KR101763979B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate type compressor and is provided with a center bore (112) slidably movably coupled to a rotary shaft (200) and integrally rotated with a rotary shaft (200) A communication passage 700 leading from the crank chamber 121 to the suction chamber 131 through an intermediate chamber 610 formed inside the bush 600 and a communication passage 700 connecting the discharge chamber 132 and the crank And an intermediate passage 800 communicating with the chamber 121 and selectively communicating with the intermediate chamber 610 of the bush 600. Such a variable displacement swash plate type compressor can prevent the excessive change in the suction chamber pressure that occurs during the maximum operation, thereby achieving the effect of improving pulsation and providing a sufficient communication path between the crank chamber and the suction chamber, Can be improved.

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 in which, when compressing a refrigerant sucked from an external refrigerant line by a plurality of pistons reciprocating in accordance with rotation of a swash plate, The present invention relates to a variable displacement swash plate type compressor.

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.

FIG. 1 is a view showing the overall structure of a conventional variable displacement swash plate type compressor, and FIG. 2 is a view showing an example of an oil separation structure applied to 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 FIGS. 1 and 2. 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 and a suction chamber 131 and a discharge chamber 132 are defined inside the rear head 130.

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 oil separator S is inserted into the center bore 112 and inserted into the center bore 112.

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 is provided between the cylinder block 110 and the rear head 130 to suck and discharge the refrigerant. A plurality of suction valves and discharge valves are formed in the valve unit 500. The discharge chamber 132 and the crank chamber 121 communicate with each other through the air supply passage L and the crank chamber 121 and the suction chamber 131 communicate with each other through the additional passage 700, In the middle of the passage L, a pressure control valve V for varying the inclination angle of the swash plate 300 is connected by adjusting the opening degree of the air supply passage L.

A portion of the rear side of the center bore 112 of the cylinder block 110 accommodates the oil separator S and constitutes a receiving chamber 113 for receiving refrigerant and oil. A refrigerant passage 210 communicating with the crank chamber 121 and the containing chamber 113 may be formed at the center of the crank chamber 121.

2, the additional passage 700 is connected to the intake chamber 113 and the valve unit (not shown) The crank chamber 121 and the suction chamber 131 are communicated with each other through the orifice 510 formed in the cylinder 500.

The air supply passage L is formed such that a part of the air between the pressure regulating valve V and the crank chamber 121 passes through the lower portion of the containing chamber 113 and is separated from the refrigerant through the oil separator S Is returned to the crank chamber (121) through the supply passage (L).

However, in the conventional variable displacement swash plate type compressor as described above, when the suction amount of the refrigerant is reduced, there is a problem that vibration occurs in the suction port and pulsation or noise is generated.

In order to solve this problem, when the refrigerant suction amount is small, a suction check valve M (not shown) is formed on the pipeline 135 connecting the suction port 133 to the suction chamber 131 in order to gradually change the flow area of the suction port, ), A suction muffler is installed, or the volume of the suction chamber 132 is increased or the like.

However, there is a limitation in increasing the volume of the suction chamber, and a problem of increase in cost is obstructed when the suction muffler is installed. Even when the suction check valve M is provided, the limit to reduce the suction pulsation at the time of the maximum variable operation .

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 there is a problem of delay in initial operation delay in which 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. It is an object of the present invention to provide an internal combustion engine capable of preventing the excessive change in the suction chamber pressure, , And a variable displacement swash plate type compressor capable of completely improving the initial operation delay.

In order to accomplish the above object, according to the present invention, there is provided a variable capacity swash plate type compressor, comprising: a cylinder block having a plurality of cylinder bores, a center bore and a containing chamber forming a certain rear portion of a center bore, A housing having a front head formed with a thread and a rear head disposed behind the cylinder block and formed with a suction chamber and a discharge chamber to form an outer body; a rotating shaft rotatably mounted through one side of the housing; A swash plate installed to the swash plate and integrally rotated with the swash plate so that the angle of the swash plate with respect to the swash plate can be changed so that the refrigerant discharge amount can be adjusted; A plurality of pistons linearly reciprocating, and a plurality of pistons arranged between the cylinder block and the rear head A bush which is slidably mounted on the center bore and rotates integrally with the rotary shaft and is connected to the rotary shaft and passes through the valve unit; And an intermediate passage communicating with the discharge chamber and the crank chamber and selectively communicating with the intermediate chamber of the bush.

The communication passage may include a first passage formed between the cylinder bore and the center bore, and a second passage corresponding to a predetermined region of the intermediate chamber formed in the bush.

The bush may be formed with an inlet hole through which the first passage communicates with the second passage, and an outlet hole communicating with the second passage and the suction chamber may be formed at an end of the bush.

And a slide valve for interrupting the opening and closing of the inflow hole is provided in the bush.

Wherein the slide valve includes a spring supported on an inner side of the bush and an opening and closing core that is elastically supported by the spring and slides along an axial direction of the bush and divides a certain region of the intermediate chamber of the bush into the second passage, .

And the slide valve is structured such that when the intermediate passage communicates with the intermediate chamber of the bush, the opening and closing core is configured to slide in a direction closing the inflow hole of the bush by the pressure of the intermediate passage.

When the opening and closing core is completely slid in the direction of closing the inflow hole of the bush by the pressure of the intermediate passage, a fine gap for oil separation and recovery is formed between the opening and closing core and the inflow hole of the bush .

The intermediate passage is communicated with the suction chamber via the second passage when the opening / closing core is slid completely in a direction closing the inflow hole of the bush by the pressure of the intermediate passage. It is preferable that an orifice is formed.

The first passage and the second passage are formed in such a manner that when the opening and closing core is completely slid in the direction closing the inflow hole of the bush by the pressure of the intermediate passage, A third passage is formed between the valve units and an orifice communicating the third passage and the suction chamber is formed in the valve unit.

Sectional area across the entire area of the communication path is preferably larger than the cross-sectional area of the orifice having a size of? 2.4 mm.

The bush may be formed with a communication hole for communicating the intermediate passage and the intermediate chamber, and a communication groove may be formed in the rotation shaft for smooth communication between the communication hole and the intermediate chamber.

According to the variable capacity swash plate type compressor as described above, it is possible to obtain the effect of improving the pulsation by preventing excessive change in the suction chamber pressure generated at the maximum operation, and by forming a sufficient communication path between the crank chamber and the suction chamber, The initial operation delay problem can be completely improved.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing the overall structure of a conventional variable displacement swash plate type compressor. Fig.
2 is a view showing an example of an oil separation structure applied to a conventional variable displacement swash plate type compressor.
3 is a longitudinal sectional view of a variable displacement swash plate type compressor according to an embodiment of the present invention, showing a swash plate in an unoperated state in which the swash plate is erected in the radial direction of the rotary shaft.
4 is a longitudinal sectional view of a variable capacity swash plate type compressor according to an embodiment of the present invention, in which swash plate is inclined at a maximum angle with respect to the radial direction of the rotation axis.
5 is a longitudinal sectional view of a variable displacement swash plate type compressor according to an embodiment of the present invention, in which the swash plate is inclined at an appropriate angle with respect to the radial direction of the rotary shaft and is in a variable operation state.
FIG. 6 is a longitudinal sectional view of a variable capacity swash plate type compressor according to an embodiment of the present invention, showing another state in which the swash plate is inclined at a minimum angle with respect to the radial direction of the rotation axis to be in a variable operation state.
7 is a longitudinal sectional view of a variable displacement swash plate type compressor according to an embodiment of the present invention, in which the swash plate is inclined at an appropriate angle with respect to the radial direction of the rotary shaft and is in a variable operation state.

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. 3 is a longitudinal sectional view of a variable capacity swash plate type compressor according to an embodiment of the present invention, in which the swash plate is in an unactuated state in a radial direction of a rotary shaft, and FIG. 4 is a cross- 5 is a longitudinal sectional view of a variable displacement swash plate type compressor according to an embodiment of the present invention, in which a swash plate is used as a swash plate type compressor, 6 is a longitudinal sectional view of a variable displacement swash plate type compressor according to an embodiment of the present invention, in which the swash plate is inclined at an appropriate angle with respect to the radial direction of the rotary shaft, 7 is a longitudinal sectional view of the variable displacement swash plate type compressor according to the embodiment of the present invention, Inclined at an appropriate angle to the radial direction of the rotating shaft is a view showing the other being variable operation.

3 to 7, a swash plate type compressor according to an embodiment of the present invention will be described in detail with reference to FIG. 1, which is the same as the prior art structure described above with reference to FIG. A variable capacity swash plate type compressor according to an embodiment of the present invention includes: A valve unit 500, a bush 600, a communication passage 700, an intermediate passage (not shown), and a communication passage 700. The housing 100 includes a housing 100, a rotary shaft 200, a swash plate 300, a plurality of pistons 400, 800).

The housing 100 includes a cylinder block 110, a front head 120, and a rear head 130, which are parts of an outer body of the variable displacement 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, and a hollow portion is formed therein to house the plurality of pistons 400 as well as the rotary shaft 200 .

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 slope adjusting mechanism 320 can be received while securing the crank chamber 121 which is the rotating space of the crank chamber 121. [

The rear head 130 has a front end open toward the cylinder block 110 and includes a suction chamber 132 for supplying the refrigerant to the cylinder bore 111 of the cylinder block 110 during the suction stroke, A discharge chamber 134 through which the refrigerant in the cylinder bore 111 is discharged is formed. A suction port 133 and a discharge port (not shown), which are connected to the suction chamber 131 and the discharge chamber 132, respectively, are formed on an outer wall surface of the rear head 130.

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, the piston 400 reciprocates in the cylinder bore 111 to compress the refrigerant.

The plurality of pistons 400 is a means for reciprocating the inside of the cylinder bore 111 by the swash plate 300 and compressing the refrigerant. The pistons 400 can be moved relative to the edge of the swash plate 300 through the shoe 310 And is linearly reciprocated along the inner circumferential surface of the cylinder bore 111 of the cylinder block 110 by the rotation of the swash plate 300 to thereby reciprocate the cylinder bore 111 through the suction port 133 of the rear head 130, (Not shown) of the rear head 130 so as to discharge the refrigerant into the external refrigerant line.

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 bush 600 is formed in a substantially cylindrical shape and is slidably mounted on the center bore 112. The bush 600 is coupled to the rotation shaft 200 and integrally rotates with the rotation shaft 200. When the inclination of the swash plate 300 is varied, the bush 600 slides along with the rotation axis 200 in the axial direction, and moves through the valve unit 500 when sliding in the axial direction.

The communication passage 700 is an oil passage extending from the crank chamber 121 to the suction chamber 131 via an intermediate chamber 610 formed in the bush 600. It is preferable that the communication passage 700 is formed to have a sectional area larger than the cross sectional area of the orifice installed to communicate the crank chamber 121 and the suction chamber 131 to obtain the effect of improving the pulsation. Sectional area across the entire area of the opening 700 is preferably larger than the cross-sectional area of the orifice having the size of 2.4 mm.

The intermediate passage 800 is a passage that communicates with the discharge chamber 132 and the crank chamber 121 and selectively communicates with the intermediate chamber 610 of the bush 600, In the middle, a pressure control valve V for varying the inclination angle of the swash plate 300 is connected by adjusting the opening degree of the intermediate passage 800.

A communication hole 620 is formed in the bush 600 in order to communicate between the intermediate passage 800 and the intermediate chamber 610. The communication hole 620 is formed between the communication hole 620 and the intermediate chamber 610, A communication groove 210 is formed in the rotary shaft 200 for smooth communication.

The communication passage 700 includes a first passage 710 formed between the cylinder bore 111 and the center bore 112 and a second passage 710 formed between the cylinder bore 111 and the center bore 112, And a second passageway 720 corresponding to the region.

An inlet hole 721 is formed at the side of the bush 600 so that the first passage 710 and the second passage 720 are communicated with each other. An outlet hole 722 is formed to allow the passage 720 and the suction chamber 131 to communicate with each other.

A slide valve 900 is provided in the bushing 600 to intermittently open and close the inflow hole 721. The slide valve 900 includes a spring 910 supported inside the bush 600, And is slidably moved along the axial direction of the bush 600 by being elastically supported by the spring 910 so that a certain region of the intermediate chamber 610 of the bush 600 is divided into the second passage 720, And an opening / closing core (920).

When the intermediate passage 800 communicates with the intermediate chamber 610 of the bush 600, the slide valve 900 is operated by the pressure of the intermediate passage 800 so that the opening / The spring 910 and the opening and closing core 920 are positioned as shown in FIGS.

5 to 7, when the opening and closing core 920 is completely slid in the direction of closing the inlet hole 721 of the bush 600 by the pressure of the intermediate passage 800, It is preferable that a fine gap for oil separation and recovery is formed between the opening and closing core 920 and the inlet hole 721 of the bush 600. When the refrigerant flows along the fine gap, The separated oil can be separated and recovered again into the crank chamber.

3 to 6, the opening / closing core 920 closes the inlet hole 721 of the bush 600 by the pressure of the intermediate passage 800 An orifice 921 may be formed to allow the intermediate passage 800 to communicate with the suction chamber 131 via the second passage 720. Alternatively, 7, when the opening and closing core 920 is completely slid in the direction of closing the inlet hole 721 of the bush 600 by the pressure of the intermediate passage 800, the intermediate passage 800 A third passage 1000 is formed between the first passage 710 and the valve unit 500 so that the first passage 710 can communicate with the suction chamber 131 via the first passage 710, The valve unit 500 includes an orifice 1 for communicating the third passage 1000 with the suction chamber 131, 100 may be formed.

The sensing unit 40 and the sensor 60 may be further provided behind the bushing 600 to reduce fluctuations in the engine speed and to improve the fuel economy by avoiding the torque fluctuation of the compressor.

The sensing unit 40 is supported at one side of a bearing 10 provided at the rear end of the bush 600 via a spring 20 and has a tubular guide protruding from the inner wall of the rear head 130, As shown in Fig. The sensor 60 is inserted into the sensor mounting portion 50 formed on the rear surface of the rear head 130 to sense proximity or separation of the sensing portion 40.

Hereinafter, the operation of the variable displacement swash plate type compressor according to the embodiment of the present invention will be described in detail with reference to FIG. 1 and with reference to FIG. 3 to FIG.

The variable capacity swash plate type compressor according to the present invention compresses the refrigerant sucked from the external refrigerant line through the suction port 133 by the reciprocating pistons and then discharges the refrigerant to the external refrigerant line again, The discharge amount of the refrigerant is adjusted by varying the inclination of the refrigerant.

That is, when the swash plate 300 rotates in the maximum inclined state with respect to the rotary shaft 200, the stroke of each piston 400 becomes the maximum, and the discharge capacity of the refrigerant becomes maximum at this time. On the contrary, when the inclination of the swash plate 300 is 90 DEG, the reciprocation of each piston 400 disappears and the stationary state is maintained in the cylinder bore 111, and the discharge capacity of the refrigerant is minimized.

3, when the swash plate 300 is in an unactuated state erected in the radial direction of the rotary shaft, the refrigerant flows from the crank chamber 121 to the suction chamber 131 using the communication passage 700 When the rotary shaft 200 is driven by centrifugal separation through the gap between the opening and closing core 920 and the inlet hole 721 of the bushing 600, The oil is separated and moved in the direction of the arrow B, and the moved oil is recovered to the crank chamber 121 again.

Since the crank chamber 121 and the suction chamber 131 are communicated with each other through the communication passage 700 at the beginning of operation as described above, the pressure of the crank chamber 121 can be rapidly lowered during the initial operation, The problem of the initial operation delay due to the pressure rise of the crank chamber 121 can be solved.

On the other hand, when the swash plate 300 is inclined at the maximum angle with respect to the radial direction of the rotation axis, as shown in FIG. 4, the same refrigerant flow as that described with reference to FIG. 3 is obtained. That is, the refrigerant is moved in the direction of arrow A from the crank chamber 121 to the suction chamber 131 by using the communication passage 700. At this time, the opening / closing core 920 and the inlet hole The oil contained in the refrigerant is separated and moved in the direction of arrow B by centrifugal separation through the gap between the oil separator 721 and the crank chamber 121,

5, when the swash plate 300 is inclined at an appropriate angle with respect to the radial direction of the rotary shaft and is in a variable operation state, the opening and closing cores (not shown) of the slide valve 900 are closed by the pressure of the intermediate passage 800, The refrigerant flows from the intermediate passage 800 to the middle chamber 610 and the opening and closing core 920 formed in the opening and closing core 920. In this case, The orifice 921 and the second passage 720 in the direction of the arrow C toward the suction chamber 131. In this case, Also in this case, the oil contained in the refrigerant is separated by the centrifugal separation through the gap between the opening / closing core 920 and the inlet hole 721 of the bushing 600 and is moved in the direction of the arrow D, The transferred oil is recovered to the crank chamber 121 again.

On the other hand, when the swash plate 300 is inclined at a minimum angle with respect to the radial direction of the rotary shaft and is in the variable operation state, as shown in FIG. 6, the refrigerant flow is the same as that described with reference to FIG. That is, by the pressure of the intermediate passage 800, the opening / closing core 920 of the slide valve 900 is completely slid in a direction closing the inflow hole 721 of the bush 600, And moves in the direction of arrow C toward the suction chamber 131 via the intermediate chamber 610, the orifice 921 formed in the opening / closing core 920, and the second passage 720 in this order from the passage 800 . Also in this case, the oil contained in the refrigerant is separated by the centrifugal separation through the gap between the opening / closing core 920 and the inlet hole 721 of the bushing 600 and is moved in the direction of the arrow D, The transferred oil is recovered to the crank chamber 121 again.

7, when the swash plate 300 is inclined at an appropriate angle with respect to the radial direction of the rotating shaft and is in a variable operation state, the opening and closing cores (not shown) of the slide valve 900 The refrigerant flows from the intermediate passage 800 to the intermediate chamber 610 through the first passage 710 and the second passage 710 from the middle passage 610. In this case, The third passage 1000 and the orifice 1100 in the direction of the arrow E toward the suction chamber 131 in this order. At this time, the oil contained in the refrigerant is separated by the centrifugal separation through the gap between the opening / closing core 920 and the inlet hole 721 of the bush 600 and is moved in the direction of the arrow F, Is returned to the crank chamber 121 again.

When the swash plate 300 is operated at the maximum inclination in various operating states of the compressor according to the inclination angle of the swash plate 300 as described above, the pressure of the suction chamber 131 through the communication passage 700 is lower than the pressure of the crank chamber 121 So that the excessive change in the pressure in the suction chamber 131 is prevented, and the effect of the pulsation improvement can be sufficiently obtained.

According to the variable capacity swash plate type compressor according to the above-described embodiment of the present invention, it is possible to obtain an effect of improving the pulsation by preventing excessive change in the suction chamber pressure generated at the maximum operation, and sufficient communication between the crank chamber and the suction chamber The initial operation delay problem can be completely improved.

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: Suction port 200:
300: swash plate 400: piston
500: valve unit 600: bush
700: communication passage 800: intermediate passage
900: Slide valve 1000: Third passage

Claims (11)

A cylinder block 110 in which a plurality of cylinder bores 111 and a storage chamber 113 constituting a rear portion of the center bore 112 and the center bore 112 are formed; A front head 120 formed with a chamber 121 and a rear head 130 disposed behind the cylinder block 110 and having a suction chamber 131 and a discharge chamber 132 formed therein, 100);
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 along an inner circumferential surface of the cylinder bore 111 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;
A bush 600 installed to be slidable on the center bore 112 and coupled to the rotary shaft 200 and rotating integrally with the rotary shaft 200 and passing through the valve unit 500;
A communication passage 700 extending from the crank chamber 121 to the suction chamber 131 through an intermediate chamber 610 formed in the bush 600; And
An intermediate passage 800 communicating the discharge chamber 132 and the crank chamber 121 and selectively communicating with the intermediate chamber 610 of the bush 600;
Wherein the compressor is a compressor. The method according to claim 1,
The communication passage 700 includes a first passage 710 formed between the cylinder bore 111 and the center bore 112 and a second passage 710 formed in a certain region of the intermediate chamber 610 And a corresponding second passage (720). The method of claim 2,
An inlet hole 721 for communicating the first passage 710 and the second passage 720 is formed on a side of the bush 600 and an end of the second passage 720 And an outlet hole (722) communicating the suction chamber (131) with the suction chamber (131). The method of claim 3,
Wherein the bush (600) is provided with a slide valve (900) for interrupting the opening and closing of the inlet hole (721). The method of claim 4,
The slide valve 900 includes a spring 910 supported on the inside of the bush 600 and a spring 910 supported on the bush 600 by being elastically supported by the spring 910 and sliding along the axial direction of the bush 600, And an opening / closing core (920) for partitioning a certain region of the intermediate chamber (610) of the first intermediate chamber (610) into the second passage (720). The method of claim 5,
The slide valve 900 is configured such that when the intermediate passage 800 communicates with the intermediate chamber 610 of the bush 600, the opening / closing core 920 is biased by the pressure of the intermediate passage 800, Is configured to slide in a direction to close the inlet hole (721) of the compressor (600). The method of claim 6,
When the opening and closing core 920 is completely slid in the closing direction of the inlet hole 721 of the bush 600 by the pressure of the intermediate passage 800, the opening / closing core 920 and the bush 600 Wherein a fine gap for oil separation and recovery is formed between the compressor housing and the inlet hole of the variable displacement swash plate compressor. The method of claim 7,
When the opening and closing core 920 is completely slid in the direction of closing the inlet hole 721 of the bush 600 by the pressure of the intermediate passage 800, 800) is formed with an orifice (921) for communicating with the suction chamber (131) via the second passage (720). The method of claim 7,
When the opening and closing core 920 is completely slid in the direction of closing the inflow hole 721 of the bush 600 by the pressure of the intermediate passage 800, A third passage 1000 is formed between the first passage 710 and the valve unit 500 so as to communicate with the suction chamber 131 via the first passage 710, And an orifice (1100) communicating with the third passage (1000) and the suction chamber (131) is formed. The method according to any one of claims 1 to 9,
Sectional area of the communicating passage 700 is greater than the cross sectional area of the orifice 510 having a diameter of 2.4 mm which is provided so as to communicate the crank chamber 121 and the suction chamber 131. [ A swash plate compressor. The method according to any one of claims 1 to 9,
The bush 600 is formed with a communication hole 620 for communicating the intermediate passage 800 with the intermediate chamber 610. The communication hole 620 and the intermediate chamber 620 are formed in the rotation shaft 200, And a communication groove (210) is formed for communication.

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