KR20140014809A - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable capacity swash plate type compressor having a relief valve on one side of a discharge chamber to partially guide compressed refrigerant inside the discharge chamber to flow into a crank chamber when discharge pressure excessively increases. The discharge chamber and the crank chamber are connected to each other through a relief flow passage inside the compressor. The relief valve is installed on one end of the relief flow passage around the discharge chamber.

Description

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

The present invention relates to a swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor having a relief valve installed at one side of the discharge chamber so that a part of the compression refrigerant in the discharge chamber flows to the crank chamber when the discharge pressure is excessively increased. will be.

In general, a compressor that serves to compress a refrigerant in a vehicle cooling system has been developed in various forms, and such a compressor has a configuration that compresses a refrigerant to perform compression while performing a reciprocating motion and a rotational motion to perform a reciprocating motion. There is a rotary.

Here, the reciprocating type includes a crank type in which the driving force of the drive source is transmitted to a plurality of pistons by using a crank, a swash plate type in which the swash plate is transmitted to a swash plate provided with a swash plate, a wobble plate type in which a wobble plate is used, Vane rotary using vanes, scroll type using revolving scroll and fixed scroll.

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.

In general, the compressor sucks the refrigerant into the suction chamber through the suction port, compresses the refrigerant by a compression mechanism such as swash plate, vane or scroll in the cylinder where the compression chamber is formed, and the compressed refrigerant is discharged into the discharge chamber. It is supplied to the outside through the discharge port.

At this time, when the pressure in the discharge chamber becomes excessively high beyond a predetermined value, the overpressure refrigerant in the discharge chamber is discharged to the outside of the compressor through a relief valve provided to communicate with the discharge chamber.

However, when the overpressure refrigerant in the discharge chamber is discharged to the outside of the compressor, the lubricant contained in the refrigerant is also discharged. Therefore, when the refrigerant and the lubricant are not supplemented properly, the cooling system may be deteriorated or the compressor may be deposited. There is a risk of failure. In addition, there is a risk of environmental pollution due to discharge of the refrigerant, in particular, it is difficult to actively cope with the CO ₂ emission regulation.

1 is a cross-sectional view of a conventional variable displacement swash plate compressor disclosed in Japanese Unexamined Patent Publication No. 2009-228493 (Patent Document 1), which has been proposed to solve the above problems.

In the case of the compressor 10 shown in FIG. 1, a cylinder block 12 in which a plurality of cylinder bores 12a are formed, a front housing 13 coupled to the front of the cylinder block 12, and a cylinder block 12 The housing 11 which constitutes the overall appearance of the compressor 10 is configured by the rear housing 14 which is coupled to the rear of the.

Here, the crank chamber 16 is formed inside the front housing 13, and the rear of the crank chamber 16 is closed by the cylinder block 12.

Then, the rotary shaft 17 is installed through the central portion of the crank chamber 16, wherein the rotary shaft 17 is rotated by the bearings 18 and 19 installed in the front housing 13 and the cylinder block 12, respectively. It is possibly supported and is connected to an external drive source by a power transmission mechanism (not shown) such as a clutch.

On one side of the crank chamber 16, the lag plate 21 is rotatably installed on the rotating shaft, and on the rear of the lag plate 21, the inclined plate 22 constituting the capacity variable mechanism slides in the axial direction of the rotating shaft 17. It is installed to move and tilt.

On the other hand, in the plurality of cylinder bores 12a formed in the cylinder block 12, the pistons 28 are accommodated so as to reciprocate, respectively, and one side of the inclined plate 22 is inserted into one side of these pistons 28 When the inclined plate 22 rotates together with the rotary shaft 17, the respective pistons 28 reciprocate to compress the refrigerant in the compression chamber 30 in the cylinder bore 12a.

At this time, the suction chamber 32 is formed on one side of the central portion of the rear housing 14, the suction chamber 32 is the compression chamber 30 in the cylinder bore 12a through the suction port 31a provided in the valve plate 31. It communicates with, and receives the refrigerant through the suction passage (37).

In addition, the discharge chamber 33 is formed spaced apart radially outward from the suction chamber 32 of the rear housing 14, the discharge chamber 33 and the suction chamber 32 is divided by a partition wall (14a) The discharge chamber 33 communicates with the compression chamber 30 in the cylinder bore 12a through the discharge port 31b provided in the valve plate 31, and cools the outside of the compressor 10 through the discharge passage 38. Supply compressed refrigerant to the system.

 Here, the connection tube 43 connecting the discharge chamber 33 and the crank chamber 16 to the outside of the cylinder block 12 and the rear housing 14 is coupled, the discharge chamber 33 of the connection tube 43 Relief valve 39 is provided at the side end portion.

Accordingly, if the pressure in the discharge chamber 33 rises excessively, the refrigerant in the discharge chamber 33 is guided to the crank chamber 16 through the relief valve 39, and the pressure of the crank chamber 16 changes. The inclination angle of the inclined plate 22 and the stroke of the piston 28 are changed to adjust the discharge capacity.

However, in the conventional compressor as described above, since the relief valve 39 and the connection tube 43 protrude out of the housing 11 of the compressor 10, the space required for installing the compressor 10 increases. In addition, there is a problem that the leakage of the refrigerant occurs in the sealing (sealing) portion of the relief valve (39).

Patent Document 1: Japanese Unexamined Patent Publication No. 2009-228493 (2009.10.08)

The present invention has been made to solve the problems described above, in one embodiment of the present invention, the discharge chamber and the crank chamber is connected through an internal flow path, a relief valve which is in communication with the flow path is provided on one side of the discharge chamber Further, an object of the present invention is to provide a variable displacement swash plate type compressor in which a high pressure refrigerant in a discharge chamber is guided to a crank chamber along an internal flow path when a discharge pressure is excessively increased due to a poor control of a cooling system.

According to a preferred embodiment of the present invention, a cylinder block in which a plurality of cylinder bores is formed; A front housing coupled to the front of the cylinder block and having a crank chamber formed therein; A rear housing coupled to the rear of the cylinder block and having a suction chamber and a discharge chamber formed therein; A rotating shaft rotatably installed through the center of the front housing and the cylinder block; A swash plate coupled to the rotary shaft through a central portion thereof so as to rotate integrally with the rotary shaft, and slantedly installed in the crank chamber; A plurality of pistons coupled to one side of the swash plate to linearly reciprocate by rotation of the swash plate; A flow path formed in the rear housing and the cylinder block to communicate the discharge chamber and the crank chamber; And a relief valve installed at one side of the discharge chamber, the relief valve opening and closing the flow path according to the pressure of the discharge chamber.

Here, the relief valve, the valve body is coupled to one end of the flow path and the inlet is formed on one side and a hollow valve chamber is formed therein, an elastic member installed in the valve chamber and the elastic member by the It may be configured to include an opening and closing member elastically supported in the inlet direction.

On the other hand, the relief valve is coupled to one end of the flow path and the inlet is formed through the one side, the stepped protruding on one side of the flow path to form a valve chamber between the support and one end to the step It may be configured to include an elastic member to be supported, and an opening and closing member elastically supported in the inlet direction by the elastic member.

At this time, it is preferable that an enlarged diameter portion having a wider width is formed at one side of the valve chamber, and a gap is formed between the inner peripheral surface of the enlarged diameter portion of the valve chamber and the outer peripheral surface of the opening / closing member.

The flow path may include a first flow path formed at one side of the rear housing to communicate with the rear end of the rotary shaft from one side of the discharge chamber, and formed at one side of the cylinder block to communicate with the crank chamber from the rear end of the rotary shaft. It may comprise a second flow path.

According to the variable displacement swash plate compressor according to the preferred embodiment of the present invention, when the pressure in the discharge chamber is abnormally increased, the refrigerant having the overpressure in the discharge chamber is led to the crank chamber without discharging the refrigerant to the outside of the compressor as conventionally. Therefore, it is possible to prevent problems such as violation of CO ₂ emission regulations and air pollution due to refrigerant leakage.

At this time, since the flow path communicating the discharge chamber and the crank chamber is formed inside the rear housing and the cylinder block, the connection pipe or the valve body is not exposed to the outside of the compressor housing as in the prior art, thus saving the installation space of the compressor.

In addition, in the related art, in the coupling of the valve body to the outer circumferential surface of the compressor housing, a sealing member such as an O-ring was required, and there was a problem of leakage of refrigerant through the sealing portion, but according to one embodiment of the present invention, such a sealing The member can be deleted, thereby reducing the cost and shortening the manufacturing time, and preventing external leakage of the refrigerant.

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.
Figure 3 is a sectional view of the installation of the relief valve according to an embodiment of the present invention.
4 is a cross-sectional view of an installation of a relief valve according to another embodiment of the present invention.

Hereinafter, preferred embodiments of a variable displacement swash plate type compressor according to an embodiment of the present invention will be described 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.

Example

2 is a cross-sectional view of a variable displacement swash plate compressor according to an embodiment of the present invention.

As shown in FIG. 2, the variable displacement swash plate compressor 100 (hereinafter, 'compressor') according to an embodiment of the present invention has a housing 200, a rotation shaft 300, a swash plate 400, A plurality of pistons 500, a relief flow path 600 inside the housing 200, and a relief valve 700 are included.

In this case, the housing 200 forms an appearance of the compressor 100 and includes a cylinder block 210, a front housing 220, and a rear housing 230 as shown in FIG. 2.

At this time, the cylinder block 210 is a tubular body disposed in the middle portion in the longitudinal direction of the housing 200, as shown in the center bore 211 that can accommodate the rotating shaft 300 therein, as well as a plurality of pistons ( A cylinder bore 212 is formed that can accommodate 500.

In addition, the front housing 220 and the rear housing 230 are respectively coupled to the cylinder to close the open end of the front and rear cylinder block 210, the front housing 220 is the rear end is opened toward the cylinder block 210. And it is made of a shape that can accommodate the inclination adjustment mechanism 222 while securing the crank chamber 221 that is the rotation space of the swash plate (400).

In addition, the rear housing 230 has a shape in which the front end is open toward the cylinder block 210, the suction chamber 231 for supplying the refrigerant to the cylinder bore 212 of the cylinder block 210 during the suction stroke, A discharge chamber 232 through which the refrigerant in the cylinder bore 212 is discharged during the compression stroke is formed.

At this time, the inlet 213a and the outlet 213b are formed in the valve plate 213 interposed between the cylinder block 210 and the rear housing 230 so as to communicate with the suction chamber 231 and the discharge chamber 232, respectively. .

On the other hand, the rotating shaft 300 is a means for transmitting the rotational driving force of the external drive source to the inside of the compressor 100, the front end portion is rotatable through one side of the housing 200, that is, the central portion of the front housing 220 The rear end is inserted into the center bore 211 formed at the center of the cylinder block 210 and rotatably installed.

At this time, the rotating pulley 310 is coupled to one end of the rotating shaft 300 exposed to the outside of the front housing 220, and the external driving force is transmitted to the rotating shaft 300 through the rotating pulley 310, the rotating shaft 300 will rotate.

The swash plate 400 is a means for converting the rotational driving force of the rotary shaft 300 into the reciprocating linear motion of the piston 500. The swash plate 400 is installed in an inclined state on the rotary shaft 300 by passing through a central portion thereof, and together with the rotary shaft 300. Rotate integrally

In this case, a plurality of shoes 410 are installed along the circumferential direction of the rim of the swash plate 400, and the plurality of pistons 500 are slidably supported by the shoe 410 so as to be relatively movable.

In addition, the swash plate 400 is installed so that the inclination angle with respect to the rotating shaft 300 is variable so that the refrigerant discharge capacity can be adjusted, for example, when the inclination of the swash plate 400 with respect to the rotating shaft 300 is 90 degrees, Since the reciprocating motion of the piston 500 disappears, the rotating shaft 300 is idle. On the contrary, when the swash plate 400 is inclined with respect to the rotation shaft 300, the piston 500 compresses the refrigerant while reciprocating in the cylinder bore 212.

The plurality of pistons 500 are means for compressing the refrigerant while reciprocating the inside of the cylinder bore 212 by the swash plate 400, as shown in FIG. 2, the shoe 410 at the edge of the swash plate 400. Relatively moveable through), by linear reciprocating motion along the inner circumferential surface of the cylinder bore 212 of the cylinder block 210 by the rotation of the swash plate 400, through the inlet 213a inside the cylinder bore 212 Compresses the refrigerant sucked into.

At this time, the refrigerant compressed by the cylinder bore 212 by the piston 500 is discharged to the discharge chamber 232 of the rear housing 230, and then supplied to the external cooling system through the discharge port (not shown), Conventionally, when the discharge pressure of the refrigerant is excessively increased, the discharge pressure is properly adjusted by discharging a part of the refrigerant to the outside of the compressor 100 through a relief valve coupled to one side of the outer circumferential surface of the rear housing 230.

However, discharging the refrigerant to the outside of the compressor 100 as described above has a hassle that needs to be replenished by the amount of the discharged refrigerant and the lubricant contained in the refrigerant, and when replenishment is not made in a timely manner, There is a problem that is one cause of performance degradation or failure, and it is particularly difficult to meet the CO ₂ emission regulations.

In addition, when the relief valve is installed to protrude to the outer circumferential surface of the rear housing 230, not only the installation space of the compressor 100 is increased, but also there is a risk of leakage of refrigerant in the sealing portion of the relief valve.

Accordingly, the variable displacement swash plate compressor 100 according to the embodiment of the present invention includes a relief flow path 600 communicating with one side of the discharge chamber 232 and one side of the crank chamber 221 in the compressor 100. And a relief valve 700 which opens and closes the relief flow path 600 according to the pressure of the discharge chamber 232 on the discharge chamber 232 side of the relief flow path 600.

Here, the relief flow path 600 is a first relief flow path 610 formed in the rear housing 230 so as to communicate with the rear end of the rotary shaft 300 from one side of the discharge chamber 232 from the rear end of the rotary shaft 300 A second relief flow path 620 is formed in the cylinder block 210 to communicate with one side of the crank chamber 221.

In this case, the first relief passage 610 and the second relief passage 620 may communicate with each other through the space portion at the rear end of the rotation shaft 300, and as another example, through the inside of the side wall forming the space portion at the rear end of the rotation shaft 300. It is also possible to connect them.

At this time, one side of the rear housing 230 may be provided with a pressure control valve 233 for adjusting the inclination angle of the swash plate 400, in this case the refrigerant in the discharge chamber 232 of the first relief passage 610 It may flow to the pressure control valve 233 through the pressure control passage 611 communicated to the pressure control valve 233 from one side.

3 is a cross-sectional view of an installation of a relief valve according to an embodiment of the present invention.

According to one embodiment of the present invention, the relief valve 700 is an inlet 715 is formed on one side and the valve body 710 is formed in the valve chamber 713 and the elasticity is installed in the valve chamber 713 The member 720 and the opening and closing member 730 is elastically supported in the direction of the inlet 715 by the elastic member 720.

Here, the valve body 710 is a tubular shape having a hollow, at the front end of the cylindrical body portion 711 and the body portion 711 in which the valve chamber 713 is formed so that the elastic member 720 is installed therein. It includes a locking portion 712 is formed that the width is extended and the inlet 715 is formed through the center.

At this time, as shown in Figure 3 is inserted so that the outer peripheral surface of the body portion 711 of the valve body 710 is in close contact with the inner circumferential surface of the relief flow path 600, the valve body 710 by fitting or screwing, etc. It can be fixed to one side of the relief flow path 600, the locking portion 712 is supported by the locking step 630 formed on one side of the relief flow path 600.

In the body portion 711 of the valve body 710, the valve chamber 713 is formed as a space in which the opening / closing member 730 can move along with the expansion and contraction of the elastic member 720, and at the center of the locking portion 712. An inlet 715 is formed in communication with the valve chamber 713.

On the opposite side of the inlet port 715, that is, at the rear end of the valve chamber 713, a step 714 protrudes from the inner circumferential surface along the circumferential direction, and one end of the elastic member 720 such as a coil spring is supported by the step 714. .

The other end of the elastic member 720 is supported on one side of the opening and closing member 730 to elastically support the opening and closing member 730 in the inlet 715 direction, as shown in FIG. 3 as an example of the opening and closing member 730. As described above, a ball plunger may be used, and the edge portion of the inlet 715 inside the locking portion 712 may be recessed to form a curved surface so that the ball plunger may be accurately supported by the inlet 715. Of course, the shape of the opening and closing member 730 is not limited to the above examples, it may be appropriately selected according to the need, such as conical or plate-like.

On the other hand, the enlarged diameter portion 716 is formed on the inner circumferential surface of the valve chamber 713 inside the inlet 715, and thus the inlet 715 is formed between the outer circumferential surface of the opening and closing member 730 and the inner circumferential surface of the enlarged diameter portion 716. When opening, a gap is formed through which the refrigerant can flow.

Therefore, when the inlet 715 is opened by the pressure of the discharge chamber 232, the refrigerant in the discharge chamber 232 flows into the valve chamber 713 along the gap between the inlet 715 and the gap, and then the relief flow path ( Along the 600 is to flow into the crank chamber (221).

At this time, opening and closing of the inlet 715 is performed according to the pressure of the discharge chamber 232. That is, when the pressure in the discharge chamber 232 is greater than the sum of the pressure in the relief passage 600 and the elastic force of the elastic member 720, the high pressure refrigerant in the discharge chamber 232 opens and closes through the inlet 715. ) To open the inlet 715.

4 is a cross-sectional view of an installation of a relief valve according to another embodiment of the present invention.

In another embodiment of the present invention, the valve body 710 in FIG. 3 described above is deleted and a valve chamber 821 is formed on one side of the relief flow path 600.

That is, the relief valve 800 according to another embodiment of the present invention includes a support 810 coupled to one end of the relief flow path 600 and having an inlet 811 penetrating through the center thereof, and a predetermined distance from the support 810. An elastic member 830 and an elastic member 830 installed in the relief channel 600 between the step 820 and the support 810, which are spaced apart from each other and protrude from one side of the relief channel 600. It includes an opening and closing member 840 is elastically supported in the inlet 811 direction.

Here, the support 810 is a ring-shaped member formed by penetrating the inlet 811 at the center thereof, and is fixed by being coupled to one end of the relief flow path 600 by fitting or screwing. In addition, the step 820 is formed at one side of the inner circumferential surface of the relief flow path 600 by being spaced apart from the support 810 by a predetermined distance, and the space between the support 810 and the step 820 forms a valve chamber 821.

One end of the elastic member 830 such as the coil spring is supported by the step 820, and the opening and closing member 840 such as the ball plunger is elastically supported by the inlet 811 by the elastic member 830.

At this time, when the ball plunger is applied as the opening and closing member 840, as shown in Figure 4, the inlet 811 edge portion of the inner surface of the support 810 so that the ball plunger can be accurately supported on the inlet 811 is curved It is desirable to be recessed to achieve.

In addition, when the inlet 811 is opened by the pressure of the discharge chamber 232, the relief flow passage adjacent to the support 810 so that the refrigerant in the discharge chamber 232 can smoothly flow into the valve chamber 821. The enlarged diameter portion 822 is formed at one side of the 600, so that a gap of a predetermined interval is formed between the outer circumferential surface of the opening and closing member 840 and the inner circumferential surface of the enlarged diameter portion 822.

100: variable displacement swash plate compressor
200: housing
210: cylinder block
220: front housing
221 crankcase
230: rear housing
232: discharge chamber
300: rotation axis
400: swash plate
500: piston
600: relief euro
700, 800: relief valve

Claims (5)

A cylinder block 210 in which a plurality of cylinder bores 212 are formed;
A front housing 220 coupled to the front of the cylinder block 210 and having a crank chamber 221 formed therein;
A rear housing (230) coupled to the rear of the cylinder block (210) and having a suction chamber (231) and a discharge chamber (232) formed therein;
A rotating shaft 300 rotatably installed through the center of the front housing 220 and the cylinder block 210;
A swash plate 400 which is coupled to the rotating shaft 300 through a central portion so as to be integrally rotated with the rotating shaft 300 and is inclined in the crank chamber 221;
One side of the rim of the swash plate 400 is coupled, a plurality of piston 500 for linear reciprocating motion by the rotation of the swash plate 400;
A relief flow path 600 formed in the rear housing 230 and the cylinder block 210 to communicate the discharge chamber 232 and the crank chamber 221; And
And a relief valve (700,800) installed at one side of the discharge chamber (232) to open and close the relief flow path (600) according to the pressure of the discharge chamber (232).
[3] The apparatus of claim 1, wherein the relief valve (700)
A valve body 710 is coupled to one end of the relief flow path 600 and the inlet 715 is formed on one side and a hollow valve chamber 713 is formed therein, and an elastic member installed in the valve chamber 713. Member 720 and the opening and closing member 730 is elastically supported in the inlet 715 direction by the elastic member 720, characterized in that it comprises a swash plate type compressor.
The method according to claim 1, The relief valve 800,
A support chamber 810 coupled to one end of the relief passage 600 and having an inlet 811 penetrated thereon, and a protrusion formed at one side of the relief passage 600 to be provided with a valve chamber between the support passage 810. The step 820 forming the 821, the elastic member 830 having one end supported by the step 820, and the opening and closing member 840 elastically supported in the inlet 811 direction by the elastic member 830 Variable displacement swash plate compressor comprising a).
The method according to claim 2 or 3,
Expanded diameter parts 716 and 822 are formed on one side of the valve chambers 713 and 821 so that a gap is formed between an inner circumferential surface of the enlarged parts 716 and 822 of the valve chambers 713 and 821 and an outer circumferential surface of the opening and closing members 730 and 840. A variable displacement swash plate compressor, characterized in that.
The method according to claim 1, The relief flow path 600,
A first relief flow passage 610 formed at one side of the rear housing 230 so as to communicate with a rear end of the rotary shaft 300 from one side of the discharge chamber 232, and the crank chamber from a rear end of the rotary shaft 300. And a second relief flow passage 620 formed at one side of the cylinder block 210 so as to communicate with the 221.

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