JP2016133095A - Variable displacement swash plate type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement swash plate type compressor capable of suppressing vibration and noise while reducing power loss.SOLUTION: In a compressor of this invention, a second supporting member 43b is inserted into a driving shaft body 30 of a driving shaft 3. The second supporting member 43b is movable to a driving axis O direction in accordance with movement of a moving body 13a. A second thrust bearing 35b for supporting thrust force acting on the driving shaft 3 is provided between the second supporting member 43b and a second cylinder block 23. A regulating part 30c for regulating movement of the second supporting member 43b to the moving body 13a side at least when a tilt angle is minimum is provided on the driving shaft body 30 of the driving shaft 3.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a variable displacement swash plate compressor.

  Patent Document 1 discloses a conventional swash plate compressor. This swash plate compressor is of a fixed capacity type and includes a housing, a drive shaft, a swash plate, a piston, and a conversion mechanism.

  The housing has a swash plate chamber, a first cylinder block disposed on the front end side of the drive shaft, and a second cylinder block disposed on the rear end side of the drive shaft. The first cylinder block is formed with a first cylinder bore extending in the drive axis direction. The second cylinder block is formed with a second cylinder bore extending in the drive axis direction.

  The drive shaft is rotatably supported by the first and second cylinder blocks. The swash plate can be rotated in the swash plate chamber by the rotation of the drive shaft. The swash plate has a constant inclination angle with respect to the direction orthogonal to the drive axis of the drive shaft. The piston is a double-headed piston and is accommodated in the first and second cylinder bores so as to be able to reciprocate. The conversion mechanism reciprocates the piston in the first and second cylinder bores with a stroke corresponding to the inclination angle by the rotation of the swash plate.

  Thrust bearings are provided between the drive shaft and the first cylinder block and between the drive shaft and the second cylinder block in a state where a predetermined preload is applied.

  In this swash plate compressor, a compression reaction force due to reciprocation of the piston during operation is transmitted to the drive shaft via the swash plate, and a thrust force acts on the drive shaft. A thrust force acting on the drive shaft is supported by a thrust bearing to which a predetermined preload is applied. Thus, in this swash plate compressor, vibration and noise are suppressed by suitably supporting the drive shaft on the thrust bearing.

JP 7-197883 A

  By the way, this type of swash plate compressor includes a variable capacity type. The variable capacity swash plate compressor may further include a link mechanism that allows a change in the inclination angle of the swash plate, an actuator that can change the inclination angle, and a control mechanism that controls the actuator. In this variable displacement swash plate compressor, when the tilt angle of the swash plate is changed, the piston reciprocates in the cylinder bore with a stroke corresponding to the tilt angle, and the discharge capacity increases or decreases.

  However, in this variable displacement swash plate compressor, when the discharge capacity increases or decreases, the compression reaction force received by the piston increases or decreases, and the thrust force acting on the drive shaft also increases or decreases. For this reason, the appropriate range of the preload required for a thrust bearing will also increase / decrease accordingly.

  Here, it is considered to set a large preload applied to the thrust bearing according to the thrust force acting on the drive shaft in a state where the discharge capacity is increased. In this case, in a state where the discharge capacity is increased, the thrust bearing can favorably support the drive shaft and suppress vibration and noise. However, when the discharge capacity is reduced, the preload applied to the thrust bearing becomes excessive with respect to the reduced thrust force. As a result, in this variable displacement swash plate compressor, drag resistance acting on the drive shaft from the thrust bearing increases, and power loss increases.

  On the other hand, it is considered that the preload applied to the thrust bearing is set small in accordance with the thrust force acting on the drive shaft in a state where the discharge capacity is reduced. In this case, in a state where the discharge capacity is reduced, the thrust bearing can favorably support the drive shaft to suppress vibration and noise, and drag resistance acting on the drive shaft from the thrust bearing can be reduced, thereby reducing power loss. However, in a state where the discharge capacity is increased, the preload applied to the thrust bearing becomes excessively small with respect to the increased thrust force. As a result, in this capacity variable swash plate compressor, it becomes difficult for the thrust bearing to properly support the drive shaft, and vibration and noise cannot be suppressed.

  The present invention has been made in view of the above-described conventional situation, and an object to be solved is to provide a variable displacement swash plate compressor capable of suppressing vibration and noise while reducing power loss. .

The variable capacity swash plate compressor according to the present invention includes a housing having a swash plate chamber and a cylinder block in which a cylinder bore is formed, a drive shaft rotatably supported by the housing, and rotation of the drive shaft. A swash plate rotatable within a plate chamber, and a link mechanism provided between the drive shaft and the swash plate and allowing a change in the inclination angle of the swash plate with respect to a direction perpendicular to the drive axis of the drive shaft; A piston accommodated reciprocally in the cylinder bore, a conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the inclination angle by rotation of the swash plate, and the inclination angle being changeable An actuator, and a control mechanism for controlling the actuator,
The actuator is provided with a partition provided on the drive shaft, a connecting portion connected to the swash plate, a movable body movable in the direction of the drive axis in the swash plate chamber, the partition and the A control pressure chamber that is partitioned by the moving body and moves the moving body so that the inclination angle is increased by introducing the refrigerant into the inside,
A support member that is inserted through the drive shaft and is movable in the direction of the drive shaft along with the movement of the movable body;
Between the support member and the cylinder block, a thrust bearing that supports a thrust force acting on the drive shaft is provided,
The drive shaft is provided with a restricting portion that restricts the support member from moving toward the moving body when at least the inclination angle is minimum.

  In the variable capacity swash plate compressor (hereinafter simply referred to as a compressor) of the present invention, when the refrigerant is introduced into the control pressure chamber and the movable body moves in the direction of the drive shaft, the inclination angle of the swash plate is increased. Increases and discharge capacity increases. At this time, the support member moves in the direction of the drive shaft along with the movement of the moving body, strongly presses the thrust bearing, and increases the preload applied to the thrust bearing. Thus, in this compressor, the thrust bearing with the increased preload can support the drive shaft in a state where the discharge capacity is increased, thereby suppressing vibration and noise.

  On the other hand, when the refrigerant is not introduced into the control pressure chamber and the moving body moves in the opposite direction, the inclination angle of the swash plate is reduced and the discharge capacity is reduced. At this time, the support member moves in the reverse direction as the moving body moves in the reverse direction, weakly presses the thrust bearing, and reduces the preload applied to the thrust bearing. Here, at least when the inclination angle is the minimum, the restricting portion provided on the drive shaft restricts the support member from moving toward the moving body. Therefore, the support member is separated from the moving body, and the support member moves the thrust bearing. A weak pressing state is maintained. In this way, in this compressor, the thrust bearing with the reduced preload with the reduced discharge capacity can suitably support the drive shaft to suppress vibration and noise, and the drag resistance acting on the drive shaft from the thrust bearing can be reduced. it can.

  Therefore, the compressor of the present invention can suppress vibration and noise while reducing power loss. Further, in this compressor, the durability of the thrust bearing can be increased as compared with the case where the preload applied to the thrust bearing does not change regardless of the increase or decrease of the discharge capacity.

  In the compressor of the present invention, it is preferable that the support member regulates the maximum value of the inclination angle. In this case, the preload applied to the thrust bearing is maximized by maximizing the inclination angle. For this reason, in this compressor, vibration and noise can be suitably suppressed at the maximum discharge capacity.

  The support member preferably has an annular shape around the drive axis. The thrust bearing preferably includes a first race, a second race, and rolling elements sandwiched between the first race and the second race. It is preferable that the outer peripheral edge side of the first race is in contact with the cylinder block, and the inner peripheral edge side of the second race is in contact with the support member.

  In this case, in this compressor, since the thrust bearing is easily elastically deformed in the shape of a disc spring, it is possible to favorably support the thrust force acting on the support member and the drive shaft.

  According to the variable capacity swash plate compressor of the present invention, vibration and noise can be suppressed while reducing power loss.

FIG. 1 is a cross-sectional view of the compressor according to the embodiment when the capacity is minimum. FIG. 2 is a cross-sectional view of the compressor of the embodiment at the maximum capacity. FIG. 3 is a schematic diagram illustrating a control mechanism according to the compressor of the embodiment. FIG. 4 is an enlarged cross-sectional view of a main part showing a first thrust bearing and the like according to the compressor of the embodiment. FIG. 5 is an enlarged cross-sectional view of a main part illustrating the position of the second support member, the second thrust bearing, and the like, according to the compressor of the embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating the position of the second support member, the second thrust bearing, and the like when the inclination angle of the swash plate increases to the maximum value in the compressor of the embodiment. FIG. 7 is an enlarged cross-sectional view of a main part showing the first thrust bearing and the like when the inclination angle of the swash plate is increased to the maximum value in the compressor of the embodiment.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings. The compressor of an Example is mounted in the vehicle and comprises the refrigerating circuit of the vehicle air conditioner.

  As shown in FIGS. 1 and 2, the capacity variable type swash plate compressor of the embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, and a plurality of pairs. Shoes 11a and 11b and an actuator 13 are provided. Moreover, this compressor is provided with the control mechanism 15 as shown in FIG.

  As shown in FIGS. 1 and 2, the housing 1 includes a first housing 17, a second housing 19, a first cylinder block 21, a second cylinder block 23, a first valve forming plate 39, and a second housing. And an annuloplasty plate 41. In the present embodiment, the front-rear direction of the compressor is defined with the side where the first housing 17 is located as the front side of the compressor and the side where the second housing 19 is located as the rear side of the compressor. The front side of the compressor corresponds to “one end side of the drive shaft” in the present invention, and the rear side of the compressor corresponds to “the other end side of the drive shaft” in the present invention.

  The first housing 17 is formed with a boss 17a protruding forward. A shaft seal device 25 is provided in the boss 17a. A first suction chamber 27a and a first discharge chamber 29a are formed in the first housing 17. The first suction chamber 27 a is formed in an annular shape and is located on the inner peripheral side of the first housing 17. The first discharge chamber 29 a is also formed in an annular shape, and is positioned on the outer peripheral side of the first suction chamber 27 a in the first housing 17.

  Further, the first housing 17 is formed with a first front communication path 18a. The first front communication path 18 a has a front end communicating with the first discharge chamber 29 a and a rear end opening on the rear end surface of the first housing 17.

  The second housing 19 is provided with part of the control mechanism 15 described above. The second housing 19 includes a second suction chamber 27b, a second discharge chamber 29b, and a pressure adjustment chamber 31. The pressure adjustment chamber 31 is located in the central portion of the second housing 19. The second suction chamber 27 b is formed in an annular shape, and is located on the outer peripheral side of the pressure adjustment chamber 31 in the second housing 19. The second discharge chamber 29 b is also formed in an annular shape, and is positioned on the outer peripheral side of the second suction chamber 27 b in the second housing 19.

  Further, a first rear side communication passage 20 a is formed in the second housing 19. The first rear communication path 20 a has a rear end side communicating with the second discharge chamber 29 b and a front end side opening on the front end surface of the second housing 19.

  The first cylinder block 21 is provided on the front side of the compressor and between the first housing 17 and the second cylinder block 23. The first cylinder block 21 is formed with a plurality of first cylinder bores 21a extending in the direction of the drive axis O. The first cylinder bores 21a are arranged at equiangular intervals in the circumferential direction. The first cylinder block 21 is formed with a first shaft hole 21b through which the drive shaft 3 is inserted. A first sliding bearing 22a is provided in the first shaft hole 21b.

  Further, the first cylinder block 21 is formed with a first recess 21c communicating with the first shaft hole 21d from the rear side of the compressor. The first recess 21c is coaxial with the first shaft hole 21b and has an inner diameter larger than that of the first shaft hole 21b. As shown in an enlarged view in FIG. 4, a first concave surface 21d that is recessed toward the front side of the compressor is formed in an annular shape on the front wall of the first concave portion 21c.

  A first thrust bearing 35a is provided in the first recess 21c. The first thrust bearing 35a includes a first race 351, a second race 352, a plurality of rolling elements 353 sandwiched between the first and second races 351 and 352, and the first and second races 351 and 352. And a holder (not shown) for holding the rolling elements 353.

  The first cylinder block 21 is provided with a first retainer groove 21e for restricting the maximum opening of each first suction reed valve 391a described later. Further, as shown in FIGS. 1 and 2, the first cylinder block 21 is formed with a first communication path 37 a and a second front side communication path 18 b. Each of the first communication path 37 a and the second front side communication path 18 b has a front end opened on the front end face of the first cylinder block 21 and a rear end opened on the rear end face of the first cylinder block 21. .

  The second cylinder block 23 is provided on the rear side of the compressor and between the first cylinder block 21 and the second housing 19. The second cylinder block 23 is joined to the first cylinder block 21, thereby forming a swash plate chamber 33 with the first cylinder block 21. The swash plate chamber 33 communicates with the first recess 21c. Thereby, the first recess 21 c constitutes a part of the swash plate chamber 33.

  The second cylinder block 23 is formed with a plurality of second cylinder bores 23a extending in the direction of the drive axis O. Like the first cylinder bores 21a, the second cylinder bores 23a are arranged at equal angular intervals in the circumferential direction, and are paired with the first cylinder bores 21a in the front-rear direction. Each first cylinder bore 21a and each second cylinder bore 23a are formed to have the same diameter. In addition, if the 1st cylinder bore 21a and the 2nd cylinder bore 23b have made a pair, these numbers can be designed suitably.

  The second cylinder block 23 has a second shaft hole 23b through which the drive shaft 3 is inserted. A second sliding bearing 22b is provided in the second shaft hole 23b. Instead of the first sliding bearing 22a and the second sliding bearing 22b, rolling bearings may be provided.

  The second cylinder block 23 is formed with a second recess 23c communicating with the second shaft hole 23b from the front side of the compressor. The second recess 23c is coaxial with the second shaft hole 23b and has an inner diameter larger than that of the second shaft hole 23b. The second recess 23 c is also in communication with the swash plate chamber 33 and constitutes a part of the swash plate chamber 33. As shown in FIG. 5, a second concave surface 23d that is recessed toward the rear side of the compressor is formed in an annular shape on the rear wall of the second concave portion 23c.

  A second thrust bearing 35b is provided in the second recess 23c. The second thrust bearing 35b includes a first race 354, a second race 355, a plurality of rolling elements 356 sandwiched between the first and second races 354 and 355, and the first and second races 354 and 355. And a holder (not shown) for holding the rolling element 356.

  The second cylinder block 23 is provided with a second retainer groove 23e that restricts the maximum opening degree of each second suction reed valve 411a described later. Further, as shown in FIGS. 1 and 2, the second cylinder block 23 includes a discharge port 230, a merged discharge chamber 231, a third front side communication path 18c, a second rear side communication path 20b, and a suction port. A port 330 and a second communication path 37b are formed. The discharge port 230 and the merged discharge chamber 231 communicate with each other. The merging / discharging chamber 231 is connected via a discharge port 230 to a condenser (not shown) that forms a pipe line. The swash plate chamber 33 is connected via an intake port 330 to an evaporator (not shown) constituting a pipe line.

  The third front side communication path 18 c communicates with the second front side communication path 18 b and the merged discharge chamber 231. The second rear communication path 20 b has a front end communicating with the merging / discharging chamber 231 and a rear end opening on the rear end surface of the second cylinder block 23. The front end side of the second communication path 37 b opens to the swash plate chamber 33, and the rear end side opens to the rear end face of the second cylinder block 23.

  The first valve forming plate 39 is provided between the first housing 17 and the first cylinder block 21. The first housing 17 and the first cylinder block 21 are joined via the first valve forming plate 39. The second valve forming plate 41 is provided between the second housing 19 and the second cylinder block 23. The second housing 19 and the second cylinder block 23 are joined via the second valve forming plate 41.

  The first valve forming plate 39 includes a first valve plate 390, a first suction valve plate 391, a first discharge valve plate 392, and a first retainer plate 393. The first valve plate 390 and the first intake valve plate 391 extend to the outer circumferences of the first housing 17 and the first cylinder block 21. The first valve plate 390, the first discharge valve plate 392, and the first retainer plate 393 are formed with the same number of first suction holes 390a as the first cylinder bores 21a. The first valve plate 390 and the first intake valve plate 391 are formed with the same number of first discharge holes 390b as the first cylinder bores 21a. Furthermore, a first suction communication hole 390c is formed in the first valve plate 390, the first suction valve plate 391, the first discharge valve plate 392, and the first retainer plate 393. A first discharge communication hole 390d is formed in the first valve plate 390 and the first suction valve plate 391.

  Each first cylinder bore 21a communicates with the first suction chamber 27a through each first suction hole 390a. Each first cylinder bore 21a communicates with the first discharge chamber 29a through each first discharge hole 390b. The first suction chamber 27a and the first communication path 37a communicate with each other through the first suction communication hole 390c. The first front communication path 18a and the second front communication path 18b communicate with each other through the first discharge communication hole 390d.

  The first suction valve plate 391 is provided on the rear surface of the first valve plate 390. The first suction valve plate 391 is formed with a plurality of first suction reed valves 391a that can open and close each first suction hole 390a by elastic deformation. The first discharge valve plate 392 is provided on the front surface of the first valve plate 390. The first discharge valve plate 392 is formed with a plurality of first discharge reed valves 392a that can open and close each first discharge hole 390b by elastic deformation. The first retainer plate 393 is provided on the front surface of the first discharge valve plate 392. The first retainer plate 393 regulates the maximum opening degree of each first discharge reed valve 392a.

  The second valve forming plate 41 includes a second valve plate 410, a second suction valve plate 411, a second discharge valve plate 412, and a second retainer plate 413. The second valve plate 410 and the second intake valve plate 411 extend to the outer circumferences of the second housing 19 and the second cylinder block 23. The second valve plate 410, the second discharge valve plate 412 and the second retainer plate 413 are formed with the same number of second suction holes 410a as the second cylinder bores 23a. The second valve plate 410 and the second intake valve plate 411 are formed with the same number of second discharge holes 410b as the second cylinder bores 23a. Further, a second suction communication hole 410c is formed in the second valve plate 410, the second suction valve plate 411, the second discharge valve plate 412 and the second retainer plate 413. A second discharge communication hole 410d is formed in the second valve plate 410 and the second suction valve plate 411.

  Each second cylinder bore 23a communicates with the second suction chamber 27b through each second suction hole 410a. Each second cylinder bore 23a communicates with the second discharge chamber 29b through each second discharge hole 410b. The second suction chamber 27b and the second communication path 37b communicate with each other through the second suction communication hole 410c. The first rear communication path 20a and the second rear communication path 20b communicate with each other through the second discharge communication hole 410d.

  The second intake valve plate 411 is provided on the front surface of the second valve plate 410. The second suction valve plate 411 is formed with a plurality of second suction reed valves 411a that can open and close each second suction hole 410a by elastic deformation. The second discharge valve plate 412 is provided on the rear surface of the second valve plate 410. The second discharge valve plate 412 is formed with a plurality of second discharge reed valves 412a capable of opening and closing each second discharge hole 410b by elastic deformation. The second retainer plate 413 is provided on the rear surface of the second discharge valve plate 412. The second retainer plate 413 regulates the maximum opening degree of each second discharge reed valve 412a.

  A first discharge communication path 18 is formed by the first front communication path 18a, the first discharge communication hole 390d, the second front communication path 18b, and the third front communication path 18c. Further, the second discharge communication passage 20 is formed by the first rear communication passage 20a, the second discharge communication hole 410d, and the second rear communication passage 20b.

  The first and second suction chambers 27a and 27b and the swash plate chamber 33 communicate with each other through the first and second communication paths 37a and 37b and the first and second suction communication holes 390c and 410c. Therefore, the pressures in the first and second suction chambers 27a and 27b and the swash plate chamber 33 are substantially equal. Since the low-pressure refrigerant gas that has passed through the evaporator flows into the swash plate chamber 33 through the suction port 330, the first and second discharge chambers 29a are provided in the swash plate chamber 33 and the first and second suction chambers 27a and 27b. , 29b.

  The drive shaft 3 includes a drive shaft main body 30 and a first support member 43a press-fitted into the drive shaft main body 30.

  The drive shaft main body 30 extends from the front side of the housing 1 toward the rear side in the axial direction. A first small diameter portion 30 a is formed on the front end side of the drive shaft main body 30. A second small diameter portion 30 b is formed on the rear end side of the drive shaft main body 30. As shown in FIG. 5, a step portion 30 c is formed at a boundary portion between the second small diameter portion 30 b and a portion of the drive shaft main body 30 in front of the second small diameter portion 30 b. This step portion 30c corresponds to a regulating portion in the present invention. An O-ring 51a is provided in the second small diameter portion 30b.

  As shown in FIGS. 1 and 2, the drive shaft main body 30 is inserted into the shaft sealing device 25 and the first and second sliding bearings 22 a and 22 b in the housing 1. As a result, the drive shaft main body 30 and thus the drive shaft 3 are pivotally supported by the housing 1 so as to be rotatable around the drive shaft center O. The front end of the drive shaft body 30 is inserted through the shaft seal device 25 in the boss 17a. The rear end of the drive shaft main body 30 protrudes into the pressure adjustment chamber 31.

  The drive shaft main body 30 is provided with the swash plate 5, the link mechanism 7, and the actuator 13. The swash plate 5, the link mechanism 7, and the actuator 13 are respectively disposed in the swash plate chamber 33.

  A threaded portion 3 a is formed at the front end of the drive shaft main body 30. The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) via the screw portion 3a.

  The first support member 43a is formed in a cylindrical shape with the drive axis O as the central axis. The first support member 43 a is press-fitted into the first small diameter portion 30 a of the drive shaft body 30 and is integrated with the drive shaft body 30. The first support member 43a is supported by the first sliding bearing 22a in the first shaft hole 21b. On the rear end side of the first support member 43a, a first flange 430 and an attachment portion (not shown) through which a second pin 47b described later is inserted are formed.

  As shown in FIG. 4, the first thrust bearing 35a is sandwiched from the axial direction by the first flange 430 and the front wall of the first recess 21c. As a result, a predetermined preload is applied to the first thrust bearing 35a, and the thrust force toward the front end side of the compressor acting on the drive shaft body 30 including the first support member 43a during operation is supported.

  Here, the outer diameter of the first flange 430 is set to be larger than the inner diameter of the first thrust bearing 35a and smaller than the outer diameter of the first thrust bearing 35a. As a result, the first thrust bearing 35 a contacts the first flange 430 only on the inner peripheral edge side of the second race 352. On the other hand, the inner diameter of the first concave surface 21d formed on the front wall of the first recess 21c is set larger than the inner diameter of the first thrust bearing 35a and smaller than the outer diameter of the first thrust bearing 35a. Thereby, the first thrust bearing 35a contacts the front wall of the first recess 21c only on the outer peripheral edge side of the first race 351.

  As shown in FIGS. 1 and 2, the front end of the return spring 44a is inserted through the first support member 43a. The return spring 44a extends from the flange 430 side toward the swash plate 5 side in the drive axis O direction.

  Further, the compressor includes a second support member 43b. The second support member 43b corresponds to the support member in the present invention. As shown in FIG. 5, the second support member 43 b is formed in a cylindrical shape having the drive shaft center O as a central axis. The second support member 43b is inserted into the second small diameter portion 30b so as to be movable in the direction of the drive axis O. Accordingly, the second support member 43b can move the second small diameter portion 30b in the front-rear direction in the direction of the drive axis O while being supported by the second sliding bearing 22b in the second shaft hole 23b. It has become. When the O-ring 51a is elastically deformed between the second support member 43b and the second small diameter portion 30b, on the inner peripheral side of the second support member 43b, between the pressure adjustment chamber 31 and the second recess 23c, by extension, The space between the pressure adjustment chamber 31 and the swash plate chamber 33 is sealed. In addition, it is good also as a structure which seals between the pressure regulation chamber 31 and the swash plate chamber 33 in the inner peripheral side of the 2nd support member 43b with the lubricating oil which exists in a compressor, without providing O-ring 51a.

  A second flange 431 is formed at the front end of the second support member 43b. Furthermore, O-rings 51b and 51c are provided in the second support member 43b at a position closer to the rear end side than the second flange 431. These O-rings 51b and 51c seal the space between the pressure adjustment chamber 31 and the swash plate chamber 33 also on the outer peripheral side of the second support member 43b.

  The second thrust bearing 35b is sandwiched from the axial direction by the second flange 431 and the rear wall of the second recess 23c. Thus, a predetermined preload is applied to the second thrust bearing 35b, and the thrust force toward the rear end side of the compressor acting on the drive shaft main body 30 including the second support member 43b during operation is supported.

  Here, the outer diameter of the second flange 431 is set larger than the inner diameter of the second thrust bearing 35b and smaller than the outer diameter of the second thrust bearing 35b. Accordingly, the second thrust bearing 35b contacts the second flange 431 only on the inner peripheral side of the second race 355. On the other hand, the inner diameter of the second concave surface 23d formed on the rear wall of the second recess 23c is set larger than the inner diameter of the second thrust bearing 35b and smaller than the outer diameter of the second thrust bearing 35b. Accordingly, the second thrust bearing 35b contacts the rear wall of the second recess 23c only on the outer peripheral edge side of the first race 354.

  As shown in FIGS. 1 and 2, the swash plate 5 has an annular flat plate shape and has a front surface 5a and a rear surface 5b. The front surface 5 a faces the front side of the compressor in the swash plate chamber 33. The rear surface 5 b faces the rear side of the compressor in the swash plate chamber 33.

  The swash plate 5 has a ring plate 45. The ring plate 45 is formed in an annular flat plate shape, and an insertion hole 45a is formed at the center. The swash plate 5 is attached to the drive shaft 3 by inserting the drive shaft main body 30 through the insertion hole 45 a in the swash plate chamber 33. The ring plate 45 is formed with a connecting portion (not shown) that is connected to each connecting arm 132 described later.

  The link mechanism 7 has a lug arm 49. The lug arm 49 is disposed in front of the swash plate 5 in the swash plate chamber 33 and is positioned between the swash plate 5 and the first support member 43a. The lug arm 49 is formed to be substantially L-shaped from the front end side toward the rear end side. On the rear end side of the lug arm 49, a weight portion 49a is formed. The weight portion 49 a extends in the circumferential direction of the actuator 13 and covers approximately half the circumference of the actuator 13. The shape of the weight portion 49a can be designed as appropriate.

  The rear end side of the lug arm 49 is connected to the ring plate 45 by the first pin 47a. Thereby, the lug arm 49 is supported by the ring plate 45, that is, the swash plate 5 so as to be swingable around the first swing axis M1 with the first pin 47a as the first swing axis M1. ing. The first swing axis M1 extends in a direction orthogonal to the drive axis O of the drive shaft 3.

  The front end side of the lug arm 49 is connected to the first support member 43a by the second pin 47b. As a result, the lug arm 49 can swing around the second swing axis M2 with respect to the first support member 43a, that is, the drive shaft 3, with the second pivot 47b serving as the second pivot axis M2. It is supported. The second swing axis M2 extends in parallel with the first swing axis M1. The link mechanism 7 in the present invention is constituted by the lug arm 49 and the first and second pins 47a and 47b.

  The weight portion 49a is provided to extend to the rear end side of the lug arm 49, that is, on the opposite side of the second swing axis M2 with respect to the first swing axis M1. For this reason, the lug arm 49 is supported by the ring plate 45 by the first pin 47 a, so that the weight portion 49 a passes through the groove portion 45 b of the ring plate 45 and faces the rear surface of the ring plate 45, that is, the rear surface 5 b side of the swash plate 5. To position. Then, the centrifugal force generated when the swash plate 5 rotates around the drive axis O also acts on the weight portion 49a on the rear surface 5b side of the swash plate 5.

  In this compressor, the swash plate 5 and the drive shaft 3 are connected by the link mechanism 7 so that the swash plate 5 can rotate together with the drive shaft 3. Further, the both ends of the lug arm 49 swing around the first swing axis M1 and the second swing axis M2, respectively, so that the swash plate 5 moves from the minimum value shown in FIG. 1 to the maximum value shown in FIG. The inclination angle can be changed.

  As shown in FIGS. 1 and 2, each piston 9 is a double-headed piston, and has a first head 9a on the front end side and a second head 9b on the rear end side. Each first head 9a is accommodated in each first cylinder bore 21a so as to be capable of reciprocating. The first compression chambers 53a are defined in the first cylinder bores 21a by the first heads 9a and the first valve forming plate 39, respectively. Each second head portion 9b is accommodated in each second cylinder bore 23a so as to be capable of reciprocating. The second compression chambers 53b are defined in the second cylinder bores 23a by the second heads 9b and the second valve forming plate 41, respectively.

  Each piston 9 has an engaging portion 9c at the center. In each engaging portion 9c, hemispherical shoes 11a and 11b are provided. Each shoe 11 a slides on the front surface 5 a of the swash plate 5. On the other hand, each shoe 11b slides on the rear surface 5b of the swash plate 5. Thus, the rotation of the swash plate 5 is converted into the reciprocating motion of the piston 9 by each shoe 11a and each shoe 11b. Each shoe 11a, 11b corresponds to a conversion mechanism in the present invention. Thus, each first head 9a can reciprocate within the first cylinder bore 21a with a stroke corresponding to the inclination angle of the swash plate 5, and each second head 9b can move to the second cylinder bore 23a. It is possible to reciprocate inside.

  Here, in this compressor, the top dead center positions of the first heads 9a and the second heads 9b move as the strokes of the pistons 9 change as the inclination angle of the swash plate 5 changes. To do. Specifically, as the inclination angle of the swash plate 5 becomes smaller, the top dead center position of each second head 9b moves larger than the top dead center position of each first head 9a.

  The actuator 13 is disposed in the swash plate chamber 33. The actuator 13 is located behind the swash plate 5 in the swash plate chamber 33, and can enter the second recess 23c. The actuator 13 has a moving body 13a, a partitioning body 13b, and a control pressure chamber 13c. The control pressure chamber 13c is formed between the movable body 13a and the partition body 13b.

  The moving body 13a has a rear wall 130, a peripheral wall 131, and a pair of pulling arms 132. 1 and 2, only one of the pair of pulling arms 132 is shown.

  The rear wall 130 is located behind the movable body 13a and extends in the radial direction in a direction away from the drive axis O. The rear wall 130 is provided with an insertion hole 130a through which the second small diameter portion 30b of the drive shaft main body 30 is inserted. An O-ring 51d is provided in the insertion hole 130a. The peripheral wall 131 is continuous with the outer peripheral edge of the rear wall 130 and extends toward the front of the moving body 13a. Each traction arm 132 is formed at the front end of the peripheral wall 131 with the drive axis O interposed therebetween, and projects toward the front of the movable body 13a. Each pulling arm 132 corresponds to a connecting portion in the present invention. By these rear wall 130, peripheral wall 131, and each pulling arm 132, the movable body 13a has a bottomed cylindrical shape.

  The partition body 13b is formed in a disk shape having substantially the same diameter as the inner diameter of the moving body 13a. The partition 13b has an insertion hole 133 extending through the center. An O-ring 51e is provided on the outer periphery of the partition 13b.

  Between the partition 13b and the ring plate 45, a tilt angle reducing spring 44b is provided. Specifically, the rear end of the tilt angle reducing spring 44b is disposed so as to contact the partitioning body 13b, and the front end of the tilt angle decreasing spring 44b is disposed so as to contact the ring plate 45. The inclination-decreasing spring 44b urges both the partition 13b and the ring plate 45 so that they are remote from each other.

  The drive shaft main body 30 is inserted through the insertion hole 130a of the moving body 13a. Thereby, the moving body 13a can move the drive shaft main body 30 in the direction of the drive axis O. On the other hand, the drive shaft main body 30 is press-fitted into the insertion hole 133 of the partition 13b. As a result, the partition body 13 b is fixed to the drive shaft main body 30, and the partition body 13 b can rotate together with the drive shaft main body 30. The partition 13b may also be inserted through the drive shaft main body 30 so as to be movable in the direction of the drive axis O.

  The partition 13b is disposed in the movable body 13a behind the swash plate 5, and the periphery thereof is surrounded by the peripheral wall 131. Thereby, when the moving body 13a moves in the direction of the drive axis O, the inner peripheral surface of the peripheral wall 131 of the moving body 13a and the outer peripheral surface of the partition 13b slide.

  And the control body 13c is formed between the mobile body 13a and the division body 13b because the division body 13b is surrounded by the surrounding wall 131. FIG. The control pressure chamber 13c is partitioned from the swash plate chamber 33 by the rear wall 130, the peripheral wall 131, and the partition body 13b.

  Each pulling arm 132 and the ring plate 45 are connected by a third pin 47c. Accordingly, the swash plate 5 is supported by the movable body 13a so as to be swingable around the action axis M3 with the axis of the third pin 47c as the action axis M3. The action axis M3 extends in parallel with the first and second oscillation axes M1 and M2. Thus, the moving body 13a is connected to the swash plate 5. Then, the movable body 13a is connected to the swash plate 5, so that the partition 13b and the swash plate 5 face each other.

  In the second small diameter portion 30b, an axial path 3b extending in the direction of the drive axis O from the rear end toward the front, and a radial path 3c extending in the radial direction from the front end of the axial path 3b and opening to the outer peripheral surface of the drive shaft main body 30. And are formed. The rear end of the axial path 3 b communicates with the pressure adjustment chamber 31. On the other hand, the path 3c communicates with the control pressure chamber 13c. Thereby, the control pressure chamber 13c communicates with the pressure regulation chamber 31 through the radial path 3c and the axial path 3b.

  As shown in FIG. 3, the control mechanism 15 has an extraction passage 15a, an air supply passage 15b, a control valve 15c, an orifice 15d, an axial path 3b, and a radial path 3c.

  The extraction passage 15a is connected to the pressure adjustment chamber 31 and the second suction chamber 27b. The control pressure chamber 13c, the pressure adjustment chamber 31, and the second suction chamber 27b communicate with each other through the extraction passage 15a, the axial path 3b, and the radial path 3c. The air supply passage 15b is connected to the pressure adjusting chamber 31 and the second discharge chamber 29b. The control pressure chamber 13c, the pressure adjustment chamber 31, and the second discharge chamber 29b are communicated with each other by the air supply passage 15b, the axial path 3b, and the radial path 3c. An orifice 15d is provided in the supply passage 15b.

  The control valve 15c is provided in the extraction passage 15a. The control valve 15c can adjust the opening degree of the extraction passage 15a based on the pressure in the second suction chamber 27b.

  In this compressor, a pipe connected to the evaporator is connected to the suction port 330 shown in FIGS. 1 and 2, and a pipe connected to the condenser is connected to the discharge port 230. The condenser is connected to the evaporator via a pipe and an expansion valve. These compressors, evaporators, expansion valves, condensers and the like constitute a refrigeration circuit for a vehicle air conditioner. In addition, illustration of an evaporator, an expansion valve, a condenser, and each piping is abbreviate | omitted.

  In the compressor configured as described above, when the drive shaft 3 rotates, the swash plate 5 rotates, and each piston 9 reciprocates in the first cylinder bore 21a and the second cylinder bore 23a. For this reason, the first and second compression chambers 53a and 53b change in volume according to the piston stroke. Therefore, in this compressor, the suction stroke for sucking the refrigerant gas into the first and second compression chambers 53a and 53b, the compression stroke for compressing the refrigerant gas in the first and second compression chambers 53a and 53b, and the compression are performed. The discharge stroke and the like in which the refrigerant gas is discharged into the first and second discharge chambers 29a and 29b are repeatedly performed.

  The refrigerant gas discharged into the first discharge chamber 29 a reaches the merged discharge chamber 231 through the first discharge communication path 18. Similarly, the refrigerant gas discharged into the second discharge chamber 29 b reaches the merged discharge chamber 231 through the second discharge communication path 20. Then, the refrigerant gas reaching the merged discharge chamber 231 is discharged from the discharge port 230 to the condenser via the pipe.

  During these suction strokes and the like, a piston compression force that reduces the inclination angle of the swash plate 5 acts on the rotating body including the swash plate 5, the ring plate 45, the lug arm 49, and the first pin 47a. If the inclination angle of the swash plate 5 is changed, it is possible to perform capacity control by increasing or decreasing the stroke of the piston 9.

  Specifically, in the control mechanism 15 shown in FIG. 3, if the control valve 15c reduces the opening degree of the extraction passage 15a, the pressure in the pressure adjustment chamber 31 increases due to the pressure of the refrigerant gas in the second discharge chamber 29b. As a result, the pressure in the control pressure chamber 13c increases. For this reason, the variable differential pressure, which is the differential pressure between the control pressure chamber 13c and the swash plate chamber 33, increases. Thereby, in the actuator 13, the moving body 13a moves from the position shown in FIGS. 1 and 5 toward the rear side in the swash plate chamber 33 against the piston compression force acting on the swash plate 5, and FIG. As shown in FIG. 6, it enters the second recess 23c.

  As a result, as shown in FIG. 2, in this compressor, the moving body 13 a moves the swash plate 5 through the traction arm 132 in the swash plate chamber 33 through the pulling arms 132 at the action axis M <b> 3 while resisting the urging force of the inclination reducing spring 44 b. Pull backwards. For this reason, in this compressor, the swash plate 5 swings counterclockwise around the action axis M3. The rear end of the lug arm 49 swings clockwise around the first swing axis M1, and the front end of the lug arm 49 swings clockwise around the second swing axis M2. For this reason, the front end side of the lug arm 49 moves rearward from the first flange 430 of the first support member 43a. As a result, the swash plate 5 swings with the action axis M3 and the first swing axis M1 as the action point and the fulcrum, respectively, and the inclination angle of the swash plate 5 with respect to the drive axis O of the drive shaft 3 increases. For this reason, in this compressor, the stroke of each piston 9 increases and the discharge capacity per rotation of the drive shaft 3 increases.

  FIG. 2 shows a state where the inclination angle of the swash plate 5 is at the maximum value. The position of the moving body 13a shown in FIG. 6 corresponds to the state where the inclination angle of the swash plate 5 shown in FIG. 2 is at the maximum value. On the other hand, FIG. 1 shows a state where the inclination angle of the swash plate 5 is at the minimum value. The position of the moving body 13a shown by the solid line in FIG. 5 corresponds to the state where the inclination angle of the swash plate 5 shown in FIG. 1 is at the minimum value.

  Here, as shown in FIGS. 5 and 6, the portion of the rear wall 130 of the moving body 13 a where the insertion hole 130 a is formed projects rearward in a cylindrical shape, and the rear end surface of the cylindrical portion is a pressing portion. 139. In the state where the inclination angle of the swash plate 5 is at the maximum value shown in FIG. 2, as shown in FIG. 6, the pressing portion 139 of the moving body 13a presses the second flange 431 of the second support member 43b rearward. In this state, the pressing portion 139 is displaced rearward from the stepped portion 30c, and makes the second support member 43b remote from the stepped portion 30c rearward. That is, the second support member 43 b regulates the maximum value of the inclination angle of the swash plate 5. As indicated by a two-dot chain line in FIG. 5, in a state where the moving body 13 moves forward and the pressing portion 139 is in a position that coincides with the stepped portion 30 c, the pressing portion 139 is the second flange 431 of the second support member 43 b. Will not be pushed backwards. In this state, the second support member 43b abuts on the stepped portion 30c, and forward displacement is restricted. As shown by a solid line in FIG. 5, the pressing portion 139 moves away from the second flange 431 of the second support member 43b when displaced to the front side of the step portion 30c. Even in this state, the second support member 43b abuts on the stepped portion 30c, and the forward displacement is restricted.

  In this compressor, a predetermined angle smaller than the maximum value and larger than the minimum value is defined for the inclination angle of the swash plate 5. As shown by a two-dot chain line in FIG. 5, the predetermined angle is in a position where the pressing portion 139 of the moving body 13a coincides with the step portion 30c, that is, in a position where the pressing portion 139 cannot press the second support member 43b. The inclination angle of the swash plate 5 at.

  In this compressor, when the inclination angle of the swash plate 5 increases from a predetermined angle to the maximum value, the second flange 431 of the second support member 43b pressed by the pressing portion 139 is the second of the second thrust bearing 35b. The inner peripheral edge side of the race 355 is pressed toward the rear wall side of the second recess 23c. Therefore, as shown in FIG. 6, the second thrust bearing 35 b is gradually and strongly pressed by the second flange 431, and a preload that is gradually larger than a predetermined preload that is set in advance is applied. For this reason, in this compressor, as the discharge capacity approaches the maximum capacity, the second thrust bearing 35b is deformed into a disc spring shape, and the compressor acting on the drive shaft body 30 with gradually strong support force is deformed. Support thrust force toward the rear side.

  Further, the second support member 43b moves the second small diameter portion 30b toward the rear of the drive shaft 3, whereby the second support member 43b and the first support member 43a are separated from each other, and the first flange 430 is moved forward. Move towards. Therefore, as shown in FIG. 7, the first thrust bearing 35a is gradually and strongly pressed by the first flange 430, and a preload which is gradually larger than a predetermined preload set in advance is applied. For this reason, in this compressor, as the discharge capacity approaches the maximum capacity, the first thrust bearing 35a is deformed into a disc spring shape, and the compressor shaft acting on the drive shaft main body 30 with gradually strong support force. Support thrust force toward the front side.

  When the inclination angle of the swash plate 5 is at the maximum value, as shown in FIG. 7, the first thrust bearing 35a is more strongly pressed by the first flange 430, and as shown in FIG. 6, the second thrust bearing 35b is The second flange 431 is more strongly pressed. As a result, the preload of the first and second thrust bearings 35a and 35b is maximized. For this reason, when the discharge capacity is the maximum, the first and second thrust bearings 35a and 35b are greatly deformed into a disc spring shape, and act on the drive shaft main body 30 and thus the drive shaft 3 with a stronger support force. Supports the thrust force. 6 and 7 exaggerate the deformation of the first and second thrust bearings 35a and 35b for easy explanation.

  On the other hand, in the control mechanism 15 shown in FIG. 3, if the control valve 15c increases the opening degree of the extraction passage 15a, the pressure in the pressure adjusting chamber 31 and the pressure in the control pressure chamber 13c are increased in the second suction chamber 27b. It becomes almost equal to the pressure, and the variable differential pressure becomes small. Therefore, due to the piston compression force acting on the swash plate 5, the moving body 13 a moves toward the front side of the swash plate chamber 33 in the actuator 13 as shown in FIG. 1.

  As a result, in this compressor, the swash plate 5 is urged in the direction in which the inclination angle decreases by the compression reaction force acting on the swash plate 5 via each piston 9, and each traction arm 132 is applied at the action axis M <b> 3. Through this, the moving body 13a is pulled to the front side of the swash plate chamber 33, and the ring plate 45 contacts the rear end of the return spring 44a. Then, the movable body 13a is pulled to the front side of the swash plate chamber 33, and in this compressor, the swash plate 5 is swung clockwise around the action axis M3 while resisting the urging force of the return spring 44a. Move. Further, the rear end of the lug arm 49 swings counterclockwise around the first swing axis M1, and the front end of the lug arm 49 swings counterclockwise around the second swing axis M2. For this reason, the front end side of the lug arm 49 approaches the first flange 430 of the first support member 43a. As a result, the swash plate 5 swings in the opposite direction to the case where the inclination angle increases with the action axis M3 as the action point and the first swing axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 5 with respect to the drive axis O of the drive shaft 3 decreases, and the stroke of each piston 9 decreases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 becomes small.

  Moreover, in this compressor, the centrifugal force which acted on the weight part 49a is also given to the swash plate 5. For this reason, in this compressor, it is easy to displace the swash plate 5 in the direction to reduce the inclination angle.

  In this compressor, the inclination angle of the swash plate 5 is reduced and the stroke of each piston 9 is reduced, so that the top dead center position of each second head 9 b is remote from the second valve forming plate 41. For this reason, in this compressor, when the inclination angle of the swash plate 5 approaches zero degrees, the compression work is slightly performed on the first compression chamber 53a side, while the compression work is performed on the second compression chamber 53b side. Disappear.

  Here, when the inclination angle of the swash plate 5 decreases from the maximum value to a predetermined angle, the moving body 13a moves from the position shown in FIG. 6 to the front end side of the drive shaft main body 30. Thereby, the 2nd support member 43b contact | abutted with the press part 139 of the moving body 13a also moves to the front-end side of the 2nd small diameter part 30b with the restoring force of the 2nd thrust bearing 35b. For this reason, since the 2nd flange 431 presses the 2nd thrust bearing 35b weakly compared with when the inclination-angle of the swash plate 5 has the maximum value, the preload added to the 2nd thrust bearing 35b decreases. At this time, the distance between the second support member 43b and the first support member 43a is shortened, and the first flange 430 also presses the first thrust bearing 35a weakly, so the preload applied to the first thrust bearing 35a is also reduced. .

  When the inclination angle of the swash plate 5 decreases to a predetermined angle, the moving body 13a moves to the position indicated by the two-dot chain line in FIG. 5, and the front end of the second flange 431 contacts the step portion 30c of the drive shaft main body 30. Touch. Thereby, the step part 30c restrict | limits the 2nd support member 43b moving toward the front-end side of the drive shaft main body 30 exceeding the 2nd small diameter part 30b. As a result, when the inclination angle of the swash plate 5 decreases from a predetermined angle, the moving body 13a is separated from the second support member 43b, and further toward the front end side of the drive shaft main body 30 as shown by the solid line in FIG. Moving. At this time, as described above, since the movement of the second support member 43b is restricted by the step portion 30c, the state in which the second flange 431 presses the second thrust bearing 35b weakly is maintained. Further, the state in which the first flange 430 presses the first thrust bearing 35a weakly is also maintained. Thus, in this compressor, when the discharge capacity is reduced, the preload applied to the first and second thrust bearings 35a and 35b is reduced as compared with the state where the discharge capacity is the maximum capacity.

  Thus, in this compressor, the preload applied to the first and second thrust bearings 35a and 35b increases when the discharge capacity is increased. For this reason, in this compressor, even if it operates with a large discharge capacity, the first and second thrust bearings 35a and 35b can favorably support the drive shaft 3 and suppress vibration and noise. Further, in this compressor, when the discharge capacity is reduced, the preload applied to the first and second thrust bearings 35a and 35b is reduced. Therefore, in this compressor, the first and second thrust bearings 35a and 35b can favorably support the drive shaft 3 and suppress vibration and noise during operation with a small discharge capacity. Further, in this compressor, drag resistance acting on the drive shaft 3 from the first and second thrust bearings 35a and 35b when the discharge capacity is reduced can be reduced.

  Therefore, the compressor of the embodiment can suppress vibration and noise while reducing power loss. Further, in this compressor, the durability of the first and second thrust bearings 35a and 35b is increased compared to the case where the preload applied to the first and second thrust bearings 35a and 35b does not change regardless of the increase or decrease of the discharge capacity. can do.

  In particular, in this compressor, as shown in FIG. 6, the second support member 43 b regulates the maximum inclination angle of the swash plate 5. For this reason, in this compressor, the maximum preload applied to the first and second thrust bearings 35a and 35b is maximized when the inclination angle is maximized, and vibration and noise are suitably suppressed when operating at the maximum discharge capacity. can do.

  Further, in this compressor, as shown in FIGS. 4 and 7, the first thrust bearing 35 a contacts the front wall of the first recess 21 c only on the outer peripheral side of the first race 351, It is in contact with the first flange 430 only on the peripheral side. Similarly, as shown in FIGS. 5 and 6, the second thrust bearing 35 b is in contact with the rear wall of the second recess 23 c only on the outer peripheral side of the first race 354 and only on the inner peripheral edge of the second race 355. 2 is in contact with the flange 431. For this reason, in this compressor, when the second flange 431 strongly presses the second thrust bearing 35b, the first and second thrust bearings 35a and 35b are easily elastically deformed in the shape of a disc spring, respectively. Each acting thrust force can be suitably supported.

  While the present invention has been described with reference to the embodiments, it is needless to say that the present invention is not limited to the above-described embodiments and can be appropriately modified and applied without departing from the spirit thereof.

  For example, another member that can contact both of the movable body 13a and the second flange 43b is provided, and the movable body 13a contacts the second flange 431 via this separate member, and the second support member 43b. It is good also as a structure which presses indirectly. In addition, when such another member is provided, the second support member 43b indirectly regulates the maximum value of the inclination angle of the swash plate 5 by contacting the moving body 13a via the separate member. May be.

  The first and second concave surfaces 21d and 23d are not formed, the first race 351 of the first thrust bearing 35a is in contact with the front wall of the first recess 21c over the entire surface, and the first race 354 of the second thrust bearing 35b is over the entire surface. It is good also as a structure contact | abutted by the rear wall of the 2nd recessed part 21c. Further, only one of the first concave surface 21d and the second concave surface 23d may be formed.

  The control mechanism 15 may be configured such that a control valve 15c is provided for the air supply passage 15b and an orifice 15d is provided in the extraction passage 15a. In this case, the opening degree of the supply passage 15b can be adjusted by the control valve 15c. As a result, the control pressure chamber 13b can be quickly increased in pressure by the pressure of the refrigerant gas in the second discharge chamber 29b, and the discharge capacity can be increased rapidly.

  In the compressor of the embodiment, the piston 9 is a double-headed piston, but is not limited to this configuration. The present invention can also be applied to a variable displacement swash plate compressor that employs a single-headed piston.

  The present invention can be used for an air conditioner or the like.

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 5 ... Swash plate 7 ... Link mechanism 9 ... Piston 9a ... 1st head 9b ... 2nd head 11a, 11b ... Shoe (conversion mechanism)
DESCRIPTION OF SYMBOLS 13 ... Actuator 13a ... Moving body 13b ... Partition body 13c ... Control pressure chamber 15 ... Control mechanism 21 ... 1st cylinder block 21a ... 1st cylinder bore 23 ... 2nd cylinder block 23a ... 2nd cylinder bore 27a ... 1st suction chamber 27b ... 2nd suction chamber 29a ... 1st discharge chamber 29b ... 2nd discharge chamber 30 ... Drive shaft main body 30c ... Step part (regulation part)
33 ... Swash plate chamber 43a ... First support member 43b ... Second support member (support member)
O ... Drive shaft center 35a, 35b ... Thrust bearing (35a ... First thrust bearing, 35b ... Second thrust bearing)

Claims (3)

A housing having a swash plate chamber and a cylinder block in which a cylinder bore is formed; a drive shaft rotatably supported by the housing; a swash plate rotatable in the swash plate chamber by rotation of the drive shaft; and the drive A link mechanism that is provided between the shaft and the swash plate and allows the inclination angle of the swash plate to be changed with respect to a direction orthogonal to the drive axis of the drive shaft; and a piston that is housed in the cylinder bore so as to be reciprocally movable A conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the inclination angle by rotation of the swash plate, an actuator capable of changing the inclination angle, and a control mechanism for controlling the actuator. Prepared,
The actuator is provided with a partition provided on the drive shaft, a connecting portion connected to the swash plate, a movable body movable in the direction of the drive axis in the swash plate chamber, the partition and the A control pressure chamber that is partitioned by the moving body and moves the moving body so that the inclination angle is increased by introducing the refrigerant into the inside,
A support member that is inserted through the drive shaft and is movable in the direction of the drive shaft along with the movement of the movable body;
Between the support member and the cylinder block, a thrust bearing that supports a thrust force acting on the drive shaft is provided,
A variable displacement swash plate compressor, wherein the drive shaft is provided with a restricting portion for restricting the support member from moving toward the movable body at least when the inclination angle is minimum.   The capacity-variable swash plate compressor according to claim 1, wherein the support member regulates a maximum value of the tilt angle. The support member has an annular shape around the drive axis;
The thrust bearing has a first race, a second race, and a rolling element sandwiched between the first race and the second race,
3. The variable displacement swash plate compressor according to claim 1, wherein an outer peripheral edge side of the first race is in contact with the cylinder block, and an inner peripheral edge side of the second race is in contact with the support member.

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