KR101452499B1 - Compressor - Google Patents

Abstract

The present invention relates to a compressor and uses a rotary shaft 140 having a swash plate 142 to drive a piston 158 that linearly reciprocates in a cylinder bore 135 formed in a cylinder block 130 or 130 '. A shoe 145 is provided between the swash plate 142 and the piston 158 for smooth relative movement between the swash plate 142 and the piston 158. A machining groove 143 is formed on a surface of the swash plate 142 contacting the shoe 145 and a Teflon coated portion T is formed on the machined groove 143. At this time, the machining groove 143 is formed in a curve along the relative movement path of the swash plate 142 and the shoe 145. According to the present invention, friction between the swash plate 142 and the shoe 145 is reduced by the machining groove 143 during the relative movement between the swash plate 142 and the shoe 145, Is improved.

Compressor, swash plate, Teflon coating

Description

Compressor

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor, and more particularly, to a compressor in which a working fluid is compressed by a cylinder bore by a piston driven by a swash plate which is transmitted to a cylinder bore through a flow path formed inside a rotary shaft, will be.

Generally, a compressor used in an automotive air conditioning system sucks a vaporized working fluid from an evaporator and transfers it to a condenser in a high-temperature and high-pressure state which is easy to be liquefied.

In such a compressor, there is actually a reciprocating type in which compression is performed while reciprocating movement of the working fluid is compressed, and a rotary type in which compression is performed while rotating. In the reciprocating type, there is a crank type in which the driving force of the driving source is transmitted using a crankshaft, a swash plate type in which the swash plate is transmitted, and a wobble plate type in which a wobble plate is used. Rotary types include rotary rotary axes with vane rotary vanes, scrolling with rotary scrolls and fixed scrolls.

Figs. 1 and 2 show the construction of a general swash plate type compressor. The schematic configuration of the swash plate type compressor will be described with reference to the drawings. The skeleton and appearance of the compressor 1 are formed by the front housing 10, the rear housing 20, and the front and rear cylinder blocks 30, 30 '. A rotary shaft 40 is installed to penetrate through the center of the front housing 10 and the front and rear cylinder blocks 30 and 30 '. The rotary 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.

A piston 50 linearly reciprocating by the rotation of the rotary shaft 40 is installed in the cylinder bore 35 of the front and rear cylinder blocks 30 and 30 ' A valve unit 60 for controlling the 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 and the front and rear cylinder blocks 30 and 30 'are fastened to each other by fixing bolts 70. The fixing bolts 70 are fixed to the front housing 10, (20), and the front and rear cylinder blocks (30, 30 '). For this purpose, the bolt holes 10 'and 20' are formed in the front housing 10 and the rear housing 20.

Now, the detailed configuration of each component described above will be described. First, the front housing 10 is formed in a substantially circular plate shape with a shaft hole 12 through which the rotating shaft 40 passes. The shaft hole 12 passes through the center of the boss 13 protruding from the center of the front surface of the front housing 10. A discharge chamber (14) is formed on the opposite surface of the front housing (10) where the boss (13) is formed. The discharge chamber 14 is formed over a substantially ring-shaped area, and is selectively communicated with the respective cylinder bores 35 of the front cylinder block 30 through the valve unit 60.

The rear housing 20 is mounted on one side of the rear cylinder block 30 '. A discharge chamber (22) is formed on a surface of the rear housing (20) facing the rear cylinder block (30 '). The discharge chamber 22 is formed to selectively 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 formed with recessed portions on the surfaces to be coupled with each other to constitute the swash plate chamber 31. A swash plate (42) provided on the rotary shaft (40) is rotatably positioned in the swash plate chamber (31). An axial hole 32 is formed through the front and rear cylinder blocks 30 and 30 '. The rotary shaft (40) passes through the shaft hole (32).

A plurality of cylindrical cylinder bores 35 are formed in the front and rear cylinder blocks 30 and 30 'with the axial hole 32 as a center and in the forming direction of the axial hole 32. 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 hole (32) communicate with each other through a suction passage (36). The suction passage 36 allows the working fluid delivered through the inside of the rotating shaft 40 to be transmitted to the cylinder bore 35, respectively.

The front and rear cylinder blocks 30 and 30 'are provided with a discharge passage 38 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.

One end of the rotary shaft 40 passes through the front housing 10 and an intermediate portion passes through the front and rear cylinder blocks 30 and 30 '. A substantially disk-shaped swash plate 42 is provided on the rotating shaft 40 so as to be inclined with respect to the extending direction of the rotating shaft 40. In the center of the swash plate 42, a hub 44 is provided in a cylindrical shape, and the rotary shaft 40 passes through the hub 44. The communication hole 44 'is penetrated through the hub 44 so as to communicate with the inside of the rotary shaft 40. Further, a plurality of shoeholes 45 surrounding the edges of the swash plate 42 are installed. The shoe 45 is configured to move along the edge of the swash plate 42. A bearing 46 is provided between both ends of the swash plate 42 and the cylinder block 30, 30 '.

At this time, a Teflon coated portion T is formed on the surface of the swash plate 42. The Teflon coated portion T is formed on both side surfaces of the swash plate 42 contacting with the shoe 45 so that the swash plate 42 is worn by the friction between the shoe 45 and the swash plate 42 . The Teflon coated portion T is formed by applying a Teflon material to the surface of the swash plate 42.

As shown in FIG. 2, in order to form the Teflon coated portion T, the surface of the swash plate 42 is first roughened, and a Teflon material is coated on the surface. This is for allowing the Teflon coated portion T to be adhered to the swash plate 42 well.

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

The piston (50) linearly reciprocates inside the cylinder bore (35). The piston 50 is substantially cylindrical in shape corresponding to the inside of the cylinder bore 35 and is positioned at the cylinder bore 35 of the front and rear cylinder blocks 30 and 30 '. That is, both ends of one piston 50 serve to compress the working fluid in the cylinder bore 35. The piston (50) is coupled to the shoe (45) at an intermediate portion thereof and linearly reciprocates according to 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 disposed in close contact with one surface of the front and rear cylinder blocks 30 and 30 ' A discharge hole 64 is formed. Discharge leads 66 are used for selectively opening and closing the discharge holes 64, respectively. The discharge reed 66 is elastically deformable 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 has a substantially disc shape and a communication hole 67 is formed at a position corresponding to the discharge passage 38. The communication holes 67 serve to communicate the respective discharge chambers 14, 22 with the discharge passage 38.

A muffler 68 is formed on the outer surfaces 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 provided with a discharge port 69 for discharging the working fluid to the outside (condenser) of the compressor 1. 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. The swash plate 42 is rotated together with the rotation of the rotation shaft 40 as the rotation shaft 40 rotates by the external driving force. The rotation of the swash plate 42 causes the piston 50 to linearly reciprocate within the cylinder bore 35. [

At this time, as the rotary shaft 40 rotates, the flow passage 47 in the rotary shaft 40 communicates with the cylinder bore 35 through the outlet 48 'and the suction passage 36. The communication between the oil passage 47 and the cylinder bore 35 allows the working fluid sucked into the swash plate chamber 31 to be transmitted to the cylinder bore 35. For reference, the operation 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 toward the valve plate 62, the working fluid is compressed. 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 reed 66 is pushed and elastically deformed, Is opened.

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 discharged through the communication hole 67 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.

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

The surface of the swash plate 42 is roughened, more precisely, in the machined grooves 42 ', and the machined grooves 42' are formed in a straight line, as shown in FIG. 2, The dogs are formed closely. However, the direction in which the surface of the swash plate 42 and the shoe 45 move relative to each other does not coincide with the forming direction of the machining groove 42 '. That is, the shoe 45 is moved in a circle along the surface edge of the swash plate 42 about the rotation axis 40 (arrow 1 in Fig. 2), whereas the machined groove 42 ' And is formed on the surface of the swash plate 42 along a straight path (arrow 2 in Fig. 2).

Accordingly, the shoe 45 is moved while slightly crossing the forming groove of the machining groove 42 'in the process of relative movement with the swash plate 42, As a result, the efficiency of the compressor 1 is deteriorated.

Of course, in order to solve this problem, the machined groove 42 'may not be formed, but the Teflon coated portion T may not be firmly adhered to the surface of the swash plate 42.

The machined grooves 42 'are linearly formed on the surface of the swash plate 42 so that both ends thereof are opened to both sides of the swash plate 42. Accordingly, the lubricating oil can easily escape from the inside of the machining groove 42 ', and the lubricating oil can not be sufficiently supplied between the shoe 45 and the swash plate 42.

SUMMARY OF THE INVENTION It is an object of the present invention to solve the problems of the prior art as described above, and it is an object of the present invention to make the forming direction of the groove for Teflon coating of the swash plate coincide with the relative moving direction of the swash plate and the shoe.

It is another object of the present invention to make the machining grooves for the Teflon coating of the swash plate form a closed curve so that the oil does not easily escape from the inside of the machining grooves.

According to an aspect of the present invention, there is provided a compressor comprising: a front and a rear housing forming at least both ends of an outer tube of a compressor; and a plurality of cylinder bores located around the center of the front and rear housings, A cylinder block having a swash plate chamber therein and a swash plate disposed in the swash plate chamber so as to be rotatable and having a passage for transmitting a working fluid sucked into the compressor into the cylinder bore, A plurality of pistons linearly reciprocating in the cylinder bores in accordance with a rotational motion of the swash plate, and a shoe disposed between the swash plate and the piston and moving relative to the swash plate, A machining groove is formed along the relative movement path of the swash plate and the shoe, and a Teflon coating portion is formed in the machining groove.

The machining grooves are formed on the surface of the swash plate at a plurality of different radii around the rotation axis to form closed curves.

The cross section of the machining groove is formed in a triangular shape.

The machining groove is formed by laser machining.

According to the compressor of the present invention, the following effects can be expected.

In the present invention, the forming grooves for Teflon coating on the surface of the swash plate are formed in a curved shape along the relative moving direction of the swash plate and the shoe. As a result, the friction between the swash plate and the shoe is reduced by the grooves in the relative movement of the swash plate and the shoe, thereby improving the efficiency of the compressor.

In the present invention, since the working groove of the swash plate forms a closed curve, the lubricating oil can not easily escape from the inside of the working groove. Therefore, since the lubricating oil is sufficiently supplied between the swash plate and the shoe, the wear of the parts due to the friction between the swash plate and the shoe is also reduced.

Further, in the present invention, since the machined grooves of the swash plate are formed by laser machining, only the necessary parts can be easily processed, the byproducts are hardly generated in the machining process, and the environmental pollution is more likely to occur than chemical processing such as anodizing There is also a shrinking effect.

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

FIG. 3 is a cross-sectional view of a compressor according to a preferred embodiment of the present invention. FIG. 4 is a perspective view of a rotary shaft and a swash plate, Some configurations of the swash plate and shoe constituting the embodiment are shown in cross-section.

As shown in these drawings, the skeleton and the exterior of the compressor 100 are formed by the front housing 110, the rear housing 120, and the front and rear cylinder blocks 130 and 130 '. Of course, the skeleton and outer appearance of the compressor 100 are formed by the front housing 110 and the rear housing 120, and the cylinder blocks 130 and 130 'may be provided in the inner spaces of the front and rear housings 110 and 120.

These are arranged in the order of the front housing 110, the front and rear cylinder blocks 130 and 130 ', and the rear housing 120, and a rotation shaft 140 rotated by an external driving source through the centers of the front housing 110 and the rear housing 120 is installed.

A piston 158 reciprocating linearly 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 and 130 'and the discharge of the working fluid compressed by the cylinder bore 135 And the valve unit 160.

The front and rear housings 110 and 120 and the front and rear cylinder blocks 130 and 130 'are fastened together by a plurality of fixing bolts 170 passing through the front and rear housing blocks 110 and 120. To this end, bolt holes 110' and 120 ' Is formed.

Hereinafter, the components constituting the compressor 100 will be described in more detail. The front housing 110 has a substantially circular plate shape and an axial hole 112 through which the rotation shaft 140 passes is formed through the center. The shaft hole 112 is formed through a center of the boss 113 protruding from the center of one side of the front housing 110.

A discharge chamber 114 is formed on the opposite surface of the front housing 110 where the boss 113 is formed. The discharge chamber 114 may extend over a substantially ring-shaped area so as to selectively communicate with the respective cylinder bores 135 of the front cylinder block 130 through the valve unit 160.

The rear housing 120 is mounted on one side of the rear cylinder block 130 ', that is, on the opposite side 132 of the rear cylinder block 130' which is in contact with the front cylinder block 130. A discharge chamber (122) is formed on a surface of the rear housing (120) facing the rear cylinder block (130 ').

A rotary shaft chamber 124 corresponding to one end of the rotary shaft 140 is formed at the center of the rear housing 120. The rotary shaft chamber 124 is formed in the center of the discharge chamber 122 so as to be partitioned from the discharge chamber 122.

The front and rear cylinder blocks 130 and 130 'are formed so as to correspond to the portions of the front and rear cylinder blocks 130 and 130' that are coupled to each other to form a swash plate chamber S. A swash plate (142) provided on the rotating shaft (140) is rotatably positioned in the swash plate chamber (S). A suction port (not shown) for transmitting a working fluid transferred from the evaporator to the inside of the swash plate chamber S is formed at an outer surface of the front and rear cylinder blocks 130 and 130 'corresponding to the swash plate chamber S.

An axial hole 131 is 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.

A plurality of cylindrical cylinder bores 135 are formed in the front and rear cylinder blocks 130 and 130 'with respect to the direction of the mounting holes 131 and 131' with the axial hole 131 as a center. At this time, the cylinder bores 135 are formed at positions corresponding to the front and rear cylinder blocks 130 and 130 ', respectively.

A suction passage 136 is formed in the front and rear cylinder blocks 130 and 130 '. The suction passage 136 communicates between the cylinder bore 135 and the shaft support hole 131 to allow the working fluid to be transmitted to the cylinder bore 135 through the rotation shaft 140.

A discharge passage 138 is formed in the front and rear cylinder blocks 130 and 130 'so as to communicate with the 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.

One end of the rotation shaft 140 passes through the front housing 110 and the other end of the rotation shaft 140 faces the rotation shaft chamber 124 of the rear housing 120. A swash plate 142 having a substantially disk shape is provided on the rotating shaft 140 so as to be inclined with respect to the extending direction of the rotating shaft 140. The swash plate 142 is inclined with respect to the rotation shaft 140 to linearly move the piston 158 during the rotation process.

At this time, a Teflon coated portion T is formed on the surface of the swash plate 142. The Teflon coated portion T is formed by applying a Teflon material to the surface of the swash plate 142. The friction between the swash plate 142 and a shoe 145 to be described later causes the swash plate 142 to be worn It is a kind of reinforcing membrane to prevent the problem.

As shown in FIG. 4, a machining groove 143 is formed on the surface of the swash plate 142. The machining groove 143 is machined before the Teflon coated portion T is machined so that the Teflon coated portion T can be more reliably adhered to the surface of the swash plate 142, Is formed on the surface of the substrate 142 by laser machining or the like. Such a laser processing is a processing method for instantly burning the surface of a material by using high heat, which is eco-friendly as compared with a chemical method such as anodizing and can process only a necessary part, and there is an advantage that by-products are hardly generated.

The machining groove 143 is formed on the surface of the swash plate 142 so as to be curved along the relative movement path of the swash plate 142 and the shoe 145 while drawing a circle. That is, the forming groove 143 forms a closed curve.

At this time, a plurality of the machining grooves 143 are formed with a different radius around the rotation axis 140. This is because the shoe 145 is seated on the plurality of the processing grooves 143 so that the friction surface between the swash plate 142 and the shoe 145 is reduced and the shoe 145 is stably mounted on the surface of the rotation shaft 142 So that it can be done.

5, it is preferable that the cross section of the machining groove 143 is formed in a triangular shape. This is because the contact area between the surface of the swash plate 142 and the bottom surface of the shoe 145 is relatively reduced by the machining groove 143 formed so as to be wider toward the surface of the swash plate 142 The friction is also intended to be small. Of course, the shape of the cross section of the machining groove 143 may be formed in a semicircular or other polygonal shape.

 In the center of the swash plate 142, a hub 144 is provided in a cylindrical shape, and the rotation shaft 140 passes through the hub 144. The communication hole 144 'is penetrated through the hub 144 so as to communicate with the inside of the rotation shaft 140.

A plurality of shoes 145 are disposed to surround the edge of the swash plate 142. The shoe 145 is configured to move along the surface edge of the swash plate 142. More precisely, the shoe 145 is moved relative to the swash plate 142 while forming a circle along the longitudinal direction of the machining groove 143 formed in the swash plate 142. Reference numeral 146 denotes a bearing.

A flow path 147 through which a working fluid flows is formed in the rotating shaft 140. The flow path 147 is formed in the rotation shaft 140 in the longitudinal direction of the rotation shaft 140. The flow path 147 is formed to be open at one end of the rotation shaft 140 and the opened part is located at a position facing the rotation axis chamber 124 of the rear housing 120.

An inlet 148 and an outlet 148 are formed in the rotary shaft 140 so as to be opened to the outer surface of the rotary shaft 140 for the communication between the oil passage 147 and the swash plate chamber S and the suction passage 136, '). A plurality of the inlet 148 and the outlet 148 'may be formed. Reference numeral 149 denotes an axial sealing portion for blocking a gap between the inner surface of the axial hole 112 of the front housing 110 and the outer surface of the rotary shaft 140.

The piston 158 linearly reciprocates inside the cylinder bore 135. The piston 158 has a substantially cylindrical shape corresponding to the inside of the cylinder bore 135 and has both ends positioned at the cylinder bore 135 of the front and rear cylinder blocks 130 and 130 '. That is, both ends of one piston 158 serve 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 disposed in close contact with one surface of the front and rear cylinder blocks 130 and 130 ' A discharge hole 164 is formed. Discharge leads 166 are used to selectively open and close the discharge holes 164, respectively. The discharge reed 166 is elastically deformable and 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 disc shape, and a communication hole 167 is formed at a position corresponding to the discharge passage 138. The communication holes 167 serve to communicate the discharge chambers 114 and 122 with the discharge passage 138.

A muffler 168 is formed on the 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 formed with a discharge port 169 for discharging 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 compressor according to the present invention will be described in detail.

In the compressor 100 of the present invention, the swash plate 142 rotates together with the rotation shaft 140 as the rotation shaft 140 rotates by an external driving force. Rotation of the swash plate 142 causes the piston 158 to reciprocate linearly within the cylinder bore 135. A shoe 145 is provided between the swash plate 142 and the piston 158 to reduce friction between the swash plate 142 and the piston 158.

The shoe 145 and the swash plate 142 are moved relative to each other with the bottom of the shoe 145 in contact with the Teflon coating portion T formed on the surface of the swash plate 142, The surface of the swash plate 142 can be prevented from being worn to some extent.

At this time, a machining groove 143 for reliably adhering the Teflon coated portion T is formed in a circular shape on the surface of the swash plate 142 along the relative movement path of the shoe 145 and the swash plate 142, Friction between the shoe 145 and the swash plate 142 is reduced. That is, since the machining groove 143 is formed so as to correspond to the moving direction of the shoe 145 without violating the movement path of the shoe 145, the shoe 145 is moved along the machining groove 143 Can be moved relative to the swash plate (142).

Particularly, the Teflon coating portion T is formed along the texture of the machining groove 143 even if the surface of the swash plate 148 is coated with Teflon, because the forming groove 143 is formed so as to form a closed curve. Are formed while forming a closed curve. The lubricant can not easily escape and can be maintained in a state of being sufficiently impregnated with the recessed portion formed by the Teflon coated portion T along the surface of the machined groove 143, The friction between the two ends can be more effectively reduced.

The operation of the compressor 100 will be described below. As the rotation shaft 140 rotates, a flow passage 147 in the rotation shaft 140 is connected to the outlet 148 'and the suction passage 136 through the outlet 148' And the cylinder bores 135 of the cylinder head 130 are sequentially communicated with each other. That is, the cylinder bore 135 and the oil passage 147 communicate with each other through the outlet 148 'and the suction passage 136 of the front and rear cylinder blocks 130 and 130'.

The communication between the oil passage 147 and the cylinder bore 135 allows the working fluid delivered from the outside of the compressor 100 to be transmitted to the cylinder bore 135. For reference, the operation fluid is sucked into the cylinder bore 135 when the piston 158 is positioned 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 toward the valve plate 162, the working fluid is compressed. 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 reed 166 is pushed and elastically deformed so that the discharge hole 164 is opened do.

The working fluid compressed through the discharge hole 164 is transferred to the discharge chambers 114 and 122 and the working fluid delivered to the discharge chambers 114 and 122 is discharged through the discharge hole 138 To the muffler 168, and is transmitted from the muffler 168 to the condenser through the discharge port 169.

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

In the above-described embodiment, the fixed displacement type swash plate type compressor in which the inclination angle of the swash plate 142 is fixed to the rotation axis 140 is described as an example. However, the present invention is also applicable to a variable displacement swash plate type compressor in which the inclination angle of the swash plate can be adjusted Can be applied.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a configuration of a compressor according to a prior art; FIG.

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a compressor.

3 is a sectional view showing a configuration of a preferred embodiment of the compressor according to the present invention.

4 is a perspective view showing the construction of a rotary shaft and a swash plate coupled thereto, which constitute an embodiment of the present invention.

5 is a sectional view showing a part of a swash plate and a shoe constituting an embodiment of the present invention.

Description of the Related Art [0002]

100: compressor 110: front housing

116: Oil chamber 118:

120: rear housing 122: discharge chamber

124: rotary shaft chamber 130: front cylinder block

130 ': rear cylinder block 131:

135: cylinder bore 140:

142: swash plate 143: machining groove

145: Shu 147: Euro

160: Valve unit 164: Discharge hole

S: Swash plate T: Teflon coated part

Claims (4)

Front and rear housings 110 and 120 forming at least both ends of the compressor 100, A cylinder block 130 positioned between the front and rear housings 110 and 120 and formed with a plurality of cylinder bores 135 through the center thereof and having a swash plate chamber S therein, A rotary shaft 140 installed to be rotatable in a swash plate 142 positioned in the swash plate chamber S, A plurality of pistons 158 linearly reciprocating in the cylinder bores 135 in accordance with the rotation of the swash plate 142, And a shoe (145) provided between the swash plate (142) and the piston (158) and moving relative to the swash plate (142) A machining groove 143 is formed on the surface of the swash plate 142 along the relative movement path of the swash plate 142 and the shoe 145 and a Teflon coating portion T is formed on the machining groove 143 Characterized by a compressor. 2. The compressor according to claim 1, wherein the machining grooves (143) are formed on the surface of the swash plate (142) with a radius being different from each other around the rotation axis (140), thereby forming a closed curve. 3. The compressor according to claim 2, wherein the cross-section of the machining groove (143) is formed in a triangular shape. The compressor according to any one of claims 1 to 3, wherein the machining groove (143) is formed by laser machining.

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