JP6037027B2 - 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). The compressor includes a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a conversion mechanism, and a capacity control mechanism.

  A suction chamber, a discharge chamber, a swash plate chamber, and a plurality of cylinder bores are formed in the housing. The drive shaft is rotatably supported by the housing. The swash plate can be rotated in the swash plate chamber by the 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 with respect to the direction orthogonal to the drive axis of the drive shaft. This link mechanism has a lug member and a transmission member. The lug member is fixed to the drive shaft in the swash plate chamber. The transmission member is provided integrally with the swash plate in the swash plate chamber, and transmits the rotation of the lug member to the swash plate. Each piston is accommodated in each cylinder bore so as to be able to reciprocate. The conversion mechanism reciprocates each piston in each cylinder bore with a stroke corresponding to the inclination angle by the rotation of the swash plate. The capacity control mechanism has an air supply passage, an extraction passage, and a control valve. The air supply passage communicates the discharge chamber and the swash plate chamber. The extraction passage communicates the swash plate chamber and the suction chamber. The control valve can change the pressure in the swash plate chamber by adjusting the opening of the air supply passage.

  In this compressor, if the pressure in the swash plate chamber is increased by the control valve, the inclination angle is reduced and the stroke of the piston is reduced. For this reason, the compression capacity per rotation of the drive shaft is reduced. On the other hand, if the pressure in the swash plate chamber is lowered by the control valve, the inclination angle of the swash plate increases and the stroke of the piston increases. For this reason, the compression capacity per rotation of the drive shaft increases. Thus, in this compressor, it is possible to change the refrigerant discharge capacity in accordance with the operating conditions of the vehicle or the like to be mounted.

  However, when the tilt angle is changed by a pressure change in the swash plate chamber as in this compressor, it is necessary to secure an amount of refrigerant in the swash plate chamber sufficient to change the tilt angle. For this reason, the compressor is easily increased in size by a large swash plate chamber.

  In this compressor, inflow of high-pressure blow-by gas into the swash plate chamber is unavoidable. Further, in this compressor, the refrigerant in the swash plate chamber is condensed due to a decrease in the outside air temperature, and a liquid pool is likely to be generated in the swash plate chamber. For these reasons, it is difficult for this compressor to suitably change the inclination angle.

  For this reason, a compressor as disclosed in Patent Document 2 has also been proposed. This compressor includes an actuator capable of changing an inclination angle and a control mechanism for controlling the actuator.

  Specifically, the actuator is partitioned by a lug member, a movable body that engages with the swash plate so as to be integrally rotatable, can move in the direction of the drive axis, and can change an inclination angle, and the lug member and the movable body. And a control pressure chamber for moving the movable body by the internal pressure. The control mechanism has a control passage and a control valve. The control passage has a variable pressure passage communicating with the control pressure chamber, a low pressure passage communicating with the suction chamber and the swash plate chamber, and a high pressure passage communicating with the discharge chamber. A part of the transformation passage is formed in the drive shaft. The control valve adjusts the opening degree of the variable pressure passage, the low pressure passage, and the high pressure passage. That is, the control valve communicates the variable pressure passage with the low pressure passage or the high pressure passage.

  In this compressor, when the control valve communicates the variable pressure passage with the high pressure passage, the control pressure chamber has a higher pressure than the swash plate chamber. Thereby, the movable body of the actuator moves away from the lug member, and the inclination angle decreases. For this reason, the stroke of the piston is reduced and the discharge capacity is reduced. On the other hand, if the control valve connects the variable pressure passage to the low pressure passage, the control pressure chamber is at a low pressure as much as the swash plate chamber. As a result, the movable body of the actuator approaches the lug member, and the inclination angle increases. For this reason, the stroke of the piston increases and the discharge capacity increases.

  Since this compressor changes the pressure in the control pressure chamber having a smaller volume than the swash plate chamber, the amount of refrigerant required for changing the tilt angle may be less than that of the compressor that changes the pressure in the swash plate chamber. It is possible to achieve downsizing.

  Further, in this compressor, since the tilt angle is changed by the pressure change in the control pressure chamber, the flow of blow-by gas into the swash plate chamber and the liquid pool in the swash plate chamber are unlikely to adversely affect the change in the tilt angle.

JP 2002-213350 A JP-A-52-131204

  However, in the compressor described in Patent Document 2, a spherical hinge sphere having a center on the drive shaft center is provided in the insertion hole of the swash plate, and the outer peripheral surface of the hinge sphere is slidable with the swash plate. It has become. The movable body of the actuator and the swash plate are engaged via this hinge sphere. For this reason, in this compressor, unless the whole size is increased, it is difficult to increase the diameter of the movable body, and it is difficult to move the movable body with a larger thrust.

  Moreover, in this compressor, in reducing the inclination angle of the swash plate, the movable body presses the swash plate via the hinge sphere. Here, in this compressor, the contact position between the outer peripheral surface of the hinge sphere and the swash plate is likely to vary due to manufacturing tolerances and the like, and this acts on the swash plate when the movable body presses the hinge sphere. The direction of the load is easy to change. For this reason, in this compressor, it is difficult for the movable body to press the hinge sphere in the direction of the drive axis, and the movable body is stable and it is difficult to reduce the inclination angle of the swash plate. Moreover, in this compressor, since the attitude | position of a movable body is unstable, there exists a possibility of producing a leak in the pressure in a control pressure chamber. For these reasons, in this compressor, it is difficult to quickly change the discharge capacity in accordance with the driving condition of the vehicle or the like, and thus it is difficult to exhibit sufficient controllability.

  The present invention has been made in view of the above-described conventional situation, and solves the problem of providing a variable capacity swash plate compressor capable of exhibiting sufficient controllability while realizing as small a size as possible. It is an issue that should be done.

A variable capacity swash plate compressor according to the present invention includes a housing in which a swash plate chamber and a cylinder bore are formed, a drive shaft rotatably supported by the housing, and rotation in the swash plate chamber by rotation of the drive shaft. A swash plate, 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 orthogonal to the drive shaft center of the drive shaft; and reciprocating motion to the cylinder bore A piston housed in a possible manner, a conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the tilt angle by rotation of the swash plate, an actuator capable of changing the tilt angle, and the actuator A control mechanism for controlling,
The link mechanism includes a lug member fixed to the drive shaft in the swash plate chamber, and a transmission member that transmits the rotation of the lug member to the swash plate.
The swash plate is formed with an insertion hole that slides on the outer periphery of the drive shaft in accordance with the change in the inclination angle.
The swash plate is guided in the drive axis direction and the tilt angle direction by the link mechanism and the insertion hole to change the tilt angle,
The actuator can be rotated integrally with the lug member and the swash plate, and is partitioned by a movable body that can move in the drive axis direction and change the tilt angle, and the lug member and the movable body. A control pressure chamber that moves the movable body by changing an internal pressure by the control mechanism,
The movable body is formed with an action portion capable of pressing the swash plate by the pressure in the control pressure chamber,
The swash plate is formed with an actuated portion that is pressed against the acting portion.

  In the compressor of the present invention, the transmission member of the link mechanism transmits the rotation of the lug member to the swash plate. Then, the tilted angle is changed by pressing the acted portion formed on the swash plate in contact with the acted portion formed on the movable body. That is, in this compressor, when changing the inclination angle, the movable body presses while directly contacting the swash plate. For this reason, in this compressor, since the sleeve like the conventional hinge sphere is not provided between the movable body and the swash plate, the size can be reduced by the amount of such a sleeve. In other words, even if the whole is not enlarged, the diameter of the movable body can be increased and the movable body can be moved by a larger thrust.

  In this compressor, since the movable body presses while directly contacting the swash plate, the direction of the load acting on the swash plate is difficult to change. For this reason, in this compressor, the movable body can easily press the swash plate in the drive axis direction, and the movable body can stably change the inclination angle of the swash plate. Moreover, in this compressor, since the attitude | position of a movable body is stabilized, it is hard to produce a leak in the pressure in a control pressure chamber. For these reasons, in this compressor, the discharge capacity can be quickly changed in accordance with the driving situation of the vehicle or the like.

  Therefore, the compressor of the present invention can exhibit sufficient controllability while realizing miniaturization as much as possible.

  By the way, in such a swash plate type compressor, a moment to rotate in a direction perpendicular to the drive axis acts on the swash plate due to a compression reaction force during operation. In this respect, in this compressor, the insertion hole formed in the swash plate slides on the outer periphery of the drive shaft in accordance with the change of the inclination angle. The swash plate is guided in the drive axis direction and the tilt angle direction by the link mechanism and the insertion hole to change the tilt angle. For this reason, in this compressor, even when the swash plate is not tilted in the direction perpendicular to the drive axis during operation, such a tilt can be suitably prevented without being prevented by the sleeve. By omitting the sleeve, it is possible to reduce the manufacturing cost by reducing the number of parts.

  In addition, for example, it is not impossible to employ a configuration in which the operating portion and the operated portion are connected by a connecting pin or the like. However, in this case, the posture of the movable body may change depending on the configuration of the connecting portion. Further, the increase in the number of parts complicates the configuration of the compressor and increases the manufacturing cost. On the other hand, in the compressor of the present invention, when the inclination angle of the swash plate is changed, the movable body only presses while directly contacting the swash plate, and the posture of the movable body is difficult to change. In addition, in this compressor, it is possible to suppress the complexity of the configuration and to realize a reduction in manufacturing cost.

  The control mechanism may have a control passage and a control valve. The control passage may include a variable pressure passage communicating with the control pressure chamber, a low pressure passage communicating with the suction chamber or the swash plate chamber, and a high pressure passage communicating with the discharge chamber.

  It is preferable that the movable body is inserted through the drive shaft and can be fitted to the lug member. In this case, it is possible to suitably secure a space for the movable body to move in the drive axis direction between the lug member and the swash plate.

  Further, the movable body may have a movable cylindrical portion having a cylindrical shape coaxial with the drive shaft. The lug member preferably has a cylindrical shape coaxial with the drive shaft on the outer peripheral side of the movable cylindrical portion, and has a cylindrical fixed cylindrical portion that secures a control pressure chamber in the movable cylindrical portion. In this case, the movable body can be fitted to the lug member by fitting the movable cylindrical portion to the fixed cylindrical portion. Further, since the control pressure chamber is secured in the movable cylinder portion by the fixed cylinder portion, the control pressure chamber can be suitably formed between the lug member and the movable body.

  In this case, a first sealing means for sealing the control pressure chamber may be provided between the movable cylindrical portion and the drive shaft. And it is preferable that the 2nd sealing means which seals a control pressure chamber is provided between the movable cylinder part and the fixed cylinder part. As a result, it is possible to suitably ensure the airtightness of the control pressure chamber. In addition, as the first sealing means and the second sealing means, it is possible to employ various sealing materials in addition to an O-ring or the like. Further, the first sealing means and the second sealing means may be the same type or different.

  A thrust bearing that receives a thrust force acting on the piston may be provided between the housing and the lug member. The movable cylindrical portion preferably has a smaller diameter than the thrust bearing and can be fitted into the thrust bearing.

  In this case, the thrust bearing can favorably support the suction reaction force acting on the piston during the suction stroke and the compression reaction force acting on the piston during the compression stroke. In addition, since the movable cylindrical portion can be fitted into the thrust bearing, it is possible to secure a sufficient space for the movable body to move in the direction of the drive shaft even if the axial length of the compressor is short. Become.

  In the compressor of the present invention, the position where the action part is formed on the movable body and the position where the action part is formed on the swash plate can be appropriately designed. In particular, the swash plate may be defined with a top dead center corresponding portion that positions the piston at the top dead center. And it is preferable that the action part and the to-be-acted part are eccentric from the drive shaft center to the top dead center corresponding part side. In this case, for example, when the operating portion and the operated portion are in contact with each other on the drive axis and the operated portion is pressed against the operating portion, the drive axis of the movable body is the same when the inclination angle range is the same. The direction stroke can be reduced. Thereby, in this compressor, the enlargement of an axial length can be suppressed and the mounting property to a vehicle etc. can be improved.

  In the compressor of the present invention, the action part and the action part can be in point contact or line contact with each other at the action position. And it is preferable that the action position moves toward the drive shaft center side when the inclination angle becomes smaller. In this case, it is possible to reduce the load on the movable body when the inclination angle is reduced. For this reason, in this compressor, it becomes possible to make controllability higher. The straight line that makes line contact is orthogonal to the first virtual plane determined by the top dead center corresponding portion of the swash plate and the drive axis. Further, when the action part and the action part are brought into point contact or line contact at the action position, either the contact part of the action part with the action part or the contact part of the action part with the action part is a curved surface. It is preferable to be formed.

  The action part may have an action surface extending in a direction orthogonal to the drive axis. And it is preferable that the to-be-acted part has the convex part which protrudes from a swash plate and contact | abuts an action surface. In this case, it is possible to suitably bring the contact portion and the contact portion into point contact or line contact.

  It is preferable that the action part protrudes on the top dead center corresponding part side in the movable cylindrical part. In this case, the action part and the acted part can be easily brought into contact with each other.

  The swash plate preferably has a swash plate main body in which an insertion hole is formed, and an actuated portion formed integrally with the swash plate main body. In this case, it is possible to reduce the number of parts in the compressor, which facilitates manufacture and reduces manufacturing costs.

  Moreover, it is also preferable that the swash plate has a swash plate main body in which an insertion hole is formed and an actuated portion fixed to the swash plate main body. In this case, it is possible to increase the degree of design freedom in the swash plate body and the acted part.

  In the compressor of the present invention, a suction chamber and a discharge chamber can be formed in the housing. The suction chamber and the swash plate chamber are preferably in communication. In this case, the swash plate chamber can be set to a low pressure similarly to the suction chamber.

  The control mechanism may include a control passage that communicates the control pressure chamber with the suction chamber and / or the discharge chamber, and a control valve that can adjust the opening of the control passage. And it is preferable that at least a part of the control passage is formed in the drive shaft. In this case, it is possible to suitably change the pressure in the control pressure chamber while reducing the size of the control mechanism, and it is possible to suitably move the movable body.

  Between the housing and one end of the drive shaft, a pressure adjusting chamber that communicates with the control pressure chamber via the control passage and whose pressure is changed by the control valve can be formed. And it is preferable that the 3rd sealing means which seals a pressure regulation chamber is provided between the housing and the drive shaft.

  In this case, the control pressure chamber moves the movable body by changing the pressure of the pressure adjustment chamber by the control valve. And it becomes possible to ensure the airtightness of a pressure regulation chamber suitably by a 3rd sealing means. The third sealing means can employ various sealing materials in addition to the O-ring and the like, similar to the first and second sealing means. Further, the third sealing means may be the same type as or different from the first and second sealing means.

  The compressor of the present invention can exhibit sufficient controllability while realizing as small a size as possible.

FIG. 1 is a cross-sectional view of the compressor of the first embodiment at the maximum capacity. FIG. 2 is a schematic diagram illustrating a control mechanism according to the compressor of the first embodiment. FIG. 3 is an essential part enlarged cross-sectional view illustrating a rear end portion of a drive shaft according to the compressor of the first embodiment. FIG. 4 is an essential part enlarged cross-sectional view illustrating the actuator in the compressor according to the first embodiment. FIG. 5 is a front perspective view illustrating the swash plate according to the compressor of the first embodiment. FIG. 6 is a schematic front view illustrating a swash plate according to the compressor of the first embodiment. FIG. 7 is a cross-sectional view of the compressor according to the first embodiment when the capacity is minimum. FIG. 8 is an essential part enlarged cross-sectional view showing an action part and an action part in the compressor of the first embodiment. The figure (A) has shown the action position in case a tilt angle is the maximum. FIG. 5B shows the operation position when the tilt angle is the minimum. FIG. 9 is a schematic diagram illustrating the difference in the stroke of the movable body between the compressor of the first embodiment and the compressor of the comparative example. FIG. 10 is a graph showing the relationship between the tilt angle and the variable differential pressure. FIG. 11 is a cross-sectional view of the compressor of the second embodiment at the maximum capacity.

  Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings. The compressors of Examples 1 and 2 are variable capacity single-head swash plate compressors. All of these compressors are mounted on a vehicle, and constitute a refrigeration circuit of a vehicle air conditioner.

Example 1
As shown in FIG. 1, the compressor according to the first embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, a plurality of pairs of shoes 11a and 11b, and an actuator. 13 and a control mechanism 15 shown in FIG. In FIG. 1, the shape of the swash plate 5 is partially simplified for easy explanation. The same applies to FIGS. 7 and 10 described later.

  As shown in FIG. 1, the housing 1 includes a front housing 17 located in front of the compressor, a rear housing 19 located behind the compressor, and a cylinder block located between the front housing 17 and the rear housing 19. 21 and a valve unit 23.

  The front housing 17 includes a front wall 17a that extends in the vertical direction of the compressor in front and a peripheral wall 17b that is integrated with the front wall 17a and extends rearward from the front of the compressor. The front housing 17 has a substantially cylindrical shape with a bottom by the front wall 17a and the peripheral wall 17b. A swash plate chamber 25 is formed in the front housing 17 by the front wall 17a and the peripheral wall 17b.

  A boss 17c that protrudes forward is formed on the front wall 17a. A shaft seal device 27 is provided in the boss 17c. Further, a first shaft hole 17d extending in the front-rear direction of the compressor is formed in the boss 17c. A first sliding bearing 29a is provided in the first shaft hole 17d.

  A suction port 250 communicating with the swash plate chamber 25 is formed in the peripheral wall 17b. Through the suction port 250, the swash plate chamber 25 is connected to an evaporator (not shown).

  A part of the control mechanism 15 is provided in the rear housing 19. The rear housing 19 is formed with a first pressure adjustment chamber 31a, a suction chamber 33, and a discharge chamber 35. The first pressure adjustment chamber 31 a is located at the center portion of the rear housing 19. The discharge chamber 35 is annularly positioned on the outer peripheral side of the rear housing 19. The suction chamber 33 is formed in an annular shape between the first pressure adjustment chamber 31 a and the discharge chamber 35 in the rear housing 19. The discharge chamber 35 is connected to a discharge port (not shown).

  In the cylinder block 21, the same number of cylinder bores 21a as the pistons 9 are formed at equal angular intervals in the circumferential direction. The front end side of each cylinder bore 21 a communicates with the swash plate chamber 25. The cylinder block 21 is formed with a retainer groove 21b that regulates the lift amount of a suction reed valve 41a, which will be described later.

  Further, the cylinder block 21 is provided with a second shaft hole 21c that communicates with the swash plate chamber 25 and extends in the front-rear direction of the compressor. A second sliding bearing 29b is provided in the second shaft hole 21c. The cylinder block 21 has a spring chamber 21d. The spring chamber 21d is located between the swash plate chamber 25 and the second shaft hole 21c. A return spring 37 is disposed in the spring chamber 21d. The return spring 37 urges the swash plate 5 having the smallest inclination angle toward the front of the swash plate chamber 25. Further, a suction passage 39 communicating with the swash plate chamber 25 is formed in the cylinder block 21.

  The valve unit 23 is provided between the rear housing 19 and the cylinder block 21. The valve unit 23 includes a valve plate 40, a suction valve plate 41, a discharge valve plate 43, and a retainer plate 45.

  The valve plate 40, the discharge valve plate 43, and the retainer plate 45 are formed with the same number of intake ports 40a as the cylinder bores 21a. The valve plate 40 and the intake valve plate 41 are formed with the same number of discharge ports 40b as the cylinder bores 21a. Each cylinder bore 21a communicates with the suction chamber 33 through each suction port 40a and also communicates with the discharge chamber 35 through each discharge port 40b. Further, the valve plate 40, the suction valve plate 41, the discharge valve plate 43, and the retainer plate 45 are formed with a first communication hole 40c and a second communication hole 40d. The suction chamber 33 and the suction passage 39 communicate with each other through the first communication hole 40c.

  The intake valve plate 41 is provided on the front surface of the valve plate 40. The suction valve plate 41 is formed with a plurality of suction reed valves 41a capable of opening and closing each suction port 40a by elastic deformation. The discharge valve plate 43 is provided on the rear surface of the valve plate 40. The discharge valve plate 43 is formed with a plurality of discharge reed valves 43a capable of opening and closing each discharge port 40b by elastic deformation. The retainer plate 45 is provided on the rear surface of the discharge valve plate 43. The retainer plate 45 regulates the lift amount of the discharge reed valve 43a.

  The drive shaft 3 has a cylindrical outer peripheral surface 30. The drive shaft 3 is inserted from the boss 17 c side toward the rear side of the housing 1. The front end side of the drive shaft 3 is supported by the shaft seal device 27 in the boss 17c, and is supported by the first sliding bearing 29a in the first shaft hole 17d. The rear end side of the drive shaft 3 is pivotally supported by the second sliding bearing 29b in the second shaft hole 21c. Thus, the drive shaft 3 is supported so as to be rotatable around the drive axis O with respect to the housing 1. A second pressure adjusting chamber 31b is defined between the rear end of the drive shaft 3 in the second shaft hole 21c. The second pressure regulation chamber 31b communicates with the first pressure regulation chamber 31a through the second communication hole 40d. These first and second pressure adjusting chambers 31a and 31b form a pressure adjusting chamber 31.

  As shown in FIG. 3, ring grooves 3 c and 3 d are formed at the rear end of the drive shaft 3. O-rings 49a and 49b are provided in the ring grooves 3c and 3d, respectively. The pressure adjustment chamber 31 is sealed by the O-rings 49a and 49b, and the swash plate chamber 25 and the pressure adjustment chamber 31 are not in communication. Each of these O-rings 49a and 49b corresponds to the third sealing means in the present invention.

  As shown in FIG. 1, a link mechanism 7, a swash plate 5, and an actuator 13 are attached to the drive shaft 3. The link mechanism 7 includes a lug plate 51, a pair of lug arms 53 formed on the lug plate 51, and a pair of swash plate arms 5e and 5f. The lug plate 51 corresponds to the lug member in the present invention. The swash plate arms 5e and 5f correspond to the transmission member in the present invention.

  The lug plate 51 is formed in a substantially annular shape. The lug plate 51 is press-fitted into the drive shaft 3 and can rotate integrally with the drive shaft 3. The lug plate 51 is located on the front end side in the swash plate chamber 25 and is disposed in front of the swash plate 5. A thrust bearing 55 is provided between the lug plate 51 and the front wall 17a.

  As shown in FIG. 4, the lug plate 51 is provided with a cylindrical fixed cylindrical portion 51 a extending in the front-rear direction of the lug plate 51. As shown in FIG. 1, the fixed cylindrical portion 51 a extends from the rear end surface of the lug plate 51 to a location inside the thrust bearing 55 in the lug plate 51.

  Each lug arm 53 extends rearward from the lug plate 51. The lug plate 51 is formed with a cam surface 51 b at a position between the lug arms 53. In FIG. 1 and the like, only one side of the lug arm 53 is shown for ease of explanation.

  As shown in FIG. 5, the swash plate 5 includes a swash plate main body 50, swash plate arms 5e and 5f, and a convex portion 5g. This convex part 5g is equivalent to the to-be-acted part in this invention.

  The swash plate main body 50 has an annular flat plate shape and includes a front surface 5a and a rear surface 5b, and also defines a top dead center corresponding portion T for positioning each piston 9 at the top dead center. The front surface 5 a is formed with a restricting portion 5 c that protrudes toward the front of the swash plate 5. As shown in FIG. 1, the restricting portion 5 c comes into contact with the lug plate 51 when the inclination angle of the swash plate 5 becomes maximum. The swash plate body 50 is formed with an insertion hole 5d. The drive shaft 3 is inserted through the insertion hole 5d.

  As shown in FIG. 6, a pair of planar guide surfaces 52a and 52b are formed in the insertion hole 5d. These guide surfaces 52a and 52b come into contact with the outer peripheral surface 30 of the drive shaft 3 when the drive shaft 3 is inserted into the insertion hole 5d. In FIG. 6, for ease of explanation, the shapes of the swash plate arms 5e, 5f, the convex portions 5g, etc. are shown in a simplified manner.

  As shown in FIG. 5, each swash plate arm 5 e, 5 f is formed on the front surface 5 a of the swash plate body 50 at a position eccentric from the drive axis O toward the top dead center corresponding portion T side of the swash plate 5. Yes. Each swash plate arm 5e, 5f extends forward from the front surface 5a.

  The convex portion 5g protrudes forward from the front surface 5a and is integrated with the swash plate body 50. The convex portion 5g is formed in a substantially hemispherical shape, and is eccentric to the top dead center corresponding portion T side of the swash plate 5 with respect to the drive axis O, and is located between the swash plate arm 5e and the swash plate arm 5f. ing.

  As shown in FIG. 1, the swash plate arms 5 e and 5 f are inserted between the lug arms 53, thereby connecting the lug plate 51 and the swash plate 5. As a result, the swash plate 5 can rotate in the swash plate chamber 25 together with the lug plate 51. Each swash plate arm 5e, 5f is in contact with the cam surface 51b at each tip side.

  Further, by connecting the lug plate 51 and the swash plate 5, the swash plate arms 5 e, 5 f and the convex portion 5 g are offset from the drive axis O toward the top dead center corresponding portion T side of the swash plate 5. doing. When the swash plate arms 5e and 5f slide on the cam surface 51b, the swash plate 5 substantially maintains the position of the top dead center corresponding portion T with respect to its own inclination angle with respect to the direction orthogonal to the drive axis O. However, the maximum inclination angle shown in the figure can be changed to the minimum inclination angle shown in FIG. At this time, the guide surfaces 52 a and 52 b shown in FIG. 6 slide on the outer peripheral surface 30 of the drive shaft 3 in accordance with the change in the inclination angle of the swash plate 5. Thus, the swash plate 5 changes the tilt angle as described above while being guided by the link mechanism 7 and the drive shaft 3 in the drive axis O direction and the tilt angle direction.

  As shown in FIG. 4, the actuator 13 includes a lug plate 51, a movable body 13a, and a control pressure chamber 13b.

  The movable body 13a is inserted through the drive shaft 3, and is movable in the direction of the drive axis O while being in sliding contact with the drive shaft 3. The movable body 13a has a cylindrical shape coaxial with the drive shaft 3, and is formed with a smaller diameter than the thrust bearing 55 shown in FIG. As shown in FIG. 4, the movable body 13 a includes a first movable cylindrical portion 131, a second movable cylindrical portion 132, and a third movable cylindrical portion 133. The first movable cylindrical portion 131 is located on the rear end side of the movable body 13a and is formed to have the smallest diameter in the movable body 13a. The second movable cylindrical portion 132 is continuous with the front end of the first movable cylindrical portion 131, and is formed so that the diameter gradually increases toward the front of the movable body 13a. The third movable cylindrical portion 133 is continuous with the front end of the second movable cylindrical portion 132 and extends toward the front of the movable body 13a. The third movable cylindrical portion 133 is formed with the largest diameter in the movable body 13a.

  In addition, an action part 134 is integrally formed at the rear end of the first movable cylindrical part 131. As shown in FIG. 1, the action part 134 extends vertically from the drive axis O side toward the top dead center corresponding part T side of the swash plate 5, and the top dead center of the swash plate 5 from the drive axis O. It is eccentric to the corresponding part T side. This action part 134 has the action surface 134a formed in the plane. As shown in FIG. 8, the action surface 134 a makes point contact with the convex portion 5 g at the action position F. Thereby, the movable body 13a can rotate integrally with the lug plate 51 and the swash plate 5. Here, since the convex part 5g and the action part 134 are eccentric to the top dead center corresponding part T side of the swash plate 5 with respect to the drive axis O, as shown in FIG. It is eccentric from O to the top dead center corresponding part T side of the swash plate 5.

  The movable body 13a can be fitted into the lug plate 51 by causing the second movable cylindrical portion 132 and the third movable cylindrical portion 133 shown in FIG. 4 to enter the fixed cylindrical portion 51a (FIG. 1). In a state where the second movable cylindrical portion 132 and the third movable cylindrical portion 133 are most advanced into the fixed cylindrical portion 51a, the third movable cylindrical portion 133 is located inside the thrust bearing 55 within the fixed cylindrical portion 51a. Will come.

  As shown in FIG. 4, the control pressure chamber 13 b is formed between the second movable cylindrical portion 132, the third movable cylindrical portion 133, the fixed cylindrical portion 51 a, and the drive shaft 3. A ring groove 131a is formed on the inner peripheral surface of the first movable cylindrical portion 131, and a ring groove 133a is formed on the outer peripheral surface of the third movable cylindrical portion 133. O-rings 49c and 49d are provided in the ring grooves 131a and 133a, respectively. The O-ring 49c corresponds to the first sealing means in the present invention, and the O-ring 49d corresponds to the second sealing means in the present invention. The control pressure chamber 13b is sealed by these O-rings 49c and 49d, and the airtightness in the control pressure chamber 13b is secured.

  As shown in FIG. 1, in the drive shaft 3, an axial path 3a extending in the direction of the drive axis O from the rear end to the front end of the drive shaft 3, and a drive shaft extending in the radial direction from the front end of the axial path 3a. 3 is formed on the outer peripheral surface 30 of the main body 3. 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 13b. The pressure adjusting chamber 31 and the control pressure chamber 13b communicate with each other by the axial path 3a and the radial path 3b.

  The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) by a screw portion 3e formed at the tip.

  Each piston 9 is housed in each cylinder bore 21a, and can reciprocate in each cylinder bore 21a. Each piston 9 and valve unit 23 define a compression chamber 57 in each cylinder bore 21a.

  Further, each piston 9 is provided with an engaging portion 9a. In the engaging portion 9a, hemispherical shoes 11a and 11b are respectively provided. Each shoe 11 a, 11 b converts the rotation of the swash plate 5 into the reciprocating motion of each piston 9. Each of these shoes 11a and 11b corresponds to a conversion mechanism in the present invention. Thus, each piston 9 can reciprocate within the cylinder bore 21a with a stroke corresponding to the inclination angle of the swash plate 5. In addition to the shoes 11a and 11b, a wobble type conversion mechanism that supports the swing plate on the rear surface 5b side of the swash plate main body 50 via a thrust bearing and connects the swing plate and each piston 9 by connecting rods. Can also be adopted.

  As shown in FIG. 2, the control mechanism 15 includes a low pressure passage 15a, a high pressure passage 15b, a control valve 15c, an orifice 15d, an axial path 3a, and a radial path 3b. The low pressure passage 15a, the high pressure passage 15b, the axial passage 3a, and the radial passage 3b form a control passage in the present invention. Moreover, the axial path 3a and the path 3b function as a transformation path.

  The low pressure passage 15 a is connected to the pressure adjustment chamber 31 and the suction chamber 33. Thus, the control pressure chamber 13b, the pressure adjusting chamber 31, and the suction chamber 33 are in communication with each other by the low pressure passage 15a, the axial passage 3a, and the radial passage 3b. The high-pressure passage 15 b is connected to the pressure adjustment chamber 31 and the discharge chamber 35. The control pressure chamber 13b, the pressure adjustment chamber 31, and the discharge chamber 35 are communicated with each other by the high pressure passage 15b, the axial path 3a, and the radial path 3b. The high pressure passage 15b is provided with an orifice 15d, and the flow rate of the refrigerant flowing through the high pressure passage 15b is reduced.

  The control valve 15c is provided in the low pressure passage 15a. The control valve 15c can adjust the flow rate of the refrigerant flowing through the low pressure passage 15a based on the pressure in the suction chamber 33.

  In this compressor, a pipe connected to the evaporator is connected to the suction port 250 shown in FIG. 1, 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, when the drive shaft 3 rotates, the swash plate 5 rotates and each piston 9 reciprocates in each cylinder bore 21a. For this reason, the compression chamber 57 changes the volume according to the piston stroke. Therefore, the refrigerant sucked into the swash plate chamber 25 from the evaporator through the suction port 250 is compressed in the compression chamber 57 from the suction passage 39 through the suction chamber 33. The refrigerant compressed in the compression chamber 57 is discharged into the discharge chamber 35 and discharged from the discharge port to the condenser.

  During this time, in this compressor, a piston compression force that reduces the inclination angle of the swash plate 5 acts on the swash plate 5, the lug plate 51, and the like. In this compressor, the capacity control can be performed by changing the inclination angle of the swash plate 5 to increase or decrease the stroke of the piston 9.

  Specifically, in the control mechanism 15, if the control valve 15c shown in FIG. 2 increases the flow rate of the refrigerant flowing through the low-pressure passage 15a, the refrigerant in the discharge chamber 35 is adjusted in pressure through the high-pressure passage 15b and the orifice 15d. It becomes difficult to be stored in the chamber 31. For this reason, the pressure in the control pressure chamber 13 b is substantially equal to that of the suction chamber 33. For this reason, as shown in FIG. 1, the actuator 13 reduces the volume of the control pressure chamber 13 b due to the piston compression force acting on the swash plate 5, and the movable body 13 a moves from the swash plate 5 side in the direction of the drive axis O. It moves toward the lug plate 51 side. In the movable body 13a, the second movable cylindrical portion 132 and the third movable cylindrical portion 133 enter the fixed cylindrical portion 51a.

  At the same time, in this compressor, the swash plate 5 slides the cam surface 51b so that each swash plate arm 5e, 5f is remote from the drive shaft O by the piston compression force acting on itself and the urging force of the return spring 37. Move. For this reason, in the swash plate 5, the bottom dead center side is swung clockwise while substantially maintaining the position of the top dead center corresponding portion T. Thus, in this compressor, the inclination angle of the swash plate 5 with respect to the drive axis O of the drive shaft 3 increases. Thereby, in this compressor, the stroke of piston 9 increases and the discharge capacity per one rotation of drive shaft 3 becomes large. The inclination angle of the swash plate 5 shown in FIG. 1 is the maximum inclination angle in this compressor. When the swash plate 5 is at the maximum inclination angle, the swash plate arms 5e and 5f and the cam surface 51b come into contact with each other at the first position P1.

  On the other hand, if the control valve 15c shown in FIG. 2 reduces the flow rate of the refrigerant flowing through the low pressure passage 15a, the refrigerant in the discharge chamber 35 is easily stored in the pressure adjustment chamber 31 through the high pressure passage 15b and the orifice 15d. . For this reason, the pressure in the control pressure chamber 13 b is substantially equal to that in the discharge chamber 35, and the pressure in the control pressure chamber 13 b is higher than that in the swash plate chamber 25. For this reason, as shown in FIG. 7, in the actuator 13, the volume of the control pressure chamber 13b increases, and the movable body 13a moves away from the lug plate 51 in the direction of the drive axis O toward the swash plate 5 side. .

  Thereby, in this compressor, the action surface 134 a of the action part 134 presses the convex part 5 g toward the rear of the swash plate chamber 25 at the action position F. For this reason, the swash plate arms 5e and 5f slide on the cam surface 51b so as to be close to the drive axis O, and the swash plate 5 maintains the position of the top dead center corresponding portion T while maintaining the bottom dead center. The side swings counterclockwise. Thus, in this compressor, the inclination angle of the swash plate 5 with respect to the drive axis O of the drive shaft 3 decreases. Thereby, in this compressor, the stroke of the piston 9 is reduced, and the discharge capacity per one rotation of the drive shaft 3 is reduced. Further, the swash plate 5 comes into contact with the return spring 37 as the inclination angle decreases. The inclination angle of the swash plate 5 shown in FIG. 7 is the minimum inclination angle in this compressor. When the swash plate 5 is at the minimum inclination angle, the swash plate arms 5e and 5f and the cam surface 51b come into contact with each other at the second position P2.

  Thus, in this compressor, the actuator 13 is employed, and the inclination angle of the swash plate 5 is changed by the pressure change in the control pressure chamber 13 b having a smaller volume than the swash plate chamber 25. For this reason, in this compressor, it is possible to reduce the amount of refrigerant required for changing the inclination angle, compared to a compressor that changes the inclination angle by changing the pressure in the swash plate chamber 25. For this reason, in this compressor, it is possible to suppress an increase in the size of the swash plate chamber 25 and consequently the housing 1.

  Further, in this compressor, the swash plate arms 5e and 5f of the link mechanism 7 transmit the rotation of the lug plate 51 to the swash plate 5 and substantially maintains the position of the top dead center corresponding portion T of the swash plate 5. The change of the inclination angle is allowed. And the convex part 5g formed in the swash plate main body 5 is contact | abutted and pressed by the action part 134 formed in the movable body 13a, and the inclination-angle of the swash plate 5 is changed. That is, in this compressor, when changing the inclination angle of the swash plate 5, the movable body 13 a presses while directly contacting the swash plate 5. For this reason, in this compressor, since a sleeve such as a conventional hinge sphere is not provided between the movable body 13a and the swash plate 5, it is possible to realize downsizing by the amount of such a sleeve. ing.

  In this compressor, since the movable body 13a presses while directly contacting the swash plate 5, the direction of the load acting on the swash plate 5 is difficult to change. For this reason, in this compressor, the movable body 13a can easily press the swash plate 5 in the direction of the drive axis O, and the movable body 13a can stably change the inclination angle of the swash plate 5. Moreover, in this compressor, since the attitude | position of the movable body 13a is stabilized, it is hard to produce a leak in the pressure in the control pressure chamber 13b.

  And in this compressor, the action part 134 of the movable body 13a and the convex part 5g formed in the swash plate main body 50 are eccentric from the drive shaft center O toward the top dead center corresponding part T side of the swash plate 5. For this reason, in this compressor, it is easy to ensure a space for the movable body 13a to move in the direction of the drive axis O between the lug plate 51 and the swash plate 5 without hindering the change of the inclination angle. It has become. For these reasons, in this compressor, it is possible to increase the diameter of the actuator 13 and move the movable body 13a with sufficient thrust. For this reason, in this compressor, the inclination angle can be quickly changed according to the driving situation of the vehicle.

  Further, in this compressor, each swash plate arm 5e, 5f substantially maintains the position of the top dead center corresponding portion T of the swash plate 5, and the working surface 134a and the convex portion 5g come into contact with each other, thereby corresponding to the top dead center. The movable body 13a presses the swash plate 5 on the portion T side. For this reason, in this compressor, when the inclination angle range is the same, the stroke of the movable body 13a in the direction of the drive axis O can be reduced. For this reason, in this compressor, the long axis is suppressed. Hereinafter, it will be specifically described by comparison with a comparative example.

  The compressor of the comparative example is configured by partially changing the swash plate 5 and the movable body 13a of the compressor of the first embodiment and without providing the convex portion 5g and the action portion 134. Thereby, in the compressor of the comparative example, the rear end of the first movable cylindrical portion 131 of the movable body 13a contacts the front surface 5a around the insertion hole 5d. For this reason, in the compressor of a comparative example, the movable body 13a and the swash plate 5 will contact | abut in the position which becomes on the drive shaft center O substantially.

  In such a compressor of the comparative example, when the swash plate 5 (see the two-dot chain line) in the state where the inclination angle is maximum in FIG. 8 is displaced until the inclination angle becomes the minimum state, the movable body 13a needs to move in the direction of the drive axis O by a distance S2.

  On the other hand, in the compressor according to the first embodiment, when the swash plate 5 having the maximum inclination angle is displaced to the minimum state, the movable body 13a has a distance S1 in the direction of the drive axis O. It is enough to move only. That is, the stroke of the movable body 13a in the direction of the drive axis O of the compressor of the first embodiment is smaller than that of the compressor of the comparative example.

  Further, as shown in FIG. 8A, in the compressor of the first embodiment, when the inclination angle is maximum, the working surface 134a and the convex portion 5g are located at a position remote from the drive axis O. Point contact is made at a certain operating position F. Then, the inclination angle becomes smaller, and the swash plate arms 5e and 5f and the cam surface 51b move to the second position P2 side. As a result, in this compressor, as indicated by the white arrow in FIG. 8B, the action position F moves toward the drive axis O when the inclination angle decreases. Here, in this compressor, even when the inclination angle is minimized, the operating position F does not move beyond the drive shaft center O to the side opposite to the top dead center corresponding portion T side. On the other hand, in the compressor of the comparative example, even when the inclination angle is changed, the operating positions of the movable body 13a and the swash plate 5 are not substantially changed.

  For this reason, as shown in the graph of FIG. 10, in the compressor of Example 1, it becomes possible to reduce the load of the movable body 13a when the inclination angle is reduced. As a result, in this compressor, the differential pressure between the swash plate chamber 25 and the control pressure chamber 13b (hereinafter referred to as variable differential pressure) when changing the inclination angle is made to be substantially uniform while reducing the overall pressure. it can.

  On the other hand, in the compressor of the comparative example, since the operation position is almost unchanged, the load on the movable body 13a when the inclination angle is reduced is increased. For this reason, in the compressor of the comparative example, it is necessary to increase the variable differential pressure as the inclination angle is decreased.

  Therefore, the compressor of Example 1 can exhibit sufficient controllability while realizing as small a size as possible.

  In this compressor, a moment to rotate in the direction orthogonal to the drive axis O acts on the swash plate 5 due to a compression reaction force during operation. In this respect, in this compressor, the guide surfaces 52 a and 52 b formed in the insertion hole 5 d slide on the outer peripheral surface 30 of the drive shaft 3 in accordance with the change in the inclination angle of the swash plate 5. The swash plate 5 changes the tilt angle while being guided by the link mechanism 7 and the drive shaft 3 in the drive axis O direction and the tilt angle direction. For this reason, in this compressor, even if the swash plate 5 is not tilted in the direction orthogonal to the drive axis O during operation, such a tilt can be suitably prevented. Yes. In this compressor, the manufacturing cost is reduced by reducing the number of parts by omitting the sleeve.

  Further, in this compressor, when the inclination angle of the swash plate 5 is changed, the movable body 13a only presses while directly contacting the swash plate 5, and the action portion 134 and the convex portion 5g are connected by a connecting pin or the like. There is no consolidation. For this reason, in this compressor, there is no possibility that the posture of the movable body 13a will change depending on the configuration of the connecting portion, and it is difficult for the posture of the movable body 13a to change when the inclination angle is changed. Further, in this compressor, it is possible to suppress the complication of the configuration, and in this respect also, it is possible to reduce the manufacturing cost.

  Further, in this compressor, the movable body 13a is inserted through the drive shaft 3, and the movable body 13a can be fitted to the lug plate 51 by housing the movable body 13a in the fixed cylindrical portion 51a. . Here, in this compressor, the third movable cylindrical portion 133 of the movable body 13 a enters the fixed cylindrical portion 51 a to a position inside the thrust bearing 55. For this reason, in this compressor, it is possible to suitably secure a space for the movable body 13a to move in the direction of the drive axis O between the lug plate 51 and the swash plate 5 while shortening the axial length. It has become. Further, in this compressor, the thrust bearing 55 is provided, so that the suction reaction force and the compression reaction force acting on the piston 9 can be suitably supported.

  Further, in this compressor, it is possible to suitably form the control pressure chamber 13b between the lug plate 51 and the movable body 13a by the fixed cylindrical portion 51a. In this compressor, the air tightness of the control pressure chamber 13b is suitably ensured by the O-rings 49c and 49d provided in the first and third movable cylindrical portions 131 and 133, respectively.

  Furthermore, in this compressor, the action part 134 projects from the top dead center corresponding part T side of the swash plate 5 in the first movable cylindrical part 131 and is integrated with the movable body 13a. An action surface 134 a is formed on the action part 134. For these reasons, in this compressor, the working surface 134a and the convex portion 5g can be easily brought into contact with each other at a position eccentric from the drive axis O toward the top dead center corresponding portion T side. Here, since the convex portion 5g is formed so as to protrude in a substantially hemispherical shape, it is possible to suitably make point contact between the working surface 134a and the convex portion 5g, and the swash plate 5 changes the inclination angle. It is easy to do.

  Further, the convex portion 5 g is formed integrally with the front surface 5 a of the swash plate body 50. For this reason, in this compressor, the number of parts can be reduced, and the manufacturing is facilitated and the manufacturing cost can be reduced.

  Further, in this compressor, the swash plate chamber 25 and the suction chamber 33 communicate with each other through the suction passage 39. Thereby, in this compressor, the swash plate chamber 25 can be set to a low pressure similarly to the suction chamber 33.

  In addition, the control mechanism 15 adjusts the pressure in the pressure adjustment chamber 31 and thus the control pressure chamber 13b by adjusting the opening of the control valve 15c. An axial path 3 a and a radial path 3 b are formed in the drive shaft 3. Thus, in this compressor, the control mechanism 15 can be reduced in size, the pressure in the control pressure chamber 13b can be suitably changed, and the movable body 13a can be suitably moved. It has become.

  Moreover, in this compressor, the airtightness of the pressure regulation chamber 31 is suitably ensured by O-rings 49 a and 49 b provided at the rear end of the drive shaft 3.

(Example 2)
As shown in FIG. 11, in the compressor according to the second embodiment, the swash plate 5 includes a swash plate body 50, swash plate arms 5 e and 5 f, and a contact member 59. This contact member 59 also corresponds to the operated part in the present invention.

  The contact member 59 is formed separately from the swash plate body 50. The front surface 5a of the swash plate main body 50 is attached between the swash plate arms 5e and 5f, and is eccentrically located on the top dead center corresponding portion T side of the swash plate 5 with respect to the drive axis O. .

  The contact member 59 is formed with a convex portion 59a protruding forward. The convex portion 59a is formed in a substantially hemispherical shape. The convex part 59a is in point contact with the action surface 134a of the action part 134 at the action position F. Thus, in this compressor, the action part 134 and the contact member 59 are in contact with each other through the action surface 134a and the convex part 59a at a position eccentric from the drive axis O to the top dead center corresponding part T side of the swash plate 5. Yes. Other configurations of the compressor are the same as those of the compressor according to the first embodiment, and the same components are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, since the swash plate 5 and the contact member 59 are separate, it is possible to increase the degree of freedom in designing the swash plate body 50 and the contact member 59. Other functions of this compressor are the same as those of the compressor of the first embodiment.

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

  For example, in the compressors according to the first and second embodiments, while the inclination angle of the swash plate 5 decreases from the maximum state to the predetermined angle, the operating position F moves toward the drive axis O side, and the minimum from the predetermined angle. You may comprise so that the action position F may not move until it becomes an inclination angle.

  Further, the convex portion 5g and the convex portion 59a may be formed in a flat shape, and the action surface 134a of the action portion 134 may be formed in a curved shape. As a result, at the operating position F, the convex portion 5g and the contact member 59 can be brought into line contact with the operating portion 134.

  Further, the control mechanism 15 may be configured such that the control valve 15c is provided for the high pressure passage 15b and the orifice 15d is provided for the low pressure passage 15a. In this case, the flow rate of the high-pressure refrigerant flowing through the high-pressure passage 15b can be adjusted by the control valve 15c. As a result, the control pressure chamber 13b can be quickly brought to a high pressure by the high pressure in the discharge chamber 35, and the compression capacity can be quickly reduced. Further, in place of the control valve 15c, a three-way valve connected to the low-pressure passage 15a and the high-pressure passage 15b is provided, and by adjusting the opening of the three-way valve, the refrigerant flowing in the low-pressure passage 15a and the high-pressure passage 15b The flow rate may be adjusted.

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

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 3a ... Axis path (control path)
3b: Path (control passage)
5 ... Swash plate 5d ... Insertion hole 5e, 5f ... Swash plate arm (transmission member)
5g ... convex part (acting part)
7 ... Link mechanism 9 ... Piston 11a, 11b ... Shoe (conversion mechanism)
13 ... Actuator 13a ... Movable body 13b ... Control pressure chamber (control passage)
15 ... Control mechanism 15a ... Low pressure passage (control passage)
15b ... High pressure passage (control passage)
15c ... Control valve 25 ... Swash plate chamber 30 ... Outer peripheral surface 31 ... Pressure adjustment chamber 33 ... Suction chamber 35 ... Discharge chamber 21a ... Cylinder bore 49a, 49b ... O-ring (third sealing means)
49c ... O-ring (first sealing means)
49d ... O-ring (second sealing means)
50 ... Swash plate body 51 ... Lug plate (lug member)
51a ... fixed cylindrical part 55 ... thrust bearing 59 ... contact member (acting part)
59a ... convex portion 131 ... first movable cylindrical portion (movable cylindrical portion)
132: second movable cylindrical portion (movable cylindrical portion)
133: Third movable cylindrical portion (movable cylindrical portion)
134 ... action part F ... action position O ... drive shaft center T ... top dead center corresponding part

Claims (14)

A housing in which 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; the drive shaft and the swash plate; A link mechanism that allows a change in the inclination angle of the swash plate with respect to a direction orthogonal to the drive axis of the drive shaft, a piston that is reciprocally moved in the cylinder bore, and a swash plate A conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the inclination angle by rotation; an actuator capable of changing the inclination angle; and a control mechanism for controlling the actuator;
The link mechanism includes a lug member fixed to the drive shaft in the swash plate chamber, and a transmission member that transmits the rotation of the lug member to the swash plate.
The swash plate is formed with an insertion hole that slides on the outer periphery of the drive shaft in accordance with the change in the inclination angle.
The swash plate is guided in the drive axis direction and the tilt angle direction by the link mechanism and the insertion hole to change the tilt angle,
The actuator can be rotated integrally with the lug member and the swash plate, and is partitioned by a movable body that can move in the drive axis direction and change the tilt angle, and the lug member and the movable body. A control pressure chamber that moves the movable body by changing an internal pressure by the control mechanism,
The movable body is formed with an action portion capable of pressing the swash plate by the pressure in the control pressure chamber,
A variable displacement swash plate compressor, wherein the swash plate is formed with an actuated portion that is pressed against the acting portion.   The variable displacement swash plate compressor according to claim 1, wherein the movable body is inserted through the drive shaft and can be fitted into the lug member. The movable body has a movable cylindrical portion having a cylindrical shape coaxial with the drive shaft,
The lug member has a cylindrical shape coaxial with the drive shaft center on the outer peripheral side of the movable cylindrical portion, and has a cylindrical fixed cylindrical portion that secures the control pressure chamber in the movable cylindrical portion. 2. The variable capacity swash plate compressor according to 2. Between the movable cylindrical portion and the drive shaft, a first sealing means for sealing the control pressure chamber is provided,
4. The variable capacity swash plate compressor according to claim 3, wherein a second sealing means for sealing the control pressure chamber is provided between the movable cylindrical portion and the fixed cylindrical portion. A thrust bearing that receives a thrust force acting on the piston is provided between the housing and the lug member,
The variable displacement swash plate compressor according to claim 3 or 4, wherein the movable cylindrical portion has a smaller diameter than the thrust bearing and can be fitted into the thrust bearing. The swash plate defines a top dead center corresponding portion that positions the piston at the top dead center,
6. The variable displacement swash plate compressor according to claim 1, wherein the acting part and the acted part are eccentric from the driving shaft toward the top dead center corresponding part. The acting part and the acted part are in point contact or line contact with each other at the action position,
The variable displacement swash plate compressor according to claim 6, wherein the operating position moves toward the drive shaft when the tilt angle becomes small. The action portion has an action surface extending in a direction orthogonal to the drive shaft center,
The capacity-variable swash plate compressor according to claim 6 or 7, wherein the actuated portion has a convex portion that protrudes from the swash plate body and abuts against the working surface. The swash plate defines a top dead center corresponding portion that positions the piston at the top dead center,
The movable body has a movable cylindrical portion having a cylindrical shape coaxial with the drive shaft,
9. The variable displacement swash plate compressor according to claim 7, wherein the action portion protrudes on the top dead center corresponding portion side of the movable cylindrical portion.   10. The variable capacity slant according to claim 1, wherein the swash plate includes a swash plate main body in which the insertion hole is formed, and the actuated portion formed integrally with the swash plate main body. Plate type compressor.   10. The variable displacement swash plate compression according to claim 1, wherein the swash plate includes a swash plate main body in which the insertion hole is formed, and the actuated portion fixed to the swash plate main body. Machine. The housing is formed with a suction chamber and a discharge chamber,
The variable displacement swash plate compressor according to any one of claims 1 to 11, wherein the suction chamber and the swash plate chamber communicate with each other. The control mechanism includes a control passage communicating the control pressure chamber and the suction chamber and / or the discharge chamber, and a control valve capable of adjusting an opening degree of the control passage,
The variable displacement swash plate compressor according to claim 12, wherein at least part of the control passage is formed in the drive shaft. Between the housing and one end of the drive shaft, a pressure adjustment chamber is formed that communicates with the control pressure chamber via the control passage and the pressure is changed by the control valve.
14. The variable capacity swash plate compressor according to claim 13, wherein third sealing means for sealing the pressure adjusting chamber is provided between the housing and the drive shaft.

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