WO2018034410A1

WO2018034410A1 - Driving part for variable-capacity compressor

Info

Publication number: WO2018034410A1
Application number: PCT/KR2017/004467
Authority: WO
Inventors: 송세영
Original assignee: 한온시스템 주식회사
Priority date: 2016-08-16
Filing date: 2017-04-26
Publication date: 2018-02-22
Also published as: US20190178236A1; KR20180019382A

Abstract

A driving part for a variable-capacity compressor, according to the present invention, comprises: a driving shaft (100) of which one end is connected to an engine pulley so as to receive driving power; a support balancer (300) coupled to one side of the driving shaft (100) at a pulley side and supporting a thrust bearing; a swash plate (500) disposed to be spaced from the support balancer (300), and adjusting a refrigerant discharge amount and pressure according to an inclination angle; a hinge part (700) for connecting the support balancer (300) and the swash plate, and transmitting the rotating power of the driving shaft (100) to the swash plate (500); and a friction ring module for generating friction force between the friction ring module and the driving shaft (100) so as to control the inclination angle of the swash plate (500) in a low-flow condition. According to the present invention, the friction ring module is provided so as to prevent hunting occurring in the low-flow condition, while maintaining controllability.

Description

Drive for variable displacement compressor

The present invention relates to a drive for a variable displacement compressor, and more particularly to a drive for a variable displacement compressor with a simplified structure of the drive.

In general, a compressor applied to an air conditioning system sucks refrigerant gas that has passed through an evaporator, compresses the refrigerant gas to a high temperature and high pressure refrigerant gas, and discharges the refrigerant gas. Various types of compressors are used, such as reciprocating type, rotary type, scroll type, and swash plate type.

In the swash plate type compressor, a disk-shaped swash plate is inclined to the drive shaft which is rotated by the power of the engine, and rotates by the drive shaft. In addition, the swash plate type compressor is a principle that sucks or compresses and discharges refrigerant gas by linearly reciprocating a plurality of pistons in a cylinder by rotation of the swash plate. For example, in the variable displacement swash plate type compressor as disclosed in Korean Patent Publication No. 2012-0100189, the inclination angle of the swash plate installed in the drive shaft is variable according to the heat load, and the reciprocating feed amount of the piston is changed as the inclination angle of the swash plate is changed. The refrigerant discharge amount is adjusted.

In general, the drive unit of the conventional variable displacement swash plate compressor is configured to adjust the inclination angle of the swash plate through the shaft bush that the hinge pin is fixed to the rotor fixed to the rotating shaft is fixed to the hub, and sliding around the rotating shaft Have

This hinge mechanism requires a process of injecting a rotor into the rotating shaft, which is complicated in the work process and the product structure, and has a disadvantage in that the price is competitive in terms of weight and process. In addition, the clearance between components due to the clearance of the hinge mechanism has a relatively large disadvantage.

It is an object of the present invention to provide a drive for a variable displacement compressor that simplifies the structure of the drive.

In order to achieve the above object, the drive unit for a variable displacement compressor of the present invention includes a drive shaft 100 having one end connected to a pulley of the engine and receiving driving force, and coupled to one side of the pulley side of the drive shaft 100 and being thrust. A support balance 300 supporting a bearing, a support plate 300 spaced apart from the support balance 300, a swash plate 500 for adjusting a refrigerant discharge amount and a pressure according to an inclination angle, the support balance 300 and the swash plate 500. The inclination angle of the swash plate 500 in a low flow condition by generating a friction force between the hinge portion 700 and the driving shaft 100 to transfer the rotational force of the drive shaft 100 to the swash plate 500 It includes a friction ring module to control.

The friction ring module includes a polygonal pipe-shaped ring body 1000 inserted along the longitudinal direction of the drive shaft 100, and a support spring 1100 inserted outside the ring body 1000.

The friction ring module includes a cylindrical ring body 1000 inserted along the longitudinal direction of the drive shaft 100, and a support spring 1100 inserted outside the ring body 1000.

The ring body 1000 has an inner diameter smaller than an outer diameter of the drive shaft 100.

The ring body 1000 is characterized in that the opening 1002 is formed along the longitudinal direction.

The ring body 1000 includes a plurality of hooks 1004 extending outward from one end facing the swash plate 500 and bent and extended in the direction of the retainer 1300.

The support spring 1100 is inserted between the hook 1004 and the ring body 1000.

The inner diameter of the support spring 1100 is larger than the outer diameter of the ring body 1000.

The gap between the ring body 1000 and the hook 1004 is greater than the thickness of the support spring 1100.

One side of the drive shaft 100 opposite to the pulley connection portion further includes a retainer 1300 of a circular or semi-circular shape to limit the movement of the friction ring module.

The ring body 1000 moves along the drive shaft 100 when the inclination angle of the swash plate 500 is changed, and stops by contacting the retainer 1300 at a minimum angle of the swash plate 500. do.

The ring body 1000 is characterized in that a plurality of friction protrusions (1006a) protruding from the inner peripheral surface toward the drive shaft 100 is formed.

The present invention also provides a variable displacement compressor including a drive shaft 100 rotatably supported in a housing and a swash plate 500 that receives a driving force received by the drive shaft 100 and variably controls the discharge amount of the refrigerant according to an inclination angle. In this case, coupled to the drive shaft 100 is movable in the axial direction, is located between the swash plate 500 and the support spring (1100) for applying a force in the direction of increasing the inclination angle, and has a force in the centrifugal direction The friction member 1000 is provided, and the friction member 1000 generates a friction force between the drive shaft 100 to limit the rapid movement of the inclination angle of the swash plate 500 under low flow conditions. .

The friction member 1000 is formed as a module with the support spring 1100 is characterized in that coupled to the drive shaft 100 in the axial direction.

The drive unit for a variable displacement compressor according to an embodiment of the present invention has an effect of preventing hunting problems generated under low flow conditions while maintaining controllability by providing a friction ring module.

1 is a perspective view showing a maximum inclination angle state of the drive unit for a variable displacement compressor according to an embodiment of the present invention,

2 is an exploded perspective view of a drive unit for a variable displacement compressor according to FIG. 1;

3 is a perspective view illustrating a friction ring of a driving unit for a variable displacement compressor according to FIG. 1;

4 is a perspective view illustrating a friction ring of a driving unit for a variable displacement compressor according to another embodiment of the present invention;

5 is a plan view illustrating a coupling state of the friction ring according to FIG. 4.

Hereinafter, with reference to the drawings, a drive unit for a variable displacement compressor according to an embodiment of the present invention will be described in detail.

1 is a perspective view showing a maximum inclination angle state of the drive unit for a variable displacement compressor according to an embodiment of the present invention, FIG. 2 is an exploded perspective view of the drive unit for a variable displacement compressor according to FIG. 1, FIG. It is a perspective view which shows the friction ring of the drive part for capacitive compressors.

As shown in Figure 1 and 2, the drive unit 10 for a variable displacement compressor according to an embodiment of the present invention is inserted into the compressor consisting of a cylinder block and a front, rear housing. The drive unit 10 includes a pulley (not shown) receiving power of an engine, a drive shaft 100 coupled to the pulley to rotate by the pulley, and a support balance 300 and a swash plate 500 coupled to the drive shaft. It is configured by. The support balancing 300 and the swash plate 500 are connected by the hinge portion 700. The coil spring 910 and the bush 900 are coupled between the swash plate 500 and the drive shaft 100 to help initial operation of the swash plate 500. A friction ring module is provided at an end side opposite to the pulley connection portion of the drive shaft 100 to prevent hunting in a low flow condition while maintaining controllability.

One end of the driving shaft 100 is rotatably supported by the front housing and the other end is rotatably supported by the rear housing. The drive shaft 100 is provided with a hinge connection portion 110 in contact with the support balance 300.

The hinge connector 110 prevents the support balance 300 from moving toward the swash plate 500, and at the same time, the hinge portion 700 to be described later is connected to the driving shaft 100. To this end, the hinge connector 110 is provided with a through hole formed through the drive shaft 100 along a direction connecting both ends of the counter weight 330 of the support balance 300 based on FIG. 1 (the support balance will be described later). The direction is defined based on the support balance because it is fixed to the combined position without rotating itself when coupled to the drive shaft). When the through-hole is formed in the hinge connection portion 110 may affect the rigidity of the drive shaft 100, it is preferable that the rigidity of the drive shaft 100 is not reduced by reinforcing the thickness of the peripheral portion where the through-hole is formed. Therefore, the hinge connector 110 is formed to protrude outward from the outer circumferential surface of the drive shaft 100.

The support balance 300 is coupled to one side of the pulley side of the drive shaft 100, and the swash plate 500 is inserted at a predetermined interval from the support balance 300.

The support balance 300 is a structure that replaces a rotor in which a conventional lug plate is integrally formed, and serves to support a thrust bearing (not shown). The reason why the conventional rotor is disposed at a position opposite to the swash plate is that yawing occurs due to the transmission of rotational force to the swash plate and the weight imbalance when a mass is provided on the drive shaft 100. This is to rebalance the function (static balance function). Conventionally, the rotor is integrally formed with a lug plate, but the size and weight are large, and the hinge structure is complicated, which makes it difficult to miniaturize the driving unit. In addition, in the process of coupling the rotor to the drive shaft 100 by a press-in process, the deformation of the drive shaft 100 and the peripheral parts. The present invention proposes a support balance 300 as a structure to replace such a rotor.

The support balance 300 includes a disc shaped bearing supporter 310, a stepped portion 312 protruding in a direction in which the pulley is connected, and having a diameter smaller than that of the bearing supporter 310, and an outer peripheral surface of the bearing supporter 310. It is provided on one side and comprises a counter weight 330 in the form of a partial ring having a larger radius than the bearing supporter 310.

The stepped part 312 is integrally formed in the bearing supporter 310, and a hollow in which the drive shaft 100 is inserted is formed in the center of the bearing supporter 310 and the stepped part 312.

The counter weight 330 is preferably disposed below the bearing supporter 310 when the counter weight 330 is based on the driving unit arrangement of FIGS. 1 and 2. The support balance 300 is a form having an eccentric load because the counter weight 330 is provided inclined. The position of the counter weight 330 is to prevent the eccentricity of the weight according to the structure of the hinge portion 700 for adjusting the swash plate angle, so that the weight of the swash plate 500 and the hinge portion 700 is biased It is deployed.

Unlike the existing rotor, in which the support balance 300 is coupled by the indentation process, the hollow portion inserted into the drive shaft 100 has an eccentric shape, thereby maintaining a structure in which the support balance 300 does not rotate on the drive shaft 100. Have

The swash plate 500 is connected to a piston (not shown) inserted into the cylinder bore provided in the cylinder block. As the swash plate 500 rotates, the piston moves linearly in the cylinder bore to suck the refrigerant or compress the refrigerant inside the cylinder bore. By adjusting the inclination angle of the swash plate 500, the refrigerant discharge amount and the pressure are adjusted.

The swash plate 500 protrudes from the swash plate arm 510 and the hub 530 on the plate surface facing the support balance 300. The swash plate arm 510 is disposed on the upper side relative to the position of FIGS. 1 and 2, and the hub 530 is spaced apart from the swash plate arm 510 and disposed on the lower side.

The swash plate arm 510 is formed of a pair of plate facing each other, the through hole is formed so that the second hinge pin 770 to be described later penetrate into the plate. A hinge portion 700 to be described later is inserted between the swash plate arms 510 to be rotatably coupled to the swash plate arms 510 by a second hinge pin 770.

The hub 530 has a substantially semi-cylindrical shape and protrudes from the swash plate arm 510 toward the support balance 300. The hub 530 serves to limit the movement of the swash plate 500 so that the swash plate 500 is not inclined to be disposed above a set angle when the inclination angle of the swash plate 500 is adjusted. To this end, the hub 530 is preferably protruded to contact the support balance 300 when the inclination angle of the swash plate 500 is the maximum.

The support balance 300 and the swash plate 500 described above are connected by the hinge 700.

The hinge part 700 includes a first hinge arm 710 disposed on both sides of the hinge connection part 110 of the drive shaft 100, a second hinge arm 730 protruding toward the swash plate arm 510, and a first hinge. The first hinge pin 750 is coupled to the arm 710 and the second hinge pin 770 is coupled to the second hinge arm 730.

The first hinge arm 710 is connected to the second hinge arm 730 and is composed of a pair of plate facing each other. The first hinge arm 710 grips the hinge connector 110 on both sides of the hinge connector 110 based on FIG. 3, and a through hole through which the first hinge pin 750 is inserted is formed. The first hinge pin 750 penetrates through one side plate of the first hinge arm 710, passes through a through hole of the hinge connection unit 110, and then penetrates through the other side plate of the first hinge arm 710. The first hinge arm 710 is rotatably coupled to the hinge connector 110 by the first hinge pin 750. When the hinge connecting portion 110 has a curved outer circumferential surface according to the shape of the outer circumferential surface of the drive shaft 100, the engaging portion with the first hinge arm 710 is lifted without surface contact. Therefore, it is preferable that the contact surface of the hinge connecting portion 110 to which the first hinge arm 710 is in contact is not flat but planar so that the first hinge arm 710 can stably hold the hinge connecting portion 110.

The second hinge arm 730 has a thickness corresponding to the gap between the pair of swash plate arms 510, and a through hole through which the second hinge pin 770 is inserted is formed. The second hinge pin 770 is inserted into one side of the swash plate arm 510 and penetrates through the second hinge arm 730 to be inserted into the other side of the swash plate arm 510 facing each other. The swash plate arm 510 is rotatably coupled to the second hinge arm 730 by the second hinge pin 770.

As shown in FIG. 2, the bush 900 is provided in a cylindrical shape and inserted between the swash plate 500 and the driving shaft 100, and a coil spring 910 is provided between the bush 900 and the driving shaft 100. Is inserted. The bush 900 is elastically supported by the coil spring 910 and slides along the drive shaft 100. When the inclination angle of the swash plate 500 is changed, the bush 900 slides together with the swash plate 500 so that the swash plate 500 can move smoothly along the drive shaft 100.

On the other hand, the friction ring module is provided to prevent the hunting phenomenon that the noise does not maintain the swash plate angle when the friction is too low in low flow conditions.

As shown in Figures 2 and 3, the friction ring module is composed of a ring body 1000 and the support spring (1100). A retainer 1300 for restricting movement of the friction ring module is inserted at an end opposite to the pulley connection portion of the drive shaft 100. The retainer 1300 has a circular or semi-circular ring shape and serves as a stopper.

The ring body 1000 is a polygonal pipe shape in which a portion thereof is cut to form the opening 1002, and is inserted along the longitudinal direction of the driving shaft 100. Since the ring body 1000 is not a cylindrical shape, the ring body 1000 is coupled in a form having play in some sections instead of completely surrounding the outer circumferential surface of the drive shaft 100. The opening 1002 is formed along the longitudinal direction of the drive shaft 100, and the inner diameter of the ring body 1000 is preferably smaller than the outer diameter of the drive shaft 100 when the opening 1002 is not opened. This is to generate a force in the direction of the drive shaft 100 and to generate a friction force between the ring body 1000 and the drive shaft 100 through this. Even if the inner diameter of the ring main body 1000 is smaller than the outer diameter of the drive shaft 100, there is no problem in assembling the ring main body 1000 because there is an opening 1002. One end of the ring body 1000 facing the swash plate 500 is formed with a plurality of hooks 1004 to which the support springs 1100 are coupled.

The hook 1004 extends outward from one end of the ring body 1000 facing the swash plate 500 and is bent and extended in the direction of the retainer 1300. The interval between the hook 1004 and the outer circumferential surface of the ring body 1000 is preferably greater than the thickness of the support spring 1100 so as not to interfere with the operation of the support spring 1100. The support spring 1100 is inserted between the hook 1004 and the ring body 1000.

One end of the support spring 1100 is inserted between the hook 1004 and the ring body 1000, and the other end thereof extends toward the retainer 1300. The inner diameter of the support spring 1100 is formed somewhat larger than the outer diameter of the ring body 1000.

Although the inner diameter of the support spring 1100 is larger than the outer diameter of the ring body 1000, the reason why the hook 1004 is provided is to facilitate the assembly of the support spring 1100. That is, the hook 1004 serves as a temporary fixing role of the support spring 1100 during assembly to prevent the support spring 1100 from escaping toward the swash plate 500. However, the hook 1004 does not interfere with the retainer 1300 side movement of the support spring 1100.

4 and 5, in the friction ring module according to another embodiment of the present invention, the ring body 1000a is formed in a cylindrical shape, and an opening 1002a is formed at one side thereof. A plurality of hooks 1004a are formed on an outer circumferential surface of the ring body 1000a, and may further include a plurality of friction protrusions 1006a protruding from the inner circumferential surface of the ring body 1000a toward the driving shaft 100 (previous implementation). Detailed description of the same configuration as the example will be omitted).

The friction protrusion 1006a serves to increase the friction force between the drive shaft 100 and the ring body 1000a, and as shown in FIG. 5, increases the force generated toward the center of the drive shaft 100.

There is no restriction on the shape of the ring body 1000a, but as in the present embodiment, the ring body 1000a is formed in a cylindrical shape, and the driving shaft 100 is supported by three points through the friction protrusion 1006a. press) has the effect of improving productivity.

If the frictional force is too high, the friction ring module is fixed to the drive shaft 100, causing a problem that the pressure does not change at all. If the frictional force is too low, the swash plate angle is difficult to keep small under low load conditions. There is a problem (hunting).

In the present invention, the inner diameter of the ring body 1000a is made smaller than the outer diameter of the drive shaft 100, or the friction protrusion 1006a is provided to properly maintain the frictional force while maintaining controllability while maintaining controllability. It is effective to prevent.

In the above-described embodiments, the

ring bodies

1000 and 1000a move between the bush 900 and the retainer 1300 inserted between the swash plate 500 and the drive shaft 100, and at the minimum angle of the swash plate 500. The movement is stopped while being pushed by 900 to contact the retainer 1300. Therefore, the length of the drive shaft 100 in the longitudinal direction of the

ring bodies

1000 and 1000a varies depending on the position of the retainer 1300 when the swash plate 500 is at the minimum angle.

On the other hand, the above-described ring body 1000 is coupled to the drive shaft 100 is movable in the axial direction, is located between the operating spring swash plate 500 and the support spring (1100) for applying a force in the direction of increasing the inclination angle, It can be configured to have a force in the direction. Accordingly, the ring body 1000 may be defined as a friction member because the ring body 1000 has an effect of generating a friction force between the driving shaft 100 and limiting the rapid movement of the inclination angle of the swash plate 500 under low flow conditions. In addition, the ring body 1000 may be formed as a module with the support spring 1100 may be coupled to the drive shaft 100 in the axial direction.

By providing the friction ring module having the structure as described above, there is an effect of preventing hunting problems generated under low flow conditions while maintaining controllability.

The present invention can be applied to a drive unit for a variable displacement compressor, which simplifies the structure of the drive unit.

Claims

A driving shaft 100 having one end connected to a pulley of the engine and receiving a driving force;

A support balance 300 coupled to one side of the pulley of the drive shaft 100 and supporting a thrust bearing;

Is disposed apart from the support balance 300, the swash plate 500 to adjust the refrigerant discharge amount and pressure in accordance with the inclination angle,

A hinge part 700 connecting the support balance 300 and the swash plate 500 and transmitting a rotational force of the driving shaft 100 to the swash plate 500;

And a friction ring module for generating a friction force between the drive shaft 100 and controlling the inclination angle of the swash plate 500 under low flow conditions.
The method of claim 1,

The friction ring module includes a variable pipe shape ring body 1000 inserted along a longitudinal direction of the drive shaft 100 and a support spring 1100 inserted outside the ring body 1000. Drive for compressor.
The method of claim 2,

The friction ring module includes a cylindrical ring body 1000 inserted along the longitudinal direction of the drive shaft 100 and a support spring 1100 inserted outside the ring body 1000. Drive part for machine.
The method according to claim 2 or 3,

The ring body 1000 is a drive unit for a variable displacement compressor, characterized in that the inner diameter is smaller than the outer diameter of the drive shaft (100).
The method of claim 4, wherein

The ring body 1000 is a drive unit for a variable displacement compressor, characterized in that the opening 1002 is formed along the longitudinal direction.
The method of claim 5,

The ring body 1000 is a drive unit for a variable displacement compressor including a plurality of hooks (1004) extending from one end toward the swash plate (500) to the outside, bent toward the retainer (1300).
The method of claim 6,

The support spring (1100) is a drive unit for a variable displacement compressor, characterized in that inserted between the hook (1004) and the ring body (1000).
The method of claim 7, wherein

The inner diameter of the support spring (1100) is a drive unit for a variable displacement compressor, characterized in that larger than the outer diameter of the ring body (1000).
The method of claim 8,

Drive between the ring body (1000) and the hook (1004) is greater than the thickness of the support spring (1100) drive unit for a variable displacement compressor.
The method of claim 9,

One side of the drive shaft (100) facing the pulley connection portion further comprises a retainer (1300) of a circular or semi-circular shape to limit the movement of the friction ring module.
The method of claim 10,

The ring body 1000 moves along the drive shaft 100 when the inclination angle of the swash plate 500 is changed, and stops by contacting the retainer 1300 at a minimum angle of the swash plate 500. A drive unit for a variable displacement compressor.
The method of claim 3,

The ring body (1000) drive unit for a variable displacement compressor, characterized in that a plurality of friction projections (1006a) protruding from the inner peripheral surface toward the drive shaft (100) is formed.
In the variable displacement compressor having a drive shaft 100 rotatably supported in the housing and a swash plate 500 to receive the driving force received by the drive shaft 100 and to variably control the discharge amount of the refrigerant according to the inclination angle,

A friction member coupled to the drive shaft 100 and movable in the axial direction, positioned between the swash plate 500 and the support spring 1100 that exerts a force in a direction in which the inclination angle increases, and has a force in the centrifugal direction. 1000,

The friction member (1000) generates a friction force with the drive shaft (100) to limit the rapid movement of the inclination angle of the swash plate (500) under low flow conditions.
The method of claim 13,

The friction member (1000) is a variable displacement compressor which is formed in a module with the support spring (1100) is axially coupled to the drive shaft (100).