KR101463266B1 - Compressor - Google Patents

Abstract

The present invention relates to a compressor. The shaft hole 113 is formed through the center of the front cylinder block 112 and the rear cylinder block 112 'constituting the compressor 100 in the present invention. Cylindrical cylinder bores 112a and 112a 'are formed in the front cylinder block 112 and the rear cylinder block 112' in the direction of forming the shaft hole 113 with the shaft hole 113 as the center A plurality of them are formed. The piston 130 linearly reciprocates inside the cylinder bores 112a and 112a 'to compress the refrigerant. A shaft hole (O) is formed through a center of the front head (111) installed at one end of the front cylinder block (112). A rotary shaft 124 for transmitting power for linear reciprocating motion of the piston 130 is rotatably installed through the shaft hole 113 and the axial hole O. [ The inner circumferential surfaces of the cylinder bores 112a and 112a 'are anodized. According to the present invention having such a configuration, when the inner peripheral surface of the cylinder bores 112a and 112a 'is anodized, the hardness is relatively improved and the abrasion resistance of the cylinder bores 112a and 112a' And 112a 'are prevented from being worn on the inner circumferential surfaces of the cylinder bores 112a and 112a' due to the friction generated in the process of linearly reciprocating the piston 130 in the cylinder bores 112a and 112a '.

Compressor, cylinder block, cylinder bore, anodizing

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 refrigerant is compressed by a piston in a cylinder bore as the rotary shaft rotates to receive a driving force of the engine.

The compressor used in the automobile air conditioning system sucks the evaporated refrigerant from the evaporator and transfers it to the condenser at a high temperature and high pressure state which is easy to be liquefied.

In such a compressor, there is a reciprocating type in which compression is performed while reciprocating motion is actually performed for compressing the refrigerant, and a rotary type in which compression is performed while rotating. In the reciprocating type, there is a crank type in which a driving force of a driving source is transmitted to a plurality of pistons using a crank, a swash plate type in which the swash plate is transmitted to a rotary shaft, 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.

1 is a sectional view of a general swash plate type compressor.

As shown in the figure, the skeleton and the exterior of the compressor 10 are formed by the front head 11, the front cylinder block 12 and the rear cylinder block 12 ', and the rear head 28. These are arranged and joined in the order of the front head 11, the front cylinder block 12, the rear cylinder block 12 'and the rear head 28 in this order.

The front head 11 has a substantially cylindrical shape, and a discharge chamber 11a is formed therein. The discharge chambers 11a are opened toward the front cylinder block 12, respectively. The discharge chamber 11a is formed over a substantially ring-shaped area. The discharge chamber 11a is formed to be selectively connected to each cylinder bore 12a of the front cylinder block 12 through a valve assembly 14 described below.

An axial hole (O) is formed through the center of the front head (11). The shaft hole (O) is provided with a rotation shaft (24) to be described below.

The front cylinder block 12 and the rear cylinder block 12 'are coupled to the front head 11 and the rear head 28, respectively. A plurality of cylindrical cylinder bores 12a are formed in the front cylinder block 12 and the rear cylinder block 12 'in the direction of forming the shaft hole 13 with the shaft hole 13 as the center . Of course, the cylinder bore 12a is formed at a position corresponding to the front cylinder block 12 and the rear cylinder block 12 ', respectively. The cylinder bore 12a and the shaft hole 13 are connected to each other through a suction passage 13 '. The suction passage 13 'allows the refrigerant transferred through the inside of the rotary shaft 24 to be transmitted to the cylinder bore 12a.

Discharge passages (not shown) are formed in the front cylinder block 12 and the rear cylinder block 12 'so as to communicate with the discharge chambers 11a and 28a of the front head 11 and the rear head 28, respectively. The discharge passage serves as a passage for discharging the refrigerant compressed in the cylinder bore 12a to the outside.

A flow of coolant is controlled between the discharge chamber 11a and the cylinder bore 12a between the front head 11 and the front cylinder block 12 and between the rear head 28 and the rear cylinder block 12 ' A valve assembly 14 is provided. That is, the valve assembly 14 controls the refrigerant flow from the cylinder bore 12a to the discharge chamber 11a.

The valve assembly 14 is provided with a valve plate 15. The valve plate 15 is formed in a substantially disc shape and has a discharge hole 15 'at a position corresponding to each cylinder bore 12a.

A discharge lead 17 is provided on one surface of the valve plate 15 facing the front head 11 and on one surface of the valve plate 15 facing the rear head 28. The discharge lead 17 is elastically deformable and is elastically deformed according to the internal pressure of the cylinder bore 12a to open and close the discharge hole 15 '.

A communication hole (not shown) is formed in the valve plate 15 at a position corresponding to the discharge passage. And the communication hole connects the discharge passage.

The front cylinder block 12 and the rear cylinder block 12 'are formed with recessed portions on the surfaces to be coupled with each other to constitute the swash plate chamber 23. A swash plate (26) provided on the rotary shaft (24) is rotatably positioned in the swash plate chamber (23).

A rotating shaft 24 is provided to pass through the center of the front head 11, the front cylinder block 12 and the rear cylinder block 12 '. A flow path 24 'through which the refrigerant flows is formed in the rotating shaft 24. The flow path 24 'is formed long in the longitudinal direction of the rotary shaft 24 inside the rotary shaft 24. An inlet 24a and an outlet 24b are formed on the outer surface of the rotary shaft 24. The inlet 24a connects the swash plate chamber 23 and the oil passage 24 'and the outlet 24b connects the suction passage 13' of the front cylinder block 12 and the rear cylinder block 12 ' In the present embodiment. The position of the outlet 24b should be formed in accordance with the compression order of the refrigerant flowing in each of the cylinder bores 12a.

A shaft shaft 25 is inserted into one side of the rotating shaft 24 and is in close contact with the inner surface of the shaft hole O of the front head 11. [ The shaft shaft 25 serves to prevent the refrigerant from leaking between the rotary shaft 24 and the axial hole O. [ The shaft end work (25) is formed of a rubber material capable of elastic deformation.

A substantially disk-shaped swash plate 26 is provided on the rotating shaft 24 so as to be inclined with respect to the extending direction of the rotating shaft 24. A plurality of shoe (27) is provided to surround the edge of the swash plate (26). The shoe (27) is configured to move along an edge of the swash plate (26).

On the other hand, a piston 30 is installed in the cylinder bore 12a so as to reciprocate linearly. The piston 30 has a substantially cylindrical shape corresponding to the inside of the cylinder bore 12a and both ends thereof are located at the cylinder bore 12a of the front cylinder block 12 and the rear cylinder block 12 '. That is, both ends of each of the pistons 30 serve to compress the refrigerant in the cylinder bore 12a. The intermediate portion of the piston 30 is engaged with the shoe 27 and reciprocates linearly in accordance with the rotation of the swash plate 26.

The rear head 28 is mounted on one side of the rear cylinder block 12 '. The rear head 28 is provided with a discharge chamber 28a. The discharge chamber 28a is formed over an approximately ring-shaped area. Each of the discharge chambers 28a is opened toward the rear cylinder block 12 '. The discharge chamber 28a is selectively connected to the cylinder bores 12a formed in the rear cylinder block 12 'through a valve plate 15.

A pulley (40) is rotatably installed on one side of the front head (11). The pulley 40 is formed in a substantially cylindrical shape. The pulley 40 receives the driving force of the engine through a belt (not shown) and is rotated.

A field coil 41 is embedded in the pulley 40. The field coil 41 generates a magnetic attraction flux when power is applied to cause the disk 46 to be described below to be brought into close contact with the friction surface 40 'of the pulley 40.

A hub 43 is provided at one end of the rotary shaft 24 and a damper 44 is provided at the hub 43. The damper 44 absorbs an impact generated when power is transmitted between the rotary shaft 24 and the pulley 40. The damper 44 is provided with a disk 46 movably installed at a position facing the friction surface 40 'of the pulley 40.

The operation of the compressor having such a structure will be described. When the driving force of the engine is transmitted to the pulley 40 through the belt, the pulley 40 is rotated. However, if power is not applied to the field coil 41, the disk 46 is not brought into close contact with the friction surface 40 'of the pulley 40, so that the rotation shaft 24 does not rotate.

If the compressor needs to be driven due to the necessity of operating the air conditioning system in such a state, the control system of the user or the vehicle provides a signal for the operation of the air conditioning system. When the operation of the air conditioning system is started and the refrigerant needs to be compressed, the field coil 41 generates power to the field coil 41 to generate the suction flux.

When power is applied to the field coil 41, the disk 46 is brought into close contact with the friction surface 40 'of the pulley 40 by the attracting magnetic flux of the field coil 41. Accordingly, the rotational force of the pulley 40 is transmitted to the rotary shaft 24 through the disk 46, the damper 44, and the hub 43.

When the rotational force of the pulley 40 is transmitted to the rotary shaft 24 as described above, the rotary shaft 24 rotates and linearly reciprocates the piston to perform compression of the refrigerant.

At this time, as the rotary shaft 24 rotates, the flow passage 24 'inside the rotary shaft 24 is connected to the cylinder bore 12a through the outlet 24b and the suction passage 13'. The connection between the flow path 24 'and the cylinder bore 12a allows the refrigerant sucked into the swash plate chamber 23 to be transferred to the cylinder bore 12a. For reference, the refrigerant is sucked into the cylinder bore 12a when the piston 30 is located at the bottom dead center of the corresponding cylinder bore 12a. When the refrigerant is delivered to the cylinder bore 12a, the piston 30 of the corresponding cylinder bore 12a moves in the direction of the valve plate 15 and the refrigerant is compressed.

Thus, when the refrigerant is compressed in the cylinder bore 12a, the pressure inside the cylinder bore 12a becomes relatively high, and the refrigerant is discharged to the discharge chambers 11a and 28a. The refrigerant discharged to the discharge chambers 11a and 28a is transferred to a condenser (not shown) through an external discharge port.

The refrigerant transferred to the condenser through the discharge port passes through a condenser (not shown), an expansion valve (not shown), and an evaporator (not shown), and then is returned to the compressor. In the compressor, the refrigerant is compressed by repeating the process described above.

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

The front cylinder block 12 and the rear cylinder block 12 'and the piston 30 are both made of aluminum. At this time, the friction between the cylinder bore 12a and the cylinder bore 12a due to the reciprocating motion of the piston 30 in the cylinder bore 12a of the front cylinder block 12 and the rear cylinder block 12 ' Wear occurs on the inner circumferential surface.

In this state, when the piston 30 continuously reciprocates, the refrigerant compressed in the cylinder bore 12a flows between the outer circumferential surface of the piston 30 and the inner circumferential surface of the cylinder bore 12a So that the piston 30 may be shaken and hit the inner circumferential surface of the cylinder bore 12a to damage the cylinder bore 12a.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above-mentioned problems occurring in the prior art, and it is an object of the present invention to enhance the durability of the cylinder block constituting the compressor.

In order to achieve the above object, according to an aspect of the present invention, there is provided a cylinder bore for a compressor, the cylinder bore being formed to penetrate through a center and passing through a shaft support hole, A cylinder block formed to penetrate the perforations; A front head installed at one end of the cylinder block and having a shaft hole formed through the center thereof and having a discharge chamber in which refrigerant is discharged; A rear head installed at the other end of the cylinder block and having a discharge chamber in which refrigerant is discharged; And a rotating shaft which transmits power for linear reciprocating motion of the piston and which is rotatably installed through a shaft support hole of the cylinder block and a shaft hole of the front head, Is anodized.

The inner circumferential surface of the axial hole of the cylinder block is anodized.

In the present invention, the inner circumferential surface of the cylinder bore formed in the front cylinder block and the rear cylinder block performs an anodizing treatment. That is, when the inner peripheral surface of the cylinder bore is anodized, the hardness is relatively improved. Therefore, the abrasion resistance of the cylinder bore is improved, and the abrasion of the inner circumferential surface of the cylinder bore due to the friction generated in the course of the linear reciprocating motion of the piston in the cylinder bore is prevented, thereby increasing the durability.

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

2 is a cross-sectional view of a preferred embodiment of the compressor according to the present invention.

The front head 111, the front cylinder block 112 and the rear cylinder block 112 ', and the rear head 128 form the skeleton and the appearance of the compressor 100 according to these figures. These are arranged in the order of the front head 111, the front cylinder block 112, the rear cylinder block 112 'and the rear head 128 in this order.

The front head 111 has a substantially cylindrical shape, and a discharge chamber 111a is formed therein. The discharge chamber (111a) is opened toward the front cylinder block (112). The discharge chamber 111a is formed over a substantially ring-shaped area. The discharge chamber 111a is formed to be selectively connected to each of the cylinder bores 112a and 112a 'of the front cylinder block 112 through a valve assembly 114 described below.

A shaft hole (O) is formed through the center of the front head (111). The shaft hole (O) is provided with a rotation shaft (124) penetrating through the shaft hole (O).

An axial hole 113 is formed through the center of the front cylinder block 112 and the rear cylinder block 112 '. A shaft (124) penetrates through the shaft hole (113). The inner diameter of the shaft hole 113 is designed so that the outer surface of the rotary shaft 124 can be closely contacted.

The front cylinder block 112 and the rear cylinder block 112 'are coupled to the front head 111 and the rear head 128, respectively. Cylindrical cylinder bores 112a and 112a 'are formed in the front cylinder block 112 and the rear cylinder block 112' in the direction of forming the shaft hole 113 with the shaft hole 113 as the center A plurality of them are formed. Of course, the cylinder bores 112a and 112a 'are formed at positions corresponding to the front cylinder block 112a and the rear cylinder block 112', respectively. The cylinder bores 112a and 112a 'and the shaft hole 113 are connected to each other through a suction passage 113'. The suction passage 113 'allows the refrigerant transferred through the inside of the rotating shaft 124 to be transmitted to the cylinder bores 112a and 112a', respectively.

The inner circumferential surfaces of the cylinder bores 112a and 112a 'are formed in a shape corresponding to the outer circumferential surface of the piston 130, which will be described below. A piston 130 is installed inside the cylinder bores 112a and 112a '. The inner circumferential surfaces of the cylinder bores 112a and 112a 'are anodized. For reference, anodizing is also referred to as anodizing, and is a treatment method in which an oxide film is formed on the surface of a metal by oxygen generated in the anode through current flow through the product as an anode in the electrolyte solution.

When the inner circumferential surfaces of the cylinder bores 112a and 112a 'are subjected to an anodizing process, an oxide film A having a predetermined thickness (an aluminum oxide film) is formed on the inner circumferential surfaces of the cylinder bores 112a and 112a' : Al2O3) is formed. In this case, the hardness of the inner circumferential surfaces of the cylinder bores 112a and 112a 'is about three to four times as great as when the anodizing treatment is performed. The values of the Vickers hardness (Hv) can be found from the experimental data shown in Table 1. [

[Table 1]

No anodizing Anodizing Vickers hardness (Hv) 60 to 80 250

From the experimental data in Table 1, it can be seen that the value of Vickers hardness (Hv) when the inner circumferential surface of the cylinder bores 112a and 112a 'is anodized is relatively higher than when the anodizing treatment is not performed. In other words, when the inner circumferential surface of the cylinder bores 112a and 112a 'is subjected to an anodizing treatment, the hardness is improved, so that the abrasion resistance of the cylinder bores 112a and 112a' is improved, The inner circumferential surface of the cylinder bores 112a and 112a 'is prevented from being abraded due to the friction generated in the course of linear reciprocating motion of the cylinder bores 130a and 112b'.

Discharge passages (not shown) are formed in the front cylinder block 112 and the rear cylinder block 112 'so as to communicate with the discharge chambers 111a and 128a of the front head 111 and the rear head 128, respectively. The discharge passage serves as a passage for discharging the refrigerant compressed in the cylinder bores 112a and 112a 'to the outside.

Between the front head 111 and the front cylinder block 112 and between the rear head 128 and the rear cylinder block 112 ' A valve assembly 114 for controlling the flow is provided. That is, the valve assembly 114 controls the refrigerant flow from the cylinder bores 112a and 112a 'to the discharge chamber 111a.

The valve assembly 114 is provided with a valve plate 115. The valve plate 115 has a substantially disc shape and a discharge hole 115 'is formed at a position corresponding to each of the cylinder bores 112a and 112a'.

A discharge lead 117 is provided on one surface of the valve plate 115 facing the front head 111 and on one surface of the valve plate 115 facing the rear head 128. The discharge reed 117 is elastically deformable and is elastically deformed according to internal pressures of the cylinder bores 112a and 112a 'to open and close the discharge hole 115'.

A communication hole (not shown) is formed in the valve plate 115 at a position corresponding to the discharge passage. And the communication hole connects the discharge passage.

The front cylinder block 112 and the rear cylinder block 112 'are formed with recessed portions on surfaces to be coupled to each other to form a swash plate chamber 123. A swash plate (126) provided on the rotating shaft (124) is rotatably positioned in the swash plate chamber (123).

A rotating shaft 124 is provided to pass through the center of the front head 111, the front cylinder block 112 and the rear cylinder block 112 '. A flow path 124 'through which the refrigerant flows is formed inside the rotating shaft 124. The flow path 124 'is formed long inside the rotation axis 124 in the longitudinal direction of the rotation axis 124. An inlet 124a and an outlet 124b are formed on the outer surface of the rotating shaft 124. [ The inlet 124a connects the swash plate chamber 123 and the oil passage 124 'and the outlet 124b connects the suction passage 113' of the front cylinder block 112 and the rear cylinder block 112 ' In the present embodiment. The position of the outlet 124b should be formed in accordance with the compression order of the refrigerant flowing in the respective cylinder bores 112a.

A shaft shaft thread 125 is inserted into one side of the rotary shaft 124 and is in close contact with the inner surface of the axial hole O of the front head 111. The shaft shaft 125 serves to prevent the refrigerant from leaking between the rotary shaft 124 and the axial hole O. [ The shaft end work 125 is formed of a rubber material capable of elastic deformation.

A substantially disk-shaped swash plate 126 is provided on the rotating shaft 124 so as to be inclined with respect to the extending direction of the rotating shaft 124. And a plurality of shoe 127 surrounding the edge of the swash plate 126 is installed. The shoe 127 is configured to move along the edge of the swash plate 126.

Meanwhile, the piston 130 is installed in the cylinder bores 112a and 112a 'so as to reciprocate linearly. The piston 130 has a substantially cylindrical shape corresponding to the inside of the cylinder bore 112a and has both ends thereof located at the cylinder bores 112a and 112a 'of the front cylinder block 112 and the rear cylinder block 112' do. That is, both ends of one piston 130 serve to compress the refrigerant in the cylinder bores 112a and 112a '. The intermediate portion of the piston 130 is engaged with the shoe 127, and is linearly reciprocated according to the rotation of the swash plate 126.

The rear head 128 is mounted on one side of the rear cylinder block 112 '. The rear head 128 is provided with a discharge chamber 128a. The discharge chamber 128a is formed over an approximately ring-shaped area. The discharge chamber 128a is opened toward the rear cylinder block 112 '. The discharge chamber 128a is selectively connected to the cylinder bores 112a formed in the rear cylinder block 112 'through a valve plate 115. [

A pulley 140 is rotatably installed at one side of the front head 111. The pulley 140 is formed in a substantially cylindrical shape. The pulley 140 receives the driving force of the engine via a belt (not shown) and is rotated.

A field coil 141 is embedded in the pulley 140. The field coil 141 generates a magnetic attraction force when power is applied to cause the disk 146, which will be described below, to come into contact with the friction surface 140 'of the pulley 140.

A hub 143 is installed at one end of the rotary shaft 124 and a damper 144 is installed at the hub 143. The damper 144 absorbs an impact generated when power is transmitted between the rotation shaft 124 and the pulley 140. The damper 144 is provided with a disk 146 movably installed at a position facing the friction surface 140 'of the pulley 140. The piston 130 is installed in the interior of the damper 144 so as to reciprocate linearly. The piston 130 has a substantially cylindrical shape corresponding to the interior of the cylinder bores 112a and 112a 'and has both ends connected to the cylinder bores 112a and 112a' of the front cylinder block 112 and the rear cylinder block 112 ' ). That is, both ends of one piston 130 serve to compress the refrigerant in the cylinder bores 112a and 112a '. The intermediate portion of the piston 130 is engaged with the shoe 127, and is linearly reciprocated according to the rotation of the swash plate 126.

The rear head 128 is mounted on one side of the rear cylinder block 112 '. The rear head 128 is provided with a discharge chamber 128a. The discharge chamber 128a is formed over an approximately ring-shaped area. The discharge chamber 128a is opened toward the rear cylinder block 112 '. The discharge chamber 128a is selectively connected to the cylinder bores 112a formed in the rear cylinder block 112 'through a valve plate 115. [

A pulley 140 is rotatably installed on one side of the front head 111. [ The pulley 140 is formed in a substantially cylindrical shape. The pulley 140 receives the driving force of the engine via a belt (not shown) and is rotated.

A field coil 141 is embedded in the pulley 140. The field coil 141 generates a magnetic attraction force when power is applied to cause the disk 146, which will be described below, to come into contact with the friction surface 140 'of the pulley 140.

A hub 143 is installed at one end of the rotary shaft 124 and a damper 144 is installed at the hub 143. The damper 144 absorbs an impact generated when power is transmitted between the rotation shaft 124 and the pulley 140. The damper 144 is provided with a disk 146 movably installed at a position facing the friction surface 140 'of the pulley 140.

Hereinafter, the operation of the compressor according to the present invention will be described in detail.

In the compressor 100 of the present invention, when the driving force of the engine is transmitted to the pulley 140 through the belt, the pulley 140 rotates. However, if the field coil 141 is not energized, the disk 146 is not brought into close contact with the friction surface 140 'of the pulley 140, so that the rotation shaft 124 does not rotate.

If the compressor needs to be driven due to the necessity of operating the air conditioning system in such a state, the control system of the user or the vehicle provides a signal for the operation of the air conditioning system. When the operation of the air conditioning system is started and the refrigerant needs to be compressed, the field coil 141 generates power to the field coil 141 to generate the suction magnetic flux.

When power is applied to the field coil 141, the disk 146 is brought into close contact with the friction surface 140 'of the pulley 140 by the magnetic attraction of the field coil 141. Accordingly, the rotational force of the pulley 140 is transmitted to the rotating shaft 124 through the disc 146, the damper 144, and the hub 143.

When the rotational force of the pulley 140 is transmitted to the rotary shaft 124, the rotary shaft 124 rotates to linearly reciprocate the piston 130 to compress the refrigerant.

As the rotary shaft 124 rotates, a flow passage 124 'inside the rotary shaft 124 is connected to the cylinder bores 112a and 112a' through the outlet 124b and the suction passage 113 '. The connection between the flow path 124 'and the cylinder bores 112a and 112a' allows the refrigerant sucked into the swash plate chamber 123 to be transmitted to the cylinder bores 112a and 112a '. For reference, refrigerant is sucked into the cylinder bores 112a and 112a 'when the piston 130 is positioned at the bottom dead center of the corresponding cylinder bores 112a and 112a'. When the refrigerant is delivered to the cylinder bores 112a and 112a ', the piston 130 of the cylinder bores 112a and 112a' moves in the direction of the valve assembly 114, This happens.

At this time, if the inner circumferential surface of the cylinder bores 112a and 112a 'is subjected to an anodizing treatment, the hardness is improved and the abrasion resistance is relatively improved. Therefore, it is possible to prevent abrasion on the inner circumferential surfaces of the cylinder bores 112a and 112a 'due to friction generated in the course of linear reciprocation of the piston 130 in the cylinder bores 112a and 112a' do.

When the refrigerant is compressed in the cylinder bores 112a and 112a ', the pressure inside the cylinder bores 112a and 112a' becomes relatively high, and the refrigerant is discharged to the discharge chambers 111a and 128a. The refrigerant discharged to the discharge chambers (111a, 128a) is transferred to a condenser (not shown) through an external discharge port.

The refrigerant transferred to the condenser through the discharge port passes through a condenser (not shown), an expansion valve (not shown), and an evaporator (not shown), and then is returned to the compressor. In the compressor, the refrigerant is compressed by repeating the process described above.

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 illustrated embodiment, the inner circumferential surfaces of the cylinder bores 112a 'and 112a of the front cylinder block 112 and the rear cylinder block 112' are subjected to an anodizing process, but the present invention is not limited thereto. For example, the inner circumferential surface of the shaft hole 113 formed through the front cylinder block 112 and the rear cylinder block 112 'can also be anodized.

In the illustrated embodiment, the swash plate type compressor having the swash plate is described, but the present invention is not limited thereto. For example, the present invention can be applied to all compressors in which a cylinder bore is formed in a cylinder block and a piston reciprocating linearly is provided in the cylinder bore.

1 is a sectional view showing the construction of a general swash plate type compressor.

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

Description of the Related Art [0002]

100: compressor 111: front head

111a: discharge chamber 112: front cylinder block

112 ': rear cylinder block 112a: cylinder bore

112a ': cylinder bore 113: shaft hole

114: valve assembly 124:

126: swash plate 128: rear head

130: Piston 140: Pulley

O: axial hole

Claims (2)

A cylinder block through which a shaft support hole penetrates, a cylinder block in which a plurality of cylinder bores for compressing a refrigerant while the piston reciprocates in a straight line are formed so as to pass through the shaft hole; A front head installed at one end of the cylinder block and having a shaft hole formed through the center thereof and having a discharge chamber in which refrigerant is discharged; A rear head installed at the other end of the cylinder block and having a discharge chamber in which refrigerant is discharged; And And a rotating shaft that transmits power for linear reciprocating motion of the piston and is rotatably installed through a shaft support hole of the cylinder block and a shaft hole of the front head, Wherein an inner circumferential surface of the cylinder bore and an inner circumferential surface of the shaft hole of the cylinder block are each subjected to an anodizing treatment to form an oxide film. delete

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