VARIABLE DISPLACEMENT SWASH PLATE TYPE COMPRESSOR

Abstract

A variable displacement swash plate type compressor includes an actuator having a movable body and a control pressure chamber. An acting portion capable of pressing a swash plate by the pressure in the control pressure chamber is formed at the movable body, and an acted portion that abuts on and is pressed by the acting portion is formed at the swash plate. The acting portion abuts on the acted portion at an operative position, which moves in accordance with the change of an inclination angle of the swash plate. A top-dead-center corresponding portion is defined in the swash plate, and the operative position when the inclination angle is maximum is closer to the top-dead-center corresponding portion as compared to the operative position when the inclination angle is minimum.

Description

TECHNICAL FIELD

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

BACKGROUND ART

Patent Literature 1 discloses a conventional variable displacement swash plate type compressor (hereinafter referred to as a compressor). This compressor comprises a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a conversion mechanism, and a capacity control mechanism.

In the housing, a suction chamber, a discharge chamber, a swash plate chamber and a plurality of cylinder bores are formed. The drive shaft is rotatably supported by the housing. The swash plate is rotatable in the swash plate chamber by rotation of the drive shaft. The link mechanism is provided between the drive shaft and the swash plate and permits change of an inclination angle of the swash plate with respect to a direction perpendicular to a driving axis of the drive shaft. The 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 rotation of the lug member to the swash plate. The pistons are reciprocally accommodated in respective cylinder bores. The conversion mechanism reciprocates the pistons in the cylinder bores at a stroke corresponding to the inclination angle by rotation of the swash plate. The capacity control mechanism has a supply passage, a bleed passage and a control valve. The supply passage provides communication between the discharge chamber and the swash plate chamber. The bleed passage provides communication between the swash plate chamber and the suction chamber. The control valve is capable of changing the pressure in the swash plate chamber by regulating an opening degree of the supply passage.

In the compressor, when the control valve increases the pressure in the swash plate chamber, the inclination angle becomes small and the stroke of the pistons decreases. Therefore, a compression capacity per rotation of the drive shaft becomes small. On the other hand, when the control valve decreases the pressure in the swash plate chamber, the inclination angle of the swash plate becomes large, and the stroke of the pistons increases. Therefore, the compression capacity per rotation of the drive shaft becomes large. In this manner, in this compressor, the discharge capacity of refrigerant is changeable in response to the driving conditions of a vehicle or the like on which the compressor is mounted.

However, in the case of changing the inclination angle by changing the pressure in the swash plate chamber like this compressor, it is necessary to provide a sufficient amount of refrigerant in the swash plate chamber in order to change the inclination angle. Therefore, the size of the compressor tends to be increased due to a large swash plate chamber.

Furthermore, in this compressor, it is inevitable that blow-by gas having a high pressure flows into the swash plate chamber. Furthermore, in this compressor, when the outside air temperature drops, the refrigerant in the swash plate chamber is likely to condense and liquid accumulation occurs in the swash plate chamber. For these reasons, in this compressor, it is difficult to change the inclination angle suitably.

Therefore, a compressor as disclosed in Patent Literature 2 has also been proposed. This compressor includes an actuator that is capable of changing an inclination angle, and a control mechanism that controls the actuator.

Specifically, the actuator has a lug member, a movable body that engages with a swash plate so as to be rotatable integrally therewith and is movable in the direction of a driving axis to change the inclination angle, and a control pressure chamber that is defined by the lug member and the movable body and moves the movable body by its internal pressure. The control mechanism has a control passage and a control valve. The control passage has a variable pressure passage that communicates with the control pressure chamber, a low pressure passage that communicates with a suction chamber and a swash plate chamber, and a high pressure passage that communicates with a discharge chamber. A part of the variable pressure passage is formed in a drive shaft. The control valve regulates an opening degree of the variable pressure passage, the low pressure passage and the high pressure passage. In other words, the control valve allows the variable pressure passage to communicate with the low pressure passage or the high pressure passage.

In this compressor, when the control valve allows the variable pressure passage to communicate with the high pressure passage, the pressure in the control pressure chamber becomes higher than that of the swash plate chamber. Thereby, the movable body of the actuator moves away from the lug member, and the inclination angle decreases. Therefore, the stroke of the pistons decreases and the discharge capacity becomes small. On the other hand, when the control valve allows the variable pressure passage to communicate with the low pressure passage, the pressure in the control pressure chamber becomes as low as that of the swash plate chamber. Thereby, the movable body of the actuator approaches the lug member, and the inclination angle increases. Therefore, the stroke of the pistons increases and the discharge capacity becomes large.

Since this compressor is configured to change the pressure in the control pressure chamber, which has a smaller volume than the swash plate chamber, the amount of the refrigerant required to change the inclination angle can be reduced as compared to the compressor configured to change the pressure in the swash plate chamber, and thereby downsizing can be realized.

Furthermore, since this compressor is configured to change the inclination angle by changing the pressure in the control pressure chamber, the blow-by gas flowing into the swash plate chamber and the liquid accumulation in the swash plate chamber are less likely to exert an adverse effect on the change of the inclination angle.

CITATION LIST

Patent Literature

Patent Literature 1: Japanese Patent Laid-Open No. 2002-213350

Patent Literature 2: Japanese Patent Laid-Open No. 52-131204

SUMMARY OF INVENTION

Technical Problem

However, in the compressor described in Patent Literature 2 described above, when a plane determined by the driving axis and a top-dead-center corresponding portion of the swash plate is defined as a first imaginary plane, the movable body of the actuator engages with the swash plate at a second imaginary plane that is perpendicular to the first imaginary plane and includes the driving axis. In addition, an operative position where the movable body abuts on the hinge ball moves in parallel with the direction of the driving axis as the inclination angle of the swash plate changes. The same applies to an operative position where the hinge ball abuts on the swash plate. That is, in this compressor, the distance between the operative position and the driving axis does not change even when the inclination angle of the swash plate changes.

Therefore, in this compressor, at the time of decreasing the inclination angle, it is necessary to increase a differential pressure between the swash plate chamber and the control pressure chamber (hereinafter referred to as a variable differential pressure) to thereby move the movable body by a larger thrust force. That is, in this compressor, the load exerted on the movable body increases as the inclination angle decreases. Therefore, in this compressor, the amount of change in the variable differential pressure when the inclination angle changes is large; therefore, it is difficult to quickly change the inclination angle in response to the driving conditions of a vehicle or the like, and controllability is lowered.

Furthermore, in this compressor, since the distance between the operative position and the driving axis does not change, a stroke of the movable body in order to change the inclination angle of the swash plate is long in the direction of the driving axis. Consequently, it is inevitable to enlarge the compressor in the axial length, and therefore, there is a concern about mountability on a vehicle or the like.

The present invention has been made in the light of the conventional circumstances described above, and an object of the invention is to provide a variable displacement swash plate type compressor capable of exhibiting high controllability and excellent mountability.

Solution to Problem

A variable displacement swash plate type compressor of the present invention comprises: a housing in which a swash plate chamber and a cylinder bore are formed; a drive shaft that is rotatably supported by the housing; a swash plate that is rotatable in the swash plate chamber by rotation of the drive shaft; a link mechanism that is provided between the drive shaft and the swash plate and permits change of an inclination angle of the swash plate with respect to a direction perpendicular to a driving axis of the drive shaft; a piston that is reciprocally accommodated in the cylinder bore; a conversion mechanism that reciprocates the piston in the cylinder bore at a stroke corresponding to the inclination angle by rotation of the swash plate; an actuator capable of changing the inclination angle; and a control mechanism that controls the actuator,

wherein the link mechanism has a lug member that is fixed to the drive shaft in the swash plate chamber and a transmission member that transmits rotation of the lug member to the swash plate,

the actuator has the lug member, a movable body that is rotatable integrally with the swash plate and is capable of changing the inclination angle by moving in the direction of the driving axis, and a control pressure chamber that is defined by the lug member and the movable body and moves the movable body by changing its internal pressure by the control mechanism,

an acting portion that is capable of pressing the swash plate by the pressure in the control pressure chamber is formed at the movable body,

an acted portion that abuts on and is pressed by the acting portion is formed at the swash plate,

the acting portion abuts on the acted portion at an operative position,

the operative position moves in accordance with the change of the inclination angle,

a top-dead-center corresponding portion for positioning the piston at its top dead center is defined in the swash plate, and

the operative position when the inclination angle is maximum is closer to the top-dead-center corresponding portion as compared to the operative position when the inclination angle is minimum.

In the compressor of the present invention, the transmission member of the link mechanism transmits rotation of the lug member to the swash plate. In addition, the operative position at which the acting portion of the movable body abuts on the acted portion of the swash plate moves in accordance with the change of the inclination angle of the swash plate. Specifically, the operative position when the inclination angle is maximum is closer to the top-dead-center corresponding portion of the swash plate as compared to the operative position when the inclination angle is minimum.

Therefore, in this compressor, as compared with the case where the operative position has a constant distance from the driving axis even when the inclination angle of the swash plate changes, it is possible to move the movable body without increasing the variable differential pressure at the time of decreasing the inclination angle so as to provide a large thrust force. That is, in this compressor, it is possible to reduce the load exerted on the movable body at the time of decreasing the inclination angle. Consequently, in this compressor, the amount of change in the variable differential pressure when the inclination angle changes is small; therefore, it is easy to quickly change the inclination angle in response to the driving conditions of a vehicle or the like, and high controllability can be exhibited.

Furthermore, in this compressor, since the operative position moves as described above in accordance with the change of the inclination angle of the swash plate, the stroke of the movable body in the direction of the driving axis can be reduced as compared with the case where the operative position has a constant distance from the driving axis, provided that the range of their inclination angle is the same. This suppresses enlargement of the compressor in the axial length.

Accordingly, the compressor of the present invention is capable of exhibiting high controllability and excellent mountability.

It is not impossible to employ such a configuration that, for example, the acting portion is connected to the acted portion with a connection pin etc. However, in this case, there is a risk that the configuration of a connection portion changes the posture of the movable body. In addition, because the number of components increases, the configuration of the compressor is complicated and manufacturing cost increases. In contrast, in the compressor of the present invention, the movable body merely abuts directly on and presses the swash plate to change the inclination angle of the swash plate, and therefore, the posture of the movable body is less likely to change. In addition, in this compressor, it is possible to suppress complication of the configuration, and reduction in manufacturing cost can be realized.

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

It is preferable that the drive shaft is inserted through the movable body, and the movable body is capable of being fitted to the lug member. In this case, a space for allowing the movable body to move in the direction of the driving axis can be suitably provided between the lug member and the swash plate.

Furthermore, the movable body may have a movable cylindrical portion that is formed into a cylindrical shape and coaxial with the driving axis. It is preferable that the lug member has a fixed cylindrical portion that is formed into a cylindrical shape and is coaxial with the driving axis at an outer circumferential side of the movable cylindrical portion to thereby provide the control pressure chamber in the movable cylindrical portion. In this case, by fitting the movable cylindrical portion into the fixed cylindrical portion, the movable body can be fitted to the lug member. Furthermore, since the control pressure chamber is provided in the movable cylindrical portion by the fixed cylindrical portion, the control pressure chamber can be suitably formed between the lug member and the movable body.

Furthermore, in this case, a first seal member that seals the control pressure chamber may be provided between the movable cylindrical portion and the drive shaft. In addition, it is preferable that a second seal member that seals the control pressure chamber is provided between the movable cylindrical portion and the fixed cylindrical portion. Thereby, hermeticity of the control pressure chamber can be suitably ensured. Here, as the first seal member and the second seal member, various seals can be employed besides O-rings etc. The first seal member and the second seal member may be of the same kind or different kinds.

A thrust bearing that receives a thrust force which acts on the piston may be provided between the housing and the lug member. In addition, it is preferable that the movable cylindrical portion is smaller in diameter than the thrust bearing and capable of advancing to an inner side of the thrust bearing.

In this case, it is possible for the thrust bearing to suitably receive a suction reaction force which acts on the piston during a suction phase and a compression reaction force which acts on the piston during a compression phase. Furthermore, by allowing the movable cylindrical portion to advance to the inner side of the thrust bearing, even if the axial length of the compressor is short, the space for allowing the movable body to move in the direction of the driving axis can be sufficiently ensured.

In the compressor of the present invention, the acting portion and the acted portion come into point-contact or line-contact with each other at the operative position. In this case, the contact area between the acting portion and the acted portion can be made small. Here, the straight line on which the operative position and the acted portion are brought into line-contact is perpendicular to the first imaginary plane determined by the top-dead-center corresponding portion of the swash plate and the driving axis. Furthermore, when bringing the acting portion into point-contact or line-contact with the acted portion at the operative position, it is preferable that either one of a portion in the acting portion where it abuts on the acted portion and a portion in the acted portion where it abuts on the acting portion is formed into a curved shape.

Furthermore, the position in the movable body where the acting portion is formed and the position in the swash plate where the acted portion is formed can be designed as appropriate. In particular, in the compressor of the present invention, the acting portion and the acted portion may be located eccentrically toward the top-dead-center corresponding portion from the driving axis. It is preferable that the operative position moves toward the driving axis when the inclination angle decreases.

In this case, a space for allowing the movable body to move in the direction of the driving axis is easily provided between the lug member and the swash plate without disrupting the change of the inclination angle. Therefore, in this compressor, it is possible to increase the diameter of the actuator so as to quickly move the movable body by a sufficient thrust force while suppressing enlargement of the compressor in the axial length.

The acting portion may have an acting surface that extends in the direction perpendicular to the driving axis. It is preferable that the acted portion has a protrusion that protrudes from the swash plate and abuts on the acting surface. In this case, the acting portion and the acted portion can be suitably brought into point-contact or line-contact with each other.

It is preferable that the acting portion protrudes from the movable cylindrical portion toward the top-dead-center corresponding portion. In this case, the acting portion easily abuts on the acted portion.

It is preferable that the swash plate has a swash plate main body that is formed with an insertion hole, through which the drive shaft is inserted, and the acted portion that is integrally formed with the swash plate main body. In this case, it is possible to reduce the number of components in the compressor, facilitate manufacturing, and reduce manufacturing cost.

It is also preferable that the swash plate has a swash plate main body that is formed with an insertion hole, through which the drive shaft is inserted, and the acted portion that is fixed to the swash plate main body. In this case, it is possible to improve the flexibility of design with respect to the swash plate main body and the acted portion.

In the compressor of the present invention, a suction chamber and a discharge chamber may be formed in the housing. It is preferable that the suction chamber and the swash plate chamber communicate with each other. In this case, the pressure in the swash plate chamber can be made low as well as the suction chamber.

Furthermore, the control mechanism may have a control passage that provides communication between the control pressure chamber and the suction chamber and/or the discharge chamber, and a control valve that is capable of regulating an opening degree of the control passage. 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 and suitably move the movable body while downsizing the control mechanism.

A pressure regulation chamber that communicates with the control pressure chamber through the control passage and allows a pressure therein to be changed by the control valve may be formed between the housing and one end of the drive shaft. It is preferable that a third seal member that seals the pressure regulation chamber is provided between the housing and the drive shaft.

In this case, when the pressure in the pressure regulation chamber is changed by the control valve, the control pressure chamber moves the movable body. By the third seal member, hermeticity of the pressure regulation chamber can be suitably ensured. Here, as the third seal member, various seals can be employed besides O-rings etc. as in the case of the first and second seal members described above. Furthermore, the third seal member may be of the same kind as or a different kind from the first and second seal members.

Advantageous Effects of Invention

The compressor of the present invention is capable of exhibiting high controllability and excellent mountability.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a sectional view of a compressor according to Embodiment 1 at the time of maximum displacement.

FIG. 2 is a schematic diagram showing a control mechanism of the compressor according to Embodiment 1.

FIG. 3 is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing a rear end portion of a drive shaft.

FIG. 4 is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing an actuator.

FIG. 5 is a front perspective view showing a swash plate of the compressor according to Embodiment 1.

FIG. 6 is a sectional view of the compressor according to Embodiment 1 at the time of minimum displacement.

FIG. 7A is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing an operative position where an acting portion abuts on an acted portion when an inclination angle of the swash plate is maximum.

FIG. 7B is an enlarged sectional view of an essential part of the compressor according to Embodiment 1, showing the operative position when the inclination angle is minimum.

FIG. 8 is a graph showing a relation between the inclination angle and a variable differential pressure.

FIG. 9 is a schematic view of the compressor according to Embodiment 1 and a compressor of a comparative example, showing a difference in strokes of movable bodies.

FIG. 10 is a sectional view of a compressor according to Embodiment 2 at the time of maximum displacement.

DESCRIPTION OF EMBODIMENTS

Hereinafter, Embodiments 1 and 2, which embody the present invention, will be described with reference to the drawings. The compressors of Embodiments 1 and 2 are variable displacement single-head swash plate type compressors. These compressors are both mounted on vehicles and constitute refrigeration circuits of vehicle air-conditioning apparatus.

Embodiment 1

As shown in FIG. 1, the compressor of Embodiment 1 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, an actuator 13, and a control mechanism 15 which is shown in FIG. 2. In FIG. 1, the illustration of the swash plate 5 is partially simplified for ease of explanation. The same applies to FIGS. 6 and 10, which will be described later.

As shown in FIG. 1, the housing 1 has a front housing 17 that is located at a front side in the compressor, a rear housing 19 that is located at a rear side in the compressor, a cylinder block 21 that is located between the front housing 17 and the rear housing 19, and a valve unit 23.

The front housing 17 has a front wall 17a that extends in the up-down direction of the compressor at the front side, and a circumferential wall 17b that is integrated with the front wall 17a and extends rearward from the front side of the compressor. By the front wall 17a and the circumferential wall 17b, the front housing 17 is formed into a substantially cylindrical shape with a bottom. Furthermore, by the front wall 17a and the circumferential wall 17b, a swash plate chamber 25 is formed in the front housing 17.

A boss 17c that protrudes frontward is formed on the front wall 17a. A shaft seal device 27 is provided in the boss 17c. Furthermore, a first shaft hole 17d that extends 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.

An inlet port 250 that communicates with the swash plate chamber 25 is formed through the circumferential wall 17b. Through the inlet port 250, the swash plate chamber 25 is connected to an evaporator, which is not illustrated.

A part of the control mechanism 15 is provided in the rear housing 19. In addition, a first pressure regulation chamber 31a, a suction chamber 33 and a discharge chamber 35 are formed in the rear housing 19. The first pressure regulation chamber 31a is disposed at the center of the rear housing 19. The discharge chamber 35 is disposed annularly at an outer circumferential side in the rear housing 19. Furthermore, the suction chamber 33 is formed annularly between the first pressure regulation chamber 31a and the discharge chamber 35 in the rear housing 19. The discharge chamber 35 is connected to an outlet port which is not illustrated.

Cylinder bores 21a, the number of which is the same as that of the pistons 9, are formed in the cylinder block 21 at equiangular intervals in a circumferential direction. Front end sides of the respective cylinder bores 21a communicate with the swash plate chamber 25. Furthermore, a retainer groove 21b that restricts a lift amount of suction reed valves 41a, which will be described later, is formed in the cylinder block 21.

Furthermore, a second shaft hole 21c that extends in the front-rear direction of the compressor and communicates with the swash plate chamber 25 is formed through the cylinder block 21. A second sliding bearing 29b is provided in the second shaft hole 21c. Furthermore, a spring chamber 21d is formed in the cylinder block 21. 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 frontward in the swash plate chamber 25 when the inclination angle becomes minimum. Furthermore, a suction passage 39 that communicates 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.

Suction ports 40a, the number of which is the same as that of the cylinder bores 21a, are formed in the valve plate 40, the discharge valve plate 43 and the retainer plate 45. Furthermore, discharge ports 40b, the number of which is the same as that of the cylinder bores 21a, are formed in the valve plate 40 and the suction valve plate 41. The respective cylinder bores 21a communicate with the suction chamber 33 through the respective suction ports 40a, and communicate with the discharge chamber 35 through the respective discharge ports 40b. Furthermore, a first communication hole 40c and a second communication hole 40d are formed in the valve plate 40, the suction valve plate 41, the discharge valve plate 43 and the retainer plate 45. Through the first communication hole 40c, the suction chamber 33 and the suction passage 39 communicate with each other.

The suction valve plate 41 is provided on the front surface of the valve plate 40. A plurality of suction reed valves 41a that are capable of opening and closing the respective suction ports 40a by elastic deformation are formed in the suction valve plate 41. Furthermore, the discharge valve plate 43 is provided on the rear surface of the valve plate 40. A plurality of discharge reed valves 43a that are capable of opening and closing the respective discharge ports 40b by elastic deformation are formed in the discharge valve plate 43. The retainer plate 45 is provided on the rear surface of the discharge valve plate 43. The retainer plate 45 restricts a lift amount of the discharge reed valves 43a.

The drive shaft 3 is inserted from a boss 17c to 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 supported by the first sliding bearing 29a in the first shaft hole 17d. The rear end side of the drive shaft 3 is supported by the second sliding bearing 29b in the second shaft hole 21c. In this manner, the drive shaft 3 is rotatably supported around a driving axis O with respect to the housing 1. A second pressure regulation chamber 31b is defined by 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. A pressure regulation chamber 31 is formed by the first and the second pressure regulation chambers 31a and 31b.

As shown in FIG. 3, ring grooves 3c and 3d 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 regulation chamber 31 is sealed with the O-rings 49a and 49b, whereby the swash plate chamber 25 does not communicate with the pressure regulation chamber 31. The O-rings 49a and 49b correspond to the third seal member in the present invention.

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

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

As shown in FIG. 4, a fixed cylindrical portion 51a that is formed into a cylindrical shape and extends in the front-rear direction of the lug plate 51 is provided in a recessed manner in the lug plate 51. As shown in FIG. 1, the fixed cylindrical portion 51a extends from the rear end surface of the lug plate 51 to a position on an inner side of the thrust bearing 55 in the lug plate 51.

The lug arms 53 extend rearward from the lug plate 51. Furthermore, a cam surface 51b is formed at the lug plate 51 at a position between the lug arms 53. In FIG. 1 etc., only one of the lug arms 53 is illustrated for ease of explanation.

As shown in FIG. 5, the swash plate 5 has a swash plate main body 50, the swash plate arms 5e and 5f, and a protrusion 5g. The protrusion 5g corresponds to the acted portion in the present invention.

The swash plate main body 50 is formed into an annular flat-plate shape and has a front surface 5a and a rear surface 5b; in addition, a top-dead-center corresponding portion T for positioning the respective pistons 9 at their top dead center is defined therein. A restriction portion 5c that protrudes frontward from the swash plate 5 is formed on the front surface 5a. As shown in FIG. 1, the restriction portion 5c abuts on the lug plate 51 when the inclination angle of the swash plate 5 becomes maximum. Furthermore, the swash plate main body 50 is formed with an insertion hole 5d. The drive shaft 3 is inserted through the insertion hole 5d.

As shown in FIG. 5, the swash plate arms 5e and 5f are formed on the front surface 5a of the swash plate main body 50 at positions eccentric toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O. The swash plate arms 5e and 5f extend frontward from the front surface 5a.

The protrusion 5g protrudes frontward from the front surface 5a and is integrated with the swash plate main body 50. The protrusion 5g is formed into a substantially hemispherical shape, and located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O so as to be disposed between the swash plate arm 5e and the swash plate arm 5f.

As shown in FIG. 1, by inserting the swash plate arms 5e and 5f between the lug arms 53, the lug plate 51 is connected to the swash plate 5. Thereby, the swash plate 5 is rotatable along with the lug plate 51 in the swash plate chamber 25. The tip ends of the swash plate arms 5e and 5f abut on the cam surface 51b.

By connecting the lug plate 51 to the swash plate 5, the swash plate arms 5e and 5f and the protrusion 5g are located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O. In addition, the swash plate arms 5e and 5f slide on the cam surface 51b, whereby the swash plate 5 is able to change its inclination angle with respect to the direction perpendicular to the driving axis O from the maximum inclination angle shown in FIG. 1 to the minimum inclination angle shown in FIG. 6 while substantially maintaining the position of the top-dead-center corresponding portion T.

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

The movable body 13a, through which the drive shaft 3 is inserted, is slidable in contact with the drive shaft 3 to move in the direction of the driving axis O. The movable body 13a is formed into a cylindrical shape and coaxial with the drive shaft 3, and the diameter thereof is smaller than that of the thrust bearing 55 shown in FIG. 1. As shown in FIG. 4, the movable body 13a has 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 at a rear end side in the movable body 13a and has the smallest diameter in the movable body 13a. The second movable cylindrical portion 132 continues from the front end of the first movable cylindrical portion 131 and is formed such that its diameter increases gradually toward the front side of the movable body 13a. The third movable cylindrical portion 133 continues from the front end of the second movable cylindrical portion 132 and extends toward the front side of the movable body 13a. The third movable cylindrical portion 133 has the largest diameter in the movable body 13a.

Furthermore, an acting portion 134 is integrally formed at the rear end of the first movable cylindrical portion 131. As shown in FIG. 1, the acting portion 134 extends vertically from a position near the driving axis O toward the top-dead-center corresponding portion T of the swash plate 5, and is located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O. The acting portion 134 has an acting surface 134a which is formed into a flat shape. As shown in FIG. 7, the acting surface 134a comes into point-contact with the protrusion 5g at an operative position F. Thereby, the movable body 13a is rotatable integrally with the lug plate 51 and the swash plate 5. Here, since the protrusion 5g and the acting portion 134 are located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O, the operative position F is also located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O as shown in FIG. 1.

The movable body 13a is capable of being fitted to the lug plate 51 by allowing the second movable cylindrical portion 132 and the third movable cylindrical portion 133 shown in FIG. 4 to advance into the fixed cylindrical portion 51a (see FIG. 1). When the second movable cylindrical portion 132 and the third movable cylindrical portion 133 has advanced farthest into the fixed cylindrical portion 51a, the third movable cylindrical portion 133 reaches a position on an inner side of the thrust bearing 55 in the fixed cylindrical portion 51a.

As shown in FIG. 4, the control pressure chamber 13b is formed by the second movable cylindrical portion 132, the third movable cylindrical portion 133, the fixed cylindrical portion 51a and the drive shaft 3. Furthermore, a ring groove 131a is formed in the inner circumferential surface of the first movable cylindrical portion 131, and a ring groove 133a is formed in the outer circumferential 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 seal member in the present invention, and the O-ring 49d corresponds to the second seal member in the present invention. The control pressure chamber 13b is sealed with the O-rings 49c and 49d, whereby the hermeticity of the control pressure chamber 13b is ensured.

As shown in FIG. 1, an axial path 3a that extends in the direction of the driving axis O from the rear end of the drive shaft 3 toward the front end thereof and a radial path 3b that extends radially from the front end of the axial path 3a and opens at the outer circumferential surface of the drive shaft 3 are formed in the drive shaft 3. The rear end of the axial path 3a opens to the pressure regulation chamber 31. The radial path 3b opens to the control pressure chamber 13b. Through the axial path 3a and the radial path 3b, the pressure regulation chamber 31 and the control pressure chamber 13b communicate with each other.

The drive shaft 3 is connected to a pulley or an electromagnetic clutch, which are not illustrated, via a screw portion 3e which is formed at the tip end thereof.

The pistons 9 are respectively accommodated in the respective cylinder bores 21a and capable of reciprocating in the respective cylinder bores 21a. Compression chambers 57 are defined in the respective cylinder bores 21a by the respective pistons 9 and the valve unit 23.

Furthermore, an engaging portion 9a is formed in a recessed manner in each of the pistons 9. The shoes 11a and 11b formed into a hemispherical shape are provided in the respective engaging portions 9a. The shoes 11a and 11b convert the rotation of the swash plate 5 into reciprocal movement of the pistons 9. The shoes 11a and 11b correspond to the conversion mechanism in the present invention. In this manner, the pistons 9 are able to reciprocate in the cylinder bores 21a at a stroke corresponding to the inclination angle of the swash plate 5. Alternatively, instead of the shoes 11a and 11b, it is also possible to employ a wobble type conversion mechanism, in which a wobble plate is supported at the side of the rear surface 5b of the swash plate main body 50 via a thrust bearing and the wobble plate is connected to the respective pistons 9 via connecting rods.

As shown in FIG. 2, the control mechanism 15 has a low pressure passage 15a, a high pressure passage 15b, a control valve 15c, an orifice 15d, the axial path 3a and the radial path 3b. A control passage in the present invention is formed by the low pressure passage 15a, the high pressure passage 15b, the axial path 3a and the radial path 3b. Furthermore, the axial path 3a and the radial path 3b serve as variable pressure passages.

The low pressure passage 15a is connected to the pressure regulation chamber 31 and the suction chamber 33. Thereby, the control pressure chamber 13b, the pressure regulation chamber 31 and the suction chamber 33 communicate with one another through the low pressure passage 15a, the axial path 3a and the radial path 3b. The high pressure passage 15b is connected to the pressure regulation chamber 31 and the discharge chamber 35. The control pressure chamber 13b, the pressure regulation chamber 31 and the discharge chamber 35 communicate with one another through the high pressure passage 15b, the axial path 3a and the radial path 3b. Furthermore, the high pressure passage 15b is provided with the orifice 15d, whereby the flow rate of the refrigerant flowing through the high pressure passage 15b is reduced.

The control valve 15c is provided at the low pressure passage 15a. The control valve 15c is capable of regulating 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 that leads to the evaporator is connected to the inlet port 250 shown in FIG. 1, and a pipe that leads to a condenser is connected to the outlet port. The condenser is connected to the evaporator via pipes and an expansion valve. The refrigeration circuit of vehicle air-conditioning apparatus is constituted by the compressor, the evaporator, the expansion valve, the condenser and the like. Illustration of the evaporator, the expansion valve, the condenser and the pipes is omitted.

In the compressor configured as above, by rotation of the drive shaft 3, the swash plate 5 rotates and the pistons 9 reciprocate in the respective cylinder bores 21a. The volume of the compression chambers 57 thus changes in response to the stroke of the pistons 9. The refrigerant introduced from the evaporator into the swash plate chamber 25 through the inlet port 250 thus passes the suction chamber 33 through the suction passage 39 and then is compressed in the compression chambers 57. Subsequently, the refrigerant compressed in the compression chambers 57 is discharged to the discharge chamber 35 and then discharged to the condenser from the outlet port.

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. By changing the inclination angle of the swash plate 5 to increase or decrease the stroke of the pistons 9, it is possible to perform capacity control in this compressor.

Specifically, in the control mechanism 15, when 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 less likely to pass the high pressure passage 15b and the orifice 15d and be stored in the pressure regulation chamber 31. Therefore, the pressure in the control pressure chamber 13b becomes substantially equal to that in the suction chamber 33. As a result, as shown in FIG. 1, due to the piston compression force acting on the swash plate 5, in the actuator 13, the volume of the control pressure chamber 13b decreases and the movable body 13a moves from the side of the swash plate 5 toward the lug plate 51 in the direction of the driving axis O. Then, in the movable body 13a, the second movable cylindrical portion 132 and the third movable cylindrical portion 133 advance into the fixed cylindrical portion 51a.

At the same time, in this compressor, due to the piston compression force and the urging force of the return spring 37 acting on the swash plate 5, the swash plate arms 5e and 5f slide on the cam surface 51b so as to move away from the driving axis O. Therefore, a bottom dead center side of the swash plate 5 pivots in a clockwise direction while substantially maintaining the position of the top-dead-center corresponding portion T. In this manner, in this compressor, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the driving axis O of the drive shaft 3 increases. Thereby, in this compressor, the stroke of the pistons 9 increases and the discharge capacity per rotation of the drive shaft 3 becomes large. Here, 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 abut on the cam surface 51b at a first position P1.

On the other hand, when the control valve 15c shown in FIG. 2 decreases the flow rate of the refrigerant flowing through the low pressure passage 15a, the refrigerant in the discharge chamber 35 is more likely to pass the high pressure passage 15b and the orifice 15d and be stored in the pressure regulation chamber 31. Therefore, the pressure in the control pressure chamber 13b becomes substantially equal to that of the discharge chamber 35, and the pressure in the control pressure chamber 13b becomes higher than that of the swash plate chamber 25. As a result, as shown in FIG. 6, 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 toward the swash plate 5 in the direction of the driving axis O.

Thereby, in this compressor, the acting surface 134a of the acting portion 134 operates in such a manner as to press the protrusion 5g rearward in the swash plate chamber 25 at the operative position F. Therefore, the swash plate arms 5e and 5f slide on the cam surface 51b so as to approach the driving axis O, and the bottom dead center side of the swash plate 5 pivots in a counterclockwise direction while substantially maintaining the position of the top-dead-center corresponding portion T. In this manner, in this compressor, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the driving axis O of the drive shaft 3 decreases. Thereby, in this compressor, the stroke of the pistons 9 decreases and the discharge capacity per rotation of the drive shaft 3 becomes small. Furthermore, when the inclination angle decreases, the swash plate 5 abuts on the return spring 37. Here, the inclination angle of the swash plate 5 shown in FIG. 6 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 abut on the cam surface 51b at a second position P2.

As described above, this compressor employs the actuator 13 so as to change the inclination angle of the swash plate 5 by changing the pressure in the control pressure chamber 13b, which has a smaller volume than the swash plate chamber 25. Therefore, in this compressor, the amount of the refrigerant required to change the inclination angle can be reduced as compared to the compressor configured to change the inclination angle by changing the pressure in the swash plate chamber 25. As a result, this compressor is capable of suppressing enlargement of the swash plate chamber 25 and the housing 1.

Furthermore, 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 permit change of the inclination angle while substantially maintaining the position of the top-dead-center corresponding portion T of the swash plate 5. Furthermore, the acting portion 134 of the movable body 13a and the protrusion 5g of the swash plate 5 are located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O. The acting surface 134a of the acting portion 134 comes into point-contact with the protrusion 5g at the operative position F, and in order to decrease the inclination angle of the swash plate 5, the acting surface 134a presses the protrusion 5g. The operative position F moves in accordance with the change of the inclination angle.

Specifically, in this compressor, as shown in FIG. 7A, when the inclination angle is maximum, the operative position F is located at a position near the top-dead-center corresponding portion T of the swash plate 5. Then, as the inclination angle decreases, the position where the swash plate arms 5e and 5f abuts on the cam surface 51b moves toward the second position P2. Thereby, in this compressor, as shown by the white arrow in FIG. 7B, the operative position F moves toward the driving axis O as the inclination angle of the swash plate 5 decreases. In other words, the operative position F when the inclination angle is maximum is closer to the top-dead-center corresponding portion T of the swash plate 5 as compared to the operative position F when the inclination angle is minimum. Here, in this compressor, even when the inclination angle becomes minimum, the operative position F does not move to the opposite side of the top-dead-center corresponding portion T across the driving axis O.

Therefore, in this compressor, as compared with the case where the operative position F has a constant distance from the driving axis O, it is possible to move the movable body 13a without increasing the variable differential pressure at the time of decreasing the inclination angle so as to provide a large thrust force. That is, in this compressor, the load exerted on the movable body 13a at the time of decreasing the inclination angle can be reduced. Consequently, in this compressor, the amount of change in the variable differential pressure when the inclination angle changes is small; therefore, it is easy to change the inclination angle quickly in response to the driving conditions of the vehicle on which the compressor is mounted, and high controllability can be exhibited.

Furthermore, in this compressor, since the operative position F moves as described above in accordance with the change of the inclination angle of the swash plate 5, the stroke of the movable body 13a in the direction of the driving axis O is reduced as compared to the compressor in which the operative position F has a constant distance from the driving axis O, provided that the range of their inclination angle is the same. Therefore, enlargement of the compressor in the axial length is suppressed. These operations will be specifically described below by comparison with a comparative example.

The compressor of the comparative example is configured by partially changing the compressor of Embodiment 1 such that the protrusion 5g and the acting portion 134 are not provided in the swash plate 5 and the movable body 13a. Thereby, in the compressor of the comparative example, the rear end of the first movable cylindrical portion 131 of the movable body 13a abuts on the front surface 5a at a position around the insertion hole 5d. Therefore, in the compressor of the comparative example, the movable body 13a abuts on the swash plate 5 at a position almost on the driving axis O. As a result, in this compressor, when the inclination angle of the swash plate 5 changes, the operative position between the movable body 13a and the swash plate 5 moves in parallel with the direction of the driving axis O. That is, in the compressor of the comparative example, the distance between the operative position and the driving axis O is constant and unchanged even when the inclination angle changes.

Therefore, as the graph in FIG. 8 shows, in the compressor of the comparative example, it is necessary to increase the variable differential pressure when the inclination angle decreases so as to move the movable body 13a by a larger thrust force. In contrast, in the compressor of Embodiment 1, it is possible to move the movable body 13a without increasing the variable differential pressure to thereby provide a large thrust force as described above. Consequently, in the compressor of Embodiment 1, the variable differential pressure required at the time of changing the inclination angle can be made small and almost uniform as a whole.

Furthermore, as shown in FIG. 9, in the compressor of the comparative example, in order to displace the swash plate 5 at the maximum inclination angle in this drawing (see the double-dashed chain line) until it reaches the minimum inclination angle, the movable body 13a needs to move by a distance S2 in the direction of the driving axis O.

In contrast, in the compressor of Embodiment 1, it is sufficient if the movable body 13a moves by a distance S1 in the direction of the driving axis O in order to displace the swash plate 5 at the maximum inclination angle until it reaches the minimum inclination angle. That is, in the compressor of Embodiment 1, the stroke of the movable body 13a in the direction of the driving axis O is shorter than that of the compressor in the comparative example.

Accordingly, the compressor of Embodiment 1 is capable of exhibiting high controllability and excellent mountability.

In particular, in this compressor, since the movable body 13a directly abuts on and presses the swash plate 5 via the acting portion 134 and the protrusion 5g, the direction of the load which acts on the swash plate 5 is less likely to vary. Consequently, in this compressor, the movable body 13a easily presses the swash plate 5 in the direction of the driving axis O, and the movable body 13a is able to stably change the inclination angle of the swash plate 5. Furthermore, in this compressor, because the posture of the movable body 13a is stable, leakage of the pressure from the control pressure chamber 13b is less likely to occur.

Furthermore, in this compressor, in order to change the inclination angle of the swash plate 5, the movable body 13a merely abuts directly on and presses the swash plate 5, and the acting portion 134 is not connected to the protrusion 5g with a connection pin or the like. Consequently, in this compressor, there is no risk that the configuration of a connecting portion changes the posture of the movable body 13a, and thus, the posture of the movable body 13a is less likely to change at the time of changing the inclination angle. Furthermore, in this compressor, it is possible to suppress complication of the configuration and realize reduction in manufacturing cost.

Furthermore, in this compressor, the drive shaft 3 is inserted through the movable body 13a, and the movable body 13a is capable of being fitted to the lug plate 51 by accommodating the movable body 13a in the fixed cylindrical portion 51a. Here, in this compressor, the third movable cylindrical portion 133 of the movable body 13a advances to the position on the inner side of the thrust bearing 55 in the fixed cylindrical portion 51a. Therefore, in this compressor, the space for allowing the movable body 13a to move in the direction of the driving axis O can be suitably provided between the lug plate 51 and the swash plate 5 while making the axial length short. Furthermore, the thrust bearing 55 provided in the compressor can suitably receive the suction reaction force and the compression reaction force which act on the pistons 9.

Furthermore, in this compressor, the control pressure chamber 13b can be suitably formed between the lug plate 51 and the movable body 13a by the fixed cylindrical portion 51a. In this compressor, the hermeticity of the control pressure chamber 13b is suitably ensured by the O-rings 49c and 49d which are provided at the first and the third movable cylindrical portions 131 and 133 respectively.

Furthermore, in this compressor, the acting portion 134 and the protrusion 5g are located eccentrically toward the top-dead-center corresponding portion T from the driving axis O, and the operative position F moves toward the driving axis O as described above as the inclination angle of the swash plate 5 decreases. Therefore, in this compressor, the space for allowing the movable body 13a to move in the direction of the driving axis O is easily provided between the lug plate 51 and the swash plate without disrupting the change of the inclination angle. Therefore, in this compressor, it is possible to increase the diameter of the actuator 13 to quickly move the movable body 13a by a sufficient thrust force. Also in this aspect, this compressor is capable of quickly changing the inclination angle in response to the driving conditions of a vehicle.

Furthermore, in this compressor, the acting portion 134 protrudes from the first movable cylindrical portion 131 toward the top-dead-center corresponding portion T of the swash plate 5 and is integrated with the movable body 13a. Furthermore, the acting surface 134a is formed at the acting portion 134. Thereby, in this compressor, the acting surface 134a can easily abut on the protrusion 5g at the position eccentric toward the top-dead-center corresponding portion T from the driving axis O. Here, since the protrusion 5g is formed to protrude in a substantially hemispherical manner, the acting surface 134a can be suitably brought into point-contact with the protrusion 5g. Consequently, in this compressor, the contact area between the acting surface 134a and the protrusion 5g can be made small, whereby the swash plate 5 can easily change its inclination angle.

Furthermore, the protrusion 5g is integrally formed with the front surface 5a of the swash plate main body 50. Therefore, in this compressor, it is possible to reduce the number of components, facilitate manufacturing, and reduce manufacturing cost.

Furthermore, 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 pressure in the swash plate chamber 25 can be made low as well as the suction chamber 33.

Furthermore, the control mechanism 15 adjusts the pressure in the pressure regulation chamber 31 and thus the pressure in the control pressure chamber 13b by regulating the opening degree of the control valve 15c. In addition, the axial path 3a and the radial path 3b are formed in the drive shaft 3. Consequently, in this compressor, it is possible to suitably change the pressure in the control pressure chamber 13b and suitably move the movable body 13a while downsizing the control mechanism 15.

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

Embodiment 2

As shown in FIG. 10, in a compressor of Embodiment 2, the swash plate 5 has the swash plate main body 50, the swash plate arms 5e and 5f and a contact member 59. The contact member 59 also corresponds to the acted portion in the present invention.

The contact member 59 is formed to be a separate body from the swash plate main body 50. The contact member 59 is attached to the front surface 5a of the swash plate main body 50 at a position between the swash plate arms 5e and 5f, and located eccentrically toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O.

A protrusion 59a that protrudes frontward is formed at the contact member 59. The protrusion 59a is formed into a substantially hemispherical shape. The protrusion 59a comes into point-contact with the acting surface 134a of the acting portion 134 at the operative position F. In this manner, in this compressor, via the acting surface 134a and the protrusion 59a, the acting portion 134 abuts on the contact member 59 at a position eccentric toward the top-dead-center corresponding portion T of the swash plate 5 from the driving axis O. The other components of this compressor are the same as those of the compressor of Embodiment 1, and, where the components are the same, same reference numerals are used and detailed explanation thereof is omitted.

In this compressor, since the swash plate 5 and the contact member 59 are separate bodies, it is possible to improve the flexibility of design with respect to the swash plate main body 50 and the contact member 59. The other operations of this compressor are the same as those of the compressor of Embodiment 1.

Although the present invention has been described above in line with Embodiments 1 and 2, it is needless to say that the present invention is not limited to Embodiments 1 and 2 described above and may be modified and applied as appropriate without departing from the gist of the invention.

For example, the compressors of Embodiments 1 and 2 may be configured such that the operative position F moves toward the driving axis O while the inclination angle of the swash plate 5 decreases to a predetermined angle from the maximum state, and the operative position F does not move while the inclination angle of the swash plate 5 reaches its minimum inclination angle from the predetermined angle.

Furthermore, the protrusion 5g and the protrusion 59a may be formed into a flat-plate shape, and the acting surface 134a of the acting portion 134 may be formed into a curved shape. This enables the protrusion 5g and the protrusion 59a to come into line-contact with the acting portion 134 at the operative position F.

Furthermore, the control mechanism 15 may be configured such that the control valve 15c is provided at the high pressure passage 15b and the orifice 15d is provided at 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 regulated by the control valve 15c. Therefore, due to the high pressure in the discharge chamber 35, the pressure in the control pressure chamber 13b can be increased quickly and the compression capacity can be decreased quickly. Furthermore, instead of the control valve 15c, a three-way valve that is connected to the low pressure passage 15a and the high pressure passage 15b may be provided so that the flow rate of the refrigerant flowing through the low pressure passage 15a and the high pressure passage 15b is adjusted by regulating an opening degree of the three-way valve.

INDUSTRIAL APPLICABILITY

The present invention is applicable to air-conditioning apparatus and the like.

REFERENCE SIGNS LIST

• • 1 HOUSING
  • 3 DRIVE SHAFT
  • 3a AXIAL PATH (CONTROL PASSAGE)
  • 3b RADIAL PATH (CONTROL PASSAGE)
  • 5 SWASH PLATE
  • 5d INSERTION HOLE
  • 5e, 5f SWASH PLATE ARM (TRANSMISSION MEMBER)
  • 5g PROTRUSION (ACTED PORTION)
  • 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
  • 31 PRESSURE REGULATION CHAMBER
  • 33 SUCTION CHAMBER
  • 35 DISCHARGE CHAMBER
  • 21a CYLINDER BORE
  • 49a, 49b O-RING (THIRD SEAL MEMBER)
  • 49c O-RING (FIRST SEAL MEMBER)
  • 49d O-RING (SECOND SEAL MEMBER)
  • 51 LUG PLATE (LUG MEMBER)
  • 51a FIXED CYLINDRICAL PORTION
  • 55 THRUST BEARING
  • 59 CONTACT MEMBER (ACTED PORTION)
  • 59a PROTRUSION
  • 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 ACTING PORTION
  • F OPERATIVE POSITION
  • O DRIVING AXIS
  • T TOP-DEAD-CENTER CORRESPONDING PORTION

Claims

1. A variable displacement swash plate type compressor comprising: a housing in which a swash plate chamber and a cylinder bore are formed; a drive shaft that is rotatably supported by the housing; a swash plate that is rotatable in the swash plate chamber by rotation of the drive shaft; a link mechanism that is provided between the drive shaft and the swash plate and permits change of an inclination angle of the swash plate with respect to a direction perpendicular to a driving axis of the drive shaft; a piston that is reciprocally accommodated in the cylinder bore; a conversion mechanism that reciprocates the piston in the cylinder bore at a stroke corresponding to the inclination angle by rotation of the swash plate; an actuator capable of changing the inclination angle; and a control mechanism that controls the actuator,

wherein the link mechanism has a lug member that is fixed to the drive shaft in the swash plate chamber and a transmission member that transmits rotation of the lug member to the swash plate,

the actuator has the lug member, a movable body that is rotatable integrally with the swash plate and is capable of changing the inclination angle by moving in the direction of the driving axis, and a control pressure chamber that is defined by the lug member and the movable body and moves the movable body by changing its internal pressure by the control mechanism,

an acting portion that is capable of pressing the swash plate by the pressure in the control pressure chamber is formed at the movable body,

an acted portion that abuts on and is pressed by the acting portion is formed at the swash plate,

the acting portion abuts on the acted portion at an operative position,

the operative position moves in accordance with the change of the inclination angle,

a top-dead-center corresponding portion for positioning the piston at its top dead center is defined in the swash plate, and

the operative position when the inclination angle is maximum is closer to the top-dead-center corresponding portion as compared to the operative position when the inclination angle is minimum.

2. The variable displacement swash plate type compressor according to claim 1,

wherein the drive shaft is inserted through the movable body, and the movable body is capable of being fitted to the lug member.

3. The variable displacement swash plate type compressor according to claim 2,

wherein the movable body has a movable cylindrical portion that is formed into a cylindrical shape and coaxial with the driving axis, and

the lug member has a fixed cylindrical portion that is formed into a cylindrical shape and coaxial with the driving axis at an outer circumferential side of the movable cylindrical portion to thereby provide the control pressure chamber in the movable cylindrical portion.

4. The variable displacement swash plate type compressor according to claim 3,

wherein a first seal member that seals the control pressure chamber is provided between the movable cylindrical portion and the drive shaft, and

a second seal member that seals the control pressure chamber is provided between the movable cylindrical portion and the fixed cylindrical portion.

5. The variable displacement swash plate type compressor according to claim 3,

wherein a thrust bearing that receives a thrust force which acts on the piston is provided between the housing and the lug member, and

the movable cylindrical portion is smaller in diameter than the thrust bearing and capable of advancing to an inner side of the thrust bearing.

6. The variable displacement swash plate type compressor according to claim 1,

wherein the acting portion comes into point-contact or line-contact with the acted portion at the operative position.

7. The variable displacement swash plate type compressor according to claim 6,

wherein the acting portion and the acted portion are located eccentrically toward the top-dead-center corresponding portion from the driving axis, and

the operative position moves toward the driving axis as the inclination angle decreases.

8. The variable displacement swash plate type compressor according to claim 7,

wherein the acting portion has an acting surface that extends in the direction perpendicular to the driving axis, and

the acted portion has a protrusion that protrudes from the swash plate and abuts on the acting surface.

9. The variable displacement swash plate type compressor according to claim 7,

wherein the movable body has a movable cylindrical portion that is formed into a cylindrical shape and coaxial with the driving axis, and

the acting portion protrudes from the movable cylindrical portion toward the top-dead-center corresponding portion.

10. The variable displacement swash plate type compressor according to claim 1,

wherein the swash plate has a swash plate main body that is formed with an insertion hole, through which the drive shaft is inserted, and the acted portion that is integrally formed with the swash plate main body.

11. The variable displacement swash plate type compressor according to claim 1,

wherein the swash plate has a swash plate main body that is formed with an insertion hole, through which the drive shaft is inserted, and the acted portion that is fixed to the swash plate main body.

12. The variable displacement swash plate type compressor according to claim 1,

wherein a suction chamber and a discharge chamber are formed in the housing, and

the suction chamber and the swash plate chamber communicate with each other.

13. The variable displacement swash plate type compressor according to claim 12,

wherein the control mechanism has a control passage that provides communication between the control pressure chamber and the suction chamber and/or the discharge chamber and a control valve that is capable of regulating an opening degree of the control passage, and

at least a part of the control passage is formed in the drive shaft.

14. The variable displacement swash plate type compressor according to claim 13,

wherein a pressure regulation chamber that communicates with the control pressure chamber through the control passage and allows a pressure therein to be changed by the control valve is formed between the housing and one end of the drive shaft, and

a third seal member that seals the pressure regulation chamber is provided between the housing and the drive shaft.