JP6269386B2 - Variable capacity swash plate compressor - Google Patents

Description

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

  Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter referred to as a compressor). In this compressor, a suction chamber, a discharge chamber, a swash plate chamber, and a plurality of cylinder bores are formed in a housing. A drive shaft is rotatably supported in 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 changes 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 thrust bearing, the swing plate, and the connecting rod reciprocate each piston in the cylinder bore with a stroke corresponding to the tilt angle by the rotation of the swash plate as a conversion mechanism. The tilt angle of the actuator can be changed by changing the volume of the control pressure chamber. The control mechanism controls the actuator.

  The actuator has a partition body and a moving body. The partition body is fixed to the drive shaft. The moving body is movable in the direction of the drive axis with respect to the drive shaft. This moving body is connected to the swash plate via a hinge sphere that is movable in the direction of the drive axis to the drive shaft. The control pressure chamber is partitioned by the partition body and the moving body. These are located in front of the swash plate in the swash plate chamber. The moving body is arranged to press the swash plate via the hinge sphere and reduce the inclination angle when the pressure in the control pressure chamber increases. In the swash plate chamber, a pressure spring is provided on the rear side of the swash plate to bias the tilt angle.

  In this compressor, when the control mechanism introduces the high-pressure refrigerant in the discharge chamber into the control pressure chamber, the moving body presses the swash plate against the urging force of the pressing spring, so the inclination angle of the swash plate becomes small. . Thus, the discharge capacity per rotation of the drive shaft is reduced. On the other hand, unless the control mechanism introduces the high-pressure refrigerant in the discharge chamber into the control pressure chamber, the volume of the control pressure chamber gradually decreases. For this reason, since the moving body returns to the original position by the urging force of the pressing spring, the inclination angle of the swash plate increases. Thus, the discharge capacity per rotation of the drive shaft increases.

  Patent Document 2 discloses another compressor. In this compressor, a first connecting body, a swash plate, a second connecting body, a thrust bearing, and a moving body are mounted on a drive shaft from the front to the rear. A control pressure chamber is formed behind the movable body. The second coupling body can rotate together with the drive shaft and can move in the direction of the drive shaft. The moving body does not rotate with the drive shaft, but is movable in the direction of the drive shaft. A thrust bearing is provided between the second coupling body and the moving body. A pressure spring is provided in the control pressure chamber. The pressing spring biases the moving body forward.

  In this compressor, when the control mechanism introduces the high-pressure refrigerant in the discharge chamber into the control pressure chamber, the moving body presses the second coupling body while being urged by the pressing spring. This increases the inclination angle of the swash plate. Thus, the discharge capacity per rotation of the drive shaft increases. On the other hand, unless the control mechanism introduces the high-pressure refrigerant in the discharge chamber into the control pressure chamber of the actuator, the inclination angle of the swash plate is reduced. Thus, the discharge capacity per rotation of the drive shaft is reduced.

JP-A-52-131204 Japanese Patent Laid-Open No. 05-172052

  However, in the compressors described in Patent Documents 1 and 2, when the inclination angle of the swash plate is changed, the moving body and the second connected body press the swash plate by increasing the pressure in the control pressure chamber. Yes. For this reason, in order to realize high controllability, when the moving body and the second connecting body are enlarged in the radial direction, the moving body and the second connecting body are inclined with an increased inclination angle when moved in the pressing direction. Easy to interfere with the board. For this reason, if it is going to avoid such interference, since the shape of a mobile body or a 2nd coupling body will become complicated, a compressor will enlarge. In particular, in the compressor of Patent Document 2, since the pressing spring that is the urging member presses the swash plate via the moving body, the thrust bearing, and the second connecting body, the axial length is long, and an increase in size is inevitable. In this case, the mounting property to a vehicle etc. will be impaired.

  Further, in the compressor of Patent Document 2, when the inclination angle of the swash plate is increased, the moving body, the thrust bearing, and the second connecting body must press the swash plate against the increasing compression reaction force. In addition, there is a concern that the second connected body having a complicated shape may be deformed. For this reason, if it is going to ensure the rigidity of a 2nd coupling body, the weight of a 2nd coupling body will increase, by extension, the weight of a compressor will increase, and the manufacturing cost of a compressor will also increase.

  Furthermore, in the compressor of Patent Document 2, since the pressing spring that is the urging member presses the swash plate via the moving body, the thrust bearing, and the second connecting body, the resistance force during movement in the direction of the drive shaft Therefore, the urging force of the urging member is hardly transmitted to the swash plate, and it is difficult to increase the inclination angle of the swash plate. That is, there is a difficulty in controllability.

  The present invention has been made in view of the above-described conventional situation, and can achieve downsizing, excellent durability, and light weight, and can realize a reduction in manufacturing cost and high controllability. The problem to be solved is to provide a compressor capable of realizing the above.

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 provided in the swash plate chamber, An actuator capable of changing the tilt angle; and a control mechanism for controlling the actuator;
The actuator is partitioned by a partition provided on the drive shaft, a movable body connected to the swash plate and movable in the drive shaft center direction in the swash plate chamber, and the partition and the movable body. A control pressure chamber that moves the movable body by introducing the 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.
A biasing member that increases the tilt angle when the tilt angle is minimum is provided between the partition body and the movable body ,
The movable body extends from the movable bottom wall in a direction approaching the swash plate, a peripheral wall extending in the drive axis direction and surrounding the partition, a movable bottom wall extending from the peripheral wall toward the drive shaft, The drive shaft and a sliding portion that slides;
The partition has a partition bottom wall and a guide portion extending from the partition bottom wall in a direction away from the swash plate along the inner surface of the peripheral wall,
When the swash plate angle is minimum, the guide portion and the sliding portion are arranged to overlap,
The urging member is housed between the guide portion and the sliding portion .

  In the compressor of the present invention, the moving body pulls the swash plate when the inclination angle of the swash plate is increased. That is, in this compressor, when the swash plate is displaced in the increasing direction of the tilt angle, the moving body is remote from the swash plate. For this reason, in this compressor, even if the moving body is enlarged to increase the traction force on the swash plate, interference between the moving body and the swash plate hardly occurs. Thereby, in this compressor, in order to avoid interference, it is not necessary to make a moving body into a complicated shape, and the moving body does not require much rigidity.

  For this reason, in this compressor, in order to realize high controllability, it is possible to make the moving body thin to some extent and to increase the size in the radial direction. Furthermore, it is possible to reduce the weight of the moving body.

  Further, in this compressor, the urging member is arranged by utilizing the control pressure chamber that changes the inclination angle of the swash plate. Therefore, compared to the case where the urging member is provided outside the control pressure chamber, the compressor The shaft length becomes shorter.

  Furthermore, in this compressor, the swash plate can be pulled only by the urging member via the actuator moving body. For this reason, the urging force of the urging member is only impaired by the resistance force when only the moving body moves in the drive axis direction. For this reason, the urging force of the urging member is easily transmitted to the swash plate, and the inclination angle of the swash plate is easily increased.

  In particular, in the compressor of the present invention, the biasing member increases the tilt angle when the tilt angle is minimum. For this reason, when the swash plate continues to rotate, the piston reciprocates within the cylinder bore with a certain amount of stroke. For this reason, the piston performs compression work in the compression chamber, and high-pressure refrigerant can be stored in the discharge chamber. For this reason, the control pressure chamber of the actuator can be increased in pressure by the refrigerant in the discharge chamber, and the moving body of the actuator can move in the drive axis direction. That is, in the compressor, the biasing member can assist the return of the tilt angle from the state where the tilt angle is minimum until the actuator increases the tilt angle.

  Therefore, the compressor of the present invention can realize downsizing, excellent durability, and light weight, and can realize low control of manufacturing cost and high controllability.

The biasing member may be a single coil spring that extends in the drive axis direction from one end to the other end. The coil spring preferably has one end portion fixed to the guide portion and the other end portion fixed to the sliding portion . The coil spring preferably reduces the swash plate angle when the swash plate angle is maximum. In this case, the single coil spring functions as a biasing member that increases the tilt angle by extending from the shortened state to the free length, and as a biasing member that decreases the tilt angle by contracting from the extended state to the free length. Function. For this reason, a plurality of urging members are not required, and the number of parts can be reduced.

The guide portion, it is preferable that the first engaging portion engaged with one end portion is formed. Further, the sliding portion, it is preferable that the second engaging portion engaged with the other end portion is formed. In this case, the first engagement portion is engaged with the one end of the coil spring, the second engaging portion is engaged with the other end portion, facilitating the coil spring with the first engaging portion and second engaging portion Can be engaged.

The moving body includes a peripheral wall extending in the direction of the drive axis and surrounding the partition body, a moving bottom wall extending from the peripheral wall toward the drive shaft, and a slide that extends from the moving bottom wall toward the swash plate and slides on the drive shaft. and a dynamic part. Further, partition body has a partition bottom wall, along the inner surface of the peripheral wall, and a guide portion extending from the compartment bottom wall in a direction away from the swash plate. Then, when the swash plate angle is at a minimum, the guide portion and the sliding portion is disposed so as to overlap Rutotomoni, the biasing member that is housed between the guide portion and the sliding portion.

Thereby, since a guide part and a sliding part overlap, axial length does not become long and the size reduction of a compressor is possible. Further, since the urging member is also housed between the guide portion and the sliding portion, the urging member does not hinder downsizing of the compressor. Also, since overlapping the biasing member also the guide portion and the sliding portion, it is possible to employ a long urging member to the drive shaft center direction, the biasing member can exert sufficient biasing force.

  In the compressor according to the present invention, it is possible to realize downsizing, excellent durability and light weight, and it is possible to realize a reduction in manufacturing cost and high controllability.

FIG. 1 is a cross-sectional view of a swash plate at the maximum inclination in the compressor of the embodiment. FIG. 2 is a cross-sectional view of the compressor according to the embodiment when the swash plate is at a minimum inclination. FIG. 3 is a schematic diagram illustrating a control mechanism according to the compressor of the embodiment. FIG. 4 is an enlarged cross-sectional view of a main part of the compressor according to the embodiment when the swash plate is at the maximum inclination. FIG. 5 is an enlarged cross-sectional view of the main part of the compressor according to the embodiment when the swash plate is at the minimum inclination.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

(Example)
As shown in FIGS. 1 and 2, the compressor of the embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, and a plurality of pairs of shoes 11a and 11b. The actuator 13 and the control mechanism 15 shown in FIG. 3 are provided. In FIGS. 1 and 2, the left side indicates the front and the right side indicates the rear.

  The housing 1 includes a front housing 17, a first cylinder block 21, a second cylinder block 23, a rear housing 19, a first valve unit 39, and a second valve unit 41.

  The front housing 17 is located in front of the compressor. The rear housing 19 is located behind the compressor. The first and second cylinder blocks 21 and 23 are located between the front housing 17 and the rear housing 19. The first valve unit 39 is provided between the front housing 17 and the first cylinder block 21. The second valve unit 41 is provided between the second cylinder block 23 and the rear housing 19.

  The front housing 17 is formed with a boss 17a, a first suction chamber 27a, a first discharge chamber 29a, and a first front communication path 17b.

  The boss 17a is provided at the front central portion of the front housing 17 and protrudes forward. A shaft seal device 25 is provided in the boss 17a.

  Further, the first suction chamber 27 a and the first discharge chamber 29 a are provided on the rear side of the front housing 17. The first suction chamber 27 a is located on the inner peripheral side of the front housing 17. The first discharge chamber 29a is formed in an annular shape and is located on the outer peripheral side of the first suction chamber 27a.

  The first front communication path 17 b has a front end communicating with the first discharge chamber 29 a and a rear end opened to the rear end of the front housing 17.

  In the rear housing 19, a second suction chamber 27b, a second discharge chamber 29b, a pressure adjustment chamber 31, and a rear communication passage 19a are formed.

  The pressure adjustment chamber 31 is located in the center portion of the rear 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 formed in an annular shape and is located on the outer peripheral side of the second suction chamber 27a.

  The rear communication path 19 a has a rear end communicating with the second discharge chamber 29 b and a front end opened at the front end of the rear 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.

  In the first cylinder block 21, a plurality of first cylinder bores 21a are formed in parallel at equal angular 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 that communicates with the first shaft hole 21b and is coaxial with the first shaft hole 21b. The first recess 21 c communicates with the swash plate chamber 33 and is a part of the swash plate chamber 33.

  The first recess 21c is formed in a shape that decreases in a step shape toward the front end. A first thrust bearing 35a is provided at the front end of the first recess 21c. The first thrust bearing 35 a supports a thrust force that acts on the drive shaft 3.

  Further, the first cylinder block 21 is formed with a plurality of first communication paths 37a that communicate the swash plate chamber 33 and the first suction chamber 27a.

  Further, a second front communication path 21 d is formed in the first cylinder block 21. The front end of the second front communication path 21 d is open to the front end side of the first cylinder block 21, and the rear end is open to the rear end side of the first cylinder block 21.

  In the second cylinder block 23, the same number of second cylinder bores 23a as the first cylinder bores 21a are formed in parallel at equal angular intervals in the circumferential direction. The second cylinder block 23 has a second shaft hole 23b through which the drive shaft 3 is inserted. The second shaft hole 23b is coaxial with the first shaft hole 21b. The second shaft hole 23 b communicates with the pressure adjustment chamber 31. A second sliding bearing 22b is provided in the second shaft hole 23b. The drive shaft 3 is supported by the first and second sliding bearings 22a and 22b.

  The second cylinder block 23 has 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.

  The second recess 23c is formed in a shape that decreases in a step shape toward the rear end. A second thrust bearing 35b is provided at the rear end of the second recess 23c. The second thrust bearing 35 b supports a thrust force that acts on the drive shaft 3.

  Further, the second cylinder block 23 is formed with a plurality of second communication paths 37b that communicate the swash plate chamber 33 and the second suction chamber 27b.

  The second cylinder block 23 is formed with a discharge port 23g, a merging communication passage 23h, and a suction port 23i. The discharge port 23g and the merging communication passage 23h communicate with each other. The junction communication path 23h has a front end opened to the second front communication path 21d and a rear end opened to the rear communication path 19a.

  The first valve unit 39 includes a first valve plate 390, a first intake valve plate 391, a first discharge valve plate 392, and a first retainer plate 393.

  The first valve unit 39 includes the same number of first suction holes 390a as the first cylinder bores 21a, the same number of first discharge holes 390b as the first cylinder bores 21a, a plurality of first suction communication holes 390c, and one piece. A first discharge communication hole 390d is formed. In addition, reed valves (not shown) are formed in the first suction holes 390a and the first discharge holes 390b, respectively.

  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. Further, the first suction chamber 27a communicates with each first communication path 37a through each first suction communication hole 390c. The first front communication path 17b communicates with the second front communication path 21d through the first discharge communication hole 390d.

  The second valve unit 41 includes a second valve plate 410, a second intake valve plate 411, a second discharge valve plate 412, and a second retainer plate 413.

  The second valve unit 41 includes the same number of second suction holes 410a as the second cylinder bores 23a, the same number of second discharge holes 410b as the second cylinder bores 23a, a plurality of second suction communication holes 410c, and a second discharge. A communication hole 410d is formed. In addition, a reed valve (not shown) is formed in each second suction hole 410a and each second discharge hole 410b.

  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. Further, the second suction chamber 27b communicates with the second communication path 37b through the second suction communication hole 410c. Further, the rear communication passage 19a communicates with the merging communication passage 23h through the second discharge communication hole 410d.

  In this compressor, 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. Then, the low-pressure refrigerant gas that has passed through the evaporator flows into the swash plate chamber 33 through the suction port 23i. Thereby, each pressure in the swash plate chamber 33 and the first and second suction chambers 27a and 27b is lower than that in the first and second discharge chambers 29a and 29b.

  The drive shaft 3 includes a shaft body 30, a first shaft support member 43a, and a second shaft support member 43b. The shaft body 30 extends rearward from the boss 17a. The front end of the shaft body 30 is located in the boss 17 a, and the rear end is located in the pressure adjustment chamber 31.

  An axial path 3 a and a radial path 3 b are formed in the shaft main body 30. The axial path 3a extends in the direction of the drive axis O from the rear end of the shaft main body 30 toward the front. The radial path 3 b extends in the radial direction from the front end of the axial path 3 a and opens on the outer peripheral surface of the shaft main body 30. 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.

  The 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 shaft support member 43 a is press-fitted to the front end side of the shaft body 30. The first shaft support member 43a slides in the first sliding bearing 22a as the drive shaft 3 rotates around the drive axis O. Further, the first shaft support member 43a is formed with a first flange portion 430 that contacts the first thrust bearing 35a, and an attachment portion (not shown) through which a second pin 47b described later is inserted. Has been.

  The second shaft support member 43 b is press-fitted to the rear end side of the shaft body 30. The second shaft support member 43b slides in the second sliding bearing 22b while supporting the drive shaft 3 as the drive shaft 3 rotates around the drive axis O. The second shaft support member 43b is provided between the movable body 13a and the rear housing 19 which will be described later.

  Further, the second shaft support member 43 b is provided on the drive shaft 3. A second flange portion 431 for fixing the second thrust bearing 35b is formed on the second shaft support member 43b.

  A second thrust bearing 35b is provided between the second recess 23c and the second shaft support member 43b. The second thrust bearing 35 b is formed with a larger diameter than the second flange portion 431.

  The swash plate 5 is formed in an annular flat plate shape. The swash plate 5 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 is fixed to the 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 thereof. The swash plate 5 is attached to the drive shaft 3 by inserting the shaft main body 30 through the insertion hole 45a.

  The link mechanism 7 has a lug arm 49. The lug arm 49 is disposed in front of the swash plate 5 and is positioned between the swash plate 5 and the first shaft support member 43a. The lug arm 49 is formed in a substantially L shape from the front end side toward the rear end side. As shown in FIG. 2, when the inclination angle of the swash plate 5 with respect to the drive shaft center O is minimized, the lug arm 49 comes into contact with the first flange portion 430 of the first shaft support member 43a. Thereby, in this compressor, it is possible to maintain the inclination angle of the swash plate 5 at the minimum value by the lug arm 49. 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.

  As shown in FIG. 1, the rear end side of the lug arm 49 is connected to one end side of the ring plate 45 by a first pin 47a. Accordingly, the rear end side of the lug arm 49 has the first pivot 47 M around the first swing axis M 1 with respect to one end side of the ring plate 45, that is, the swash plate 5, with the first pivot 47 a as the first pivot axis M 1. 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 first shaft support member 43a by the second pin 47b. Thereby, the front end side of the lug arm 49 has the axis of the second pin 47b as the second swing axis M2, and the first pivot support member 43a, that is, the drive shaft 3, around the second swing axis M2. It is supported so that it can swing. The second swing axis M2 extends in parallel with the first swing axis M1. The lug arm 49 and the first and second pins 47a and 47b correspond to 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. The lug arm 49 is supported by the ring plate 45 by the first pin 47a. The weight portion 49 a passes through the groove portion 45 b of the ring plate 45 and is located on the rear surface of the ring plate 45, that is, on the rear surface 5 b side of the swash plate 5. Thereby, the centrifugal force generated by the rotation of the swash plate 5 also acts on the weight portion 49a.

  In this compressor, the swash plate 5 is connected to the drive shaft 3 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 front end side and a second head 9b on the rear end side. Each first head 9a is accommodated in each first cylinder bore 21a so as to be capable of reciprocating. The first compression chambers 21e are defined in the first cylinder bores 21a by the first heads 9a and the first valve unit 39, respectively. Similarly, the second heads 9b are also housed in the second cylinder bores 23a so as to reciprocate. The second compression chambers 23f are partitioned in the second cylinder bores 23a by the second heads 9b and the second valve unit 41, respectively. Each first head 9a and each second head 9b are formed to have the same diameter.

  A concave portion 9 c is formed at the center of each piston 9. In each recess 9c, hemispherical shoes 11a and 11b are respectively 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, the first and second heads 9a and 9b can reciprocate in the first and second cylinder bores 21a and 23a, respectively, with a stroke corresponding to the inclination angle of the swash plate 5.

  As shown in FIG. 3, 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 second suction chamber 27b. Thereby, the control pressure chamber 13c, the pressure adjusting chamber 31, and the second suction chamber 27b are communicated with each other by the low pressure passage 15a, the axial passage 3a, and the radial passage 3b. A control valve 15c is provided in the low pressure passage 15a. The control valve 15c adjusts the opening of the low pressure passage 15a based on the pressure in the second suction chamber 27b.

  The high-pressure passage 15b is connected to the pressure adjustment chamber 31 and the second discharge chamber 29b. Thereby, the control pressure chamber 13c, the pressure adjusting chamber 31, and the second discharge chamber 29b are communicated 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.

  In this compressor, piping connected to the evaporator is connected to the suction port 23i shown in FIG. 1, and piping connected to the condenser is connected to the discharge port 23g. 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.

  As shown in FIGS. 4 and 5, the actuator 13 includes a moving body 13a, a partitioning body 13b, and a control pressure chamber 13c. The actuator 13 is disposed in the swash plate chamber 33. The actuator 13 is located on the rear side of the swash plate 5 and can enter the second recess 23c.

  The partition 13b is fixed to the drive shaft 3 and is rotatable together with the drive shaft 3. The partition 13b has a partition bottom wall 136 and a guide portion 137. An insertion hole 136 a through which the drive shaft 3 is inserted is provided in the partition bottom wall 136. The partition bottom wall 136 is press-fitted into the drive shaft 3 through the insertion hole 136a. The partition bottom wall 136 extends from the drive shaft 3 in the radial direction. The guide portion 137 extends in the direction of the drive axis O from the partition bottom wall 136 so as to be away from the swash plate 5, and has a cylindrical shape concentric with the drive axis O. The guide portion 137 is formed with a first engagement portion 137 a that protrudes toward the drive shaft 3. The guide part 137 slides along the inner surface of the peripheral wall 130 of the moving body 13a described later. An O-ring 138 is provided between the outer peripheral surface of the guide portion 137 and the inner peripheral surface of the peripheral wall 130.

  The movable body 13a is rotated together with the drive shaft 3 when the drive shaft 3 is inserted. The moving body 13a is movable in the direction of the drive axis O with respect to the partitioning body 13b. The moving body 13 a is connected to the swash plate 5. The moving body 13a is disposed so as to pull the swash plate 5 and increase the inclination angle when the pressure in the control pressure chamber 13c increases.

  More specifically, the moving body 13 a includes a peripheral wall 130, a moving bottom wall 131, and a sliding portion 132. The peripheral wall 130 extends from the moving bottom wall 131 toward the swash plate 5 in the direction of the drive axis O, and surrounds the partition 13b. The peripheral wall 130 has a cylindrical shape concentric with the drive shaft center O. A connecting portion 133 that is connected to the swash plate 5 is formed at the front end of the peripheral wall 130. The movable bottom wall 131 extends from the peripheral wall 130 toward the drive shaft 3. The sliding part 132 extends in the direction of the drive axis O from the moving bottom wall 131 so as to approach the swash plate 5. The sliding portion 132 is formed with a second engaging portion 132a protruding in the radial direction. The sliding portion 132 is provided with an insertion hole 132 b through which the drive shaft 3 is inserted. The sliding portion 132 can slide on the outer periphery of the drive shaft 3 by the insertion hole 132b. An O-ring 135 is provided between the inner peripheral surface of the sliding part 132 and the outer peripheral surface of the drive shaft 3.

An inner storage portion 140 is formed between the moving bottom wall 131 and the peripheral wall 130 in the moving body 13a. The inner storage part 140 can store the guide part 137. Specifically, when the swash plate angle is minimum, the guide portion 137 and the sliding portion 132 are arranged to overlap each other .

  In addition, an outer storage portion 141 is formed between the moving bottom wall 131 and the sliding portion 132 in the moving body 13a. The outer storage portion 141 can store the second flange portion 431. Specifically, when the swash plate angle is maximum, the movable bottom wall 131 and the second flange portion 431 are arranged to overlap each other.

  The other end side of the ring plate 45 is connected to the connecting portion 133 of the moving body 13a by a third pin 47c. Thereby, the other end side of the ring plate 45, that is, 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.

  The control pressure chamber 13c is partitioned by a partition body 13b and a moving body 13a. The control pressure chamber 13c allows the moving body 13a to move by introducing the refrigerant from the second discharge chamber 29b. Further, the volume of the control pressure chamber 13c is changed by the movement of the moving body 13a. The control pressure chamber 13 c is partitioned from the swash plate chamber 33 by the moving body 13 a, the partition body 13 b, and the shaft body 30.

A coil spring 50 is provided in the control pressure chamber 13c. One end 50a of the coil spring 50 is engaged with the first engaging portion 137a, and the other end 50b is engaged with the second engaging portion 132a. Further, when the free length of the coil spring 50, the inclination angle of the swash plate 5 is set to be an intermediate angle between the maximum and minimum. For this reason, the coil spring 50 biases the inclination angle to increase when the inclination angle of the swash plate 5 is minimum. Further, the coil spring 50 biases the inclination angle to be reduced when the inclination angle of the swash plate 5 is maximum. The coil spring 50 corresponds to the biasing member in the present invention.

  The coil spring 50 is rotated together with the partitioning body 13b and the moving body 13a. The coil spring 50 is housed between the guide portion 137 and the sliding portion 132 when the volume of the control pressure chamber 13c is the smallest.

  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 and second cylinder bores 21a and 23a. For this reason, the first and second compression chambers 21e and 23f change in volume according to the piston stroke. Thus, in this compressor, the first and second compression chambers 21e and 23f are respectively compressed by the suction stroke for sucking the refrigerant gas, and the compression stroke for compressing the refrigerant gas in the first and second compression chambers 21e and 23f. The discharge stroke and the like in which the refrigerant gas is discharged from the first and second compression chambers 21e and 23f are repeated.

  During these suction strokes and the like, a piston compression force that changes 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.

More specifically, in the control mechanism 15, if the control valve 15c shown in FIG. 3 increases the opening of the low-pressure passage 15a, the pressure in the pressure adjusting chamber 31 decreases, and the pressure in the control pressure chamber 13c decreases. Get smaller. Thereby, the pressure in the control pressure chamber 13c becomes substantially equal to the pressure in the second suction chamber 27b. Therefore, as shown in FIGS. 2 and 5, in the actuator 13, the sliding portion 132 of the moving body 13 a slides on the outer peripheral surface of the drive shaft 3 toward the front side of the swash plate chamber 33 and the peripheral wall 130. Also, it slides on the guide part 137 of the partition 13b toward the front side of the swash plate chamber 33. That is, the moving body 13a moves forward by the pressure of the swash plate chamber 33. At this time, the moving body 13a moves forward while resisting the biasing force of the coil spring 50 . Thereby, in this compressor, the moving body 13 a moves to the front side of the swash plate chamber 33 and approaches the lug arm 49.

Thereby, the other end side of the swash plate 5 swings clockwise around the action axis M3. Further, the rear end of the lug arm 49 swings counterclockwise around the first swing axis M1, and the front end of the lug arm 49 swings counterclockwise around the second swing axis M2. For this reason, the lug arm 49 comes close to the first flange portion 430 of the first shaft support member 43a. As a result, the swash plate 5 swings about the first swing axis M1 as a 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, when the minimum volume of the control pressure chamber 13c, the minimum inclination angle.

On the other hand, in the control mechanism 15, if the control valve 15c shown in FIG. 3 reduces the opening degree of the low pressure passage 15a, the pressure in the pressure adjusting chamber 31 increases, and the pressure in the control pressure chamber 13c increases. Therefore, as shown in FIGS. 1 and 4, in the actuator 13, the sliding portion 132 of the moving body 13 a slides on the outer peripheral surface of the drive shaft 3 toward the rear side of the swash plate chamber 33 and the peripheral wall 130. Also, it slides on the guide part 137 of the partition 13b toward the rear side of the swash plate chamber 33. That is, the moving body 13a moves backward by the pressure inside the control pressure chamber 13c. At this time, the moving body 13a moves backward while bending over to the urging force of the coil spring 50 . Thereby, in this compressor, the moving body 13 a moves to the rear side of the swash plate chamber 33 and is remote from the lug arm 49.

  As a result, the moving body 13a pulls the lower end side of the swash plate 5 to the rear side of the swash plate chamber 33 through the connecting portion 133 at the action axis M3. As a result, the other end of 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 lug arm 49 is separated from the first flange portion 430 of the first shaft support member 43a. As a result, the swash plate 5 swings around the first swing axis M1 as a fulcrum, and swings in the opposite direction to the case where the tilt angle becomes smaller. 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 becomes the maximum inclination angle when the control pressure chamber 13c has the maximum volume.

  In this compressor, the moving body 13 a pulls the swash plate 5 when the inclination angle of the swash plate 5 is increased. 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 increasing direction of the tilt angle. For this reason, in this compressor, even if the moving body 13a is enlarged in order to increase the traction force with respect to the swash plate 5, interference between the moving body 13a and the swash plate 5 hardly occurs. Thereby, in this compressor, in order to avoid interference, it is not necessary to make the mobile body 13a into a complicated shape, and the mobile body 13a is not required to have a great rigidity.

  For this reason, in this compressor, in order to realize high controllability, it is possible to thin the moving body 13a to some extent and increase the size in the radial direction. Furthermore, the moving body 13a can be reduced in weight.

Moreover, in this compressor, since the coil spring 50 is disposed using the inside of the control pressure chamber 13c that changes the inclination angle of the swash plate 5, compared with the case where the biasing member is provided outside the control pressure chamber 13c. Thus, the axial length of the compressor is shortened.

Further, in this compressor, the swash plate 5 can be pulled only by the coil spring 50 via the moving body 13 a of the actuator 13. For this reason, the biasing force of the coil spring 50 is only impaired by the resistance force when only the moving body 13a moves in the direction of the drive axis O. For this reason, the biasing force of the coil spring 50 is more easily transmitted to the swash plate 5 than the conventional compressor, and the inclination angle of the swash plate 5 is easily increased.

In particular, in this compressor, when the inclination angle of the swash plate 5 is the minimum, the coil spring 50 increases the inclination angle of the swash plate 5. For this reason, when the swash plate 5 continues to rotate, the piston 9 reciprocates in the first and second cylinder bores 21a and 23a with a certain amount of stroke. For this reason, the piston 9 can perform compression work in the first and second compression chambers 21e and 23f, and high-pressure refrigerant can be stored in the first and second discharge chambers 29a and 29b. Therefore, the control pressure chamber 13c of the actuator 13 can be increased in pressure by the refrigerant in the first and second discharge chambers 29a and 29b, and the moving body 13a of the actuator 13 can move in the direction of the drive axis O. become. That is, in the compressor, the coil spring 50 assists the return of the inclination angle of the swash plate 5 until the actuator 13 increases the inclination angle of the swash plate 5 from the state where the inclination angle of the swash plate 5 is minimum. it can.

  Therefore, this compressor can realize downsizing, excellent durability and weight reduction, and can realize a reduction in manufacturing cost and high controllability.

In this compressor, one end portion 50a of the coil spring 50 is engaged with the first engagement portion 137a, and the other end portion 50b is engaged with the second engagement portion 132a. For this reason, when the inclination angle of the swash plate 5 is maximum, the coil spring 50 urges the moving body 13a in a direction to decrease the inclination angle of the swash plate 5 in order to return to the free length. Thereby, the swash plate 5 becomes easy to displace from the maximum inclination angle to the decreasing direction of the inclination angle, and more excellent controllability can be realized.

  The single coil spring 50 functions as an urging member by extension from the shortened state to the free length, and functions as an urging member by contraction from the extended state to the free length. For this reason, it is not necessary to provide a plurality of urging members in the control pressure chamber 13c, and the number of parts can be reduced.

The first engaging portion 137a engages with one end portion 50a of the coil spring 50, since the second engaging portion 132a is engaged with the other end portion 50b, a coil spring 50 first engaging portion 137a and the second 2 can be easily engaged with the engaging portion 132a.

  Furthermore, since the guide part 137 and the sliding part 132 overlap when the swash plate angle is minimum, the axial length is not increased, and the compressor can be further downsized. Further, since the coil spring 50 is also housed between the guide portion 137 and the sliding portion 132, the coil spring 50 does not hinder downsizing of the compressor. Further, since the coil spring 50 also overlaps with the guide portion 137 and the sliding portion 132, the coil spring 50 that is long in the direction of the drive axis O can be employed, and the coil spring 50 can exhibit a sufficient urging force.

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

  For example, in the compressor control mechanism 15 according to the present invention, the control valve 15c may be provided for the high-pressure passage 15b, and the orifice 15d may be provided for the low-pressure passage 15a. In this case, the opening degree of the high-pressure passage 15b can be adjusted by the control valve 15c. As a result, the control pressure chamber 13c is quickly increased to a high pressure by the high pressure in the second discharge chamber 29b, so that the compression capacity can be increased rapidly.

  Further, the actuator 13 may be arranged on the front surface 5a side of the swash plate 5 and the lug arm 49 may be arranged on the rear surface 5b side of the swash plate 5 to constitute the compressor.

  Further, the compressor may be configured such that the compression chamber is formed only in one of the first cylinder block 21 or the second cylinder block 23.

  The present invention can be used for a refrigeration circuit, a heating circuit, a heating refrigeration circuit, and the like.

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 5 ... Swash plate 7 ... Link mechanism 9 ... Piston 11a ... Shoe (conversion mechanism)
11b ... shoe (conversion mechanism)
DESCRIPTION OF SYMBOLS 13 ... Actuator 13a ... Moving body 13b ... Partition body 13c ... Control pressure chamber 15 ... Control mechanism 21a ... 1st cylinder bore (cylinder bore)
23a ... Second cylinder bore (cylinder bore)
27a ... First suction chamber (suction chamber)
27b ... Second suction chamber (suction chamber)
29a ... 1st discharge chamber (discharge chamber)
29b ... second discharge chamber (discharge chamber)
33 ... Swash plate chamber 47a ... First pin (link mechanism)
47b ... 2nd pin (link mechanism)
50 ... Coil spring (biasing member)
50a ... one end 50b ... the other end 130 ... peripheral wall (moving body)
131 ... Moving bottom wall (moving body)
132 ... sliding part (moving body)
132a ... 2nd engaging part 136 ... division bottom wall (compartment body)
137 ... Guide part (partition body)
137a ... 1st engaging part

Claims (3)

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 shaft center of the drive shaft; A conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the inclination angle by rotation of the swash plate, an actuator provided in the swash plate chamber and capable of changing the inclination angle, and the actuator And a control mechanism for controlling
The actuator is partitioned by a partition provided on the drive shaft, a movable body connected to the swash plate and movable in the drive shaft center direction in the swash plate chamber, and the partition and the movable body. A control pressure chamber that moves the movable body by introducing the 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.
A biasing member that increases the tilt angle when the tilt angle is minimum is provided between the partition body and the movable body ,
The movable body extends from the movable bottom wall in a direction approaching the swash plate, a peripheral wall extending in the drive axis direction and surrounding the partition, a movable bottom wall extending from the peripheral wall toward the drive shaft, The drive shaft and a sliding portion that slides;
The compartment has a compartment bottom wall and a guide portion extending from the compartment bottom wall in a direction away from the swash plate along the inner surface of the peripheral wall,
When the swash plate angle is minimum, the guide portion and the sliding portion are arranged to overlap,
The variable displacement swash plate compressor , wherein the urging member is housed between the guide portion and the sliding portion . The biasing member is a single coil spring extending in the drive axis direction from one end to the other end,
The one end is fixed to the guide portion , and the other end is fixed to the sliding portion ;
The variable displacement swash plate compressor according to claim 1, wherein the biasing member reduces the swash plate angle when the swash plate angle is maximum. The guide portion has a first engagement portion engaged with the one end portion is formed,
Wherein the sliding portion is variable displacement swash plate type compressor according to claim 2, wherein the second engaging portion engaged with the other end portion is formed.

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