KR20080006258A - Compressor - Google Patents

Abstract

A compressor is provided to improve compressing efficiency by reducing a dead volume space according to the forming position of a suction passage during a maximum compressing process of a refrigerant sucked in a cylinder bore by widely forming the suction passage. A compressor includes a driving shaft, front and rear cylinder blocks, a plurality of pistons, front and rear housings, and a valve unit. The driving shaft is coupled with a swash plate rotating in a swash plate room. The driving shaft has a passage to move a refrigerant sucked in the compressor to cylinder bores(131). The cylinder blocks have shaft supporting holes(133) where the driving shaft is rotatably installed, a plurality of cylinder bores at both sides of the swash plate room, and suction paths(132) connecting the shaft supporting holes and the cylinder bores. The pistons are mounted at the outer periphery of the swash plate with a shoe interposed, and reciprocate in the cylinder bores, interlocking with the rotating motion of the swash plate. The front and rear housings are coupled to both sides of the cylinder blocks, and have discharge rooms inside. The valve unit is arranged between the cylinder blocks and the front and rear housings. The suction paths are formed a predetermined distance(d) apart from the compression surfaces of the cylinder bores.

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 partial perspective view of a cylinder block 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;

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 partial perspective view of a cylinder block in the compressor according to the invention.

<Description of Signs of Major Parts of Drawings>

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, a cylinder through a suction passage through which the refrigerant introduced from the swash plate chamber communicates with the cylinder bore through a hollow drive shaft to achieve uniform refrigerant distribution to each cylinder bore on both sides of the swash plate chamber. Compressor that can greatly improve the compression efficiency by reducing the volumetric ratio of the compressed refrigerant by minimizing the volumetric space according to the position of the suction passage during the maximum compression process of the refrigerant sucked into the cylinder bore. It is about.

Typically, a compressor for automobiles sucks refrigerant gas discharged after evaporation is completed and converts the refrigerant gas into a refrigerant gas in a high temperature and high pressure state that is easily liquefied and discharged into a condenser.

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 the refrigerant moves 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 fixing pins are formed on both sides of the valve plate 61. 65 is assembled in a fixed position while being inserted into the fixing hole 15 formed on the opposite surface 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, when the piston 50 is in the suction stroke, the suction lead valve 63 is opened by moving the piston 50 from the top dead center to the bottom dead center, wherein the refrigerant in the suction chamber 11 is a valve plate. It is sucked into the cylinder bore 21 through the refrigerant suction hole of the.

In the compression stroke of the piston 50, the refrigerant inside the cylinder bore 21 is compressed by the piston 50 moving from the bottom dead center to the top dead center. At this time, the discharge lead valve 62 is opened. The refrigerant flows to the first discharge chamber 12a of the front and rear housings 10 and 10a through the refrigerant discharge hole of the valve plate.

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 suction resistance caused by a complicated internal refrigerant flow path and a loss due to elastic resistance of the suction lead valve 63 when the valve unit 60 is opened and closed. As a result, 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 compressor). That is, the above technology applies a suction shaft integrated suction rotary valve without a suction lead valve and allows the refrigerant to directly enter the cylinder bore from the rear of the driving shaft through the inside of the driving shaft in order to reduce the loss caused by the suction resistance. will be.

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 Korean Patent Publication No. 2003-47729, since refrigerant is introduced from the rear of the drive shaft, a large amount of refrigerant is sucked into the rear cylinder bore and a small amount of refrigerant is sucked into the front cylinder bore, so that the compressor achieves an optimum compression performance. There was a problem that could not be exercised.

In particular, the Korean Patent Publication No. 2003-47729 communicates the cylinder bore 91 and the drive shaft bore 92 as illustrated in FIG. 3 in order to allow refrigerant to flow from the rear of the drive shaft and be sucked to the cylinder bore side. In forming the suction passage 93 in the cylinder block 90, the suction passage 93 is extended to the compression surface, which is the end face of the cylinder bore 91, so that the suction passage 93 extends into the cylinder bore through the suction passage. There was a problem that the compression efficiency is greatly reduced during the maximum compression process of the sucked refrigerant. That is, since the suction passage is in contact with the compressed surface position of the cylinder bore, when the piston moves through the bottom dead center to the highest top dead center to compress the refrigerant sucked into the cylinder bore to the maximum, the end surface area of the suction passage is dead volume. It becomes a space. Accordingly, there is a problem in that the compression ratio of the compressor cannot be efficiently exhibited by increasing the dead volume ratio of the compressed refrigerant, thereby greatly reducing the compression efficiency.

In addition, in the case of Korean Patent Application No. 2005-74185, there is a limitation in increasing the inlet of the flow path, which not only increases the refrigerant suction resistance, but also does not provide sufficient lubricating action to the thrust bearing supporting the swash plate. By doing so, there was a problem of increasing durability of the thrust bearing to lower durability.

Accordingly, the present invention has been made to solve the above-described problems, and the refrigerant introduced from the swash plate chamber communicates with the cylinder bore through the hollow drive shaft so that uniform refrigerant distribution is achieved by the cylinder bores on both sides of the swash plate chamber. In the structure that is sucked into the cylinder bore through the suction passage, the compression efficiency is reduced by minimizing the volumetric space according to the position of the suction passage in the maximum compression process of the refrigerant sucked into the cylinder bore. An object of the present invention is to provide a compressor that can be greatly improved.

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 cylinder block having a suction passage communicating the shaft support hole with 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 the compressor comprising a valve unit interposed between the cylinder block and the front, rear housing, characterized in that the suction passage is formed at a predetermined distance from the end surface which is the compression surface of the cylinder bore.

In the present invention, the distance is characterized in that 6mm ~ 9mm.

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 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 showing the disassembled drive shaft and the swash plate in the compressor according to the invention, Figure 7 Is a partial perspective view of a cylinder block in the compressor according to the 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.

The applicant of the present invention has applied for an example of such a compressor by Korean Patent Application No. 2005-74185.

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 refrigerant flows 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.

In the present invention employing such a structure of the compressor, in the maximum compression process of the refrigerant sucked into the cylinder bore in the compression process by minimizing the volumetric space according to the position of the suction passage to reduce the volumetric ratio of the compressed refrigerant significantly In order to improve the performance of the compressor.

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 may move through the swash plate 160 to the cylinder bores 131 and 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 cylinder bores 131 and 141 are formed to be sucked into the 131 and 141.

Here, the suction passage 132, 142 is a predetermined distance d from the end surface of the cylinder bores 131, 141, which corresponds to the compression surface during the compression stroke of the piston, as shown in Figs. ) Is formed. This is due to the dead space according to the position of the suction passage formed long to the end surface of the cylinder bore when the piston is moved to the highest top dead center, which is the maximum compression point as described above with reference to FIG. 3. It is for preventing efficiency from falling. In Fig. 3, since the suction passage is narrowly extended to the compression surface in a length of about 12 mm, the suction passage formed at the compression surface portion at the top dead center position of the piston becomes a private space. In the present invention, by forming the suction passage at a predetermined distance from the compression surface which is the end surface of the cylinder bore, it is possible to minimize the private space formed on the compression surface as in the prior art.

The distance d is appropriately determined according to the capacity of the compressor and is preferably at least 6 mm. For example, when the capacity of the compressor is 155cc, the width of the cylinder blocks 130 and 140 is approximately 35mm, so that the suction passages 132 and 142 are formed at a distance of 6mm from the compression surface, but the capacity of the compressor is higher than that. When the width of the cylinder block 130, 14 is approximately 38mm when, for example, 177cc, the suction passages 132 and 142 at this time may be formed at a distance of 9mm from the compression surface.

As such, the reason for specifying the position distance d of the suction passages 132 and 142 is to prevent leakage of the refrigerant during the compression process of the refrigerant. In general, when the piston 170 reaches its highest top dead center, the refrigerant has the highest pressure. In this case, when the suction passages 132 and 142 are formed at a position outside the range of 6 mm to 9 mm from the compression surface, the sealing area between the cylinder bores 130 and 140 and the piston 170 becomes smaller. As a result, the refrigerant having a high pressure leaks between them, so that the optimum compression efficiency cannot be exhibited.

Particularly, in the present invention, if the length of the suction passages 132 and 142 is reduced to about 6 mm or less as compared with the prior art, the contact area of the sealing area between the drive shaft 150 and the shaft support holes 133 and 143 is equivalent. Since it is not possible to secure a sufficient suction amount during the refrigerant suction process, and the compressed refrigerant may leak to the swash plate chamber side, the suction passages 132 and 142 have a wider rectangular shape than the conventional one to prevent this. Forming.

As described above, in the present invention, in forming the suction passages 132 and 142 in the cylinder bores 131 and 141, the width of the cylinder bore 131 and 141 at a predetermined distance from the compression surface of the cylinder bores 131 and 141 is rectangular. In this case, it is possible to increase the dead volume ratio during the maximum compression process of the refrigerant sucked into the cylinder bores 131 and 141 through the suction passages 132 and 142 and to prevent leakage of the compressed refrigerant, thereby providing optimum compression efficiency. Can exert.

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.

Therefore, 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 (expanded the discharge passage 134, 144 to reduce the pulsation pressure of the discharge refrigerant to reduce noise) 135) 145 are 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 hole 112 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 the inner edge thereof, and the front and rear through the bolt fastening holes 113 and 123. The housings 110 and 120 are fastened / fixed with the mutual bolts 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 drive shaft is integrally formed to form a flow path 151 inside the drive shaft 150 to directly suck the refrigerant in the swash plate chamber 136 into the cylinder bores 131 and 141. Although only the case where the suction rotary valve configuration is applied to the fixed displacement swash plate type 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 manner and configuration. The same effect can be achieved.

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 inside of the hollow drive shaft to achieve uniform refrigerant distribution to each cylinder bore on both sides of the swash plate chamber. In this case, the suction passage is formed in a wide structure at a certain distance from the compression surface of the cylinder bore, thereby minimizing the dead space according to the position of the suction passage during the maximum compression process of the refrigerant sucked into the cylinder bore. Can be greatly improved.

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. 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 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 cylinder block 130, 140 and the front, rear housing 110, 120, respectively, The suction passage (132) (142) is formed with a predetermined distance (d) from the end surface which is the compression surface of the cylinder bore (131) (141). The method of claim 1, The distance (d) is a compressor, characterized in that 6mm to 9mm. 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 both sides of the opposite side). 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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