KR20140058816A - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a compressor having a swash plate of a variable capacity capable of obtaining an estimated torque value approximate to a real value when initiating an air conditioner or inducing an abrupt torque change such as turning on or off the air conditioner. According to an embodiment of the present invention, provided is a compressor having a swash plate of a variable capacity which is prepared with a sensor unit on the rear side of a bush, moving toward the direction of a rotation shaft. The magnetic flux density change of the sensor unit can be detected by a sensor to calculate the inclination angle of the swash plate or namely the torque of the compressor.

Description

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

The present invention relates to a swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor capable of reducing variation in engine speed and improving fuel efficiency by detecting torque variation of a compressor.

Generally, compressors for compressing refrigerant in a vehicle cooling system have been developed in various forms. Such a compressor includes a reciprocating type in which compression is performed while reciprocating the refrigerant, There is a rotary that performs.

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

On the other hand, as the swash plate type compressor, there are a fixed displacement type in which the installation angle of the swash plate is fixed and a variable displacement type in which the discharge displacement can be changed by changing the inclination angle of the swash plate.

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 Patent Laid-Open No. 2007-303416 (Patent Document 1) for detecting the torque fluctuation of the 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 in that the accuracy of the measured value is decreased.

Patent Document 1: Japanese Unexamined Patent Application Publication No. 2007-303416 (published on November 22, 2007)

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.

According to a preferred embodiment of the present invention, a cylinder block having a center bore formed at a center thereof and having a plurality of cylinder bores spaced apart from each other in a circumferential direction on a radially outer side of the center bore; A front housing coupled to the front of the cylinder block and having a crank chamber formed therein; A rear housing coupled to the rear of the cylinder block and having a suction chamber and a discharge chamber formed therein; A bush installed slidably on the center bore; A sensing unit installed at a rear end side of the bush and movable together with the bush; A rotating shaft inserted into the hollow of the bushing through the front housing and rotating integrally with the bush; A swash plate coupled to the rotary shaft through a central portion thereof so as to rotate integrally with the rotary shaft, and slantedly installed in the crank chamber; A plurality of pistons coupled to one side of the swash plate and reciprocating linearly by rotation of the swash plate; And a sensor installed on one side of the rear housing so as to face the sensing unit and sensing a proximity or separation of the sensing unit.

Here, the sensing unit may be a magnetic body, and the sensor may be a magnetic sensor that detects a change in magnetic flux density of the sensing unit.

At this time, the sensing unit may be provided in the hollow of the bush or on the rear surface of the bush.

The sensing unit may be elastically supported by a pair of elastic members facing each other in a space between a rear end of the bush and an inner wall of the rear housing.

At this time, a first elastic member is interposed between the rear end of the bush and the sensing unit, and a second elastic member is interposed between the sensing unit and the inner wall of the rear housing.

At this time, it is preferable that one end of the first elastic member is supported on one side of a race of the bearing installed at the rear end of the bush.

According to the variable capacity swash plate type compressor according to the preferred 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 portion is provided in the rear housing without a separate throttle portion, the refrigerant discharge amount can be accurately measured.

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 and 4 are sectional views of a variable displacement swash plate type compressor according to a first embodiment of the present invention.
5 and 6 are partial cross-sectional schematic views of a variable displacement swash plate type compressor according to a second embodiment of the present invention.

Hereinafter, preferred embodiments of a variable displacement swash plate type compressor according to an embodiment of the present invention will be described with reference to the accompanying drawings. In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation.

In addition, the terms described below are defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

In addition, the following embodiments are not intended to limit the scope of the present invention, but merely as exemplifications of the constituent elements set forth in the claims of the present invention, and are included in technical ideas throughout the specification of the present invention, Embodiments that include components replaceable as equivalents in the elements may be included within the scope of the present invention.

First Embodiment

3 and 4 are sectional views of a variable capacity swash plate type compressor according to a first embodiment of the present invention, FIG. 3 is a sectional view when the swash plate has a maximum inclination angle, and FIG. 4 is a cross- Sectional view.

3 and 4, a variable capacity swash plate type compressor 100 according to an exemplary embodiment of the present invention includes a housing 200, a rotary shaft 400, a swash plate 500 , And a plurality of pistons (600).

3 and 4, the housing 200 includes a cylinder block 210, a front housing 220, and a rear housing 230. As shown in FIGS.

At this time, the cylinder block 210 is a cylinder disposed at an intermediate portion in the longitudinal direction of the housing 200, and includes a center bore 211 capable of receiving the rotation shaft 400 therein, as well as a center bore 211 A cylinder bore 212 capable of accommodating a plurality of pistons 600 is formed.

The front housing 220 and the rear housing 230 are coupled to each other so as to close the open ends at the front and rear sides of the cylinder block 210. The front housing 220 has a rear end opened toward the cylinder block 210, So as to accommodate the inclination adjusting mechanism 222 for adjusting the inclination angle of the swash plate 500 while securing the crank chamber 221 which is the rotating space of the swash plate 500. [

The rear housing 230 has a front end opened toward the cylinder block 210 and includes a suction chamber 231 for supplying refrigerant to the cylinder bore 212 of the cylinder block 210 during an intake stroke, A discharge chamber 232 through which the compressed refrigerant in the cylinder bore 212 is discharged during the compression stroke is formed.

At this time, a valve plate 240 interposed between the cylinder block 210 and the rear housing 230 is formed with a suction port 241 and a discharge port 242. The suction port 241 is connected to the cylinder bore 212, And the discharge port 242 makes the cylinder bore 212 and the discharge chamber 232 communicate with each other.

The rotating shaft 400 is a means for transmitting the rotational driving force of an external driving source such as an engine to the inside of the compressor 100. The rotating shaft 400, which is exposed to the outside of the front housing 220, And an external rotating driving force is transmitted to the rotating shaft 400 through the rotating pulley 410 so that the rotating shaft 400 rotates.

The front end of the rotary shaft 400 is rotatably supported by a radial bearing 223 through one side of the housing 200, that is, the central portion of the front housing 220, The bush 300 is inserted into the hollow of the bush 300 rotatably installed in the bush 211 to support the radial load of the rotary shaft 400 by the bush 300.

A bush 300 is rotatably coupled to one side of the bush 300 and a bush 300 is rotatably coupled to a rotary shaft 400 to accommodate the inclination angle displacement of the swash plate 500 relative to the rotary shaft 400. [ As shown in Fig.

That is, when the swash plate 500 is displaced at the maximum inclination angle, the bush 300 advances toward the front housing 220, and when the swash plate 500 is displaced at the minimum inclination angle, the bush 300 is moved backward toward the rear housing 230 .

The swash plate 500 is a means for converting the rotational driving force of the rotational shaft 400 into a reciprocating linear motion of the piston 600. The swash plate 500 is pivotally mounted on the rotational shaft 400, .

At this time, a plurality of shoes 510 are installed along the circumferential direction at the rim of the swash plate 500, and the plurality of pistons 600 are slidably supported by the shoe 510 through the shoe 510.

For example, when the slope of the swash plate 500 relative to the rotary shaft 400 is 90 °, the slash angle of the swash plate 500 with respect to the rotary shaft 400 is changed so that the refrigerant discharge capacity can be adjusted. The reciprocating motion of the piston 600 disappears, so that the rotation shaft 400 idles.

Alternatively, when the swash plate 500 is inclined with respect to the rotary shaft 400, the piston 600 reciprocates in the cylinder bore 212 and compresses the refrigerant. The adjustment of the inclination angle of the swash plate 500 is controlled by a pressure control valve (not shown) installed at one side of the rear housing 230 to adjust the opening degree of a flow passage (not shown) communicating with the discharge chamber 232 and the crank chamber 221 Time).

The plurality of pistons 600 are means for compressing the refrigerant while reciprocating in the cylinder bore 212 by the swash plate 500 and as shown in Figures 3 and 4, And is linearly reciprocated along the inner circumferential surface of the cylinder bore 212 of the cylinder block 210 by the rotation of the swash plate 500, 212 are compressed.

At this time, the refrigerant compressed by the cylinder bore 212 by the piston 600 is discharged to the discharge chamber 232 of the rear housing 230 and then supplied to the external cooling system through the discharge port (not shown).

Since the bush 300 moves according to the change of the inclination angle of the swash plate 500, the compressor 100 according to the embodiment of the present invention detects the inclination angle of the swash plate 500, The torque of the engine 100 can be calculated.

For this purpose, a sensing unit 310 is provided at the rear end of the bush 300, and a sensor 233 is provided at one side of the rear housing 230 so as to face the sensing unit 310. The sensor 233 detects the movement of the sensing unit 310. For example, the sensing unit 310 is made of a magnetic material, and the sensor 233 senses the movement of the sensing unit 310, And a magnetic sensor for detecting the magnetic flux density.

3 and 4, the sensing unit 310 is provided at the rear inner end of the bushing 300 and the sensor 233 is installed at the outer side of the rear housing 230. However, The sensing unit 310 may be provided on the rear surface of the bush 300 or the sensor 233 may be provided on the inner wall of the rear housing 230.

At this time, the change value of the magnetic flux density measured by the sensor 233 according to the movement of the sensing unit 310 is transmitted to a separate control unit (not shown) provided at one side of the compressor 100, Calculates the discharge amount of the refrigerant and the torque of the compressor 100, controls the pressure regulating valve, and performs feedback control on the engine control means (not shown) so that the engine speed is controlled optimally.

Second Embodiment

5 and 6 are partial cross-sectional views of a variable capacity swash plate type compressor according to a second embodiment of the present invention, wherein FIG. 5 is a sectional view when the swash plate has a maximum inclination angle, Fig.

The compressor 100 'according to the second embodiment of the present invention is entirely similar to the compressor 100 of the first embodiment described above except that the sensing unit 310' is spaced apart from the rear of the bush 300, And it is installed so as to be elastically supported by a member.

Therefore, the same reference numerals are assigned to the same components as those of the above-described first embodiment, and redundant description of the components already described in the first embodiment will be omitted.

5 and 6, in the compressor 100 'according to the second embodiment of the present invention, the sensing unit 310' is installed in the suction chamber 231 at a distance behind the bush 300 do.

A first elastic member 320 is interposed between the rear end of the bush 300 and the sensing unit 310 'and a second elastic member 330 is interposed between the sensing unit 310' and the inner wall of the rear housing 230. And the sensing portion 310 'is elastically supported by the first and second elastic members 320 and 330.

It is preferable that the first elastic member 320 and the second elastic member 330 are formed of coil springs and that the sensing unit 310 'is moved toward or away from the sensor 233 as the bush 300 moves, The elastic modulus of the first elastic member 320 is preferably equal to or greater than the elastic modulus of the second elastic member 330.

6, when the inclination angle of the swash plate 500 is minimum, the bush 300 moves in the direction of the sensor 233. At this time, the compressive deformation of the second elastic member 330 is advanced first, The portion 310 'is moved toward the sensor 233.

As described above, when the sensing unit 310 'is elastically supported by the first elastic member 320 and the second elastic member 330 so as to be spaced apart from the rear end of the bush 300, The moving distance of the part 310 'is reduced, and the output of the sensor 233 is increased, so that the stability of the output can be obtained.

The bush 300 moves in the axial direction of the rotary shaft 400 in accordance with the inclination angle of the swash plate 500 and integrally rotates together with the rotary shaft 400, It is preferable that a thrust means is provided at the rear end of the bush 300 so that one end of the member 320 can be stably supported at the rear end of the bush 300.

5 and 6 show one example of such a thrust means. One end of the first elastic member 320 is connected to the race 340 of the bearing 340, and a bearing 340 is provided at the rear end of the bush 300. [ So that the rotational force of the bush 300 can be prevented from being transmitted to the first elastic member 320.

An insertion groove 311 'is formed in the front and rear surfaces of the sensing unit 310' so that the other end of the first elastic member 320 and one end of the second elastic member 330 can be inserted and supported, respectively. One end of the first elastic member 320 can be inserted and supported by forming an insertion groove on the rear surface of the race 341 and inserted into the inner wall of the rear housing 230 for supporting the other end of the second elastic member 330 It is of course possible to form a groove.

In order to prevent separation of the first elastic member 320, a tubular first guide portion 342 surrounding the periphery of the first elastic member may be formed on the rear surface of the race 341, The second guide portion 234 may be formed to protrude from the inner wall of the rear housing 230 so as to prevent separation of the second elastic member 330 and guide the moving direction of the second elastic member 330. In addition, the sensor 233 may be inserted into the mounting groove 236 of the sensor mounting portion 235 formed on the rear surface of the rear housing 230.

100, 100 ': compressor 200: housing
210: Cylinder block 211: Center bore
212: cylinder bore 220: front housing
221: crank chamber 230: rear housing
231: suction chamber 232: discharge chamber
233: Sensor 300: Bush
310, 310 ': sensing unit 320: first elastic member
330: second elastic member 340: bearing
341: race 400: rotating shaft
410: rotating pulley 500: swash plate
510: Shoe 600: Piston

Claims (7)

A cylinder block 210 in which a center bore 211 is formed at a center and a plurality of cylinder bores 212 are formed at a radially outer side of the center bore 211 in a circumferential direction and spaced apart from each other;
A front housing 220 coupled to the front of the cylinder block 210 and having a crank chamber 221 formed therein;
A rear housing (230) coupled to the rear of the cylinder block (210) and having a suction chamber (231) and a discharge chamber (232) formed therein;
A bush 300 slidably mounted on the center bore 211;
A sensing unit 310, 310 'installed at a rear end side of the bush 300 and movable together with the bush 300;
A rotating shaft 400 inserted into the hollow of the bushing 300 through the front housing 220 and rotating integrally with the bushing 300;
A swash plate 500 coupled to the rotation shaft 400 through a central portion thereof so as to rotate integrally with the rotation shaft 400 and slantly installed in the crank chamber 221;
A plurality of pistons (600) coupled to one side of the swash plate (500) and linearly reciprocating by rotation of the swash plate (500); And
And a sensor (233) installed on one side of the rear housing (230) so as to face the sensing unit (310) and sensing proximity or separation of the sensing unit (310).
The method according to claim 1,
Wherein the sensing units (310, 310 ') are made of a magnetic material, and the sensor (233) is a magnetic sensor for detecting a magnetic flux density change of the sensing units (310, 310').
[3] The apparatus of claim 1, wherein the sensing unit (310)
Wherein the bush (300) is provided in the hollow of the bush (300) or on the rear surface of the bush (300).
[3] The apparatus of claim 1, wherein the sensing unit (310 '
Is elastically supported by a pair of elastic members (320, 330) opposed to each other in a space between a rear end of the bush (300) and an inner wall of the rear housing (230).
The method of claim 4,
A first elastic member 320 is interposed between the rear end of the bush 300 and the sensing unit 310 'and a second elastic member 320 is interposed between the sensing unit 310' and the inner wall of the rear housing 230. [ (330) is interposed between the compressor and the compressor.
The method of claim 5,
Wherein one end of the first elastic member is supported at one side of a race of the bearing installed at a rear end of the bush.
The method of claim 5,
Wherein the elastic modulus of the first elastic member (320) is greater than or equal to the elastic modulus of the second elastic member (330).

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