KR101693042B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate type compressor. In the present invention, the check valve body 190 is provided to allow the refrigerant to pass therethrough only when the pressure of the refrigerant is equal to or higher than a predetermined value. The check valve body 190 includes a valve case 191 in which a plurality of discharge holes 195 are biased to one side of the side face, a valve 193 installed to be movable in the valve case 191, And a spring (S) installed in the case (191) and elastically supporting the valve (193) in a direction blocking the inlet of the valve case (191). According to the present invention having such a configuration, even when the pressure of the refrigerant is relatively low, the refrigerant exits while contacting the valve 193 of the check valve body 190 to one side of the inner circumferential surface of the valve case 191, 193) of the valve case (191) is minimized by colliding against the inner circumferential surface of the valve case (191).

Description

[0001] The present invention relates to a variable displacement swash plate type compressor,

The present invention relates to a variable displacement swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor having a check valve body configured to prevent noise and vibration from occurring.

FIG. 1 is a cross-sectional view of a conventional variable displacement swash plate type compressor, and FIG. 2 is a partial cross-sectional perspective view of a check valve body according to the prior art.

As shown in the figure, a variable capacity swash plate type compressor (hereinafter referred to as a compressor) includes a cylinder block 10 having a plurality of cylinder bores 11, A housing 30, and a rear housing 50 coupled to the rear of the cylinder block 10.

A plurality of cylinder bores 11 are formed in the cylinder block 10. The cylinder bore 11 is formed for compressing the refrigerant and is formed in a cylindrical shape. The cylinder bores 11 are arranged at regular intervals along the outer edge of the cylinder block 10 and are formed substantially through the cylinder block 10. A piston 15 is installed in the cylinder bore 11 to reciprocate linearly and compress the refrigerant in a space therebetween. The piston 15 has a cylindrical shape.

The front housing 30 is coupled to one side of the cylinder block 10, that is, forward. The rear of the front housing 30 is concave and engages with the cylinder block 10 to form a crank chamber 31 therebetween. A mechanism for reciprocating the piston 15 is installed in the crank chamber 31.

Further, the rear housing 50 is coupled to the other side of the cylinder block 10, that is, the rear side. The rear housing 50 is formed with a front surface opened and includes a suction chamber 51 which is engaged with the cylinder block 10 and sucks refrigerant into the cylinder bore 11, Thereby forming a discharge chamber 53 through which the compressed refrigerant is discharged.

The suction chamber 51 is a portion for supplying the refrigerant to be compressed into the cylinder bore 11. The cylinder block 10 of the rear housing 50 corresponding to the cylinder bore 11, And is formed at a portion corresponding to the center of the facing surface. In the rear housing 50, a suction port 55 for transferring refrigerant from the outside to the suction chamber 51 is formed.

The discharge chamber 53 through which the compressed refrigerant is discharged after being supplied into the cylinder bore 11 through the suction chamber 51 is connected to the rear housing 50 In the radially outer portion. The compressed refrigerant discharged to the discharge chamber (53) is supplied to the heat exchanger for air conditioning required by the automobile.

The suction chamber 51 and the discharge chamber 53 are selectively communicated with the cylinder bores 11 due to a pressure difference with the cylinder bores 11 to move the refrigerant. At this time, the valve assembly 60 controls the flow of the refrigerant based on the pressure difference between the cylinder bore 11, the suction chamber 51, and the discharge chamber 53.

The suction chamber 51 and the discharge chamber 53 are formed between the cylinder block 10 and the rear housing 50 and between the cylinder bore 11 and the suction chamber 51 and the discharge chamber 53, A valve assembly 60 for interrupting the flow of the refrigerant is installed.

Next, a configuration for driving the piston 15 for compressing the refrigerant while performing the linear reciprocating motion in the cylinder bore 11 will be described.

The driving source for operating the piston 15 is a driving force transmitted from an engine of an automobile. The drive force of the engine is transmitted to the drive shaft 20 and the drive shaft 20 is rotated. The drive shaft 20 is coupled to a center bore 13 formed at the rear center of the cylinder block 10 through a shaft hole 32 formed in the center of the front housing 30, And is rotatably supported.

Inside the crank chamber 31, there is provided a substantially disk-shaped rotor 22 to which the driving shaft 20 is fixedly coupled to the center thereof. The rotor 22 rotates along with the rotation of the drive shaft 20.

A swash plate 26 is provided on the drive shaft 20 to linearly reciprocate the piston 15. The swash plate 26 is formed in a disk shape and is installed so that the angle with respect to the driving shaft 20 can be changed according to the discharge capacity of the compressor. That is, the swash plate 26 is coupled to the driving shaft 20 so as to be orthogonal to the driving shaft 20 or to be inclined at a predetermined angle with respect to the driving shaft 20. The swash plate 26 is hingedly coupled to the rotor 22 and rotated together.

A connecting portion 17 for connecting with the swash plate 26 is formed at one side of the piston 15 that performs the linear reciprocating motion, that is, at the front side. A pair of hemispherical shoe 19 is provided in the connecting portion 17, which is partly opened toward the driving shaft 20.

The edge portion of the swash plate 26 is engaged between the shoe 19 of the connecting portion 17. When the swash plate 26 having a predetermined inclination rotates and its edge portion passes the shoe 19, the swash plate 26 is connected to the connecting portion 17 having the shoe 19 by the inclination of the swash plate 26 The piston 15 is reciprocated linearly in the cylinder bore 11 to compress the refrigerant.

The refrigerant compressed in the cylinder bore 11 is discharged to the discharge chamber 53 through the valve assembly 60. When the piston 15 moves in the top dead center (left direction in the drawing) in the cylinder bore 11, the internal pressure of the cylinder bore 11 is lowered. Therefore, the refrigerant guided to the suction chamber 51 Is introduced into the interior of the cylinder bore 11 again via the valve assembly 60. Through this process, the refrigerant is sucked and compressed through the plurality of cylinder bores 11, so that the air conditioner of the automobile operates.

As described above, the inclination angle of the swash plate 26 changes from a vertical state to the drive shaft 20 to a predetermined inclination angle, and the discharge amount of the refrigerant to be compressed can be adjusted. In order to adjust the inclination angle of the swash plate 26, a control valve 70 is installed on one side of the rear housing 50.

The control valve 70 guides a part of the high-pressure refrigerant discharged from the discharge chamber 53 through the valve portion (not shown) to the crank chamber 31 and controls the flow rate thereof, To control the pressure in the chamber. That is, the valve portion of the control valve 70 serves to selectively communicate the discharge chamber 53 and the crank chamber 31.

When the compressor 1 is stopped and the valve portion of the control valve 80 is opened, a part of the high-pressure refrigerant discharged into the discharge chamber 53 flows into the crank chamber 31 to increase the pressure of the crank chamber 31 . The fact that the pressure of the crank chamber 31 is increased means that the inclination angle of the swash plate 26 is substantially reduced, that is, it is maintained at a right angle with respect to the drive shaft 20. [ Accordingly, this state is such that the stroke of the piston 15 is minimized and the refrigerant compressed and discharged is minimized.

On the other hand, a discharge passage 57 is formed in the rear housing 50 at one side of the discharge chamber 53. The discharge passage 57 communicates with the discharge chamber 53 and the muffler portion 82 of the discharge manifold 80 formed in the cylinder block 10.

A check valve body (90) is provided in the discharge chamber (53). The check valve body 90 serves to prevent the refrigerant from escaping through the discharge passage 57 when the pressure of the refrigerant discharged into the discharge chamber 53 is a predetermined value or less.

2, the check valve body 90 includes a valve case 91 having a bottom surface 91 'and a cylindrical outer circumferential surface, And a valve 93 installed as far as possible.

A plurality of discharge holes 95 are formed on the outer peripheral surface of the valve case 91. And the refrigerant introduced into the valve case 91 is transferred to the discharge passage 57 through the discharge hole 95. The discharge holes 95 are arranged at regular intervals and penetrate in a direction perpendicular to the longitudinal direction of the valve case 91.

The valve 93 is formed to be movable in the valve case 91, and is formed in a substantially cylindrical shape. The valve 93 is for blocking refrigerant from escaping through the discharge passage 57.

The valve 93 is resiliently supported by a spring S provided in the internal space 92 and receives an elastic force by the spring S toward the inlet side of the valve case 91. At this time, the elastic force of the spring S must continuously exert an elastic force in a direction blocking the inlet of the valve case 91 before the refrigerant is discharged toward the discharge chamber 53. When the refrigerant is discharged, The valve body 93 must be able to move in the direction of the bottom surface 91 'of the valve case 91 to overcome the elastic force.

A through hole 94 is radially formed at the center of the bottom surface 91 'of the valve case 91 and the center of the bottom surface 91'. The through hole 94 is formed to prevent the valve 93 from moving due to the pressure of the internal space 92 of the valve case 91.

A ring-shaped cover 97 is coupled to the valve case 91. The inner diameter D of the cover 97 is formed to be smaller than the outer diameter d of the valve 93. This is to prevent the valve (93) from being separated from the valve case (91). The cover (97) is press-fitted into the inner surface of the discharge chamber (53).

On the other hand, a muffler portion 82 is formed on one side of the outer surface of the cylinder block 10. The muffler portion 82 is formed inside the cylinder block 10 by fastening the discharge manifold 80 to the cylinder block 10. Reference numeral 84 denotes a discharge port.

Next, the refrigerant is transferred into the cylinder bore 11 will be described. Refrigerant is sucked from the outside into the suction chamber (51), and the refrigerant transferred to the suction chamber (51) is transferred to the inside of the cylinder bore (11).

The refrigerant compressed in the reciprocating motion of the piston 15 is transmitted to the discharge chamber 53 through the valve assembly 60. [ The refrigerant discharged to the discharge chamber (53) passes through the check valve body (90).

At this time, the valve 93 of the check valve body 90 moves toward the bottom surface 91 'of the valve case 91 while overcoming the elastic force, (95) and moves to the discharge passage (57). The refrigerant that has been moved to the muffler portion 82 through the discharge passage 57 is discharged through the discharge port 84 and is delivered to the outside of the compressor 1. [

However, the above-described conventional techniques have the following problems.

When the pressure of the refrigerant discharged to the discharge chamber 53 is low and the valve 93 is varied in the direction in which the angle of the swash plate 26 is reduced, the spring force of the spring S of the check valve body 80 Will not be completely overcome. In this state, when the refrigerant is forced through the discharge hole 95 and the through hole 94 arranged at regular intervals, the valve 93 is pressed against the inner peripheral surface of the valve case 91 Vibration and noise are generated.

When the compressor 1 is driven again under the condition of the low temperature / low pressure operation from the stop state, since the discharge capacity of the compressor 1 is small, the refrigerant can not sufficiently overcome the elastic force of the spring S, So that noise is generated as it flows out through the gap between the ball 95 and the valve 90.

The generated noise and vibration are transmitted to the interior of the vehicle through a pipe (not shown) connected to the compressor 1, thus causing a problem of generating room noise.

SUMMARY OF THE INVENTION An object of the present invention is to provide a variable displacement swash plate compressor in which a check valve is provided to prevent noise and vibration from occurring under a small displacement of the compressor.

According to an aspect of the present invention, there is provided a cylinder block including a plurality of cylinder bores; A front housing coupled to the front of the cylinder block to form a crank chamber therein; A rear housing coupled to a rear portion of the cylinder block and having a suction chamber and a discharge chamber formed therein; And a check valve body provided on a refrigerant path between the cylinder bore and a discharge port through which the compressed refrigerant is discharged and allowing the refrigerant to pass therethrough only when the pressure of the refrigerant is equal to or greater than a predetermined value, CLAIMS What is claimed is: The check valve body includes a valve case having a plurality of discharge holes formed therein, a valve movably installed in the valve case, and a spring installed in the valve case to elastically support the valve in a direction blocking the valve case And a valve closing means for preventing the valve from shaking.

It is preferable that the valve close-up means is a through-hole formed in the bottom surface of the valve case, and a part of the through-hole is opened toward the valve case.

The discharge hole may be formed on one side of the valve case.

The tension of the spring is preferably between 200 kgf and 500 kgf.

The area of the through hole is preferably between 1.0 mm 2 and 7.0 mm 2.

In the present invention, when the pressure of the refrigerant discharged into the discharge chamber is varied in a direction in which the angle of the swash plate is reduced, the refrigerant is discharged through the discharge hole formed on the side of the check valve body The valve of the check valve is brought into contact with one side of the inner circumferential surface of the check valve body. Therefore, even when the pressure of the refrigerant is relatively low, the refrigerant exits from the state that the valve is in contact with one side of the inner circumferential surface of the valve case, so that the noise generated when the valve hits the inner circumferential surface of the valve case is minimized, There is an effect that can be maintained.

In the present invention, when the compressor is driven again under the condition of the low temperature / low pressure operation from the stop state, even if the discharge capacity of the compressor is reduced, the valve of the check valve body overcomes the elastic force of the spring, It is possible. Therefore, since the valve can be smoothly moved toward the bottom surface of the valve case even with a relatively small refrigerant pressure, there is also an effect that the noise generated while escaping from the discharge hole of the check valve body is effectively reduced.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a configuration of a variable capacity swash plate type compressor according to a related art; FIG.
2 is a partial cross-sectional perspective view showing a configuration of a check valve body according to the prior art.
3 is a sectional view showing a configuration of a preferred embodiment of a variable displacement swash plate type compressor according to the present invention.
4 is a perspective view showing a configuration of a check valve constituting an embodiment of the present invention.
5 is a plan view showing a configuration of a check valve constituting an embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of a variable displacement swash plate compressor according to the present invention will be described in detail with reference to the accompanying drawings.

3 is a cross-sectional view of a preferred embodiment of a variable displacement swash plate type compressor according to the present invention. FIG. 4 is a perspective view of a check valve constituting an embodiment of the present invention. A configuration of a check valve constituting an embodiment of the invention is shown in a plan view.

3, the compressor 100 of the present invention includes a cylinder block 110 having a plurality of cylinder bores 111, a crank chamber 131 coupled to the front of the cylinder block 110, And a rear housing 150 coupled to the rear of the cylinder block 110 to form a suction chamber 151 and a discharge chamber 153.

In the cylinder block 110, a plurality of cylinder bores 111 are radially formed at regular intervals. The cylinder bore 111 is a portion for compressing the refrigerant. The piston 115 is accommodated in the cylinder bore 111, and is linearly reciprocated to compress the refrigerant in a space therebetween. The cylinder bore 111 is formed in a cylindrical shape so as to pass through the cylinder block 110, and the piston 115 is formed into a cylindrical shape corresponding to the cylinder bore 111.

The front housing 130 is coupled to one side of the cylinder block 110, that is, the front side. The rear of the front housing 130 is recessed to form a crank chamber 131 in cooperation with the cylinder block 110. In the crank chamber 131 formed between the cylinder block 110 and the front housing 130, a mechanism for reciprocating the piston 115, that is, a rotor 122 and a swash plate 126, The same parts are installed.

A rear housing 150 is installed on the opposite side of the cylinder block 110 on which the front housing 130 is installed. A suction chamber 151 for sucking refrigerant is formed at the center of a surface of the rear housing 150 facing the cylinder block 110. The suction chamber 151 serves to transfer the refrigerant to be compressed into the cylinder bore 111.

A discharge chamber 153 through which the refrigerant compressed by the cylinder bore 111 is discharged is formed in the rear housing 150. The discharge chamber 153 is formed at a portion radially outward of the rear housing 153 at a portion corresponding to the cylinder bore 111.

A suction port 155 is formed in the rear housing 150 to transmit the refrigerant to the suction chamber 151. The suction port 155 is formed to penetrate the outside of the compressor 100 and the inside of the suction chamber 151.

A valve assembly 160 is provided between the cylinder block 110 and the rear housing 150 for interrupting the flow of the refrigerant between the suction chamber 151 and the discharge chamber 153. The suction chamber 151 and the discharge chamber 153 are selectively communicated with the cylinder bore 111 due to a pressure difference between the cylinder bore 111 and the cylinder bore 111 to move the refrigerant. At this time, the valve assembly 160 controls the flow of the refrigerant based on the pressure difference between the cylinder bore 111 and the suction chamber 151 and the discharge chamber 153.

Next, a configuration for driving a piston 115 for compressing a refrigerant while performing a linear reciprocating motion in the cylinder bore 111 will be described.

The driving source for operating the piston 115 is a driving force transmitted from an engine of an automobile. The drive force of the engine is transmitted to the drive shaft 120, and the drive shaft 120 is rotated. The drive shaft 120 is coupled to a center bore 113 formed at the rear center of the cylinder block 110 through a shaft hole 132 formed in the front housing 130. The drive shaft 120 is rotatably supported based on a rotational force transmitted from the engine.

The crank chamber 131 is provided with a substantially disk-shaped rotor 122 in which the driving shaft 120 is fixedly coupled to the center thereof. Accordingly, the rotor 122 rotates in accordance with the rotation of the driving shaft 120.

A swash plate 126 for reciprocating the piston 115 is installed on the driving shaft 120. The swash plate 126 is formed in a disk shape and is installed so that the angle of the swash plate 126 with respect to the driving shaft 120 can be changed according to the discharge capacity of the compressor. That is, the swash plate 126 is coupled to the driving shaft 120 so as to be orthogonal to the driving shaft 120 or to be inclined at a predetermined angle with respect to the driving shaft 120.

A hemispherical shoe 119 is provided at one side of the piston 115 that performs a linear reciprocating motion, that is, inside a connection portion 117 for connection with the swash plate 126 at the front side. And an edge portion of the swash plate 126 is coupled between the shoes 119. When the swash plate 126 having a predetermined inclination rotates and its edge portion passes through the shoe 119, the connecting portion 117 having the shoe 119 due to the inclination of the swash plate 126 The connected piston 115 linearly reciprocates in the cylinder bore 111 to compress the refrigerant.

In order to adjust the inclination angle of the swash plate 126, a control valve 170 is installed on one side of the rear housing 150. The control valve 170 includes a valve unit (not shown) that can selectively communicate the discharge chamber 153 and the crank chamber 131. The control valve 170 controls the pressure in the crank chamber 131 by controlling the flow rate of the refrigerant while guiding part of the refrigerant of the discharge pressure discharged from the discharge chamber 153 through the valve portion to the crank chamber 131 .

In other words, by changing the pressure of the crank chamber 131, the inclination angle of the swash plate 126 can be changed, whereby the stroke of the piston 115 is changed and the discharge amount of the refrigerant is adjusted. It is the control valve 170 that controls the inside pressure of the crank chamber 131 to be changed.

On the other hand, a discharge passage 157 is formed in the rear housing 150 at one side of the discharge chamber 153. The discharge passage 157 communicates with the discharge chamber 153 and the muffler portion 182 of the discharge manifold 180 formed in the cylinder block 110. Reference numeral 184 denotes a discharge port. The discharge port 184 serves to transfer the refrigerant discharged to the discharge chamber 153 to the outside.

In the variable capacity swash plate type compressor 100, a check valve body 190 is provided in the discharge chamber 153. More specifically, the check valve body 190 is provided on the refrigerant path between the cylinder bore 111 and the discharge port 184. The check valve body 190 blocks the refrigerant from escaping through the discharge passage 157 when the pressure of the refrigerant transferred to the discharge chamber 153 is lower than a predetermined value so that the refrigerant enters the crank chamber 131, . This is to minimize the stroke of the piston 115 by adjusting the angle of the swash plate 126 when the compressor is stopped. In this case, since the stroke of the piston 115 is minimized, the refrigerant is hardly compressed, so that the pressure of the refrigerant that can pass through the check valve body 190 is not formed.

4, the check valve body 190 includes a valve case 191 having a bottom surface 191 'and an inlet and a cylindrical outer circumferential surface which are open toward the valve assembly 160, And a valve 193 movably installed inside the case 191.

A plurality of discharge holes 195 are formed on the side surface of the valve case 191. The refrigerant discharged to the discharge chamber 153 through the discharge hole 195 is transferred to the discharge passage 157. The discharge hole 195 is formed to penetrate in a direction perpendicular to the longitudinal direction of the valve case 191. The discharge hole 195 serves as a kind of passage so that the refrigerant can move between the discharge passage 157 and the discharge chamber 153.

A plurality of the discharge holes 195 may be formed. In the present embodiment, the discharge holes 195 are formed on one side of the valve case 191 to be three. This is to prevent the refrigerant from escaping through the discharge hole 195 so that the valve 193 flows in the longitudinal direction of the valve case 191 or hits against the inner circumferential surface. Since the valve 193 is in contact with the inner circumferential surface of the valve case 191 when the refrigerant passes through the discharge hole 195 and the valve 193 is in contact with the inner circumferential surface of the valve case 191 The noise is minimized.

A through hole 196 is formed in the bottom surface 191 'of the valve case 191. The through hole 196 is formed to prevent the valve 193 from moving due to pressure inside the valve case 191. The through hole 196 is partly opened toward the valve case 191. This is to allow the valve 193 to move more smoothly toward the inner circumferential surface of the valve case 191.

The area of the through hole 196 is preferably between 1.0 mm 2 and 7.0 mm 2. When the area of the through hole 196 is smaller than 1.0 mm2 as shown in Table 1, the valve 193 is pressed against the bottom surface of the valve case 191 by the internal pressure of the valve case 191, And it is difficult to move toward the center line 191 '. When the area of the through hole 196 is larger than 7.0 mm 2, the valve 193 easily moves toward the bottom surface 191 'of the valve case 191 and hits against the inner circumferential surface of the valve case 191 This is because noise may occur.

division 0.9 mm 2 1.0 < ... 7.0㎟ 7.1mm2 Operational x o o o o Noise generation x x x x o

The valve 193 is formed to be movable in the valve case 191 and is formed in a substantially cylindrical shape. The valve 193 prevents the high-pressure refrigerant in the crank chamber 131 from passing through the discharge chamber 153 and escaping to the discharge passage 157 at a time.

The valve 193 is resiliently supported by a spring S provided in the valve case 191 and receives an elastic force by the spring S in the closing direction of the inlet side of the valve case 191. The elastic force of the spring S must continuously exert an elastic force in a direction of closing the inlet of the valve case 191 before the refrigerant flows into the discharge chamber 153. When the refrigerant flows into the valve 193, Must be able to move in the direction of the bottom surface 191 'of the valve case 191 to overcome the elastic force.

At this time, the tension of the spring S is preferably 200 kgf to 500 kgf. This is to allow the valve 193 to move smoothly toward the bottom surface 191 'of the valve case 191 even with a relatively small refrigerant pressure, as shown in Table 2. When the tension of the spring S is less than 200 kgf, the valve 191 moves too easily in the direction of the bottom surface 191 'of the valve case 191 and the tension of the spring S is greater than 500 kgf , It is difficult for the valve 191 to move toward the bottom surface 191 'of the valve case 191.

division 150kgf 200kgf 350kgf 500kgf 550kgf Operational o o o o x Noise generation o x x x x

One side of the spring S is supported by the bottom surface 101 ', and the other side supports the bottom surface of the valve 103. A support boss 197 protruding from the bottom surface 191 'is inserted into one side of the spring S to prevent the spring S from flowing.

On the other hand, a ring-shaped cover 198 is coupled to the inlet of the valve case 191. The cover 198 may be formed by, for example, the valve case 191 and insert injection. The inner diameter D of the cover 198 is formed to be smaller than the outer diameter d of the valve 193. This is to prevent the valve 193 from being separated from the valve case 191. That is, the cover 198 serves as a kind of stopper for restricting the movement of the valve 193.

The outer diameter of the cover 198 is formed to be slightly larger than the inner diameter of the discharge chamber 153. This is because the outer circumferential surface of the cover 198 is press-fitted into the inner circumferential surface of the discharge chamber 153 and fixed.

Hereinafter, the operation of the check valve applied to the variable displacement swash plate type compressor according to the present invention will be described.

In driving the variable displacement swash plate type compressor 100, when the inclination angle of the swash plate 126 becomes maximum, the stroke length of the piston 114 becomes maximum, and the discharge amount of the refrigerant also becomes maximum. When an electric current is applied to the control valve 170 and an electromagnetic force is applied, the valve portion of the control valve 170 acts in the closing direction. Here, the fact that the valve part of the control valve 170 is completely closed means that the air conditioner is operating at its maximum because the heat load inside the vehicle is large. This is because the swash plate 126 has a maximum inclination angle And the stroke length of the piston 115 is maximized while rotating.

In this state, when the inclination angle of the swash plate 126 is varied by the control valve in a direction in which the inclination angle of the swash plate 126 is reduced, the amount of the refrigerant compressed in the cylinder bore 113 is also reduced.

Thus, the refrigerant compressed in the cylinder bore 113 is discharged to the discharge chamber 153. The refrigerant discharged to the discharge chamber 153 passes through the check valve body 190 and moves toward the discharge manifold 180 side. In this state, the valve 193 of the check valve body 190 is resiliently supported in the direction of closing the inlet of the check valve body 190 by the elastic force of the spring S, And escapes through the discharge hole 195 of the check valve body 190 while overcoming the elastic force of the spring S.

A plurality of the discharge holes 195 are formed on the side surface of the valve case 191 and the through holes 196 are formed in the valve case 191. In this case, The refrigerant passes through the through hole 196 while contacting the valve 193 to one side of the inner circumferential surface of the valve case 191. The valve 191 is formed with a through hole 196 ' .

Thus, the refrigerant exits the valve 193 while contacting the inner circumferential surface of the valve case 191, so that the noise generated when the valve 193 hits the inner circumferential surface of the valve case 191 is minimized.

When the discharge capacity of the compressor 100 is low, the pressure of the refrigerant is relatively low when the compressor 100 is driven again in the stopped state. At this time, since the tension of the spring S of the check valve body 190 is between 200 kgf and 500 kgf, the valve 193 smoothly flows into the bottom surface of the valve case 191 191 ', so that the noise generated when the air passes through the discharge hole 195 of the check valve body 190 is minimized.

The scope of the present invention is not limited to the embodiments described above, but may be defined by the scope of the claims, and those skilled in the art may make various modifications and alterations within the scope of the claims It is self-evident.

100: compressor 110: cylinder block
111: cylinder bore 115: piston
130: front housing 131: crank chamber
150: rear housing 151: suction chamber
153: Discharge chamber 157: Discharge passage
180: Discharge manifold 182: muffler part
190: check valve body 191: valve case
193: valve 195: discharge hole
196: Through hole S: Spring

Claims (5)

A cylinder block 110 having a plurality of cylinder bores 111;
A front housing 130 coupled to the front of the cylinder block 110 to form a crank chamber 131 therein;
A rear housing 150 coupled to the rear of the cylinder block 110 and having a suction chamber 151 and a discharge chamber 153 formed therein; And
A check valve body 190 installed on the refrigerant path between the cylinder bore 111 and the discharge port 184 through which the compressed refrigerant is discharged and allowing the refrigerant to pass therethrough only when the pressure of the refrigerant is equal to or greater than a predetermined value, A variable capacity swash plate compressor comprising:
The check valve body (190)
A valve case 191;
A discharge hole 195 formed on the sidewall of the valve case 191 to discharge the refrigerant;
A valve (193) installed in the valve case (191) and moved by the pressure of the refrigerant to open the discharge hole (195);
A spring S for restricting movement of the valve 193;
Is formed on a bottom surface 191 'of the valve case 191 and a part of a side wall surface adjacent to the bottom surface 191' so that the valve 193 is opened when the discharge hole 195 is opened, And a through hole (196) for discharging a part of the refrigerant. delete delete The method according to claim 1,
Wherein the tension of the spring (S) is between 200 kgf and 500 kgf. The method according to claim 1,
And the area of the through hole (196) is between 1.0 mm < 2 > and 7.0 mm < 2 >.

Images