KR101193268B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate compressor. In the present invention, the oil recovery hole 117 is provided in the cylinder block 110 in which the plurality of cylinder bores 113 are formed. Both ends of the oil recovery hole 117 are connected to the crank chamber 121 and the suction chamber 133 of the rear housing 130, respectively, and are separated from the refrigerant by an oil separator 147 ″ to separate the crank chamber ( The oil accumulated in 121 is delivered to the suction chamber 133. According to the present invention as described above, the oil separated from the refrigerant by the oil separator 147 ″ embedded in the compressor 100 is transferred to the suction chamber 133 along the oil recovery hole 117 provided in the cylinder block 110. Since the oil can be smoothly circulated, the lubrication performance of the compressor 100 is improved, and the surface temperature of the compressor 100 can be prevented from rising.

Swash plate, compressor, oil separation

Description

Variable displacement swash plate type compressor

The present invention relates to a compressor, and more particularly, to a variable displacement swash plate type compressor in which a refrigerant is delivered into a cylinder bore and compressed through a rotary valve provided on a rotating shaft.

Looking briefly at the air conditioning system of the vehicle, first, the refrigerant of the high temperature low pressure gas state is brought into the high temperature high pressure gas state by the compressor. The refrigerant in the high temperature and high pressure gas state becomes a high temperature high pressure liquid state by a condensation action of the condenser via a condenser, and the refrigerant in the high temperature and high pressure liquid state becomes a low temperature low pressure liquid state by a throttling action of the expansion valve through an expansion valve. do. The refrigerant in the low temperature low pressure liquid state is returned to the high temperature low pressure gas state through heat exchange in the evaporator through the evaporator, and the high temperature low pressure gas is compressed by the compressor to become a high temperature high pressure gas state. By repeating this process, the vehicle air conditioning system is operated.

Compressors for compressing a refrigerant include a reciprocating type that actually compresses a working fluid, a reciprocating type that performs compression while reciprocating, and a rotary type that performs compression while rotating.

The reciprocating type includes a crank type for transmitting the driving force of the drive source to the plurality of pistons using a crank, a swash plate type for transmitting using 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 shows a configuration of a variable displacement swash plate compressor according to the prior art. According to this, the swash plate compressor 1 is provided with a cylinder block 10. The cylinder block 10 forms part of the appearance and skeleton of the compressor 1. A center bore 11 is formed through the center of the cylinder block 10. The center bore 11 is a portion in which the rotating shaft 40 to be described below is rotatably installed.

In addition, a plurality of cylinder bores 13 are formed to radially penetrate the center bore 11 and penetrate the cylinder block 10. The piston 15 is installed inside the cylinder bore 13 to enable a straight reciprocating motion. The piston 15 compresses the refrigerant while linearly reciprocating in the cylinder bore 13.

One front housing 20 is installed at one end of the cylinder block 10. The front housing 20 is recessed to face the cylinder block 10 to cooperate with the cylinder block 10 to form a crank chamber 21 therein. The crank chamber 21 is kept airtight with the outside of the compressor.

The pulley shaft part 22 in which the pulley 60 is rotatably installed protrudes from the opposite side of the cylinder block 10 of the front housing 20. A shaft hole 23 is formed by penetrating the center of the pulley shaft portion 22 and penetrating the front housing 20 back and forth to the crank chamber 21.

The rear housing 30 is installed at the other end of the cylinder block 10, that is, on the opposite side to which the front housing 20 is installed. The rear housing 30 is formed with a discharge chamber 31 in selective communication with the cylinder bore 13. The discharge chamber 31 is a place where the refrigerant compressed in the cylinder bore 13 is discharged and temporarily stays.

The suction chamber 33 is formed at the center of the rear housing 30 facing the cylinder block 10. The suction chamber 33 serves to deliver the refrigerant to be compressed into the cylinder bore 13.

The bolt 37 is fastened through to fasten the cylinder block 10, the front housing 20, and the rear housing 30 to each other. A plurality of bolts 37 are fastened through the edges of the cylinder block 10, the front housing 20, and the rear housing 30 simultaneously.

The rotating shaft 40 is rotatably installed through the center bore 11 of the cylinder block 10 and the shaft hole 23 of the front housing 20. The rotating shaft 40 is rotated by the driving force transmitted from the engine. The rotation shaft 40 is rotatably installed in the front housing 20 and the cylinder block 10.

The rotor 46 is installed on the rotation shaft 40. The rotor 46 is installed in the crank chamber 21 so that the rotating shaft 40 passes through the center and rotates integrally with the rotating shaft 40. The hinge arm 47 protrudes from one surface of the rotor 46. The hinge arm 47 has a hinge slot 47 '.

The swash plate 48 is installed on the rotation shaft 40. The swash plate 48 is formed to protrude a connecting arm 49 is connected to the hinge arm 47 of the rotor 46. The swash plate 48 is hinged and rotated together with the rotor 46. The swash plate 48 is installed so that the angle is variable on the rotation shaft 40, between the state orthogonal to the longitudinal direction of the rotation shaft 40 and inclined at a predetermined angle with respect to the rotation shaft 40 To be in position.

The swash plate 48 has its edge connected via the pistons 15 and the shoe 52. That is, the edge of the swash plate 48 is connected to the connecting portion 16 of the piston 15 through the shoe 52 so that the piston 15 is rotated in the cylinder bore 13 by the rotation of the swash plate 48. Make a straight reciprocating movement.

A valve assembly 53 is provided between the cylinder block 10 and the rear housing 30 to control the flow of the refrigerant between the discharge chamber 31 and the cylinder bore 13. The valve assembly 53 is constituted by a valve plate 54 having a discharge hole 54 'and a discharge lead 56, which controls the flow of refrigerant from the cylinder bore 13 to the discharge chamber 31.

The pulley 60 is rotatably installed at the pulley shaft portion 22 formed at the front end of the front housing 20. The pulley 60 is selectively connected to the rotary shaft 40 and the clutch 62 to transmit the driving force of the engine to the rotary shaft 40 via the pulley 60 and the clutch 62.

On the other hand, it will be described that the refrigerant is delivered into the cylinder bore (13). The refrigerant is sucked from the outside into the suction chamber 33, and the refrigerant delivered to the suction chamber 33 is transferred into the cylinder bore 13.

In addition, the refrigerant delivered to the cylinder bore 13 and compressed during the reciprocating motion of the piston 15 is delivered to the discharge chamber 31 by the valve assembly 53 and is transferred to the outside of the compressor 1. . That is, when the refrigerant is compressed and the pressure inside the cylinder bore 13 becomes large, the tip of the discharge lead 56 is pushed by the pressure, and the refrigerant is discharged into the discharge chamber 31 inside the cylinder bore 13. It is.

However, the above-described conventional techniques have the following problems.

If the oil contained in the refrigerant is not sufficiently supplied or leaked, there is a problem that the durability of the compressor 1 is lowered because the lubrication of the compressor 1 is not smoothly performed.

In order to solve this problem, an oil separator 47 ″ may be installed to separate and recover oil from the refrigerant discharged in the compressor 1 and return the oil to the inside of the compressor 1. Types of such oil separator 47 '' include a built-in oil separator 47 '' embedded in the compressor 1 and an external oil separator installed outside the compressor 1 according to the installed position. In the case of an external oil separator, the manufacturing and designing are relatively easy and the oil separation efficiency is good. However, the external oil separator is installed separately from the compressor 1 and takes a large installation space.

On the other hand, in the case of the built-in oil separator 47 '' by discharging the relatively viscous oil to the crank chamber 21 by using the centrifugal force according to the rotation of the rotor 46, it does not occupy a separate installation space, When the compressor 1 is operated at a high speed, the oil separation function is excessively performed, so that oil is accumulated in the compressor 1, in particular, the crank chamber 21, and thus cannot be recovered. 1 shows a compressor 1 employing a built-in oil separator 47 ″.

In particular, if the oil is not recovered and stays in the crank chamber 21, the cooling performance by the oil is lowered, so that the total temperature of the compressor is increased. There is a problem that the durability of the compressor, such as being damaged.

Accordingly, an object of the present invention is to solve the problems of the prior art as described above, so that the oil separated from the oil separator installed inside the compressor in the variable displacement swash plate compressor is smoothly recovered to the suction chamber and the center bore. It is.

Another object of the present invention is to adjust the oil circulation rate and the temperature of the compressor by appropriately setting the size of the oil recovery hole formed in the cylinder block.

According to a feature of the present invention for achieving the object as described above, the present invention is a cylinder block through which a center bore is formed and a plurality of cylinder bores are formed around the center bore, and the front end of the cylinder block. And a rotating shaft provided at the rear end and the front housing and the rear housing, respectively, rotating through the center bore and the crank chamber of the front housing and rotating together with a swash plate positioned in a variable inclination in the crank chamber. A rotor having an oil separator coupled to the rotating shaft and connected together with one end of the swash plate and separating oil from a refrigerant to be discharged into the crank chamber, and receiving the rotation of the rotating shaft through the swash plate; A swash plate compressor comprising a piston for respectively compressing a refrigerant in the In the cylinder block, it is that both ends are provided with oil return holes each coupled to the crank chamber and the suction chamber of the rear housing conveys the oil in the crank chamber a suction chamber.

The oil recovery hole is provided between the cylinder bore and the center bore provided in the lowermost direction in the direction of gravity of the plurality of cylinder bores.

The oil recovery hole includes an inlet hole communicating with the crank chamber and a discharge hole connected with the inlet hole and communicating with the suction chamber.

The inlet hole has a diameter of 1.5mm to 3.5mm, and the discharge hole is formed to be greater than or equal to the inlet hole.

In the variable displacement swash plate compressor according to the present invention having such a configuration, the following effects can be obtained.

In the variable displacement swash plate compressor according to the present invention, the oil separated from the refrigerant by the oil separator built into the compressor can be introduced into the suction chamber and the center bore along the oil recovery hole provided in the cylinder block. The smoother the better the lubrication performance of the compressor, thereby improving the durability of the compressor.

In addition, in the present invention, since the oil separated from the refrigerant is continuously circulated without staying inside the crank chamber, the total temperature of the compressor is lowered, thereby preventing the parts of the compressor from being damaged by heat.

In addition, in the present invention, the surface temperature of the compressor is lowered by appropriately setting the size of the oil recovery hole provided in the cylinder block, and at the same time, the oil circulation rate can be maintained below a certain size, thereby improving the compressor performance.

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

2 is a cross-sectional view showing the configuration of a preferred embodiment of a variable displacement swash plate compressor according to the present invention, and FIGS. 3 and 4 are a cross-sectional view and a front view showing the configuration of a cylinder block constituting an embodiment of the present invention. 5 is a cross-sectional view of the configuration of the rotor and the rotating shaft coupled to the embodiment of the present invention.

As shown in these figures, the swash plate compressor 100 is provided with a cylinder block 110. The cylinder block 110 forms part of an appearance and a skeleton of the compressor 100. A center bore 111 is formed through the center of the cylinder block 110. The center bore 111 is a portion in which the rotating shaft 140 to be described below is rotatably installed.

A plurality of cylinder bores 113 are formed to radially penetrate the center bore 111 and penetrate the cylinder block 110. A communication path 114 is formed to communicate the cylinder bore 113 and the center bore 111. The communication path 114 is a passage for transferring the refrigerant to the cylinder bore 113.

 The piston 115 is installed inside the cylinder bore 113 to enable a straight reciprocating motion. The piston 115 has a cylindrical shape, and the cylinder bore 113 has a cylindrical shape corresponding thereto. The piston 115 compresses the refrigerant while linearly reciprocating in the cylinder bore 113.

On the other hand, the cylinder block 110 has a weight loss groove 116 is formed. The weight loss groove 116 serves to reduce the weight of the cylinder block 110, and further the compressor 100.

In this case, an oil recovery hole 117 is formed in the cylinder block 110. The oil recovery hole 117 is a kind of passage in which oil separated from the refrigerant by the oil separator 155 to be described below and discharged into the crank chamber 121 is recovered into the suction chamber 133 and the center bore 111. to be. That is, the oil is lubricated by a part of the oil into the center bore 111 through the oil recovery hole 117, and part of the oil is introduced into the cylinder bore 113 through the suction chamber 133 to play a lubricating role. . In addition, in the oil circulation process, the oil also performs a role of cooling the inside of the compression chamber.

As shown in FIG. 2, the oil recovery hole 117 is very small in diameter, and is formed to extend in the operation direction of the piston 115. The oil recovery hole 117 is formed to have a very small diameter compared to the size of the crank chamber 121, and absorbs oil by the capillary phenomenon and transfers it to the suction chamber 133.

More precisely, as shown in FIG. 3, the oil recovery hole 117 includes an inlet hole 117a connecting the fat loss groove 116 and the crank chamber 121, and the fat loss groove 116. It is composed of a discharge hole (117b) for communicating between the center bore (111). That is, the inflow hole 117a is formed in a direction parallel to the direction of movement of the piston 115, and the discharge hole 117b is formed in a direction orthogonal thereto.

At this time, as shown in Figure 4, the diameter of the inlet hole (117a) is preferably located at the lower side when viewed in the direction of gravity of the fat groove 116. This is to allow the oil separated by the crank seal 121 to be easily moved along the inlet hole 117a. This can be seen more clearly in the table below.

Location of inflow hole 117a Compressor Surface Temperature Reduction (%) % Of oil remaining in the crankcase compared to the standard Image (① of Fig. 4) -26.2 -19.8 (② of Fig. 4) -40.2 -20.8 Lower (③ in Fig. 4) -68.8 -46.1

As shown in the above table, the surface of the compressor exists when the oil recovery hole is not present and when the position of the inflow hole 117a is located at the lowermost side when viewed in the direction of gravity among the fat loss grooves 116. It can be seen that the temperature and the amount of oil remaining in the crank chamber 121 are reduced.

On the other hand, Figure 6 is a graph showing the change in the surface temperature and oil circulation rate of the compressor according to the diameter of the inlet hole (117a). In this case, the oil circulation rate (Oil In Circulation) represents the weight ratio of the oil to the total weight of the refrigerant and the oil. This unique circulation rate should be maintained at an appropriate level. If it is too small, a problem occurs in lubrication of parts, and if too large, a compression function made by the refrigerant is deteriorated, resulting in a decrease in compressor efficiency. In addition, the surface temperature of the compressor must also be maintained below a certain level to maintain the efficiency of the compressor.

More precisely, the oil circulation rate should be kept below 8% and the compressor's surface temperature below 160 °.

As shown in the graph, it can be seen that the oil circulation rate increases rapidly from the point where the diameter of the inlet hole 117a becomes 2 mm or more, and the surface temperature of the compressor decreases steadily as the diameter of the inlet hole 117a increases. I can see that. And, it can be seen from the graph that when the diameter of the inlet hole 117a is 1.5 mm to 3.5 mm, both the oil circulation rate and the surface temperature of the compressor can be satisfactorily satisfied.

More precisely, when the diameter of the inlet hole 117a is 1.5 mm or less, the surface temperature of the compressor is 160 ° or more, and when the diameter of the inlet hole 117a is 3.5 mm or more, the oil circulation rate exceeds 8%. Therefore, the diameter of the inflow hole (117a) should be formed of 1.5mm to 3.5mm, preferably 2.5mm.

In this case, the size of the cross-sectional area of the discharge hole 117b is preferably greater than or equal to the size of the cross-sectional area of the inlet hole 117a. This is to move the oil along the inlet hole (117a) to the fat loss groove 116 to be more smoothly introduced into the suction chamber 133 and the center bore 111 through the discharge hole (117b). will be.

The front housing 120 is installed at one end of the cylinder block 110. The front housing 120 has a concave side facing the cylinder block 110 to cooperate with the cylinder block 110 to form a crank chamber 121 therein. The crank chamber 121 is kept airtight with the outside of the compressor.

The pulley shaft portion 122, on which the pulley 160 is rotatably installed, protrudes from the opposite side of the cylinder block 110 of the front housing 120. The shaft hole 123 is formed by penetrating the center of the pulley shaft portion 122 and penetrating the front housing 120 back and forth to the crank chamber 121. The shaft hole 123 is formed to coincide with the center bore 111. One end of the rotating shaft 140 is rotatably supported by the shaft hole 123.

The other end of the cylinder block 110, that is, the rear housing 130 is installed on the opposite side where the front housing 120 is installed. The rear housing 130 is formed with a discharge chamber 131 in selective communication with the cylinder bore 113. The discharge chamber 131 is formed along an edge of a surface of the rear housing 130 that faces the cylinder block 110. The discharge chamber 131 is a place where the refrigerant compressed in the cylinder bore 113 is discharged and temporarily stays.

The suction chamber 133 is formed at the center of the rear housing 130 facing the cylinder block 110. The suction chamber 133 also selectively communicates with the cylinder bore 113. The suction chamber 133 serves to deliver a refrigerant to be compressed into the cylinder bore 113.

The bolt 137 penetrates and fastens the cylinder block 110, the front housing 120, and the rear housing 130 to be fastened to each other. A plurality of bolts 137 penetrates through the edges of the cylinder block 110, the front housing 120, and the rear housing 130 simultaneously.

The rotating shaft 140 is rotatably installed through the center bore 111 of the cylinder block 110 and the shaft hole 123 of the front housing 120. The rotating shaft 140 is rotated by the driving force transmitted from the engine. The rotation shaft 140 is rotatably installed in the front housing 120 and the cylinder block 110.

The rotor 146 is installed on the rotation shaft 140. The rotor 146 is installed in the crank chamber 121 so that the rotating shaft 140 passes through the center and rotates integrally with the rotating shaft 140. The rotor 146 is installed to be fixed to the rotating shaft 140 in a substantially disk shape. The hinge arm 147 protrudes from one surface of the rotor 146. A hinge slot 147 'is formed in the hinge arm 147.

At this time, as shown in Figure 5, the rotor 146 is provided with an oil separator (147 ''). The oil separator 147 ″ is used to separate oil in a state in which a refrigerant and oil are mixed, and oil having a relatively high viscosity using a centrifugal force due to the rotation of the rotor 146 is an oil separator 147 ″. Through the crank chamber 121 is discharged.

The swash plate 148 is installed on the rotation shaft 140. The swash plate 148 protrudes from the connecting arm 149 which is connected to the hinge arm 147 of the rotor 146. A hinge pin 149 'is installed at a distal end of the connecting arm 149 in a direction orthogonal to the longitudinal direction of the connecting arm 149. The hinge pin 149' is a hinge arm 147 of the rotor 146. It is movably walked to the hinge slot 147 'formed at the tip of the head.

The swash plate 148 is hinged and rotated together with the rotor 146. The swash plate 148 is installed so that the angle is variable on the rotating shaft 140, between the state orthogonal to the longitudinal direction of the rotating shaft 140 and inclined at a predetermined angle with respect to the rotating shaft 140 To be in position.

The radial shaft spring 150, which is a coil spring, is installed on the rotary shaft 140 to surround the rotary shaft 140. The radial yarn spring 150 exerts an elastic force between the rotor 146 and the swash plate 148. The radial yarn spring 150 exerts an elastic force in a direction in which the inclination angle of the swash plate 148 decreases, and absorbs a force acting on the swash plate 148 when the compressor 100 is stopped. do.

The swash plate 148 has an edge thereof connected to the pistons 115 and the shoe 152. That is, the edge of the swash plate 148 is connected to the connecting portion 116 of the piston 115 through the shoe 152 so that the piston 115 is in the cylinder bore 113 by the rotation of the swash plate 148. Make a straight reciprocating movement.

A valve assembly 153 is provided between the cylinder block 110 and the rear housing 130 to control the flow of the refrigerant between the discharge chamber 131 and the cylinder bore 113. The valve assembly 153 is constituted by a valve plate 154 and a discharge lead 156 having a discharge hole 154 ′, which controls the flow of refrigerant from the cylinder bore 113 to the discharge chamber 131.

A pulley 160 is rotatably installed at the pulley shaft portion 122 formed at the front end of the front housing 120. The pulley 160 is selectively connected to the rotary shaft 140 and the clutch 162 to transmit the driving force of the engine to the rotary shaft 140 via the pulley 160, the clutch 162.

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

When the rotation shaft 140 is rotated by the driving force of the engine, the rotor 146 rotates together, and the swash plate 148 rotates together by the rotor 146. Rotation of the swash plate 148 is transmitted to the piston 115 through the shoe 152.

Accordingly, the piston 115 compresses the refrigerant while linearly reciprocating in the cylinder bore 113. At this time, the stroke distance of the piston 115 is determined according to the angle of the swash plate 148. The angle of the swash plate 148 may be adjusted by the pressure of the refrigerant delivered into the crank chamber 121.

On the other hand, when the refrigerant is delivered into the cylinder bore 113, the refrigerant compressed by the piston 115 is delivered to the discharge chamber 131 by the valve assembly 153 and transferred to the outside of the compressor 100. do. That is, when the refrigerant is compressed to increase the pressure inside the cylinder bore 113, the tip of the discharge lead 156 is pushed by the pressure, and the discharge hole 154 ′ is opened to open the inside of the cylinder bore 113. Discharges the refrigerant to the discharge chamber 131.

On the other hand, in the operation of the compressor 100, the oil contained in the refrigerant is subjected to a process that is separated from the refrigerant recovered, which is made by the oil separator 147 ″ and the oil recovery hole 117. That is, the oil separated from the refrigerant by the oil separator 147 ″ provided in the rotor 147 and accumulated in the crank chamber 121 moves along the oil recovery hole 117 to move to the suction chamber 133 and the center. It is delivered to the bore 111.

More precisely, the oil accumulated in the crank chamber 121 is moved along the inflow hole 117a in the oil recovery hole 117 by the capillary phenomenon, and flows into the fat loss groove 116. Then, it moves along the discharge hole (117b) provided on one side of the fat groove 116 is finally delivered to the suction chamber 133.

As such, the oil does not stay in the crank chamber 121, but flows along the inside of the compressor 100 to be contained in the refrigerant at a constant ratio, thereby lubricating and cooling, and thus the temperature of the compressor 100 is increased by the oil. Is prevented.

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

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

Figure 2 is a cross-sectional view showing the configuration of a preferred embodiment of a variable displacement swash plate compressor according to the present invention.

Figure 3 is a cross-sectional view showing the configuration of the cylinder block constituting the embodiment of the present invention.

Figure 4 is a front view showing the configuration of the cylinder block constituting the embodiment of the present invention.

Figure 5 is a cross-sectional view showing the configuration of a rotor and a rotating shaft coupled to the embodiment of the present invention.

6 is a graph showing changes in the temperature of the compressor and the size of the oil circulation rate according to the size of the oil recovery hole of the cylinder block constituting an embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

100: compressor 110: cylinder block

111: center bore 113: cylinder bore

114: communication path 115: piston

116: lose weight home 117: oil recovery hole

120: front housing 121: crankcase

122: pulley shaft portion 123: shaft hole

130: rear housing 131: discharge chamber

133: suction chamber 140: rotation axis

146: rotor 147: hinge arm

147 ': hinge slot 147' ': oil separator

148: Saphan 149: connecting arm

150: radial yarn spring 153: valve assembly

154: valve plate 154 ': discharge hole

156: discharge lead 160: pulley

Claims (4)

A cylinder block 110 having a center bore 111 formed therethrough and a plurality of cylinder bores 113 formed around the center bore 111; A front housing 120 and a rear housing 130 provided at the front and rear ends of the cylinder block 110, respectively; Rotating shaft which is installed and rotated through the crank chamber 121 of the center bore 111 and the front housing 120 and rotated in combination with the swash plate 148 variablely inclined in the crank chamber 121 140, Rotor 147 is coupled to the rotary shaft 140 is rotated together, connected to one end of the swash plate 148 and is provided with an oil separator (147 '') for separating oil from the refrigerant to discharge into the crank chamber 121 ), And In the swash plate-type compressor comprising a piston 115 for receiving the rotation of the rotary shaft 140 through the swash plate 148 to compress the refrigerant in the cylinder bore 113, respectively, The cylinder block 110 has an inflow hole 117a communicating with the crank chamber 121, an inner space of the center bore 111 and an inner space of the suction chamber 133 of the rear housing 130. An oil recovery hole 117 having a discharge hole 117b communicating with each other is formed so that oil accumulated in the crank chamber 121 is formed in the inner space of the center bore 111 and the suction chamber of the rear housing 130. 133) to flow into, The oil recovery hole 117 is characterized in that it is provided between the cylinder bore 113 and the center bore 111 located in the lowermost when viewed based on the direction of gravity of the respective cylinder bore (113) Variable displacement swash plate compressor. delete delete The variable displacement swash plate of claim 1, wherein a diameter of the inflow hole 117a is 1.5mm to 3.5mm, and the discharge hole 117b is formed to be larger than or equal to the inflow hole 117a. Type compressor.

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