KR101032184B1 - Compressor - Google Patents

Abstract

The present invention relates to a compressor, and more particularly, in a structure in which the refrigerant introduced from the swash plate chamber is uniformly sucked into the cylinder bore through the hollow drive shaft, the outer peripheral surface of the drive shaft by the compression reaction force received by the swash plate during the compression stroke of the piston. The purpose of the present invention is to improve the sealing property between the inner and outer circumferential surfaces of the shaft support hole and to minimize the wear of the drive shaft and the shaft support hole so as to improve durability and to achieve the optimal compression performance.

To this end, the present invention is a swash plate rotating in the swash plate chamber in the compressor is inclined, the drive shaft formed therein so that the refrigerant sucked into the swash plate chamber can move to the cylinder bore; The drive shaft is rotatably installed in the shaft support hole and a plurality of cylinder bores are formed on both sides of the swash plate chamber, and the refrigerant sucked into the flow path of the drive shaft can be sequentially sucked into each cylinder bore when the drive shaft rotates. A front and rear cylinder block having a suction passage communicating the shaft support hole and each cylinder bore; A plurality of pistons mounted on an outer circumference of the swash plate and reciprocating in the cylinder bore in conjunction with a rotational movement of the swash plate; Front and rear housings coupled to both sides of the cylinder block and having discharge chambers formed therein; In a compressor including a valve unit interposed between the cylinder block and the front and rear housings, the clearance between the outer circumferential surface of the drive shaft front side and the inner circumferential surface of the shaft support hole of the front cylinder block is rear and outer circumferential surface of the drive shaft rear side. It is characterized in that it is set larger than the gap between the inner peripheral surface of the shaft support hole of the cylinder block.

Compressor, drive shaft, flow path, cylinder bore, swash plate, compression reaction force, clearance, durability, sealing property, adhesion

Description

Compressor

1 is a cross-sectional view showing a conventional compressor,

2 is a cross-sectional view taken along the line A-A in FIG.

3 is a perspective view of a compressor according to the present invention;

4 is an exploded perspective view showing a compressor according to the present invention;

5 is a sectional view showing a compressor according to the present invention;

6 is a perspective view illustrating a state in which the drive shaft and the swash plate are disassembled in the compressor according to the present invention;

7 is a sectional view showing a main part of a compressor according to the present invention;

8a to 8c is a schematic perspective view showing a process in which the refrigerant in the swash plate chamber is sucked into the cylinder bore through the flow path in accordance with the rotation of the drive shaft in the compressor according to the present invention,

9 is an exploded perspective view showing a valve unit in the compressor according to the present invention.

Description of the Related Art [0002]

100: compressor 110: front housing

111,121: discharge chamber 112,122: fixing hole

113,123: Bolted hole 120: Rear housing

130: front cylinder block 131,141: cylinder bore

132,142: suction passage 133,143: shaft support hole

134,144: discharge passage 135,145: muffler

136: swash chamber 140: rear cylinder block

146: suction port 147: discharge port

150: drive shaft 151: flow path

152: entrance 153: exit

160: Saphan 161: Hub

165: shoe 170: piston

180: valve unit 181: valve plate

181a: refrigerant discharge hole 181b: communication path

182: discharge lead valve 182a: valve plate

183: fixing pin 190: bolt

The present invention relates to a compressor, and more particularly, in a structure in which the refrigerant introduced from the swash plate chamber is uniformly sucked into the cylinder bore through the hollow drive shaft, and the drive shaft outer circumferential surface due to the compression reaction force received by the swash plate during the compression stroke of the piston. The present invention relates to a compressor that can achieve an optimal compression performance by improving the sealing property between the inner circumferential surface of the shaft support hole and minimizing wear of the driving shaft and the shaft support hole to improve durability.

In general, a compressor for automobiles sucks refrigerant gas discharged after evaporation is completed from an evaporator, converts the refrigerant gas into a refrigerant gas in a high temperature and high pressure state that is easily liquefied, and discharges the refrigerant gas.

There are various kinds of such compressors, such as a swash plate type compressor in which a piston reciprocates by the rotation of an inclined swash plate, a scroll compressor compressed by a rotational motion of two scrolls, and a rotary compressor compressed by a rotary vane. .

Among these, the reciprocating compressor that compresses the refrigerant according to the reciprocating motion of the piston includes crank type and wobble plate type in addition to the swash plate type compressor, and the swash plate type compressor also has a fixed capacity swash plate type compressor and a variable capacity type according to the use. And swash plate compressors.

1 and 2 is a view showing a conventional fixed-capacity swash plate type compressor, briefly described with reference to the following.

As shown, the swash plate compressor 1 is coupled to the front housing 10, the front cylinder block 20 is built, the rear housing is coupled to the front housing 10 and the rear cylinder block 20a ( 10a).

Inside the front and rear housings 10 and 10a, the discharge chamber 12 and the suction are respectively provided inside and outside of the partition wall 13 in correspondence with the refrigerant discharge hole and the refrigerant suction hole of the valve plate 61 to be described below. The yarn 11 is formed.

Here, the discharge chamber 12 is formed in the first discharge chamber 12a formed inside the partition 13, and formed outside the partition 13 so as to be partitioned from the suction chamber 11 and the first discharge chamber 12a. ) And a second discharge chamber 12b communicating through the discharge hole 12c.

That is, when the refrigerant in the first discharge chamber 12a passes through the discharge hole 12c having the small diameter, the refrigerant is reduced and enlarged when moving to the second discharge chamber 12b. The pulsation pressure drops to reduce vibration and noise.

On the other hand, a plurality of bolted fastening holes 16 are formed in the circumferential direction of the suction chamber 11. Through the bolt fastening hole 16, the front and rear housings 10 and 10a are fastened / fixed to the mutual bolts 80 in a state where a plurality of components are assembled therein.

The front and rear cylinder blocks 20 and 20a are provided with a plurality of cylinder bores 21 therein, and the cylinder bores 21 corresponding to each other of the front and rear cylinder blocks 20 and 20a are provided. The pistons 50 are coupled to the linear reciprocating motion as well as the pistons 50 are coupled to the outer circumference of the swash plate 40 inclined to the drive shaft 30 via the shoe 45.

Accordingly, the pistons 50 reciprocate inside the cylinder bore 21 of the front and rear cylinder blocks 20 and 20a in conjunction with the swash plate 40 rotating together with the drive shaft 30.

The valve unit 60 is installed between the front and rear housings 10 and 10a and the front and rear cylinder blocks 20 and 20a.

Here, the valve unit 60 is composed of a valve plate 61 having a refrigerant suction hole and a refrigerant discharge hole, and a suction lead valve 63 and a discharge lead valve 62 installed at both sides thereof.

The valve unit 60 is assembled between the front and rear housings 10 and 10a and the front and rear cylinder blocks 20 and 20a, respectively, in which fixings are formed on both sides of the valve plate 61. The pin 65 is assembled in a fixed position while being inserted into the fixing holes 15 formed on the opposite surfaces of the front and rear housings 10 and 10a and the front and rear cylinder blocks 20 and 20a. .

On the other hand, the front and rear cylinder block 20 (20) (so that the refrigerant supplied to the swash plate chamber 24 provided between the front and rear cylinder blocks 20, 20a can flow to each suction chamber 11 ( A plurality of suction passages 22 are formed in 20a, and the second discharge chamber 12b of the front and rear housings 10 and 10a is formed through the front and rear cylinder blocks 20 and 20a. It is communicated with each other by the connecting passage 23.

Therefore, the suction and compression of the refrigerant may be simultaneously performed in the bore 21 of the front and rear cylinder blocks 20 and 20a according to the reciprocating motion of the piston 50.

In addition, a shaft support hole 25 is formed at the center of the front and rear cylinder blocks 20 and 20a to support the drive shaft 30, and a needle roller bearing 26 is formed in the shaft support hole 25. It interposes and supports the said drive shaft 30 rotatably.

On the other hand, the upper portion of the outer side of the rear housing (10a) is supplied with the refrigerant transferred from the evaporator during the intake stroke of the piston 50 into the compressor (1), during the compression stroke of the piston 50 inside the compressor (1) The muffler 70 is formed to discharge the compressed refrigerant in the condenser.

Referring to the refrigerant circulation process of the compressor (1) configured as described above are as follows.

The refrigerant supplied from the evaporator is sucked into the suction part of the muffler 70 and then supplied to the swash plate chamber 24 between the front and rear cylinder blocks 20 and 20a through the refrigerant suction port 71. The refrigerant supplied to 24 flows into the suction chamber 11 of the front and rear housings 10 and 10a along the suction passage 22 formed in the front and rear cylinder blocks 20 and 20a. .

Thereafter, the suction lead valve 63 is opened during the suction stroke of the piston 50. At this time, the refrigerant in the suction chamber 11 is sucked into the cylinder bore 21 through the refrigerant suction hole of the valve plate. .

In addition, during the compression stroke of the piston 50, the refrigerant inside the cylinder bore 21 is compressed. In this case, the discharge lead valve 62 is opened, and the refrigerant passes through the refrigerant discharge hole of the valve plate. 10) to the first discharge chamber 12a of 10a.

Subsequently, the refrigerant flowing into the first discharge chamber 12a is discharged to the discharge portion of the muffler 70 through the refrigerant discharge port 72 of the muffler 70 through the second discharge chamber 12b and then to the condenser. It will be fluid.

Meanwhile, the refrigerant compressed in the cylinder bore 21 of the front cylinder block 20 is discharged to the first discharge chamber 12a of the front housing 10 and then flows to the second discharge chamber 12b. Along the connecting passage 23 formed in the front and rear cylinder blocks 20 and 20a, the second discharge chamber 12b of the rear housing 10a flows to the refrigerant discharge port 72 together with the refrigerant therein. Through the discharge portion of the muffler 70 is discharged.

However, the above-described conventional compressor 1 has a loss due to the suction resistance caused by the complicated refrigerant passage inside, a loss due to the elastic resistance of the suction lead valve 63 when the valve unit 60 is opened and closed. There was a problem that the suction volume efficiency of the refrigerant is reduced.

On the other hand, a technique for reducing the loss caused by the elastic resistance of the suction lead valve 63 is disclosed in Korean Patent Publication No. 2003-47729 (name: lubrication structure in a fixed capacity piston type compressor). That is, the above technique applies a suction shaft integrated suction rotary valve without a suction lead valve, and a refrigerant flows from the rear of the driving shaft to the inside of the driving shaft in order to reduce the loss caused by the suction resistance. It is to be able to enter the cylinder bore directly through the refrigerant suction passage communicating with the shaft support hole.

In addition, in the domestic patent application No. 2005-74185 filed previously by the applicant of the present invention, the cylinder bore formed in the cylinder block the refrigerant sucked into the compressor inside the drive shaft in which the swash plate rotating in the swash plate chamber is inclined It has been disclosed a compressor having a structure in which a flow path is formed so as to move to a side, and an inlet and an outlet are spaced apart from both sides of the flow path.

Here, the inlet of the flow passage is formed through one side of the hub and the drive shaft of the swash plate, or formed in opposite directions on both sides of the drive shaft. In the latter case, one inlet is formed at a position spaced apart from each other so as not to face the other inlet.

In addition, the outlet of the flow path is formed so as to communicate with the suction passage of each cylinder bore, the cylinder bore provided on both sides of the swash plate chamber during rotation of the drive shaft is formed on both sides of the drive shaft in opposite directions to each other at the same time so as to suck the refrigerant It is.

However, in the related arts, a regular gap is normally provided between the outer circumferential surface of the drive shaft and the inner circumferential surface of the shaft support hole to smoothly drive the drive shaft and to secure lubricity through the gap. Due to the gap, the adhesion between the outer circumferential surface of the drive shaft and the inner circumferential surface of the shaft support hole is reduced, so that the refrigerant sucked into the cylinder bore flows back and the high pressure refrigerant gas can be leaked.

In general, in the case of the fixed displacement swash plate type compressors, the clearance between the shaft support hole of the front cylinder block and the drive shaft front side in connecting the drive shaft through the respective shaft support holes of the front and rear cylinder blocks is determined by the rear cylinder. It is set to be equal to the gap between the shaft support hole of the block and the drive shaft rear side.

By the way, in the fixed displacement swash plate type compressor, the drive shaft front side supports the shaft of the front cylinder block by a naturally generated compression reaction as much as the force transmitted by the drive shaft to the piston when the drive shaft compresses the piston to transmit the force to the piston. Although it is common to incline slightly by the force in the direction to be in close contact with the ball (see FIG. 6 of the present invention), as described above, if the clearance gap between the front and the rear is the same, the tilt of the drive shaft due to the compression reaction force is prevented and the shaft Adhesion between the supporting holes is reduced.

This is because the front end of the drive shaft extending through the shaft support hole of the front cylinder block is connected to the electromagnetic clutch. When the driving force of the engine is transmitted to the electromagnetic clutch, the front and rear sides of the driving shaft are respectively driven by the centrifugal force of the electromagnetic clutch. Axial force is applied because the front side of the drive shaft is closer to the center point of the electromagnetic clutch than the rear side of the drive shaft, so that the pressure is greater.

As a result, there is a problem that the shaft support holes corresponding to the drive shaft front side and the shaft support holes corresponding to the drive shaft front side are more likely to wear than the shaft support holes corresponding to the drive shaft rear side due to the large pressure applied to the drive shaft front side during the compression stroke of the piston. In addition, the adhesion between the outer circumferential surface of the drive shaft front side and the inner circumferential surface of the corresponding shaft support hole is weakened and sufficient sealing property cannot be secured, so that the refrigerant suction passage cannot be completely blocked, and thus the refrigerant is sucked into the cylinder bore during the compression process. As a result of the leak of the refrigerant through the refrigerant suction passage, there is a problem in that the optimum compression performance cannot be exhibited.

As such, in the prior art, there is no research on such a gap that may greatly affect the performance of the compressor.

Accordingly, the present invention has been made in view of the above-mentioned conventional problems, and in the structure in which the refrigerant introduced from the swash plate chamber is uniformly sucked into the cylinder bore through the hollow drive shaft, the compression reaction force received by the swash plate during the compression stroke of the piston Accordingly, an object of the present invention is to provide a compressor capable of exhibiting an optimal compression performance by improving the sealing property between the outer circumferential surface of the drive shaft and the inner circumferential surface of the shaft support hole and minimizing wear of the drive shaft and the shaft support hole to improve durability.

The present invention for achieving the above object is a swash plate rotating in the swash plate chamber in the compressor is inclined, the drive shaft formed therein so that the refrigerant sucked into the swash plate chamber can move to the cylinder bore; The drive shaft is rotatably installed in the shaft support hole and a plurality of cylinder bores are formed on both sides of the swash plate chamber, and the refrigerant sucked into the flow path of the drive shaft can be sequentially sucked into each cylinder bore when the drive shaft rotates. A front and rear cylinder block having a suction passage communicating the shaft support hole and each cylinder bore; A plurality of pistons mounted on an outer circumference of the swash plate and reciprocating in the cylinder bore in conjunction with a rotational movement of the swash plate; Front and rear housings coupled to both sides of the cylinder block and having discharge chambers formed therein; A compressor including a valve unit interposed between the cylinder block and the front and rear housings, wherein a gap Da between an outer circumferential surface of the drive shaft front side and an inner circumferential surface of the shaft support hole of the front cylinder block is located on the rear side of the drive shaft. It is characterized by being set larger than the clearance Db between the outer peripheral surface and the inner peripheral surface of the axial support hole of the rear cylinder block.

Further, in the present invention, the gap Da is 1 to 10 µm larger than the gap Db.

In addition, in the present invention, the inlet of the flow passage is formed to communicate with the swash plate chamber, the outlet is characterized in that it is formed to communicate with the suction passage of the cylinder block.

In addition, in the present invention, the inlet of the flow passage is formed through one side of the hub and the drive shaft of the swash plate, the outlet of the flow path is characterized in that formed in opposite directions on both sides of the flow path.

In the present invention, the valve unit is a valve plate formed with a plurality of refrigerant discharge holes to communicate with each of the cylinder bore and the discharge chamber of the front and rear housings, and is installed on one side of the valve plate for the refrigerant discharge hole It is characterized by consisting of the discharge lead valve for opening and closing.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

Repeated description of the same construction and operation as in the prior art will be omitted.

Figure 3 is an exploded perspective view showing a compressor according to the present invention, Figure 4 is a cross-sectional view showing a compressor according to the invention, Figure 5 is a perspective view showing a state in which the drive shaft and the swash plate in the compressor according to the invention, Figure 6 Is a cross-sectional view showing the main part of a compressor according to the present invention.

The present invention employs a structure of a compressor capable of allowing the refrigerant supplied to the swash plate chamber to be directly sucked into the cylinder bore through the hollow drive shaft.

According to the compressor having such a structure, by forming a flow path inside the drive shaft and allowing the refrigerant supplied to the swash chamber to be directly sucked into the cylinder bore through the flow path as the drive shaft rotates, thereby providing uniform refrigerant to each cylinder bore on both sides of the swash chamber. As well as the distribution is made, there is an advantage that the flow of the refrigerant to the driving unit, such as the swash plate and the drive shaft in the swash plate chamber can be improved to improve the lubrication performance by the oil.

The present invention employs such a compressor structure to improve the sealing property between the outer peripheral surface of the drive shaft and the inner peripheral surface of the shaft support hole by the compression reaction force received by the swash plate so that the refrigerant sucked into the cylinder bore does not flow back when the piston is compressed. It is to improve the performance of the compressor by improving the durability by minimizing the wear of the drive shaft and the shaft support hole.

As shown, the compressor 100 according to the present invention includes a drive shaft 150 in which the swash plate 160 rotating in the swash plate chamber 136 inside the compressor 100 is inclinedly coupled to the drive shaft 150. The front and rear cylinder blocks 130 and 140 rotatably installed in the paper holes 133 and 143 and the outer circumference of the swash plate 160 are mounted via a shoe 165 to rotate the swash plate 160. A plurality of pistons 170 for reciprocating the inside of the cylinder bore (131, 141) formed on both sides of the swash plate chamber 136 of the front and rear cylinder block 130, 140, and the front and rear cylinder block The front and rear housings 110 and 120 and the front and rear cylinder blocks 130 and 140 are coupled to both sides of the 130 and 140, respectively, and the discharge chambers 111 and 121 are formed therein. The valve unit 180 is interposed between the rear housings 110 and 120, respectively.

First, both sides of the drive shaft 150 are rotatably installed in the shaft support holes 133 and 143 of the front and rear cylinder blocks 130 and 140, and one end thereof penetrates the front housing 110. It extends and is engaged with the electromagnetic clutch (not shown).

The swash plate 160 rotating in the swash plate chamber 136 is obliquely coupled to the drive shaft 150, and is sucked into the swash plate chamber 136 through the suction port 146 of the rear cylinder block 140. A flow path 151 is formed in communication with the swash plate chamber 136 and the cylinder bores 131, 141 so that the suction refrigerant can pass through the swash plate 160 and move to the cylinder bores 131, 141. .

The inlet 152 of the flow path 151 is formed to communicate with the swash plate chamber 136, the outlet 153 is each suction passage 132 of the front and rear cylinder blocks 130, 140 to be described below. 142 is formed to communicate with.

Here, the inlet 152 of the flow path 151 is formed penetrating through one side of the hub 161 and the drive shaft 150 of the swash plate 160.

Meanwhile, only one inlet 152 of the flow path 151 may be formed on one side of the driving shaft 150, or two may be formed in opposite directions.

In addition, the outlet 153 of the flow path 151 is formed on both sides of the flow path 151 in opposite directions to each cylinder bore 131 provided on both sides of the swash plate chamber 136 when the drive shaft 150 rotates. At the same time, the refrigerant can be sucked into the 141.

That is, since the swash plate 160 is formed to be inclined, the piston 170 disposed in opposite directions among the piston 170 coupled to the outer circumference of the swash plate 160 performs the same suction or compression stroke, so that the flow path ( Both outlets 153 of the 151 must be formed in opposite directions so that the refrigerant can be sucked into the cylinder bores 131 and 141 provided on both sides of the swash plate chamber 136 at the same time.

Of course, the direction of each outlet 153 of the flow path 151 formed in the drive shaft 150 may vary depending on the design purpose such as the number of the piston 170.

In addition, the front and rear cylinder blocks 130 and 140 are each formed with a plurality of cylinder bores 131 and 141 on both sides of the swash plate chamber 136, the center of the drive shaft 150 to be rotatable Axial support holes 133 and 143 are formed to be supported.

In addition, the front and rear cylinder blocks (130, 140), the refrigerant sucked into the flow path 151 of the drive shaft 150 in the swash plate chamber 136, each cylinder bore (sequential) during rotation of the drive shaft 150 ( Suction passages 132 and 142 communicating with the shaft support holes 133 and 143 and the respective cylinder bores 131 and 141 are formed to be sucked into the 131 and 141.

On the other hand, between the drive shaft 150 and the cylinder block 130, 140, that is, between the outer peripheral surface of the drive shaft 150 and the inner peripheral surface of the shaft support holes 134, 143 for supporting the drive shaft 150 lubrication with smooth drive of the drive shaft There is a certain gap so that the action and the sealing action can be performed. That is, a part of the oil piggybacked on the refrigerant sucked through the inlet 152 of the flow path 151 is smoothly discharged on the inner wall surface of the outlet 153 during the rotational drive of the drive shaft 150 by its own weight, thereby driving the drive shaft 150. It flows toward the said gap in the state surrounding the outer peripheral surface of). As a result, the lubricity and sealing property between the outer circumferential surface of the drive shaft 150 and the inner circumferential surface of the shaft support holes 134 and 143 supporting the drive shaft 150 can be significantly improved.

However, in the present invention, in forming the gap as described above, as shown in Figure 7, the inner peripheral surface of the shaft support hole 133 formed in the front cylinder block 130 and the drive shaft 150 supported by the shaft support hole 133 A gap Db between the inner circumferential surface of the shaft support hole 143 formed in the rear cylinder block 140 and the outer circumferential surface of the rear side of the drive shaft 150 supported by the shaft support hole 143. It is larger than).

This is because, when the driving shaft front side and the rear side are each axially applied by the centrifugal force of the electromagnetic clutch connected to the driving shaft end as described in connection with the prior art, the distance from the center point of the electromagnetic clutch is closer to the driving shaft front side than the driving shaft rear side. In consideration of the greater pressure on the drive shaft, the same pressure acts on the front and rear of the drive shaft to increase the adhesion between the drive shaft 150 and the shaft support hole 133 by the compression reaction force during the compression stroke of the piston. .

When the gap Da is made larger than the gap Db as in the present invention, the area of the shaft support hole 133 of the front cylinder block 130 is larger than the area of the shaft support hole 143 of the rear cylinder block 140. . Therefore, the pressure acting per unit area is proportional to the force but inversely proportional to the area (P = F / A, P: pressure, F: force, A: area), so the front of the drive shaft is centered on the electromagnetic clutch compared to the rear of the drive shaft. Although the distance from the front is close to the drive shaft 150 supported by the shaft support hole 133 of the front cylinder block 130 and the drive shaft 150 supported by the shaft support hole 143 of the rear cylinder block 140 is applied to the rear side The losing pressure works the same.

If the gap Da is smaller than the gap Db, the inclination of the drive shaft due to the compression reaction force during the compression stroke of the piston is hindered by the small gap Da so that the outer peripheral surface and the shaft support hole of the drive shaft are interrupted. The sealing gap between the inner circumferential surfaces of and the large gap Db has a problem that wear occurs when the drive shaft rotates due to the large pressure applied thereto, so that the gap Da is made larger than the gap Db. It is preferable.

Accordingly, when starting the compression stroke of the piston 170 which transmits a force to the piston 170 (in the direction of the white arrow in FIG. 7), the drive shaft 150 is equal to the force transmitted to the piston 170. The suction passage formed in the shaft support hole 133 is smoothly moved in the direction of the white arrow in the vertical direction in FIG. 7 by the naturally occurring compression reaction (the black arrow in the horizontal direction in FIG. 7). By completely blocking the 132, a high-pressure refrigerant sucked into the cylinder bore 131 does not leak through the suction passage 132, thereby ensuring a reliable sealing function.

As such, the gap Da between the outer circumferential surface of the drive shaft 15 front side and the inner circumferential surface of the shaft support hole 133 is larger than the gap Db between the outer circumferential surface of the drive shaft 15 rear side and the inner circumferential surface of the shaft support hole 143. When the drive shaft 150 is rotated 15, the wear of the drive shaft 150 front side and the shaft support hole 133 may be minimized, and thus durability may be greatly improved.

If the gap Da is too large, sufficient sealing property cannot be ensured, so that the gap Da is preferably 1 to 10 µm larger than the gap Db.

In addition, the gap Da may be adjusted by increasing the inner diameter of the shaft support hole 133 or by decreasing the outer diameter of the front side of the driving shaft 150.

On the other hand, the outer surface of one of the front and rear cylinder blocks 130, 140 and the suction port 146 in communication with the swash plate chamber 136 to supply an external refrigerant to the swash plate chamber 136, and Discharge ports 147 communicating with the discharge chambers 111 and 121 are formed to discharge the refrigerant in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 to the outside.

Accordingly, the discharge passage 134 connecting the discharge chambers 111 and 121 and the discharge port 147 of the front and rear housings 110 and 120 to the front and rear cylinder blocks 130 and 140. 144 is formed on the outer surface of the cylinder block 130, 140 muffler 135 to expand the discharge passage 134, 144 to reduce the pulsation pressure of the discharge refrigerant to reduce the noise 145 is formed.

In addition, the valve unit 180 has a plurality of refrigerant discharge holes 181a so as to communicate the cylinder bores 131 and 141 with the discharge chambers 111 and 121 of the front and rear housings 110 and 120. ) Is formed of a valve plate 181 and a discharge lead valve 182 installed at one side of the valve plate 181 to open and close the refrigerant discharge hole 181a.

That is, the discharge lead valve 182 is installed in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 with respect to the valve plate 181 to compress the stroke of the piston 170. The valve plate 182a is elastically deformed to open the refrigerant discharge hole 181a and to close the refrigerant discharge hole 181a during the suction stroke.

In addition, the valve plate 181 has refrigerant in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 discharge passages 134 of the front and rear cylinder blocks 130 and 140. A communication path 181b is formed to communicate the discharge chambers 111 and 121 and the discharge passages 134 and 144 so as to be discharged to the discharge port 147 via the 144.

In addition, the valve unit 180 has fixing pins 183 provided at both sides of the valve plate 181 facing the front and rear housings 110 and 120 and the front and rear cylinder blocks 130 and 140. It is coupled / fixed while being inserted into the fixing holes 112 and 122 formed in the surface.

Meanwhile, the front and rear housings 110 and 120 are formed with a plurality of bolt fastening holes 113 and 123 at edges thereof, and the front and rear through the bolt fastening holes 113 and 123. The housings 110 and 120 are fastened / fixed to the mutual bolt 190 in the state in which the above components are assembled. Of course, bolt fastening holes 138, 148, and 184 are formed in the front and rear cylinder blocks 130 and 140 and the valve unit 180 to allow the bolt 190 to pass therethrough.

As described above, in the compressor 100 according to the present invention, when the driving shaft 150 selectively receives power from an electronic clutch (not shown), the swash plate 160 rotates, and the swash plate ( The plurality of pistons 170 linked to the rotational movement of 160 repeats the action of sucking and compressing the refrigerant while reciprocating inside the cylinder bores 131 and 141 of the front and rear cylinder blocks 130 and 140. It will be done.

That is, in the suction stroke of the piston 170, an external refrigerant is supplied into the swash plate chamber 136 through the suction port 146, and then the cylinder bore 131 (through the flow path 151 of the drive shaft 150) ( 141 is directly sucked in, and during the compression stroke of the piston 170, the refrigerant sucked into the cylinder bore (131, 141) is compressed by the piston 170, the front and rear housing (110, 120) Is discharged into the discharge chambers 111 and 121 of the discharge chamber and discharged through the discharge passages 134 and 144 and the muffler 135 and 145 of the front and rear cylinder blocks 130 and 140 to the discharge port 147. Will be.

As described above, in the present invention, the flow path 151 is formed in the drive shaft 150 so that the refrigerant in the swash plate chamber 136 is directly sucked into the cylinder bores 131 and 141. Although only the case where the rotary valve configuration is applied to the fixed displacement swash plate compressor 100 has been described, the present invention is not limited thereto and may be applied to various types of compressors such as an electric compressor in the same method and configuration. You can get the effect.

As described above, according to the present invention, the refrigerant introduced from the swash plate chamber into the cylinder bore through the suction passage in communication with the cylinder bore through the hollow drive shaft to achieve uniform refrigerant distribution to each cylinder bore on both sides of the swash plate chamber. In the suction structure, the swash plate is compressed during the compression stroke by making the gap between the outer circumferential surface of the drive shaft front side and the inner circumferential surface of the shaft support hole of the front cylinder block larger than the gap between the outer circumferential surface of the drive shaft rear side and the inner circumferential surface of the shaft support hole of the rear cylinder block. The compressive reaction force can improve the sealing property between the outer peripheral surface of the drive shaft and the inner peripheral surface of the shaft support hole, and can minimize the wear of the driving shaft and the shaft support hole, thereby improving durability, thereby achieving optimal compression performance.

Claims (5)

The swash plate 160 which rotates in the swash plate chamber 136 inside the compressor 100 is inclinedly coupled therein, and a flow path for allowing the refrigerant sucked into the swash plate chamber 136 to move to the cylinder bores 131 and 141. A drive shaft 150 on which 151 is formed; The drive shaft 150 is rotatably installed in the shaft support holes 133 and 143, and a plurality of cylinder bores 131 and 141 are formed at both sides of the swash plate chamber 136, and the driving shaft 150 is The shaft support holes 133 and 143 and each cylinder bore 131 and 141 may be sucked into the cylinder bore 131 and 141 sequentially during the rotation of the drive shaft 150. The front and rear cylinder blocks 130 and 140 formed with suction passages 132 and 142 communicating therewith; A plurality of pistons (170) mounted on an outer circumference of the swash plate (160) via a shoe (165) and reciprocating in the cylinder bores (131, 141) in conjunction with a rotational movement of the swash plate (160); Front and rear housings 110 and 120 coupled to both sides of the front and rear cylinder blocks 130 and 140 and having discharge chambers 111 and 121 formed therein, respectively; In the compressor comprising a valve unit 180 interposed between the front and rear cylinder blocks 130, 140 and the front and rear housings 110, 120, respectively, A gap Da between the outer circumferential surface of the front side of the drive shaft 150 and the inner circumferential surface of the shaft support hole 133 of the front cylinder block 130 is an outer circumferential surface of the rear side of the drive shaft 150 and the shaft support hole of the rear cylinder block 140. The compressor characterized by being set larger than the clearance gap (Db) between the inner peripheral surfaces of (143). The method of claim 1, The gap Da is a compressor, characterized in that 1 to 10㎛ larger than the gap (Db). The method of claim 1, The inlet 152 of the flow path 151 is formed to communicate with the swash plate chamber 136, the outlet 153 is formed to communicate with the suction passages 132, 142 of the cylinder block 130, 140. Compressor, characterized in that. The method of claim 3, wherein The inlet 152 of the flow path 151 penetrates through one side of the hub 161 and the driving shaft 150 of the swash plate 160, and the outlet 153 of the flow path 151 is the flow path 151. Compressor, characterized in that formed on opposite sides of each other). The method of claim 1, The valve unit 180 has a plurality of refrigerant discharge holes 181a to communicate the cylinder bores 131 and 141 with the discharge chambers 111 and 121 of the front and rear housings 110 and 120. And a discharge lead valve (182) formed at one side of the valve plate (181) and the valve plate (181) to open and close the refrigerant discharge hole (181a).

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