JP2017172420A - Variable displacement swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor capable of developing high controllability.SOLUTION: The compressor includes a driving shaft 3, a partition body 13b, and a movable body 13a, the partition body 13b having an O-ring 51b as a first seal member, the movable body 13a having an O-ring 51a as a second seal member, the O-ring 51b being located between the partition body 13b and the movable body 13a for sealing a space between a control pressure chamber 13c and a swash plate chamber 33 while being elastically deformed, the O-ring 51a being located between the driving shaft 3 and the movable body 13a for sealing a space between the control pressure chamber 13c and the swash plate chamber 33 while being elastically deformed. The compressor is formed so that a second space S2 between the partition body 13b and the movable body 13a when the inclination angle of a swash plate 5 is minimum is larger than a first space S1 between the partition body 13b and the movable body 13a when the inclination angle is maximum.SELECTED DRAWING: Figure 4

Description

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

  1 and 3 of Patent Document 1 disclose a conventional variable displacement swash plate compressor (hereinafter simply referred to as a compressor). The compressor includes a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a moving body, a control pressure chamber, and a control mechanism. A plurality of cylinder bores are formed in the housing, and a swash plate chamber and a control pressure chamber are formed. The housing is formed with a main shaft through hole connected to the swash plate chamber and the control pressure chamber.

  The drive shaft is rotatably supported on the housing. The swash plate is provided in the swash plate chamber and can be rotated by rotation of the drive shaft. The link mechanism is provided between the drive shaft and the swash plate, and allows the inclination angle of the swash plate to be changed. 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. Each piston reciprocates in each cylinder bore and partitions a compression chamber in each cylinder bore. A shoe as a conversion mechanism is provided between each piston and the swash plate. The shoe makes a pair for each piston, and reciprocates each piston with a stroke corresponding to the inclination angle by the rotation of the swash plate.

  The moving body is inserted into the drive shaft and disposed in the main shaft through hole. The moving body slides in the direction of the drive axis in the main shaft through hole to change the inclination angle. The moving body partitions the control pressure chamber and the swash plate chamber. Moreover, the moving body has a sealing member. The sealing member seals between the control pressure chamber and the swash plate chamber while being elastically deformed between the outer peripheral surface of the movable body and the inner peripheral surface of the spindle through hole. The control mechanism controls the pressure in the control pressure chamber.

  In this compressor, when the control mechanism increases the pressure in the control pressure chamber, the moving body slides in the direction of the drive shaft in the main shaft through hole toward the front housing side. As a result, the link mechanism increases the inclination angle of the swash plate. Thus, in this compressor, the discharge capacity per rotation of the drive shaft increases. On the other hand, when the control mechanism lowers the pressure in the control pressure chamber, the moving body slides in the direction of the drive shaft in the main shaft through hole toward the rear housing side. Thereby, the link mechanism decreases the inclination angle of the swash plate, and the discharge capacity decreases.

JP-A-5-172052

  In the conventional compressor, as the moving body slides in the main shaft through hole, the sealing member slides while elastically deforming between the outer peripheral surface of the moving body and the inner peripheral surface of the main shaft through hole. Therefore, the sealing member generates a resistance force when the moving body slides in the main shaft through hole. For this reason, in increasing the discharge capacity by increasing the tilt angle, the pressure in the control pressure chamber is increased so that the movable body can slide while overcoming the resistance of the sealing member applied to the movable body. It is necessary to increase the pressure in the control pressure chamber applied to the body. In this regard, when the pressure in the control pressure chamber is low, the resistance force of the sealing member applied to the moving body is relatively greater than the pressure in the control pressure chamber applied to the moving body. For this reason, it is difficult for the moving body to slide, and it is difficult to increase the inclination angle, so it is difficult to increase the discharge capacity. For this reason, this compressor has low controllability.

  The present invention has been made in view of the above-described conventional situation, and an object to be solved is to provide a variable displacement swash plate compressor capable of exhibiting high controllability.

A variable capacity swash plate compressor of the present invention includes a housing in which a swash plate chamber and a plurality of cylinder bores are formed,
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the drive axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided on the drive shaft and rotatable integrally with the drive shaft in the swash plate chamber;
A movement that is provided on the drive shaft, can rotate integrally with the drive shaft in the swash plate chamber, and slides in the drive shaft center direction with respect to the drive shaft and the partition body to change the inclination angle. Body,
A control pressure chamber that is partitioned by the partition body and the moving body, and the internal pressure is increased to move the moving body to increase the tilt angle;
A control mechanism for controlling the pressure in the control pressure chamber,
The partition has a first sealing member that is located between the partition and the movable body and seals between the control pressure chamber and the swash plate chamber while being elastically deformed.
The movable body has a second sealing member that is located between the drive shaft and the movable body and seals between the control pressure chamber and the swash plate chamber while being elastically deformed.
At least one of the partition body and the movable body and between the drive shaft and the movable body has a larger interval when the inclination angle is minimum than the interval when the inclination angle is maximum. It is formed.

  In the compressor of the present invention, the interval between the partition body and the moving body when the pressure in the control pressure chamber is low and the inclination angle is minimum is high, the pressure in the control pressure chamber is high and the inclination angle is maximum. If it is formed larger than the time interval, the elastic deformation amount of the first sealing member becomes smaller when the inclination angle is minimum than when the inclination angle is maximum, that is, when the pressure in the control pressure chamber is low. . Similarly, if the distance between the drive shaft and the moving body when the inclination angle is minimum is larger than the distance when the inclination angle is maximum, the elastic deformation amount of the second sealing member Is smaller when the tilt angle is minimum than when the tilt angle is maximum.

  Thus, in this compressor, when the pressure in the control pressure chamber is low and the inclination angle is minimum, the amount of elastic deformation of at least one of the first sealing member and the second sealing member can be reduced. . As a result, when the pressure in the control pressure chamber is low and the pressure in the control pressure chamber applied to the moving body is small, that is, when the inclination angle is small, the pressure in the control pressure chamber applied to the moving body is reduced. The resistance force of the first sealing member and the second sealing member to be applied becomes relatively small. For this reason, in this compressor, even when the pressure in the control pressure chamber applied to the moving body is small, the moving body easily slides, and therefore the inclination angle is likely to increase.

  Therefore, the variable capacity swash plate compressor of the present invention exhibits high controllability.

  In the compressor of the present invention, it is preferable that the interval when the inclination angle is minimum is formed larger than the interval when the inclination angle is maximum only between the partition body and the moving body.

  In this case, manufacturing can be facilitated. Moreover, since the partition body provided with the first sealing member is provided on the drive shaft, the first sealing member is larger than the second sealing member provided on the movable body. For this reason, by reducing the amount of elastic deformation of the first sealing member when the inclination angle is minimum, the first pressure applied to the moving body with respect to the pressure in the control pressure chamber applied to the moving body when the inclination angle is small. The resistance force of the 1 sealing member and the 2nd sealing member can be made small suitably.

  The variable capacity swash plate compressor of the present invention exhibits high controllability.

FIG. 1 is a cross-sectional view showing a state where the inclination angle is minimum in the compressor of the first embodiment. FIG. 2 is a cross-sectional view showing a state where the inclination angle is maximum in the compressor of the first embodiment. FIG. 3 is a schematic diagram illustrating a control mechanism according to the compressor of the first embodiment. FIG. 4 is an enlarged cross-sectional view of a main part illustrating the drive shaft, the partition body, the moving body, the control pressure chamber, and the like according to the compressor of the first embodiment. FIG. 5 is an enlarged cross-sectional view of a main part illustrating the interval between the partition body and the moving body when the inclination angle is large, according to the compressor of the first embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating the interval between the partition body and the moving body when the inclination angle is small, according to the compressor of the first embodiment. FIG. 7 is an enlarged cross-sectional view of a main part showing a drive shaft, a partition body, a moving body, a control pressure chamber, and the like, in the compressor of the comparative example. FIG. 8 is a graph showing a change in the pressure in the control pressure chamber applied to the moving body and a change in the resistance force of each O-ring applied to the moving body due to a change in the pressure in the control pressure chamber in the compressor of the comparative example. It is. FIG. 9 relates to the compressor of the first embodiment, and shows changes in the pressure in the control pressure chamber applied to the moving body and changes in the resistance force of each O-ring applied to the moving body due to changes in the pressure in the control pressure chamber. It is a graph. FIG. 10 is an enlarged cross-sectional view of a main part illustrating a drive shaft, a partition body, a moving body, a control pressure chamber, and the like, according to the compressor of the second embodiment. FIG. 11 is an enlarged cross-sectional view of a main part illustrating a drive shaft, a partition body, a moving body, a control pressure chamber, and the like, according to the compressor of the third embodiment. FIG. 12 is an enlarged cross-sectional view of a main part illustrating a drive shaft, a partitioning body, a moving body, a control pressure chamber, and the like according to the compressor of the fourth embodiment. FIG. 13 is an enlarged cross-sectional view of a main part illustrating the interval between the drive shaft and the moving body when the inclination angle is large, according to the compressor of the fourth embodiment. FIG. 14 is an enlarged cross-sectional view of a main part illustrating the interval between the drive shaft and the moving body when the inclination angle is small, according to the compressor of the fourth embodiment. FIG. 15 is an enlarged cross-sectional view of a main part illustrating a drive shaft, a partition body, a moving body, a control pressure chamber, and the like, according to the compressor of the fifth embodiment. FIG. 16 is an enlarged cross-sectional view of a main part illustrating a drive shaft, a partition body, a moving body, a control pressure chamber, and the like according to the compressor of the sixth embodiment.

  Embodiments 1 to 6 embodying the present invention will be described below with reference to the drawings. All of these compressors are mounted on a vehicle, and constitute a refrigeration circuit of a vehicle air conditioner.

Example 1
As shown in FIGS. 1 and 2, the compressor of the first embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, and a plurality of pairs of shoes 11a and 11b. And an actuator 13. In addition, the compressor includes a control mechanism 15 shown in FIG.

  As shown in FIGS. 1 and 2, the housing 1 includes a front housing 17, a rear housing 19, a first cylinder block 21, a second cylinder block 23, a first valve forming plate 39, and a second valve forming. Plate 41. In this embodiment, the front-rear direction of the compressor is defined with the side where the front housing 17 is located as the front side of the compressor and the side where the rear housing 19 is located as the rear side of the compressor. 1 and 2 is defined as the upper side of the compressor, and the lower side of the page is defined as the lower side of the compressor to define the vertical direction of the compressor. In FIG. 4 and subsequent figures, the front-rear direction and the vertical direction are displayed in correspondence with FIGS. In addition, the front-back direction in Example 1 is an example, and the attitude | position of the compressor of this invention is suitably changed according to the vehicle etc. which are mounted.

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

  The rear housing 19 is provided with part of the control mechanism 15 described above. The rear housing 19 includes a second suction chamber 27b, a second discharge chamber 29b, and a pressure adjustment chamber 31. The pressure adjustment chamber 31 is located in the 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 also formed in an annular shape and is located on the outer peripheral side of the second suction chamber 27b. The first discharge chamber 29a and the second discharge chamber 29b communicate with each other through a discharge passage (not shown). The discharge passage is connected to a discharge port (not shown).

  The first cylinder block 21 is provided between the front housing 17 and the second cylinder block 23. The first cylinder block 21 is formed with a plurality of first cylinder bores 21 a extending in the direction of the drive axis O of the drive shaft 3. The first cylinder bores 21a are arranged at equiangular intervals in the circumferential direction.

  The first cylinder block 21 is formed with a first shaft hole 21b through which the drive shaft 3 is inserted. A first sliding bearing 22a is provided in the first shaft hole 21b. Further, the first cylinder block 21 is formed with a first recess 21c communicating with the first shaft hole 21b from the rear side of the compressor. The first recess 21c is coaxial with the first shaft hole 21b. The first recess 21c has an inner diameter larger than that of the first shaft hole 21b. A first thrust bearing 35a is provided in the first recess 21c. The first cylinder block 21 is formed with a first communication path 37a extending in the front-rear direction.

  The second cylinder block 23 is provided between the first cylinder block 21 and the rear housing 19. The second cylinder block 23 is joined to the first cylinder block 21, thereby forming a swash plate chamber 33 with the first cylinder block 21. The swash plate chamber 33 communicates with the first recess 21c. Thereby, the first recess 21 c constitutes a part of the swash plate chamber 33. The swash plate chamber 33 communicates with the first communication path 37a.

  The second cylinder block 23 is formed with a plurality of second cylinder bores 23 a extending in the direction of the drive axis O of the drive shaft 3. Like the first cylinder bores 21a, the second cylinder bores 23a are arranged at equiangular intervals in the circumferential direction, and are coaxially and paired with the first cylinder bores 21a in the front-rear direction. Each first cylinder bore 21a and each second cylinder bore 23a are formed to have the same diameter. In addition, if the 1st cylinder bore 21a and the 2nd cylinder bore 23a have made a pair, these numbers can be designed suitably. Moreover, you may form in the magnitude | size of a different diameter in each 1st cylinder bore 21a and each 2nd cylinder bore 23a. Furthermore, the axial centers of the paired first cylinder bore 21a and second cylinder bore 23a may be shifted.

  The second cylinder block 23 is formed with a second shaft hole 23b through which the drive shaft 3 is inserted. A second sliding bearing 22b is provided in the second shaft hole 23b. In place of the first and second sliding bearings 22a and 22b, rolling bearings may be provided in the first and second shaft holes 21b and 23b.

  The second cylinder block 23 is formed with a second recess 23c communicating with the second shaft hole 23b from the front side of the compressor. The second recess 23c is coaxial with the second shaft hole 23b. The second recess 23c has an inner diameter larger than that of the second shaft hole 23b. The second recess 23 c is also in communication with the swash plate chamber 33 and constitutes a part of the swash plate chamber 33. A second thrust bearing 35b is provided in the second recess 23c.

  The second cylinder block 23 is formed with a suction port 330 and a second communication path 37b. The swash plate chamber 33 is connected via an intake port 330 to an evaporator (not shown) constituting a pipe line. The second communication path 37 b extends in the front-rear direction and communicates with the swash plate chamber 33.

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

  In the first valve forming plate 39, the same number of first suction holes 390a and first discharge holes 390b as the first cylinder bores 21a are formed, and a first suction communication hole 390c is formed. Each first cylinder bore 21a communicates with the first suction chamber 27a through each first suction hole 390a. Each first cylinder bore 21a communicates with the first discharge chamber 29a through each first discharge hole 390b. The first suction chamber 27a and the first communication path 37a communicate with each other through the first suction communication hole 390c.

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

  In the second valve forming plate 41, the same number of second suction holes 410a and second discharge holes 410b as the second cylinder bores 23a are formed, and a second suction communication hole 410c is formed. Each second cylinder bore 23a communicates with the second suction chamber 27b through each second suction hole 410a. Each second cylinder bore 23a communicates with the second discharge chamber 29b through each second discharge hole 410b. The second suction chamber 27b and the second communication path 37b communicate with each other through the second suction communication hole 410c.

  Although not shown, the first valve forming plate 39 includes a suction reed valve capable of opening and closing each first suction hole 390a by elastic deformation, and a discharge reed valve capable of opening and closing each second discharge hole 390b by elastic deformation. A retainer plate that regulates the maximum opening of the discharge reed valve is provided. The same applies to the second valve forming plate 41. The first cylinder block 21 and the second cylinder block 23 are each provided with a retainer groove for restricting the maximum opening of each suction reed valve.

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

  The drive shaft 3 includes a drive shaft main body 30, a first support member 43a, and a second support member 43b. A screw portion 3 a is formed at the front end of the drive shaft 3. The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) via the screw portion 3a. The drive shaft 3 is formed with an axial path 3b and a radial path 3c. Details of the axial path 3b and the path 3c will be described later.

  The drive shaft main body 30 extends from the front side of the housing 1 toward the rear side in the axial direction. A first small diameter portion 30 a is formed on the front side of the drive shaft main body 30. A second small diameter portion 30 b is formed on the rear side of the drive shaft main body 30.

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

  The first support member 43 a is formed in a cylindrical shape having the drive axis O of the drive shaft 3 as the central axis. The first support member 43 a is press-fitted into the first small diameter portion 30 a of the drive shaft main body 30. The first support member 43a is provided with a first flange 430 and an attachment portion (not shown) through which a second pin 47b described later is inserted.

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

  The second support member 43b is also formed in a cylindrical shape having the drive shaft O of the drive shaft 3 as the central axis. The second support member 43b is press-fitted into the second small diameter portion 30b of the drive shaft main body 30, and is located at the rear end of the second small diameter portion 30b. A second flange 431 is formed at the front end of the second support member 43b. In the second support member 43b, a first seal ring 46a and a second seal ring 46b are provided behind the second flange 431.

  In the housing 1, the drive shaft 3 is connected to the shaft seal device 25, the first suction chamber 27 a, the first and second shaft holes 21 b and 23 b, the first and second thrust bearings 35 a and 35 b, the swash plate chamber 33, and the pressure adjustment chamber 31. It is inserted. Thus, the drive shaft 3 is supported by the housing 1 and can rotate around the drive axis O parallel to the front-rear direction of the compressor. In addition, when the drive shaft 3 is supported by the housing 1, the first flange 430 sandwiches the first thrust bearing 35a from the axial direction between the first flange 430 and the front wall of the first recess 21c. The second flange 431 sandwiches the second thrust bearing 35b from the axial direction between the second flange 431 and the rear wall of the second recess 23c. The first seal ring 46 a and the second seal ring 46 b are located in the second shaft hole 23 b and seal between the pressure adjustment chamber 31 and the swash plate chamber 33.

  The swash plate 5 has an annular flat plate shape and has a front surface 5a and a rear surface 5b. The front surface 5 a faces the front side of the compressor in the swash plate chamber 33, that is, the front housing 17 side. The rear surface 5 b faces the rear side of the compressor in the swash plate chamber 33, that is, the rear housing 19 side.

  The swash plate 5 has a ring plate 45. The ring plate 45 is formed in an annular flat plate shape, and an insertion hole 45a is formed at the center. The swash plate 5 is attached to the drive shaft 3 by inserting the drive shaft main body 30 through the insertion hole 45 a in the swash plate chamber 33. Further, the ring plate 45 is formed with a groove portion 45b penetrating from the front surface 5a side to the rear surface 5b side of the swash plate 5. Further, the ring plate 45 is formed with a connecting portion 45 c that protrudes rearward of the swash plate 5. The connecting portion 45c is located on the opposite side of the groove 45b with respect to the drive axis O.

  The link mechanism 7 has a lug arm 49. The lug arm 49 is disposed in front of the swash plate 5 in the swash plate chamber 33 and is positioned between the swash plate 5 and the first support member 43a. The lug arm 49 is formed so as to be substantially L-shaped from the front to the rear. The lug arm 49 has a weight portion 49a. The shape of the weight portion 49a can be designed as appropriate.

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

  The front end side of the lug arm 49 is connected to the first support member 43a by the second pin 47b. As a result, the lug arm 49 can swing around the second swing axis M2 with respect to the first support member 43a, that is, the drive shaft 3, with the second pivot 47b serving as the second pivot axis M2. It is supported. In addition to the lug arm 49 and the first and second pins 47a and 47b, the link arm 7 and the third pin 47c, which will be described later, constitute the link mechanism 7 in the present invention.

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

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

  As shown in FIG.1 and FIG.2, each piston 9 has the 1st head 9a in the front end, respectively, and has the 2nd head 9b in the rear end. That is, each piston 9 is a double-headed piston. Each first head portion 9a is accommodated in each first cylinder bore 21a so as to reciprocate. The first compression chambers 53a are formed in the first cylinder bores 21a by the first heads 9a and the first valve forming plate 39, respectively. Each of the second heads 9b is housed so as to reciprocate within the second cylinder bore 23a. The second compression chambers 53b are formed in the second cylinder bores 23a by the second heads 9b and the second valve forming plate 41, respectively.

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

  Here, in this compressor, the stroke of each piston 9 changes with the change of the inclination angle of the swash plate 5, so that the link mechanism 7 is connected to each of the first head 9 a and each second head 9 b. Move the top dead center position. Specifically, as shown in FIG. 1, as the inclination angle of the swash plate 5 becomes smaller, the link mechanism 7 moves the second head 9b than the top dead center position of each first head 9a. Move the top dead center position greatly.

  The actuator 13 is disposed behind the swash plate 5 in the swash plate chamber 33. More specifically, the actuator 13 is located on the second cylinder block 23 side with respect to the swash plate 5 in the swash plate chamber 33. Thereby, the actuator 13 can enter the second recess 23c.

  As shown in FIG. 4, the actuator 13 has a moving body 13a, a partitioning body 13b, and a control pressure chamber 13c. The control pressure chamber 13c is formed between the movable body 13a and the partition body 13b.

  The moving body 13a includes a rear wall 130, a peripheral wall 131, a pair of connecting arms 132, and an O-ring 51a. The O-ring 51a is an example of a second sealing member in the present invention. In FIG. 1 and the like, only one of the connecting arms 132 is shown.

  As shown in FIG. 4, the rear wall 130 is located behind the movable body 13 a and extends in the radial direction in a direction away from the drive axis O. Further, an insertion hole 130a is provided in the rear wall 130. Furthermore, a first groove 130b is formed in the rear wall 130 so as to face the insertion hole 130a. The O-ring 51a is disposed in the first concave groove 130b. 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. Due to the rear wall 130 and the peripheral wall 131, the movable body 13a has a bottomed cylindrical shape. Each connecting arm 132 is formed at the front end of the peripheral wall 131 and extends from the peripheral wall 131 toward the front of the compressor. Each connecting arm 132 is formed with an insertion hole 132a through which a third pin 47c described later is inserted.

  The partition 13b has a larger diameter than the drive shaft main body 30, and is formed in a disc shape having substantially the same diameter as a first inner diameter L1 of the moving body 13a described later. The partition 13b has an O-ring 51b. The O-ring 51b is an example of a first sealing member in the present invention. As the first and second sealing members, instead of the O-ring 51a and the O-ring 51b, for example, a so-called X-ring having a substantially X-shaped cross section may be employed.

  The partition 13b has an insertion hole 133 extending through the center. Moreover, the 2nd ditch | groove 134a is formed in the outer peripheral surface 134 of the division body 13b. The O-ring 51b is disposed in the second concave groove 134a. As described above, since the partition 13b is formed with a larger diameter than the drive shaft main body 30, the O-ring 51b is formed with a larger diameter than the O-ring 51a.

  The second small diameter portion 30b of the drive shaft main body 30 is inserted through the insertion hole 130a of the moving body 13a. Thereby, the moving body 13a can slide the second small diameter portion 30b in the direction of the drive axis O. On the other hand, the 2nd small diameter part 30b is press-fit with respect to the insertion hole 133 of the division body 13b. Thereby, the partition body 13b is fixed to the second small diameter portion 30b, and the partition body 13b can rotate together with the drive shaft main body 30. The partition 13b may also be configured to be inserted into the second small diameter portion 30b so as to be slidable in the direction of the drive axis O.

  Further, the partition 13b is fixed to the second small diameter portion 30b so as to be disposed in the moving body 13a and surrounded by the peripheral wall 131. Thereby, when the movable body 13a slides in the direction of the drive axis O, the inner peripheral surface 131a of the peripheral wall 131 and the outer peripheral surface 134 of the partition 13b slide.

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

  The O-ring 51a is positioned between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a when the moving body 13a is inserted through the second small diameter portion 30b. The O-ring 51a seals between the control pressure chamber 13c and the swash plate chamber 33 by elastically deforming between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a. Similarly, the O-ring 51b is positioned between the partition body 13b and the moving body 13a when the partition body 13b is surrounded by the peripheral wall 131. The O-ring 51b seals between the control pressure chamber 13c and the swash plate chamber 33 by elastically deforming between the outer peripheral surface 134 of the partition 13b and the inner peripheral surface 131a of the peripheral wall 131. In this way, the airtightness between the control pressure chamber 13c and the swash plate chamber 33 is ensured by the O-rings 51a and 51b.

  Further, on the inner peripheral surface 131a of the peripheral wall 131, the first sliding region X1 that slides with the outer peripheral surface 134 of the partition 13b when the moving body 13a slides the second small diameter portion 30b in the direction of the drive axis O. Is stipulated. In addition, a second sliding region X2 in which the movable body 13a slides is defined on the outer peripheral surface 300 of the second small diameter portion 30b.

  Here, the 1st taper part 135 which comprises a part of 1st sliding area | region X1 is formed in the internal peripheral surface 131a. The first taper portion 135 extends linearly so as to increase in diameter from the front toward the rear. Thereby, the moving body 13a is formed with the first inner diameter L1 in front of the first taper portion 135, whereas the moving body 13a has a larger diameter than the first inner diameter L1 behind the first taper portion 135. A second inner diameter L2 is formed.

Therefore, in this actuator 13, as shown in FIG. 5, the movable body 13a slides behind the second small diameter portion 30b in the direction of the drive axis O, and in the first sliding region X1, the partitioning body 13b When it is located ahead of the 1 taper part 135, the space between the outer peripheral surface 134 of the partition 13b and the inner peripheral surface 131a of the peripheral wall 131 is the first interval S1. On the other hand, as shown in FIG. 6, the movable body 13a slides in front of the second small-diameter portion 30b in the direction of the drive axis O, and in the first sliding region X1, the partition body 13b has the first tapered portion 135. In the case where it is located further rearward, the distance between the outer peripheral surface 134 and the inner peripheral surface 131a is the second interval S2 that is larger than the first interval S1. That is, in this actuator 13, in the 1st sliding area | region X1, as the division body 13b moves back the 1st taper part 135 toward back, between the outer peripheral surface 134 and the internal peripheral surface 131a from 1st space | interval S1. It changes so as to gradually increase up to the second interval S2. On the other hand, in this compressor, even when the moving body 13a slides in the second sliding region X2, the distance between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a remains constant. 5 and 6, the shapes of the first interval S1 and the second interval S2 are exaggerated for ease of explanation.

  As shown in FIGS. 1 and 2, each pulling arm 132 and the connecting portion 45c of the ring plate 45 are connected by a third pin 47c. As a result, the swash plate 5 is pivotally connected to the moving body 13a around the third axis M3 with the third pin 47c as the third axis M3. Here, the first pin 47a and the third pin 47c are arranged to face each other with the drive shaft body 30 in between. That is, each traction arm 132 is connected to the ring plate 45 on the side opposite to the groove 45b with the drive axis O as a reference.

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

  The axial path 3 b is formed in the second small diameter portion 30 b of the drive shaft main body 30. The axial path 3b extends in the direction of the drive axis O. The rear end of the axial path 3b opens to the rear end surface of the second small diameter portion 30b and communicates with the pressure adjustment chamber 31. The radial path 3c extends in the radial direction of the second small diameter part 30b while being connected to the front end side of the axial path 3b, and opens to the outer peripheral surface of the second small diameter part 30b. By providing the actuator 13 in the drive shaft main body 30 as described above, the path 3c opens into the control pressure chamber 13c. Thus, the pressure regulation chamber 31 and the control pressure chamber 13c are communicated with each other by the axial path 3b and the radial path 3c.

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

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

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

  In this compressor, a pipe connected to the evaporator is connected to the suction port 330 shown in FIGS. 1 and 2, and a pipe connected to the condenser is connected to the discharge port. 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, the swash plate 5 rotates as the drive shaft 3 rotates. Thereby, in each piston 9, each 1st head 9a reciprocates within each 1st cylinder bore 21a, and each 2nd head 9b reciprocates within each 2nd cylinder bore 23a. For this reason, the first and second compression chambers 53 a and 53 b change in volume according to the stroke of the piston 9. For this reason, in this compressor, the suction process of sucking the refrigerant gas from the first and second suction chambers 27a and 27b to the first and second compression chambers 53a and 53b, and the refrigerant gas in the first and second compression chambers 53a and 53b. The compression stroke to be compressed and the discharge stroke in which the compressed refrigerant gas is discharged into the first and second discharge chambers 29a and 29b are repeatedly performed. The refrigerant gas discharged into the first and second discharge chambers 29a and 29b is discharged from the discharge port to the condenser via the discharge passage through the discharge passage.

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

  Specifically, in the control mechanism 15 shown in FIG. 3, if the control valve 15c increases the opening degree of the extraction passage 15a, the pressure in the pressure adjusting chamber 31 and, in turn, the pressure in the control pressure chamber 13c are changed to the second suction chamber. The pressure in the control pressure chamber 13c and the swash plate chamber 33 are reduced, and the variable differential pressure, which is substantially equal to the pressure in 27b, is reduced. Thus, in the actuator 13, the pressure P1 (see FIGS. 8 and 9) in the pressure adjustment chamber 31 applied to the moving body 13a is reduced. For this reason, as shown in FIG. 1, the moving body 13 a slides forward on the second small diameter portion 30 b of the drive shaft body 30 by the piston compression force acting on the swash plate 5.

  Thereby, in this compressor, the swash plate 5 is urged in a direction in which the inclination angle decreases by the compression reaction force acting on the swash plate 5 via each piston 9. The compression reaction force is a resultant force of piston compression force that acts on the swash plate 5 by each piston 9. For this reason, the movable body 13a is pulled by the swash plate 5 through each connecting arm 132 and the connecting portion 45c, and moves to the front of the swash plate chamber 33 in the direction of the drive axis O. Thereby, in the swash plate 5, the ring plate 45 contacts the rear end of the return spring 44a. When the moving body 13a moves to the front side of the swash plate chamber 33, in this compressor, the swash plate 5 swings around the operating axis M3 while resisting the urging force of the return spring 44a. The rear end side of the lug arm 49 swings around the first swing axis M1, and the front end side of the lug arm 49 swings around the second swing axis M2. For this reason, the front end side of the lug arm 49 approaches the first flange 430 of the first support member 43a. As a result, the swash plate 5 swings with the operating axis M3 as the operating point and the first swinging axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 5 with respect to the direction orthogonal to the drive axis O of the drive shaft 3 decreases, and the stroke of each piston 9 decreases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 becomes small.

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

  In this compressor, the top dead center position of each second head 9b is moved away from the second valve forming plate 41 by decreasing the inclination angle of the swash plate 5 and decreasing the stroke of each piston 9. For this reason, in this compressor, when the inclination angle of the swash plate 5 approaches zero degrees, on the first compression chamber 53a side, the refrigerant gas slightly opens the discharge reed valve to perform the compression work, but the second compression On the chamber 53b side, the refrigerant gas cannot open the discharge reed valve and does not perform compression work.

  In addition, as described above, the pressure in the control pressure chamber 13c decreases, and the pressure P1 in the pressure adjustment chamber 31 applied to the moving body 13a decreases, so that the moving body 13a moves to the front side of the second small diameter portion 30b. If it slides toward, the division body 13b will move to the back side relatively in the 1st sliding area | region X1 shown in FIG. 4, sliding with the internal peripheral surface 131a of the surrounding wall 131. FIG. And as shown in FIG. 6, when the inclination-angle of the swash plate 5 becomes the minimum, the division body 13b is located in the back side rather than the 1st taper part 135 in the 1st sliding area | region X1. In the second sliding region X2, the moving body 13a is located on the front side.

  On the other hand, in the control mechanism 15 shown in FIG. 3, if the control valve 15c reduces the opening degree of the extraction passage 15a, the pressure in the pressure adjustment chamber 31 is increased by the pressure of the refrigerant gas in the second discharge chamber 29b, and the control is performed. The pressure in the pressure chamber 13c increases. For this reason, the variable differential pressure increases, and in the actuator 13, the pressure P1 in the pressure adjustment chamber 31 applied to the moving body 13a increases. As a result, the moving body 13a slides from the position shown in FIG. 1 toward the rear side of the second small diameter portion 30b in the direction of the drive axis O against the piston compression force acting on the swash plate 5. As shown in FIG. 2, it penetrates into the second recess 23c.

  As a result, in this compressor, the moving body 13a moves the swash plate 5 to the rear of the swash plate chamber 33 in the direction of the drive axis O through each connecting arm 132 and the connecting portion 45c while resisting the biasing force of the tilt angle reducing spring 44b. Tow. For this reason, in this compressor, the swash plate 5 swings around the action axis M3 in the opposite direction to the case where the inclination angle becomes small. Further, the rear end side of the lug arm 49 swings around the first swing axis M1 in the opposite direction to the case where the inclination angle becomes smaller, and the front end side of the lug arm 49 is opposite to the case where the inclination angle becomes smaller. Swings around the second swing axis M2. For this reason, the front end side of the lug arm 49 moves away from the first flange 430 of the first support member 43a. As a result, the swash plate 5 swings in the opposite direction to the case where the tilt angle becomes small, with the action axis M3 and the first swing axis M1 as the action point and the fulcrum, respectively. For this reason, the inclination angle of the swash plate 5 with respect to the direction orthogonal to the drive axis O of the drive shaft 3 increases, and the stroke of each piston 9 increases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 increases.

  Here, as described above, the pressure in the control pressure chamber 13c increases, and the pressure P1 in the pressure adjustment chamber 31 applied to the moving body 13a increases, so that the moving body 13a is behind the second small diameter portion 30b. If it slides toward, the division body 13b will move to the front side relatively in the 1st sliding area | region X1 shown in FIG. When the inclination angle of the swash plate 5 becomes maximum, as shown in FIG. 5, the partition body 13b is positioned on the front side of the first taper portion 135 in the first sliding region X1. In the second sliding region X2, the moving body 13a is located on the rear side.

  Thus, in this compressor, in changing the discharge capacity by changing the inclination angle of the swash plate 5, in the actuator 13, the moving body 13 a causes the second small diameter portion 30 b of the drive shaft body 30 to move in the direction of the drive axis O. To slide. As the moving body 13a moves in the direction of the drive axis O, the O-ring 51a slides while elastically deforming between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a, and O The ring 51b slides between the outer peripheral surface 134 of the partition 13a and the inner peripheral surface 131a of the peripheral wall 131 while being elastically deformed. For this reason, the O-ring 51a and the O-ring 51b generate a resistance force when the movable body 13a moves in the direction of the drive axis O. That is, when increasing the inclination angle of the swash plate 5 to increase the discharge capacity, the resistance force of the O-ring 51a and the O-ring 51b applied to the moving body 13a (hereinafter referred to as sliding resistance force R3; see FIGS. 8 and 9). It is necessary to increase the pressure P1 in the control pressure chamber 13c applied to the moving body 13a so that the moving body 13a can slide while overcoming the above. Here, in this compressor, as the pressure in the control pressure chamber 13 c decreases and the inclination angle of the swash plate 5 decreases, the actuator 13 is biased by the return spring 44 a via the swash plate 5. For this reason, the actuator 13 is biased in the direction of increasing the inclination angle of the swash plate 5. Thereby, in this compressor, the situation where the movable body 13a cannot overcome the sliding resistance R3 and cannot slide in the direction of increasing the inclination angle of the swash plate 5 does not occur.

  FIG. 7 shows a compressor of a comparative example. In the compressor of the comparative example, the first tapered portion 135 is not formed on the inner peripheral surface 131 a of the peripheral wall 131. For this reason, in the compressor of the comparative example, the moving body 13a remains unchanged at the first inner diameter L1. Similarly to the compressor of the first embodiment, in the compressor of the comparative example, even if the moving body 13a slides on the second sliding region X2, the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a The interval remains constant. Other configurations of the compressor of the comparative example are the same as those of the compressor of the first embodiment, and the same components are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the compressor of the comparative example configured as described above, when the pressure in the control pressure chamber 13c is low and the partition body 13b is located on the rear side of the first sliding region X1, or conversely, Even when the pressure is high and the partition 13b is located on the front side of the first sliding region X1, the first gap S1 is provided between the outer peripheral surface 134 of the partition 13b and the inner peripheral surface 131a of the peripheral wall 131. It becomes. That is, the first gap S1 is constant between the outer peripheral surface 134 and the inner peripheral surface 131a regardless of whether the inclination angle is minimum or maximum. Further, the interval between the second small diameter portion 30b and the moving body 13a is constant regardless of the change in the pressure in the control pressure chamber 13c, that is, the change in the inclination angle of the swash plate 5.

  As shown in the graphs of FIG. 8 and FIG. 9, the sliding resistance R3 is a resultant force of the resistance R1 due to tightening and the resistance R2 due to pressurization. The resistance R1 due to the tightening margin is the resistance generated by the elastic deformation of the O-ring 51a based on the size of the distance between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a, and the partition 13b. This is a resultant force of the resistance force generated by elastic deformation of the O-ring 51b based on the size of the interval between the outer peripheral surface 134 and the inner peripheral surface 131a of the peripheral wall 131. On the other hand, the resistance force R2 due to pressurization is caused by the resistance force generated by elastic deformation of the O-ring 51a due to the pressure in the control pressure chamber 13c and the O-ring 51b elastically deformed by the pressure in the control pressure chamber 13c. It is the resultant force with the resistance force to be generated. That is, as the pressure in the control pressure chamber 13c increases, the resistance force R2 due to pressurization increases. Further, in the drawing, in addition to the sliding resistance R3 and the like, the pressure P1 in the control pressure chamber 13c applied to the moving body 13a is illustrated.

  In the compressor of the comparative example, regardless of the change in the inclination angle of the swash plate 5, the distance between the outer peripheral surface 134 and the inner peripheral surface 131a is constant at the first interval S1, and the second small diameter portion 30b and the moving body 13a The interval is also constant. For this reason, as shown in the graph of FIG. 8, even when the pressure in the control pressure chamber 13c is low or the pressure in the control pressure chamber 13c is high, the resistance force R1 due to tightening is constant. Value. The resistance force R2 due to pressurization increases as the pressure in the control pressure chamber 13c increases. For these reasons, in the compressor of the comparative example, as the pressure in the control pressure chamber 13c increases, the sliding resistance R3 gradually increases with the value of the resistance R1 due to tightening as the lower limit. For this reason, when the pressure in the control pressure chamber 13c is low and the inclination angle is minimum, the pressure P1 in the control pressure chamber 13c applied to the moving body 13a is small, so the pressure in the control pressure chamber 13c applied to the moving body 13a. The sliding resistance R3 is relatively large with respect to P1. For this reason, in the compressor of the comparative example, when the pressure in the control pressure chamber 13c is low, it becomes difficult for the moving body 13a to slide in the direction of the drive axis O along the second small diameter portion 30b. As a result, in the compressor of the comparative example, since it is difficult to increase the inclination angle from the state where the inclination angle of the swash plate 5 is the minimum, the controllability is lowered.

  On the other hand, in the compressor according to the first embodiment, the first tapered portion 135 is formed on the inner peripheral surface 131a of the peripheral wall 131. Thereby, the moving body 13a has a first inner diameter L1 in front of the first taper portion 135, whereas it has a second inner diameter L2 in the rear of the first taper portion 135. For this reason, as shown in FIG. 5, when the pressure in the control pressure chamber 13c is high and the partition 13b is located in front of the first taper portion 135 in the first sliding region X1, the comparison is made. Similar to the compressor of the example, the first interval S1 is between the outer peripheral surface 134 and the inner peripheral surface 131a. On the other hand, when the pressure in the control pressure chamber 13c is low and the partition 13b is located behind the first taper portion 135 in the first sliding region X1, as shown in FIG. And the inner peripheral surface 131a is a second interval S2 wider than the first interval S1.

  Thereby, in the compressor of Example 1, when the inclination angle of the swash plate 5 is the maximum, the space between the outer peripheral surface 134 and the inner peripheral surface 131a is the first interval S1, whereas the swash plate 5 When the inclination angle is minimum, the second interval S2 is provided between the two. Note that, similarly to the compressor of the comparative example, in the compressor of Example 1, there is an interval between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a regardless of the change in the inclination angle of the swash plate 5. It becomes constant.

  Thus, in the compressor of Example 1, when the pressure of the control pressure chamber 13c is low because the space between the outer peripheral surface 134 and the inner peripheral surface 131a increases from the first interval S1 to the second interval S2. The amount of elastic deformation of the O-ring 51b is smaller than when the pressure in the control pressure chamber 13c is high. For this reason, as shown in the graph of FIG. 9, in the compressor of Example 1, when the pressure in the control pressure chamber 13c is low, the amount of elastic deformation of the O-ring 51b is reduced by the tightening allowance. The resistance force R1 is reduced. Thereby, also in the compressor of Example 1, the sliding resistance R3 increases as the pressure in the control pressure chamber 13c increases, but unlike the compressor of the comparative example, the pressure in the control pressure chamber 13c is low. In this case, since the resistance force R1 due to the tightening margin is reduced, the sliding resistance force R3 when the pressure in the control pressure chamber 13c is low can be reduced accordingly.

  Thereby, in the compressor of Example 1, when the inclination angle of the swash plate 5 is the minimum, that is, the pressure in the control pressure chamber 13c is low, and the pressure P1 in the control pressure chamber 13c applied to the moving body 13a is small. In this case, the sliding resistance force R3 can be made relatively smaller than the pressure P1 in the control pressure chamber 13c applied to the moving body 13a. For this reason, even when the pressure in the control pressure chamber 13c is low, the movable body 13a easily slides in the direction of the drive axis O along the second small diameter portion 30b. As a result, in the compressor of the first embodiment, it is easy to increase the inclination angle from the state where the inclination angle of the swash plate 5 is the minimum.

  Therefore, the compressor of Example 1 demonstrates high controllability.

  In particular, in this compressor, by forming the first taper portion 135 on the inner peripheral surface 131a of the peripheral wall 131, the inclination angle is increased only between the outer peripheral surface 134 of the partition 13b and the inner peripheral surface 131a of the peripheral wall 131. By changing from the maximum to the minimum, it is formed to increase from the first interval S1 to the second interval S2. As a result, the distance between the outer peripheral surface 134 and the inner peripheral surface 131a changes, and at the same time, the distance between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a is also changed. The compressor can be easily manufactured. Moreover, since the division body 13b is formed larger in diameter than the drive shaft main body 30 and is fixed to the second small diameter portion 30b, the O-ring 51b has a larger diameter than the O-ring 51a. Therefore, when only the elastic deformation amount of the O-ring 51a is reduced by reducing the elastic deformation amount of the O-ring 51b when the pressure in the control pressure chamber 13c is low and the inclination angle of the swash plate 5 is minimum. As compared with, the resistance force R1 due to the tightening allowance can be effectively reduced. Thereby, in this compressor, when the pressure P1 in the control pressure chamber 13c applied to the moving body 13a is small, the sliding resistance R3 can be suitably reduced.

(Example 2)
As shown in FIG. 10, in the compressor according to the second embodiment, a second tapered portion 136 is formed on the inner peripheral surface 131 a of the peripheral wall 131. Similar to the first tapered portion 135 described above, the second tapered portion 135 also extends linearly so as to increase in diameter from the front to the rear. Here, in this compressor, the entire first sliding region X1 is configured by the second tapered portion 136. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

(Example 3)
As shown in FIG. 11, in the compressor of the third embodiment, a third taper portion 137 is formed on the inner peripheral surface 131 a of the peripheral wall 131. Similar to the first tapered portion 135 described above, the third tapered portion 137 constitutes a part of the first sliding region X1. Here, unlike the first and second tapered portions 135 and 136, the third tapered portion 137 extends in a convex curved shape so as to increase in diameter from the front toward the rear. In addition, you may comprise all the 1st sliding area | regions X1 by the 3rd taper part 137. FIG. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

  The compressors of the second and third embodiments can achieve the same effects as the compressor of the first embodiment. In particular, in the compressor of the second embodiment, the entire first sliding region X1 is configured by the second tapered portion 136. For this reason, compared with the compressor of Example 1, between the outer peripheral surface 134 and the inner peripheral surface 131a can be changed more finely from 1st space | interval S1 to 2nd space | interval S2.

Example 4
As shown in FIG. 12, in the compressor of Example 4, the 4th taper part 301 is formed in the outer peripheral surface 300 of the 2nd small diameter part 30b. The 4th taper part 301 comprises a part of 2nd sliding area | region X2. The fourth taper portion 301 extends linearly so as to increase in diameter from the front toward the rear. Accordingly, the second small diameter portion 30b is formed at the first outer diameter L3 in front of the fourth taper portion 301, whereas the second small diameter portion 30b is behind the first outer diameter L3 behind the fourth taper portion 301. Is formed in a large second outer diameter L4.

  For this reason, as shown in FIG. 13, the moving body 13a slides on the second small diameter portion 30b in the direction of the drive axis O, and the moving body 13a is behind the fourth taper portion 301 in the second sliding region X2. Is located between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a, the third distance S3 is set. And as shown in FIG. 14, in the 2nd sliding area | region X2, as the moving body 13a moves the 4th taper part 301 toward the front side, the outer peripheral surface 300 of the 2nd small diameter part 30b, and the moving body 13a Gradually changes to a fourth interval S4 wider than the third interval S3. In FIGS. 13 and 14, the shapes of the third interval S3 and the fourth interval S4 are exaggerated for ease of explanation.

  Further, as shown in FIG. 12, in this compressor, unlike the compressor of the first embodiment, the first taper portion 135 is not formed on the inner peripheral surface 131 a of the peripheral wall 131. For this reason, the moving body 13a is formed in the 1st internal diameter L1. Thereby, the space between the outer peripheral surface 134 of the partition 13b and the inner peripheral surface 131a of the peripheral wall 131 remains unchanged at the first interval S1 shown in FIG. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

  In this compressor, when the pressure in the control pressure chamber 13c is increased, the moving body 13a is positioned rearward of the fourth tapered portion 301 in the second sliding region X2. For this reason, when the inclination angle of the swash plate 5 is maximum, the distance between the outer peripheral surface 300 of the second small diameter portion 30b and the moving body 13a is the third interval S3. On the other hand, when the pressure in the control pressure chamber 13c decreases, the moving body 13a moves to the front side of the fourth taper portion 301 in the second sliding region X2. For this reason, when the inclination angle of the swash plate 5 is the smallest, the distance between the outer peripheral surface 300 and the moving body 13a is the fourth interval S4.

  Thus, in this compressor, when the pressure of the control pressure chamber 13c is low, the space between the outer peripheral surface 300 and the moving body 13a is widened from the third interval S3 to the fourth interval S4. The amount of elastic deformation of the O-ring 51a is smaller than when the pressure at 13c is high. Thereby, like the compressor of Example 1, also in this compressor, when the inclination | tilt angle of the swash plate 5 is the minimum, it slides with respect to the pressure P1 in the control pressure chamber 13c added to the moving body 13a. The resistance force R3 can be relatively reduced. For this reason, also in this compressor, it becomes easy to increase a tilt angle from the state where the tilt angle of the swash plate 5 is the minimum. Other functions of this compressor are the same as those of the compressor of the first embodiment.

(Example 5)
As shown in FIG. 15, in the compressor of Example 5, the 5th taper part 302 is formed in the outer peripheral surface 300 of the 2nd small diameter part 30b. Similar to the fourth tapered portion 301 described above, the fifth tapered portion 302 also extends linearly so as to increase in diameter from the front toward the rear. Here, in this compressor, the second sliding region X2 is entirely constituted by the fifth tapered portion 302. Other configurations of this compressor are the same as those of the compressors of the first and fourth embodiments.

(Example 6)
As shown in FIG. 16, in the compressor of Example 6, the 6th taper part 303 is formed in the outer peripheral surface 300 of the 2nd small diameter part 30b. Similar to the fourth taper portion 301 described above, the sixth taper portion 303 constitutes a part of the second sliding region X2. Here, unlike the fourth and fifth taper portions 301 and 302, the sixth taper portion 303 extends in a convex curve shape so as to increase in diameter from the front to the rear. In addition, you may comprise all the 2nd sliding area | regions X2 by the 6th taper part 303. FIG. Other configurations of this compressor are the same as those of the compressors of the first and fourth embodiments.

  The compressors of the fifth and sixth embodiments can achieve the same effects as the compressors of the first and fourth embodiments. In particular, in the compressor of the fifth embodiment, since the entire second sliding region X2 is constituted by the fifth tapered portion 302, the outer peripheral surface of the second small diameter portion 30b is compared with the compressor of the fourth embodiment. 300 and the moving body 13a can be changed more finely from the third interval S3 to the fourth interval S4.

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

  For example, you may comprise a compressor by combining one of the compressors of Examples 1-3 with one of the compressors of Examples 4-6. In this case, when the pressure in the control pressure chamber 13c is low, the amount of elastic deformation of both the O-ring 51a and the O-ring 51b can be reduced. For this reason, when the pressure in the control pressure chamber 13c is low and the inclination angle of the swash plate 5 is minimum, the sliding resistance R3 is made smaller than the pressure P1 in the control pressure chamber 13c applied to the moving body 13a. can do.

  Further, by providing the first cylinder bore 21 a only in the first cylinder block 21 and providing only the first head 9 a in the piston 9, a one-head piston type variable displacement swash plate compressor may be configured.

  Further, in the swash plate chamber 33, the actuator 13 may be disposed in front of the swash plate 5, and the link mechanism 7 may be disposed behind the swash plate 5.

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

  Moreover, it is good also as a structure which adjusts the opening degree of the extraction passage 15a or the supply passage 15b with a flow control valve instead of the control valve 15c. In this case, a first pressure monitoring point is set in the discharge region of the refrigeration circuit, and the first pressure is further downstream in the flow direction of the refrigerant gas than the first pressure monitoring point in the discharge region of the refrigeration circuit. A second pressure monitoring point is set at a location where the pressure is lower than the monitoring point. Thereby, the flow control valve can adjust the opening degree of the extraction passage 15a or the supply passage 15b based on the differential pressure between the first pressure monitoring point and the second pressure monitoring point.

  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 13a ... Moving body 13b ... Partition body 13c ... Control pressure chamber 15 ... Control mechanism 51a ... O-ring (2nd sealing member)
51b ... O-ring (first sealing member)
S1 to S4: 1st to 4th intervals

Claims (2)

A housing in which a swash plate chamber and a plurality of cylinder bores are formed;
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the drive axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided on the drive shaft and rotatable integrally with the drive shaft in the swash plate chamber;
A movement that is provided on the drive shaft, can rotate integrally with the drive shaft in the swash plate chamber, and slides in the drive shaft center direction with respect to the drive shaft and the partition body to change the inclination angle. Body,
A control pressure chamber that is partitioned by the partition body and the moving body, and the internal pressure is increased to move the moving body to increase the tilt angle;
A control mechanism for controlling the pressure in the control pressure chamber,
The partition has a first sealing member that is located between the partition and the movable body and seals between the control pressure chamber and the swash plate chamber while being elastically deformed.
The movable body has a second sealing member that is located between the drive shaft and the movable body and seals between the control pressure chamber and the swash plate chamber while being elastically deformed.
At least one of the partition body and the movable body and between the drive shaft and the movable body has a larger interval when the inclination angle is minimum than the interval when the inclination angle is maximum. A variable capacity swash plate compressor characterized by being formed.   2. The variable capacity swash plate type according to claim 1, wherein an interval when the inclination angle is minimum is formed larger than the interval when the inclination angle is maximum only between the partition body and the moving body. Compressor.

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