KR101451472B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate type compressor and more particularly to a variable displacement swash plate type compressor in which a differential pressure valve for controlling the flow of refrigerant from a discharge chamber (132) to a discharge port (134) by a differential pressure between a pressure in a discharge chamber (132) (600) is provided on a connection passage (L1) for communicating the discharge chamber (132) and the discharge port (134). Such a variable displacement swash plate type compressor can prevent the refrigerant discharge pressure from being lost and the initial operation delay of the swash plate 300 can be minimized.

Description

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

The present invention relates to a variable displacement swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor which compresses a refrigerant sucked from an external refrigerant line by a plurality of reciprocating pistons in accordance with rotation of a swash plate, To a variable displacement swash plate compressor capable of preventing loss of discharge pressure of refrigerant discharged to an external refrigerant line and effectively removing liquid refrigerant in the crank chamber.

Generally, compressors that serve to compress refrigerant in automotive cooling systems have been developed in various forms. Such a compressor includes a reciprocating type in which compression is performed while a refrigerant is compressed and a rotary type in which compression is performed while rotating. In the reciprocating type, there are 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 by a swash plate installed shaft, a wobble plate type in which a wobble plate is used, There are vane rotary type, scroll type using revolving scroll and fixed scroll.

Among the above various types of compressors, the swash plate type compressor is driven according to on / off of the air conditioner switch. When the compressor is driven, the temperature of the evaporator is lowered, and when the compressor is stopped, the temperature of the evaporator is raised.

On the other hand, as the swash plate type compressor, there are fixed capacity type and variable capacity type. These compressors are driven by receiving power from the rotational force of the engine of the vehicle. In the fixed capacity type, an electromagnetic clutch is provided to control the operation of the swash plate type compressor. However, in the case of the fixed capacity type having the electromagnetic clutch, there is a problem that the RPM of the vehicle flows when the compressor is driven or stopped, thereby hindering stable vehicle operation.

Therefore, in recent years, a variable displacement type, which is not provided with a clutch, is always driven with the driving of the engine of the vehicle, and can vary the discharge capacity by changing the inclination angle of the swash plate, is widely used. In such a variable displacement swash plate type compressor, a pressure control valve for adjusting the inclination angle of the swash plate is generally used for adjusting the refrigerant discharge amount.

1 is a view showing the overall structure of a conventional variable displacement swash plate type compressor. The structure of the conventional variable displacement swash plate type compressor will be described with reference to FIG.

The front head 120 and the rear head 130 are coupled to the front and rear sides of the cylinder block 110 in which the plurality of cylinder bores 111 are formed to form the housing 100. In the center portion of the cylinder block 110, A center bore 112 is formed.

A crank chamber 121 is defined inside the front head 120. A suction chamber 131, a discharge chamber 132, a suction port 133 and a discharge port (not shown) .

The front end of the rotary shaft 200 is disposed to protrude from the front head 120 and the rear end of the rotary shaft 200 is formed at a central portion of the cylinder block 110. The rotary shaft 200 is rotatably inserted through the crank chamber 121, The center bore 112 is inserted into the center bore 112 and a rear portion of the center bore 112 receives the oil separator (not shown) and constitutes a receiving chamber 113 for receiving the refrigerant and the oil. A refrigerant passage communicating the crank chamber 121 and the containing chamber 113 is formed at the center of the rotating shaft 200 and a separate refrigerant passage communicating the crank chamber 121 and the containing chamber 113 A refrigerant passage may be formed. Therefore, the pressure of the storage chamber 113 becomes substantially equal to the pressure of the crank chamber 121.

The swash plate 300 is installed on the rotary shaft 200 so as to rotate integrally with the rotary shaft 200 and to adjust the angle of the rotary shaft 200 so that the refrigerant discharge amount can be controlled.

A plurality of pistons 400 are slidably supported at an edge portion of the swash plate 300 to be relatively movable via a shoe 310 and are reciprocated by a linear reciprocating motion along an inner peripheral surface of a cylinder bore 111 of the plurality of pistons 400. [ By exercising, the refrigerant is compressed.

A valve unit 500 for sucking and discharging refrigerant is provided between the cylinder block 110 and the rear head 130. A plurality of suction valves and discharge valves are formed in the valve unit 500, And an orifice communicating with the containing chamber 113 and the suction chamber 131 is formed.

However, in the above-described conventional variable displacement swash plate type compressor, the refrigerant compressed by the plurality of pistons 400 is discharged to the discharge chamber 132 and then discharged to the external refrigerant line again through the discharge port (not shown) (Not shown) installed in the discharge port. However, since the discharge pressure of the discharge check valve has to be set to a high value, the discharge pressure of the refrigerant discharged to the external refrigerant line is lost , The performance of the compressor is reduced due to the loss of the discharge pressure, and the energy consumption of the external power for driving the compressor is increased.

In the case of the conventional variable displacement swash plate type compressor, when the compressor is left for a long time without being driven, the refrigerant is liquefied and accumulated in the crank chamber 121. Such liquid refrigerant evaporates at the initial stage of the compressor, And thus the formation of the inclination angle of the swash plate 300 is delayed.

SUMMARY OF THE INVENTION The present invention has been proposed in order to solve the above-mentioned problems, and it is an object of the present invention to provide a differential pressure control valve for controlling a refrigerant flow from a discharge chamber to a discharge port by a pressure difference between a discharge chamber pressure and a crank chamber pressure, Provided is a variable displacement swash plate compressor capable of preventing the loss of the refrigerant discharge pressure and minimizing the initial operation delay of the swash plate by providing a valve and allowing liquid refrigerant in the crank chamber to be discharged through the differential pressure valve .

According to an aspect of the present invention, there is provided a variable displacement swash plate compressor including a cylinder block having a plurality of cylinder bores formed therein, a front head disposed in front of the cylinder block and formed with a crank chamber, A rotary shaft which is rotatably mounted through one side of the housing; and a rotary shaft provided on the rotary shaft and integrally rotated with the rotary shaft, wherein the refrigerant discharge amount A plurality of pistons connected to the swash plate and linearly reciprocating by rotation of the swash plate, and a plurality of pistons installed between the cylinder block and the rear head, A valve unit for sucking and discharging the fluid, To be installed on, it communicates the crank chamber, and by the differential pressure between the discharge chamber pressure and the crank chamber pressure, characterized in that it comprises a differential pressure valve to regulate the flow of refrigerant to said discharge chamber from the discharge port.

Wherein the differential pressure valve includes a case having a first inlet communicating with the discharge chamber, an outlet communicating with the discharge port, and a second inlet communicating with the crank chamber, and a case supported by a spring on the inside of the case, And an opening / closing core that adjusts the flow of the refrigerant leading from the inlet to the outlet by the differential pressure between the crank chamber pressure and the discharge chamber pressure.

A liquid refrigerant outlet communicating with the suction chamber is formed at one side of the case, and the liquid refrigerant outlet is preferably opened when the first inlet and the outlet are closed by the opening / closing core.

The case is further provided with a third inlet communicating with the discharge chamber, and the opening / closing core is provided with an opening that allows the flow path from the third inlet to the outlet to be opened even when the flow path from the first inlet to the outlet is closed. It is preferable that a communication hole is further formed.

And a liquid refrigerant outlet communicating with the suction chamber is formed at one side of the case, and the liquid refrigerant outlet is opened when the first inlet, the third inlet, and the outlet are closed by the opening / closing core.

And the outlet side check valve is connected to the outlet side of the differential pressure valve.

And an inlet-side check valve is connected to the inlet side of the differential pressure valve.

In accordance with another aspect of the present invention, there is provided a variable displacement swash plate type compressor, including: a cylinder block having a plurality of cylinder bores formed therein; a front head disposed in front of the cylinder block and having a crank chamber; A housing having a suction chamber, a discharge chamber, a suction port, and a rear head formed with a discharge port to form an outer body; a rotary shaft mounted rotatably through one side of the housing; A plurality of pistons connected to the swash plate and linearly reciprocating by rotation of the swash plate, and a plurality of pistons installed between the cylinder block and the rear head, A valve unit for sucking and discharging the refrigerant, and a valve unit for connecting the discharge chamber and the discharge port And a differential pressure valve that is provided on the connection passage and communicates with the suction chamber to interrupt the flow of the refrigerant from the discharge chamber to the discharge port by a differential pressure between the discharge chamber pressure and the suction chamber pressure.

Wherein the differential pressure valve includes a case having a first inlet communicating with the discharge chamber, an outlet communicating with the discharge port, and a second inlet communicating with the suction chamber, and a case supported by a spring on the inside of the case, And an opening / closing core for controlling the flow of the refrigerant leading from the inlet to the outlet by the differential pressure between the crankcase pressure and the suction chamber pressure.

And the outlet side check valve is connected to the outlet side of the differential pressure valve.

And an inlet-side check valve is connected to the inlet side of the differential pressure valve.

According to the above-described variable displacement swash plate type compressor, the pressure difference between the discharge chamber pressure and the crank chamber pressure or the differential pressure between the discharge chamber pressure and the suction chamber pressure controls the refrigerant flow from the discharge chamber to the discharge port The valve is installed and the liquid refrigerant in the crank chamber is discharged through the differential pressure valve, whereby the loss of the refrigerant discharge pressure can be prevented, and the initial operation delay of the swash plate can be minimized.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing the overall structure of a conventional variable displacement swash plate type compressor. Fig.
FIG. 2 is a view showing a first embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which the applied differential pressure valve is opened. FIG.
FIG. 3 is a view showing a first embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which the applied differential pressure valve is closed; FIG.
4 is a view showing a first embodiment of a refrigerant discharge structure applied to a variable displacement swash plate type compressor according to an embodiment of the present invention, in which a check valve is connected to an outlet side of an applied differential pressure valve.
5 is a view showing a first embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which a check valve is connected to the inlet side of an applied differential pressure valve.
FIG. 6 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which the applied differential pressure valve is opened; FIG.
FIG. 7 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable displacement swash plate type compressor according to an embodiment of the present invention, in which the applied differential pressure valve is closed; FIG.
8 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable displacement swash plate type compressor according to an embodiment of the present invention, in which a check valve is connected to an outlet side of an applied differential pressure valve.
9 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which a check valve is connected to an inlet side of an applied differential pressure valve.
10 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable displacement swash plate type compressor according to an embodiment of the present invention in which a check valve is connected to the inlet side of an applied differential pressure valve in a different manner.
FIG. 12 is a view showing a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to another embodiment of the present invention, in which the applied differential pressure valve is opened; FIG.
FIG. 13 is a view showing a refrigerant discharge structure applied to a variable displacement swash plate type compressor according to another embodiment of the present invention, in which the applied differential pressure valve is closed; FIG.
FIG. 14 is a view showing a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to another embodiment of the present invention, in which a check valve is connected to an outlet side of an applied differential pressure valve; FIG.
15 is a view showing a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to another embodiment of the present invention, in which a check valve is connected to an inlet side of an applied differential pressure valve.

BRIEF DESCRIPTION OF THE DRAWINGS The objectives, specific advantages and novel features of the present invention will become more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which: FIG. In the following description of the present invention, detailed description of known related arts will be omitted when it is determined that the gist of the present invention may be unnecessarily obscured by the present invention. Also, the thickness of the lines and the size of the components shown in the drawings may be exaggerated for clarity and convenience of explanation. In addition, terms used are terms defined in consideration of functions in the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be based on the entire contents of the present specification.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

FIG. 2 is a view showing a first embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to the present invention, in which the applied differential pressure valve is opened, FIG. 3 is a cross- FIG. 4 is a view showing a first embodiment of a refrigerant discharging structure applied to a swash plate type compressor, in which the applied differential pressure valve is closed, and FIG. 4 is a sectional view of a refrigerant discharging structure applied to a variable capacity swash plate type compressor according to the present invention. 1 is a view showing an embodiment in which a check valve is connected to an outlet side of an applied differential pressure valve, and FIG. 5 is a view showing a first embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to the present invention As shown in the drawing, a check valve is connected to an inlet side of an applied differential pressure valve.

First, a variable displacement swash plate type compressor according to the present invention will be described in general, and a first embodiment of a refrigerant discharge structure applied to a variable displacement swash plate type compressor according to an embodiment of the present invention will be described.

Referring to FIGS. 2 to 5, a variable capacity swash plate type compressor according to an embodiment of the present invention includes a housing 100, a rotary shaft 200, a swash plate 300 , A plurality of pistons (400), a valve unit (500), and a differential pressure valve (600).

The housing 100 includes a cylinder block 110, a front head 120, and a rear head 130 as shown in FIG. 1, which is an outer body of the variable capacity swash plate type compressor. Here, the cylinder block 110 is a tubular body disposed at an intermediate portion in the longitudinal direction of the housing 100. As shown in the figure, the cylinder block 110 includes a center bore 112 capable of receiving the rotation shaft 200 therein, A cylinder bore 111 capable of receiving the piston 400 is formed.

The front head 120 and the rear head 130 are cylinders for closing the open and close ends of the upper cylinder block 110. The front head 120 is opened toward the cylinder block 110, And the crank chamber 121, which is a rotating space of the crank chamber 121, of the crank chamber.

The rear head 130 has a front end opened toward the cylinder block 110 and includes a suction chamber 131 for supplying the refrigerant to the cylinder bore 111 of the cylinder block 110 during the suction stroke, A discharge chamber 132 through which the refrigerant in the cylinder bore 111 is discharged is formed. The rear head 130 is formed with a suction port 133 and a discharge port 134 that are connected to the suction chamber 131 and the discharge chamber 132, respectively.

The rotating shaft 200 is a means for transmitting the rotational driving force of the external driving source to the inside of the compressor. The front end of the rotating shaft 200 is rotatably mounted on one side of the housing 100, that is, the center portion of the front head 120, Is inserted into the center bore 112 formed at the center of the cylinder block 110, and is rotatably mounted. A rotary pulley 140 is coupled to one end of a rotary shaft 200 exposed to the outside of the front head 120 and an external rotary driving force is transmitted to the rotary shaft 200 through the rotary pulley 140 The rotating shaft 200 is rotated.

The swash plate 300 is a means for converting the rotational driving force of the rotating shaft 200 into a reciprocating linear motion of the piston 400 and is mounted on the rotating shaft 200 in an inclined state to rotate together with the rotating shaft 200 . At this time, a plurality of shoes 310 are mounted in the circumferential direction of the swash plate 300, and the plurality of pistons 400 are slidably supported by the shoe 310 through the shoe 310.

The swash plate 300 is installed such that the inclination angle of the swash plate 300 with respect to the rotary shaft 200 is variable so that the refrigerant discharge capacity can be adjusted. When the inclination of the swash plate 300 with respect to the rotary shaft 200 is 90 °, 400 are disappeared, the rotating shaft 200 is idly rotated. Conversely, when the swash plate 300 is inclined with respect to the rotary shaft 200 as shown in FIG. 1, the piston 400 reciprocates in the cylinder bore 111 to compress the refrigerant.

The plurality of pistons 400 are means for compressing the refrigerant while reciprocating in the cylinder bore 111 by means of the swash plate 300. As shown in Figure 1, 310 and reciprocates linearly along the inner peripheral surface of the cylinder bore 111 of the cylinder block 110 by the rotation of the swash plate 300 so that the suction port 133 of the rear head 130 So that the refrigerant sucked into the cylinder bore 111 is discharged to the outside refrigerant line through the discharge port 134 of the rear head 130.

A certain portion of the rear side of the center bore 112 of the cylinder block 110 accommodates the oil separator and constitutes a storage chamber 113 for storing refrigerant and oil.

A refrigerant passage communicating the crank chamber 121 and the containing chamber 113 is formed at the center of the rotating shaft 200 and a separate refrigerant passage communicating the crank chamber 121 and the containing chamber 113 A refrigerant passage may be formed. Therefore, the pressure of the storage chamber 113 becomes substantially equal to the pressure of the crank chamber 121.

The valve unit 500 controls the suction and discharge of the refrigerant so that the refrigerant can flow between the front head 120 or the cylinder block 110 and the rear head 130. The valve unit 500 includes a cylinder block 110, The valve unit 500 is provided with a plurality of suction valves and discharge valves.

The differential pressure valve 600 is for controlling the refrigerant that is compressed by the piston 400 and discharged to the discharge chamber 132 and then flows to the discharge port 134 for discharging to the external refrigerant line again. And is connected to the crank chamber 121 through a connection passage L1 that communicates the discharge chamber 132 and the discharge port 134 at a position adjacent to the valve unit 500 as shown in FIG. The flow of the refrigerant from the discharge chamber 132 to the discharge port 134 is interrupted by the differential pressure between the pressure in the discharge chamber 132 and the pressure in the crank chamber 121.

The differential pressure valve 600 mainly comprises a case 610, an opening / closing core 620, and a spring S.

The case 610 is a substantially tubular body with one end closed and a first inlet 611 communicating with the discharge chamber 132 is formed on one side of the case 610, And a second inlet 613 communicating with the crank chamber 121 is formed on the other side adjacent to the valve unit 500. The second inlet 613 communicates with the discharge port 134 on the other side. The second inlet 613 is connected to a passage L2 through which the refrigerant is introduced from the containing chamber 113. [

Here, in the illustrated embodiment, the second inlet 613 communicates with the crank chamber 121 and the storage chamber 113 communicated with the crank chamber 121 to indirectly communicate with the crank chamber 121. However, the second inlet 613 may be configured to directly communicate with the crank chamber 121. The pressure of the crank chamber 121 and the pressure of the containing chamber 113 are substantially equal to each other so that the second inlet 613 flows into the second inlet 613 even if the second inlet 613 is indirectly communicated with the crank chamber 121 The pressure of the refrigerant is regarded as the pressure of the crank chamber 121.

The opening / closing core 620 is a means for interrupting the flow of the refrigerant passing through the inside of the case 610, and is formed in a cylindrical shape with one side opened, and a spring S is inserted into the inside of the case 610 And the pressure of the discharge chamber 132 flowing through the first inlet 611 so as to intermit the flow of the refrigerant leading from the first inlet 611 to the outlet 612 of the case 610, The flow path from the first inlet 611 to the outlet 612 is opened or closed according to the differential pressure of the pressure of the crank chamber 121 flowing through the second inlet 613 in the axial direction.

On the other hand, a liquid refrigerant outlet 614 communicating with the suction chamber 131 is further formed at the other side of the case 610, and a passage (not shown) communicating with the suction chamber 131 is formed in the liquid refrigerant outlet 614, (L3) are connected.

The liquid refrigerant outlet 614 is opened when the flow path from the first inlet 611 to the outlet 612 is closed by the open / close core 620, through which the liquid refrigerant in the crank chamber 121 is sucked So that it can be discharged to the chamber 131.

3, an outlet side check valve 700 may be further connected to the outlet side of the differential pressure valve 600, and an inlet side check valve 700 may be connected to the inlet side of the differential pressure valve 600 as shown in FIG. (800) can be further connected. At this time, the outlet-side check valve 700 or the inlet-side check valve 800 may be replaced with another differential pressure valve.

When the outlet check valve 700 is further connected to the outlet of the differential pressure valve 600 or the inlet check valve 800 is further connected to the inlet of the differential pressure valve 600, The flow path from the discharge chamber 132 to the discharge port 134 can be immediately closed. Here, it is preferable that the opening setting value of the outlet check valve 700 or the inlet check valve 800 is set to a value as small as possible so that the loss of the discharge pressure can be minimized. Further, the discharge muffler can be positioned anywhere on the flow path from the discharge chamber 132 to the discharge port 134. [

Meanwhile, a refrigerant interrupting process according to the first embodiment of the refrigerant discharging structure applied to the variable capacity swash plate type compressor according to the embodiment of the present invention will be described as follows.

When the pressure of the discharge chamber 132 is greater than the sum of the pressure of the crank chamber 121 and the elastic repulsive force of the spring S as shown in FIG. 2, the opening / closing core 620 moves from the first inlet 611 The flow path leading to the outlet 612 is opened so that the refrigerant can flow from the discharge chamber 132 to the discharge port 134.

3, when the pressure in the discharge chamber 132 is smaller than the sum of the pressure in the crank chamber 121 and the elastic repulsive force of the spring S, the opening / closing core 620 moves the first inlet 611 ) To the outlet 612 is closed, so that the refrigerant can not flow from the discharge chamber 132 to the discharge port 134.

However, when the flow path from the first inlet 611 to the outlet 612 is closed by the opening / closing core 620, the liquid refrigerant outlet 614 is opened so that the liquid refrigerant in the crank chamber 121 flows into the containing chamber 113) to the suction chamber (131).

When the refrigerant flow from the discharge chamber 132 to the discharge port 134 is interrupted through the first embodiment of the refrigerant discharge structure applied to the variable capacity swash plate type compressor according to the embodiment of the present invention, Since the flow of the refrigerant from the discharge chamber 132 to the discharge port 134 is interrupted by the differential pressure between the pressure of the refrigerant and the pressure of the crank chamber 121, The problem that the performance of the compressor is reduced and the problem that the energy consumption of the external power for driving the compressor is increased can be solved.

Further, the liquid refrigerant in the crank chamber 121 can be discharged to the suction chamber 131 through the differential pressure valve 600, so that the initial operation delay of the swash plate can be minimized.

Hereinafter, a second embodiment of the refrigerant discharge structure applied to the variable displacement swash plate type compressor according to the embodiment of the present invention will be described.

FIG. 6 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which the applied differential pressure valve is opened, and FIG. FIG. 8 is a view showing a second embodiment of the refrigerant discharge structure applied to the variable capacity swash plate type compressor according to the embodiment, in which the applied differential pressure valve is closed, and FIG. 8 is a cross- FIG. 9 is a view showing a second embodiment of a refrigerant discharge structure applied to a capacitive swash plate type compressor, in which a check valve is connected to an outlet side of an applied differential pressure valve, and FIG. 9 is a cross- A second embodiment of a refrigerant discharge structure applied to a swash plate type compressor, in which a check valve is connected to an inlet side of an applied differential pressure valve, 10 is a view showing a second embodiment of a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to an embodiment of the present invention, in which a check valve is connected to an inlet side of an applied differential pressure valve in a different manner .

6 to 10, in the second embodiment of the refrigerant discharge structure applied to the variable displacement swash plate type compressor according to the embodiment of the present invention, the structure is substantially similar to the differential pressure valve 600 described above, And the same reference numerals are used for the same components.

6 and 7, the differential pressure valve 600 applied to the second embodiment includes a connection passage L1 that is positioned to pass through the valve unit 500 and communicates with the discharge chamber 132 and the discharge port 134, And the refrigerant flows from the discharge chamber 132 to the discharge port 134 by a differential pressure between the pressure in the discharge chamber 132 and the pressure in the crank chamber 121 I will crack down.

The differential pressure valve 600 mainly comprises a case 610, an opening / closing core 620, and a spring S.

The case 610 is a substantially tubular body with one end closed and a first inlet 611 communicating with the discharge chamber 132 is formed on one side of the case 610, And an outlet 612 communicating with the discharge port 134 is formed on the other side of the valve unit 500. The other end of the outlet 612 communicating with the crank chamber 121 communicates with the crank chamber 121, 2 inlet 613 are formed. In addition, the second inlet 613 is connected to a passage L2 through which the refrigerant is introduced from the containing chamber 113.

The opening / closing core 620 is a means for interrupting the flow of the refrigerant passing through the inside of the case 610 and is formed in a substantially cylindrical shape. The inside of the case 610 is covered with a spring S The pressure of the discharge chamber 132 flowing through the first inlet 611 and the pressure of the refrigerant flowing from the first inlet 611 to the outlet 612 of the case 610, 2 through the inlet 613 and opens or closes the flow path leading from the first inlet 611 to the outlet 612. [

A third inlet 615 communicating with the discharge chamber 132 is formed at a position spaced apart from the first inlet 611 by a predetermined distance. The discharge chamber 132 is connected to the third inlet 615, And the third inlet 615 is connected to a separate passage L4 through which the refrigerant is introduced from the first inlet 611 to the outlet 612. When the flow path from the first inlet 611 to the outlet 612 is closed, An intermediate communication hole 621 is formed so that the flow path leading to the outlet 612 can be opened.

6 to 10, the indirect communication between the second inlet 613 and the crank chamber 121 is the same as that of the first embodiment described above.

On the other hand, a liquid refrigerant outlet 614 communicating with the suction chamber 131 is further formed at the other side of the case 610, and a passage (not shown) communicating with the suction chamber 131 is formed in the liquid refrigerant outlet 614, (L3) are connected.

The liquid refrigerant outlet 614 is opened when the flow path from the third inlet 615 to the outlet 612 is closed by the open / close core 620, whereby the liquid refrigerant in the crank chamber 121 is sucked So that it can be discharged to the chamber 131.

8, the outlet side check valve 700 may be further connected to the outlet side of the differential pressure valve 600, and the outlet side check valve 700 may be connected to the inlet side of the differential pressure valve 600, Side check valve 800 may be further connected to only the first inlet 611 and the third inlet 615 at the inlet side of the differential pressure valve 600 as shown in Figure 10, An inlet-side check valve 800 may be further connected. At this time, the outlet-side check valve 700 or the inlet-side check valve 800 may be replaced with another differential pressure valve.

When the outlet check valve 700 is further connected to the outlet of the differential pressure valve 600 or the inlet check valve 800 is further connected to the inlet of the differential pressure valve 600, The flow path from the discharge chamber 132 to the discharge port 134 can be immediately closed. Here, it is preferable that the opening setting value of the outlet check valve 700 or the inlet check valve 800 is set to a value as small as possible so that the loss of the discharge pressure can be minimized. Further, the discharge muffler can be positioned anywhere on the flow path from the discharge chamber 132 to the discharge port 134. [

Meanwhile, a refrigerant interception process through the second embodiment of the refrigerant discharge structure applied to the variable capacity swash plate type compressor according to the embodiment of the present invention will be described as follows.

When the pressure in the discharge chamber 132 is greater than the sum of the pressure in the crank chamber 121 and the elastic repulsive force of the spring S as shown in FIG. 6, the opening / closing core 620 moves the third inlet 615, Even if the flow path from the first inlet 611 to the outlet 612 is opened before the flow path from the first inlet 611 to the outlet 612 and the pressure in the discharge chamber 132 is lower than that in the first embodiment, It is possible to flow from the chamber 132 to the discharge port 134 so that the loss of the discharge pressure of the refrigerant can be further prevented.

7, when the pressure of the discharge chamber 132 is smaller than the sum of the pressure of the crank chamber 121 and the elastic repulsive force of the spring S, the opening / closing core 620 moves the first inlet 611 The flow path from the third inlet 615 to the outlet 612 and the flow path from the third inlet 615 to the outlet 612 are closed so that the refrigerant can not flow from the discharge chamber 132 to the discharge port 134.

However, when the flow path from the first inlet 611 to the outlet 612 and the flow path from the third inlet 615 to the outlet 612 are closed by the opening / closing core 620, the liquid refrigerant outlets 614 So that the liquid refrigerant in the crank chamber 121 can be discharged to the suction chamber 131 through the housing chamber 113.

When the refrigerant flow from the discharge chamber 132 to the discharge port 134 is interrupted through the second embodiment of the refrigerant discharge structure applied to the variable capacity swash plate type compressor according to the embodiment of the present invention, Since the flow of the refrigerant from the discharge chamber 132 to the discharge port 134 is interrupted by the differential pressure between the pressure of the refrigerant and the pressure of the crank chamber 121, The problem that the performance of the compressor is reduced and the problem that the energy consumption of the external power for driving the compressor is increased can be solved.

Further, the liquid refrigerant in the crank chamber 121 can be discharged to the suction chamber 131 through the differential pressure valve 600, so that the initial operation delay of the swash plate can be minimized.

Hereinafter, a refrigerant discharge structure applied to the variable displacement swash plate type compressor according to another embodiment of the present invention will be described, and a description of parts overlapping one embodiment of the present invention described above will be omitted.

FIG. 12 is a view showing a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to another embodiment of the present invention, in which the applied differential pressure valve is opened, and FIG. 13 is a cross- FIG. 14 is a view showing a refrigerant discharge structure applied to the variable capacity swash plate type compressor, and FIG. 14 is a sectional view showing a refrigerant discharge structure applied to the variable capacity swash plate type compressor according to another embodiment of the present invention. FIG. 15 is a view illustrating a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to another embodiment of the present invention, and FIG. 15 is a view illustrating a refrigerant discharge structure applied to a variable capacity swash plate type compressor according to another embodiment of the present invention. And a check valve is connected to the inlet side of the differential pressure valve.

12 to 14, a differential pressure valve 600 'applied to a refrigerant discharge structure applied to a variable capacity swash plate compressor according to another embodiment of the present invention includes a differential valve 600' 132) and the discharge port (134), and communicates with the suction chamber (131), and the pressure difference between the pressure of the discharge chamber (132) and the pressure of the suction chamber (131) The flow of the refrigerant from the discharge chamber 132 to the discharge port 134 is interrupted.

The differential pressure valve 600 'includes a case 610', an opening / closing core 620 ', and a spring S.

The case 610 'is a cylindrical tubular body with one end closed and a first inlet 611' communicating with the discharge chamber 132 at one side. And a second inlet 613 'communicating with the suction chamber 131 is formed at another side adjacent to the valve unit 500. The second inlet 613' Is formed. A passage L5 through which the refrigerant is introduced from the suction chamber 131 is connected to the second inlet 613 '.

The opening / closing core 620 'is a means for interrupting the flow of the refrigerant passing through the inside of the case 610' and is formed in a cylindrical shape with one side opened. A spring S And is connected to the first inlet 611 'of the case 610' through the first inlet 611 'so as to intermit the flow of the refrigerant from the first inlet 611' to the outlet 612 ' (612 ') to the outlet (612') while reciprocating in the axial direction in accordance with the pressure of the first inlet (132) and the pressure difference between the pressure of the suction chamber (131) flowing through the second inlet (613 ' The following channels are opened or closed.

13, an outlet side check valve 700 'may be further connected to the outlet side of the differential pressure valve 600', and an inlet side port of the differential pressure valve 600 'may be connected to the inlet side of the differential pressure valve 600' Side check valve 800 'can be further connected. At this time, the outlet check valve 700 'or the inlet check valve 800' may be replaced with another differential pressure valve.

When the outlet check valve 700 'is further connected to the outlet side of the differential pressure valve 600' or the inlet check valve 800 'is further connected to the inlet side of the differential pressure valve 600' The flow path from the discharge chamber 132 to the discharge port 134 can be immediately closed. Here, the opening setting value of the outlet check valve 700 'or the inlet check valve 800' is preferably set to a value as small as possible so as to minimize the loss of the discharge pressure. Further, the discharge muffler can be positioned anywhere on the flow path from the discharge chamber 132 to the discharge port 134. [

Meanwhile, a refrigerant interception process through the refrigerant discharge structure applied to the variable capacity swash plate type compressor according to another embodiment of the present invention will be described.

11, when the pressure in the discharge chamber 132 is greater than the sum of the pressure in the suction chamber 121 and the elastic repulsive force of the spring S, the opening / closing core 620 ' To the outlet 612 'is opened so that the refrigerant can flow from the discharge chamber 132 to the discharge port 134. [

12, when the pressure in the discharge chamber 132 is smaller than the sum of the pressure in the suction chamber 121 and the elastic repulsive force of the spring S, the opening / closing core 620 ' 611 'to the outlet 612' is closed so that the refrigerant can not flow from the discharge chamber 132 to the discharge port 134.

When the refrigerant flow from the discharge chamber 132 to the discharge port 134 is interrupted through the refrigerant discharge structure applied to the variable capacity swash plate type compressor according to another embodiment of the present invention, Since the flow of the refrigerant from the discharge chamber 132 to the discharge port 134 is interrupted by the differential pressure between the pressure in the discharge chamber 121 and the pressure in the discharge chamber 121, loss of the discharge pressure of the refrigerant, It is possible to solve the problem that the performance is decreased and the problem that the energy consumption of the external power for driving the compressor is increased.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it will be understood by those of ordinary skill 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. It is to be understood that the invention may be variously modified and changed.

100: housing 110: cylinder block
111: cylinder bore 112: center bore
113: receiving chamber 120: front head
121: crank chamber 130: rear head
131: Suction chamber 132: Discharge chamber
133: inlet port 134: outlet port
300: swash plate 400: piston
500: Valve unit 600,600 ': Differential pressure valve
610, 610 ': case 620, 620: opening / closing core
611,611 ': First inlet 612,612': Outlet
613,613 ': Second inlet 614: Liquid refrigerant outlet
615: Third inlet 621: Intermediate communication hole
700,700 ': Check valve at the outlet side 800,800': Check valve at the inlet side

Claims (11)

A cylinder block 110 in which a plurality of cylinder bores 111 are formed, a front head 120 disposed in front of the cylinder block 110 and formed with a crank chamber 121, And a rear head 130 having a suction port 133, a discharge port 133 and a discharge port 134 to form an outer body;
A rotating shaft 200 rotatably mounted through one side of the housing 100;
A swash plate 300 mounted on the rotary shaft 200 and integrally rotated with the rotary shaft 200 so as to be able to vary the angle with respect to the rotary shaft 200 so that the refrigerant discharge amount can be adjusted;
A plurality of pistons 400 connected to the swash plate 300 and linearly reciprocating by rotation of the swash plate 300;
A valve unit (500) installed between the cylinder block (110) and the rear head (130) to suck and discharge the refrigerant; And
Is provided on a connection passage L1 that communicates with the discharge chamber 132 and the discharge port 134 and is communicated with the crank chamber 121 so that the pressure in the discharge chamber 132 and the pressure in the crank chamber 121 And a differential pressure valve (600) for controlling the flow of the refrigerant from the discharge chamber (132) to the discharge port (134) by differential pressure,
The differential pressure valve (600)
A case 612 having a first inlet 611 communicating with the discharge chamber 132, an outlet 612 communicating with the discharge port 134 and a second inlet 613 communicating with the crank chamber 121 610); And
The flow of the refrigerant from the first inlet 611 to the outlet 612 is controlled by the pressure of the crank chamber 121 and the pressure of the discharge chamber 132 An opening / closing core 620 which is adjusted by the pressure difference of the first and second openings;
Wherein the compressor is a compressor. delete The method according to claim 1,
A liquid refrigerant outlet port 614 communicating with the suction chamber 131 is formed at one side of the case 610. The liquid inlet port 614 is connected to the first inlet 611 and the outlet 612, And is opened when it is closed by the opening / closing core (620). The method according to claim 1,
A third inlet 615 communicating with the discharge chamber 132 is formed in the case 610 and a flow path extending from the first inlet 611 to the outlet 612 is formed in the opening and closing core 620, Wherein an intermediate communication hole (621) is formed to allow a flow path from the third inlet (615) to the outlet (612) to be opened. The method of claim 4,
A liquid refrigerant outlet 614 communicating with the suction chamber 131 is formed at one side of the case 610. The liquid refrigerant outlet 614 is connected to the first inlet 611 and the third inlet 615, And the outlet (612) is closed by the opening / closing core (620). The method according to claim 1 or 3,
And an outlet side check valve (700) is connected to the outlet side of the differential pressure valve (600). The method according to claim 1 or 3,
And an inlet side check valve (800) is connected to the inlet side of the differential pressure valve (600). A cylinder block 110 in which a plurality of cylinder bores 111 are formed, a front head 120 disposed in front of the cylinder block 110 and formed with a crank chamber 121, And a rear head 130 having a suction port 133, a discharge port 133 and a discharge port 134 to form an outer body;
A rotating shaft 200 rotatably mounted through one side of the housing 100;
A swash plate 300 mounted on the rotary shaft 200 and integrally rotated with the rotary shaft 200 so as to be able to vary the angle with respect to the rotary shaft 200 so that the refrigerant discharge amount can be adjusted;
A plurality of pistons 400 connected to the swash plate 300 and linearly reciprocating by rotation of the swash plate 300;
A valve unit (500) installed between the cylinder block (110) and the rear head (130) to suck and discharge the refrigerant; And
And is connected to the suction chamber 131 and communicates with the pressure of the discharge chamber 132 and the pressure of the suction chamber 131. The suction chamber 131 is connected to the discharge chamber 132 and the discharge port 134, And a differential pressure valve (600 ') for controlling the flow of the refrigerant from the discharge chamber (132) to the discharge port (134) by differential pressure,
The differential pressure valve 600 '
A first inlet 611 'communicating with the discharge chamber 132, an outlet 612' communicating with the discharge port 134 and a second inlet 613 'communicating with the suction chamber 131 A formed case 610 '; And
The flow of the refrigerant from the first inlet 611 'to the outlet 612' is supported by the inner side of the case 610 'via the spring S and the pressure of the crank chamber 121 and the suction chamber 132) an opening / closing core (620 ') controlled by pressure differential pressure;
Wherein the compressor is a compressor. delete The method of claim 8,
And an outlet side check valve (700 ') is connected to the outlet side of the differential pressure valve (600'). The method of claim 8,
, And an inlet side check valve (800 ') is connected to the inlet side of the differential pressure valve (600').

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