KR20080052370A - Variable displacement compressor - Google Patents

Abstract

A variable capacitance compressor is provided to maintain a proper amount of lubricant in a control pressure chamber by forming an intake hole in a rotary shaft and forming a communication passage around a through hole of a swash plate. A variable capacitance compressor comprises a housing(12), a rotary shaft(15), a rotation support body(22) and a swash plate(24) connected to the rotation support body. A shaft-inside discharge passage(15b) is formed in the rotary shaft to form a part of a discharge passage. An intake hole(16d) is formed at a side of the rotation support body in a control pressure chamber(C). At least one of the swash plate and the rotary shaft has a communication passage(46). The intake hole is opened toward a front area(C2) in a side of the rotation support body between the swash plate and the rotation support body while communicating with the shaft-inside discharge passage. The communication passage allows the front area to communicate with a rear area(C1) in a side of the rotation support body.

Description

Variable displacement compressors {VARIABLE DISPLACEMENT COMPRESSOR}

The present invention relates to a variable displacement compressor in which the inclination angle of the swash plate is changed by controlling the inside of the control pressure chamber and the discharge capacity is controlled.

As this kind of variable displacement compressor (hereinafter, simply referred to as a compressor), for example, one disclosed in Patent Document 1 may be mentioned. As shown in FIG. 10, the crank chamber 80 is partitioned and the shaft 81 is rotatably supported in the housing of the compressor of patent document 1. As shown in FIG. In the crank chamber 80, the rotor 92 is fixed to the shaft 81, the rotary swash plate 82 is supported at variable inclination angles, and the rotary swash plate 82 is provided with a plurality of pistons 83. Mooring through). The piston 83 is inserted into the cylinder bore 94 in the housing so as to reciprocate.

Moreover, the discharge chamber 85 and the suction chamber 86 are partitioned in the housing of the compressor. The discharge chamber 85 and the crank chamber 80 communicate with each other through the first passage 87 and the second passage 88, and the suction chamber 86 and the crank chamber 80 communicate with each other through a ventilator. . The duct includes an axial passage 89 formed in the shaft 81 along the axial direction, a communication hole 90 formed in the shaft 81 so as to communicate with the axial passage 89, and the axial passage. It is formed by the third passage 91 which communicates the 89 and the suction chamber 86. The communication hole 90 is located between the rotary swash plate 82 and the rotor 92.

In the compressor, the refrigerant gas in the discharge chamber 85 is supplied to the crank chamber 80 through the first passage 87 and the second passage 88. In addition, the refrigerant gas of the crank chamber 80 passes through the axial passage 89 from the communication hole 90 and is discharged to the suction chamber 86 through the third passage 91. Then, the pressure in the crank chamber 80 is pressure-controlled, and the inclination angle of the rotating swash plate 82 is changed by the pressure-regulation so that the discharge capacity of the compressor is adjusted.

The refrigerant gas supplied from the discharge chamber 85 to the crank chamber 80 and the broby gas leaked from the cylinder bore 94 and the piston 83 to the crank chamber 80 contain lubricating oil. And when the refrigerant gas and the broby gas move in the crank chamber 80 toward the communication hole 90, the lubricating oil contained in the refrigerant gas and the broby gas moves to each sliding part (for example, the crank chamber 80). For example, it is supplied to the rotating swash plate 82 and the sliding part of the shoe 84). In addition, the lubricating oil contained in the refrigerant gas and the broby gas moving in the crank chamber 80 is subjected to the centrifugal force of each rotating member (rotating swash plate 82, rotor 92, etc.) by the rotation of the shaft 81. It separates from each gas and disperse | distributes to the periphery of the shaft 81 and the inner wall surface of the crank chamber 80. As shown in FIG. And the dispersed lubricating oil is supplied to each sliding part in the crank chamber 80. Therefore, the lubricating oil is to achieve lubrication of each sliding part.

By the way, the lubricating oil contained in the refrigerant gas is blown around the shaft 81 by the centrifugal force by the rotation of the shaft 81, and the lubricating oil is in a state where the lubricating oil is insufficient around the communication hole 90. For this reason, it is difficult for the lubricant oil to be discharged to the suction chamber 86 through the communication hole 90, the axial passage 89, and the third passage 91, and an excessive amount of lubricant oil is present in the crank chamber 80. It becomes the atmosphere. And when an excessive amount of lubricating oil exists in the crank chamber 80, the lubricating oil is agitated by the rotary swash plate 82 or the rotor 92 to generate heat, the viscosity of the lubricating oil is lowered by the heat generated, the lubrication of the lubricating oil The ability is degraded.

Here, the inlet to the additional gas discharger for discharging the refrigerant gas is formed not in the rotating body (shaft 81) but in the end face of the non-rotating body, for example, the housing (cylinder block) forming the crank chamber 80, and lubricating oil. It is conceivable that the structure makes it difficult to be influenced by the centrifugal force and discharges lubricant oil into the suction chamber 86. However, in this structure, lubricating oil is excessively discharged | emitted to the suction chamber 86 too much, and the amount of lubricating oil in the crank chamber 80 becomes small, and the said sliding part will become inadequate in lubrication.

Patent Document 1: Japanese Unexamined Patent Publication No. 2004-28090

This invention is made | formed in view of the said conventional problem, The objective is to provide the variable displacement compressor which can ensure an appropriate amount of lubricating oil in a control pressure chamber.

In order to solve the above problems, the invention described in claim 1 is characterized in that, while the first end side of the rotating shaft is rotatably supported on the front side of the housing, the second end side of the rotating shaft is rotatably supported on the rear side, In the control pressure chamber, a rotary support fixed to the rotary shaft and a swash plate directly supported by the rotary shaft and connected to the rotary support via a hinge mechanism and integrally rotated with the rotary shaft are accommodated at variable inclination angles, and the discharge pressure region and the control pressure chamber are accommodated. The refrigerant gas in the discharge pressure region is supplied to the control pressure chamber through a supply passage communicating with each other, and the refrigerant gas in the control pressure chamber is discharged into the suction pressure region through the discharge passage communicating the suction pressure region with the control pressure chamber to regulate the pressure in the control pressure chamber. And a variable displacement compressor in which the inclination angle of the swash plate is changed to control the discharge capacity. The in-axis discharge passage which forms a part of the discharge passage is formed, and is opened toward the front side region between the swash plate and the rotating support in the control pressure chamber, and communicates with the in-axis discharge passage. An introduction hole is formed, and at least one of the swash plate and the rotating shaft is provided with a communication path communicating with the front side region and the rear side region of the anti-rotation support side of the swash plate in the control pressure chamber.

According to this configuration, the refrigerant gas in the rear region and the lubricant oil contained in the refrigerant gas in the control pressure chamber pass through the communication path and are supplied to the front region. That is, the refrigerant gas in the rear region and the lubricating oil contained in the refrigerant gas are not supplied to the front side region by turning around the outer circumferential side of the swash plate, but in the rear region through the communication path formed in at least one of the swash plate and the rotating shaft. Supplied to the area. For this reason, compared with the case where a communication path is not formed, the amount of lubricating oil around an introduction hole can be made large. Therefore, as compared with the case where the communication path is not formed, the amount of lubricating oil discharged from the inlet hole to the suction pressure region can be increased, thereby avoiding a situation in which excessive amount of lubricating oil is present in the control pressure chamber. As a result, an appropriate amount of lubricating oil can be ensured in the control pressure chamber.

The communication path may be formed by penetrating the swash plate in the thickness direction. According to this configuration, unlike the case where the lubricant gas contained in the refrigerant gas and the refrigerant gas in the rear region is passed through the outer circumferential side of the swash plate and supplied to the front region, the refrigerant gas and the refrigerant gas are included in the front region. It is possible to supply lubricating oil which is surely and quickly.

In the swash plate, an insertion passage hole through which the rotating shaft is inserted may be formed, and the communication path may be formed by a groove extending over the entire thickness direction of the swash plate on the inner circumferential surface of the swash plate forming the insertion passage hole. The communication path may be formed by a groove communicating with the introduction hole while being concave on the circumferential surface of the rotation shaft. Also in this configuration, the refrigerant gas in the rear region and the lubricant oil contained in the refrigerant gas in the control pressure chamber can be supplied to the front region.

In addition, the swash plate protrudes from the maximum inclination angle regulating portion that restrains the maximum inclination angle of the swash plate by contacting the rotatable support, and the opening to the front side area in the communication path is formed between the maximum inclination angle regulating portion and the hinge mechanism. It may be located in. In particular, it is preferable that the opening to the front side area in the communication path is located between the maximum inclination angle restricting portion and the rotation shaft.

According to this configuration, the refrigerant gas and the lubricant oil contained in the refrigerant gas supplied from the opening to the front side region in the communication path to the front side region are hardly affected by the centrifugal force by the maximum inclination angle restricting portion and the hinge mechanism. Therefore, the refrigerant gas and the lubricating oil contained in the refrigerant gas can be kept around the rotating shaft. Therefore, for example, compared with the case where the opening to the front side area | region in a communication path is formed in the outer peripheral side of the swash plate radial direction instead of between a maximum inclination-angle restricting part and a hinge mechanism, it is an inlet hole to a suction pressure area | region. The amount of lubricating oil discharged can be increased.

According to the present invention, an appropriate amount of lubricant can be ensured in the control pressure chamber.

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of the variable displacement compressor which embodied this invention is described according to FIGS. In addition, in the following description, "before" and "after" of the variable displacement compressor correspond to before and after in the arrow Y extending in the front-back direction of FIG.

FIG. 1: shows the longitudinal cross-sectional view of the variable displacement compressor 10 of this embodiment. The housing of the variable displacement compressor 10 includes a cylinder block 11, a front housing 12 bonded and fixed to the front end thereof, and a rear housing 14 bonded and fixed to the rear end of the cylinder block 11. have. In addition, an intake valve forming plate 36 and a valve plate 13 are interposed between the cylinder block 11 and the rear housing 14 from the cylinder block 11 side toward the rear housing 14 side. The valve plate 13 is equipped with a discharge valve forming plate 28 and a retainer 33. The control pressure chamber C is formed between the cylinder block 11 and the front housing 12, and the rotary shaft 15 passes through the control pressure chamber C in the cylinder block 11 and the front housing 12. This is rotatably supported.

The said rotation shaft 15 is the inside of the 1st rotation shaft 16 which comprises the hollow cylinder which the rear end surface of the rear housing 14 side opened, and front and rear end surfaces of the front housing 12 side and the rear housing 14 side. The 2nd rotating shaft 17 which comprises this open hollow cylinder is press-inserted (inserted), and is formed in double tube shape. An O ring O is interposed between the inner circumferential surface of the first rotating shaft 16 and the outer circumferential surface of the second rotating shaft 17. And the in-axis supply passage 15a extended along the axial direction of the central axis T of the rotating shaft 15 is formed in the rotating shaft 15. As shown in FIG. Moreover, in the rotating shaft 15, the in-axis discharge passage 15b is formed between the inner peripheral surface of the 1st rotating shaft 16 and the outer peripheral surface of the 2nd rotating shaft 17. As shown in FIG.

In the first rotating shaft 16 in the rotating shaft 15, a discharge passage 16c is formed which communicates with the in-axis supply passage 15a and opens toward the front housing 12. Moreover, in the rotating shaft 15, the in-axis supply passage 15a is opened in the rear end surface of the rotating shaft 15. As shown in FIG. In the first rotary shaft 16 of the rotary shaft 15, an inlet 16d for communicating the in-axis discharge passage 15b and the controlled pressure chamber C is formed at a position facing the control pressure chamber C. have. Moreover, in the rotating shaft 15, the in-axis discharge passage 15b is opened in the rear end surface of the rotating shaft 15. As shown in FIG.

In the rotating shaft 15 of the said structure, the front end side used as the 1st end side of the rotating shaft 15 is supported by the front housing 12 so that rotation is possible. In the front housing 12, the shaft seal chamber 20 is formed between the circumferential surface of the rotation shaft 15 and the inner circumferential surface of the front housing 12 opposite to the circumferential surface. And in the shaft seal chamber 20, the shaft seal member 21 which seals between the circumferential surface of the said rotating shaft 15 (1st rotating shaft 16a) and the inner peripheral surface of the shaft seal chamber 20 is formed. . By this shaft sealing member 21, leakage of the refrigerant gas out of the variable displacement compressor 10 from the control pressure chamber C along the circumferential surface of the rotating shaft 15 is suppressed.

The rear end side serving as the second end side of the rotating shaft 15 is inserted into the shaft hole 11b formed in the cylinder block 11 and is rotatably supported by the shaft hole 11b by the bearing 19. Accordingly, the rotation shaft 15 is rotatably supported on the front end (front housing 12) side of the housing, and the second end side is rotated on the rear side (rear housing 14 side) of the housing. Possibly supported.

In addition, a receiving hole 11c communicating with the shaft hole 11b is partitioned between the cylinder block 11 and the valve plate 13. In the accommodation hole 11c, the rear end of the second rotation shaft 17 in the rotation shaft 15 protrudes, and the in-axis supply passage 15a communicates with the accommodation hole 11c. Moreover, in the accommodation hole 11c, the lip seal 37 is interposed between the outer peripheral surface of the 2nd rotation shaft 17 and the circumferential surface of the accommodation hole 11c. And the lip seal 37 seals the in-axis supply passage 15a and the in-axis discharge passage 15b at the rear end of the rotating shaft 15, and the inside of the accommodating hole 11c in the in-axis supply passage 15a. Is divided into a supply space (S1) communicating with each other) and a discharge space (S2) communicating with the in-axis discharge passage (15b).

In the control pressure chamber C, the rotary support 22 is fixed to the rotary shaft 15, and the rotary support 22 is fixed to the rotary shaft 15 so as to be integrally rotatable. This rotating support 22 is rotatably supported by the front housing 12 by the radial bearing 18. That is, the rotation shaft 15 is rotatably supported by the front housing 12 by the radial bearing 18 via the rotation support body 22. In addition, a thrust bearing 23 is formed between the rotary support 22 and the inner wall surface of the front housing 12. Moreover, the swash plate 24 which forms substantially disk shape is accommodated in the control pressure chamber C. As shown in FIG. On the side of the rear housing 14 in this swash plate 24, the 1st protrusion part 41 which comprises a cylindrical shape protrudes.

Moreover, in the state in which the 1st protrusion part 41 passed through the support hole 42a which penetrated the center part, the sliding plate 42 which comprises an annular shape is inserted in the outer peripheral side of the 1st protrusion part 41 in the center part, It is arranged. Between the first protrusion 41 and the inner circumferential surface of the support hole 42a of the sliding plate 42 and between the outer circumferential portion of the swash plate 24 and the sliding plate 42 facing the outer circumferential portion, the bearing 43 Intervened. And the swash plate 24 rear by the end surface 42c of the rear housing 14 side in the said sliding plate 42, and the end surface 41a of the rear housing 14 side of the 1st protrusion part 41. The cross section of the side is formed. In the center of the swash plate 24, an insertion through hole 24a protrudes through the swash plate 24, and the rotation shaft 15 is inserted into the insertion through hole 24a.

The hinge mechanism 25 is interposed between the rotary support 22 and the swash plate 24. The swash plate 24 is the rotary shaft 15 and the rotary support by the hinge connection between the rotary support 22 via the hinge mechanism 25 and the direct support of the rotary shaft 15 through the insertion through hole 24a. In addition to being able to rotate synchronously with 22, the inclination angle can be changed with respect to the rotational shaft 15 with the slide movement in the axial direction along the central axis T of the rotational shaft 15. That is, the swash plate 24 is capable of changing its inclination within a predetermined angle range between the maximum inclination angle and the minimum inclination angle with respect to the plane perpendicular to the axial direction along the central axis T of the rotation shaft 15. . In addition, the maximum inclination angle is the inclination angle of the swash plate 24 when the discharge capacity in the variable displacement compressor 10 becomes the maximum, and the minimum inclination angle is the inclination of the swash plate 24 when the discharge capacity becomes minimum. Angle.

In the cylinder block 11, the some cylinder bore 26 is penetrated by the equal angle space | interval about the rotating shaft 15. As shown in FIG. The cylinder bore 26 is housed so that the migrating piston 27 can reciprocate in the axial direction of the central axis T of the rotation 15. The opening of the cylinder bore 26 is closed by the valve plate 13 and the piston 27, and in this cylinder bore 26, the compression chamber 38 which changes in volume with the movement of the piston 27 is provided. It is partitioned. The piston 27 is a swash plate 24 and a sliding plate 42 through a pair of shoes 29 formed on the front housing 12 side of the swash plate 24 and the rear housing 14 side of the sliding plate 42. Moored to the outer periphery of the That is, the shoe 29 is the sliding plate 24b formed in the outer peripheral part of the front side end surface 24c of the swash plate 24, the end surface 42c of the sliding plate 42, and the shoe accommodating part 27a of the piston 27. Is accommodated between the inner surfaces of the And the rotational motion of the swash plate 24 is moved back and forth of the piston 27 through the shoe 29 by the sliding contact with the sliding surface 24b of the shoe 29 and the inner surface of the shoe accommodating part 27a. It is intended to be converted to reciprocating motion.

In the rear housing 14, the suction chamber 30 which faces the said valve plate 13 as a suction pressure area | region, and the discharge chamber 31 as a discharge pressure area | region are formed. Specifically, the discharge chamber 31 is formed in the central portion of the rear housing 14, and the suction chamber 30 surrounds the discharge chamber 31 in a ring shape on the outer circumferential side of the discharge chamber 31. Formed. In the valve plate 13, a suction port 32 is formed at the radially outer side of the valve plate 13 at a position facing the cylinder bore 26, and at the radially inner side of the valve plate 13. Discharge ports 34 are formed, respectively. The suction valve forming plate 36 is formed with a suction valve 36a for opening and closing the suction port 32 at a position corresponding to the suction port 32. Moreover, the discharge hole 36b is formed in the said suction valve formation plate 36 in the position corresponding to the said discharge port 34. As shown in FIG. The discharge valve formation plate 28 is provided with a discharge valve 28a for opening and closing the discharge port 34 at a position corresponding to the discharge port 34. The discharge position of the discharge valve 28a is restricted by the retainer 33.

The high pressure refrigerant gas discharged into the discharge chamber 31 is led to the external refrigerant circuit 40. The refrigerant gas derived from the external refrigerant circuit 40 is cooled in the condenser 40a constituting the external refrigerant circuit 40, decompressed by the expansion valve 40b, and then sent to the evaporator 40c to be evaporated. The return gas from the evaporator 40c (external refrigerant circuit 40) is sucked into the suction chamber 30, and the variable displacement compressor 10 of the present embodiment is discharged from the external refrigerant circuit 40O. A refrigerant circulation circuit is constructed. In addition, the rear housing 14 is provided with a capacity control valve 60 made of a solenoid valve.

In the rear housing 14 and the cylinder block 11, the 1st channel | path 61a which communicates the discharge chamber 31 and the said accommodation hole 11c (supply space S1) is formed. The displacement control valve 60 is formed in the middle of the first passage 61a. In addition, in the cylinder block 11 and the valve plate 13, a second passage 61b which communicates with the discharge space S2 and the suction chamber 30 and constitutes a part of the discharge passage is formed.

And when the rotating shaft 15 rotates by the drive source (not shown), the variable displacement compressor 10 of the said structure rotates the swash plate 24, and the piston 27 reciprocates in the cylinder bore 26, do. Then, the refrigerant gas circulating in the external refrigerant circuit 40 enters the cylinder bore 26 from the suction chamber 30 through the suction port 32 and the suction valve 36a and is compressed in the compression chamber 38. The compressed refrigerant gas is discharged to the discharge chamber 31 through the discharge port 34 and the discharge valve 28a. A part of the refrigerant gas discharged into the discharge chamber 31 is led to the external refrigerant circuit 40 (condenser 40a). In addition, part of the refrigerant gas is led to the supply space S1 via the first passage 61a as the control gas.

In addition, by adjusting the opening degree by the capacity control valve 60, the flow rate of the refrigerant gas led to the supply space S1 through the first passage 61a is adjusted. The refrigerant gas supplied to the supply space S1 is supplied to the in-axis supply passage 15a. And the refrigerant gas which passed the in-axis supply passage 15a is further led to the shaft seal chamber 20 through the derivation path 16c, and the shaft seal member 21 in the shaft seal chamber 20 is carried out. Is sprayed on. Then, the shaft seal base material 21 is lubricated by the lubricating oil contained in the refrigerant gas, and the lubrication state is maintained satisfactorily, while being cooled by the refrigerant gas. Thereafter, the refrigerant gas introduced into the shaft seal chamber 20 passes between the rotary support 22 and the front housing 12 and is supplied to the control pressure chamber C, so that the radial bearing 18 and the thrust bearing It is injected to 23. Then, both bearings 18 and 23 are lubricated by the lubricating oil contained in the refrigerant gas, the lubrication state is maintained well, and the refrigerant is cooled by the gas. Therefore, in this embodiment, the 1st channel | path 61a, the displacement control valve 60, the supply space S1, the in-axis supply channel | path 15a, the guideway 16c, and the shaft seal chamber 20 are, The discharge chamber 31 and the control pressure chamber C communicate with each other to form a supply passage for supplying the refrigerant gas of the discharge chamber 31 to the control pressure chamber C as the control gas.

In addition, the refrigerant gas in the control pressure chamber C is introduced into the in-axis discharge passage 15b from the introduction hole 16d and is led to the discharge space S2, and the suction chamber 30 is passed through the second passage 61b. Is discharged. Therefore, in this embodiment, the introduction hole 16d, the in-axis discharge passage 15b, the discharge space S2, and the second passage 61b communicate with the control pressure chamber C and the suction chamber 30. And a discharge passage for discharging the refrigerant gas in the control pressure chamber C into the suction chamber 30 as the control gas.

Then, the balance between the amount of refrigerant gas supplied to the control pressure chamber C through the supply passage and the amount of refrigerant gas discharged from the control pressure chamber C through the discharge passage is controlled to determine the pressure of the control pressure chamber C (control pressure chamber C ) Is pressured). When the pressure in the control pressure chamber C is changed, the pressure difference in the control pressure chamber C and the cylinder bore 26 through the piston 27 is changed, and the inclination angle of the swash plate 24 is changed. As a result, the stroke of the piston 27 (discharge capacity of the variable displacement compressor 10) is adjusted.

Next, the swash plate 24 will be described in detail. As shown in FIGS. 1-4, the insertion through-hole 24a penetrates the swash plate 24 in the thickness direction in the center part of the swash plate 24, and in the cross-section center part of the rear housing 14 side, The 1st protrusion part 41 is formed so that it may enclose the insertion through-hole 24a. In addition, the thickness direction of the swash plate 24 is a direction intersecting (orthogonal in this embodiment) with respect to the imaginary plane H passing through the front side end surface 24c (sliding surface 24b) of the swash plate 24. to be. As for the swash plate 24, the end surface 41a of the rear housing 14 side of the 1st protrusion part 41 abuts against the contact restricting member 44 (refer FIG. 1) formed in the outer peripheral surface of the rotating shaft 15, The inclination angle is controlled to be the minimum inclination angle.

In addition, as shown in FIG. 2 and FIG. 3, in the front end face 24c of the swash plate 24, a second cylindrical portion 45 having a semi-cylindrical shape protrudes toward the front housing 12 side. The second protrusion 45 is formed so as to surround almost half along the circumferential direction of the insertion through hole 24a. In the swash plate 24, the front end face of the swash plate 24 is formed of the front end face 24c and the end face 45a of the second protrusion 45. And as for the swash plate 24, the end surface 45a of the front housing 12 side of the 2nd protrusion part 45 abuts the rear end surface 22a (refer FIG. 1) of the said rotation support body 22, The inclination angle of the swash plate 24 is restricted to the maximum inclination angle. In this embodiment, the 2nd protrusion part 45 comprises the largest inclination-angle regulation part which regulates the inclination angle of the swash plate 24 to a maximum inclination angle.

Here, as shown in FIG. 1, in the control pressure chamber C, the end face on the rear side of the swash plate 24 (the end face 42c of the sliding plate 42 and the end face of the first protrusion 41) ( 41a)) and the end surface 11d of the cylinder block 11 which contact | connects the control pressure chamber C as the rear side area | region C1. Moreover, in the control pressure chamber C, the front end surface of the swash plate 24 (front end surface 24c of the swash plate 24 and the end surface 45a of the second protrusion 45) and the rotating support 22 Let front side area | region C2 be between the rear end surface 22a of (). That is, in the control pressure chamber C, when the swash plate 24 is the basis, it is the rotating support 22 side (front side) of the swash plate 24, and is formed between the swash plate 24 and the rotating support 22. Let the area be the front side area C2. In addition, in the control pressure chamber C, when the swash plate 24 is used as a reference, the anti-rotation support 22 side of the swash plate 24, that is, the rotation support 22 with the swash plate 24 interposed therebetween. Let the opposite side (rear side) area be rear side area | region C1.

In this case, the inlet hole 16d opens toward the front side region C2 even when the swash plate 24 is in any state of the minimum inclination angle or the maximum inclination angle. As shown in FIGS. 2-4, in the swash plate 24, the position which becomes the periphery of the said insertion through-hole 24a, ie, the rotation axis 15 inserted through the insertion-through hole 24a, Three communication paths 46 penetrating the swash plate 24 in the thickness direction are formed.

As shown in FIG. 4, in each communication path 46, the 1st opening 46a of the said rear side area | region C1 side is formed in the end surface 41a of the said 1st protrusion part 41. As shown in FIG. On the other hand, as shown in FIG. 2, the 2nd opening 46b of the said front side area | region C2 side of each communication path 46 is formed in the front side end surface 24c of the swash plate 24. As shown in FIG. Moreover, the 2nd opening 46b of each communication path 46 is located between the hinge mechanism 25 and the 2nd protrusion part 45, Specifically, it is located inside the 2nd protrusion part 45, and It is formed in the position surrounded by the 2 protrusion part 45. As shown in FIG. In addition, the fact that the 2nd opening 46b of the communication path 46 is located inside the 2nd protrusion part 45 is that the 2nd opening 46b opposes the inner peripheral surface of the 2nd protrusion part 45, and its inner peripheral surface. What is located between the peripheral surfaces of the rotating shaft 15 to be said.

And the communication path 46 passes through the swash plate 24 in the thickness direction, and communicates the rear side area | region C1 and the front side area | region C2 in the control pressure chamber C in the thickness direction. In addition, the communication path 46 forms a circular shape, and the path diameter thereof is equal to the diameter of the introduction hole 16d anywhere in the axial direction of the communication path 46. Moreover, when the end surface 45a of the 2nd protrusion part 45 abuts on the rear side end surface 22a of the rotation support body 22, and the inclination angle of the swash plate 24 became the maximum inclination angle, each 2nd opening 46b ) Is formed to be located immediately near the outer circumferential surface of the rotation shaft 15.

Next, the effect | action of the variable displacement compressor 10 of the said structure is demonstrated.

The refrigerant gas discharged into the discharge chamber 31 includes the first passage 61a, the capacity control valve 60, the supply space S1, the in-axis supply passage 15a, the draw passage 16c, and the shaft seal chamber ( It passes through 20 and is supplied toward the front side region C2 of the control pressure chamber C. Moreover, the broby gas leaks from the compression chamber 38 to the rear side region C1 of the control pressure chamber C between the piston 27 and the cylinder bore 26. The refrigerant gas in the control pressure chamber C moves toward the inlet hole 16d communicating with the suction chamber 30 from the pressure difference between the control pressure chamber C and the suction chamber 30.

In the front region C2 of the control pressure chamber C, the lubricating oil contained in the refrigerant gas is rotated by the centrifugal force by the rotation of the rotary shaft 15, the rotary support 22, and the swash plate 24. It is blown around and attached to the inner peripheral surface of the front housing 12 which forms the control pressure chamber C. As shown in FIG. Moreover, since the lubricating oil is contained also in the broby gas, much lubricating oil is disperse | distributed to the rear side area | region C1. And since the rear side area | region C1 is a high pressure area | region between the rear side area | region C1 and the front side area | region C2 rather than the front side area | region C2 which is closer to the introduction hole 16d, it is a rear side by a pressure difference. The refrigerant gas in the region C1 and the lubricating oil included in the refrigerant gas pass through the communication path 46 and are supplied to the circumference of the rotation shaft 15 in the front region C2. At this time, since the 2nd opening 46b is formed in the position between the 2nd protrusion part 45 and the rotating shaft 15, the lubricating oil contained in the refrigerant gas supplied to the front side area | region C2, and refrigerant gas. Stays around the rotation shaft 15 that is inside of the second protrusion 45 and is prevented from being blown away immediately around the rotation shaft 15 by the rotation of the rotation shaft 15.

And since the 2nd opening 46b of the communication path 46 is close to the circumference | surroundings of the rotating shaft 15, the lubricating oil contained in the refrigerant gas and refrigerant gas which passed through the communication path 46 rotates with the swash plate 24. It is introduced into the introduction hole 16d formed in the region sandwiched between the supports 22. The refrigerant gas and the lubricating oil contained in the refrigerant gas are introduced into the inlet hole 16d and then discharged into the suction chamber 30 through the in-axis discharge passage 15b and the discharge space S2. That is, by forming the communication path 46 in the swash plate 24, the refrigerant gas and the lubricating oil contained in the refrigerant gas are discharged to the suction chamber 30 in the rear region C1.

The graph shown in FIG. 5 shows the residual oil rate (%) which is the ratio of the lubricating oil flow rate with respect to the volume of the control pressure chamber C on the vertical axis, and the content rate which is the ratio of the lubricating oil flow rate with respect to the refrigerant gas circulating in the refrigerant circulation circuit on the horizontal axis ( %). The said residual oil ratio is set to the value which enables lubrication of each sliding part in control pressure chamber C, suppressing the heat_generation | fever by excess amount of lubricating oil in control pressure chamber C, In this embodiment, The residual oil ratio is preferably set to M%. Moreover, the said content rate is used for the component (condenser 40a, expansion valve 40b, and evaporator 40c) of the external refrigerant circuit 40 in the refrigerant | coolant circulation circuit containing the variable displacement compressor 10. As shown in FIG. In order to suppress the deterioration of the refrigerating ability as the lubricating oil is attached, it is set to a value that enables lubrication of each sliding portion in the control pressure chamber C of the variable displacement compressor 10 while being as small as possible. In this embodiment, it is preferable that the said content rate is set to N%. In the variable displacement compressor 10, when the content rate is N%, the residual oil rate of the control pressure chamber C becomes M%, and when the appropriate amount of lubricating oil is secured in the control pressure chamber C. to be.

And in the graph of FIG. 5, graph G1 shows the residual flow rate and content rate of the variable displacement compressor 10 in which the communication path 46 was formed in the swash plate 24 like the present embodiment. On the other hand, in the graph G2, as in the background art, the communication path 46 is not formed in the swash plate 24, and the refrigerant gas in the front region C2 passes through the in-axis discharge passage 15b from the inlet 16d. The residual flow rate and the content rate in the variable displacement compressor of the type discharged to the suction chamber 30 are shown. In addition, the graph G3 is a residual in the variable displacement compressor of the type in which the refrigerant gas is discharged to the suction chamber 30 from the discharge passage formed in the end face 11d facing the control pressure chamber C of the cylinder block 11. The flow rate and content rate are shown.

As shown in the graph of FIG. 5, in the variable displacement compressor 10 of the present embodiment, when the content of lubricating oil is N%, the residual oil ratio in the control pressure chamber C is at M%, and the control pressure chamber is used. It is shown in (C) that the appropriate amount of lubricating oil is secured. On the other hand, in the variable displacement compressor of the type shown in graph G2, when the content rate is N%, it turns out that the residual oil rate is very high. That is, graph G2 shows that the discharge of the lubricating oil from the control pressure chamber C is not performed well, and the lubricating oil remains in the control pressure chamber C more than necessary. On the other hand, in the variable displacement compressor of the type shown in graph G3, when the content rate is N%, it shows that the residual oil rate is very low. That is, the graph G3 shows that the lubricating oil is excessively discharged from the control pressure chamber C, so that the necessary lubricating oil does not remain in the control pressure chamber C.

According to the said embodiment, the following effects can be acquired.

(1) The inlet hole 16d opening toward the front side region C2 is formed in the rotation shaft 15 and the penetrating plate 24 passes around the insertion hole 24a of the swash plate 24. The communication path 46 was formed, and the rear side area | region C1 and the front side area | region C2 of the control pressure chamber C were communicated through the communication path 46. As shown in FIG. For this reason, the refrigerant gas of the rear side area | region C1, and the lubricating oil contained in refrigerant gas can be supplied to the front side area | region C2 via the communication path 46. As shown in FIG. Therefore, in the front side region C2, even if the lubricating oil contained in the refrigerant gas is blown around the rotary shaft 15 under the centrifugal force of the rotary shaft 15, the rear side region ( Lubricating oil can be supplied from C1) to the introduction hole 16d formed in the front region C2. For this reason, the lubricating oil can be discharged | emitted from the control pressure chamber C to the suction chamber 30, the lubricating oil in the control pressure chamber C can be prevented from becoming excess, and the quantity of the lubricating oil in the control pressure chamber C can be moderately maintained. . As a result, the excess amount of lubricating oil is heated in the control pressure chamber C by agitation by the swash plate 24 or the like, and the viscosity of the lubricating oil is lowered by the heating, thereby preventing the lubricating ability of the lubricating oil from being lowered. Can be.

(2) The communication path 46 penetrates the swash plate 24 in the thickness direction around the communication hole 24a in the swash plate 24. For this reason, like the background art, the refrigerant gas in the rear region C1 passes through the outer circumferential side of the swash plate 24 and is supplied to the front region C2 in the front region. The amount of the refrigerant gas supplied to (C2) and the lubricant oil contained in the refrigerant gas can be increased. In particular, since the swash plate 24 swings in the axial direction of the rotary shaft 15, the refrigerant gas and the lubricating oil contained in the refrigerant gas are difficult to move from the rear side region C1 to the front side region C2. For this reason, the structure which made it possible to supply the refrigerant gas and the lubricating oil contained in refrigerant gas from the rear side area | region C1 to the front side area | region C2 through the communication path 46 which penetrated the swash plate 24 is the rear. The supply of the refrigerant gas and the lubricant oil contained in the refrigerant gas from the side region C1 to the front side region C2 can be performed effectively.

(3) The second opening 46b of the communication path 46 is located between the second protrusion 45 and the hinge mechanism 25 that restrict the maximum inclination angle of the swash plate 24. For this reason, the refrigerant gas supplied to the front side area | region C2 from the 2nd opening 46b, and the lubricating oil contained in refrigerant gas are influenced by the centrifugal force by the 2nd protrusion part 45 and the hinge mechanism 25. As shown in FIG. It becomes difficult, and it can make it easy to introduce refrigerant gas and the lubricating oil contained in refrigerant gas into the introduction hole 16d.

(4) The second opening 46b of the communication path 46 is formed at a position surrounded by the second protrusion 45 and the rotation shaft 15 of the swash plate 24. This prevents the refrigerant gas supplied from the second opening 46b to the front side region C2 via the communication passage 46 and the lubricant oil contained in the refrigerant gas being blown away immediately around the second opening 46b. Thus, the lubricating oil can be kept around the rotating shaft 15. Therefore, compared with the case where the 2nd opening 46b of the communication path 46 is not formed in the position enclosed by the 2nd protrusion part 45 and the rotating shaft 15, the front side area | region (through the communication path 46) The refrigerant gas supplied to C2) and the lubricating oil contained in the refrigerant gas can be efficiently introduced into the introduction hole 16d.

(5) When the inclination angle of the swash plate 24 is the largest, the second opening 46b of the communication path 46 is closest to the introduction hole 16d. Moreover, the 2nd opening 46b of the communication path 46 is formed in the vicinity of the insertion passage hole 24a through which the rotating shaft 15 was inserted. For this reason, the refrigerant gas supplied to the front side area | region C2 from the rear side area | region C1, and the lubricating oil contained in refrigerant gas can be discharged | emitted quickly from the introduction hole 16d.

In addition, you may change each embodiment as follows.

○ As shown to Fig.6 (a) and FIG.6 (b), in the rotation axis 15, the axial direction of the center axis T of the rotation shaft 15 is located in the vicinity of the introduction hole 16d. It extends along and forms notch 16f which inclines toward the center axis T side toward the introduction hole 16d. In addition, you may provide the collision part 16g which collides refrigerant gas and the lubricating oil contained in refrigerant gas in the front housing 12 side rather than the introduction hole 16d. Moreover, the collection | recovery part extended in the vicinity of the introduction hole 16d to the position beyond the opening of the front side area | region C2 side of the introduction hole 16d, and extended so that it may cross | intersect the rotation direction of the rotation shaft 15, You may form (16h). If comprised in this way, the refrigerant gas supplied to the front side area | region C2 through the communication path 46, and moving toward the introduction hole 16d, and the lubricating oil contained in refrigerant gas are introduce | transduced by the notch 16f. It is guided toward the ball 16d and collides with the collision part 16g. And the refrigerant gas which collided with the collision part 16g, and the lubricating oil contained in refrigerant gas are introduce | transduced into the introduction hole 16d as it is. Moreover, when the rotating shaft 15 rotates, the refrigerant | coolant gas and the lubricating oil contained in refrigerant | coolant gas are scraped by the collection | recovery part 16h, and the lubricating oil contained in the scraped refrigerant gas and refrigerant gas is introduce | transduced into the inlet 16d. . Therefore, the discharge efficiency of the lubricating oil from the control pressure chamber C can be improved as compared with the case where the notch 16f, the collision part 16g, and the recovery part 16h are not formed near the introduction hole 16d. have.

As shown in FIG. 7, in the rotation shaft 15, the outer peripheral surface of the first rotation shaft 16 extends from the rear side region C1 to the front side region C2, and the rear side region C1. The communication groove 58 which is the groove | channel which communicates with the front side area | region C2 may be formed concave, and the communication path 58 may be comprised by the communication groove 58. FIG. In this case, the communication groove 58 communicates with the introduction hole 16d, and the communication groove 58 communicates with the introduction hole 16d. Therefore, the rear region C1 and the introduction hole 16d communicate with each other via the communication groove 58. In such a configuration, the refrigerant gas in the rear region C1 and the lubricant oil contained in the refrigerant gas can be directly supplied to the inlet hole 16d, and the lubricant oil is sucked more efficiently than the case where the communication groove 58 is not formed. The chamber 30 can be discharged.

○ As shown in FIG. 8, the through-hole 61c which penetrates the cylinder block 11 is formed in the cylinder block 11, and the control pressure chamber C and the displacement control valve are formed by the through-channel 61c. (60) is communicated. The discharge chamber 31 and the control pressure chamber C communicate with each other by the first passage 61a and the through passage 61c, and the supply passage is formed by the first passage 61a and the common passage 61c. In this case, the second rotary shaft 17 of the rotary shaft 15, the in-axis supply passage 15a, the lip seal 37, and the guide passage 16c are deleted.

○ As shown in FIG. 9, in the swash plate 24, a communication groove 59 which is a groove extending over the entire thickness direction of the swash plate 24 on the inner circumferential surface of the swash plate 24 forming the insertion through hole 24a. ) May be formed, and the communication groove 59 may communicate with the rear side region C1 and the front side region C2.

A sleeve may be formed between the inner circumferential surface of the swash plate 24 forming the insertion through hole 24a and the outer circumferential surface of the rotation shaft 15. Further, even in the state where the sleeve is formed, the swash plate 24 is directly supported by the rotation shaft 15 and leaks of the refrigerant gas from the rear side region C1 to the front side region C2 through the insertion through hole 24a. Is regulated.

○ The communication path 46 may be provided only one point or two points on the swash plate 24.

The communication path 46 may be formed in four or more points on the swash plate 24.

○ Although the path diameter of the communication path 46 was made the same as the path diameter of the introduction hole 16d, it is not limited to this, You may change suitably the path diameter of the communication path 46.

○ In addition to the communication path 46 formed in the swash plate 24, the outer peripheral surface of the first rotational shaft 16 extends from the rear side region C1 to the front side region C2, and the rear side region C1. The communication groove which is the groove which communicates with the front side area | region C2 may be formed concave. Alternatively, in addition to the communication path 46 formed in the swash plate 24, a communication groove which is a groove extending over the entire thickness direction of the swash plate 24 on the inner circumferential surface of the swash plate 24 forming the insertion passage hole 24a. 59 may be formed, and the rear side region C1 and the front side region C2 may communicate with the communication groove 59.

○ The swash plate 24 which recesses the communication groove which is the groove | channel which communicates the rear side area | region C1 and the front side area | region C2 in the outer peripheral surface of the 1st rotating shaft 16, and forms the insertion hole 24a. A communication groove 59 is formed on the inner circumferential surface of the swash plate 24 that extends over the entire thickness direction of the swash plate 24, and the rear side region C1 and the front side region C2 communicate with each other by the communication groove 59. You can also do it.

○ The second opening 46b of the communication path 46 is not a position surrounded by the second protrusion 45 and the rotation shaft 15, and is formed between the hinge mechanism 25 and the rotation shaft 15, for example. You may be.

BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional view which shows the variable displacement compressor of embodiment.

2 is a view showing a side facing a front side region of a swash plate;

3 is a side view showing a swash plate;

4 is a view showing a side facing a rear side region of a swash plate;

5 is a graph showing the residual oil content and the content rate of a variable displacement compressor.

Fig. 6A is a sectional view showing the vicinity of an introduction hole in another example of the rotational shaft, and Fig. 6B is a perspective view showing the introduction of an introduction hole in the other example of the rotation shaft.

7 is a cross-sectional view showing another example of a communication path.

8 is a longitudinal sectional view showing a variable displacement compressor showing another example of a supply passage.

9 is a diagram illustrating another example of a communication path.

10 is a longitudinal sectional view showing a compressor of the background art.

Explanation of symbols on the main parts of the drawings

C… Control pressure chamber, C1.. Rear region, C2... Front side area, S1... Supply space, S2… Discharge space constituting the discharge passage, 10... Variable displacement compressor, 11... Cylinder block constituting the housing, 12... Front housing constituting the housing; Rear housing constituting the housing; Axis of rotation, 15a... In-axis supply passage constituting the supply passage, 15b... In-axis discharge passage constituting the discharge passage, 16c... Derivation constituting the supply passage, 16d... Introduction hole constituting discharge passage, 20... Axial seal chamber constituting the supply passage, 22... Rotary support, 24... Saphan, 25... Hinge mechanism, 24a... Insertion through hole, 30.. Suction chamber as suction pressure region, 31... Discharge chamber as discharge pressure region, 45... 2nd protrusion part as a maximum inclination-angle restricting part, 46. Communication path, 46b... Second opening as opening to front side area, 61a... First passage constituting the supply passage, 58,59... Communication grooves as communication paths, 60... Capacity control valve constituting the supply passageway, 61b... Second passage constituting the discharge passage, 61c... Through passages that constitute the supply passages.

Claims (10)

The first end side of the rotary shaft is rotatably supported on the front side of the housing, and the second end side of the rotary shaft is rotatably supported on the rear side, and the control pressure chamber in the housing is connected to the rotary support fixed to the rotary shaft and the rotary shaft. Directly supported, the swash plate connected to the rotating support via a hinge mechanism and integrally rotated with the rotating shaft is accommodated with a variable inclination angle, and controls the refrigerant gas in the discharge pressure region through a supply passage communicating the discharge pressure region with the control pressure chamber. A variable in which the inclination angle of the swash plate is changed and the discharge capacity is controlled by supplying the pressure chamber and discharging the refrigerant gas in the control pressure chamber to the suction pressure region through the discharge passage communicating the suction pressure region and the control pressure chamber and manipulating the inside of the control pressure chamber. As a capacitive compressor, The in-axis discharge passage which forms a part of the discharge passage is formed in the rotating shaft, and is opened toward the front side region between the swash plate and the rotary support in the control pressure chamber, and further opens in the shaft. An introduction hole communicating with the passage is formed, and at least one of the swash plate and the rotating shaft has a communication path communicating with the front side region and the rear side region of the anti-rotation support side of the swash plate in the control pressure chamber. Capacity compressors. The method of claim 1, The communication path is a variable displacement compressor formed by penetrating the swash plate in the thickness direction. The method according to claim 1 or 2, The swash plate is formed with an insertion passage hole through which the rotating shaft is inserted, and the communication passage is formed by a groove extending over the entire thickness direction of the swash plate on the inner circumferential surface of the swash plate forming the insertion passage hole. . The method according to claim 1 or 2, The communication path is concave in the circumferential surface of the rotating shaft, and is formed by a groove communicating with the introduction hole. The method according to claim 1 or 2, The swash plate protrudes from the maximum inclination angle regulating portion that restrains the maximum inclination angle of the swash plate by contacting the rotatable support, and an opening to the front side area in the communication path is formed between the maximum inclination angle regulating portion and the hinge mechanism. Variable displacement compressors. The method of claim 5, wherein An opening to the front side region of the communication path is located between the maximum inclination angle restricting portion and the rotating shaft. The method of claim 3, wherein The communication path is concave in the circumferential surface of the rotating shaft, and is formed by a groove communicating with the introduction hole. The method of claim 3, wherein The swash plate protrudes from the maximum inclination angle regulating portion that restrains the maximum inclination angle of the swash plate by contacting the rotatable support, and an opening to the front side area in the communication path is formed between the maximum inclination angle regulating portion and the hinge mechanism. Variable displacement compressors. The method of claim 4, wherein The swash plate protrudes from the maximum inclination angle regulating portion that restrains the maximum inclination angle of the swash plate by contacting the rotatable support, and an opening to the front side area in the communication path is formed between the maximum inclination angle regulating portion and the hinge mechanism. Variable displacement compressors. The method of claim 7, wherein The swash plate protrudes from the maximum inclination angle regulating portion that restrains the maximum inclination angle of the swash plate by contacting the rotatable support, and an opening to the front side area in the communication path is formed between the maximum inclination angle regulating portion and the hinge mechanism. Variable displacement compressors.

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