KR20010014520A - Variable displacement compressor - Google Patents

Abstract

PURPOSE: To provide a variable displacement type compressor to prevent the occurrence of one-sided floating of a rotary support body with delivery capacity is varied from a maximum. CONSTITUTION: A trust bearing 61 is located between a rotary support body 17 and a front housing 11. The thrust bearing 61 has appearance formed in a ring-form state centering around the axis L of a drive shaft 16. The thrust bearing 61 bears a compression load F from a piston 22 exerted on a rotary support body 17 through a swash plate 18 and a hinge mechanism 19. The effective bearing radius 11 of a compression load F of the thrust bearing 61 is set to a valve higher than a distance between the link fulcrum S of the hinge mechanism 19 and the axis L of the drive shaft 16 in a state that the swash plate 18 is brought into a maximum inclination angle state.

Description

Variable displacement compressor {VARIABLE DISPLACEMENT COMPRESSOR}

The present invention relates to, for example, a variable displacement compressor applied to an air conditioner of a vehicle.

As such a variable displacement compressor (hereinafter, simply referred to as a compressor) of this kind, there are some as shown in FIG. 6, for example.

That is, the crank chamber 101 is partitioned in the housing 102. The drive shaft 103 is rotatably supported by the housing 102 by inserting the crank chamber 101 through. The rotary support 104 is fixed to the drive shaft 103 in the crank chamber 101. The swash plate 105 is slide-movable in the direction of the axis line L with respect to the drive shaft 103 and is inserted and supported to enable the inclined movement.

The hinge mechanism 106 is interposed between the rotary support 104 and the swash plate 105. The hinge mechanism 106 is installed on the swash plate 105 and at the same time, the guide pin 111 having the spherical portion 111a at the tip and the rotating support 104, and the spherical shape of the guide pin 111 at the tip. Part 111a is composed of a support arm 112 having a guide hole (112a) is inserted and coupled to enable the slide movement.

The swash plate 105 can be tilted with respect to the drive shaft 103 by the hinge mechanism 106 interposed with the rotation support 107 and can be rotated integrally with the drive shaft 103. have.

The cylinder bore 108 is formed in the housing 102. The piston 107 is accommodated in the cylinder bore 108 so as to reciprocate. The piston 107 is connected to the swash plate 105, and when the drive shaft 103 is driven to rotate, the swash plate 105 is integrally rotated through the rotary support 104 and the hinge mechanism 106.

The rotational motion of the swash plate 105 is converted into a reciprocating motion of the piston 107, and the suction of the refrigerant gas into the cylinder bore 108, the compression of the suction refrigerant gas, and the compressed refrigerant gas are discharged from the cylinder bore 108 A series of compression cycles is repeated.

The thrust bearing 109 is interposed between the rotational support 104 and the inner wall surface 102a of the housing 102 in the crank chamber 101. The thrust bearing 109 accommodates and supports the compression load F from the piston 107 by the compression of the refrigerant gas acting on the rotary support 104 via the swash plate 105 and the hinge mechanism 106.

The discharge capacity of the compressor is adjusted by changing the inclination angle of the swash plate 105. The swash plate 105 is guided to the hinge mechanism 106 while sliding the drive shaft 103 to change the inclination angle with respect to the drive shaft 103, whereby the stroke of the piston 107, i.e., the discharge capacity Adjusted.

The maximum inclination angle of the swash plate 105 is a portion (maximum inclination angle defining portion 110) positioned substantially opposite to the hinge mechanism 106 along the axis L of the drive shaft 103, and is directly connected to the rotary support 104. It is defined as abutment.

By the way, the compression load F is the largest at the discharge capacity with the largest amount of refrigerant gas handled in one compression cycle. However, at the maximum discharge capacity (state shown in FIG. 6), the transmission of the compressive load F from the swash plate 105 to the rotary support 104 is carried out at the link point (the spherical portion 111a) of the hinge mechanism 106. In addition to the point of contact with the inner surface of the guide hole 112a) S, the hinge mechanism 106 also passes through the maximum inclination angle defining portion 110 positioned almost opposite to the axis L of the drive shaft 103. That is, it is performed in the position where the bias in the axis line L is small. Therefore, the inclination motion moment (moment to incline with respect to the drive shaft 103) by this compressive load F does not apply to the rotation support body 104. FIG.

However, at the moment when the discharge capacity is changed (reduced) from the maximum, the direct abutment support of the inclined plate 105 through the maximum inclination angle defining portion 110 by the rotary support 104 is released and rotated from the swash plate 105. The transfer of the compressive load F (which may be regarded as the same size as the maximum discharge capacity) to the support 104 is carried out at the link point S of the hinge mechanism 106 (which may be regarded as the same position as the maximum discharge capacity). Only by passing through, that is, at the position deviated around the axis L, it becomes.

The thrust bearing 109 has an effective receiving radius I1 of the compressive load F and an axis of the link point S of the hinge mechanism 106 and the drive shaft 103 in the state of the maximum inclination angle of the swash plate 105. It is smaller than the distance between (L). Therefore, the thrust bearing 109 cannot adequately support the compression load F transmitted through the link point S (within the effective receiving radius I1).

For this reason, at the moment when the discharge capacity is changed from the maximum, the rotation support 104 has a large moment of inclination motion based on the compressive load F, so that it is partially between the inner wall surface 102a of the housing 102. It became the state which floated to one side to which space | interval becomes large. As a result, the thrust bearing 109 becomes large or the thrust bearing 109 is rotated to the inner wall surface 102a of the housing 102 by the rotating support 104 which is rotated in an inclined state with respect to the housing 102. Due to the crash, it has been a cause of abnormal sound or vibration generated by the compressor.

SUMMARY OF THE INVENTION The present invention has been made in view of the problems existing in the prior art as described above, and an object thereof is to provide a variable displacement compressor capable of preventing the occurrence of a floating state on one side of the rotating support when the discharge capacity is changed from the maximum. It is.

1 is a longitudinal sectional view of a variable displacement compressor.

2 is a view showing a state in which the discharge capacity is reduced in FIG.

3 is a perspective view showing the vicinity of the hinge mechanism;

4 is a schematic diagram illustrating a main part of the present embodiment.

5 is a longitudinal sectional view of the variable displacement compressor of the second embodiment;

6 is a vertical cross-sectional view of a conventional variable displacement compressor.

(Explanation of symbols for the main parts of the drawing)

11. Front housing constituting the housing

12. Cylinder block making up the housing

12a. Cylinder bore

13. Rear housing constituting the housing

15. Crankcase

16. Drive shaft

17. Rotating Support

18. Swash plate as a cam plate

19. Hinge mechanism

35. Maximum inclination angle regulation

61. Thrust Bearing

F. Compression Load

L. Axis of Drive Shaft

S. Link Point

I1. Effective Acceptance Radius of Compression Load in Thrust Bearing

I2. Distance between the link point of the hinge mechanism and the axis of the drive shaft when the cam plate is at its maximum inclination angle.

In order to achieve the above object, in the invention of claim 1, the housing is configured as the end housing and the cylinder block is fixedly bonded, the housing is enclosed by the end housing and the cylinder block to form a crank seal, the end housing Drive shaft is hypothetically rotatably supported by inserting a crank chamber between the cylinder block and the cylinder block, a cylinder bore is formed in the cylinder block, a migrating piston is accommodated in the cylinder bore, and a drive shaft in the crank chamber. Rotating support is fixed to the rotatable support integrally, the cam support is connected to the rotatable support through the hinge mechanism, and also possible to change the inclination angle, the piston is connected to the cam plate, The rotational movement of the drive shaft is rotated support, hinge mechanism and cam play The gas is compressed in the cylinder bore by converting the piston into a reciprocating motion. In the crank chamber, a compression load acting on the rotating support is received between the rotating support and the end housing in accordance with the compression of the gas. The thrust bearing for supporting is interposed, and the discharge capacity can be changed by changing the inclination angle of the cam plate, and the maximum inclination angle of the cam plate is rotated with the maximum inclination angle defining portion that moves in accordance with the change of the inclination angle of the cam plate. In the variable displacement compressor of the configuration defined by the contact with the support,

The effective receiving radius of the compressive load in the thrust bearing is a variable displacement compressor characterized in that the cam plate is set to be equal to or larger than the distance between the link point of the hinge mechanism and the axis of the drive shaft in the state of the maximum inclination angle.

In this configuration, the transmission of the compressive load from the cam plate to the rotational support at the maximum discharge capacity is also performed through the maximum inclination angle defining portion in addition to the link point of the hinge mechanism, i.e., at a position where the bias in the axis of the drive shaft is small. Getting Therefore, the tilting moment based on this compressive load does not act on the rotating support.

However, at the moment when the discharge capacity is changed (reduced) from the maximum, the direct contact of the cam plate through the maximum inclination angle defining portion by the rotating support is released, and the transmission of the compressive load from the cam plate to the rotating support is carried out by the hinge mechanism. This is done only through the link point of, i.e., at a position biased around the axis of the drive shaft.

Here, the effective receiving radius of the compressive load in the thrust bearing is set to be equal to or more than the distance between the link point of the hinge mechanism and the axis of the drive shaft in the state where the cam plate is at the maximum tilt angle. Therefore, even if the transmission position of the compression load from the cam plate to the rotary support at the moment when the discharge capacity is changed from the maximum is only the link point of the hinge mechanism, it is within the effective receiving radius of the thrust bearing.

As a result, the supporting load of the compressive load by the thrust bearing is appropriately performed, and the inclined motion moment is not applied to the rotating support, so that the floating state can be prevented.

According to claim 2, The hinge mechanism is a spherical portion provided on one side of the rotary support or the cam plate, the guide is installed on the other side of the rotary support or the cam plate, the spherical portion is guided to allow relative slide movement It is characterized by consisting of a ball.

In this configuration, the link point of the hinge mechanism is a point of contact with the spherical portion and the guide hole.

(Example)

The following describes the first and second embodiments of the present invention in the variable displacement compressor applied to an air conditioner of a vehicle. In the second embodiment, only differences from the first embodiment will be described.

(First embodiment)

As shown in FIG. 1, the front housing 11 as an end housing is joined and fixed to the front end (left side of the figure) of the cylinder block 12. As shown in FIG. The rear housing 13 is fixed to the rear end of the cylinder block 12 by fitting the valve port forming member 14 to the rear end (right side of the drawing). The front housing 11, the cylinder block 12 and the rear housing 13 constitute a housing of the compressor. The crank chamber 15 is enclosed by the front housing 11 and the cylinder block 12 to form a partition.

The drive shaft 16 is hypothetically rotatable between the front housing 11 and the cylinder block 12 so as to pass through the crank chamber 15.

The rotary support 17 is fixed to the drive shaft 16 in the crank chamber 15. The swash plate 18 as a cam plate is accommodated in the crank chamber 15. The drive shaft 16 is inserted through the through hole 18a which is provided through the central portion of the swash plate 18. The hinge mechanism 19 is interposed between the rotary support 17 and the swash plate 18.

As shown in FIG. 1 and FIG. 3, the hinge mechanism 19 has a pair of guide pins 20 at a symmetrical position centering on the top dead center corresponding position D1 at the front outer periphery of the swash plate 18. It is installed. The spherical portion 20a is formed at the tip of the guide pin 20. The pair of support arms 21 are protruded at a symmetrical position centering on the top dead center corresponding position D1 of the swash plate 18 on the rear surface of the rotary support 17. The guide hole 21a is penetrated to the front end of each support arm 21. Each guide pin 20 is inserted into and coupled to the guide hole 21a of the corresponding support arm 21 by the spherical portion 20a.

The swash plate 18 is a slide guide relationship between the spherical portion 20a of the guide pin 20 and the guide hole 21a of the support arm 21, and slide support through the through hole 18a by the drive shaft 16. By the action, the inclined movement is possible while slidingly moving in the direction of the axis L with respect to the drive shaft 16.

As shown in FIG. 2, when the radial center part of the swash plate 18 slides to the cylinder block 12 side, the spherical part 20a of the guide pin 20 will guide the hole 21a of the support arm 21. As shown in FIG. The inside of the hinge mechanism 19 is moved to the axis L side, that is, the link point (the point of contact between the spherical portion 20a and the inner surface of the guide hole 21a) S of the hinge mechanism 19 is the guide hole 21a. The inclination angle of the swash plate 18 is reduced by moving toward the axis L side of the drive shaft 16 along the inclination of.

As shown in FIG. 1, when the radial center part of the swash plate 18 slides to the rotating support body 17, the spherical part 20a moves in the guide hole 21a to the opposite side to the axis L, ie, , The link point S of the hinge mechanism 19 moves to the side opposite to the axis L side along the inclination of the guide hole 21a, so that the inclination angle of the swash plate 18 is increased. The maximum inclination angle of the swash plate 18 is on the opposite side of the hinge mechanism 19 and is located on the substantially opposite side, that is, a convex portion (maximum inclination angle defining portion 35) located near the bottom dead center corresponding position D2. ) Is defined to abut directly with the rotating support 17 (without the hinge mechanism 19).

A plurality of cylinder bores 12a (only two are shown in the drawing) are formed on the same circumference of the axis L of the drive shaft 16 in the cylinder block 12 at predetermined intervals. have. In the lateral piston 22, the head 22a side is accommodated in the cylinder bore 12a. The piston 22 is moored to the outer circumference of the swash plate 23 with the shoe 23 on the neck 22b side. The piston 22 has a rotational movement of the drive shaft 16 is converted through the swash plate 18 and the shoe 23 so that the head 22a is moved back and forth in the cylinder bore 12a.

The suction chamber 24 and the discharge chamber 25 are partitioned in the rear housing 13, respectively. The suction port 26, the suction valve 27, the discharge port 28, and the discharge valve 29 are formed in the valve port forming body 14, respectively.

When the drive shaft 16 is rotated by an external drive source such as a vehicle engine (not shown), the refrigerant gas in the suction chamber 24 is sucked by moving from the top dead center side to the bottom dead center side of the piston 22. It is sucked into the cylinder bore 12a through the port 26 and the suction valve 27. The refrigerant gas sucked into the cylinder bore 12a is compressed to a predetermined pressure by moving from the bottom dead center side to the top dead center side of the piston 22 and discharged to the discharge chamber 25 through the discharge port 28 and the discharge valve. do.

The additional passage 30 communicates the crank chamber 15 and the suction chamber 24. The air supply passage 31 communicates the discharge chamber 25 with the crank chamber 15. The displacement control valve 32 is disposed in the air supply passage 31. Then, the opening degree of the air supply passage 31 is adjusted by the capacity control valve 32, so that the inflow of the high pressure discharge refrigerant gas from the discharge chamber 25 to the crank chamber is adjusted, and through the bleed passage 30. The pressure of the crank chamber 15 is changed in relation to the discharge amount of the refrigerant gas into the suction chamber 24.

As the pressure of the crank chamber 15 is changed, the pressure of the cylinder bore 12a and the difference through the piston 22 are changed, and the inclination angle of the swash plate 18 is changed to adjust the discharge capacity.

Next, the feature points of this embodiment will be described.

As shown in FIG. 1, the thrust bearing 61 is interposed between the front surface of the rotary support 17 and the inner wall surface 11a of the front housing 11 in the crank chamber 15. The thrust bearing 61 is comprised in ring shape centering on the axis L of the drive shaft 16 in the external appearance. The thrust bearing 61 is applied to the rotary support 17 through the swash plate 18 and the hinge mechanism 19. A compression load F from the piston 22 is accommodated and supported by the compression of the refrigerant gas.

The thrust bearing 61 has a ring-shaped rotary side race 62 whose rotation is blocked by the rotary support 17 and a ring-shaped fixed side race whose rotation is prevented by the inner wall surface 11a of the front housing 11. (63) and a plurality of transmission elements 64 (only two are shown in FIG. 1) comprising rollers interposed between the races 62 and 63 are provided. The power elements 64 are disposed radially about the axis L, and the races 62 and 63 are rotated by the relative rotation of both races 62 and 63 in accordance with the rotation of the rotary support 17. It rotates around the axis (L) while rotating the above.

As shown in Figs. 1 and 4, the thrust bearing 61 has a link point of the hinge mechanism 19 in which the effective receiving radius I1 of the compressive load F is the maximum and the swash plate 18 is at the maximum inclination angle. It is set more than the distance I2 between (S) and the axis line L of the drive shaft 16. The effective receiving radius I1 in the thrust bearing 61 is the radius of the electric trajectory which is drawn at the outermost circumference of the contact portion with both races 62 and 63 in the transmission element 64. Say

By the way, as shown in FIG. 1, in the state of the compressor maximum discharge capacity, the transmission of the compressive load F from the swash plate 18 to the rotation support 17 is carried out to the link point S of the hinge mechanism 19. As shown in FIG. In addition, also through the maximum inclination angle defining part 35 which is located about the opposite side to the hinge mechanism 19, and is located in the substantially opposite side, ie, in the position where the bias in the axis L of the drive shaft 16 is small. All. Therefore, the inclination motion moment by this compressive load F does not act on the rotation support 17.

However, at the moment when the discharge capacity is changed (reduced) from the maximum, the direct contact of the swash plate 18 through the maximum inclination angle defining portion 35 by the rotary support 17 is released, and the swash plate 18 The transmission of the compressive load F (which may be regarded as the same size as the maximum discharge capacity) from the rotating support 17 to the rotating support 17 may be regarded as the same position as the link point S of the hinge mechanism 19 (the maximum discharge capacity). It is performed only at the position which is biased about the axis L of the drive shaft 16 only by passing through.

Here, the effective receiving radius I1 of the compression load F in the thrust bearing 61 is the link point S and the drive shaft 16 of the hinge mechanism 19 with the swash plate 18 at the maximum inclination angle. It is set to the distance I2 or more between the axis line L of ().

Therefore, even when the delivery position of the compression load F from the swash plate 18 to the rotary support 17 becomes only the link point S of the hinge mechanism 19 at the moment when the discharge capacity is changed from the maximum, it is the thrust bearing. It is within the effective acceptance radius I1 of (61). As a result, accommodating support of the compressive load F by the thrust bearing 61 is performed suitably, and the inclination motion moment is not acted on the rotation support 17, and the state floating to one side can be prevented.

Therefore, abnormal noise and vibration of the compressor due to floating on one side of the rotary support 17 are eliminated, and the air conditioning atmosphere of the vehicle air conditioning system is improved.

(Second embodiment)

As shown in FIG. 5, in this embodiment, the support structure of the swash plate 18 by the drive shaft 16 and the structure of the hinge mechanism 71 are different from the first embodiment.

That is, the sleeve 72 is provided on the drive shaft 16 so as to be slidable back and forth in the direction of the axis L. As shown in FIG. A pair of support pins 73 are provided on both left and right sides of the sleeve 72 (only one is shown in the drawing). The swash plate 18 is supported to the sleeve 72 so as to change the inclination angle through the support pin 73.

One support arm 75 is provided at a position opposite to the top dead center corresponding position D1 of the swash plate 18 on the rear surface of the rotary support 17. The guide hole 75a has an elongated hole shape and penetrates in the horizontal direction (the front and back direction of the ground, and in the vertical direction of the ground in the guide hole 21a of the first embodiment) at the tip of the support arm 75. have. The link pin 74 is disposed in the horizontal direction across the top dead center corresponding position of the swash plate 18 and is coupled to the guide hole 75a of the support arm 75.

Then, the swash plate 18 is a slide guide relationship between the link pin 74 and the guide hole 75a of the support arm 75 and the slide support action through the sleeve 72 by the drive shaft 16. The inclined movement is possible while slidingly moving with respect to the drive shaft 16 in the axis line L direction. For example, when the sleeve 72 moves on the drive shaft 16 to the cylinder block 12 side by slide, the link point of the hinge mechanism 71 (the outer peripheral surface of the link pin 74 and the guide hole 75a) An abutting line S in the surface front and rear direction with the inner surface is moved along the guide hole 75a toward the axis L side of the drive shaft 16, so that the inclination angle of the swash plate 18 is reduced.

On the contrary, when the sleeve 72 slides on the drive shaft 16 toward the rotational support 17 side, the link point S of the hinge mechanism 71 is located along the guide hole 72a with the axis L side. Moving to the opposite side, the inclination angle of the swash plate 18 is increased.

The maximum inclination angle of the swash plate 18 is defined such that the front end face of the sleeve 72 as the maximum inclination angle defining portion is in direct contact with the rotary support 17.

Also in the thrust bearing 61 of this embodiment, the effective receiving radius I1 of the compression load F is the link of the hinge mechanism 71 in the state where the swash plate 18 is the maximum inclination angle (state shown in FIG. 5). It is set more than the distance I2 between the point which is farthest from the axis line L of the point S, and the axis line L of the drive shaft 16 (relationship similar to FIG. 4). Thus, the same operations and effects as those of the first embodiment are obtained.

Moreover, it can also be implemented in the following forms within the range which does not deviate from the meaning of this invention.

○ In the hinge mechanism 19 of the first embodiment, the support pin 21 (guide hole 21a) is placed on the rotational support 17 side with the guide pin 20 (spherical portion 20a). It is installed on the 18) side.

In the hinge mechanism (71) of the second embodiment, the support pin (75) is provided on the swash plate (18) with the link pin (74) on the rotational support (17) side.

In the hinge mechanism 19 of the first embodiment, only one set of the guide pin 20 (spherical portion 20a) and the support arm 21 (processing 21a) is used.

O At least one race 62, 63 is removed from the thrust bearing 61, and on this side, the transmission element 64 is placed on the front surface of the rotary support 17 or inside the front housing 11; It is set as the structure to electrically drive directly on the wall surface 11a. In this way, the number of parts constituting the compressor can be reduced.

O The transmission element 64 of the thrust bearing 61 as a ball. In addition, the thrust bearing 61 is not limited to a transmission base, but may be a transmission base structure without a transmission element.

To be specified in waffle type variable displacement compressors.

According to the present invention having the above-described configuration, even when the discharge capacity is changed from the maximum, the support for receiving the compressive load by the thrust bearing can be appropriately performed to prevent the floating state on one side of the rotating support.

Claims (2)

The housing is configured as the end housing and the cylinder block are bonded and fixed, The housing is surrounded by the end housing and the cylinder block to form a crank chamber, Between the end housing and the cylinder block is inserted into the crank chamber through the drive shaft is hypothetically rotatably supported, The cylinder block is formed with a cylinder bore, The cylinder bore receives a migraine piston, In the crank chamber, the rotating support is fixed to the drive shaft to be integrally rotatable, Cam plate is rotatably connected to the rotatable support through a hinge mechanism, it is possible to change the inclination angle, The cam plate is connected to the piston, The rotation of the drive shaft is converted into a reciprocating motion of the piston through the rotating support, the hinge mechanism and the cam plate, thereby compressing the gas in the cylinder bore, In the crank chamber, a thrust bearing is interposed between the rotary support and the end housing to accommodate the compression load acting on the rotary support in accordance with the compression of the gas. It is possible to change the discharge capacity by changing the inclination angle of the cam plate, In a variable displacement compressor having a configuration in which the maximum inclination angle of the cam plate is defined by abutment between the maximum inclination angle defining portion moving in accordance with the change of the inclination angle of the cam plate and the rotating support, The effective capacity of the compressive load in the thrust bearing is a variable displacement compressor, characterized in that the cam plate is set to be equal to or more than the distance between the link point of the hinge mechanism and the axis of the drive shaft in the state of the maximum inclination angle. The method of claim 1, The hinge mechanism is variable, characterized in that it consists of a spherical portion provided on one side of the rotating support, or cam plate, and a guide hole installed on the other side of the rotating support or cam plate, the spherical portion is inserted and coupled to allow relative slide movement. Capacity compressors.