JP2008144631A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor capable of securing appropriate quantity of lubricating oil in a control pressure chamber. <P>SOLUTION: In the variable displacement compressor 10, an in-shaft delivery passage 15b constructing a part of a delivery passage is formed in the rotary shaft 15, and an introduction hole 16 opening toward a front side area C2 in the control pressure chamber C and communicating to the in-shaft delivery passage 15b is formed. A communication path 46 establishing communication between a rear side area C1 and the front side area C2 in the control pressure chamber C having a boarder on a swash plate 24 is formed on the swash plate 24. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a variable displacement compressor in which the discharge capacity is controlled by changing the tilt angle of a swash plate by adjusting the pressure in a control pressure chamber.

  An example of this type of variable capacity compressor (hereinafter simply referred to as a compressor) is disclosed in Patent Document 1. As shown in FIG. 10, a crank chamber 80 is defined in the housing of the compressor of Patent Document 1, and a shaft 81 is rotatably supported. In the crank chamber 80, a rotor 92 is fixed to the shaft 81 and a rotary swash plate 82 is supported with a variable tilt angle. A plurality of pistons 83 are moored to the rotary swash plate 82 via shoes 84. The piston 83 is inserted into a cylinder bore 94 in the housing so as to reciprocate.

  Further, a discharge chamber 85 and a 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 a first passage 87 and a second passage 88, and the suction chamber 86 and the crank chamber 80 communicate with each other through an extraction passage. The bleed passage includes an axial passage 89 provided 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 89. A third passage 91 communicating with the suction chamber 86 is formed. 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 via the first passage 87 and the second passage 88. Further, the refrigerant gas in 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 adjusted, and the inclination angle of the rotary swash plate 82 is changed by the pressure adjustment to adjust the discharge capacity of the compressor.

In addition, the refrigerant gas supplied from the discharge chamber 85 to the crank chamber 80 and the blow-by gas leaked from between the cylinder bore 94 and the piston 83 into the crank chamber 80 contain lubricating oil. When the refrigerant gas and the blow-by gas move in the crank chamber 80 toward the communication hole 90, the lubricating oil contained in the refrigerant gas and the blow-by gas is moved to each sliding portion (for example, the rotary swash plate 82) in the crank chamber 80. And the sliding portion of the shoe 84). The lubricant contained in the refrigerant gas and the blow-by gas moving in the crank chamber 80 is separated from each gas by the centrifugal force of each rotating member (rotating swash plate 82, rotor 92, etc.) due to the rotation of the shaft 81, and the shaft. Dispersed around 81 and the inner wall surface of the crank chamber 80. The dispersed lubricating oil is supplied to each sliding portion in the crank chamber 80. Therefore, lubrication of each sliding part is achieved by the lubricating oil.
Japanese Patent Laid-Open No. 2004-28090

  By the way, the lubricating oil contained in the refrigerant gas is blown off around the shaft 81 due to the centrifugal force generated by the rotation of the shaft 81, and the surroundings of the communication hole 90 are in a state where the lubricating oil is scarce. For this reason, the lubricating oil is difficult to be discharged to the suction chamber 86 through the communication hole 90, the axial passage 89, and the third passage 91, resulting in an atmosphere in which an excessive amount of lubricating oil exists in the crank chamber 80. . When an excessive amount of lubricating oil is present in the crank chamber 80, the lubricating oil is heated by being swung by the rotary swash plate 82 and the rotor 92, and the generated heat lowers the viscosity of the lubricating oil. The lubrication capacity will be reduced.

  Here, the inlet of the extraction passage for discharging the refrigerant gas is formed not on the rotating body (shaft 81) but on the end surface of the non-rotating body, for example, the housing (cylinder block) forming the crank chamber 80, and the lubricating oil is subjected to centrifugal force. A configuration in which the lubricating oil is discharged to the suction chamber 86 without being affected by the influence of the above is conceivable. However, in this configuration, the lubricating oil is excessively discharged into the suction chamber 86, and the amount of lubricating oil in the crank chamber 80 is reduced, and the sliding portion is poorly lubricated.

  The present invention has been made in view of the above-described conventional problems, and an object of the present invention is to provide a variable displacement compressor that can secure an appropriate amount of lubricating oil in a control pressure chamber.

  In order to solve the above problems, the invention according to claim 1 is characterized in that the first end side of the rotating shaft is rotatably supported on the front side of the housing and the second end side of the rotating shaft is rotated on the rear side. The control pressure chamber in the housing is supported by a rotation support member fixed to the rotation shaft, and is directly supported by the rotation shaft, and is connected to the rotation support member through a hinge mechanism to be connected to the rotation shaft. A swash plate that rotates integrally is accommodated in a variable tilt angle, and supplies the refrigerant gas in the discharge pressure region to the control pressure chamber via a supply passage that communicates the discharge pressure region and the control pressure chamber. Variable displacement type in which the discharge angle is controlled by changing the inclination angle of the swash plate by discharging the refrigerant gas in the control pressure chamber to the suction pressure region and adjusting the pressure in the control pressure chamber through a discharge passage communicating with the chamber A compressor, wherein the rotary shaft An in-shaft discharge passage that forms a part of the outlet passage is formed, and on the rotation support side of the swash plate in the control pressure chamber, toward a front side region between the swash plate and the rotation support body An introduction hole that is open and communicates with the in-shaft discharge passage is formed, and at least one of the swash plate and the rotation shaft has the front region and the counter-rotation of the swash plate out of the control pressure chamber. A communication path communicating with the rear side region on the support side is formed.

  According to this configuration, the refrigerant gas in the rear region in the control pressure chamber and the lubricating oil contained in the refrigerant gas are supplied to the front region through the communication path. That is, the refrigerant gas in the rear side region and the lubricant contained in the refrigerant gas are not supplied to the front side region around the outer periphery of the swash plate, but are connected to at least one of the swash plate and the rotating shaft. It is supplied from the rear side region to the front side region via the passage. For this reason, compared with the case where a communicating path is not formed, the amount of lubricating oil around an introduction hole can be increased. Therefore, the amount of lubricating oil discharged from the introduction hole to the suction pressure region can be increased as compared with the case where the communication path is not formed, and a situation where an excessive amount of lubricating oil exists in the control pressure chamber is avoided. Can do. As a result, an appropriate amount of lubricating oil can be secured in the control pressure chamber.

  The communication path may be formed through the swash plate in the thickness direction. According to this configuration, for example, the refrigerant gas and the refrigerant gas in the front side region differ from the case where the refrigerant gas in the rear side region and the lubricant contained in the refrigerant gas are supplied to the front side region through the outer peripheral side of the swash plate. Can be supplied reliably and promptly.

  Further, the swash plate is formed with an insertion hole through which the rotating shaft is inserted, and the communication path is a groove extending over the entire thickness direction of the swash plate on the inner peripheral surface of the swash plate forming the insertion hole. The communication path may be recessed in the peripheral surface of the rotating shaft, and may be formed by a groove communicating with the introduction hole. Even with this configuration, the refrigerant gas in the rear side region in the control pressure chamber and the lubricating oil contained in the refrigerant gas can be supplied to the front side region.

  Further, the swash plate is provided with a maximum inclination restriction portion that restricts the maximum inclination angle of the swash plate by coming into contact with the rotary support, and an opening to a front side region in the communication path is formed with the maximum inclination restriction portion. It may be located between the hinge mechanisms. In particular, it is preferable that an opening to the front side region in the communication path is located between the maximum inclination angle restricting portion and the rotation shaft.

  According to this configuration, the refrigerant gas supplied to the front side region from the opening to the front side region in the communication path and the lubricating oil contained in the refrigerant gas are affected by the centrifugal force generated by the maximum inclination restriction unit and the hinge mechanism. Thus, the refrigerant gas and the lubricating oil contained in the refrigerant gas can be retained around the rotating shaft. Therefore, for example, compared to the case where the opening to the front side region in the communication path is formed near the outer periphery in the radial direction of the swash plate rather than between the maximum inclination angle restricting portion and the hinge mechanism, suction is performed from the introduction hole. The amount of lubricating oil discharged to the pressure region can be increased.

  According to the present invention, an appropriate amount of lubricating oil can be secured in the control pressure chamber.

  Hereinafter, an embodiment of a variable capacity compressor embodying the present invention will be described with reference to FIGS. In the following description, “front” and “rear” of the variable displacement compressor correspond to front and rear in arrows Y extending in the front-rear direction of FIG.

  FIG. 1 shows a longitudinal sectional view of a variable capacity compressor 10 of the present embodiment. The housing of the variable displacement compressor 10 includes a cylinder block 11, a front housing 12 joined and fixed to the front end thereof, and a rear housing 14 joined and fixed to the rear end of the cylinder block 11. 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 to the rear housing 14 side. An annuloplasty plate 28 and a retainer 33 are attached. A control pressure chamber C is defined between the cylinder block 11 and the front housing 12, and a rotary shaft 15 is rotatable in the cylinder block 11 and the front housing 12 so as to penetrate the control pressure chamber C. It is supported.

  The rotary shaft 15 has a hollow cylindrical shape in which the front and rear end surfaces on the front housing 12 side and the rear housing 14 side are opened inside the first rotary shaft 16 having a hollow cylindrical shape with an open rear end surface on the rear housing 14 side. The second rotating shaft 17 is press-fitted (inserted) to form a double tube. An O-ring O is interposed between the inner peripheral surface of the first rotating shaft 16 and the outer peripheral surface of the second rotating shaft 17. The rotation shaft 15 is formed with an in-axis supply passage 15 a extending along the axial direction of the central axis T of the rotation shaft 15. Further, in the rotating shaft 15, an in-shaft discharge passage 15 b is formed between the inner peripheral surface of the first rotating shaft 16 and the outer peripheral surface of the second rotating shaft 17.

  The first rotating shaft 16 of the rotating shaft 15 is formed with a lead-out path 16 c that communicates with the in-axis supply path 15 a and opens toward the front housing 12. Further, in the rotating shaft 15, the in-axis supply passage 15 a is opened at the rear end surface of the rotating shaft 15. In the first rotary shaft 16 of the rotary shaft 15, an introduction hole 16 d for communicating the in-shaft discharge passage 15 b and the control pressure chamber C is formed at a position facing the control pressure chamber C. Further, in the rotary shaft 15, the in-shaft discharge passage 15 b is opened at the rear end surface of the rotary shaft 15.

  In the rotary shaft 15 configured as described above, the front end side which is the first end portion side of the rotary shaft 15 is rotatably supported by the front housing 12. In the front housing 12, a shaft seal chamber 20 is formed between the peripheral surface of the rotating shaft 15 and the inner peripheral surface of the front housing 12 facing the peripheral surface. In the shaft seal chamber 20, a shaft seal member 21 that seals between the peripheral surface of the rotary shaft 15 (first rotary shaft 16 a) and the inner peripheral surface of the shaft seal chamber 20 is provided. The shaft seal member 21 suppresses leakage of the refrigerant gas from the control pressure chamber C along the peripheral surface of the rotary shaft 15 to the outside of the variable displacement compressor 10.

  The rear end side that is the second end portion side of the rotary shaft 15 is inserted into a shaft hole 11 b formed in the cylinder block 11 and is rotatably supported by the shaft hole 11 b by a bearing 19. Therefore, the rotary shaft 15 is supported such that the first end side is rotatable on the front (front housing 12) side of the housing and the second end side is rotatably supported on the rear side (rear housing 14 side) of the housing. Yes.

  Further, an accommodation hole 11 c communicating with the shaft hole 11 b is defined between the cylinder block 11 and the valve plate 13. The rear end of the second rotating shaft 17 of the rotating shaft 15 protrudes into the receiving hole 11c, and the in-shaft supply passage 15a communicates with the receiving hole 11c. In the accommodation hole 11c, a lip seal 37 is interposed between the outer peripheral surface of the second rotating shaft 17 and the peripheral surface of the accommodation hole 11c. The lip seal 37 seals the in-shaft supply passage 15a and the in-shaft discharge passage 15b at the rear end of the rotary shaft 15, and supplies the interior of the accommodation hole 11c to the in-shaft supply passage 15a. And a discharge space S2 communicating with the in-shaft discharge passage 15b.

  In the control pressure chamber C, a rotary support 22 is fixed to the rotary shaft 15, and the rotary support 22 is fixed so as to rotate integrally with the rotary shaft 15. The rotary support 22 is rotatably supported on the front housing 12 by a radial bearing 18. That is, the rotary shaft 15 is rotatably supported by the front housing 12 by the radial bearing 18 via the rotary support 22. A thrust bearing 23 is provided between the rotary support 22 and the inner wall surface of the front housing 12. Further, a swash plate 24 having a substantially disc shape is accommodated in the control pressure chamber C. A cylindrical first protrusion 41 is provided on the swash plate 24 on the rear housing 14 side.

  Further, an annular sliding plate 42 is disposed on the outer peripheral side of the first projecting portion 41 in a state where the first projecting portion 41 is inserted into a support hole 42a formed through the central portion thereof. ing. Between the first protrusion 41 and the inner peripheral surface of the support hole 42a of the sliding plate 42, and between the outer peripheral portion of the swash plate 24 and the sliding plate 42 facing the outer peripheral portion, bearings 43 are respectively provided. Is intervened. An end face on the rear side of the swash plate 24 is formed by an end face 42c on the rear housing 14 side of the sliding plate 42 and an end face 41a on the rear housing 14 side of the first protrusion 41. In the center of the swash plate 24, an insertion hole 24a is formed through the swash plate 24, and the rotary shaft 15 is inserted through the insertion hole 24a.

  A hinge mechanism 25 is interposed between the rotary support 22 and the swash plate 24. The swash plate 24 can be rotated synchronously with the rotary shaft 15 and the rotary support 22 by the hinge connection with the rotary support 22 via the hinge mechanism 25 and the direct support of the rotary shaft 15 via the insertion hole 24a. In addition, the tilt angle can be changed with respect to the rotary shaft 15 while being slid in the axial direction along the central axis T of the rotary shaft 15. That is, the swash plate 24 can change its inclination within a predetermined angle range between the maximum inclination angle and the minimum inclination angle with respect to a plane perpendicular to the axial direction along the central axis T of the rotation shaft 15. It has become. The maximum tilt angle is the tilt angle of the swash plate 24 when the discharge capacity in the variable displacement compressor 10 is maximum, and the minimum tilt angle is the tilt angle of the swash plate 24 when the discharge capacity is minimum.

  A plurality of cylinder bores 26 are formed in the cylinder block 11 so as to penetrate the rotating shaft 15 at equal angular intervals. A single-headed piston 27 is accommodated in the cylinder bore 26 so as to be capable of reciprocating in the axial direction of the central axis T of the rotary shaft 15. The opening of the cylinder bore 26 is closed by the valve plate 13 and the piston 27, and a compression chamber 38 whose volume changes according to the movement of the piston 27 is defined in the cylinder bore 26. The piston 27 is moored to the outer peripheral portion of the swash plate 24 and the sliding plate 42 through a pair of shoes 29 disposed on the front housing 12 side of the swash plate 24 and the rear housing 14 side of the sliding plate 42. . That is, the shoe 29 is accommodated between the sliding surface 24b provided on the outer peripheral portion of the front side end surface 24c of the swash plate 24, the end surface 42c of the sliding plate 42, and the inner surface of the shoe accommodating portion 27a of the piston 27. Yes. The rotational movement of the swash plate 24 is converted into the back-and-forth reciprocating movement of the piston 27 through the shoe 29 by sliding contact with the sliding surface 24b of the shoe 29 and the inner surface of the shoe housing portion 27a. .

  The rear housing 14 is formed with a suction chamber 30 as a suction pressure region and a discharge chamber 31 as a discharge pressure region facing the valve plate 13. Specifically, the discharge chamber 31 is provided at the center of the rear housing 14, and the suction chamber 30 is provided on the outer peripheral side of the discharge chamber 31 in an annular shape so as to surround the discharge chamber 31. In the valve plate 13, a suction port 32 is formed radially outward of the valve plate 13 and a discharge port 34 is formed radially inward of the valve plate 13 at a position facing each cylinder bore 26. . The suction valve forming plate 36 is formed with a suction valve 36 a that opens and closes the suction port 32 at a position corresponding to the suction port 32. Further, the suction valve forming plate 36 is formed with a discharge hole 36 b at a position corresponding to the discharge port 34. The discharge valve forming plate 28 is formed with a discharge valve 28 a that opens and closes the discharge port 34 at a position corresponding to the discharge port 34. The opening position of the discharge valve 28a is regulated by the retainer 33.

  The high-pressure refrigerant gas discharged into the discharge chamber 31 is led out to the external refrigerant circuit 40. The refrigerant gas led out to the external refrigerant circuit 40 is cooled by 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 40 c (external refrigerant circuit 40) is sucked into the suction chamber 30, and the variable capacity compressor 10 of this embodiment is connected to the external refrigerant circuit 40 with a refrigerant circulation circuit. Is configured. The rear housing 14 is assembled with a capacity control valve 60 made of an electromagnetic valve.

  The rear housing 14 and the cylinder block 11 are formed with a first passage 61a that communicates the discharge chamber 31 with the accommodation hole 11c (supply space S1). The capacity control valve 60 is provided in the middle of the first passage 61a. The cylinder block 11 and the valve plate 13 are formed with a second passage 61b that communicates the discharge space S2 and the suction chamber 30 and constitutes a part of the discharge passage.

  In the variable capacity compressor 10 having the above-described configuration, when the rotary shaft 15 is rotated by a drive source (not shown), the swash plate 24 is rotated so that the piston 27 reciprocates in the cylinder bore 26. 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 36 a and is compressed in the compression chamber 38. The compressed refrigerant gas is discharged into the discharge chamber 31 through the discharge port 34 and the discharge valve 28a. A part of the refrigerant gas discharged to the discharge chamber 31 is led to the external refrigerant circuit 40 (condenser 40a). A part of the refrigerant gas is led out to the supply space S1 as the control gas through the first passage 61a.

  The flow rate of the refrigerant gas led out to the supply space S1 through the first passage 61a is adjusted by adjusting the opening degree by the capacity control valve 60. The refrigerant gas supplied to the supply space S1 is supplied to the in-shaft supply passage 15a. The refrigerant gas that has passed through the in-shaft supply passage 15a further passes through the lead-out path 16c, is led out to the shaft seal chamber 20, and is blown onto the shaft seal member 21 in the shaft seal chamber 20. Then, the shaft seal member 21 is lubricated by the lubricating oil contained in the refrigerant gas, the lubrication state is maintained well, and the shaft seal member 21 is 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 sprayed to the radial bearing 18 and the thrust bearing 23 when supplied to the control pressure chamber C. . Then, both the bearings 18 and 23 are lubricated by the lubricating oil contained in the refrigerant gas, the lubrication state is maintained well, and the bearing 18 is cooled by the refrigerant gas. Therefore, in the present embodiment, the first passage 61a, the capacity control valve 60, the supply space S1, the in-shaft supply passage 15a, the outlet passage 16c, and the shaft seal chamber 20 make the discharge chamber 31 and the control pressure chamber C communicate with each other. A supply passage for supplying the refrigerant gas in the discharge chamber 31 to the control pressure chamber C as a control gas is configured.

  Further, the refrigerant gas in the control pressure chamber C is introduced from the introduction hole 16d into the in-shaft discharge passage 15b, further led out to the discharge space S2, and discharged to the suction chamber 30 through the second passage 61b. Therefore, in the present embodiment, the introduction hole 16d, the in-shaft discharge passage 15b, the discharge space S2, and the second passage 61b communicate the control pressure chamber C and the suction chamber 30 and control the refrigerant gas in the control pressure chamber C. A discharge passage for discharging the gas to the suction chamber 30 is configured.

  The balance between the refrigerant gas supply amount to the control pressure chamber C via the supply passage and the refrigerant gas discharge amount from the control pressure chamber C via the discharge passage is controlled to determine the pressure of the control pressure chamber C. (Control pressure chamber C is regulated). When the pressure in the control pressure chamber C is changed, the differential pressure between the control pressure chamber C and the cylinder bore 26 via 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 (the 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 to 4, the insertion hole 24 a is formed in the center portion of the swash plate 24 so as to penetrate the swash plate 24 in the thickness direction, and the end portion on the rear housing 14 side has the first hole. One protruding portion 41 is provided so as to surround the insertion hole 24a. The thickness direction of the swash plate 24 is a direction intersecting (orthogonal in the present embodiment) with a virtual plane H passing through the front side end surface 24c (sliding surface 24b) of the swash plate 24. The inclination angle of the swash plate 24 is minimized when the end surface 41a of the first projecting portion 41 on the rear housing 14 side contacts an abutment regulating member 44 (see FIG. 1) provided on the outer circumferential surface of the rotary shaft 15. It is regulated by the tilt angle.

  As shown in FIGS. 2 and 3, a second projecting portion 45 having a semi-cylindrical shape is provided on the front end face 24 c of the swash plate 24 so as to project toward the front housing 12. The second projecting portion 45 is formed so as to surround almost half of the insertion hole 24a along the circumferential direction. In the swash plate 24, the front-side end surface of the swash plate 24 is formed by the front-side end surface 24 c and the end surface 45 a of the second protrusion 45. The swash plate 24 has an inclination angle of the swash plate 24 as a result of the end surface 45a on the front housing 12 side of the second projecting portion 45 coming into contact with the rear end surface 22a (see FIG. 1) of the rotary support 22. The maximum tilt angle is regulated. In the present embodiment, the second projecting portion 45 constitutes a maximum inclination restriction portion that restricts the inclination angle of the swash plate 24 to the maximum inclination angle.

  Here, as shown in FIG. 1, in the control pressure chamber C, the rear side end face of the swash plate 24 (the end face 42 c of the sliding plate 42 and the end face 41 a of the first protrusion 41) and the control pressure chamber C are faced. A region between the end surface 11d of the cylinder block 11 to be performed is a rear side region C1. Further, in the control pressure chamber C, there is a gap between the front side end surface of the swash plate 24 (the front side end surface 24c of the swash plate 24 and the end surface 45a of the second protrusion 45) and the rear side end surface 22a of the rotation support 22. Let it be a front side region C2. That is, in the control pressure chamber C, when the swash plate 24 is used as a reference, the region between the swash plate 24 and the rotary support 22 is the front side. Region C2. Further, in the control pressure chamber C, when the swash plate 24 is used as a reference, an area on the counter-rotating support 22 side of the swash plate 24, that is, on the opposite side (rear side) of the rotating support 22 across the swash plate 24. Is a rear side region C1.

  In this case, the introduction hole 16d opens toward the front side region C2 regardless of whether the swash plate 24 is in the minimum inclination angle or the maximum inclination angle. As shown in FIGS. 2 to 4, in the swash plate 24, the swash plate 24 is arranged in the thickness direction at a position around the insertion hole 24 a, that is, around the rotary shaft 15 inserted through the insertion hole 24 a. Three communicating passages 46 are formed therethrough.

  As shown in FIG. 4, in each communication passage 46, the first opening 46 a on the rear side region C <b> 1 side is formed on the end surface 41 a of the first projecting portion 41. On the other hand, as shown in FIG. 2, the second opening 46 b on the front side region C <b> 2 side of each communication passage 46 is formed in the front side end surface 24 c of the swash plate 24. Further, the second opening 46b of each communication passage 46 is located between the hinge mechanism 25 and the second projecting portion 45, more specifically, located inside the second projecting portion 45, and the second projecting portion It is formed at a position surrounded by 45. Note that the second opening 46b of the communication path 46 is located inside the second projecting portion 45. The second opening 46b faces the inner peripheral surface of the second projecting portion 45 and the rotary shaft 15 facing the inner peripheral surface. It is located between the peripheral surface of

  The communication passage 46 communicates the rear side region C1 and the front side region C2 in the control pressure chamber C through the swash plate 24 in the thickness direction. Further, the communication passage 46 has a circular hole shape, and the diameter of the passage is the same as the diameter of the introduction hole 16 d in any axial direction of the communication passage 46. Further, when the end surface 45 a of the second projecting portion 45 abuts on the rear side end surface 22 a of the rotation support 22 and the inclination angle of the swash plate 24 reaches the maximum inclination angle, each second opening 46 b is formed on the outer peripheral surface of the rotation shaft 15. It is formed to be located in the immediate vicinity.

Next, the operation of the variable displacement compressor 10 having the above configuration will be described.
Now, the refrigerant gas discharged into the discharge chamber 31 passes through the first passage 61a, the capacity control valve 60, the supply space S1, the in-shaft supply passage 15a, the outlet passage 16c, and the shaft seal chamber 20, and the control pressure chamber C. To the front side region C2. Further, blow-by gas leaks from the compression chamber 38 to the rear side region C1 of the control pressure chamber C through the gap between the piston 27 and the cylinder bore 26. The refrigerant gas in the control pressure chamber C moves from the pressure difference between the control pressure chamber C and the suction chamber 30 toward the introduction hole 16 d communicating with the suction chamber 30.

  In the front side region C2 of the control pressure chamber C, the lubricating oil contained in the refrigerant gas is blown out around the rotation shaft 15 by the centrifugal force generated by the rotation of the rotation shaft 15, the rotation support 22 and the swash plate 24, and the control pressure is reduced. It adheres to the inner peripheral surface of the front housing 12 forming the chamber C. Further, since the blow-by gas also contains lubricating oil, a large amount of lubricating oil is dispersed in the rear side region C1. Since the rear side region C1 is a higher pressure region between the rear side region C1 and the front side region C2 than the front side region C2 close to the introduction hole 16d, the refrigerant gas and the refrigerant gas in the rear side region C1 are caused by the pressure difference. Is supplied to the periphery of the rotary shaft 15 in the front region C2. At this time, since the second opening 46b is formed at a position between the second projecting portion 45 and the rotary shaft 15, the refrigerant gas supplied to the front side region C2 and the lubricating oil contained in the refrigerant gas are The rotation stays around the rotation shaft 15 inside the second protrusion 45 and is prevented from being blown immediately around the rotation shaft 15 by the rotation of the rotation shaft 15.

  Since the second opening 46 b of the communication path 46 is near the periphery of the rotating shaft 15, the refrigerant gas that has passed through the communication path 46 and the lubricating oil contained in the refrigerant gas are sandwiched between the swash plate 24 and the rotary support 22. It is introduced into the introduction hole 16d provided in the region. The refrigerant gas and the lubricating oil contained in the refrigerant gas are introduced into the introduction hole 16d and then discharged to the suction chamber 30 through the in-shaft 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 from the rear side region C1 to the suction chamber 30.

  In the graph shown in FIG. 6, the vertical axis indicates the residual oil ratio (%), which is the ratio of the lubricating oil amount to the volume of the control pressure chamber C, and the horizontal axis indicates the ratio of the lubricating oil amount to the refrigerant gas circulating in the refrigerant circulation circuit. The oil content (%) is shown. The residual oil rate is set to a value that enables lubrication of each sliding portion in the control pressure chamber C while suppressing heat generation due to an excessive amount of lubricating oil in the control pressure chamber C. The residual oil ratio is preferably set to M%. In addition, the oil content is determined based on the refrigeration capacity due to the lubricant oil adhering to the components (condenser 40a, expansion valve 40b, and evaporator 40c) of the external refrigerant circuit 40 in the refrigerant circuit including the variable displacement compressor 10. 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 reducing as much as possible. In the present embodiment, the oil content is preferably set to N%. In the variable capacity compressor 10, when the oil content is N%, the residual oil rate in the control pressure chamber C is M%, but the appropriate amount of lubricating oil is secured in the control pressure chamber C. It is.

  In the graph of FIG. 6, a graph G <b> 1 shows the residual oil ratio and oil content of the variable capacity compressor 10 in which the communication path 46 is formed in the swash plate 24 as in the present embodiment. On the other hand, in the graph G2, as in the background art, the communication passage 46 is not formed in the swash plate 24, and the refrigerant gas in the front side region C2 passes through the in-shaft discharge passage 15b from the introduction hole 16d and is discharged into the suction chamber 30. The residual oil ratio and oil content in a variable displacement compressor of the type to be used are shown. Further, the graph G3 shows a residual oil ratio and an oil content ratio in a variable displacement compressor of a type in which the refrigerant gas is discharged from the discharge passage formed in the end surface 11d facing the control pressure chamber C of the cylinder block 11 into the suction chamber 30. Indicates.

  As shown in the graph of FIG. 6, in the variable displacement compressor 10 of the present embodiment, when the oil content of the lubricating oil is N%, the residual oil ratio in the control pressure chamber C is M%, and the control pressure chamber C shows that an appropriate amount of lubricating oil is secured. On the other hand, in the variable displacement compressor of the type shown in the graph G2, when the oil content is N%, the residual oil rate is shown to be very high. That is, the graph G2 shows that the lubricating oil is not discharged well from the control pressure chamber C, 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, it is shown that the residual oil ratio is very low when the oil content is N%. That is, the graph G3 shows that the lubricating oil is excessively discharged from the control pressure chamber C, and the necessary lubricating oil does not remain in the control pressure chamber C.

According to the above embodiment, the following effects can be obtained.
(1) An introduction hole 16d that opens toward the front region C2 is provided in the rotary shaft 15, and a communication passage 46 that penetrates the swash plate 24 is formed around the insertion hole 24a of the swash plate 24. 46, the rear side region C1 and the front side region C2 of the control pressure chamber C are communicated with each other. Therefore, the refrigerant gas in the rear side region C1 and the lubricating oil contained in the refrigerant gas can be supplied to the front side region C2 via the communication path 46. Therefore, in the front side region C2, even if the lubricating oil contained in the refrigerant gas receives the centrifugal force of the rotating shaft 15 and is blown off around the rotating shaft 15, the communication path 46 causes the rear side region C1 to move to the front side region C2. Lubricating oil can be supplied to the introduction hole 16d provided in the. Therefore, the lubricating oil can be discharged from the control pressure chamber C to the suction chamber 30, and the amount of lubricating oil in the control pressure chamber C can be reduced by preventing the amount of lubricating oil in the control pressure chamber C from becoming excessive. It can be kept moderate. As a result, an excessive amount of lubricating oil is stirred in the control pressure chamber C by the swash plate 24 and the like, and heat is generated. This heat generation reduces the viscosity of the lubricating oil and reduces the lubricating ability of the lubricating oil. Can be prevented.

  (2) The communication path 46 is formed through the swash plate 24 in the thickness direction around the insertion hole 24a in the swash plate 24. Therefore, as in the background art, the refrigerant gas in the rear side region C1 is supplied from the rear side region C1 to the front side region C2 as compared with the case where the refrigerant gas in the rear side region C1 is passed through the outer peripheral side of the swash plate 24 and supplied to the front side region C2. The amount of refrigerant gas and the amount of lubricating 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 less likely to move from the rear side region C1 to the front side region C2. For this reason, the configuration in which the refrigerant gas and the lubricating oil contained in the refrigerant gas can be supplied from the rear side region C1 to the front side region C2 through the communication passage 46 penetrating the swash plate 24 from the rear side region C1 to the front side. The refrigerant gas and the lubricant contained in the refrigerant gas can be effectively supplied to the side region C2.

  (3) The second opening 46 b of the communication path 46 is located between the second protrusion 45 that restricts the maximum inclination angle of the swash plate 24 and the hinge mechanism 25. For this reason, the refrigerant gas supplied from the second opening 46b to the front side region C2 and the lubricating oil contained in the refrigerant gas are less susceptible to the centrifugal force generated by the second protrusion 45 and the hinge mechanism 25, and the introduction hole It is possible to easily introduce the refrigerant gas and the lubricant contained in the refrigerant gas into 16d.

  (4) The second opening 46 b of the communication path 46 is formed at a position surrounded by the second protrusion 45 of the swash plate 24 and the rotating shaft 15. For this reason, the refrigerant gas supplied from the second opening 46b to the front side region C2 via the communication passage 46 and the lubricating oil contained in the refrigerant gas are prevented from being blown immediately around the second opening 46b and rotated. Lubricating oil can be retained around the shaft 15. Therefore, the second opening 46b of the communication path 46 is supplied to the front side region C2 via the communication path 46, as compared with the case where the second opening 46b is not formed at the position surrounded by the second protrusion 45 and the rotation shaft 15. The refrigerant gas and the lubricant contained in the refrigerant gas can be efficiently introduced into the introduction hole 16d.

  (5) The second opening 46b of the communication passage 46 is closest to the introduction hole 16d when the inclination angle of the swash plate 24 is maximum. The second opening 46b of the communication path 46 is formed in the vicinity of the insertion hole 24a through which the rotary shaft 15 is inserted. Therefore, the refrigerant gas supplied from the rear side region C1 to the front side region C2 and the lubricating oil contained in the refrigerant gas can be quickly discharged from the introduction hole 16d.

Each embodiment may be changed as follows.
As shown in FIGS. 6A and 6B, the rotary shaft 15 extends in the vicinity of the introduction hole 16d along the axial direction of the central axis T of the rotary shaft 15 and to the introduction hole 16d. A notch portion 16f that is inclined toward the central axis T as it goes is formed. Further, a collision portion 16g that collides the refrigerant gas and the lubricant contained in the refrigerant gas may be formed closer to the front housing 12 than the introduction hole 16d. In addition, a recovery portion 16h that extends to a position beyond the opening on the front side region C2 side of the introduction hole 16d and extends so as to intersect the rotation direction of the rotation shaft 15 may be provided in the vicinity of the introduction hole 16d. . With this configuration, the refrigerant gas that is supplied to the front side region C2 via the communication passage 46 and moves toward the introduction hole 16d and the lubricating oil contained in the refrigerant gas are directed toward the introduction hole 16d by the notch 16f. It is guided and further collides with the collision part 16g. The refrigerant gas that has collided with the collision portion 16g and the lubricating oil contained in the refrigerant gas are introduced into the introduction hole 16d as they are. Further, when the rotating shaft 15 rotates, the refrigerant gas and the lubricating oil contained in the refrigerant gas are scraped by the collecting unit 16h, and the refrigerant gas and the lubricating oil contained in the refrigerant gas are introduced into the introduction hole 16d. Therefore, compared with the case where notch part 16f, collision part 16g, and recovery part 16h are not formed in the vicinity of introduction hole 16d, the discharge efficiency of lubricating oil from control pressure chamber C can be improved.

  As shown in FIG. 7, the rotating shaft 15 is a groove that extends from the rear side region C1 to the front side region C2 on the outer peripheral surface of the first rotating shaft 16 and communicates the rear side region C1 and the front side region C2. The communication groove 58 may be provided as a recess, and the communication groove 58 may constitute a communication path. In this case, the communication groove 58 is connected to the introduction hole 16d, and the communication groove 58 is connected to the introduction hole 16d. Therefore, the rear side region C1 and the introduction hole 16d communicate with each other through the communication groove 58. When configured in this manner, the refrigerant gas in the rear side region C1 and the lubricating oil contained in the refrigerant gas can be directly supplied to the introduction hole 16d, and the lubricating oil can be efficiently supplied as compared with the case where the communication groove 58 is not formed. It can be discharged into the suction chamber 30.

  As shown in FIG. 8, the cylinder block 11 is provided with a through passage 61c penetrating the cylinder block 11, and the control pressure chamber C and the capacity control valve 60 are communicated with each other through the through passage 61c. The discharge chamber 31 and the control pressure chamber C may be communicated by the first passage 61a and the through passage 61c, and the supply passage may be formed by the first passage 61a and the through passage 61c. The second rotating shaft 17, the in-shaft supply passage 15a, the lip seal 37, and the lead-out passage 16c are omitted.

  As shown in FIG. 9, in the swash plate 24, on the inner peripheral surface of the swash plate 24 forming the insertion hole 24a, a communication groove 59 that is a groove extending over the entire thickness direction of the swash plate 24 is formed. You may comprise the communicating path which connects the rear side area | region C1 and the front side area | region C2 by the communication groove | channel 59. FIG.

  A sleeve may be interposed between the inner peripheral surface of the swash plate 24 that forms the insertion hole 24 a and the outer peripheral surface of the rotary shaft 15. Even in the state where this sleeve is provided, the swash plate 24 is directly supported by the rotary shaft 15 and leakage of the refrigerant gas from the rear side region C1 to the front side region C2 via the insertion hole 24a is restricted. ing.

The communication path 46 may be provided in the swash plate 24 only at one place or two places.
The communication path 46 may be provided in the swash plate 24 at four or more locations.
The passage diameter of the communication passage 46 is the same as the passage diameter of the introduction hole 16d, but the present invention is not limited to this, and the passage diameter of the communication passage 46 may be changed as appropriate.

  ○ In addition to the communication path 46 formed in the swash plate 24, the outer circumferential surface of the first rotating shaft 16 extends from the rear side region C1 to the front side region C2, and is a groove that communicates the rear side region C1 and the front side region C2. The communication groove may be recessed. Alternatively, in addition to the communication path 46 formed in the swash plate 24, a communication groove 59 that is a groove extending over the entire thickness direction of the swash plate 24 is formed on the inner peripheral surface of the swash plate 24 that forms the insertion hole 24a. The rear side region C1 and the front side region C2 may be communicated with each other by the communication groove 59.

  ○ On the outer peripheral surface of the first rotating shaft 16, a communication groove serving as a groove communicating the rear side region C1 and the front side region C2 is recessed, and further, on the inner peripheral surface of the swash plate 24 forming the insertion hole 24a, A communication groove 59 that extends over the entire thickness direction of the swash plate 24 may be formed, and the rear side region C1 and the front side region C2 may be communicated with each other by the communication groove 59.

  O The 2nd opening 46b of the communicating path 46 may be formed between the hinge mechanism 25 and the rotating shaft 15 instead of the position enclosed by the 2nd protrusion part 45 and the rotating shaft 15, for example.

The longitudinal section showing the variable capacity type compressor of an embodiment. The figure which shows the side which faces the front side area | region of a swash plate. The side view which shows a swash plate. The figure which shows the side which faces the rear side area | region of a swash plate. The graph which shows the residual oil ratio and oil content of a variable capacity type compressor. (A) is sectional drawing which shows the introduction hole vicinity in the rotating shaft of another example, (b) is a perspective view which shows the introduction hole vicinity in the rotating shaft of another example. Sectional drawing which shows another example of a communicating path. The longitudinal cross-sectional view which shows the variable capacity type compressor which shows another example of a supply channel | path. The figure which shows another example of a communicating path. The longitudinal cross-sectional view which shows the compressor of background art.

Explanation of symbols

  C ... Control pressure chamber, C1 ... Rear side region, C2 ... Front side region, S1 ... Supply space constituting supply passage, S2 ... Discharge space constituting discharge passage, 10 ... Variable capacity compressor, 11 ... Housing Cylinder block constituting, 12 ... Front housing constituting the housing, 14 ... Rear housing constituting the housing, 15 ... Rotating shaft, 15a ... In-shaft supply passage constituting the supply passage, 15b ... In-shaft discharge constituting the discharge passage A passage, 16c: a lead-out passage constituting a supply passage, 16d: an introduction hole constituting a discharge passage, 20 ... a shaft seal chamber constituting a supply passage, 22 ... a rotating support, 24 ... a swash plate, 25 ... a hinge mechanism, 24a ... Insertion hole, 30 ... Suction chamber as suction pressure region, 31 ... Discharge chamber as discharge pressure region, 45 ... Second protrusion as maximum tilt angle restricting portion, 46 ... Communication path, 46b ... A second opening as an opening to the front side region, 61a ... a first passage constituting a supply passage, 58, 59 ... a communication groove as a communication passage, 60 ... a capacity control valve constituting a supply passage, 61b ... a discharge passage. 2nd channel | path which comprises, 61c ... The penetration channel | path which comprises a supply channel.

Claims (6)

A first end side of the rotary shaft is rotatably supported on the front side of the housing, and a second end side of the rotary shaft is rotatably supported on the rear side. The control pressure chamber in the housing is fixed to the rotary shaft. And a swash plate that is directly supported by the rotary support and is connected to the rotary support via a hinge mechanism and rotates integrally with the rotary shaft, and accommodates the discharge pressure region and the control. The refrigerant gas in the discharge pressure region is supplied to the control pressure chamber through the supply passage that communicates with the pressure chamber, and the refrigerant gas in the control pressure chamber is sucked in through the discharge passage that communicates the suction pressure region and the control pressure chamber. A variable displacement compressor in which the discharge angle is controlled by changing the tilt angle of the swash plate by adjusting the pressure inside the control pressure chamber by discharging to the pressure region;
An in-shaft discharge passage that forms a part of the discharge passage is formed in the rotating shaft, and the front of the control pressure chamber between the swash plate and the rotating support is on the rotating support side of the swash plate. An introduction hole that opens toward the side region and communicates with the in-shaft discharge passage is formed, and at least one of the swash plate and the rotation shaft includes the front side region and the control pressure chamber. A variable displacement compressor in which a communication path is formed to communicate with a rear side region on the counter-rotating support side of a swash plate. The variable capacity compressor according to claim 1, wherein the communication path is formed through the swash plate in a thickness direction. The swash plate is formed with an insertion hole through which the rotation shaft is inserted, and the communication path is formed by a groove extending on the inner peripheral surface of the swash plate forming the insertion hole over the entire thickness direction of the swash plate. The variable capacity type compressor according to claim 1 or claim 2 to be performed. 4. The variable capacity compressor according to claim 1, wherein the communication path is recessed in a peripheral surface of the rotation shaft and is formed by a groove communicating with the introduction hole. 5. The swash plate is provided with a maximum inclination restriction portion that restricts the maximum inclination angle of the swash plate by coming into contact with the rotary support, and an opening to the front side region in the communication path is formed between the maximum inclination restriction portion and the The variable capacity compressor according to any one of claims 1 to 4, which is located between the hinge mechanisms. The variable capacity compressor according to claim 5, wherein an opening to a front side region in the communication path is located between the maximum inclination angle restricting portion and a rotation shaft.

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