JP2017096161A - Variable displacement-type swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement-type swash plate compressor capable of exerting high durability.SOLUTION: A compressor has a top dead center corresponding portion T on a swash plate 5. Further in the compressor, a virtual face D is defined. A moving body 13a is connected to the swash plate 5 through a connection mechanism 14. The connection mechanism 14 has a first arm 131 and a second arm 132 disposed over the virtual face D, a towed portion 45c connected to the first arm 131 and the second arm 132, and a third pin 47c as a connection shaft. A first supporting hole 131a is formed on the first arm 131, and a second supporting hole 132a is formed on the second arm 132. A third supporting hole 450 is formed on the towed portion 45c. The third supporting hole 450 is provided with a first cylindrical portion 450a and a second cylindrical portion 450b. The first cylindrical portion 450a is disposed on a position farther from the first supporting hole 131a with respect to the second cylindrical portion 450b.SELECTED DRAWING: Figure 7

Description

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

  1 and 3 of Patent Document 1 disclose a conventional variable displacement swash plate compressor (hereinafter simply referred to as a compressor). In this compressor, a housing is formed by the cylinder block, the first housing, and the second housing. The first housing is disposed in front of the compressor, and the second housing is disposed behind the compressor. The cylinder block is disposed between the first housing and the second housing. The cylinder block is formed with a plurality of cylinder bores and a swash plate chamber. A drive shaft is rotatably supported on the housing. In the swash plate chamber, there is provided a swash plate that can be rotated by the rotation of the drive shaft. A link mechanism is provided between the drive shaft and the swash plate. The link mechanism allows a change in the inclination angle of the swash plate. Here, the inclination angle is an angle of the swash plate with respect to a direction orthogonal to the rotation axis of the drive shaft. In each cylinder bore, a piston is accommodated so as to be able to reciprocate. The pair of shoes for each piston, as a conversion mechanism, reciprocates each piston within the cylinder bore with a stroke corresponding to the inclination angle by the rotation of the swash plate. The drive shaft is provided with a moving body that moves in the direction of the rotation axis and changes the tilt angle. A control pressure chamber is defined between the moving body and the cylinder block. The pressure in the control pressure chamber is controlled by a control mechanism.

  The swash plate is formed with a top dead center corresponding portion that positions each piston at the top dead center. In this compressor, a virtual plane including a top dead center corresponding part and a rotation axis is defined.

  The swash plate is formed with first and second front arms extending toward the first housing. The first front arm and the second front arm are disposed across the virtual plane. On the other hand, a lug arm is fixed to the drive shaft at a location closer to the first housing than the swash plate. The first and second front arms and the lug arm are connected by the first connecting shaft. Thereby, the swash plate and the lug arm are connected. A link mechanism is formed by the first and second front arms and the first connecting shaft.

  Further, the swash plate and the moving body are connected by a connecting mechanism. The connection mechanism is composed of first and second rear arms formed on a swash plate and extending toward the second housing, a traction portion formed on the moving body, and a second connection shaft. Both the first rear arm and the second rear arm are disposed across the virtual plane. The first rear arm is located upstream of the second rear arm with respect to the virtual plane in the rotation direction of the swash plate. The traction portion is formed so as to be positioned between the first rear arm and the second rear arm. When the second connecting shaft is inserted through the first rear arm, the second rear arm, and the connecting portion, the connecting mechanism connects the swash plate and the moving body.

  In this compressor, for example, when the control mechanism increases the pressure in the control pressure chamber by the pressure of the refrigerant in the discharge chamber, the moving body moves in the direction of the rotation axis toward the first housing side. This increases the inclination angle of the swash plate. Thus, in this compressor, the discharge capacity per rotation of the drive shaft is increased.

JP-A-5-172052

  By the way, in this type of compressor, a compression reaction force acts on each swash plate from each piston during operation. This compression reaction force acts on the upstream side of the rotation direction with respect to the virtual plane in the rotation direction of the swash plate. For this reason, a moment is applied to the swash plate to cause the swash plate to bend around a direction perpendicular to the rotational axis of the drive shaft. Thereby, in the said conventional compressor, the location where the traction part of a moving body and a 2nd connection shaft contact is closer to the 1st rear arm side rather than the 2nd rear arm side. Therefore, in this compressor, when the moving body pulls the swash plate when changing the tilt angle, the load on the first rear arm side becomes larger than that on the second rear arm side. For this reason, in this compressor, the first rear arm is easily broken. For this reason, this compressor has low durability.

  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 exhibiting high durability.

A variable capacity swash plate compressor of the present invention includes a housing in which a swash plate chamber and a plurality of cylinder bores are formed,
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the rotational axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the rotational axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
The swash plate is formed with a top dead center corresponding portion for positioning each piston at a top dead center,
A virtual plane including the upper point corresponding part and the rotation axis is defined,
The moving body is connected to the swash plate via a connection mechanism, and the inclination pressure is increased by pulling the swash plate by increasing the pressure in the control pressure chamber,
The coupling mechanism is provided on the movable body, and is provided on the swash plate between a first arm and a second arm arranged across the virtual plane, and between the first arm and the second arm. A towed portion that is positioned, and a connecting shaft that is inserted through the first arm, the second arm, and the towed portion and connects the first arm, the second arm, and the towed portion by one. And
The first arm is located upstream of the second arm with respect to the virtual plane in the rotation direction of the swash plate,
A first support hole for supporting the connecting shaft is formed in the first arm,
The second arm is formed with a second support hole for supporting the connecting shaft,
The to-be-towed part is formed with a third support hole for supporting the connecting shaft,
A small diameter portion having a first inner diameter and a large diameter portion having a second inner diameter larger than the first inner diameter are formed in the third support hole,
The small diameter portion is arranged at a position farther from the first support hole than the large diameter portion.

  In the compressor according to the present invention, the first support hole, the second support hole, and the third support hole each support the connecting shaft when the movable body pulls the swash plate to increase the inclination angle. Here, a small diameter portion having a first inner diameter and a large diameter portion having a second inner diameter are formed in the third support hole. Since the second inner diameter is larger than the larger inner diameter, the small diameter portion comes into contact with the connecting shaft in the third support hole. The small diameter portion is disposed at a position farther from the first support hole than the large diameter portion. For this reason, in this compressor, the location where the small diameter portion comes into contact with the connecting shaft, that is, the location where the third support hole supports the connecting shaft moves away from the first support hole, and approaches the second support hole accordingly. For this reason, in this compressor, the load acting on the first arm when the movable body pulls the swash plate is reduced by the amount that the portion where the third support hole supports the connecting shaft is away from the first support hole. . On the other hand, the load acting on the second arm when the movable body pulls the swash plate is increased by the amount that the third support hole supports the connecting shaft approaches the second support hole. Thereby, in this compressor, when the moving body pulls the swash plate, the load acting on the first arm and the load acting on the second arm can be balanced. For this reason, in this compressor, the first arm is difficult to break.

  Therefore, the compressor of the present invention exhibits high durability.

  In particular, in this compressor, as described above, when the moving body pulls the swash plate, the load acting on the first arm side and the load acting on the second arm side can be balanced. For this reason, in this compressor, when the inclination angle of the swash plate is changed, the moving body can smoothly move in the direction of the rotation axis of the drive shaft, and the inclination angle of the swash plate can be suitably changed. For this reason, in this compressor, controllability can be improved.

  In the third support hole, a stepped portion is preferably formed between the small diameter portion and the large diameter portion. In this case, the connecting shaft contacts the step portion, and the third support hole supports the connecting shaft at the step portion. For this reason, by adjusting the position where the step is formed in the third support hole, it is possible to adjust the distance when the portion where the third support hole supports the connecting shaft is moved away from the first support hole. Become.

  It is preferable that a chamfer is formed on the stepped portion. In this case, it is possible to suppress the occurrence of chipping or the like in the step portion when the step portion and the connecting shaft come into contact with each other.

  The compressor of the present invention exhibits high durability.

FIG. 1 is a cross-sectional view showing a state where the inclination angle is minimum in the compressor of the first embodiment. FIG. 2 is a cross-sectional view showing a state where the inclination angle is maximum in the compressor of the first embodiment. FIG. 3 is a schematic diagram illustrating a control mechanism according to the compressor of the first embodiment. FIG. 4 shows a swash plate in the compressor of the first embodiment. FIG. (A) is a front view of the swash plate. FIG. (B) is a sectional view of the swash plate. FIG. 5 is an enlarged cross-sectional view of a main part showing a YY cross section in FIG. 4 related to the swash plate in the compressor of Embodiment 1. FIG. 6 is a top view illustrating the moving body in the compressor according to the first embodiment. FIG. 7 is a schematic cross-sectional view illustrating the XX cross section in FIG. 1 according to the compressor of the first embodiment. FIG. 8 is a cross-sectional view showing the ZZ cross section in FIG. 7 according to the compressor of the first embodiment. FIG. 9 is a cross-sectional view showing a cross section in the same direction as FIG. 8, showing a state where the moving body is pulling the swash plate, according to the compressor of the first embodiment. FIG. 10 is a cross-sectional view showing a cross section in the same direction as FIG. 8 showing a state in which the moving body is pulling the swash plate in the compressor of the comparative example. FIG. 11 is an enlarged cross-sectional view of a main part showing a cross section in the same direction as FIG. FIG. 12 is an enlarged cross-sectional view of a main part showing a cross section in the same direction as FIG. FIG. 13 is an enlarged cross-sectional view of a main part showing a cross section in the same direction as FIG. FIG. 14 is an enlarged cross-sectional view of a main part showing a cross section in the same direction as FIG.

  Hereinafter, Embodiments 1 to 5 embodying the present invention will be described with reference to the drawings. All of these compressors are mounted on a vehicle, and constitute a refrigeration circuit of a vehicle air conditioner.

Example 1
As shown in FIGS. 1 and 2, the compressor of the first 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 of shoes 11a and 11b. And an actuator 13. 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. 1 and 2 is defined as the upper side of the compressor, and the lower side of the page is defined as the lower side of the compressor to define the vertical direction of the compressor. In FIG. 4 and subsequent figures, the front-rear direction, the up-down direction, and the left-right direction are displayed in correspondence with FIGS. Further, the vertical direction is defined as a first direction D1. In addition, the front-back direction etc. in Example 1 are examples. The mounting posture of the compressor of the present invention is appropriately changed in accordance with the vehicle or the like to be mounted.

  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 29a is also formed in an annular shape and is located on the outer peripheral side of the first suction chamber 27a.

  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. The second discharge chamber 29b is also formed in an annular shape and is located on the outer peripheral side of the second suction chamber 27b.

  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 rotation axis O. These 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 21b from the rear side of the compressor. The first recess 21c is coaxial with the first shaft hole 21b. The first recess 21c has an inner diameter larger than that of the first shaft hole 21b. A first thrust bearing 35a is provided in the first recess 21c.

  The first cylinder block 21 is provided with a first retainer groove 21d that restricts the maximum opening of each first suction reed valve 391a, which will be described later. Further, the first cylinder block 21 is formed with a first communication path 37a and a second front side communication path 18b. 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 swash plate chamber 33 communicates with the first communication path 37a.

  The second cylinder block 23 is formed with a plurality of second cylinder bores 23a extending in the direction of the rotation axis O. Like the first cylinder bores 21a, the second cylinder bores 23a are arranged at equiangular intervals in the circumferential direction, and are coaxially and 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 23a have made a pair, these numbers can be designed suitably. Moreover, you may form in the magnitude | size of a different diameter in each 1st cylinder bore 21a and each 2nd cylinder bore 23a. Furthermore, the axial centers of the paired first cylinder bore 21a and second cylinder bore 23a may be coaxial or may be shifted.

  The second cylinder block 23 is formed with 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 22b. The second recess 23c has an inner diameter larger than that of the second shaft hole 22b. 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. A second thrust bearing 35b is provided in the second recess 23c.

  Further, the second cylinder block 23 is provided with a second retainer groove 23d that restricts the maximum opening of each second suction reed valve 411a described later. Further, the second cylinder block 23 includes a discharge port 230, a merged discharge chamber 231, a third front communication path 18c, a second rear communication path 20b, a suction port 330, and a second communication path 37b. Is 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. Thereby, the swash plate chamber 33 communicates with the second communication path 37b.

  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 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, 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 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 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, 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, a first support member 43a, and a second support member 43b. 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. The drive shaft body 30 is inserted into the shaft seal device 25 and the first and second sliding bearings 22a and 22b in the housing 1. As a result, the drive shaft body 30, and hence the drive shaft 3, is supported by the housing 1, and can rotate around the rotation axis O parallel to the front-rear direction of the compressor. The rotation axis O and the first direction D1 are orthogonal to each other. Further, the drive shaft main body 30 is supported by the housing 1, whereby the front end of the drive shaft main body 30 is inserted into the shaft seal device 25 in the boss 17 a. 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 having the rotation axis O as a central axis. The first support member 43a is press-fitted into the first small diameter portion 30a of the drive shaft main body 30, and is supported by the first sliding bearing 22a in the first shaft hole 21b. A first flange 430 is formed on the rear end side of the first support member 43a, and an attachment portion (not shown) through which a second pin 47b described later is inserted is formed. The first flange 430 sandwiches the first thrust bearing 35a from the axial direction between the first flange 430 and the front wall of the first recess 21c.

  Further, the front end of the return spring 44a is inserted through the first support member 43a. The return spring 44a extends in the direction of the rotation axis O from the first flange 430 side toward the swash plate 5 side.

  The second support member 43b is also formed in a cylindrical shape with the rotation axis O as the central axis. The second support member 43b is press-fitted to the rear end side of the second small diameter portion 30b of the drive shaft main body 30, and is supported by the second sliding bearing 22b in the second shaft hole 23b. A second flange 431 is formed at the front end of the second support member 43b. The second flange 431 sandwiches the second thrust bearing 35b from the axial direction between the second flange 431 and the rear wall of the second recess 23c.

  In the second support member 43b, O-rings 51a and 51b are provided at positions closer to the rear end side than the second flange 431. These O-rings 51a and 51b seal between the pressure adjustment chamber 31 and the second recess 23c, and thus between the pressure adjustment chamber 31 and the swash plate chamber 33.

  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. As shown in FIG. 4, the swash plate 5 is formed with a top dead center corresponding portion T and a bottom dead center corresponding portion U. Here, the top dead center corresponding part T positions the first head 9a described later at the top dead center in each piston 9 shown in FIG. On the other hand, the bottom dead center corresponding unit U positions the first head 9a at the bottom dead center. As shown in FIG. 4, in this compressor, a virtual plane D including a top dead center corresponding portion T, a bottom dead center corresponding portion U, and a rotation axis O is defined.

  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 45a in the swash plate chamber 33 (see FIG. 1).

  Moreover, as shown to (A) of FIG. 4, the groove part 45b is formed in the location which becomes the top dead center corresponding | compatible part T side in the ring plate 45. As shown in FIG. As shown in FIG. 5B, the groove 45b penetrates from the front surface 5a to the rear surface 5b of the swash plate 5. On the other hand, in the ring plate 45, a to-be-towed portion 45c is formed at a location on the bottom dead center corresponding portion U side. Only one to-be-towed portion 45c is formed on the ring plate 45 so as to be positioned between first and second arms 131 and 132, which will be described later, and protrudes toward the rear of the swash plate 5.

  As shown in FIG. 5, a third support hole 450 is provided in the to-be-towed portion 45c. The third support hole 450 extends in a second direction D2 orthogonal to the virtual plane D. The third support hole 450 includes a first cylindrical portion 450a and a second cylindrical portion 450b that are coaxial with each other. The first cylindrical portion 450a has a first inner diameter L1, and the second cylindrical portion 450b has a second inner diameter L2. The second inner diameter L2 is set to be larger than the first inner diameter L1, and the second cylindrical portion 450b is formed to have a larger diameter than the first cylindrical portion 450a. The first cylindrical portion 450a corresponds to the small diameter portion in the present invention, and the second cylindrical portion 450b corresponds to the large diameter portion in the present invention. The first cylindrical portion 450a extends from the axial center side of the third support hole 450 toward the other side in the second direction D2. The second cylindrical portion 450b extends from the central side in the axial direction of the third support hole 450 toward one side in the second direction D2 while being continuous with the first cylindrical portion 450a. Accordingly, as shown in FIG. 8, the first cylindrical portion 450a opens toward the second support hole 132a, and the second cylindrical portion 450b opens toward the first support hole 131a. Here, since the second cylindrical portion 450b has a larger diameter than the first cylindrical portion 450a, in the third support hole 450, the first support hole 131a side is opened larger than the second support hole 132a side. Details of the first and second support holes 131a and 132a will be described later.

  As shown in FIG. 5, a step portion 451 is formed at the boundary between the first cylindrical portion 450 a and the second cylindrical portion 450 b in the third support hole 450. The step portion 451 is located at the approximate center of the third support hole 450 in the axial direction. As shown in FIG. 8, the stepped portion 451 has a shape protruding toward the third pin 47 c inserted through the third support hole 450. Further, as shown in FIG. 5, a curved surface 451a as a chamfer is formed in the step portion 451.

  As shown in FIG. 1, 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. Further, a weight portion 49 a is formed on the rear end side of the lug arm 49. The weight portion 49a extends approximately half a circumference in the circumferential direction 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. The first pin 47a extends in the second direction D2. 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 the second direction D2.

  The front end side of the lug arm 49 is connected to the first support member 43a by the second pin 47b. The second pin 47b also extends in the second direction D2. 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. In addition to the lug arm 49 and the first and second pins 47a and 47b, the first and second arms 131 and 132 and the third pin 47c, which will be described later, constitute the link mechanism 7 in the present invention.

  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 rotation 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 has a first head 9 a on the front end side and a second head 9 b on the rear end side. That is, each piston 9 is a double-headed piston. Each first head portion 9a is accommodated in each first cylinder bore 21a so as to reciprocate. The first compression chambers 53a are formed in the first cylinder bore 21a by the first heads 9a and the first valve forming plate 39, respectively. Each of the second heads 9b is housed so as to reciprocate within the second cylinder bore 23a. The second compression chambers 53b are formed in the second cylinder bores 23a by the second heads 9b and the second valve forming plate 41, respectively.

  In addition, an engaging portion 9 c is formed at the center of each piston 9. In each engaging portion 9c, hemispherical shoes 11a and 11b are provided. The rotation of the swash plate 5 is converted into the reciprocating motion of the piston 9 by these shoes 11a and 11b. The shoes 11a and 11b correspond to the conversion mechanism in the present invention. Thus, the first heads 9a can reciprocate in the first cylinder bores 21a with a stroke corresponding to the inclination angle of the swash plate 5, and the second heads 9b are secondly moved. It is possible to reciprocate within the cylinder bore 23a.

  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. More specifically, the actuator 13 is located behind the swash plate 5 in the swash plate chamber 33, that is, the actuator 13 is located on the second cylinder block 23 side with respect to the swash plate 5 in the swash plate chamber 33. ing. Thereby, the actuator 13 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.

  As shown in FIG. 6, the moving body 13 a includes a moving body main body 130, a first arm 131, and a second arm 132. As shown in FIGS. 1 and 2, the movable body main body 130 has a rear wall 133 and a peripheral wall 134. The rear wall 133 is located behind the movable body 13a and extends in a radial direction in a direction away from the rotation axis O. In addition, an insertion hole 130 a through which the second small diameter portion 30 b of the drive shaft main body 30 is inserted is provided in the rear wall 133. An O-ring 51c is provided in the insertion hole 130a. The peripheral wall 134 is continuous with the outer peripheral edge of the rear wall 133 and extends toward the front of the movable body 13a. Due to the rear wall 133 and the peripheral wall 134, the movable body main body 130 has a bottomed cylindrical shape.

  As shown in FIG. 6, the first arm 131 and the second arm 132 are both formed at the front end of the peripheral wall 134 and extend from the movable body 130 toward the front of the compressor. The 1st arm 131 and the 2nd arm 132 are arrange | positioned across the virtual surface D of the swash plate 5 in the mobile body 13a, providing a fixed space | interval. Specifically, the first arm 131 is formed on one side in the second direction D2 with respect to the virtual plane D of the swash plate 5 at the front end of the peripheral wall 134. The second arm 132 is formed at the front end of the peripheral wall 134 on the other side in the second direction D2 with respect to the virtual plane D of the swash plate 5.

  The first arm 131 is formed with a cylindrical first support hole 131a extending in the second direction D2. The first support hole 131a passes through the first arm 131 in the second direction D2, and both end surfaces of the first support hole 131a are open. The second arm 132 is formed with a cylindrical second support hole 132a extending in the second direction D2 of the compressor. The second support hole 132a also passes through the second arm 132 in the second direction D2, and both end surfaces of the second support hole 132a are open. The first support hole 131a and the second support hole 132a are formed to have the same diameter and are coaxial.

  As shown in FIGS. 1 and 2, the partition body 13 b is formed in a disk shape having substantially the same diameter as the inner diameter of the moving body main body 130. The partition 13b has an insertion hole 136 extending through the center. An O-ring 51d is provided on the outer periphery of the partition 13b.

  The second small diameter portion 30b of 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 rotation axis O. On the other hand, the 2nd small diameter part 30b is press-fit with respect to the insertion hole 136 of the division body 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 second small diameter portion 30b so as to be movable in the direction of the rotation axis O.

  The partition 13b is disposed in the mobile body 130 and is surrounded by the peripheral wall 134. Thereby, when the moving body 13a moves to the rotation axis O direction, the inner peripheral surface of the peripheral wall 134 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 134. As shown in FIG. The control pressure chamber 13c is partitioned from the swash plate chamber 33 by the rear wall 133, the peripheral wall 134, and the partition body 13b.

  As shown in FIGS. 7 and 8, the moving body 13 a and the swash plate 5 are connected by a connecting mechanism 14. The connection mechanism 14 includes a first arm 131, a second arm 132, a to-be-towed portion 45c, and a third pin 47c. The third pin 47c is a cylindrical shaft body. The third pin 47c corresponds to the connecting shaft in the present invention. In connecting the movable body 13 a and the swash plate 5, the towed portion 45 c of the swash plate 5 is disposed between the first arm 131 and the second arm 132. And the 3rd pin extended in the 2nd direction D2 with respect to the 1st support hole 131a of the 1st arm 131, the 2nd support hole 132a of the 2nd arm 132, and the 3rd support hole 450 of the to-be-towed part 45c. 47c is inserted in the axial direction. Thus, the first arm 131, the second arm 132, and the to-be-towed portion 45c are connected by the single third pin 47c, and the movable body 13a and the swash plate 5 are connected. Thereby, as shown in FIGS. 1 and 2, 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.

  Although not shown, circlips are attached to both ends of the third pin 47c in the axial direction to prevent the third pin 47c from dropping off from the first support hole 131a and the second support hole 132a. Yes. Note that the third pin 47c may be prevented from dropping from the first support hole 131a and the second support hole 132a by press-fitting the third pin 47c into the first support hole 131a and the second support hole 132. .

  In this compressor, when the drive shaft 3 rotates around the rotation axis O as described above, the swash plate 5 rotates around the rotation axis O in the rotation direction R1 shown in FIG. Here, when the movable body 13a and the swash plate 5 are connected, the first arm 131 is positioned upstream of the second arm 132 with respect to the virtual plane D in the rotation direction R1 of the swash plate 5. doing. In FIG. 7, for ease of explanation, the moving body 13 a is indicated by a virtual line, and the shapes of the first and second arms 131 and 132 are simplified. Further, the second cylinder block 23, the lug arm 49, etc. are not shown.

  Further, as shown in FIGS. 1 and 2, a tilt angle reducing spring 44 b is provided between the partition 13 b and the ring plate 45. 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 separated from each other.

  In the second small diameter portion 30b, an axial path 3b extending in the direction of the rotational 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 are provided. 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 increases the opening degree of the extraction passage 15a, the pressure in the pressure adjusting chamber 31 and, in turn, the pressure in the control pressure chamber 13c are changed to the second suction chamber. The pressure in the control pressure chamber 13c and the swash plate chamber 33 are reduced, and the variable differential pressure, which is substantially equal to the pressure in 27b, is reduced. Therefore, the moving body 13a of the actuator 13 moves toward the front side of the swash plate chamber 33 by the piston compression force acting on the swash plate 5, as shown in FIG.

  Thereby, in this compressor, the swash plate 5 is urged in a direction in which the inclination angle decreases by the compression reaction force acting on the swash plate 5 via each piston 9. The compression reaction force is a resultant force of piston compression force that acts on the swash plate 5 by each piston 9. Therefore, the movable body 13a is pulled by the swash plate 5 through the first and second arms 131 and 132 and the to-be-towed portion 45c, and moves to the front side of the swash plate chamber 33 in the direction of the rotation axis O. In the swash plate 5, the ring plate 45 abuts the rear end of the return spring 44a. As the moving body 13a moves to the front side of the swash plate chamber 33, in this compressor, the swash plate 5 swings clockwise around the action axis M3 while resisting the urging force of the return spring 44a. To do. In addition, 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 with the operating axis M3 as the operating point and the first swinging axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 5 with respect to the first direction, that is, the direction orthogonal to the rotational 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 top dead center position of each second head 9b is moved away from the second valve forming plate 41 by decreasing the inclination angle of the swash plate 5 and decreasing the stroke of each piston 9. 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.

  On the other hand, 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 is increased by the pressure of the refrigerant gas in the second discharge chamber 29b, and the control is performed. The pressure in the pressure chamber 13c increases. For this reason, the variable differential pressure increases. Thereby, in the actuator 13, the moving body 13a moves from the position shown in FIG. 1 toward the rear side in the direction of the rotation axis O against the piston compressive force acting on the swash plate 5. As shown in FIG. 2, it penetrates into the second recess 23c.

  As a result, in this compressor, the moving body 13a tilts the swash plate 5 in the direction of the rotation axis O through the first and second arms 131 and 132 and the to-be-towed portion 45c while resisting the biasing force of the inclination-decreasing spring 44b. Pull to the rear side of the plate chamber 33. 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 away from 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 becomes small, with the action axis M3 and the first swing axis M1 as the action point and the fulcrum, respectively. For this reason, the inclination angle of the swash plate 5 with respect to the 1st direction D1 increases, and the stroke of each piston 9 increases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 becomes large.

    As shown in FIGS. 7 and 8, in this compressor, the first and second arms 131 and 132 and the towed portion 45c are connected by the third pin 47c, whereby the moving body 13 and the swash plate 5 are connected. It is connected. Here, in this compressor, a compression reaction force acts on each swash plate 5 from each piston 9 at the time of operation as described above. This compression reaction force acts on the upstream side in the rotation direction with respect to the virtual plane D in the rotation direction R1 of the swash plate shown in FIG. For this reason, as shown in FIG. 9, a moment is applied to the swash plate 5 to cause the swash plate 5 to turn in the R2 direction around the first direction D1. That is, in this compressor, when the inclination angle of the swash plate 5 is increased, the moving body 13a moves the swash plate 5 in the state of being squeezed in the R2 direction with the traction force F and the swash plate 5 in the direction of the rotation axis O. Tow. Here, since the first and second arms 131 and 132 and the to-be-towed portion 45 c are connected by the third pin 47 c, the moving body 13 a pulls the swash plate 5 through the first and second arms 131 and 132. Further, when the movable body 13 pulls the swash plate 5 rearward in the direction of the rotation axis O with the traction force F, the third pin 47c is slightly curved so as to protrude toward the swash plate 5 side. For ease of explanation, FIG. 9 and FIG. 10 exaggerate the bending of the swash plate 5 and the curvature of the third pin 47c.

  FIG. 10 shows a compressor of a comparative example. In the compressor of the comparative example, the third support hole 460 is provided through the to-be-towed portion 45c. The third support hole 460 is cylindrical and extends in the second direction D2 with a constant diameter. Thereby, the step portion 451 is not formed in the third support hole 460. Other configurations of the compressor of the comparative example are the same as those of the compressor of the first embodiment, and the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

  When the inclination angle of the swash plate 5 is increased, the third pin 47c is curved as described above, and therefore the first support hole 131a does not support the third pin 47c over the entire inner wall. That is, the first support hole 131a supports the third pin 47c in the first support region P1 where the inner wall of the first support hole 131a and the third pin 47c contact. Similarly, the second support hole 132a supports the third pin 47c in the second support region P2 where the inner wall of the second support hole 132a and the third pin 47c contact. The third support hole 460 supports the third pin 47c at a fulcrum P3 where the inner wall of the third support hole 450 and the third pin 47c come into contact.

  Further, since the moving body 13a pulls the swash plate 5 through the first and second arms 131 and 132, the traction force F when the moving body 13a pulls the swash plate 5 is the first arm 131 in the first support region P1. Is the resultant force of the traction force F1 that pulls the swash plate 5 and the traction force F2 that the second arm 132 pulls the swash plate 5 in the second support region P2. Here, since the swash plate 5 is turned in the R2 direction, the position of the fulcrum P3 approaches the first support region P1, that is, the first arm 131 side in the second direction D2. Specifically, in the compressor of the comparative example, since the third support hole 460 is cylindrical, the position of the fulcrum P3 is the end surface of the third support hole 460 on the first support hole 131 side. As a result, the distance a1 from the first support region P1 to the fulcrum P3 is shorter than the distance b1 from the second support region P2 to the fulcrum P3. For this reason, in the compressor of the comparative example, the traction force F1 is larger than the traction force F2. Further, when the moving body 13a pulls the swash plate 5 with the traction force F, the reaction force F ′ acts, so the reaction force F1 ′ acts on the first arm 131 in the direction opposite to the traction force F1, and the second force A reaction force F2 ′ acts on the arm 132 in the direction opposite to the traction force F2. Thus, in the compressor of the comparative example, when the moving body 13a pulls the swash plate 5 to increase the inclination angle, the load acting on the first arm 131 side and the load acting on the second arm 132 side are The difference becomes larger. For this reason, in the compressor of the comparative example, the first arm 131 is easily broken.

  As shown in FIG. 9, also in the compressor of Example 1, when the moving body 13a pulls the swash plate 5 with the traction force F, the first arm 131 moves with the traction force F1 in the first support region P1. The second arm 132 pulls the swash plate 5 with the traction force F2 in the second support region P2. Here, in the compressor according to the first embodiment, a step portion 451 is formed in the third shaft hole 450. Since the step 451 protrudes toward the third pin 47c, the step 451 supports the third pin 47c at the fulcrum P3 in the third support hole 450. And since the step part 451 is formed in the approximate center of the axial direction of the 3rd support hole 450, even if the swash plate 5 is scooped in R2 direction as mentioned above, the position of the fulcrum P3 is 3rd. It is approximately the center in the axial direction of the support hole 450. That is, in the compressor of the first embodiment, the position of the fulcrum P3 is farther from the first support region P1 in the second direction D2 than the compressor of the comparative example, and approaches the second support region P2 by that amount. Thereby, in the compressor of Example 1, the distance a2 from the 1st support area | region P1 to the fulcrum P3 becomes longer than the distance a1 from the 1st support area | region P1 to the fulcrum P3 in the compressor of a comparative example. On the other hand, in the compressor of Example 1, the distance b2 from the second support region P2 to the fulcrum P3 is shorter than the distance b1 from the second support region P2 to the fulcrum P3 in the compressor of the comparative example. In other words, in the compressor according to the first embodiment, the difference in length between the distance a2 and the distance b2 is reduced.

  Thus, in the compressor according to the first embodiment, the traction force F1 that the first arm 131 pulls the swash plate 5 in the first support region P1 is reduced by the amount the fulcrum P3 is far from the first support region P1, and accordingly, Accordingly, the reaction force F1 ′ acting on the first arm 131 is also reduced. On the other hand, in the compressor according to the first embodiment, the traction force F2 that the second arm 132 pulls the swash plate 5 in the second support region P2 increases as the fulcrum P3 approaches the second support region P2. The reaction force F2 ′ acting on the second arm 132 is also increased. Thereby, in the compressor of Example 1, when the movable body 13a pulls the swash plate 5, the load which acts on the 1st arm 131 becomes small, and the load which acts on the 2nd arm 132 correspondingly becomes large. As a result, the load acting on the first arm 131 and the load acting on the second arm 132 can be balanced. In the compressor of the first embodiment, as long as the loads acting on the first and second arms 131 and 132 can be balanced, not only the case where both are perfectly balanced, but the size of both is constant. There may be a difference.

  Thus, in the compressor according to the first embodiment, when the inclination angle of the swash plate 5 is changed, the first arm 131 can be prevented from being broken by a load acting on the first arm 131 side.

  Therefore, the compressor of Example 1 exhibits high durability.

  In particular, in this compressor, as described above, when the movable body 13a pulls the swash plate 5, the load acting on the first arm 131 side and the load acting on the second arm 132 side can be balanced. it can. For this reason, in this compressor, when the inclination angle of the swash plate 5 is changed, the moving body 13a can move smoothly in the direction of the rotational axis of the drive shaft, and the inclination angle of the swash plate 5 can be suitably changed. For this reason, in this compressor, controllability is also high.

  Further, in this compressor, the third support hole 450 supports the third pin 47c at the fulcrum P3 by the step portion 451 formed between the first cylindrical portion 450a and the second cylindrical portion 450b. For this reason, in this compressor, the position of the step portion 451 in the third support hole 450 can be adjusted by appropriately designing the lengths of the first cylindrical portion 450a and the second cylindrical portion 450b in the respective axial directions. it can. Thereby, in this compressor, it is possible to adjust the distance from the first support hole 131a to the step 451, that is, the distance from the first support region P1 to the fulcrum P3.

  Further, since the curved surface 451a is formed in the step portion 451, it is possible to prevent the step portion 451 from being chipped when the step portion 451 contacts the third pin 47c. .

(Example 2)
As shown in FIG. 11, in the compressor according to the second embodiment, a third support hole 470 is provided in the to-be-towed portion 45c. The third support hole 470 also extends in the second direction D2. The third support hole 470 includes a cylindrical portion 470a and a tapered portion 470b that are coaxial with each other. The cylindrical portion 470a has a first inner diameter L1, and extends from the axial center side of the third support hole 470 toward the other side in the second direction D2. The tapered portion 470a is continuous with the cylindrical portion 470a and extends while gradually expanding in diameter toward one side in the second direction D2. Accordingly, in the third support hole 470, the tapered portion 470b opens toward the first support hole 131a, and the cylindrical portion 470a opens toward the second support hole 132a. Here, the largest diameter portion of the tapered portion 470a is set to the second inner diameter L3, which is larger than that of the cylindrical portion 470a. The cylindrical portion 470a corresponds to the small diameter portion in the present invention, and the tapered portion 470b corresponds to the large diameter portion in the present invention. Thereby, like the compressor of Example 1, also in the 3rd support hole 470, the 1st support hole 131a side is opening more largely than the 2nd support hole 132a side.

  Further, the cylindrical portion 470a has a smaller diameter than a portion having the smallest diameter in the tapered portion 470b. For this reason, a step 452 is formed at the boundary between the tapered portion 470b and the cylindrical portion 470a also in the third support hole 470. The stepped portion 452 is located at the approximate center of the third support hole 470 in the axial direction. Similar to the compressor of the first embodiment, the stepped portion 452 also protrudes toward the third pin 47c. Further, a curved surface 452a is formed on the stepped portion 452. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

(Example 3)
As shown in FIG. 12, in the compressor according to the third embodiment, a third support hole 480 is provided in the to-be-towed portion 45c. The third support hole 480 also extends in the second direction D2. The third support hole 480 includes a cylindrical portion 480a and a tapered portion 480b. Similarly to the cylindrical portion 470a in the second embodiment, the cylindrical portion 480a has the first inner diameter L1 and extends toward the other side in the second direction D2. The taper portion 480b is formed in substantially the same manner as the taper portion 470b in the second embodiment, and continues to the cylindrical portion 480a and extends while gradually increasing in diameter toward one side in the second direction D2. Thereby, also in the 3rd support hole 480, the taper part 480b opens toward the 1st support hole 131a, and the cylindrical part 480a opens toward the 2nd support hole 132a. Here, unlike the compressor of the second embodiment, the taper portion 480b has the largest diameter at the second inner diameter L2, which is larger than the cylindrical portion 480a. The cylindrical portion 480a corresponds to the small diameter portion in the present invention, and the tapered portion 480b corresponds to the large diameter portion in the present invention.

  Further, the portion having the smallest diameter in the tapered portion 480b is formed to have the same diameter as the cylindrical portion 480a. For this reason, in the 3rd support hole 480, the cylindrical part 480a and the taper part 480b are continuing smoothly. Further, a boundary portion 480c is formed between the tapered portion 480b and the cylindrical portion 480a. The boundary portion 480 c is located at the approximate center in the axial direction of the third support hole 480. Then, the third pin 47 c inserted into the third support hole 480 is supported by the boundary portion 480 c in the third support hole 480. Other configurations of this compressor are the same as those of the compressors of the first and second embodiments.

Example 4
As shown in FIG. 13, in the compressor of the fourth embodiment, a third support hole 490 is provided through the to-be-towed portion 45 c. The third support hole 490 also extends in the second direction D2. The third support hole 490 includes a first cylindrical portion 490a and a second cylindrical portion 490b. Similar to the first cylindrical portion 450a in the first embodiment, the first cylindrical portion 490a has the first inner diameter L1 and extends toward the other side in the second direction D2. Similar to the second cylindrical portion 450a in the first embodiment, the second cylindrical portion 490b extends toward the other side in the second direction D2. The second cylindrical portion 490b has a second inner diameter L4 that is larger than the first inner diameter L1. The first cylindrical portion 490a corresponds to the small diameter portion in the present invention, and the second cylindrical portion 490b corresponds to the large diameter portion in the present invention.

  Also in the third support hole 490, a stepped portion 453 is formed at the boundary between the first cylindrical portion 490a and the second cylindrical portion 490b. The step portion 453 c is located at the approximate center in the axial direction of the third support hole 490. The step portion 453 also protrudes toward the third pin 47c. Further, a curved surface 453a is also formed in the step portion 453. Here, unlike the compressor of the first embodiment, the first cylindrical portion 490a and the second cylindrical portion 490b are formed so as to be displaced from each other in the axial direction. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

(Example 5)
As shown in FIG. 14, in the compressor according to the fifth embodiment, the third support hole 500 is provided through the to-be-towed portion 45c. The third support hole 500 also extends in the second direction D2. The third support hole 500 includes first to third cylindrical portions 500a to 500c that are coaxial. The first cylindrical portion 500a extends from the center side in the axial direction of the third support hole 500 toward the other side in the second direction D2, and opens toward the second support hole 132a. The second cylindrical portion 500b extends from the axial center side of the third support hole 500 toward one side in the second direction D2, and opens to the first support hole 131a side. The first cylindrical portion 500a and the second cylindrical portion 500b are formed to have the same diameter, and both have a second inner diameter L2. Thus, the third support hole 500 is opened with the same diameter on the first support hole 131a side and the second support hole 132a side.

  The third cylindrical portion 500c is located between the first cylindrical portion 500a and the second cylindrical portion 500b, that is, in the axial center of the third support hole 500, and the first cylindrical portion 500a and the second cylindrical portion. It is continuous with 500b. The third cylindrical portion 500c has a first inner diameter L1 that is smaller than the second inner diameter L2, and is smaller in diameter than the first and second cylindrical portions 500a and 500b. The third cylindrical portion 500c corresponds to the small diameter portion in the present invention, and the first and second cylindrical portions 500a and 500b correspond to the large diameter portion in the present invention. Since the third cylindrical portion 500c has a smaller diameter than the first and second cylindrical portions 500a and 500b, the first and second cylindrical portions 500a and 500b and the third small diameter portion 500c are disposed in the third support hole 500. A step 454 is formed therebetween. The step portion 454 also protrudes toward the third pin 47c. The step 454 also has curved surfaces 454a at both ends. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

  Each compressor of these Examples 2-5 can also have the same operation as the compressor of Example 1. Further, the third support hole 500 in the compressor of the fifth embodiment can be used even when the compressor is configured to rotate the swash plate 5 in the direction opposite to the rotation direction R1 shown in FIG. Yes.

  In the above, the present invention has been described with reference to the first to fifth embodiments. However, the present invention is not limited to the first to fifth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, in the compressor according to the first embodiment, the axial lengths of the first and second cylindrical portions 450a and 450b are designed so that the step portion 451 is formed in the approximate center of the third support hole 450 in the axial direction. ing. However, the present invention is not limited to this, and in the third support hole 450, the first cylindrical portion 450a is formed such that the stepped portion 451 is formed at a position away from the end surface of the third support hole 450 on the first insertion hole 131 side. The axial length may be designed as appropriate. The same applies to the compressors of Examples 2 to 5.

  Further, the compressor may be configured without forming each first cylinder bore 21 a in the first cylinder block 21.

  Further, the actuator 13 may be disposed on the first cylinder block 21 side in the swash plate chamber 33 with the swash plate 5 as a reference.

  Further, the control mechanism 15 may be configured such that the control valve 15c is provided for the air supply passage 15b and the orifice 15d is provided for the extraction passage 15a. In this case, the opening degree of the supply passage 15b can be adjusted by the control valve 15c. Accordingly, the control pressure chamber 13c 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.

  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 11a, 11b ... Shoe (conversion mechanism)
DESCRIPTION OF SYMBOLS 13 ... Actuator 13a ... Moving body 13b ... Partition body 13c ... Control pressure chamber 14 ... Connection mechanism 15 ... Control mechanism 21a ... 1st cylinder bore (cylinder bore)
23a ... Second cylinder bore (cylinder bore)
45c ... towed portion 47c ... third pin (connection shaft)
131 ... 1st arm 131a ... 1st support hole 132 ... 2nd arm 132a ... 2nd support hole 450, 460, 470, 480, 490, 500 ... 3rd support hole 450a ... 1st cylindrical part (small diameter part)
450b ... 2nd cylindrical part (large diameter part)
451 to 454 ... Steps 451a to 454a ... Curved surface (chamfered)
470a ... Cylindrical part (small diameter part)
470b: Tapered portion (large diameter portion)
480a ... Cylindrical part (small diameter part)
480b ... Tapered portion (large diameter portion)
500a ... 1st cylindrical part (large diameter part)
500b ... 2nd cylindrical part (large diameter part)
500c ... 3rd cylindrical part (small diameter part)
D ... Virtual plane L1 ... 1st inside diameter L2-L4 ... 2nd inside diameter T ... Top dead center corresponding | compatible part

Claims (3)

A housing in which a swash plate chamber and a plurality of cylinder bores are formed;
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the rotational axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the rotational axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
The swash plate is formed with a top dead center corresponding portion for positioning each piston at a top dead center,
A virtual plane including the upper point corresponding part and the rotation axis is defined,
The moving body is connected to the swash plate via a connection mechanism, and the inclination pressure is increased by pulling the swash plate by increasing the pressure in the control pressure chamber,
The coupling mechanism is provided on the movable body, and is provided on the swash plate between a first arm and a second arm arranged across the virtual plane, and between the first arm and the second arm. A towed portion that is positioned, and a connecting shaft that is inserted through the first arm, the second arm, and the towed portion and connects the first arm, the second arm, and the towed portion by one. And
The first arm is located upstream of the second arm with respect to the virtual plane in the rotation direction of the swash plate,
A first support hole for supporting the connecting shaft is formed in the first arm,
The second arm is formed with a second support hole for supporting the connecting shaft,
The to-be-towed part is formed with a third support hole for supporting the connecting shaft,
A small diameter portion having a first inner diameter and a large diameter portion having a second inner diameter larger than the first inner diameter are formed in the third support hole,
The variable diameter swash plate compressor, wherein the small diameter portion is disposed farther from the first support hole than the large diameter portion.   The variable displacement swash plate compressor according to claim 1, wherein a step portion is formed between the small diameter portion and the large diameter portion in the third support hole.   The variable capacity swash plate compressor according to claim 2, wherein the stepped portion is chamfered.

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