WO2014156799A1

WO2014156799A1 - Variable-capacity swash plate-type compressor

Info

Publication number: WO2014156799A1
Application number: PCT/JP2014/057236
Authority: WO
Inventors: 山本　真也; 雅樹太田; 隆容鈴木; 和也本田; 秀晴山下; 圭西井; 佑介山▲崎▼
Original assignee: 株式会社豊田自動織機
Priority date: 2013-03-27
Filing date: 2014-03-18
Publication date: 2014-10-02
Also published as: KR101793357B1; DE112014001700T5; CN105102815A; DE112014001700B4; CN105102815B; KR20150133285A; US20160032910A1

Abstract

Provided is a compressor in which discharge capacity is changed by an actuator, wherein high controllability is exhibited and compactness can be achieved. In this compressor, a mobile body (13a) has a back wall (130), a peripheral wall (131), and a joining mechanism (14). The joining mechanism (14) has a first arm (132) on which a first pulling point (132a) is set, and a second arm (133) on which a second pulling point (133a) is set. In the compressor, when the angle of incline of a swash plate (5) is increased, the mobile body (13a) pulls the swash plate via the first and second arms (132, 133). At this time, in the compressor, pulling force can be imparted at two points, the first pulling point (132a) and the second pulling point (133a). Consequently, in the compressor, even if the back wall (130) and the peripheral wall (131) are made larger, the rigidity of the first and second arms (132, 133) can be made lower.

Description

Variable capacity swash plate compressor

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

Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter referred to as a compressor). In this compressor, a housing is formed by a front housing, a cylinder block, and a rear housing. A suction chamber and a discharge chamber are formed in the front housing and the rear housing, respectively. A swash plate chamber and a plurality of cylinder bores are formed in the cylinder block. A drive shaft is rotatably supported by the housing. In the swash plate chamber, there is provided a swash plate that can be rotated by 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 drive 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 actuator has a moving body and a control pressure chamber. This actuator can change the inclination angle by changing the volume of the control pressure chamber. The control mechanism controls the actuator.

The swash plate is formed with a pair of first arms extending toward the front housing side and a pair of second arms extending toward the rear housing side. A lug arm is fixed to the drive shaft. And each 1st arm and lug arm are connected by the 1st pin. Moreover, each 2nd arm and the mobile body are connected by the 2nd pin. A link mechanism is formed by the first and second arms, the lug arm, the movable body and the first and second pins.

In this compressor, the control mechanism increases the pressure in the control pressure chamber by the pressure of the refrigerant in the discharge chamber, and increases the inclination angle of the swash plate through the link mechanism. At this time, the moving body presses the swash plate through each second arm. The swash plate pressed by the moving body presses the lug arm through each first arm. As a result, the axial length of the link mechanism in the direction of the drive axis is shortened, so that the inclination angle of the swash plate is increased. Thus, in this compressor, the discharge capacity per rotation of the drive shaft is increased.

JP-A-5-172052

By the way, in the compressor that changes the discharge capacity by the actuator as described above, higher controllability may be required.

Therefore, in the conventional compressor, it is conceivable to increase the size of the moving body in the radial direction in order to reliably increase the discharge capacity by increasing the pressure in the control pressure chamber. However, in this case, in order to avoid the interference between the moving body and the swash plate having an increased inclination angle, the swash plate chamber is increased in size, and consequently the compressor is increased in size.

In this compressor, since the moving body presses the swash plate to increase the inclination angle, the moving body is inclined by a large pressing force so as to resist the increasing compression reaction force and suction reaction force. It is necessary to press the plate. For this reason, in this compressor, when the inclination angle is increased, a large pressing force acts on each second arm. Then, if it is going to ensure high rigidity in each 2nd arm so that it can endure such a load of pressing force, each 2nd arm will enlarge. The same applies to each first arm. Here, when the moving body is enlarged in the radial direction as described above, since the pressing force acting on each of the first and second arms becomes larger, the rigidity of each of the first and second arms is higher. Is required. The increase in the size of the first and second arms also increases the size of the swash plate chamber.

The present invention has been made in view of the above-described conventional situation, and solves the problem of providing a compressor that can achieve downsizing while exhibiting high controllability in a compressor that changes the discharge capacity by an actuator. It is an issue that should be done.

The capacity-variable swash plate compressor of the present invention includes a housing in which a suction chamber, a discharge chamber, a swash plate chamber and a cylinder bore are 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 housed 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 disposed in the swash plate chamber An actuator that can change the tilt angle, and a control mechanism that controls the actuator,
The suction chamber and the swash plate chamber communicate with each other,
The actuator is connected to the partition provided on the drive shaft, the swash plate via a connection mechanism, and a movable body that is movable in the drive axis direction and movable relative to the partition. A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by introducing a refrigerant from the discharge chamber;
The moving body is arranged to pull the swash plate and increase the inclination angle when the pressure in the control pressure chamber increases.
The link mechanism has a connecting portion connected to the swash plate,
The coupling mechanism has a first arm and a second arm that are disposed on the opposite side of the coupling portion with respect to the drive shaft and are provided on the movable body across the drive shaft center. Features.

In the compressor of the present invention, when the inclination angle of the swash plate is increased, the moving body pulls the swash plate. That is, in this compressor, when the swash plate is displaced in the direction of increasing the inclination angle, the moving body is remote from the swash plate. For this reason, in this compressor, even when the size of the movable body is increased in order to reliably increase the discharge capacity due to the pressure increase in the control pressure chamber, interference between the movable body and the swash plate does not occur. Thereby, in this compressor, it becomes possible to suppress the enlargement of a swash plate chamber.

In this compressor, the moving body is connected to the swash plate through a connecting mechanism. For this reason, when increasing the inclination angle of the swash plate, the moving body applies a traction force to the swash plate through the coupling mechanism. Here, when the inclination angle is increased by pulling the swash plate, it is less affected by the compression reaction force or the suction reaction force than when the inclination angle is increased by pressing the swash plate. For this reason, this compressor does not require a large traction force to increase the inclination angle of the swash plate.

Furthermore, in this compressor, the coupling mechanism has a first arm and a second arm. The first arm and the second arm are provided on the moving body across the drive axis. Thereby, tractive force can be provided in these 1st arms and 2nd arms. For this reason, in this compressor, compared with the case where a connection mechanism has only a single arm, for example, the tractive force which a 1st arm and a 2nd arm individually provide with respect to a swash plate is made small. be able to. In this compressor, when the inclination angle of the swash plate is decreased, the moving body presses the swash plate through the first and second arms, but the pressing force at that time is not so large. This is because centrifugal force acts on the rotating body including the swash plate and the moving body in the direction of decreasing the inclination angle.

For these reasons, in this compressor, even when the movable body is enlarged as described above, the required rigidity of the first arm and the second arm can be reduced. For this reason, in this compressor, it becomes possible to suppress the enlargement of a connection mechanism.

Therefore, according to the compressor of the present invention, it is possible to achieve downsizing while exhibiting high controllability in the compressor whose discharge capacity is changed by the actuator.

In the compressor of the present invention, the cylinder bore may be at least a first cylinder bore, a second cylinder bore, and a third cylinder bore. The first cylinder bore, the second cylinder bore, and the third cylinder bore may be arranged in the housing at equiangular intervals concentrically around the drive shaft center. The swash plate chamber is partitioned by a first tangent drawn from the drive shaft to the second cylinder bore side of the first cylinder bore and a second tangent drawn from the drive shaft to the first cylinder bore side of the second cylinder bore. A first imaginary region is set, and a third tangent drawn from the drive axis to the third cylinder bore side of the second cylinder bore and a fourth tangent drawn from the drive axis to the second cylinder bore side of the third cylinder bore A second virtual area partitioned by can be set. The first arm is preferably located in the first virtual area, and the second arm is preferably located in the second virtual area.

In this case, the first arm and the second arm do not interfere with the piston that reciprocates in the first to third cylinder bores. For this reason, it becomes possible to reliably reduce the size of the compressor.

Also, the swash plate may be provided with a towed portion that protrudes between the first arm and the second arm. And it is preferable that a driving force is transmitted between a 1st arm, a 2nd arm, and a towed part. In this case, the moving body rotates stably together with the drive shaft, and the swash plate also rotates stably together with the moving body and eventually the drive shaft.

In the compressor according to the present invention, for example, the first arm and the towed part, and the second arm and the towed part can be connected by separate pins or the like.

In particular, it is preferable that a pin extending in a direction orthogonal to the drive axis is inserted through the first arm, the to-be-drawn portion, and the second arm. In this case, the first arm, the towed portion, and the second arm can be easily connected. Further, in this case, as described above, the number of parts can be reduced as compared with the case where the first arm and the towed part are connected to the second arm and the towed part by separate pins or the like. Manufacturing can be facilitated. Further, in this case, the pin is difficult to be removed from the first and second arms and the towed portion, and the reliability can be increased.

According to the compressor of the present invention, it is possible to reduce the size of the compressor whose discharge capacity is changed by an actuator while exhibiting high controllability.

It is sectional drawing at the time of the maximum capacity | capacitance in the compressor of an Example. It is a schematic diagram which shows the control mechanism in connection with the compressor of an Example. FIG. 3 is a cross-sectional view of the compressor according to the embodiment, as viewed from the direction of arrows III-III in FIG. It is the front view and sectional view which show the swash plate concerning the compressor of an Example. FIG. 1A shows a front view of the swash plate. FIG. (B) shows a cross-sectional view of the swash plate. It is sectional drawing at the time of the minimum capacity | capacitance in the compressor of an Example. It is a perspective view from the back which shows the compressor concerning an example and shows a mobile. It is a schematic top view which shows the moving body in connection with the compressor of an Example.

Hereinafter, embodiments embodying the present invention will be described with reference to the drawings. The compressor of the embodiment is a variable capacity double-head swash plate compressor. This compressor is mounted on a vehicle and constitutes a refrigeration circuit of a vehicle air conditioner.

As shown in FIG. 1, the compressor according to the first embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, a pair of

shoes

11 a and 11 b, and an actuator 13. And a control mechanism 15 shown in FIG.

As shown in FIG. 1, the housing 1 includes a rear housing 17 located behind the compressor, a front housing 19 located in front of the compressor, and a first housing located between the front housing 17 and the rear housing 19. 2

cylinder blocks

21 and 23 and first and second

valve forming plates

39 and 41.

The rear housing 17 is provided with the control mechanism 15 described above. In the rear housing 17, a first suction chamber 27a, a first discharge chamber 29a, and a pressure adjustment chamber 31 are formed. The pressure adjustment chamber 31 is located in the center portion of the rear housing 17. The first suction chamber 27 a is formed in an annular shape, and is located on the outer peripheral side of the pressure adjustment chamber 31 in the rear 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 in the rear housing 17.

Furthermore, the rear housing 17 is formed with a first rear communication path 18a. The rear end side of the first rear communication path 18 a communicates with the first discharge chamber 29 a, and the front end side opens at the front end of the rear housing 17.

The front housing 19 is formed with a boss 19a protruding forward. A shaft seal device 25 is provided in the boss 19a. In the front housing 19, a second suction chamber 27b and a second discharge chamber 29b are formed. The second suction chamber 27 b is located on the inner peripheral side of the front housing 19. The second discharge chamber 29 b is formed in an annular shape, and is located on the outer peripheral side of the second suction chamber 27 b in the front housing 19.

Furthermore, the front housing 19 is formed with a first front communication path 20a. The first front communication passage 20 a has a front end communicating with the second discharge chamber 29 b and a rear end opened at the rear end of the front housing 19.

A swash plate chamber 33 is formed between the first cylinder block 21 and the second cylinder block 23. The swash plate chamber 33 is located at the approximate center of the housing 1 in the front-rear direction.

As shown in FIG. 3, the first cylinder block 21 has first to fifth rear cylinder bores 21a to 21e formed in parallel in the circumferential direction at equal angular intervals. As shown in FIG. 1, the first cylinder block 21 has a first shaft hole 211 through which the drive shaft 3 is inserted. The first shaft hole 211 communicates with the pressure adjustment chamber 31 on the rear end side. A first sliding bearing 22a is provided in the first shaft hole 211. Note that a rolling bearing may be provided instead of the first sliding bearing 22a.

Further, the first cylinder block 21 is formed with a first recess 212 that communicates with the first shaft hole 211 and is coaxial with the first shaft hole 211. The first recess 212 communicates with the swash plate chamber 33 and is a part of the swash plate chamber 33. The 1st recessed part 212 is made into the shape which diameter-reduces to a step shape toward a rear end. A first thrust bearing 35 a is provided at the rear end of the first recess 212. Further, as shown in FIG. 3, the first cylinder block 21 is formed with five communication paths 37a that communicate the swash plate chamber 33 and the first suction chamber 27a. Each communication passage 37a is formed at equiangular intervals in the circumferential direction so as to be disposed between the first to fifth rear cylinder bores 21a to 21e. As shown in FIG. 1, the first cylinder block 21 is provided with a first retainer groove 213 that restricts the maximum opening of each first suction reed valve 391 a described later.

In the first cylinder block 21, a discharge port 160, a merged discharge chamber 161, a third front side communication path 20c, a second rear side communication path 18b, and a suction port 330 are formed. The second rear side communication passage 18 b has a front end communicating with the merging / discharging chamber 161 and a rear end opening at the rear end of the first cylinder block 21. The discharge port 160 and the merge discharge chamber 161 are in communication with each other. The merging / discharging chamber 161 is connected via a discharge port 160 to a condenser (not shown) constituting a pipe line. In addition, the front end side of the third front side communication path 20 c is open to the front end of the first cylinder block 21, and the rear end side communicates with the merged discharge chamber 161. The suction port 330 communicates with the swash plate chamber 33. The suction port 330 is connected to an evaporator (not shown) that constitutes a pipe line.

The second cylinder block 23 has a first front cylinder bore 23a corresponding to the first rear cylinder bore 21a. As a result, the first rear cylinder bore 21a and the first front cylinder bore 23a are paired in the front-rear direction. The first rear cylinder bore 21a and the first front cylinder bore 23a have the same diameter. Similarly, the second cylinder block 23 is formed with second to fifth front cylinder bores (not shown) corresponding to the second to fifth rear cylinder bores 21b to 21e, respectively.

Also, 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 23. A rolling bearing may be provided instead of the second sliding bearing 22b.

The second cylinder block 23 is formed with a second recess 23c that communicates with the second shaft hole 23b and is coaxial with the second shaft hole 23b. The second recess 23 c is also in communication with the swash plate chamber 33 and is a part of the swash plate chamber 33. Thus, the second shaft hole 23b communicates with the swash plate chamber 33 on the rear end side. The 2nd recessed part 23c is made into the shape which diameter-reduces in steps toward the front end. A second thrust bearing 35b is provided at the front end of the second recess 23c. Further, the second cylinder block 23 is formed with a plurality of communication paths 37b that communicate the swash plate chamber 33 and the second suction chamber 27b. 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.

Furthermore, a second front communication path 20b is formed in the second cylinder block 23. The front end of the second front side communication path 20 b is open to the front end side of the second cylinder block 23, and the rear end is open to the rear end side of the second cylinder block 23. The second front communication path 20b communicates with the front end side of the third front communication path 20b by joining the first cylinder block 21 and the second cylinder block 23 together.

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

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 a plurality of first suction holes 390a respectively corresponding to the first to fifth rear cylinder bores 21a to 21e. The first valve plate 390 and the first intake valve plate 391 are formed with a plurality of first discharge holes 390b corresponding respectively to the first to fifth rear cylinder bores 21a to 21e. 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. The first valve plate 390 and the first suction valve plate 391 are formed with a first discharge communication hole 390d.

The first to fifth rear cylinder bores 21a to 21e communicate with the first suction chamber 27a through the first suction holes 390a, respectively. The first to fifth rear cylinder bores 21a to 21e communicate with the first discharge chamber 29a through the first discharge holes 390b. The first suction chamber 27a and each communication path 37a communicate with each other through the first suction communication hole 390c. The first rear communication passage 18a and the second rear communication passage 18b communicate with each other through the first discharge communication hole 390d.

The first intake valve plate 391 is provided on the front surface of the first valve plate 390. The first suction valve plate 391 has the same number of first suction reed valves 391a as the first suction holes 390a that can open and close the first suction holes 390a by elastic deformation. The first discharge valve plate 392 is provided on the rear surface of the first valve plate 390. The first discharge valve plate 392 is formed with the same number of first discharge reed valves 392a as the first discharge holes 390b that can open and close the first discharge holes 390b by elastic deformation. The first retainer plate 393 is provided on the rear 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, 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 first to fifth front 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 first to fifth front cylinder bores 23a. Furthermore, 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. Further, the second discharge communication hole 410d is formed in the second valve plate 410 and the second suction valve plate 411.

The first to fifth front cylinder bores 23a communicate with the second suction chamber 27b through the second suction holes 410a. The first to fifth front cylinder bores 23a communicate with the second discharge chamber 29b through the second discharge holes 410b. The second suction chamber 27b and each communication path 37b communicate with each other through the second suction communication hole 410c. The first front communication path 20a and the second front communication path 20b communicate with each other through the second discharge communication hole 410d.

The second suction valve plate 411 is provided on the rear surface of the second valve plate 410. The second suction valve plate 411 has the same number of second suction reed valves 411a as the second suction holes 410a that can open and close the second suction holes 410a by elastic deformation. The second discharge valve plate 412 is provided on the front surface of the second valve plate 410. The second discharge valve plate 412 has the same number of second discharge reed valves 412a as the second discharge holes 410b that can open and close the second discharge holes 410b by elastic deformation. The second retainer plate 413 is provided on the front 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.

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

Further, in this compressor, the first and

second suction chambers

27a and 27b and the swash plate chamber 33 communicate with each other through the

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, each pressure in the swash plate chamber 33 and the first and

second suction chambers

27a and 27b is the first and second pressure chambers. The pressure is lower than in the

discharge chambers

29a and 29b.

The drive shaft 3 includes a drive shaft main body 30, a first support member 43a, and a second support member 43b. A first small diameter portion 30 a is formed on the rear end side of the drive shaft main body 30, and a second small diameter portion 30 b is formed on the front end side of the drive shaft main body 30. The drive shaft main body 30 extends from the front side to the rear side of the housing 1, is inserted rearward from the boss 19 a, and is inserted into the first and second sliding

bearings

22 a and 22 b. 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 located in the boss 19 a and the rear end protrudes into the pressure adjustment chamber 31.

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

The first support member 43 a is press-fitted to the rear end side of the first small diameter portion 30 a of the drive shaft main body 30 and is positioned in the first shaft hole 211. A flange 430 is formed at the front end of the first support member 43a. The flange 430 protrudes into the second recess 23c and is in contact with the first thrust bearing 35a. The rear end of the first support member 43 a protrudes into the pressure adjustment chamber 31. Furthermore, a resin-made first sliding member 431 and a second sliding member 432 are provided at a position on the rear end side of the flange 430 in the first support member 43a. These first and second sliding

members

431 and 432 can be in sliding contact with the inner peripheral surface of the first shaft hole 211.

The second support member 43b is press-fitted into the second small diameter portion 30b of the drive shaft main body 30, and is positioned between the second sliding bearing 22b in the second shaft hole 23b. The second support member 43b is formed with a flange 433 that contacts the second thrust bearing 35b and an attachment portion (not shown) through which a second pin 47b described later is inserted. Further, the front end of the first return spring 44a is fixed to the second support member 43b. The first return spring 44a extends in the direction of the drive axis O from the second support member 43b side toward the swash plate chamber 33 side.

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 of the compressor in the swash plate chamber 33. The rear surface 5 b faces the rear of the compressor in the swash plate chamber 33.

The swash plate 5 has a ring plate 45. As shown in FIG. 4, 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).

Further, as shown in FIG. 4A, a groove 45b is formed on one end side of the ring plate 45, and a towed portion 45c is formed on the other end side of the ring plate 45. 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, the towed portion 45c protrudes from the rear surface 5b toward the rear of the swash plate 5 so as to be positioned between first and

second arms

132 and 133 described later. A pin hole 450 is formed in the pulled portion 45c.

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 located between the swash plate 5 and the second support member 43b. 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 one end side of the ring plate 45 by the first pin 47a. The first pin 47a corresponds to the connecting portion in the present invention. Thereby, the front end side of the lug arm 49 is arranged around the first swing axis M1 with respect to one end side of the ring plate 45, that is, the swash plate 5, with the axis of the first pin 47a as the first swing axis M1. It is supported so that it can swing. 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 second support member 43b by the second pin 47b. Thus, the front end side of the lug arm 49 swings around the second swing axis M2 with respect to the second support member 43b, that is, the drive shaft 3, with the second pivot 47b as the second swing axis M2. It is supported movably. 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

132 and 133 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 on 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. 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 inclination angle of the swash plate 5 can be changed.

Each piston 9 has a first head 9a on the rear end side and a second head 9b on the front end side. Each of the first heads 9a is housed so as to be capable of reciprocating in each of the first to fifth rear cylinder bores 21a to 21e. The first compression chambers 210 are defined in the first to fifth rear cylinder bores 21a to 21e by the first heads 9a and the first valve forming plate 39, respectively. Each of the second heads 9b is housed so as to be able to reciprocate within the first to fifth front cylinder bores 23a. The second compression chambers 230 are defined in the first to fifth front cylinder bores 23a by the second heads 9b and the second valve forming plate 41, respectively.

Further, an engaging portion 9c 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. In this way, each first head 9a can reciprocate within the first to fifth rear cylinder bores 21a to 21f with a stroke corresponding to the inclination angle of the swash plate 5, and each second head. The portions 9b can reciprocate in the first to fifth front cylinder bores 23a.

Here, in this compressor, the top dead center positions of the first head 9a and the second head 9b move as the stroke of the piston 9 changes in accordance with the change of the inclination angle of the swash plate 5. Specifically, as shown in FIG. 5, the top dead center position of the first head 9a moves more greatly than the top dead center position of the second head 9b as the inclination angle of the swash plate 5 decreases. To do.

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 first recess 212. The actuator 13 includes a moving body 13a, a partition 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 rear wall 130, a peripheral wall 131, a first arm 132, and a coupling mechanism 14. 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. 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. The movable body 13a has a bottomed cylindrical shape due to the rear wall 130, the peripheral wall 131, and the coupling mechanism 14.

The connecting mechanism 14 has a first arm 132 and a second arm 133. The first arm 132 and the second arm 133 are both formed at the front end of the peripheral wall 131 and project toward the front of the movable body 13a. Specifically, the first arm 132 is formed on the left side of the front end of the peripheral wall 131, and the second arm 133 is formed on the right side of the front end of the peripheral wall 131. Thus, since the first arm 132 and the second arm 133 protrude toward the front of the movable body 13a, the first arm 132 and the first arm 132 are formed by the first and

second arms

132 and 133 and the front end surface of the peripheral wall 131. A recess 134 is formed between the second arm 133 and the second arm 133. A first traction point 132 a is set on the first arm 132, and a second traction point 133 a is set on the second arm 133. These first and second traction points 132a and 133a also function as pin holes through which the third pin 47 is inserted.

As shown in FIG. 7, the first arm 132 and the second arm 133 have a symmetrical shape and are disposed across the drive axis O. More specifically, the first arm 132 and the second arm 133 have a virtual plane X determined by the drive axis O, the top dead center position of the swash plate 5, and the bottom dead center position of the swash plate 5. Are arranged on both sides of each other and face each other. Thereby, in the moving body 13a, the first traction point 132a and the second traction point 133a are also arranged across the virtual plane X, respectively. In FIG. 7, the shapes of the first and

second arms

132, 133, etc. are simplified for easy explanation.

As shown in FIG. 1, the partition 13b is formed in a disk shape having substantially the same diameter as the inner diameter of the movable body 13a. A second return spring 44b is provided between the partition 13b and the ring plate 45. Specifically, the rear end of the second return spring 44b is fixed to the partition 13b, and the front end of the second return spring 44b is fixed to the other end side of the ring plate 45.

The first small diameter portion 30a of the drive shaft main body 30 is inserted through the movable body 13a and the partitioning body 13b. Thereby, the movable body 13a is assembled to the drive shaft main body 30 in a state in which the movable body 13a can be stored in the first storage chamber 21c, and is disposed in a state of facing the link mechanism 7 with the swash plate 5 interposed therebetween. On the other hand, the partition 13b is disposed in the moving body 13a behind the swash plate 5, and the periphery thereof is surrounded by the peripheral wall 131. Thereby, the control pressure chamber 13c is formed between the movable body 13a and the partition body 13b. 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 of the movable body 13a.

In this compressor, the first small-diameter portion 30a is inserted so that the movable body 13a can rotate together with the drive shaft 3, and in the swash plate chamber 33, in the direction of the drive axis O of the drive shaft 3. It is possible to move. On the other hand, the division body 13b is being fixed to the 2nd small diameter part 30a in the state penetrated by the 1st small diameter part 30a. Thereby, the partition 13b can only rotate together with the drive shaft 3, and cannot move like the movable body 13a. Thus, when the moving body 13a moves in the direction of the drive axis O, it moves relative to the partitioning body 13b. In addition, about the division body 13b, you may provide in the drive shaft main body 30 so that a movement to the drive shaft center O direction is possible.

Here, as shown in FIG. 3, the swash plate chamber 33 has a first tangent line L1 drawn from the drive axis O to the second rear cylinder bore 21b side of the first rear cylinder bore 21a, and the drive axis O. A first virtual region S1 defined by a second tangent line L2 drawn to the first rear cylinder bore 21a side in the second rear cylinder bore 21b is set. The swash plate chamber 33 includes a third tangent line L3 drawn from the drive axis O toward the third rear cylinder bore 21c in the second rear cylinder bore 21b, and a third tangent L3 in the third rear cylinder bore 21c from the drive axis O. A second virtual region S2 is set that is partitioned by a fourth tangent line L4 drawn toward the two rear cylinder bores 21b.

In this compressor, when the movable body 13a is assembled to the drive shaft main body 30, the first arm 132 is located in the first virtual area S1, and the second arm 133 is located in the second virtual area S2. Thus, first and

second arms

132 and 133 are formed, respectively. In FIG. 3, the shapes of the first and

second arms

132 and 133 are simplified for easy explanation.

As shown in FIG. 1, the first and

second arms

132 and 133 and the swash plate 5 are connected by a third pin 47c. Specifically, the first and

second arms

132 and 133 and the to-be-towed portion 45c are connected by one third pin 47c while the to-be-towed portion 45c shown in FIG. 4 is fitted to the recess 134 of the moving body 13a. is doing. Accordingly, the coupling mechanism 14 is disposed on the side opposite to the first pin 47a with respect to the drive shaft 3, that is, the drive axis O.

This third pin 47c extends from the first traction point 132a side to the second traction point 133a through the pin hole 450 of the to-be-towed part 45c in the direction orthogonal to the drive axis O. Thereby, as shown in FIG. 1, 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.

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

Threaded portion 3d is formed at the tip of drive shaft body 30. The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) via the screw portion 3d.

As shown in FIG. 2, the control mechanism 15 includes a low pressure passage 15a, a high pressure passage 15b, a control valve 15c, an orifice 15d, an axial path 3a, and a radial path 3b.

The low pressure passage 15a is connected to the pressure adjusting chamber 31 and the first suction chamber 27a. The control pressure chamber 13c, the pressure adjustment chamber 31, and the first suction chamber 27a communicate with each other by the low pressure passage 15a, the axial path 3a, and the radial path 3b. The high pressure passage 15b is connected to the pressure adjustment chamber 31 and the first discharge chamber 29a. The control pressure chamber 13c, the pressure adjustment chamber 31, and the first discharge chamber 29a communicate with each other by the high pressure passage 15b, the axial path 3a, and the radial path 3b. Further, an orifice 15d is provided in the high-pressure passage 15b.

The control valve 15c is provided in the low pressure passage 15a. The control valve 15c can adjust the opening of the low pressure passage 15a based on the pressure in the first suction chamber 27a.

In this compressor, a pipe connected to the evaporator is connected to the suction port 330 shown in FIG. 1, and a pipe connected to the condenser is connected to the discharge port 160. 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 moves to the first to fifth rear cylinder bores 21a to 21e and the first to fifth front cylinder bores 23a. Reciprocates inside. For this reason, the first and

second compression chambers

210 and 230 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

210 and 230, the compression stroke for compressing the refrigerant gas in the first and

second compression chambers

210 and 230, and the compression 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 161 through the first discharge communication path 18. Similarly, the refrigerant gas discharged into the second discharge chamber 29 b reaches the merged discharge chamber 161 through the second discharge communication path 20. Then, the refrigerant gas reaching the merged discharge chamber 161 is discharged from the discharge port 160 to the condenser.

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, if the control valve 15c shown in FIG. 2 increases the opening of the low-pressure passage 15a, the pressure in the pressure adjusting chamber 31 and thus the pressure in the control pressure chamber 13c are changed to the first suction chamber. It becomes substantially equal to the pressure in 27a. 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. 4.

Thus, in this compressor, the moving body 13a moves the other end of the swash plate 5 through the first and second traction points 132a and 133a of the first and

second arms

132 and 133 at the operating axis M3. It will be in the state pressed to the front side. For this reason, in this compressor, the other end side of the ring plate 45, that is, the other end side of the swash plate 5 oscillates clockwise around the action axis M3 while resisting the biasing force of the second return spring 44b. To do. 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 counterclockwise around the second swing axis M2. For this reason, the lug arm 49 approaches the flange 431 of the second support member 43b. 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 drive shaft center O of the drive shaft 3 decreases, and the stroke of the piston 9 decreases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 becomes small. The inclination angle of the swash plate 5 shown in FIG. 5 is the minimum value in this compressor.

Here, in this compressor, the centrifugal force acting on the weight portion 49a is also applied 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.

Further, as the inclination angle of the swash plate 5 decreases, the ring plate 45 contacts the rear end of the first return spring 44a. As a result, the first return spring 44a is elastically deformed, and the rear end of the first return spring 44a approaches the second support member 43b.

Here, in this compressor, the inclination angle of the swash plate 5 is reduced and the stroke of the piston 9 is reduced, whereby the top dead center position of the first head 9a is remote from the first valve forming plate 39. For this reason, in this compressor, when the inclination angle of the swash plate 5 approaches zero degrees, a slight compression work is performed on the second compression chamber 230 side, while a compression work is performed on the first compression chamber 210 side. Disappear.

On the other hand, if the control valve 15c shown in FIG. 2 reduces the opening of the low pressure passage 15a, the pressure in the pressure adjusting chamber 31 is increased by the pressure of the refrigerant gas in the first discharge chamber 29a, and the pressure in the control pressure chamber 13c is increased. Pressure increases. For this reason, against the piston compression force acting on the swash plate 5, in the actuator 13, the moving body 13 a moves toward the rear side of the swash plate chamber 33 as shown in FIG. 1.

second arms

132 and 133 at the operating axis M3. Pull backwards. For this reason, in this compressor, the other end side of the swash plate 5 swings counterclockwise around the action axis M3. 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 clockwise around the second swing axis M2. For this reason, the lug arm 49 is separated from the flange 431 of the second support member 43b. As a result, the swash plate 5 oscillates in the opposite direction to the case where the inclination angle becomes smaller with the action axis M3 and the first oscillation 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 drive axis O of the drive shaft 3 increases, and the stroke of the piston 9 increases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 becomes large. The inclination angle of the swash plate 5 shown in FIG. 1 is the maximum value in this compressor. Further, in this state where the inclination angle of the swash plate 5 is at the maximum value, the rear wall 130 of the moving body 13a contacts the first flange 430.

Thus, in this compressor, when the inclination angle of the swash plate 5 is increased, the moving body 13a pulls the swash plate 5 through the first and second pulling

points

132a and 133a of the first and

second arms

132 and 133. That is, in this compressor, the movable body 13a is remote from the swash plate 5 when the swash plate 5 is displaced in the direction of increasing the inclination angle. For this reason, in this compressor, even if the rear wall 130 and the peripheral wall 131 are enlarged in order to reliably increase the discharge capacity by the pressure increase in the control pressure chamber 13c, the interference between the peripheral wall 131 and the swash plate 5 does not occur. Thereby, in this compressor, it is possible to suppress an increase in the size of the swash plate chamber 33 while increasing the size of the rear wall 130 and the peripheral wall 131 of the movable body 13a.

In this compressor, the coupling mechanism 14 has first and

second arms

132 and 133. The first arm 132 is provided with a first traction point 132a for applying a traction force to the swash plate 5, and the second arm 133 is provided with a second traction point 133a for applying a traction force to the swash plate 5. Is set. Here, when the inclination angle is increased by pulling the swash plate 5, the inclination angle is increased by pressing the swash plate 5, compared with the case where the inclination angle is increased by pressing the swash plate 5. hard. For this reason, in this compressor, when increasing the inclination angle of the swash plate 5, a large traction force is not required.

Further, in this compressor, the first arm 132 and the second arm 133 have a virtual plane X determined by the drive axis O, the top dead center position of the swash plate 5 and the bottom dead center position of the swash plate 5. It is set across. A first traction point 132a and a second traction point 133a are set on the first arm 132 and the second arm 133, respectively. And the 1st arm 132 and the 2nd arm 133 can give tractive force in two places, these 1st traction points 132a and 2nd traction points 133a. Therefore, in this compressor, for example, the first arm 132 and the second arm 133 are individually applied to the swash plate 5 as compared with the case where the coupling mechanism 14 has only a single arm. Traction force can be reduced. In this compressor, when the inclination angle of the swash plate 5 is decreased, the moving body 13a presses the swash plate 5 through the first and

second arms

132 and 133, but the pressing force at that time is not much. Not the size of. This is because centrifugal force acts on the rotating body including the swash plate 5 and the moving body 13a in the direction of decreasing the inclination angle.

Therefore, in this compressor, even if the rear wall 130 and the peripheral wall 131 are enlarged as described above, the rigidity of the first and

second arms

132 and 133 required thereby can be reduced. it can. For this reason, in this compressor, it is possible to suppress the enlargement of the first and

second arms

132 and 133, that is, the enlargement of the coupling mechanism 14.

In this compressor, a first virtual area S1 and a second virtual area S2 are set for the swash plate chamber 33. When the movable body 13a is assembled to the drive shaft main body 30, the first arm 132 is located in the first virtual area S1, and the second arm 133 is located in the second virtual area S2. Therefore, in this compressor, the first arm 132 and the second arm 133 do not interfere with the pistons 9 that reciprocate within the first to fifth rear cylinder bores 21a to 21e and the first to fifth front cylinder bores 23a. . Thus, the first arm 132 and the second arm 133, the first to fifth rear cylinder bores 21a to 21e and the first to fifth front cylinder bores 23a, that is, the first arm 132 and the second arm 133, and each piston 9 Can be arranged close to each other.

Therefore, according to the compressor of the embodiment, the compressor whose discharge capacity is changed by the actuator 13 can be downsized while exhibiting high controllability.

In particular, in this compressor, the swash plate 5 is provided with a towed portion 45 c protruding between the first arm 132 and the second arm 133. And the 1st,

2nd arms

132 and 133 and the swash plate 5 are connected, fitting the to-be-towed part 45c with the recessed part 134 of the moving body 13a. Thereby, in this compressor, when the moving body 13a rotates with the drive shaft 3, a driving force is transmitted between the 1st arm 132, the 2nd arm 133, and the towed part 45c. For this reason, in this compressor, the moving body 13 a rotates stably with the drive shaft 3, and the swash plate 5 also rotates stably with the moving body 13 a and thus the drive shaft 3.

Further, a third pin 47c extending in a direction orthogonal to the drive axis O is inserted through the first arm 132, the to-be-towed portion 45c, and the second arm 133. For this reason, in this compressor, it is possible to easily connect the first arm 132, the towed portion 45c, and the second arm 133. In addition, for example, compared to the case where the first arm 132 and the towed part 45c and the second arm 133 and the towed part 45c are connected by separate pins, the number of parts can be reduced, and the manufacturing can be performed. Can be facilitated. Furthermore, in this compressor, it is difficult for the third pin 47c to come off from the first and

second arms

132 and 133 and the to-be-towed portion 45c, and the reliability is high.

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

For example, a cylinder bore may be formed only in one of the first cylinder block 21 and the second cylinder block 23 to configure a variable displacement single-head swash plate compressor.

Further, the control mechanism 15 may be configured such that a control valve 15c is provided for the high pressure passage 15b and an orifice 15d is provided for the low pressure passage 15a. In this case, the opening of the high-pressure passage 15b can be adjusted by the control valve 15c. Accordingly, the control pressure chamber 13b can be quickly increased in pressure by the pressure of the refrigerant gas in the first discharge chamber 29a, and the discharge capacity can be quickly increased.

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 rear side cylinder bore (1st cylinder bore)
21b ... Second rear cylinder bore (second cylinder bore)
21c ... Third rear cylinder bore (third cylinder bore)
27a ... 1st suction chamber 27b ... 2nd suction chamber 29a ... 1st discharge chamber 29b ... 2nd discharge chamber 33 ... Swash plate chamber 45c ... Towed part 47a ... 1st pin (connection part)
47c ... Third pin (pin)
132 ... 1st arm 133 ... 2nd arm 210 ... 1st compression chamber 230 ... 2nd compression chamber L1 ... 1st tangent L2 ... 2nd tangent L3 ... 3rd tangent L4 ... 4th tangent O ... Drive shaft center S1 ... 1st 1 virtual area S2 ... 2nd virtual area

Claims

A housing in which a suction chamber, a discharge chamber, a swash plate chamber and a cylinder bore are 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 And a conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the tilt angle by rotation of the swash plate, an actuator disposed in the swash plate chamber and capable of changing the tilt angle, A control mechanism for controlling the actuator,
The suction chamber and the swash plate chamber communicate with each other,
The actuator is connected to the partition provided on the drive shaft, the swash plate via a connection mechanism, and a movable body that is movable in the drive axis direction and movable relative to the partition. A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by introducing a refrigerant from the discharge chamber;
The moving body is arranged to pull the swash plate and increase the inclination angle when the pressure in the control pressure chamber increases.
The link mechanism has a connecting portion connected to the swash plate,
The coupling mechanism has a first arm and a second arm that are disposed on the opposite side of the coupling portion with respect to the drive shaft and are provided on the movable body across the drive shaft center. A variable capacity swash plate compressor.
The cylinder bores are at least a first cylinder bore, a second cylinder bore, and a third cylinder bore,
The first cylinder bore, the second cylinder bore, and the third cylinder bore are disposed in the housing at equiangular intervals concentrically around the drive shaft center,
The swash plate chamber has a first tangent line drawn from the drive shaft center to the second cylinder bore side of the first cylinder bore, and a first tangent line drawn from the drive shaft center to the first cylinder bore side of the second cylinder bore. A first virtual region partitioned by two tangents is set,
A third tangent drawn from the drive shaft to the third cylinder bore in the second cylinder bore and a fourth tangent drawn from the drive shaft to the second cylinder bore in the third cylinder bore. A second virtual area is set,
2. The variable displacement swash plate compressor according to claim 1, wherein the first arm is located in the first virtual area, and the second arm is located in the second virtual area.
The swash plate is provided with a towed portion that protrudes between the first arm and the second arm,
3. The variable displacement swash plate compressor according to claim 1, wherein driving force is transmitted between the first arm and the second arm and the towed portion.
4. The variable displacement swash plate compressor according to claim 3, wherein a pin extending in a direction perpendicular to the drive shaft is inserted through the first arm, the to-be-towed portion, and the second arm.