KR102006341B1

KR102006341B1 - Variable displacement swash plate type compressor

Info

Publication number: KR102006341B1
Application number: KR1020140003017A
Authority: KR
Inventors: 정유철; 손은기; 안혜림; 안휴남; 윤제수
Original assignee: 한온시스템 주식회사
Priority date: 2014-01-09
Filing date: 2014-01-09
Publication date: 2019-08-02
Also published as: KR20150083366A

Abstract

The present invention is a rotating shaft, the rotor is coupled to the rotary shaft and integrally rotated with the rotary shaft, the hinge is formed on one side, the hinge is coupled to the rotary shaft to face the rotor and the hinge receiving portion formed on one side of the hub, the hub A variable displacement swash plate type compressor comprising a swash plate formed on an outer circumferential surface and having a variable inclination angle. By disposing, it is possible to easily control the swash plate angle at the initial stage of driving of the compressor without including a separate pressure spring.

Description

[0001] DESCRIPTION [0002] VARIABLE DISPLACEMENT SWASH PLATE TYPE COMPRESSOR [0003]

The present invention relates to a variable displacement swash plate type compressor capable of controlling the swash plate angle in the initial stage without a pressure spring.

Generally, compressors for compressing refrigerant in a vehicle cooling system have been developed in various forms. Such a compressor includes a reciprocating type in which compression is performed while reciprocating the refrigerant, There is a rotary that performs.

Here, the reciprocating type includes a crank type for transmitting the driving force of the driving source to the plurality of pistons using a crank, a swash plate type for transmitting to a rotating shaft provided with a swash plate, and a wobble plate type using a wobble plate. There are vane rotary using vanes, scrolling using rotating scrolls and fixed scrolls.

On the other hand, as the swash plate type compressor, there are a fixed displacement type in which the installation angle of the swash plate is fixed and a variable displacement type in which the discharge displacement can be changed by changing the inclination angle of the swash plate.

FIG. 1 shows the construction of a general variable capacity swash plate type compressor. Hereinafter, a schematic configuration of the variable displacement swash plate type compressor will be described with reference to FIG.

A variable capacity swash plate type compressor 10 is provided with a cylinder block 20 forming a part of an outer appearance and a skeleton of the compressor 10. At this time, the center bore 21 is formed through the center of the cylinder block 20, the rotation shaft 30 is rotatably installed in the center bore 21.

A plurality of cylinder bores 22 are formed through the cylinder block 20 so as to radially surround the center bore 21, and the piston 23 is installed in the cylinder bore 22 so as to linearly reciprocate. At this time, the piston 23 is formed in a cylindrical shape, the cylinder bore 22 is a cylindrical space corresponding thereto, and the refrigerant in the cylinder bore 22 is compressed by the reciprocating motion of the piston 23.

The front housing 40 is coupled to the front of the cylinder block 20. The front housing 40 has a concave surface opposed to the cylinder block 20 to form a crank chamber 41 therein together with the cylinder block 20.

In front of the front housing 40, a pulley 42 connected to an external power source (not shown) such as an engine is rotatably installed, and the rotation shaft 30 rotates in association with the rotation of the pulley 42.

The rear housing 50 is coupled to the rear of the cylinder block 20. At this time, the discharge chamber 51 is formed in the rear housing 50 along a position adjacent to the outer circumferential side edge of the rear housing 50 to selectively communicate with the cylinder bore 22, and the radial direction of the discharge chamber 51. The suction chamber 52 is formed at the inner side, that is, the central portion of the rear housing 50.

At this time, the valve plate 60 is interposed between the cylinder block 20 and the rear housing 50, and the discharge chamber 51 is connected to the cylinder bore 22 through the discharge port 61 formed in the valve plate 60. In communication with each other, the suction chamber 52 communicates with the cylinder bore 22 through the suction port 62 of the valve plate 60.

On the other hand, the rotor 70 is installed on one side of the rotary shaft 30, the rotor 70 is rotated integrally with the rotary shaft 30 when the rotary shaft 30 rotates. At this time, the rotor 70 is installed in the crank chamber 41 so that the rotation shaft 30 passes through the center thereof, and a hinge portion 71 protrudes from one surface of the rotor 70.

The swash plate 80 is installed on the rotation shaft 30 spaced apart from the rotor 70. In the swash plate 80, a hinge receiving portion 81 hinged to the hinge portion 71 of the rotor 70 is formed to protrude, and the hinge portion 71 and the swash plate of the rotor 70 are formed by the hinge pin 72. The hinge receiving portion 81 of the 80 is hinged, the swash plate 80 is rotated together when the rotor 70 rotates.

The swash plate 80 is connected to each of the pistons 23 by the shoe 82, and the rotation of the swash plate 80 compresses the refrigerant while linearly reciprocating in the cylinder bore 22. .

At this time, the angle of the swash plate 80 with respect to the rotation shaft 30 is variable so that the amount of refrigerant discharged from the compressor 10 can be adjusted. For this purpose, the discharge chamber 51 and the crank chamber 41 communicate with each other. The opening degree of the flow path (not shown) is controlled by a pressure control valve (not shown), and the inclination angle of the swash plate 80 is changed by the pressure change of the crank chamber 41.

Looking at the initial state of the drive of the compressor, when the rotary shaft 30 receives power from the engine and rotates, the rotary shaft 30 and the rotor 70 rotate together. When the rotor 70 rotates, the swash plate 80 reciprocates along the longitudinal direction of the rotation shaft 30 by the set pressure in the crank chamber 41 and the elastic pressing action of the pressure spring 63 and the return spring 64. At the same time, the angle of inclination changes and rotates.

As such, in the initial stage of driving of the compressor, a pressure spring 63 is required to help increase the angle of the swash plate 80. However, after the operation of the compressor, that is, after the inclination angle of the swash plate 80 is formed, the pressure spring 63 is unnecessary because it does not participate in the operation of the compressor.

Since the pressure spring plays a small role in the operation of the compressor, it has to be mounted in the compressor as a separate component. Therefore, the conventional swash plate compressor has disadvantages such as an increase in the number of parts and the addition of a production process. There is an accompanying problem.

The present invention is to solve the above-mentioned problems of the prior art, an aspect of the present invention is to provide a variable displacement swash plate-type compressor that is easy to control the swash plate angle during the initial drive of the compressor without a pressure spring.

The driving unit of the variable displacement swash plate type compressor according to an embodiment of the present invention includes a rotary shaft, a rotor coupled to the rotary shaft and integrally rotating with the rotary shaft and having a hinge portion formed at one side thereof, so as to face the rotor. A hinge receiving portion coupled to the hinge portion and correspondingly coupled to the hinge portion may include a hub formed on one side, and a swash plate formed on an outer circumferential surface of the hub and having a variable inclination angle. It may be placed inclined to have an initial tilt angle of greater than 0 ° with respect to the vertical direction.

In the driving unit of the variable displacement swash plate compressor according to an embodiment of the present invention, the initial inclination angle may be 0.2 ° or more.

In the driving unit of the variable displacement swash plate compressor according to an embodiment of the present invention, the swash plate having the initial inclination angle may be inclined toward a direction in which the inclination angle of the swash plate is variable.

In the drive unit of the variable displacement swash plate type compressor according to an embodiment of the present invention, a hinge slot having a long hole shape is formed in the hinge portion, a through hole communicating with the hinge slot is formed in the hinge receiving portion, The hinge portion and the hinge receiving portion are correspondingly coupled by penetratingly coupled to the through hole and the hinge slot, and the swash plate may be disposed to have the initial inclination angle by supporting the hinge pin at an end of the hinge slot.

In the variable displacement swash plate type compressor according to the embodiment of the present invention, a center bore is formed in the center of the cylinder block and a plurality of cylinder bores are formed to be spaced apart from each other in the circumferential direction radially outward of the center bore, the cylinder block A front housing formed at the front and having a crank chamber formed therein, a rotating shaft rotatably installed through the center of the front housing and the cylinder block, coupled to the rotating shaft to rotate integrally with the rotating shaft, Rotor formed with a hinge portion, the hinge is coupled to the rotating shaft to face the rotor, the hinge receiving portion corresponding to the hinge portion is formed on one side, the outer peripheral surface of the hub is formed and the inclination angle is changed by the pressure change of the crank chamber The swash plate, and the rotation of the rotary shaft is received through the swash plate A linear reciprocating piston in the lining bore, wherein the swash plate in the pre-drive state of the compressor is arranged to be inclined so as to have an initial inclination angle of greater than 0 ° with respect to the vertical direction of the axis of the rotating shaft. Can be.

In the variable displacement swash plate compressor according to the embodiment of the present invention, the initial inclination angle may be 0.2 ° or more.

In the variable displacement swash plate compressor according to the embodiment of the present invention, the swash plate having the initial inclination angle may be inclined toward a direction in which the inclination angle of the swash plate is varied.

In the variable displacement swash plate type compressor according to an embodiment of the present invention, a long slot-shaped hinge slot is formed in the hinge portion, and a through hole communicating with the hinge slot is formed in the hinge accommodating portion so that a hinge pin passes through the hinge pin. The hinge portion and the hinge receiving portion are correspondingly coupled by penetrating through the hole and the hinge slot, and the swash plate may be disposed to have the initial inclination angle by supporting the hinge pin at the end of the hinge slot.

The features and advantages of the present invention will become more apparent from the following detailed description based on the accompanying drawings.

According to the present invention, since the swash plate is inclined at an initial inclination angle, the swash plate angle can be easily controlled at the initial stage of driving of the compressor even when the elastic pressing force by the pressure spring is not applied.

As a result, it may not include the pressure spring that had to be provided in the prior art, and as a result, benefits such as a reduction in the number of parts, a simplification of the manufacturing process, and a reduction in the weight of the compressor may be provided.

1 is a cross-sectional view of a conventional variable displacement swash plate compressor.
2 is a cross-sectional view of a variable displacement swash plate compressor according to an embodiment of the present invention.
3 and 4 are side views of main parts of the variable displacement swash plate compressor shown in FIG.

Hereinafter, a variable displacement swash plate compressor according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation.

In addition, the terms described below are defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

In addition, the following embodiments are not intended to limit the scope of the present invention, but merely as exemplifications of the constituent elements set forth in the claims of the present invention, and are included in technical ideas throughout the specification of the present invention, Embodiments that include components replaceable as equivalents in the elements may be included within the scope of the present invention.

2 is a cross-sectional view of a variable displacement swash plate compressor according to an embodiment of the present invention. As shown, the variable displacement swash plate compressor 100 according to an embodiment of the present invention, the housing 110, 120, 130, the rotary shaft 161, the rotor 170, the hub 181, The swash plate 180 and the piston 140 may be included.

Here, the housing forms the overall appearance of the compressor 100, and may include a cylinder block 110, a front housing 120, and a rear housing 130 as shown.

The cylinder block 110 may be positioned at an approximately middle portion of the entire length of the housing, and may include a cylinder disposed between the front housing 120 and the rear housing 130. A center bore 112 is formed in the inner center of the cylinder block 110 to accommodate the rotating shaft 161 described later, and a plurality of cylinder bores 111 are formed in the radially outer side of the center bore 112.

Piston 140 is accommodated in each cylinder bore 111 to compress the refrigerant while reciprocating.

The front housing 120 and the rear housing 130 may be coupled to close both open ends of the cylinder block 110. The front housing 120 is coupled to the cylinder block 110, the crank chamber 121 is formed therein, the rotation and the change of the inclination angle of the swash plate 180 to be described later in the crank chamber 121 is made.

On one side of the front housing 120, that is, the opposite side of the cylinder block 110, a pulley 122 that rotates under the driving force of the engine is rotatably installed, and an inner circumference of the pulley 122 is coupled to the rotating shaft 161. Hubs (not shown) are installed.

Between the cylinder block 110 and the rear housing 130, the valve assembly 150 for controlling the flow of the refrigerant from the suction chamber 131 to the cylinder bore 111, from the cylinder bore 111 to the discharge chamber 133 May be interposed.

The rear housing 130 is coupled to the cylinder block 110 on the opposite side where the front housing 120 is installed. The rear housing 130 may be formed with a suction chamber 131 that selectively communicates with the cylinder bore 111. The suction chamber 131 may be formed in a region corresponding to the center of the rear housing 130 facing the cylinder block 110, and the suction chamber 131 is a refrigerant to be compressed in the cylinder bore 111. It is a temporary storage function.

In addition, a discharge chamber 133 may be formed in the rear housing 130. The discharge chamber 133 is also selectively in communication with the cylinder bore 111. The discharge chamber 133 is formed at a position adjacent to an edge of a surface of the rear housing 130 that faces the cylinder block 110. The discharge chamber 133 is a space where the refrigerant compressed in the cylinder bore 111 is discharged and temporarily stays. The refrigerant temporarily stored in the discharge chamber 133 is discharged to the outside of the compressor 100 through a discharge port (not shown).

The rotating shaft 161 is installed through the cylinder block 110 and the front housing 120. The rotary shaft 161 is rotated by a driving force transmitted from the engine through the pulley 122. The rotary shaft 161 is rotatably supported by the cylinder block 110 and the front housing 120. More specifically, the front end of the rotary shaft 161 is rotatably supported through the central portion of the front housing 120, the rear end of the rotary shaft 161 is the center bore 112 formed in the central portion of the cylinder block 110 Is rotatably supported.

The rotor 170 is coupled to the rotary shaft 161, and the rotor 170 is integrally rotated together with the rotary shaft 161. On one side of the rotor 170, a hinge portion 175 corresponding to the hinge receiving portion 182 to be described later is formed to protrude.

Spaced behind the rotor 170, the hub 181 is coupled to the rotation shaft 161. At this time, a hinge accommodating part 182 corresponding to the hinge part 175 of the rotor 170 is formed on one side of the front surface of the hub 181, and the rotor 170 and the hub 181 are hinge part 175. The hinge is coupled by a hinge pin (P) connecting the hinge receiving portion (182). Accordingly, when the rotor 170 rotates, the hub 181 rotates integrally with the rotor 170, and the inclination angle of the hub 181 may be changed with respect to the rotation shaft 161 together with the swash plate 180 to be described later. This will be described in more detail with reference to FIGS. 3 and 4.

Meanwhile, a return spring 162 is interposed between the rotor 170 and the hub 181 to elastically press the swash plate 180 to its original position when the swash plate 180 is inclined.

The swash plate 180 is coupled to the outer circumferential surface of the hub 181 to rotate integrally with the rotor 170 and the hub 181 when the rotary shaft 161 rotates, and the piston 140 rotates the driving force of the rotary shaft 161. Switch to reciprocating linear motion of). That is, the engaging portion 141 which is bent in front of the piston 140 is supported by the shoe 142 to the edge of the swash plate 180, the swash plate 180 is rotated at a predetermined angle inclined swash plate 180 Piston 140 is caught on the edge of the reciprocating motion inside the cylinder bore (111).

As described above, the swash plate 180 is installed so that the inclination angle with respect to the rotary shaft 161 is variable so that the refrigerant discharge capacity of the compressor 100 can be adjusted. For example, when the swash plate 180 is inclined at an angle with respect to the rotation shaft 161, when the swash plate 180 rotates about the rotation shaft 161, the piston 140 may move in the cylinder bore 111. It reciprocates and compresses the refrigerant. On the contrary, when the inclination angle of the swash plate 180 with respect to the rotary shaft 161 is 90 degrees, the reciprocating motion of the piston 140 disappears, and the rotary shaft 161 is idle.

The inclination angle of the swash plate 180 is controlled by a pressure regulating valve (not shown) installed at one side of the rear housing 130. The pressure regulating valve communicates the discharge chamber 133 and the crank chamber 121. The opening degree of the flow path (not shown) is adjusted, and the inclination angle of the swash plate 180 changes according to the pressure change of the crank chamber 121. At this time, the stroke of the piston 140 is changed according to the change of the inclination angle of the swash plate 180 to adjust the discharge amount of the refrigerant.

In more detail, the pumping moment is generated from the force of the compression force generated during the suction and compression of the refrigerant during the operation of the compressor 100, while the crankcase moment is generated by the internal pressure of the crank chamber 121. . The total force of these moments determines the angle of inclination of the swash plate 180. The pumping moment is generated in the process of compressing and suctioning the refrigerant and cannot be arbitrarily controlled. On the other hand, the crankcase moment can change the magnitude of the moment by controlling the pressure of the crankcase 121. Therefore, the inclination of the swash plate 180 can be changed by changing the pressure of the crank chamber 121.

On the other hand, the piston 140 is a means for compressing the refrigerant while reciprocating the inside of the cylinder bore 111 by the swash plate 180, it is connected to the edge portion of the swash plate 180 to be relatively movable through the shoe 142. As the swash plate 180 rotates, linearly reciprocating motion is performed along the inner circumferential surface of the cylinder bore 111 of the cylinder block 110, thereby compressing the refrigerant sucked into the cylinder bore 111.

At this time, the refrigerant compressed by the cylinder bore 111 by the piston 140 is discharged to the discharge chamber 133 of the rear housing 130 through the discharge port, and then to the external cooling system through the discharge port (not shown) Supplied.

3 and 4 are side views illustrating a driving unit constituting the compressor 100. As shown, the drive unit of the compressor 100 is installed inside the crank chamber 121 to linearly reciprocate the piston 140 in the cylinder bore 111, the rotary shaft 161, the rotor 170, The hub 181 and the swash plate 180 may be included. As described above, the rotor 170 is coupled to the rotary shaft 161 to rotate integrally with the rotary shaft 161. The swash plate 180 is coupled to rotate integrally with the hub 181 on the outer circumferential surface of the hub 181, the hub 181 hinged to the rotor 170 is coupled to the variable inclination angle on the rotary shaft 161 It is possible to change the inclination angle of the swash plate 180 on the rotary shaft 161.

A hinge portion 175 may protrude from one side of the rear surface of the rotor 170, and a hinge slot 176 having a long hole shape may be formed in the hinge portion 175 for hinge coupling with the hinge accommodation portion 182. . In addition, a hinge accommodating part 182 accommodating the hinge part 175 may protrude from one side of the front surface of the hub 181. The hinge accommodating part 182 may have a through hole communicating with the hinge slot 176. The hinge part 175 and the hinge accommodating part may be formed by a hinge pin P which is sequentially coupled to the through hole and the hinge slot 176. 182 may be hinged to each other.

When the inclination angle of the swash plate 180 is changed, the hinge pin P coupled to the hinge receiving portion 182 of the hub 181 slides along the hinge slot 176. At this time, the return spring 162 interposed between the rotor 170 and the hub 181 is elastically pressed so that the swash plate 180 returns to its original position.

Meanwhile, in the compressor 100 according to the present embodiment, the swash plate 180 is in the axial direction of the rotating shaft 161 in a state before the compressor 100 is driven, that is, before the inclination angle of the swash plate 180 is controlled to vary. Rather than being perpendicular to, it is disposed in an inclined state.

More specifically, the swash plate 180 is disposed inclined with an initial inclination angle α greater than 0 ° with respect to a vertical direction in the axial direction of the rotating shaft 161 in the state before the compressor 100 is driven, At this time, the inclined direction may be a direction in which the inclination angle of the swash plate 180 is variable, that is, the direction in which the swash plate 180 is inclined when the compressor 100 is operated.

Since the swash plate 180 is disposed to have an initial inclination angle α, the inclination angle of the swash plate 180 may be easily increased when the compressor 100 is driven even if the swash plate 180 is not based on the conventional pressure spring 63 (see FIG. 1). That is, the compressor 100 according to the present embodiment is controlled by only the internal force change such as the elastic force of the return spring 162, the internal pressure of the crank chamber 121, the moment of inertia of the drive unit, etc. with the pressure spring removed. 180, the inclination angle can be increased. As such, the compressor 100 according to the present exemplary embodiment may easily control the swash plate angle at the initial stage of the compressor driving without the pressure spring.

Therefore, the compressor 100 according to the present embodiment does not require a pressure spring, which had to be included in the conventional variable displacement swash plate type compressor, thereby providing advantages such as a reduction in the number of parts, a simplified assembly process, and a weight reduction. have.

On the other hand, it is preferable that the initial inclination angle α of the swash plate 180 is 0.2 ° or more in order to obtain a rate of change of the inclination angle that is almost the same as when the pressure spring is mounted. At this time, the maximum inclination angle of the initial inclination angle α needs to be limited to the inclination angle so that the compressed refrigerant is not discharged in a state where the compressor 100 is not driven.

In order to arrange the swash plate 180 to be inclined to have an initial inclination angle α, the compressor 100 may be provided with various structures or means. As one example of the various structures, the swash plate 180 may have an initial inclination angle α by the coupling structure of the hinge slot 176 and the hinge pin P described above. The hinge pin P is slidably moved in the hinge slot 176, and the inclination angle of the swash plate 180 is changed according to the sliding movement. At this time, both ends of the hinge slot 176 limits the movement of the hinge pin (P), the initial inclination angle (α) of the swash plate 180 when the hinge pin (P) is supported on both ends of the hinge slot (176) Or when inclined at the maximum inclination angle. As a result, the initial inclination angle α of the swash plate 180 may be determined according to the position of one end (right lower end based on FIG. 3) of the hinge slot 176. Therefore, in the shape design such as the length of the hinge slot 176, the swash plate 180 is designed to have the initial inclination angle α described above, so that the swash plate 180 is inclined in a state before the compressor 100 is driven. You can do that. In addition to this, of course, the swash plate 180 may be arranged to have an initial inclination angle α by various other structures or means.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, It is obvious that the modification or the modification is possible by the person.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.

100: compressor 110: cylinder block
111: cylinder bore 112: center bore
120: front housing 121: crank chamber
122: pulley 130: rear housing
131: suction chamber 133: discharge chamber
140: piston 141: locking portion
142: shoe 150: valve assembly
161: rotating shaft 162: return spring
170: rotor 175: hinge portion
176: hinge slot 180: swash plate
181: hub 182: hinge receiving portion

Claims

A center block 112 formed at a center thereof, and a cylinder block 110 formed with a plurality of cylinder bores 111 spaced apart from each other in a circumferential direction on a radially outer side of the center bore 112;
A front housing 120 formed at the front of the cylinder block 110 and having a crank chamber 121 formed therein;
A rotating shaft 161 rotatably installed to penetrate the center of the front housing 120 and the cylinder block 110;
A rotor 170 coupled to the rotary shaft 161 to rotate integrally with the rotary shaft 161 and having a hinge portion 175 formed at one side thereof;
A hub 181 coupled to the rotation shaft 161 so as to face the rotor 170 and having a hinge receiving portion 182 corresponding to the hinge portion 175 and formed at one side thereof;
A swash plate 180 which is formed on an outer circumferential surface of the hub 181 and whose inclination angle is changed by a pressure change of the crank chamber 121; And
Receiving the rotation of the rotary shaft 161 through the swash plate 180, and includes a piston 140 for linear reciprocating motion in the cylinder bore 111,
In the state before the compressor 100 is driven, the swash plate 180 is disposed to be inclined such that the swash plate 180 has an initial inclination angle α that is 0.2 ° or more with respect to the vertical direction in the axial direction of the rotary shaft 161,
A long slot-shaped hinge slot 176 is formed in the hinge portion 175, and a through hole communicating with the hinge slot 176 is formed in the hinge receiving portion 182, so that the hinge pin P is formed with the through hole. The hinge unit 175 and the hinge receiving unit 182 are correspondingly coupled by penetratingly coupled to the hinge slot 176,
The swash plate (180) is a variable displacement swash plate type compressor that is arranged to have the initial inclination angle (α) by the hinge pin (P) is supported at the end of the hinge slot (176).

The method according to claim 1,
The swash plate (180) having the initial inclination angle (α) is variable capacity swash plate type compressor, characterized in that inclined toward a direction in which the inclination angle of the swash plate (180) is variable.

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