KR101915969B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate type compressor and includes an intermediate passage 600 for communicating the discharge chamber 132 with the crank chamber 121 and a passage for connecting the suction port 133 to the suction chamber 131 And a communication passage (700) for communicating the crank chamber (135) and the crank chamber (121). 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 600 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 600, 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 600.

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 600 is formed such that a portion 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 The oil is returned to the crank chamber 121 through the supply passage 600.

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 problems, and it is an object of the present invention to provide a crankcase and a suction chamber which can prevent an excessive change in 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, And a rear head disposed behind the cylinder block and formed with a suction chamber, a discharge chamber, and a suction port, a rotating shaft rotatably mounted through one side of the housing, A swash plate installed on the rotating shaft and integrally rotating with the rotating shaft so as to be able to vary the angle with respect to the rotating shaft so that the refrigerant discharge amount can be adjusted; and a swash plate connected to the swash plate, A plurality of pistons that linearly reciprocate along the cylinder block and the rear head, And a communication passage provided between the discharge passage and the crank chamber for communicating the crank chamber with a channel connecting the suction port to the suction chamber. .

The communication passage is preferably provided with a spool valve for interrupting the flow of the refrigerant from the duct to the crank chamber.

Preferably, the spool valve includes a case installed in the cylinder block, a spring supported inside the case, and an opening / closing core elastically supported and slidingly moved by the spring.

The spool valve is further formed with a first passage communicating the spool valve and the intermediate passage, and the spool valve is configured to slide in the direction in which the opening and closing core closes the communication passage by the pressure of the intermediate passage.

And a second passage communicating with the spool valve and the bush is further formed on the rotation shaft, the bush passing through the valve unit and rotating integrally with the rotation shaft is disposed slidably on the center bore, And the spool valve is configured to slide in the direction in which the opening / closing core closes the communication path by the pressure of the intermediate chamber formed inside the bush.

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, in which the applied spool valve is opened.
FIG. 4 is a longitudinal sectional view of a variable displacement swash plate type compressor according to an embodiment of the present invention, in which the applied spool valve is closed; FIG.
5 is a longitudinal sectional view showing another example of the variable displacement swash plate type compressor according to the embodiment of the present invention, in which the applied spool valve is opened.

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 vertical sectional view of a variable capacity swash plate type compressor according to an embodiment of the present invention, in which the applied spool valve is opened, and FIG. 4 is a cross sectional view of a variable capacity swash plate type compressor according to an embodiment of the present invention. 5 is a vertical sectional view showing another example of the variable capacity swash plate type compressor according to the embodiment of the present invention, in which the applied spool valve is opened FIG.

3 to 5, a variable capacity swash plate type compressor according to an embodiment of the present invention will be described with reference to FIG. 1 in detail with respect to the same structure as that of the prior art described with reference to FIG. The variable displacement swash plate type compressor according to the 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 spool valve 800, and a bushing 900. The spool valve 800 includes a spool valve 600, a communication passage 700, a spool valve 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 opened toward the cylinder block 110 and includes a suction chamber 131 for supplying the refrigerant to the cylinder bore 111 of the cylinder block 110 during the suction stroke, A discharge chamber 132 through which the refrigerant in the cylinder bore 111 is discharged is formed. 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 bushing 900 is formed in a substantially cylindrical shape and is slidably mounted on the center bodder 112 and is coupled to the rotation shaft 200 and rotates integrally with the rotation shaft 200. When the inclination of the swash plate 300 is varied, the bush 900 slides along with the rotation axis 200 in the axial direction and moves through the valve unit 500 when the slide is moved in the axial direction. The intermediate chamber 910 is formed in the bushing 900.

The intermediate passage 600 is a channel that communicates with the discharge chamber 132 and the crank chamber 121 and selectively communicates with the intermediate chamber 910 of the bush 900. In the intermediate passage 600, And a pressure regulating valve V for varying the inclination angle of the swash plate 300 is connected by adjusting the opening degree of the intermediate passage 600 in the middle.

The communication path 700 is an oil path communicating the crank chamber 121 with the channel 135 connecting the suction port 133 to the suction chamber 131.

The spool valve 800 is installed in the communication passage 700 to interrupt the flow of the refrigerant from the conduit 135 to the crank chamber 121.

The spool valve 800 includes a case 810 mounted on the cylinder block 110, a spring 820 supported on the inner side of the case 810, And an opening / closing core (830).

3 and 4, a first passage L1 for communicating the spool valve 800 and the intermediate passage 600 may be further formed, and the spool valve 800 may include a middle passage The opening and closing core 830 is configured to slide in the direction of closing the communication passage 700 by the pressure of the passage 600, and this is configured to slide in the first passage L1 as shown in FIGS. 3 and 4 The spring 820 and the opening / closing core 830 are positioned relative to each other.

5, a second passage L2 for communicating the spool valve 800 with the bush 900 may be formed instead of the first passage L1, Is configured such that the opening and closing core 830 slides in the direction of closing the communication passage 700 by the pressure of the intermediate chamber 910 formed inside the bushing 900, The spring 820 and the opening / closing core 9830 with respect to the second passage L2 as shown in Fig.

In addition, a sensing unit 40 and a sensor 60 may be further provided behind the bushing 900 to reduce variation in engine speed and deteriorate fuel economy by avoiding torque fluctuations of the compressor.

The sensing unit 40 is supported on one side of the bearing 10 provided at the rear end of the bushing 900 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.

An additional communication path 1000 extending from the crank chamber 121 to the suction chamber 131 via an intermediate chamber 910 formed in the bushing 900 is further installed near the rotary shaft 200 3 to 5, when the swash plate 300 is in an unactuated state erected in the radial direction of the rotating shaft, the refrigerant is sucked from the crank chamber 121 through the additional communication path 1000, When the rotary shaft 200 is driven, the oil contained in the refrigerant is separated by the centrifugal separation and is moved in the direction of the crank chamber 121 and is recovered.

The crank chamber 121 and the suction chamber 131 are communicated with each other through the additional communication path 1000 at the beginning of the operation as described above so that 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.

The additional communication path 1000 is preferably formed to have a sectional area larger than the cross sectional area of the orifice provided so as to communicate with the crank chamber 121 and the suction chamber 131 to obtain a pulsation improving effect, The cross-sectional area across the entire area of the additional communication path 1000 is preferably larger than the cross-sectional area of the orifice having the size of? 2.4.

Hereinafter, the operation of the variable displacement swash plate compressor according to the embodiment of the present invention will be described in detail with reference to FIG. 1 and with reference to FIGS. 3 to 5. 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 or 5, a channel 135 connecting the suction port 133 to the suction chamber 131 and a communication passage 700 communicating with the crank chamber 121 are formed, The refrigerant moves from the suction chamber 131 to the crank chamber 121 through the communication passage 700 so that the pressure of the crank chamber can be rapidly lowered during the initial operation. ) Can be solved.

When the pressure in the crank chamber 121 becomes high as in the case of the maximum operation variable, the flow of the refrigerant is opposite to that shown in FIG. 3 or FIG. 5, and the suction gas flowing into the suction chamber 131, And flows through the chamber 121, so that the durability can be increased. The pressure in the suction chamber 131 is influenced by the pressure in the crank chamber 121 through the communication passage 700 so that the excessive change in the pressure in the suction chamber 131 is prevented, .

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: intermediate passage
700: communicating passage 800: spool valve
900: Bush

Claims (5)

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; And a rear head 130 disposed behind the cylinder block 110 and formed with a suction chamber 131, a discharge chamber 132 and a suction port 133. The front head 120 includes a chamber 121, A housing (100) forming a body;
A rotating shaft 200 rotatably mounted through one side of the housing 100;
A swash plate 300 mounted on the rotary shaft 200 and integrally rotated with the rotary shaft 200 so as to be able to vary the angle with respect to the rotary shaft 200 so that the refrigerant discharge amount can be adjusted;
A plurality of pistons 400 connected to the swash plate 300 and linearly reciprocating 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;
An intermediate passage 600 communicating the discharge chamber 132 and the crank chamber 121;
A communication passage (700) for communicating the crank chamber (121) with a channel (135) connecting the suction port (133) to the suction chamber (131);
And a spool valve (800) installed in the communication passage (700) for interrupting the flow of the refrigerant from the conduit (135) to the crank chamber (121)
The spool valve (800)
A case 810 installed in the cylinder block 110;
A spring 820 supported inside the case 810; And
And an opening / closing core (830) elastically supported by the spring (820) for sliding movement,
The bush 900 is slidably mounted on the center bore 112 of the rotary shaft 200 and penetrates through the valve unit 500 and rotates integrally with the rotary shaft 200. The spool valve And a second passage L2 communicating with the bush 900 is formed in the bush 900. The spool valve 800 is connected to the bush 900 by the pressure of the intermediate chamber 910 formed in the bush 900, And the opening / closing core (830) is configured to slide in a direction to close the communication passage (700). delete delete delete delete

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