KR101058307B1 - compressor - Google Patents

Abstract

The present invention relates to a compressor, by which the residual gas in the suction passage of the cylinder bore being compressed is bypassed to the cylinder bore being sucked, thereby minimizing the driving load of the compressor during recompression, thereby minimizing the compressor's durability. And it aims to provide the compressor which can improve performance.

In the present invention, the swash plate rotating in the swash plate chamber in the compressor is inclined, the flow path is formed so that the refrigerant sucked into the compressor from the outside can move to the cylinder bore, the flow path is at least in communication with the swash plate chamber, respectively A drive shaft having at least one inlet formed therein and spaced apart from the inlet to form a pair of outlets in opposite directions; The shaft support is rotatably installed in the shaft support hole, and a plurality of cylinder bores are formed at both sides of the swash plate chamber, and the shaft support is sequentially sucked into each cylinder bore during the rotation of the drive shaft. Front and rear cylinder block formed with a plurality of suction passages for communicating the ball 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 front and rear cylinder blocks and having discharge chambers formed therein; Front and rear valve units respectively interposed between the front and rear cylinder blocks and the front and rear housings; The compressor comprising: a groove-type residual gas bypass passage communicating with the suction passage to bypass the residual gas in the suction passage of the cylinder bore in the compression stroke to an adjacent cylinder bore in the suction stroke on the outer peripheral surface of the drive shaft. It is characterized in that is formed.

Compressor, drive shaft, flow path, cylinder bore, residual gas, top dead center, compression efficiency, load

Description

Compressor

1 is a cross-sectional view showing a typical fixed displacement swash plate compressor.

2 is a cross-sectional view showing a general variable displacement swash plate compressor.

3 is a partial sectional view of a variable displacement swash plate compressor according to one example of the prior art;

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;

Figure 6 is a perspective view of the drive shaft and the swash plate assembled in the compressor according to the present invention from another direction.

7 is a cross-sectional view showing the structure of a cylinder block in the compressor according to the present invention.

Description of the Related Art [0002]

100: compressor 110: front housing

111,121: discharge chamber

113,123: Bolted hole 120: Rear housing

130: front cylinder block 131a to 131e, 141a to 141e: 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

154: residual gas bypass passage 154a: first communication passage

154b: second communication path 154c: third communication path

160: Saphan 161: Hub

165: shoe 170: piston

180: thrust bearing 190: valve unit

191: valve plate 192: discharge lead valve

200: bolts

The present invention relates to a compressor, and more particularly, to bypass the residual gas in the suction passage of the cylinder bore under compression to the cylinder bore during suction to minimize the driving load of the compressor while preventing a rise in discharge temperature during recompression. It relates to a compressor that can improve the durability and performance of the compressor.

In general, an automobile compressor sucks refrigerant gas discharged from an evaporator and is discharged into a condenser gas by converting the refrigerant gas into a high temperature and high pressure state which is easily liquefied.

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.

Figure 1 shows the structure of a typical fixed displacement swash plate type compressor.

As shown, the fixed displacement swash plate compressor comprises: a front housing (10) in which the front cylinder block (11) is built; A rear housing (10a) coupled to the front housing (10) and having a rear cylinder block (11a) embedded therein; A plurality of cylinder bores 12 formed in the front and rear cylinder blocks 11 and 11a; A plurality of double-headed pistons 13 installed in a linear reciprocating motion across the cylinder bores 12 of the front and rear cylinder blocks 11 and 11a; A drive shaft 14 rotatably installed through the centers of the front and rear housings 10 and 10a and the front and rear cylinders 11 and 11a; In the swash plate chamber 15 formed between the center portion of the front and rear cylinders 11 and 11a, the swash plate which is inclined to the drive shaft 14 and rotates in accordance with the rotation of the drive shaft 14 to advance the pistons 13 forward and backward. (16); It consists of a structure including both the valve unit 17 is provided between the front and rear cylinders (11) (11a) and the inner surface of the front and rear housings (10) (10a). Here, although not shown in detail in the drawing, the valve unit 17 includes a valve plate having a refrigerant suction hole and a refrigerant discharge hole, a suction lead valve installed back and forth with the valve plate interposed therebetween, and a discharge lead valve.

In the swash plate type compressor configured as described above, the rotational force of the pulley receiving the driving force of the engine is selectively transmitted to the drive shaft 14 of the compressor through the disk and hub assembly by the intermittent action of the electromagnetic clutch, thereby driving the drive shaft 14. The pistons 13 rotate forward and backward by the swash plate 16 which rotates in an inclined state together with the drive shaft 14 according to the rotation. During the forward and backward movement of the piston 13, the suction lead valve opens the refrigerant suction hole during the suction stroke of the piston 13, while the discharge lead valve closes the refrigerant discharge hole so that the refrigerant flows in the front and rear cylinders 11. The cylinder bore 12 of 11a is sucked into the cylinder bore 12, and the discharge lead valve opens the refrigerant discharge hole during compression stroke of the piston 13, while the suction lead valve closes the refrigerant suction hole. The refrigerant inside is compressed and discharged toward the condenser.

On the other hand, Figure 2 shows a typical variable displacement swash plate compressor.

The swash plate type compressor includes: a cylinder block 21 having a plurality of cylinder bores 22 formed in a longitudinal direction along a concentric circle; A front housing 20 installed at the front of the cylinder block 21 to form a swash plate chamber 25 therein; A rear housing (20a) installed at a rear side of the cylinder block (21) to form a refrigerant suction chamber (27) and a discharge chamber (28) therein; A plurality of migraine pistons 23 inserted back and forth in each cylinder bore 22 of the cylinder block 21 and having a bridge formed at a rear end thereof; A drive shaft 24 rotatably penetrating the front housing 20 and having a rear end inserted into the center of the cylinder block 21 to be rotatably supported; A rotor 30 coupled to the drive shaft 24 in the swash plate chamber 25 to rotate together with the drive shaft 24; In the interior of the front housing 20 is installed to be inclined around the drive shaft 24, the edge is rotatably inserted into the insertion space formed by the bridge of each piston 23, one side of the front surface of the rotor 30 A swash plate 26 pivotally hinged to and rotatable with the rotor 30 and capable of tilt adjustment; A valve unit 29 is formed between the cylinder block 21 and the rear housing 20a to suck and discharge the refrigerant. The valve unit 29 includes a valve plate 29a having a refrigerant suction hole and a refrigerant discharge hole, a suction lead valve 29b and a discharge lead valve 29c provided before and after the valve plate 29a, and discharged. At the rear side of the reed valve 29c, a retainer 31 for limiting the opening degree of the discharge lead valve 29c is provided. Reference numeral 32 denotes a pressure regulating device which acts to change the inclination angle of the swash plate by adjusting the fluid pressure level in the swash plate chamber 25.

In the swash plate type compressor configured as described above, the drive shaft 24 is rotated by receiving the power of the engine, and the rotor 30 and the swash plate hinged to the rotor 30 are rotated according to the rotation of the drive shaft 24 ( 26 rotates with the drive shaft 24. Since the swash plate 26 rotates in an inclined state, the phase is continuously changed back and forth with respect to a point inside the swash plate chamber 25, so that each piston 23 coupled with the swash plate 26 is in phase with the swash plate 26. In response to the change, the cylinder bore 22 moves forward and backward. Therefore, during the suction stroke of the piston 23, a vacuum pressure is generated inside the cylinder bore 22, and the suction lead valve 29b of the valve unit 29 is opened by this vacuum pressure, and accordingly, the rear housing is released from the evaporator. The refrigerant supplied to the suction chamber 27 of 20a flows into the cylinder bore 22 through the refrigerant suction hole of the valve plate 29a and the suction lead valve 29b. In the compression stroke of the piston 23, the refrigerant introduced into the cylinder bore 22 is compressed, and the discharge lead valve 29c opens the refrigerant discharge hole by the compression pressure of the refrigerant. Therefore, the compressed refrigerant is discharged from the cylinder bore 22 through the valve plate 29a and the discharge lead valve 29c to the discharge chamber 28 of the rear housing 20a and then pumped toward the condenser.

However, in the fixed displacement swash plate compressor as well as the variable displacement swash plate compressor described above, immediately after the piston is compressed, that is, the piston moves through the bottom dead center to the highest top dead center and is sucked into the cylinder bore of the cylinder block. Immediately after maximizing the compressed refrigerant, the compressed high-temperature, high-pressure refrigerant gas is left in a small gap between the valve unit and the cylinder bore interposed between the cylinder block and the housing without being completely discharged. Therefore, this residual gas re-expands with movement to the bottom dead center position of the piston, resulting in a decrease in the suction amount into the cylinder bore. Such a pressure loss and a decrease in the suction amount into the cylinder bore lead to deterioration of the volume efficiency. There was a problem.

As a countermeasure to solve this problem, U.S. Patent No. 5,232,349 has a variable capacity for improving the volumetric efficiency by less re-expansion of residual gas during the suction stroke of the cylinder bore and reliably sucking the refrigerant gas in the suction chamber into the cylinder bore. A type compressor is disclosed.

As shown in FIG. 3, the conventional compressor has a suction passage 43a to 43f for radially communicating the cylinder bores 41a to 41f and the shaft hole 42, and a drive shaft (not shown). It is synchronously rotatably coupled, and communicates with a suction chamber (not shown) which communicates with the shaft hole 42 of the cylinder block 40 and the suction passages 43a through 43f of the cylinder bores 41a through 41f in turn. Residual gas bypass which bypasses the rotary valve 50 having the groove-shaped communication path 51 and the residual gas in the cylinder bore from the cylinder bore 41f on the high pressure side to the cylinder bore 41c on the low pressure side. It consists of a structure including the passage (53).

The residual gas bypass passage 53 may be formed in a hole or groove shape. For example, the residual gas bypass passage 53 is formed through the inside of the rotary valve 50, and immediately after the completion of suction and the high pressure side cylinder bore 41f. Are arranged at an angle of 180 degrees around the axis of the drive shaft so as to be in communication with each of the low pressure side cylinder bores 41c.

In the compressor having such a structure, as the rotary valve 50 rotates in synchronism with the drive shaft, the refrigerant in the suction chamber is sucked into each cylinder bore 41a to 41f in turn, and the suction action of the refrigerant is caused to occur in each cylinder bore 41a to 41f. The pressure loss is extremely low because it runs smoothly and consistently. In addition, when the rotary valve 50 rotates in synchronization with the drive shaft, the residual gas is bypassed from the high pressure side cylinder bore 41f to the low pressure side cylinder bore 41c at the time of the compression stroke of the piston, and at the time of the suction stroke of the piston. There is less re-expansion of residual gas, and the refrigerant in the suction chamber is reliably sucked into the cylinder bores 41a to 41f, thereby maintaining high volumetric efficiency.

However, since the conventional technology bypasses the residual gas from the high pressure side cylinder bore 41f where the compression stroke is completed to the low pressure side cylinder bore 41c where the suction stroke is completed, the high temperature residual gas bypassed. When recompressing the high temperature again to increase the discharge temperature, as well as to give the compressor an excessive driving load, there was a problem that greatly impairs the durability of the compressor.

Accordingly, the present invention has been made in order to solve the above-described problems, while bypassing the residual gas in the suction passage of the cylinder bore under compression to the cylinder bore during the suction stroke, while preventing the rise of the discharge temperature during recompression. It is an object of the present invention to provide a compressor that can improve the durability and performance of the compressor by minimizing the driving load of the compressor.

The present invention for achieving the above object is a swash plate rotating in the swash plate chamber inside the compressor is inclined, the flow path is formed therein to allow the refrigerant sucked into the compressor from the outside to move to the cylinder bore, the flow path is At least one inlet formed in communication with the swash plate chamber, the drive shaft being spaced apart from the inlet and having a pair of outlets in opposite directions;

The shaft support is rotatably installed in the shaft support hole, and a plurality of cylinder bores are formed at both sides of the swash plate chamber, and the shaft support is sequentially sucked into each cylinder bore during the rotation of the drive shaft. Front and rear cylinder block formed with a plurality of suction passages for communicating the ball 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 front and rear cylinder blocks and having discharge chambers formed therein, respectively;

Front and rear valve units respectively interposed between the front and rear cylinder blocks and the front and rear housings;

In the compressor comprising:

On the outer circumferential surface of the drive shaft, a groove-type residual gas bypass passage communicating with the suction passage is formed so as to bypass the residual gas in the suction passage of the cylinder bore in the compression stroke to the adjacent cylinder bore in the suction stroke.

The residual gas bypass passage is in communication with the suction passage when the piston reaches the tip of the suction passage during the compression stroke.

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 4 is an exploded perspective view showing a compressor according to the present invention, Figure 5 is a cross-sectional view showing a compressor according to the present invention, Figure 6 is a perspective view of the drive shaft and the swash plate assembled in the compressor according to the present invention viewed from another direction. 7 is a cross-sectional view showing the structure of a cylinder block in the compressor according to the present invention.

Although the present invention describes an example of a fixed displacement swash plate compressor, the same can be applied to a variable displacement compressor.

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

The applicant of the present invention has applied for an example of such a compressor by Korean Patent Application No. 2005-74186.

That is, the compressor according to the pre- filed invention, the flow path is formed so that the refrigerant sucked into the compressor inside the drive shaft in which the swash plate rotating in the swash plate chamber in the compressor is inclined to move to the cylinder bore formed in the cylinder block, It consists of a structure formed spaced apart from the inlet and the outlet on 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.

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, by which the residual gas in the suction passage of the cylinder bore in the compression stroke is bypassed to the cylinder bore in the suction stroke, thereby preventing the rise of the discharge temperature during recompression. It is to improve the durability and performance of the compressor by minimizing the load.

That is, the compressor according to the present invention, as shown in the drawing, the drive shaft 150 and the drive shaft 150 is coupled to the swash plate 160 to rotate in the swash plate chamber 136 in the compressor 100 inclined; The front and rear cylinder blocks 130 and 140 rotatably installed in the shaft support holes 133 and 143, and are mounted on the outer circumference of the swash plate 160 via a shoe 165 and rotate the swash plate 160. A plurality of pistons 170 reciprocating inside the cylinder bores 131a to 131e and 141a to 141e formed on both sides of the swash plate chamber 136 of the front and rear cylinder blocks 130 and 140 in conjunction with Front and rear housings 110 and 120 coupled to both sides of the front and rear cylinder blocks 130 and 140 and the discharge chambers 111 and 121 are formed therein, and the front and rear cylinder blocks 130. The valve unit 190 is disposed between the 140 and the front and rear housings 110 and 120, respectively.

The front and rear housings 110 and 120 are formed with a plurality of bolt fastening holes 113 and 123 at edges of the inside, and the front and rear housings through the bolt fastening holes 113 and 123. 110 and 120 are fastened / fixed to the mutual bolts 200 in the state in which the above components are assembled. Of course, the front and rear cylinder blocks 130, 140 and the valve unit 190 is formed with bolt fastening holes 138, 148, 194 so that the bolt 200 can pass through.

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 center of the front housing 110. It extends and is engaged with the electromagnetic clutch (not shown).

On the other hand, since the swash plate 160 is moved forward and backward while the swash plate 160 is rotated in an inclined state while the compressor 100 is driven, the swash plate 160 flows from side to side by an axial load so that the swash plate 160 is deformed. Or the driving shaft 150 may be deformed, and in order to prevent this, generally, a thrust bearing 180 is interposed between both ends of the swash plate 160 and the front and rear cylinder blocks 130 and 140. have.

The swash plate 160 rotating in the swash plate chamber 136 is inclinedly coupled to the drive shaft 150, and the suction refrigerant sucked into the swash plate chamber 136 through the suction port 146 from the outside is swash plate. A flow path 151 is formed to communicate the swash plate chamber 136 and the cylinder bores 131a to 131e and 141a to 141e so as to move through the 160 to the cylinder bores 131a to 131e and 141a to 141e. do.

In the flow path 151, an inlet 152 for sucking the coolant and an outlet 153 for discharging the coolant are formed at positions spaced apart from each other. The inlet 152 is formed to communicate with the swash plate chamber 136, the outlet 153 is formed to communicate with each suction passage 132, 142 of the front and rear cylinder blocks 130, 140. do.

Here, the inlet 152 of the flow path 151 is formed by vertically penetrating one side of the hub 161 and the drive shaft 150 of the swash plate 160. 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 on both sides thereof in opposite directions.

The outlet 153 of the flow path 151 is formed in opposite directions on both sides of the drive shaft 151 while being spaced apart from the inlet 152 of the flow path 151. It is formed on the opposite side of the residual gas bypass passage 154 to be described below. This structure allows the refrigerant to be sucked into the cylinder bores 131a to 131e and 141a to 141e provided at both sides of the swash plate chamber 136 when the driving shaft 150 rotates.

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

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 provided with a plurality of cylinder bores 131a to 131e and 141a to 141e, respectively, on both sides of the swash plate chamber 136, and the driving shaft 150 at the center thereof. Axial support holes 133 and 143 are formed to support the rotatably.

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 in sequence during the rotation of the drive shaft 150 Suction passages 132 and 142 which communicate the axial support holes 133 and 143 and the respective cylinder bores 131a to 131e and 141a to 141e so as to be sucked into the 131a to 131e and 141a to 141e. Is formed.

On the other hand, the piston 170 is not completely in contact with the end surface corresponding to the compression surface of the cylinder bore (131a to 131e) (141a to 141e) due to the dimensional tolerances thereby the valve unit 190 and the cylinder bore (131a) A constant gap is formed between 131e and 141a-141e.

Due to the presence of the gap, when the piston 170 reaches the highest top dead center where the refrigerant is compressed through the bottom dead center where the refrigerant suction process starts and the compression is completed, the compressed high temperature and high pressure refrigerant gas is discharged. It is not completely discharged through the seal and remains in the gap. When the high-temperature, high-pressure refrigerant gas is left in the gap, the cylinder blocks 131a to 131e and 141a to 141e may overheat, resulting in thermal deformation, and inability to perform smooth refrigerant intake during recompression. The problem of lowering the rate will occur.

Therefore, in order to solve this problem, the present invention forms a residual gas bypass passage 154 on the outer circumferential surface of the drive shaft 150.

That is, the residual gas bypass passage 154 has a groove-like structure in communication with the suction passages 132 and 142 during the compression stroke, and the suction passage 132 of the cylinder bores 131a to 131e and 141a to 141e. The residual gas in 142 is bypassed from the cylinder bores 131e and 141e in the compression stroke to the adjacent cylinder bores 131a and 141a in the suction stroke.

More specifically, the residual gas bypass passage 154 is formed along the longitudinal direction of the drive shaft 150 as shown in FIGS. 6 and 7 and the cylinder bores 131e and 141e in the compression stroke. A first communication path 154a communicating with the suction passages 132 and 142 of the second communication path, and a second communication communication with the suction passages 132 and 142 of the adjacent cylinder bores 131a and 141a during the suction stroke. It consists of the furnace 154b, the 3rd communication path 154c which connects the one end of the said 1st communication path 154a, and the one end of the 2nd communication path 154b. The depth of the residual gas bypass passage 154 may be in communication with the suction passages 132 and 142.

Here, the widths of the at least the first communication path 154a and the second communication path 154b are the cylinder bores 131e and 141e during the compression stroke and the adjacent cylinder bores 131a and 141a during the suction stroke. It is preferable to set the width substantially equal to the respective width of. If the widths of the first communication path 154a and the second communication path 154b are different from each of the cylinder bores 131e and 141e in the compression stroke and the adjacent cylinder bores 131a and 141a in the suction stroke, respectively. If it is larger or smaller than the width, the refrigerant gas remaining in the cylinder bore will leak, and the intended purpose of the invention will not be achieved.

According to this structure, as shown in FIG. 5, when the end of the piston 170 reaches the front end of the suction passages 132 and 142 during the compression stroke, that is, the piston 170 is in the "A" position. When reaching, the residual gas bypass passage 154 of the drive shaft 150 is in communication with the cylinder bores 131e and 141e during the compression stroke and the adjacent cylinder bores 131a and 141a during the suction stroke. Instead of bypassing the gas remaining in the cylinder bore immediately after the completion of the compression stroke from the high pressure side cylinder bores 131f and 141f as before, the suction passage 132 of the cylinder bores 131e and 141e in which compression is in progress. The gas remaining in 142 can be bypassed to the cylinder bores 131a and 141a in which suction is in progress.

This prevents overheating of the cylinder bore and suppresses the rise of the discharge temperature with little increase in temperature upon recompression of the residual gas. Durability and performance can be greatly improved. In addition, the residual gas is directly bypassed from the suction passages 132 and 142 of the cylinder bores 131e and 141e to the adjacent cylinder bores 131a and 141a so that the moving distance of the bypass is relatively higher than before. It also has the advantage of being able to bypass residual gas smoothly.

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. At this time, the outer surface of the cylinder block 130, 140 is formed with a muffler 135, 145 to expand the discharge passage 134 to reduce the pulsation pressure of the discharge refrigerant to reduce the noise do.

The valve unit 190 has a plurality of refrigerants to communicate the cylinder bores 131a to 131e and 141a to 141e with the discharge chambers 111 and 121 of the front and rear housings 110 and 120. A valve plate 191 having a discharge hole 191a formed thereon, and a discharge lead valve 192 installed at one side of the valve plate 191 to open and close the refrigerant discharge hole 191a.

That is, the discharge lead valve 192 is installed in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 on the basis of the valve plate 191 to compress the stroke of the piston 170. The valve plate 192a is elastically deformed to open the refrigerant discharge hole 191a and to close the refrigerant discharge hole 191a when the suction stroke is performed.

In addition, the valve plate 191 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 191b is formed to communicate the discharge chambers 111 and 121 with the discharge passages 134 and 144 so as to be discharged to the discharge port 147 via the 144.

Meanwhile, the valve unit 190 has fixing pins 193 provided on both sides of the valve plate 191 facing the front and rear housings 110 and 120 and the front and rear cylinder blocks 130 and 140. It is coupled and fixed while being inserted into a fixing hole (not shown) formed on the surface.

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 ( A plurality of pistons 170 linked to the rotational movement of the 160 suctions and compresses the refrigerant while reciprocating inside the cylinder bores 131a to 131e and 141a to 141e of the front and rear cylinder blocks 130 and 140. It will repeat the action.

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 is formed through the inlet 152 of the flow path 151 of the drive shaft 150. It is directly sucked into the bores 131a to 131e and 141a to 141e.

In the compression stroke of the piston 170, the refrigerant sucked into the cylinder bores 131a to 131e and 141a to 141e is compressed by the piston 170 and then discharged from the front and rear housings 110 and 120. Discharged into the seals 111 and 121 is discharged to the discharge port 147 through the discharge passages 134 and 144 and the muffler 135 and 145 of the front and rear cylinder blocks 130 and 140. .

As described above, in the present invention, a fixed capacity swash plate type compressor includes a drive shaft integrated suction rotary valve configured to form a flow path inside the drive shaft to directly suck the refrigerant in the swash chamber into the cylinder bore. Although only the case of the present invention has been described, the present invention is not limited thereto, and the present invention can be applied to various kinds of compressors such as an electric compressor in the same method and configuration, and the same effect can be obtained.

According to the present invention described above, a structure in which the refrigerant introduced from the swash plate chamber is sucked into the cylinder bore through a suction passage communicating 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. By forming a residual gas bypass passage on the outer circumferential surface of the drive shaft to bypass the refrigerant gas remaining in the suction passage of the cylinder bore in the compression stroke to the cylinder bore in the suction stroke, thereby preventing the rise of the discharge temperature during recompression. By minimizing the driving load of the compressor, the durability and performance of the compressor can be greatly improved.

Claims (2)

The swash plate 160 that rotates in the swash plate chamber 136 inside the compressor 100 is inclinedly coupled therein, and the refrigerant sucked into the compressor 100 from the outside into the cylinder bores 131a to 131e and 141a to 141e. A flow path 151 is formed to move, and the flow path 151 is formed with at least one inlet 152 communicating with the swash plate chamber 136, and is spaced apart from the inlet 152. Drive shafts 150 having outlets 153 formed in opposite directions from each other; The drive shaft 150 is rotatably installed in the shaft support holes 133 and 143, and a plurality of cylinder bores 131a to 131e and 141a to 141e are formed at both sides of the swash plate chamber 136, and the drive shaft ( Each of the shaft support holes 133 and 143 may be sequentially sucked into the cylinder bores 131a to 131e and 141a to 141e when the refrigerant sucked into the flow path 151 of the 150 is rotated. Front and rear cylinder blocks 130 and 140 formed with suction passages 132 and 142 for communicating cylinder bores 131a to 131e and 141a to 141e; A plurality of pistons 170 mounted on the outer circumference of the swash plate 160 via a shoe 165 and reciprocating in the cylinder bores 131a to 131e and 141a to 141e in conjunction with the 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; A valve unit 190 interposed between the front and rear cylinder blocks 130 and 140 and the front and rear housings 110 and 120, respectively; In the compressor comprising: The outer circumferential surface of the drive shaft 150 is configured to bypass residual gas in the suction passages 132 and 142 of the cylinder bores 131e and 141e during the compression stroke to adjacent cylinder bores 131a and 141a during the suction stroke. Residual gas bypass passage 154 of the groove shape in communication with the suction passages (132, 142) is formed, The residual gas bypass passage 154 is in communication with the suction passages 132 and 142 when the end of the piston 170 reaches the tip of the suction passages 132 and 142 during compression stroke. compressor. delete

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