KR20070081348A - Refrigerants compressor of car mutual assistance device - Google Patents

Abstract

A refrigerant compressor of an air conditioner for vehicles is provided to simplify compressor structure, and to reduce manufacturing costs by providing fixed swash plate type compressor structure with maximum discharge capacity without using a control valve. A refrigerant compressor of an air conditioner for vehicles comprises a first flow path(A) and a second flow path(B). The first flow path is formed to be directly communicated with a crank room and a suction room(131) without installing a control valve inside a discharge room(132). Operating fluid(refrigerant and lubrication oil) in the crank room flowed into a cylinder bore with operating fluid from an evaporator through the first flow path during an air suction process of a piston. The operating fluid in the cylinder bore is compressed during a compression process of the piston, and discharged to the discharge room. The second flow path is formed so as to allow a part of the discharged compression operating fluid to be supplied from the discharge room to the crank room along a pipe path formed in a shaft center of a drive shaft(140).

Description

Refrigerants Compressor of Car Mutual Assistance Device

Figure 1 is a side cross-sectional view showing the internal structure and lubrication structure of a conventional variable displacement swash plate compressor.

Figure 2 is a side cross-sectional view showing the structure of a refrigerant compressor for a vehicle air conditioner according to the present invention.

<Description of the symbols for the main parts of the drawings>

110; Cylinder block 114; Central axis

115; Guide rod 120; Front housing

121; Crankcase 122; Central axis

124; Shaft seal 130; Rear housing

131; Suction chamber 132; Discharge chamber

133; Control valve 134; Valve plate

140; Drive shaft 141; Information

141a; Long groove 141b; Hinge pin

142; Bearing 143; bearing

144; Sleeve 145; spring

150; Rotating support 151; Saphan

A; First euro B; 2nd euro

The present invention relates to an automobile air conditioner, and in particular, by providing a fixed swash plate type compressor structure having a maximum discharge capacity without using a control valve, the structure of the compressor is simplified, and the vehicle air conditioner does not need to greatly change the existing compressor structure. It relates to a refrigerant compressor for.

In general, refrigerant compressors for vehicle air conditioners are largely classified according to a driving method of a piston for performing a compression stroke of a refrigerant. Among them, a swash plate-type refrigerant compressor using a disk-shaped swash plate is mainly used.

The swash plate type refrigerant compressor is divided into a swash plate type compressor which performs a compression stroke of a substantially constant refrigerant and a variable capacity swash plate type compressor which controls and discharges the amount of refrigerant compressed by a change in temperature of a room.

1 is a side cross-sectional view showing the internal structure and lubrication structure of a conventional variable displacement swash plate compressor.

In the prior art variable displacement swash plate type compressor as shown in the drawing, a cylinder block 10 having a plurality of cylinder bores 11 is disposed at the center thereof, and a piston 12 flows back and forth to the cylinder bore 11. It is possibly installed.

The front end of the cylinder block 10 forms a closed crank chamber 21 and is closed by the front housing 20, and the rear end thereof is closed by the rear housing 30 via the valve plate 34. .

The rear housing 30 is formed with a suction chamber 31 and a discharge chamber 32 in communication with the cylinder bore 11. In addition, the drive shaft 40 is installed in the crank chamber 21 between the cylinder block 10 and the front housing 20 in parallel with the longitudinal direction of the cylinder bore 11.

The rear end of the drive shaft 40 is supported by the central shaft hole 14 of the cylinder block 10 through the bearing 42, and also through the bearing 43 in the front end portion in the central shaft hole 22 of the front housing 20. Supported.

In addition, a spring 45 is elastically supported between the bearings 42 at the rear end of the drive shaft 40 to prevent the drive shaft 40 from flowing freely in the axial direction. At this time, the guide portion 41 protruding in the direction perpendicular to the axis is formed in the interruption portion of the drive shaft 40.

The guide 41 is connected to the drive shaft 40 and the rotatable support 50 rotatable in the crank chamber 21 via a hinge mechanism, and the hinge mechanism has a long hole 41a formed in the guide 41. The hinge pin 41b is fixed to the rotational support member 50 at the engagement surface with the long hole 41a.

A sleeve 44 is interposed between the rotatable support 50 and the drive shaft 40, and the sleeve 44 is slidably installed in the axial direction of the drive shaft 40, and the outer sleeve has a sleeve pin in a direction perpendicular to the axis. (Not shown) is installed and engaged to the installation hole of the rotary support (50).

A swash plate 51 connected to the piston 12 and the piston rod 12a is installed on the rear side surface of the rotary support 50, and a guide installed in the crank chamber 21 in the crank chamber 21 at one end of the swash plate 51. The rod 15 is engaged with the front and back fluidly.

The rotatable support 50 and the guide 41 are rotatable in synchronization with the drive shaft 40, the rotatable support 50 is capable of inclination angle displacement via the guide 41 and the sleeve 44, the swash plate While 51 is inclined angle displacement is made in synchronization with the rotary support 50 via the guide rod 15, it is not rotated in the crank chamber 21.

In the cylinder block 10, a communication hole 13 communicating with the discharge chamber 32 is formed, and in the discharge chamber 32, the communication hole 13 is opened and closed with the discharge chamber 32 to open the crank chamber 21. A control valve 33 for controlling the pressure of) is provided.

The compressor configured as described above transmits back and forth oscillation to the swash plate 51 while the inclined rotary support 50 rotates in synchronism with the driving of the drive shaft 40. Each piston 12 connected to 12a is reciprocated in the cylinder bore 11.

In the reciprocating process of the piston 12, the refrigerant gas is sucked into the cylinder bore 11 in the suction chamber 31 of the rear housing 30, and the refrigerant gas is compressed and discharged into the discharge chamber 32.

The compression capacity of the refrigerant gas discharged into the discharge chamber 32 is controlled by adjusting the output in the crank chamber 21 by the control valve 33.

That is, for example, when the control valve 33 opens the communication hole 13 in which the crank chamber 21 and the discharge chamber 32 communicate with each other, the back pressure acting on the piston 12 is increased, so that the rotary support 50 Angle of inclination becomes small.

That is, the hinge pin 41b fixed to the rotary support 50 slides backward in the long groove 41a of the guide 41, and the rotary support 50 is retracted while the sleeve 44 is retracted. It swings backwards about the pin and swings backwards. Then, the swash plate 51 swings backward through the rotational support 50 and the sleeve 44, and the inclination angle becomes small.

In the above process, the smaller the inclination angle of the swash plate 51, the shorter the reciprocating stroke of the piston 12, the smaller the compression capacity of the refrigerant gas.

However, the prior art made of the above configuration has a problem that the structure according to the installation of the control valve 33 is complicated, and the joint is generated due to friction and wear on the operating portion according to the operation of the control valve 33. There is a problem that, when the refrigerant gas compressed to high pressure flows into the crank chamber 21 through the narrow communication hole 13 at a time, there is a problem that the refrigerant noise is severely generated.

In addition, the prior art has a problem that the lubrication for the internal mechanism of the compressor is not sufficiently made as the refrigerant gas and the lubricant contained in the refrigerant gas is temporarily circulated.

An object of the present invention for solving the problems of the prior art as described above is to provide a fixed swash plate compressor structure of the maximum discharge capacity without the use of a control valve, the structure of the compressor is simplified, greatly changing the existing compressor structure It is an object of the present invention to provide a refrigerant compressor for an automobile air conditioner.

Another object of the present invention for solving the problems of the prior art is that the noise due to the refrigerant noise and friction in the variable portion according to the use of the conventional variable displacement compressor is not generated quietness is maintained, while each friction inside the compressor It is to provide a refrigerant compressor for a vehicle air conditioner to ensure that the parts are always lubricated by the working fluid.

Refrigerant compressor for a vehicle air conditioner according to the present invention for achieving the above object is a plurality of cylinder bores are formed in the crank chamber in the front housing, the suction chamber in the rear housing, the discharge chamber and the cylinder block connected thereto, The cylinder beams are reciprocally accommodated, respectively, and the drive shafts installed through the bearings in the center shaft hole of the front housing and the center shaft hole of the cylinder block are rotatably installed in the crank chamber so as to be synchronously rotatable. It is installed to be displaced in an inclined state through the sleeve between the swash plate, the swash plate coupled to the piston and the piston rod is installed to the synchronous inclined displacement on the rear side of the rotary support, the pressure in the crank chamber so that the inclination angle of the swash plate is adjusted A control valve to control is installed in the discharge chamber In the capacity swash plate type compressor,

A first flow passage is formed in direct communication between the crank chamber and the suction chamber without installing a control valve inside the discharge chamber. When the working fluid (refrigerant gas and lubricating oil) in the crank chamber is intake stroke of the piston, the first flow passage is formed. Through the working fluid from the evaporator flows into the cylinder bore, the working fluid in the cylinder bore is compressed and discharged to the discharge chamber during the compression stroke of the piston, a portion of the discharged compressed working fluid is centered on the drive shaft axis from the discharge chamber And a second flow path for supplying the crank chamber along the formed pipe line.

Hereinafter, with reference to the accompanying drawings for a preferred embodiment of the present invention will be described in detail.

Figure 2 is a longitudinal sectional view showing the structure of a refrigerant compressor for a vehicle air conditioner according to the present invention.

In the variable displacement swash plate type compressor according to the present invention as shown in the drawings, a cylinder block 110 having a plurality of cylinder bores 11 is disposed at a central portion thereof, and a piston 12 is disposed at the cylinder bore 111. It is installed to be movable (see Fig. 1).

The front end of the cylinder block 110 forms a closed crank chamber 121 and is closed by the front housing 120, and the rear end thereof is closed by the rear housing 130 via the valve plate 134. .

The rear housing 130 is formed with a suction chamber 131 and a discharge chamber 132 in communication with the cylinder bore. In addition, the drive shaft 140 is installed in the crank chamber 121 between the cylinder block 110 and the front housing 120 in parallel with the longitudinal direction of the cylinder bore.

The rear end of the drive shaft 140 is supported by the central shaft hole 114 of the cylinder block 110 through the bearing 142, and also through the bearing 143 in the front end portion in the central shaft hole 122 of the front housing 120 Supported.

In addition, a spring 145 is elastically supported between the bearings 142 at the rear end of the driving shaft 140 to prevent the driving shaft 140 from flowing in the axial direction. At this time, the guide portion 141 protruding in the direction perpendicular to the shaft is formed in the stop portion of the drive shaft 140.

The guide 141 is connected to the drive shaft 140 and the rotatable support 150 rotatable in the crank chamber 121 via a hinge mechanism, the hinge mechanism is a long hole (141a) formed in the guide 141 and The hinge pin 141b is fixed to the rotary support 150 at the engagement surface with the long hole 141a.

A sleeve 144 is interposed between the rotation support member 150 and the drive shaft 140, and the sleeve 144 is slidably installed in the axial direction of the drive shaft 140, and the sleeve pin is disposed on the outer surface at a right angle to the axis. (Not shown) is installed and engaged with the installation hole of the rotary support 150.

A swash plate 151 connected to a piston (not shown; see FIG. 1) and a piston rod 112a is installed on the rear side of the rotary support 150, and a crank chamber 121 is provided at one end of the swash plate 151. The guide rod 115 is installed in the axial direction so as to be movable back and forth.

The rotary support 150 and the guide 141 is rotatable in synchronization with the drive shaft 140, the rotary support 150 is capable of inclination angle displacement via the guide 141 and the sleeve 144, swash plate While 151 is a square-square displacement is made in synchronization with the rotary support 150 via the guide rod 115, it does not rotate in the crank chamber 121.

In this case, in the present invention having the above-described configuration, a first flow path A directly communicating the crank chamber 121 and the suction chamber 131 is formed, and a working fluid (refrigerant gas and lubricating oil) in the crank chamber 121. The gas flows into the cylinder bore along with the working fluid from the evaporator through the first flow path A, and the working fluid in the cylinder bore is compressed to the discharge chamber 132 during the compression stroke of the piston. And a second flow path (B) for discharging and supplying a part of the discharged compressed working fluid to the crank chamber (121) along a pipeline formed at the center of the drive shaft (140) axis from the discharge chamber (132). .

Hereinafter, the operation of the present invention will be described.

First, the drive shaft 140 is driven in conjunction with the engine of the vehicle. As the inclined rotary support 150 rotates in synchronism with the driving of the drive shaft 140, the front and rear swings are transmitted to the swash plate 151, and the front and rear swings are each piston connected to the swash plate 151 by the piston rod 112a. Is reciprocated in the cylinder bore.

In the reciprocating process of the piston, the refrigerant gas supplied from the evaporator (not shown) is sucked into the cylinder bore (not shown) in the suction chamber 131 of the rear housing 130, the refrigerant gas is compressed, and then the discharge chamber 132. Discharged.

At this time, by the intake stroke of the piston, the working fluid (refrigerant gas and lubricating oil) in the crank chamber 121 flows into the cylinder bore through the first flow path A, and the working fluid in the cylinder bore is compressed by the piston. At the time of stroke, it is compressed and discharged to the discharge chamber 132.

In addition, a part of the discharged compressed working fluid has a closed circulation structure in which a part of the discharged working fluid is supplied to the crank chamber 121 along a conduit formed at the center of the drive shaft 140 from the second passage B, that is, the discharge chamber 132. do.

Here, the lubricating oil contained in the atomized state in the atomizing state, during the high-speed reciprocating motion of the piston and the high-speed rotational movement of the drive shaft 140, to form a smooth film with a lubricant on the friction surface between each other to achieve a smooth drive.

In the compressor of the present invention having the above-described configuration, when the first flow path A is positioned at the upper side of the compressor, the lubricating oil contained in the working fluid is retained while the lubricating oil in the fluid state remains in the crank chamber 121. It can be circulated continuously along the refrigerant system.

As described above, the present invention provides a fixed swash plate type compressor structure having a maximum discharge capacity without using a control valve, thereby simplifying the structure of the compressor and reducing the development cost and manufacturing cost since the compressor structure does not have to be changed significantly. It is effective.

In addition, the present invention does not generate noise due to the refrigerant noise and friction in the variable portion according to the use of the conventional variable displacement compressor has the effect of maintaining the quietness.

In addition, the present invention is a structure in which each friction portion of the compressor is always lubricated by the working fluid, there is an effect to ensure a long life of the compressor.

Claims (4)

A plurality of cylinder bores are formed in the crank chamber 121 in the front housing 120, the suction chamber 131 in the rear housing 130, the discharge chamber 132 and the cylinder block 110 connected thereto, and each cylinder Pistons are reciprocally accommodated in the beams, respectively, and cranks are provided in the drive shafts 140 installed through the bearings 142 and 143 in the central shaft hole 122 of the front housing 120 and the central shaft hole 114 of the cylinder block 110. The rotary support 150 located in the chamber 121 is installed to be synchronously rotatable and is installed to be displaced in an inclined state via the sleeve 144 between the hinge mechanism and the drive shaft 140, and the rotary support 150. On the rear side of the swash plate 151 coupled to the piston and the piston rod (112a) is installed so as to be synchronous inclined displacement, to control the pressure in the crank chamber 121 to adjust the inclination angle of the swash plate (151) The control valve 133 is installed in the discharge chamber 132 In the luer binary variable displacement swash plate type compressor, Without installing the control valve 133 inside the discharge chamber 132, a first flow path A directly connecting the crank chamber 121 and the suction chamber 131 is formed, and the operation in the crank chamber 121 is performed. Fluid (refrigerant gas and lubricating oil) flows into the cylinder bore along with the working fluid from the evaporator through the first flow path A when the intake stroke of the piston is carried out, and the working fluid in the cylinder bore is compressed when the piston is compressed And discharged to the discharge chamber 132, and a part of the discharged compressed working fluid is supplied to the crank chamber 121 along a pipeline formed at the center of the drive shaft 140 axis from the discharge chamber 132 (B). Refrigerant compressor for a vehicle air conditioner, characterized in that to form a). The method of claim 1, Refrigerant compressor for a vehicle air conditioner, characterized in that the first passage (A) and the second passage (B) forms a closed circulation structure that is always open. The method of claim 1, Refrigerant for a vehicle air conditioner characterized in that the drive shaft lubrication is performed by the working fluid by passing the second flow path B communicating the crank chamber 121 from the discharge chamber 132 through the drive shaft 140. compressor. The method of claim 1, Refrigerant compressor for a vehicle air conditioner, characterized in that the compressor is installed so that the first passage (A) is located on the upper side.

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