KR101766509B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate type compressor, which is connected to a rear end of a bushing 600 through a main spring S1 and slidably moves in an axial direction together with the bushing 600, A sensing body 710 to which a spring force of the suction chamber S1 and a pressure of the suction chamber 132 act on the other side and a pressure of the discharge chamber 134 acts on the other side, And a sensor 720 installed so as to face the supporting body 710 and sensing the movement of the sensing body 710. According to such a variable displacement swash plate type compressor, it is possible to obtain a torque estimation value which is not substantially different from the actual torque, and thus, the engine torque can be efficiently controlled. Further, since the sensing part is provided in the rear housing without a separate throttle part, the flow rate reduction phenomenon is prevented and the accuracy of the measured value is maintained even at a low flow rate, so that accurate measurement of the refrigerant discharge amount can be achieved.

Description

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

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor capable of reducing variation in engine speed and improving fuel efficiency by detecting torque variation of a 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.

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

A variable capacity swash plate type compressor 10 is provided with a cylinder block 20 forming a part of an outer appearance and a skeleton of the compressor 10. At this time, a center bore 21 is formed through the center of the cylinder block 20, and a rotation shaft 60 is rotatably installed in the center bore 21. [

A plurality of cylinder bores 22 are formed through the cylinder block 20 so as to radially surround the center bore 21. A piston 70 is installed in the cylinder bore 22 so as to reciprocate linearly. At this time, the piston 70 is formed in a cylindrical shape, and the cylinder bore 22 is a cylindrical space corresponding to the cylinder bore 22. The refrigerant in the cylinder bore 22 is compressed by the reciprocating motion of the piston 70.

The front housing 30 is coupled to the front of the cylinder block 20. The front housing 30 faces the cylinder block 20 to form a crank chamber 31 together with the cylinder block 20. [

A pulley 32 connected to an external power source such as an engine is rotatably mounted on the front of the front housing 30 so that the rotary shaft 60 rotates in conjunction with the rotation of the pulley 32.

A rear housing (40) is coupled to the rear of the cylinder block (20). A discharge chamber 41 is formed in the rear housing 40 along a position adjacent to the outer circumferential edge of the rear housing 40 so as to selectively communicate with the cylinder bore 22. The discharge chamber 41 is formed in a radial direction of the discharge chamber 41 A suction chamber 42 is formed at the center of the rear housing 40.

A valve plate 50 is interposed between the cylinder block 20 and the rear housing 40 and the discharge chamber 41 is connected to the cylinder bore 22 through the discharge port 51 formed in the valve plate 50. [ And the suction chamber 42 communicates with the cylinder bore 22 through the suction port 52 of the valve plate 50. [

The swash plate 61 is provided on the rotary shaft 60. The swash plate 61 is connected to the respective pistons 70 by a shoe 62 provided along the rim of the swash plate 61. By the rotation of the swash plate 61, (70) reciprocates linearly in the cylinder bore (22).

The angle of the swash plate 61 relative to the rotary shaft 60 is variable so that the refrigerant discharge amount of the compressor 10 can be adjusted. To this end, the discharge chamber 41 and the crank chamber 31 are communicated with each other Is controlled by a pressure control valve (not shown).

On the other hand, in the case of the variable displacement swash plate type compressor, since the compression load variation of the compressor is connected to the engine load variation, it is necessary to detect the torque variation of the compressor and to control the engine rotation speed in consideration of the detection torque variation.

Fig. 2 shows a flow rate detecting apparatus disclosed in Japanese Unexamined Patent Application Publication No. 2007-303416 as a conventional technique for detecting the torque fluctuation of such a compressor.

The flow rate detecting device shown in Fig. 2 is provided in a discharge flange 2 serving as a flange member joined to the outside of the cylinder block 1, and includes a movable portion 3 accommodated in the discharge flange 2, A coil spring 4 for resiliently supporting the movable body 3 and a magnetic sensor 5 as a detection sensor fixed to the surface of the discharge flange 2. The coil spring 4 has a body 3,

At this time, in the process of moving the movable body 3 up and down by the pressure difference between the high pressure chamber 6a and the low pressure chamber 6b, the magnetic flux density change of the magnet 3a is detected by the magnetic sensor 5, It is to be appreciated that the amplifier 7 which receives the detection value from the magnetic sensor 5 via the connection line 7a calculates the discharge capacity of the compressor on the basis of the flow rate data and performs the feedback control of the pressure regulating valve, As shown in FIG.

However, in the conventional flow rate detecting device as described above, there is a problem that the flow rate is reduced by forming a separate throttle portion between the high-pressure chamber and the low-pressure chamber for installing the movable body. When the throttle portion is of a fixed size, There is a problem that the accuracy of the measured value is decreased.

SUMMARY OF THE INVENTION The present invention is conceived to solve the problems as described above, and it is an object of the present invention to provide a torque estimation apparatus which can obtain a torque estimation value approximate to an actual torque even when an air conditioning apparatus starts abruptly, And to provide a variable displacement swash plate type compressor capable of reducing the variation in the rotational speed and improving the fuel economy.

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, And a rear head which is disposed behind the cylinder block and is formed with a suction port, a suction chamber, a discharge port, and a discharge chamber, and which forms an outer body; and a housing which is rotatably mounted through one side of the housing A swash plate installed on the rotary shaft and integrally rotated with the rotary shaft so as to be able to vary the angle with respect to the rotary shaft so that the refrigerant discharge amount can be adjusted; And a piston reciprocatingly reciprocates along an inner circumferential surface of the cylinder bore by rotation of the swash plate A plurality of pistons for compressing the refrigerant sucked through the suction port and discharging the compressed refrigerant to the discharge chamber, a valve unit installed between the cylinder block and the rear head for sucking and discharging the refrigerant, A bush which is movably installed and which is coupled to the rotary shaft and penetrates through the valve unit; a sensing body which is connected to the rear end of the bush by a main spring to slide in the axial direction together with the bush; And a sensor for sensing the movement of the sensing element. The spring force of the main spring and the pressure of the suction chamber act on one side of the sensing element, And the pressure of the discharge chamber acts on the other side of the sensing body.

The bush is preferably coupled to the rotation shaft so as to rotate integrally with the rotation shaft.

Preferably, the bush is coupled to the rotation shaft so as not to be interlocked with the rotation of the rotation shaft, but to move in an axial direction interlocked with the angle change of the swash plate.

Wherein the sensor body is inserted into a sensor mounting portion formed on a rear surface of the rear head so that the sensor body can be positioned close to or spaced apart from the sensor body, .

It is preferable that the pressure of the discharge chamber is depressurized by the decompression means and then acts on the other side of the sensing body.

It is preferable that the sensing element is made of a magnetic material, and the sensor is a magnetic sensor for detecting a change in the magnetic flux density of the sensing element.

Preferably, the sensing member is supported on the inner side of the guide portion via an auxiliary spring, and the space in which the auxiliary spring is located communicates with the discharge chamber.

It is preferable that the elastic modulus of the main spring is greater than or equal to the elastic modulus of the auxiliary spring.

Wherein the sensing member is slidably mounted on an inner side of a tubular guide portion protruding from an inner wall of the rear head and the sensor is formed to be embedded in the rear side of the rear head from the rear side of the rear head, It is preferable that the sensor unit is inserted into the sensor mounting unit to sense the movement of the sensing unit in the lateral direction.

It is preferable that the pressure of the discharge chamber is depressurized by the decompression means and then acts on the other side of the sensing body.

It is preferable that the sensing element is made of a magnetic material, and the sensor is a magnetic sensor for detecting a change in the magnetic flux density of the sensing element.

Preferably, the sensing member is supported on the inner side of the guide portion via an auxiliary spring, and the space in which the auxiliary spring is located communicates with the discharge chamber.

It is preferable that the elastic modulus of the main spring is greater than or equal to the elastic modulus of the auxiliary spring.

According to the variable displacement swash plate type compressor as described above, it is possible to obtain a torque estimation value that is not substantially different from the actual torque, and thus, the engine torque can be efficiently controlled. Further, since the sensing part is provided in the rear housing without a separate throttle part, the flow rate reduction phenomenon is prevented and the accuracy of the measured value is maintained even at a low flow rate, so that accurate measurement of the refrigerant discharge amount can be achieved.

1 is a sectional view of a general variable displacement swash plate type compressor.
2 is a block diagram of a conventional flow rate detecting device.
3 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a first embodiment of the present invention.
4 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a second embodiment of the present invention.
5 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a third embodiment of the present invention.

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 displacement swash plate type compressor according to a first embodiment of the present invention, FIG. 4 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a second embodiment of the present invention, 7 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a third embodiment of the present invention.

First, a variable displacement swash plate compressor according to a first embodiment of the present invention will be described with reference to FIG. The variable displacement swash plate compressor according to the first 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, A bush 600, and a flow rate detecting mechanism 700.

The housing 100 includes a cylinder block 110, a front head 121, and a rear head 130, which constitute 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 121 and the rear head 130 are cylinders for closing the open and close ends of the upper cylinder block 110. The front head 121 is opened toward the cylinder block 110 to open the rear end of the swash plate 300 And the slope adjusting mechanism 320 can be received while securing the crank chamber 120 which is the rotating space.

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 131 and a discharge port (not shown), which are connected to the suction chamber 132 and the discharge chamber 134, respectively, are formed on an outer wall surface of the rear head 130.

The rotary shaft 200 is rotatably mounted on one side of the housing 100, that is, the center of the front head 121, as a means for transmitting the rotational driving force of the external driving source to the inside of the compressor. A rotary pulley is coupled to one end of the rotary shaft 200 exposed to the outside of the front head 121. An external rotary driving force is transmitted to the rotary shaft 200 through the rotary pulley, .

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.

3 is a variable displacement swash plate type compressor. The swash plate compressor 300 is installed such that the inclination angle of the swash plate 300 is variable. When the inclination of the swash plate 300 relative to the rotation axis 200 is 90 degrees, The reciprocating movement of the piston 400 disappears, so that the rotating shaft 200 idles. 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 adjustment of the inclination angle of the swash plate 300 is performed by a pressure adjusting valve V installed at one side of the rear housing 130 so as to adjust the opening degree of the flow passage communicating with the discharge chamber 134 and the crank chamber 120 .

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 131 of the rear head 130, And discharges the refrigerant sucked into the discharge chamber (134) of the rear head (130).

On the other hand, the refrigerant discharged to the discharge chamber 134 is discharged to the external refrigerant line through the discharge port 133 via the discharge flow path 136 formed at one side of the discharge chamber 134.

The valve unit 500 controls the suction and discharge of the refrigerant so that the refrigerant can flow between the front head 121 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 and coupled to the rotation shaft 200 to rotate together 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. At this time, the bushing 600 may have a structure for pressure control and oil separation.

The flow rate detecting mechanism 700 is configured to detect a fluctuation in torque of the compressor to reduce the engine speed variation and to improve fuel economy. The flow rate detecting mechanism 700 is connected to the rear end of the bush 600 via a main spring S1, A sensing unit 710 slidably moving in the axial direction together with the sensing unit 600 and a sensing unit 710 disposed on one side of the sensing unit 710 to detect proximity or separation of the sensing unit 710, And a sensor 720 for sensing the position of the object.

The sensor 720 detects the movement of the sensing element 710. For example, the sensing element 710 may be made of a magnetic material, and the sensor 720 may sense the proximity of the sensing element 710, And a magnetic sensor for detecting a magnetic flux density which changes when the magnetic sensor is separated from the magnetic sensor.

The sensing unit 710 is slidably installed on the inner side of a tubular guide unit 730 protruding from the inner wall of the rear head 130 and the sensor 720 is mounted on the rear head 130 And the sensor mounting portion 740 is formed on the rear surface of the sensor mounting portion 740.

One side of the sensing body 710 is connected to one side of a bearing 610 provided at a rear end of the bush 600 via a main spring S1. Therefore, as the bush 600 moves in the axial direction, the sensing element 710 connected via the main spring S1 also moves in the same axial direction as the bush 600. [

The sensing element 710 may be supported by the rear head 130 via the auxiliary spring S2 inside the guide part 730. The sensing element 710 may be supported by the auxiliary spring S2, It is possible to reliably prevent the sensing element 710 from suddenly moving in the axial direction.

It is preferable that the elastic modulus of the main spring S1 is greater than or equal to the elastic modulus of the auxiliary spring S2, The compression deformation of the auxiliary spring S2 can be performed first when the sensing element 710 approaches the sensor 720 so that the measurement of the magnetic flux density by the sensor 720 can be performed smoothly do.

A spring force of the main spring S1 connected to the bush 600 and a pressure of the suction chamber 132 act on one side of the sensing member 710 and a pressure The pressure in the discharge chamber 134 is applied and the pressure in the discharge chamber 134 acts on the other side of the sensing body 620. In order to allow the pressure in the discharge chamber 134 to act on the other side of the sensing body 620, A communication path 135 is formed to communicate the other side of the sensing element 710 and the space in which the auxiliary spring S2 is located. At this time, the communicating path 135 may be further provided with a depressurizing means 750 for depressurizing the pressure in the discharge chamber 134, and the depressurizing means 750 may be provided on the other side of the depressing body 710 It is possible to prevent the excessive pressure from acting and to reduce the sudden movement of the sensing element 710.

Meanwhile, in the course of operation of the variable capacity swash plate type compressor according to the first embodiment of the present invention, the sensing body 710 is interlocked with the movement of the bush 600 and the suction chamber 132 And the change in magnetic flux density measured by the sensor 720 in accordance with the axial movement of the sensing element 710 is transmitted to one side of the compressor (Not shown), and the control unit controls the pressure control valve V by calculating the discharge amount of the refrigerant and the torque of the compressor based on the measured value, and the control unit Feedback control is performed so that the engine speed is controlled optimally.

Since the torque of the compressor is inversely proportional to the output value of the sensor 720 and is proportional to the inclination angle of the swash plate 300 and the pressure difference between the discharge chamber 134 and the suction chamber 132, The torque fluctuation can be predicted more precisely.

Hereinafter, a variable displacement swash plate compressor according to a second embodiment of the present invention will be described with reference to FIG. The variable displacement swash plate type compressor according to the second embodiment of the present invention has the same overall structure as the variable displacement swash plate type compressor according to the first embodiment of the present invention described above. That is, the housing 100 includes the housing 100, the rotating shaft 200, the swash plate 300, the plurality of pistons 400, the valve unit 500, the bush 600, and the flow rate detecting mechanism 700 Is the same. However, there is a difference between the installation structure between the bush 600 and the rotary shaft 200 and the interlocking operation with respect to the movement of the rotary shaft 200.

That is, in the bush 600 applied to the swash plate compressor according to the second embodiment of the present invention, as shown in FIG. 4, the bush 600 is coupled to the rotating shaft 200 through the thrust bearing 800. Accordingly, the bush 600 is not interlocked with the rotation of the rotary shaft 200, but moves in the axial direction in conjunction with the change of the angle of the swash plate 300.

The movement of the bushing 600 can be limited only in the axial direction due to the difference in the installation structure of the bushing 600 on the rotary shaft 200, A more accurate detection of magnetic flux density can be achieved.

In the course of the operation of the variable capacity swash plate type compressor according to the second embodiment of the present invention, the sensing body 710 is interlocked with the movement of the bush 600, The change in the magnetic flux density measured by the sensor 720 in accordance with the axial movement of the sensing element 710 is provided on one side of the compressor (Not shown), and the control unit calculates the discharge amount of the refrigerant and the torque of the compressor based on the measured value to control the pressure control valve (V), and performs feedback control for the engine control means So that the engine speed is controlled optimally.

Since the torque of the compressor is inversely proportional to the output value of the sensor 720 and is proportional to the inclination angle of the swash plate 300 and the pressure difference between the discharge chamber 134 and the suction chamber 132, The torque fluctuation can be predicted more precisely.

Hereinafter, a variable displacement swash plate compressor according to a third embodiment of the present invention will be described with reference to FIG. The variable displacement swash plate type compressor according to the third embodiment of the present invention is the same in overall construction as the variable displacement swash plate type compressor according to the first embodiment of the present invention described above. That is, the housing 100 includes the housing 100, the rotating shaft 200, the swash plate 300, the plurality of pistons 400, the valve unit 500, the bush 600, and the flow rate detecting mechanism 700 Is the same. However, there is a difference between the installation structure of the sensor 720 and the sensing direction with respect to the sensing element 710.

That is, the sensor 720 applied to the swash plate type compressor according to the third embodiment of the present invention is embedded into the rear head 130 from the rear surface of the rear head 130, Type sensor mounting portion 740 positioned in the insertion-type sensor mounting portion 740 to sense the movement of the sensing body 710 in the lateral direction.

The movement of the sensing element 710 can be more accurately sensed due to the difference between the installation structure of the sensor 720 and the sense direction sensing the movement of the sensing element 710 from the lateral direction, Detection can be performed.

In the course of operation of the variable capacity swash plate type compressor according to the third embodiment of the present invention, the sensing body 710 is interlocked with the movement of the bush 600, The sensor 720 moves along the axial direction of the sensing element 710 in the axial direction in response to the pressure and the pressure of the discharge chamber 134. When the sensing element 720 is moved in the axial direction of the sensing element 710 in the lateral direction of the sensing element 710, And the control unit calculates the discharge amount of the refrigerant and the torque of the compressor based on the measured value, and the control unit calculates the discharge amount of the refrigerant and the torque of the compressor Controls the pressure regulating valve (V), and performs feedback control on the engine control means (not shown) so that the engine speed is controlled optimally.

Since the torque of the compressor is inversely proportional to the output value of the sensor 720 and is proportional to the inclination angle of the swash plate 300 and the pressure difference between the discharge chamber 134 and the suction chamber 132, The torque fluctuation can be predicted more precisely.

According to the variable capacity swash plate type compressor according to the above-described embodiment of the present invention, it is possible to obtain a torque estimation value that is not substantially different from the actual torque, and thus the engine torque can be efficiently controlled. Further, since the sensing part is provided in the rear housing without a separate throttle part, the flow rate reduction phenomenon is prevented and the accuracy of the measured value is maintained even at a low flow rate, so that accurate measurement of the refrigerant discharge amount can be achieved.

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
120: crank chamber 121: front head
130: rear head 131: suction port
132: suction chamber 133: discharge port
134: Discharge chamber 135:
200: rotating shaft 300: swash plate
400: Piston 500: Valve unit
600: Bush 700: Flow detection mechanism
710: Detector 720: Sensor
740: Insertion type sensor mounting part 800: Thrust bearing

Claims (13)

A cylinder block 110 in which a plurality of cylinder bores 111 and a center bore 112 are formed, a front head 121 disposed in front of the cylinder block 110 and formed with a crank chamber 120, A housing 100 disposed at the rear of the housing 100 and including a suction port 131, a suction chamber 132, a discharge port 133 and a discharge chamber 134,
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;
And is linearly reciprocated along the inner circumferential surface of the cylinder bore 111 by the rotation of the swash plate 300 so as to be reciprocated relative to the edge of the swash plate 300, A plurality of pistons (400) for compressing the refrigerant and discharging the compressed refrigerant to the discharge chamber (134);
A valve unit (500) installed between the cylinder block (110) and the rear head (130) to suck and discharge the refrigerant;
A bush 600 slidably mounted on the center bore 112 and coupled to the rotary shaft 200 and passing through the valve unit 500; And
A sensing member 710 connected to the rear end of the bushing 600 through a main spring S1 to slide in the axial direction together with the bushing 600; And a sensor (720) installed to face the sensing unit (710) and sensing movement of the sensing unit (710)
The spring force of the main spring S1 and the pressure of the suction chamber 132 act on one side of the sensing body 710 and the pressure of the discharge chamber 134 acts on the other side of the sensing body 710 Wherein the compressor is a variable displacement type swash plate type compressor. The method according to claim 1,
Wherein the bushing (600) is slidably coupled to the rotary shaft (200), and is coupled to rotate with the rotary shaft (200). The method according to claim 1,
The bush 600 is coupled to the rotation shaft 200 so as not to be interlocked with the rotation of the rotation shaft 200 but to move in an axial direction interlocked with a change in angle of the swash plate 300 Variable displacement swash plate compressor. The method according to claim 2 or 3,
The sensing unit 710 is slidably installed inside a tubular guide unit 730 protruding from the inner wall of the rear head 130 and the sensor 720 is mounted on the inner surface of the rear head 130 Is inserted into the sensor mounting portion (740) formed on the rear surface to sense proximity or spacing of the sensing member (710). The method of claim 4,
Wherein the pressure of the discharge chamber (134) is reduced by the pressure reducing means (750) and then acts on the other side of the sensing body (710). The method of claim 5,
Wherein the sensing body (710) is made of a magnetic material, and the sensor (720) is a magnetic sensor for detecting a change in magnetic flux density of the sensing body (710). The method of claim 6,
The sensing member 710 is supported on the inner side of the guide portion 730 via a support spring S2 and a space in which the auxiliary spring S2 is disposed communicates with the discharge chamber 134 A variable displacement swash plate type compressor. The method of claim 7,
Wherein the elastic modulus of the main spring (S1) is greater than or equal to the elastic modulus of the auxiliary spring (S2). The method of claim 2,
The sensing unit 710 is slidably installed inside a tubular guide unit 730 protruding from the inner wall of the rear head 130 and the sensor 720 is mounted on the inner surface of the rear head 130 Inserted into the inserting sensor mounting portion 740 located at the side of the guide portion 730 so as to be inserted into the rear head 130 from the rear and sense the movement of the sensing body 710 in the lateral direction A variable displacement swash plate type compressor. The method of claim 9,
Wherein the pressure of the discharge chamber (134) is reduced by the pressure reducing means (750) and then acts on the other side of the sensing body (710). The method of claim 10,
Wherein the sensing body (710) is made of a magnetic material, and the sensor (720) is a magnetic sensor for detecting a change in magnetic flux density of the sensing body (710). The method of claim 11,
The sensing member 710 is supported on the inner side of the guide portion 730 via a support spring S2 and a space in which the auxiliary spring S2 is disposed communicates with the discharge chamber 134 A variable displacement swash plate type compressor. The method of claim 12,
Wherein the elastic modulus of the main spring (S1) is greater than or equal to the elastic modulus of the auxiliary spring (S2).

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