can be reduced, and the weight of the variable displacement swash plate compressor can be further reduced.

In the above-described embodiment, a variable displacement swash plate compressor in which the swash plates 10, 60, and 80 rotate integrally with the shaft 5 is taken as an example of the variable displacement swash plate compressor. As described above, the invention of the present application can be applied to, for example, a wobble plate compressor. In this case, the oscillating plate corresponds to the inclined rotating plate of the present invention. Industrial applicability

As described above, the variable displacement swash plate type compressor according to the present invention is useful as a refrigerant compressor of an air conditioner mounted on a vehicle such as a passenger car, a bus or a truck, Suitable as a compressor for an air conditioner that controls the amount of refrigerant gas discharged according to the required capacity.

Claims

The scope of the claims

1. a rotating member fixed to the shaft and rotating integrally with the shaft;

An inclined rotating plate that is connected to the rotating member via a link mechanism and that rotates integrally with the rotation of the rotating member, and is movably attached to the shaft, and is inserted into the shaft; An angle regulating member for regulating the angle of the inclined rotating plate;

A piston that is connected to the inclined rotating plate via a shaft that relatively rotates a sliding surface of the inclined rotating plate, and that linearly reciprocates in a cylinder pore as the inclined rotating plate rotates. ,

In the variable displacement type swash plate type compressor, the inclination angle of the inclined rotating plate changes according to the pressure change of the crank chamber in which the inclined rotating plate is housed, and the stroke amount of the piston changes. hand,

A variable displacement swash plate compressor, wherein 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.

2. The variable displacement 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 rotating plate.

3. a rotating member fixed to the shaft and rotating integrally with the shaft;

Connected to the rotating member via a link mechanism; An inclined rotating plate that rotates integrally with the rotation of the rotating member; and a shaft insertion formed in the inclined rotating plate, through which the shaft penetrates, and restricting an angle of the inclined rotating plate with respect to the shaft. A central hole,

The center of a 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 rotary plate. Plate compressor.

4. The variable displacement type swash plate type compressor according to claim 3, wherein a center of a circle formed by a ridge line of the shaft insertion center hole coincides with a center of gravity of the inclined rotating plate. .