KR20100092722A - Swash plate type compressor - Google Patents

Abstract

PURPOSE: A swash plate type compressor is provided to minimize the useless volume by reducing the length of the suction passage formed in a cylinder block by decreasing the whole diameter of bearing assembly. CONSTITUTION: A swash plate type compressor comprises a front housing(110), a rear housing(120), cylinder blocks(130,130'), a rotary shaft(140), a piston(158), and bearing assembly(145). The cylinder block is located between the front housing and the rear housing and comprises a plurality of cylinder bores(135) and a swash plate chamber. While linearly reciprocating in the cylinder bore according to the rotational motion of a swash plate(142), the piston compresses refrigerant. The bearing assembly supports the force applied to the rotary shaft in a longitudinal direction. The bearing assembly comprises a first race, a second race, and a relative rotation ring. The first race is rotated with the swash plate. The second lace is fixed to the cylinder block. The relative rotation ring comprises a ring shape body and a contact part. The contact part makes contact with the first and second races. The body and the contact part are integrally formed from engineering plastics.

Description

Swash plate type compressor

The present invention relates to a swash plate compressor, and more particularly, to a swash plate compressor in which rotation of a swash plate installed on a rotating shaft generates a linear reciprocating motion of a piston in a cylinder bore to compress a refrigerant.

In general, the compressor used in the air conditioning system of the automobile sucks the working fluid from the evaporator to the high temperature and high pressure which is easy to liquefy, and delivers it to the condenser.

In such a compressor, a configuration for compressing a working fluid includes a reciprocating type that performs compression while reciprocating and a rotary type that performs compression while rotating. In the reciprocating type, there is a crank type for transmitting a driving force of a driving source to a plurality of pistons through a crank, a swash plate type for transferring a rotating shaft provided with a swash plate, and a wobble plate type using a wobble plate. Rotary type includes vane rotary type using rotary rotary shaft and vane, and scroll type using rotary scroll and fixed scroll.

1 illustrates a configuration of a general swash plate compressor. A schematic configuration of a swash plate compressor will be described with reference to the drawings. The front and rear housings 10, the rear housing 20, and the front and rear cylinder blocks 30 and 30 ′ form the skeleton and the exterior of the compressor 1. A rotating shaft 40 is installed through the center of the front housing 10 and the front and rear cylinder blocks 30 and 30 ', and the rotating shaft 40 is rotated by an external driving force. The front housing 10 and the rear housing 20 are coupled to the outside of the front and rear cylinder blocks 30 and 30 ', respectively.

The piston 50, which linearly reciprocates by the rotation of the rotary shaft 40, is installed in the cylinder bore 35 of the front and rear cylinder blocks 30, 30 ', and compresses the working fluid compressed by the cylinder bore 35. A valve unit 60 for controlling discharge is installed between the front housing 10 and the front cylinder block 30 and between the rear housing 20 and the rear cylinder block 30 '. The front housing 10, the rear housing 20, the front and rear cylinder blocks (30, 30 ') are fastened to each other by a fixing bolt 70, the fixing bolt 70 is the front housing 10, the rear housing 20, penetrates the front and rear cylinder blocks 30 and 30 '.

Now, the detailed configuration of each component described above will be described. First, the front housing 10 has a cylindrical hole 12 through which the rotating shaft 40 passes through the center in a substantially disk shape. The shaft hole 12 penetrates the center of the boss portion 13 protruding from the center of one surface of the front housing 10. The discharge chamber 14 is recessed on the opposite surface on which the boss portion 13 of the front housing 10 is formed. The discharge chamber 14 is formed over a substantially ring-shaped region, and selectively communicates with each cylinder bore 35 of the front cylinder block 30 through the valve unit 60.

The rear housing 20 is mounted on one surface of the rear cylinder block 30 '. The discharge chamber 22 is formed on the surface of the rear housing 20 facing the rear cylinder block 30 '. The discharge chamber 22 is selectively formed to communicate with the cylinder bores 35 formed in the rear cylinder block 30 'through the valve unit 60.

 The front and rear cylinder blocks 30 and 30 'are recessed portions formed on surfaces coupled to each other to form the swash plate chamber 31. In the swash plate chamber 31, a swash plate 42 installed on the rotating shaft 40 is rotatably positioned. The shaft support hole 32 is formed through the front and rear cylinder blocks 30 and 30 '. The rotary shaft 40 penetrates the shaft support hole 32.

A plurality of cylindrical cylinder bores 35 are formed in the front and rear cylinder blocks 30 and 30 'in the direction of forming the shaft support hole 32 with the shaft support hole 32 as the center. Of course, the cylinder bores 35 are formed at positions corresponding to the front and rear cylinder blocks 30 and 30 ', respectively.

The cylinder bore 35 and the shaft support hole 32 communicate with each other through the suction passage 36, respectively. The suction passage 36 allows the working fluid delivered through the inside of the rotating shaft 40 to be delivered to the cylinder bore 35, respectively.

Discharge passages 38 are formed in the front and rear cylinder blocks 30 and 30 ′ so as to communicate with the discharge chambers 14 and 22 of the front and rear housings 10 and 20, respectively. The discharge passage 38 serves as a passage for discharging the working fluid compressed in the cylinder bore 35 to the outside.

The rotary shaft 40 has one end penetrating the front housing 10 and an intermediate part penetrating the front and rear cylinder blocks 30 and 30 '. An approximately disk-shaped swash plate 42 is inclined with respect to the extending direction of the rotating shaft 40 on the rotating shaft 40. The center of the swash plate 42 is provided with a hub 44 having a cylindrical shape, the rotation shaft 40 penetrates through the hub 44. A communication hole 44 ′ is drilled through the hub 44 so as to communicate with the inside of the rotation shaft 40. Then, a plurality of shoes 45 surrounding the edge of the swash plate 42 is installed. The shoe 45 is configured to move along the edge of the swash plate 42. Bearing assemblies 46 are respectively provided between both ends of the swash plate 42 and the cylinder blocks 30 and 30 '.

The bearing assembly 46 includes a plurality of bearings between the first race 46-1 which rotates together with the hub 44 and the second race 46-2 which is fixed to the cylinder blocks 30, 30 ′. A cage 46-3 having needles (not shown) is installed.

The flow path 47 through which the working fluid flows is formed in the rotary shaft 40. The flow passage 47 is formed long in the longitudinal direction of the rotation shaft 40 inside the rotation shaft 40. An inlet 48 and an outlet 48 ′ are formed on the outer surface of the rotation shaft 40. The inlet 48 communicates the swash plate chamber 31 and the flow passage 47, and the outlet 48 ′ communicates with the suction passage 36 of the front and rear cylinder blocks 30 and 30 ′. Formed in position. The position of the outlet 48 ′ should be formed in accordance with the compression order of the working fluid proceeding in each cylinder bore 35. Reference numeral 49 is a shaft sealing portion that prevents the gap between the inner surface of the shaft hole 12 of the front housing 10 and the outer surface of the rotary shaft 40.

Piston 50 is to linearly reciprocate the inside of the cylinder bore (35). The piston 50 has an approximately cylindrical shape corresponding to the inside of the cylinder bore 35, and both ends thereof are positioned at the cylinder bores 35 of the front and rear cylinder blocks 30 and 30 ', respectively. That is, both ends of each of the one piston 50 serves to compress the working fluid in the cylinder bore (35). The piston 50 is coupled to the middle of the shoe 45, the linear reciprocating motion in accordance with the rotation of the swash plate 42.

The valve unit 60 is used to control the discharge of the working fluid compressed in the cylinder bore 35 to the outside of the cylinder bore 35. The valve unit 60 includes a valve plate 62 which is installed in close contact with one surface of the front and rear cylinder blocks 30 and 30 ', and each cylinder bore 35 is provided on the valve plate 62. Discharge holes 64 are formed at corresponding positions. Discharge leads 66 are used to selectively open and close the discharge holes 64, respectively. The discharge lead 66 may be elastically deformed and elastically deformed according to the pressure of the working fluid in the cylinder bore 35 to open and close the discharge hole 64.

The valve plate 62 is formed in a substantially disk-shaped communication hole 67 at a position corresponding to the discharge passage 38. The communicating hole 67 serves to communicate the respective discharge chambers 14 and 22 with the discharge passage 38.

A muffler 68 is formed on the outer surface of the front and rear cylinder blocks 30 and 30 'so as to communicate with the discharge passage 38. The muffler 68 serves to reduce pulsation and noise of the working fluid. The muffler 68 is formed with a discharge port 69 for discharging the working fluid to the outside (condenser) of the compressor (1). For reference, a suction port (not shown) for transmitting a working fluid into the swash plate chamber 31 of the compressor 1 is formed at one side of the front and rear cylinder blocks 30 and 30 '. Reference numerals 16 and 18 denote oil chambers and communication paths, respectively.

The operation of the general compressor 1 having such a configuration will be described. As the rotary shaft 40 rotates by a driving force transmitted from the outside, the swash plate 42 is rotated with the rotation of the rotary shaft 40. Rotation of the swash plate 42 allows the piston 50 to make a straight reciprocating motion inside the cylinder bore 35.

At this time, as the rotary shaft 40 rotates, the flow passage 47 inside the rotary shaft 40 communicates with the cylinder bore 35 through the outlet 48 'and the suction passage 36. The communication between the flow passage 47 and the cylinder bore 35 allows the working fluid sucked into the swash plate chamber 31 to be transferred to the cylinder bore 35. For reference, the working fluid is sucked into the cylinder bore 35 when the piston 50 is located at the bottom dead center of the corresponding cylinder bore 35.

When the working fluid is transferred to the cylinder bore 35, and the piston 50 of the corresponding cylinder bore 35 moves in the direction of the valve plate 62, compression of the working fluid occurs. When the working fluid is compressed in the cylinder bore 35, the pressure inside the cylinder bore 35 becomes relatively high, and the tip of the discharge lead 66 is pushed and elastically deformed to open the discharge hole 64. do.

In this case, the working fluid compressed through the discharge hole 64 is transferred to the discharge chambers 14 and 22, and the working fluid delivered to the discharge chambers 14 and 22 is communicated through the communication hole 67. It is delivered to the muffler 68 via the discharge passage 38, and is transferred from the muffler 68 to the condenser through the discharge port 69.

As such, the pressure of the refrigerant acting on the piston 50 during the operation of the compressor 1 provides a force for moving the rotary shaft 40 in the longitudinal direction, which is supported by the bearing assembly 46. do.

However, the conventional compressor as described above has the following problems.

As in the related art, in order to supply refrigerant to the cylinder bore 35 through the flow passage 47 of the rotation shaft 40, the cylinder blocks 30 and 30 ′ are used for communication between the cylinder bore 35 and the flow passage 47. A suction passage 36 should be formed. However, the suction passage 36 is in communication with the cylinder bore 35, but the refrigerant therein cannot be compressed by the piston 50. Therefore, the volume of the suction passage 36 corresponds to a dead volume in which the refrigerant cannot be compressed. For reference, the t '(shortest distance between the cylinder bore 35 and the shaft support hole 32) of FIG. 2 is relatively large in the prior art, and thus the dead volume increases.

The presence of the suction passage 36 has a problem of lowering the compression efficiency of the compressor, it is necessary to solve this. To this end, as shown in FIG. 2, it is necessary to connect the center of the piston 50 and reduce the diameter of an imaginary circle (hereinafter referred to as a piston bore diameter) centered on the center of rotation of the rotary shaft 40. . However, in order to reduce the diameter of the piston bore, the diameter of the bearing assembly 46 needs to be reduced. In this case, there is a problem in that it does not properly support the force acting in the longitudinal direction of the rotation shaft 40.

Accordingly, in the configuration in which the bearing assembly 46, that is, the needle 46 or the ball is provided in the cage 46-1, there is a limit in reducing the diameter of the piston bore, so that the suction passage 36 is no longer reduced. I can't.

Therefore, an object of the present invention is to solve the problems of the prior art as described above, to minimize the volume of the suction passage for delivering the refrigerant to the cylinder bore in the swash plate compressor.

According to a feature of the present invention for achieving the above object, the present invention is located between the front and rear housings and the front and rear housings to form the outer appearance of at least both ends of the compressor, and the plurality of The cylinder bore is formed to penetrate, the cylinder block having a swash plate chamber therein, a rotating shaft in which the swash plate positioned in the swash plate chamber is rotatably installed, and a straight line in the cylinder bore according to the rotational movement of the swash plate. A swash plate type compressor comprising a piston for compressing a refrigerant while reciprocating and a bearing assembly installed between the swash plate and the cylinder block to support a force acting in the longitudinal direction on the rotating shaft, wherein the bearing assembly includes the swash plate and the swash plate. A first race rotated together, a second race fixed to the cylinder block, a ring-shaped body portion and the body On either side of the surface is formed to protrude integrally is configured to include the relative rotational contact ring is in contact with the first and second rail device which is formed integrally with engineering plastic.

The relative rotation ring is formed of a PEEK (Polyether Ether Ketone) material, the contact portion is formed to the edge of the body portion.

In the swash plate compressor according to the present invention as described above, the following effects can be obtained.

First, in the present invention, the overall diameter of the bearing assembly can be relatively reduced by using a relative rotation ring made of engineering plastic between the first race and the second race in the construction of the bearing assembly. By reducing the length of the suction passage formed in the can minimize the dead volume. Therefore, the efficiency of the swash plate type compressor can be improved.

Next, the piston bore diameter can be relatively reduced by employing a bearing assembly having a relatively small diameter in the swash plate compressor as in the present invention, thereby reducing the size of the entire swash plate compressor.

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

FIG. 3 is a sectional view showing the configuration of a preferred embodiment of the swash plate compressor according to the present invention, and FIG. 4 is an exploded perspective view showing the configuration of the bearing assembly constituting the embodiment of the present invention.

As shown in these figures, the front housing 110, the rear housing 120, and the front and rear cylinder blocks (130, 130 ') form the skeleton and appearance of the compressor (100). Of course, the skeleton and appearance of the compressor 100 are formed by the front housing 110 and the rear housing 120, the cylinder block (130, 130 ') may be provided in the interior space of the front, rear housing (110, 120). have.

These are arranged and coupled in the order of the front housing 110, the front and rear cylinder blocks (130, 130 ') and the rear housing 120, the rotation shaft 140 is rotated by an external drive source through the center of each of them is installed. do.

Piston 158 linearly reciprocating in conjunction with the rotation of the rotary shaft 140 is installed in the cylinder bore 135 of the front and rear cylinder blocks (130, 130 '), and of the working fluid compressed in the cylinder bore (135) Discharge is performed by the valve unit 160.

The front and rear housings 110 and 120 and the front and rear cylinder blocks 130 and 130 'are fastened to each other by a plurality of fixing bolts 170 penetrating them.

Hereinafter, the components constituting the compressor 100 will be described in more detail. The front housing 110 is formed in a shaft through-hole 112 through which the rotating shaft 140 passes through the center in a substantially disk shape. The shaft hole 112 is formed through the center of the boss portion 113 protruding in the center of one surface of the front housing 110.

The discharge chamber 114 is formed in the front housing 110 on the opposite surface on which the boss portion 113 is formed. The discharge chamber 114 may be formed over a substantially ring-shaped region so as to selectively communicate with each cylinder bore 135 of the front cylinder block 130 and the valve unit 160.

The rear housing 120 is mounted on one surface of the rear cylinder block 130 ′, ie, the opposite surface 132 of the rear cylinder block 130 ′ in close contact with the front cylinder block 130. The discharge chamber 122 is recessed on a surface of the rear housing 120 that faces the rear cylinder block 130 ′.

The front and rear cylinder blocks (130, 130 ') are formed to correspond to the parts indented to the surface coupled to each other to form a swash plate chamber (S). The swash plate 142 installed on the rotating shaft 140 is rotatably positioned in the swash plate chamber (S). A suction port (not shown) is formed at a position corresponding to the swash plate chamber S among the outer surfaces of the front and rear cylinder blocks 130 and 130 ′ to deliver a working fluid delivered from the evaporator to the inside of the swash plate chamber S. .

Axial support holes 131 are formed in the front and rear cylinder blocks 130 and 130 '. The shaft support hole 131 is a portion into which the rotation shaft 140 is inserted, and has an inner diameter corresponding to the diameter of the rotation shaft 140.

The front and rear cylinder blocks 130 and 130 ′ are formed by passing through a plurality of cylindrical cylinder bores 135 in the direction of forming the shaft support hole 131 with the shaft support hole 131 at the center. In this case, the cylinder bore 135 is formed at positions corresponding to the front and rear cylinder blocks (130, 130 '), respectively.

Suction passages 136 are formed in the front and rear cylinder blocks 130 and 130 '. The suction passage 136 is formed to communicate between the cylinder bore 135 and the shaft support hole 131 so that the refrigerant is delivered to the cylinder bore 135 through the interior of the rotating shaft 140, respectively.

Discharge passages 138 are formed in the front and rear cylinder blocks 130 and 130 ′ so as to communicate with discharge chambers 114 and 122 of the front and rear housings 110 and 120, respectively. The discharge passage 138 serves as a passage for discharging the working fluid compressed in the cylinder bore 135 to the outside.

The rotary shaft 140 has one end penetrating the front housing 110 and the other end facing the center of the rear housing 120. An approximately disk-shaped swash plate 142 is installed to be inclined with respect to the extending direction of the rotating shaft 140. The swash plate 142 is provided to be inclined with respect to the rotation shaft 140, and serves to linearly move the piston 158 during the rotation process.

 The center of the swash plate 142 is provided with a hub 143 in a cylindrical shape, the rotating shaft 140 passes through the hub 143. The communication hole 143 ′ is drilled through the hub 143 so as to communicate with the inside of the rotation shaft 140. A plurality of shoes 144 surrounding the edge of the swash plate 142 is installed. The shoe 144 is configured to move along the surface edge of the swash plate 142.

The swash plate 142 is fixed to the rotary shaft 140 to support the force acting in the longitudinal direction to the rotary shaft 140, more precisely the bearing between the hub 143 and the cylinder block (130, 130 ') Assembly 145 is installed. As shown in FIG. 4, the bearing assembly 145 includes a relative rotation ring 146 between the first race 145 ′ and the second race 145 ″.

The first race 145 ′ is a portion that rotates integrally with the hub 143, and the second race 145 ″ is fixed to the front cylinder block 130 and the rear cylinder block 130 ′. to be.

The relative rotation ring 146 is to allow them to rotate relative to the first race 145 ′ and the second race 145 ″ at regular intervals on both surfaces of the ring-shaped body 146 ′. The contact portion 146 "is formed to protrude integrally. The contact portion 146 ″ is in contact with the first and second races 145 ′ and 145 ″. In this embodiment, the contact portion 146 ″ is substantially cylindrical, but it is not necessary. For example, it may be formed to protrude in a hemispherical shape on one surface of the body portion 146 '.

 The relative rotation ring 146 is made of a thermoplastic engineering plastic, for example, PEEK (Polyether Ether Ketone). It can be used continuously at temperatures of about 250 ° C. without permanent damage to physical properties.

In this embodiment, the relative rotation ring 146 is formed with the contact portion 146 "from the inner edge to the outer edge of the body portion 146 '. Here, the contact portion 146" actually supports the load. By forming the contact portion 146 ″ up to both edges of the body portion 146 ', the diameter of the body portion 146' can be relatively reduced. That is, the contact portion 146 " Since it is formed integrally with the body portion 146 ', a portion for supporting the end portion of the contact portion 146 " is not necessary, so that the diameter of the body portion 146' can be made relatively smaller.

Of course, the properties of the material of the material constituting the relative rotation ring 146 is also a factor that makes the relative rotation ring 146 relatively small. That is, even if the contact portion 146 ″ contacts the first and second races 145 ′ and 145 ″ and the area receiving the load is small, the load 146 ″ may sufficiently support the load.

The flow passage 147 through which the working fluid flows is formed inside the rotating shaft 140. The flow path 147 is formed long in the longitudinal direction of the rotation shaft 140 inside the rotation shaft 140. The flow path 147 is formed to be opened to one end of the rotation shaft 140, and the opened portion is positioned to face the rotation shaft chamber 124 of the rear housing 120.

In order to communicate with the flow path 147, the swash plate chamber S, and the suction passage 136, the inlet 148 and the outlet 148 are respectively opened in the rotation shaft 140 to the outer surface of the rotation shaft 140. ') Is formed. The inlet 148 and the outlet 148 ′ may each be formed in plurality. Reference numeral 149 denotes a shaft sealing part that prevents a gap between the inner surface of the shaft through hole 112 of the front housing 110 and the outer surface of the rotating shaft 140.

The piston 158 is a linear reciprocating motion in the cylinder bore (135). The piston 158 has a substantially cylindrical shape corresponding to the inside of the cylinder bore 135, and both ends thereof are positioned at the cylinder bores 135 of the front and rear cylinder blocks 130 and 130 ', respectively. That is, both ends of the one piston 158 serves to compress the working fluid in the cylinder bore 135.

The valve unit 160 is used to control the discharge of the working fluid compressed in the cylinder bore 135 to the outside of the cylinder bore 135. The valve unit 160 includes a valve plate 162 installed in close contact with one surface of the front and rear cylinder blocks 130 and 130 ′, and the valve plate 162 is positioned at a position corresponding to each cylinder bore 135. The discharge hole 164 is formed. Discharge leads 166 are used to selectively open and close the discharge holes 164, respectively. The discharge lead 166 may be elastically deformable and may be elastically deformed according to the pressure of the working fluid in the cylinder bore 135 to open the discharge hole 164.

The valve plate 162 is formed in a substantially disk shape, the communication hole 167 is formed in a position corresponding to the discharge passage 138. The communication hole 167 serves to communicate the respective discharge chambers 114 and 122 with the discharge passage 138.

A muffler 168 is formed on outer surfaces of the front and rear cylinder blocks 130 and 130 ′ so as to communicate with the discharge passage 138. The muffler 168 serves to reduce pulsation and noise of the working fluid. The muffler 168 is provided with a discharge port 169 for discharging the working fluid to the outside (condenser) of the compressor (100). Reference numerals 116 and 118 denote oil chambers and communication paths, respectively.

Hereinafter, the operation of the swash plate compressor according to the present invention having the configuration as described above in detail.

In the compressor 100 of the present invention, as the rotary shaft 140 is rotated by a driving force transmitted from the outside, the swash plate 142 is rotated together with the rotary shaft 140. Rotation of the swash plate 142 causes the piston 158 to perform a linear reciprocating motion inside the cylinder bore 135. A shoe 145 is provided between the swash plate 142 and the piston 158 to reduce the friction between the swash plate 142 and the piston 158.

As the rotary shaft 140 rotates, the flow path 147 inside the rotary shaft 140 sequentially communicates with the respective cylinder bores 135 through the outlet 148 ′ and the suction passage 136. That is, the cylinder bore 135 and the flow passage 147 communicate with each other through the suction passage 136 of the outlet 148 'and the front and rear cylinder blocks 130 and 130'.

The communication between the flow path 147 and the cylinder bore 135 allows the working fluid delivered from the outside of the compressor 100 to be transferred to the cylinder bore 135. For reference, the working fluid is sucked into the cylinder bore 135 when the piston 158 is located at the bottom dead center of the corresponding cylinder bore 135.

When the working fluid is transferred to the cylinder bore 135, and the piston 158 of the corresponding cylinder bore 135 moves in the direction of the valve plate 162, compression of the working fluid occurs. When the working fluid is compressed in the cylinder bore 135, the pressure inside the cylinder bore 135 becomes relatively high, and the tip of the discharge lead 166 is pushed and elastically deformed to open the discharge hole 164. do.

In this case, the working fluid compressed through the discharge hole 164 is transferred to the discharge chambers 114 and 122, and the working fluid transferred to the discharge chambers 114 and 122 is discharged through the communication hole 167. The muffler 168 is transferred to the muffler 168 through the discharge port 169 from the muffler 168 toward the condenser.

As described above, the pressure of the refrigerant acting on the piston 158 during the operation of the compressor 100 is supported by the bearing assembly 145. That is, the bearing assembly 145 installed between the hub 143 and the front and rear cylinder blocks 130 and 130 ′ rotatably supports the rotation shaft 140.

In particular, in the present invention, the relative rotation ring 146 constituting the bearing assembly 145 is made of engineering plastic, and the contact portion 146 "may be formed to the inner and outer edges of the body portion 146 '. According to the data tested under the same load conditions, the diameter of the general bearing assembly and the diameter of the bearing assembly 145 can be compared to the bearing assembly used in the present invention. It can be seen that the diameter of 145 is about 91% of the diameter of a typical bearing assembly, that is, about 10% smaller.

As a result, the bearing assembly 145 may be made relatively smaller in diameter than the conventional one, and when the bearing assembly 145 is used, the piston bore diameter may be reduced in designing the cylinder blocks 130 and 130 '. Can be. When the diameter of the piston bore is reduced, each cylinder bore 135 may be closer to the shaft support hole 131 through which the rotating shaft 140 passes, thereby shortening the length of the suction passage 136. When the length of the suction passage 136 is shortened, it is possible to minimize the dead volume while reducing the volume of the suction passage 136. In other words, the value of t in FIG. 3 can be relatively reduced, and the value of t / t 'is about 90%.

The scope of the present invention is not limited to the embodiments described above, but is defined by the claims, and various changes and modifications can be made by those skilled in the art within the scope of the claims. It is self evident.

1 is a cross-sectional view showing the configuration of a swash plate compressor according to the prior art.

2 is an explanatory diagram illustrating a piston bore diameter in a swash plate compressor according to the prior art.

Figure 3 is a cross-sectional view showing the configuration of a preferred embodiment of a swash plate compressor according to the present invention.

Figure 4 is an exploded perspective view showing the main configuration of the embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

100: compressor 110: front housing

116: oil chamber 118: communication path

120: rear housing 122: discharge chamber

124: rotating shaft chamber 130: front cylinder block

130 ': rear cylinder block 131: shaft support hole

135: cylinder bore 140: rotation axis

142: Saphan 143: Hub

144: shoe 145: bearing assembly

145 ': First race 145 ": Second race

146: relative rotation ring 146 ': body

146 ": contact 147: flow path

160: valve unit 164: discharge hole

S: tribunal

Claims (2)

Front and rear housings (110, 120) to form the outer appearance of at least both ends of the compressor (100), Located between the front and rear housing (110, 120), and formed around the center of the plurality of cylinder bores 135 penetrating, the cylinder block (130, 130 ') having a swash chamber (S) therein, A rotating shaft 140 in which the swash plate 142 located in the swash plate chamber S is rotatably installed; A piston 158 compressing the refrigerant while linearly reciprocating in the cylinder bore 135 according to the rotational motion of the swash plate 142; In the swash plate type compressor comprising a bearing assembly 145 is installed between the swash plate 142 and the cylinder block (130, 130 ') to support the force acting in the longitudinal direction on the rotary shaft 140, The bearing assembly 145 may include a first race 145 ′ that is rotated together with the swash plate 142, a second race 145 ″ fixed to the cylinder blocks 130 and 130 ′, and a ring-shaped body portion ( 146 'and a contact portion 146 "formed integrally protruding from both surfaces of the body portion 146' and contacting the first and second races 145 ', 145" are integrally formed of engineering plastic. Swash plate compressor characterized in that it comprises a relative rotary ring (146). The swash plate compressor of claim 1, wherein the relative rotation ring 146 is formed of a PEEK (Polyether Ether Ketone) material, and the contact portion 146 'is formed to an edge of the body portion 146'. .

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