VARIABLE DISPLACEMENT SWASH PLATE TYPE COMPRESSOR

TECHNICAL FIELD

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

BACKGROUND ART

A conventional variable displacement swash plate type compressor (hereinafter referred to as compressor) is disclosed in Japanese Patent Laid-Open No. 5-172052. In the compressor, a housing is formed by a front housing, a cylinder block, and a rear housing. A suction chamber and a discharge chamber are formed in the front housing and the rear housing, respectively. Further, a pressure regulation chamber is formed in the rear housing.

A swash plate chamber and a plurality of cylinder bores are formed in the cylinder block. Each of the cylinder bores is configured by a first cylinder bore formed on the rear side of the cylinder block, and a second cylinder bore formed on the front side of the cylinder block. Each of the first cylinder bores and the second cylinder bores has the same diameter.

A drive shaft is inserted in the housing and is supported rotatably in the cylinder block. A swash plate, which can be rotated by rotation of the drive shaft, is provided in the swash plate chamber. A link mechanism, which allows the inclination angle of the swash plate to be changed, is provided between the drive shaft and the swash plate. Here, the inclination angle means an angle formed by the swash plate with respect to the direction perpendicular to the rotational axis of the drive shaft.

Further, a piston is accommodated so as to be able to reciprocate in each of the cylinder bores. Specifically, each of the pistons includes a first head section reciprocating in each of the first cylinder bores, and a second head section reciprocating in each of the second cylinder bores. Since each of the first cylinder bores and the second cylinder bores of the cylinder bores has the same diameter, each of the first head sections and the second head sections of the pistons also has the same diameter. Thereby, in this compressor, first compression chambers are formed by each of the first cylinder bores and each of the first head sections, and second compression chambers are formed by each of the second cylinder bores and each of the second head sections. A conversion mechanism is configured such that, by rotation of the swash plate, each of the pistons is reciprocated in each of the cylinder bores at a stroke corresponding to the inclination angle of the swash plate. Further, the inclination angle can be changed by an actuator, and a control mechanism is configured to control the actuator.

In the swash plate chamber, the actuator is arranged on the side of the first cylinder bores with respect to the swash plate. The actuator includes an actuator main body and a control pressure chamber. The actuator main body includes a non-rotating movable body, a movable body, and a thrust bearing. The non-rotating movable body is arranged in the control pressure chamber so as not to be rotatable integrally with the drive shaft and covers a rear end portion of the drive shaft. The inner peripheral surface of the non-rotating movable body is configured to rotatably slidably support the rear end portion of the drive shaft, and is configured to be able to move in the direction of the rotational axis. Further, the outer peripheral surface of the non-rotating movable body is configured to slide in the direction of the rotational axis in the control pressure chamber, and is configured not to slide around the rotational axis. The movable body is connected to the swash plate so as to be movable in the direction of the rotational axis. The thrust bearing is provided between the non-rotating movable body and the movable body.

The control pressure chamber is provided on the rear side of the cylinder block, that is, on the side of the first cylinder bores in the cylinder block. A pressing spring, which urges the non-rotating movable body toward the front side, is provided in the control pressure chamber. Further, a pressure control valve, which changes the pressure in the control pressure chamber so as to enable the non-rotating movable body and the movable body to move in the direction of the rotational axis, is provided between the pressure regulation chamber and a discharge chamber.

The link mechanism is arranged so that, according to a change of the inclination angle of the swash plate, the top dead center position of the second head section of each of the pistons is moved more than the top dead center position of the first head section of each of the pistons. The link mechanism includes a movable body and a lug arm fixed to the drive shaft. A long hole, which extends in the direction perpendicular to the rotational axis and in the direction approaching the rotational axis from the outer peripheral side, is formed at the rear end portion of the lug arm. The swash plate is supported pivotably around a first pivotal axis by a pin inserted into the long hole on the front side of the swash plate. Further, a long hole, which extends in the direction perpendicular to the rotational axis and in the direction approaching the rotational axis from the outer peripheral side, is also formed at the front end portion of the movable body. The swash plate is supported pivotably around a second pivotal axis in parallel with the first pivotal axis by a pin inserted into the long hole at the rear end of the swash plate.

In this compressor, when the pressure regulation valve is controlled to be opened so that the discharge chamber communicates with the pressure regulation chamber, the pressure in the control pressure chamber is made higher than the pressure in the swash plate chamber. Thereby, the non-rotating movable body and the movable body are moved toward the front side. By this movement, the inclination angle of the swash plate is increased, so that the strokes of the pistons are increased. Thereby, the compression capacity per one revolution of the compressor is increased. When the pressure regulation valve is controlled to be closed so that the discharge chamber does not communicate with the pressure regulation chamber, the pressure in the control pressure chamber is reduced to almost the same pressure as that in the swash plate chamber. Thereby, the non-rotating movable body and the movable body are moved toward the rear side. By this movement, the inclination angle of the swash plate is reduced, so that the strokes of the pistons are reduced. As a result, the compression capacity per one revolution of the compressor is reduced.

Here, in each of the pistons of this compressor, the top dead center position of the second head section of the piston is moved more largely than the top dead center position of the first head section of the piston. Therefore, when the inclination angle of the swash plate is made close to 0 degree, a slight amount of compression work is performed only in the first compression chambers, and no compression work is performed in the second compression chambers.

Meanwhile, in a compressor, high controllability is required in order that the compression capacity can be rapidly increased or reduced according to an operation condition of a vehicle, or the like, to which the compressor is mounted. To cope with this requirement, also in the above-described conventional compressor, it is considered to increase the size of the control pressure chamber of the actuator. Therefore, it is considered that, in the compressor, the inclination angle of the swash plate is rapidly changed by sliding the non-rotating movable body and the movable body in the direction of the rotational axis with a large thrust force.

However, in this compressor, the control pressure chamber is formed in the cylinder block. Therefore, when the size of the control pressure chamber is increased, the size of the cylinder block is increased, so that the entire size of the compressor is increased. As a result, the mounting performance of the compressor to a vehicle, or the like, is lowered.

In this compressor, when the diameter of the cylinder bores is reduced to increase the size of the control pressure chamber of the actuator, desired compression capacity cannot be secured.

The present invention has been made in view of the above described circumstances. An object of the present invention is to provide a variable displacement swash plate type compressor which has high controllability and which can exhibit high mounting performance and secure sufficient compression capacity.

SUMMARY OF THE INVENTION

A variable displacement swash plate type compressor according to the present invention comprises:

a housing in which a suction chamber, a discharge chamber, a swash plate chamber, and a cylinder bore are formed; a drive shaft which is rotatably supported by the housing; a swash plate capable of rotating in the swash plate chamber by rotation of the drive shaft; a link mechanism which is provided between the drive shaft and the swash plate to allow a change of the inclination angle of the swash plate with respect to the direction perpendicular to the rotational axis of the drive shaft; a piston which is accommodated in the cylinder bore so as to be able to reciprocate in the cylinder bore; a conversion mechanism which reciprocates the piston in the cylinder bore by rotation of the swash plate and at a stroke corresponding to the inclination angle; an actuator capable of changing the inclination angle; and a control mechanism which controls the actuator, wherein

the cylinder bore is configured by a first cylinder bore provided on one surface side of the swash plate, and a second cylinder bore provided on the other surface side of the swash plate,

the piston includes a first head section being reciprocated in the first cylinder bore and partitioning a first compression chamber in the first cylinder bore, and a second head section being reciprocated in the second cylinder bore and partitioning a second compression chamber in the second cylinder bore,

the link mechanism is arranged to allow the top dead center position of the first head section to be moved more than the top dead center position of the second head section according to a change of the inclination angle,

the actuator is provided to be rotatable integrally with the drive shaft and is arranged on the side of the first cylinder bore with respect to the swash plate in the swash plate chamber,

the actuator includes an actuator main body connected to the swash plate and configured to be movable in the rotational axis direction, and a control pressure chamber configured to move the actuator main body at the time when the internal pressure of the control pressure chamber is changed by the control mechanism, and

the first cylinder bore is formed to have a diameter smaller than the diameter of the second cylinder bore.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view at the time of maximum capacity in a compressor of Embodiment 1.

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

FIG. 3 is an enlarged sectional view of a main part of a first cylinder bore and a second cylinder bore according to the compressor of Embodiment 1.

FIG. 4 is a cross-sectional view at the time of minimum capacity in the compressor of Embodiment 1.

FIG. 5 is a side view showing a piston according to the compressor of Embodiment 1.

FIG. 6 is an enlarged sectional view of a main part of a first cylinder bore and a second cylinder bore according to a compressor of Embodiment 2.

FIG. 7 is a side view showing a piston according to the compressor of Embodiment 2.

FIG. 8 is a side view showing a piston according to a compressor of Embodiment 3.

FIG. 9 is a side view showing a piston according to a compressor of Embodiment 4.

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS

In the following, Embodiments 1 to 4 exemplifying the present invention will be described with reference to the accompanying drawings. The compressor of each of Embodiments 1 to 4 is a variable displacement swash plate type compressor. Each of the compressors is mounted to a vehicle so as to configure a refrigeration circuit of a vehicle air conditioner.

Embodiment 1

As shown in FIG. 1, a compressor of Embodiment 1 comprises 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 shown in FIG. 2.

As shown in FIG. 1, the housing 1 includes a rear housing 17, a front housing 19, a first cylinder block 21, and a second cylinder block 23.

The rear housing 17 is arranged on the rear side of the compressor. The above-described control mechanism 15 is provided in the rear housing 17. Further, a pressure regulation chamber 25, a first suction chamber 27a, and a first discharge chamber 29a are formed in the rear housing 17. The pressure regulation chamber 25 is located at a center portion of the rear housing 17. The first discharge chamber 29a is located on the outer peripheral side of the rear housing 17. Further, the first suction chamber 27a is formed between the pressure regulation chamber 25 and the first discharge chamber 29a in the rear housing 17. That is, the first suction chamber 27a is formed at a position on the outer peripheral side from the pressure regulation chamber 25 and on the inner peripheral side from the first discharge chamber 29a.

A boss 19a projected toward the front side is formed at the front housing 19. In the boss 19a, a shaft seal device 31 is provided between the inner surface of the boss 19a and the drive shaft 3, more specifically, between the inner surface of the boss 19a and a second support member 43 described below. Further, a second suction chamber 27b and a second discharge chamber 29b are formed in the front housing 19. The second suction chamber 27b is located on the inner peripheral side of the front housing 19, and the second discharge chamber 29b is located on the outer peripheral side of the front housing 19. Further, the second discharge chamber 29b and the first discharge chamber 29a are connected to each other by a discharge passage (not shown). A outlet port (not shown) is formed in the discharge passage so as to communicate with the outside of the compressor.

The first cylinder block 21 and the second cylinder block 23 are located between the rear housing 17 and the front housing 19, so as to be adjacent to each other. Further, the first cylinder block 21 is located on the rear side of the compressor, so as to be adjacent to the rear housing 17. The second cylinder block 23 is located on the front side of the compressor, so as to be adjacent to the front housing 19. Further, a swash plate chamber 33 is formed by the first cylinder block 21 and the second cylinder block 23. The swash plate chamber 33 is located approximately at the front-rear direction center of the housing 1.

In the first cylinder block 21, a plurality of first cylinder bores 21a are formed in parallel with each other at equal angular intervals in the circumferential direction. Further, a first shaft hole 21b, into which the drive shaft 3 is inserted, is formed in the first cylinder block 21. The first shaft hole 21b is made to communicate with the pressure regulation chamber 25. A first slide bearing 24a is provided in the first shaft hole 21b.

Further, a first storage chamber 21c, which is made to communicate with the first shaft hole 21b so as to be coaxial with the first shaft hole 21b, is formed to be recessed in the first cylinder block 21. The periphery of the first storage chamber 21c is surrounded by the wall surface as a part of the first cylinder block 21, so that the first storage chamber 21c is partitioned from the first cylinder bores 21a. The inside of the first storage chamber 21c is made to communicate with the swash plate chamber 33. Further, the first storage chamber 21c is formed to have a shape whose diameter is reduced stepwise toward the rear end. A first thrust bearing 35a is provided at the rear end of the first storage chamber 21c. Further, a first suction passage 37a, which makes the swash plate chamber 33 communicate with the first suction chamber 27a, is formed in the first cylinder block 21.

A plurality of second cylinder bores 23a is formed in the second cylinder block 23. Further, a second shaft hole 23b, into which the drive shaft 3 is inserted, is formed in the second cylinder block 23. A second slide bearing 24b is formed in the second shaft hole 23b.

Further, a second storage chamber 23c, which is made to communicate with the second shaft hole 23b so as to be coaxial with the second shaft hole 23b, is formed to be recessed in the second cylinder block 23. The periphery of the second storage chamber 23c is surrounded by the wall surface as a part of the second cylinder block 23, so that the second storage chamber 23c is partitioned from each of the second cylinder bores 23a. The second storage chamber 23c is also made to communicate with the swash plate chamber 33. The second storage chamber 23c is formed to have a shape whose diameter is reduced stepwise toward the front end. A second thrust bearing 35b is provided at the front end of the second storage chamber 23c. Further, a second suction passage 37b, through which the swash plate chamber 33 is made to communicate with the second suction chamber 27b, is formed in the second cylinder block 23.

As shown in FIG. 3, in this compressor, the diameter D1 of the first cylinder bores 21a is smaller than the diameter D2 of the second cylinder bores 23a. That is, in this compressor, each of the first cylinder bores 21a is formed to have a diameter smaller than the diameter of each of the second cylinder bores 23a. Thereby, as shown in FIG. 1, in this compressor, the first storage chamber 21c is configured to be larger than the second storage chamber 23c.

Further, as shown in FIG. 3, in this compressor, each of the first cylinder bores 21a is formed such that a first center line O1, which passes through the center of the first cylinder bore 21a, is located on the extension line of a second center line O2, which passes through the center of the corresponding second cylinder bore 23a. That is, in this compressor, each of the first cylinder bores 21a and each of the corresponding second cylinder bores 23a are formed to be coaxial with each other.

As shown in FIG. 1, the swash plate chamber 33 is connected to an evaporator (not shown) via an inlet port 330 formed in the first cylinder block 21.

A first valve plate 39 is provided between the rear housing 17 and the first cylinder block 21. Suction ports 39a and discharge ports 39b, the numbers of which are equal to the first cylinder bores 21a, are formed in the first valve plate 39. Further, suction reed valves 39c capable of opening and closing the respective suction ports 39a are provided in the first valve plate 39. Each of the first cylinder bores 21a is made to communicate with the first suction chamber 27a through the corresponding suction port 39a and the corresponding suction reed valve 39c. Retainer grooves 39d, which regulate the lift amount of the suction reed valves 39c, are formed in the respective first cylinder bores 21a. Further, discharge reed valves 39e capable of opening and closing the respective discharge ports 39b are provided in the first valve plate 39. Each of the first cylinder bores 21a is made to communicate with the first discharge chamber 29a through the corresponding discharge port 39b and the corresponding discharge reed valve 39e. Further, a retainer plate 39f, which regulates the lift amount of the discharge reed valves 39e, is provided in the first valve plate 39. Further, a communication hole 39g, through which the first suction chamber 27a is made communicate with the first suction passage 37a, is formed in the first valve plate 39.

A second valve plate 41 is provided between the front housing 19 and the second cylinder block 23. Suction ports 41a and discharge ports 41b, the numbers of which are equal to the second cylinder bores 23a, are formed in the second valve plate 41. Further, suction reed valves 41c capable of opening and closing the respective suction ports 41a are provided in the second valve plate 41. Each of the second cylinder bores 23a is made to communicate with the second suction chamber 27b through the corresponding suction port 41a and the corresponding suction reed valve 41c. Retainer grooves 41d, which regulate the lift amount of the suction reed valves 41c, are formed in the respective second cylinder bores 23a. Further, discharge reed valves 41e capable of opening and closing the respective discharge ports 41b are provided in the second valve plate 41. Each of the second cylinder bores 23a is made to communicate with the second discharge chamber 29b through the corresponding discharge port 41b and the corresponding discharge reed valve 41e. Further, a retainer plate 41f, which regulates the lift amount of the discharge reed valves 41e, is provided at the second valve plate 41. Further, communication holes 41g, through which the second suction chamber 27b are made to communicate with the second suction passage 37b, are formed in the second valve plate 41.

The first and second suction chambers 27a and 27b are made communicate with the swash plate chamber 33 by the first and second suction passages 37a and 37b and the communication holes 39g and 41g. For this reason, the pressure in the first and second suction chambers 27a and 27b is made substantially equal to the pressure in the swash plate chamber 33. Further, refrigerating gas, having passed through the evaporator, flows into the swash plate chamber 33 through the inlet port 330, and hence the pressure in the swash plate chamber 33 and in each of the first and second suction chambers 27a and 27b is lower than the pressure in the first and second discharge chambers 29a and 29b.

The swash plate 5 and the actuator 13 are attached to the drive shaft 3. Further, a first support member 42 is press-fitted to the rear end side of the drive shaft 3. A flange 42a is formed at the first support member 42. The drive shaft 3 is made to extend from the side of the boss 19a to the rear side, so as to be inserted into the first and second slide bearings 24a and 24b. Thereby, the drive shaft 3 is supported rotatably about the rotational axis O3. Further, the drive shaft 3 is inserted into the housing 1, and thereby the swash plate 5, the actuator 13, and the flange 42a are arranged in the swash plate chamber 33, respectively.

The second support member 43 is press-fitted to the front end side of the drive shaft 3. In the second support member 43, a flange 43a, which is brought into contact with the second thrust bearing 35b, is formed, and amounting section (not shown), in which a second pin 47b described below is inserted, is formed. Further, the front end of a first return spring 44a is fixed to the second support member 43. The first return spring 44a is extended in the direction of the rotational axis O3 from the side of the support member 43 to the side of the swash plate chamber 33.

Further, a shaft passage 3b extending from a rear end toward a front end of the drive shaft 3 in the direction of the rotational axis O3, and a radial passage 3c extending from the front end of the shaft passage 3b in the radial direction of the drive shaft 3 so as to be open in the outer circumference surface of the drive shaft 3 are formed in the drive shaft 3. The rear end of the shaft passage 3b is open to the pressure regulation chamber 25. The radial passage 3c is open to a control pressure chamber 13c described below.

A screw section 3d is formed at the tip end of the drive shaft 3. The drive shaft 3 is connected to a pulley or electromagnetic clutch (not shown) via the screw section 3d. A belt (not shown), which is driven by an engine of a vehicle, is wound around the pulley or the electromagnetic clutch.

The swash plate 5 is formed in an annular flat plate shape and has a rear surface 5a and a front surface 5b. The rear surface 5a faces the side of the first cylinder bores 21a in the swash plate chamber 33, that is, the rear side of the compressor. The side of the rear surface 5a of the swash plate 5 corresponds to the one end side in the present invention. The front surface 5b faces the side of the second cylinder bores 23a in the swash plate chamber 33, that is, the front side of the compressor. The side of the front surface 5b of the swash plate 5 corresponds to the other end side in the present invention.

The swash plate 5 is fixed to a ring plate 45. The ring plate 45 is formed in an annular flat plate shape, and an insertion hole 45a is formed in the center portion of the ring plate 45. The drive shaft 3 is inserted into the insertion hole 45a in the swash plate chamber 33 so that the swash plate 5 is attached to the drive shaft 3.

The link mechanism 7 has a lug arm 49. The lug arm 49 is arranged on the front side with respect to the swash plate 5 in the swash plate chamber 33 and is located between the swash plate 5 and the second support member 43. The lug arm 49 is formed in a substantially L-shape extending from the front end side toward the rear end side. As shown in FIG. 4, the lug arm 49 is configured to be in contact with the flange 43a of the second support member 43 at the time when the inclination angle of the swash plate 5 with respect to the direction perpendicular to the rotational axis O3 is minimized. For this reason, in the compressor, the inclination angle of the swash plate 5 can be maintained at a minimum value by the lug arm 49. Further, a weight section 49a is formed on the rear end side of the lug arm 49. The weight section 49a extends over about half the circumference of the actuator 13 in the circumferential direction of the actuator 13. It should be noted that the shape of the weight section 49a can be suitably designed.

The rear end side of the lug arm 49 is connected to the one end side of the ring plate 45 by a first pin 47a. Thereby, the rear end side of the lug arm 49 is supported by using the shaft center of the first pin 47a as a first pivotal axis M1, and supported pivotably around the first pivotal axis M1 with respect to the one end side of the ring plate 45, that is, the swash plate 5. The first pivotal axis M1 extends in the direction perpendicular to the rotational axis O3 of the drive shaft 3.

The front end side of the lug arm 49 is connected to the second support member 43 by the second pin 47b. Thereby, the front end side of the lug arm 49 is supported by using the shaft center of the second pin 47b as a second pivotal axis M2, and supported pivotably around the second pivotal axis M2 with respect to the second support member 43, that is, the drive shaft 3. The second pivotal axis M2 extends in parallel with the first pivotal axis M1. The lug arm 49 and the first and second pins 47a and 47b correspond to the link mechanism 7 in the present invention.

The weight section 49a is provided to extend to the rear end side of the lug arm 49, that is, to extend to the side opposite to the second pivotal axis M2 with respect to the first pivotal axis M1. Therefore, in the state in which the lug arm 49 is supported at the ring plate 45 by the first pin 47a, the weight section 49a is made to pass through a groove section 45b of the ring plate 45, so as to be located on the side of the rear surface of the ring plate 45, that is, on the side of the rear surface 5a of the swash plate 5. Thereby, the centrifugal force, generated at the time when the swash plate 5 is rotated around the rotational axis O3, is also made to act on the weight section 49a on the side of the rear surface 5a of the swash plate 5.

In this compressor, the swash plate 5 and the drive shaft 3 are connected to the link mechanism 7, and thereby the swash plate 5 can be rotated together with the drive shaft 3. Here, in this compressor, the arrangement position of the link mechanism 7 is determined so that, when the inclination angle of the swash plate 5 is minimized, the swash plate 5 connected to the link mechanism 7 is located at a position close to the side of the second cylinder bores 23a in the swash plate chamber 33. Further, the swash plate 5 is configured so that the inclination angle thereof can be changed at the time when the both ends of the lug arm 49 are pivoted respectively around the first pivotal axis M1 and the second pivotal axis M2.

Each of the pistons 9 has a piston main body 9a, a first head section 9b formed at the rear end of the piston main body 9a, and a second head section 9c formed at the front end of the piston main body 9a. As shown in FIG. 5, the first head section 9b is formed in a substantially columnar shape and includes a first front end surface 900a, a first rear end surface 900b, and a first cylindrical surface 900c located between the first front end surface 900a and the first rear end surface 900b. Further, the second head section 9c is also formed in a substantially columnar shape and includes a second front end surface 901a, a second rear end surface 901b, and a second cylindrical surface 901c located between the second front end surface 901a and the second rear end surface 901b. The first head section 9b is connected to the piston main body 9a at the first front end surface 900a. The second head section 9c is connected to the piston main body 9a at the second rear end surface 901b. Here, in each of the pistons 9, a center line O4 passing through the center of the first head section 9b is located on the extension line of a center line O5 passing through the center of the second head section 9c. That is, each of the pistons 9 is formed such that the first head section 9b and the second head section 9c are coaxial with the piston main body 9a.

As shown in FIG. 1, each of the first head sections 9b is accommodated in each of the first cylinder bores 21a so as to be able to reciprocate in each of the first cylinder bores 21a. The inside of the first cylinder bores 21a is partitioned by the respective first head sections 9b, so that a first compression chamber 21d is formed in each of the first cylinder bores 21a. Each of the second head sections 9c is accommodated in each of the second cylinder bores 23a so as to be able to reciprocate in each of the second cylinder bores 23a. The inside of the second cylinder bores 23a is partitioned by the respective second head sections 9c, so that a second compression chamber 23d is formed in each of the second cylinder bores 23a.

As shown in FIG. 5, in each of the pistons, the piston main body 9a is configured by an engagement section 91 provided to be recessed at the longitudinal center of the piston main body 9a, a first neck section 92 extending from the engagement section 91 toward the side of the first head section 9b, and a second neck section 93 extending from the engagement section 91 toward the side of the second head section 9c. The first neck section 92 and the second neck section 93 are formed so that the length α1 of the first neck section 92 in the axial direction of the piston 9 (hereinafter referred to as the length α1 of the first neck section 92) is equal to the length α2 of the second neck section 93 in the axial direction of the piston 9 (hereinafter referred to as the length α2 of the second neck section 93).

Further, as described above, each of the first cylinder bores 21a is formed to be smaller in diameter than each of the second cylinder bores 23a, and hence the diameter of the first head section 9b is smaller than the diameter of the second head section 9c. That is, the first head section 9b is formed to be smaller in diameter than the second head section 9c. Here, the first head section 9b and the second head section 9c are formed to have the same length in the front and rear direction. Thereby, the length β1 of the first cylindrical surface 900c in the axial direction of the piston 9 (hereinafter referred to as the length β1 of the first cylindrical surface 900c) is equal to the length β2 of the second cylindrical surface 901c in the axial direction of the piston 9 (hereinafter referred to as the length β2 of the second cylindrical surface 901c). For this reason, in each of the pistons 9, the sum of the length α1 of the first neck section 92 and the length β1 of the first cylindrical surface 900c is equal to the sum of the length α2 of the second neck section 93 and the length β2 of the second cylindrical surface 901c. In this way, in each of the pistons 9, the distance L1 from the center of the engagement section 91 to the tip end of the first head section 9b is equal to the distance L2 from the center of the engagement section 91 to the tip end of the second head section 9c.

As shown in FIG. 1, the hemispherical shoes 11a and 11b are provided in each of the engagement sections 91. The rotation of the swash plate 5 is converted to the reciprocating movement of the pistons 9 by the shoes 11a and 11b. The shoes 11a and 11b correspond to the conversion mechanism in the present invention. In this way, each of the first and second head sections 9b and 9c can reciprocate in the inside of each of the first and second cylinder bores 21a and 23a at a stroke corresponding to the inclination angle of the swash plate 5.

Here, as described above, the swash plate 5 is located on the side of the second cylinder bores 23a in the swash plate chamber 33. Thereby, in this compressor, as shown in FIG. 1, when the inclination angle of the swash plate 5 is maximized so as to maximize the strokes of the pistons 9, the top dead center position of the first head section 9b is set at a position closest to the first valve plate 39, and the top dead center position of the second head section 9c is set at a position closest to the second valve plate 41. As shown in FIG. 4, as the inclination angle of the swash plate 5 is reduced to reduce the strokes of the pistons 9, the top dead center position of the first head section 9b is gradually displaced away from the first valve plate 39. The top dead center position of the second head section 9c is not almost changed from the position at the time of the maximum strokes of the pistons 9, and is maintained at the position close to the second valve plate 41.

As shown in FIG. 1, the actuator 13 is arranged in the swash plate chamber 33 and is located on the side of the first cylinder bores 21a with respect to the swash plate 5. The actuator 13 is configured such that a part thereof can enter the first storage chamber 21c so as to be accommodated in the first storage chamber 21c.

The actuator 13 includes a movable body 13a, a fixed body 13b, and the control pressure chamber 13c. The actuator main body in the present invention is formed by the movable body 13a and the fixed body 13b. The control pressure chamber 13c is formed between the movable body 13a and the fixed body 13b.

The movable body 13a includes a main body section 130 and a peripheral wall 131. The main body section 130 is located on the rear side of the movable body 13a and is extended in the radial direction away from the rotational axis O3. The peripheral wall 131 is made continuous with the outer peripheral edge of the main body section 130 and is extended from the rear side toward the front side. Further, a connection section 132 is formed at the front end of the peripheral wall 131. The movable body 13a has a bottomed cylindrical shape formed by the main body sections 130, the peripheral wall 131, and the connection section 132.

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

The drive shaft 3 is inserted into the movable body 13a and the fixed body 13b. Thereby, the movable body 13a is arranged in a state of being accommodated in the first storage chamber 21c and facing the link mechanism 7 via the swash plate 5. The fixed body 13b is arranged in the movable body 13a and on the rear side of the swash plate 5, so that the periphery of the fixed body 13b is surrounded by the peripheral wall 131. Thereby, the control pressure chamber 13c is formed between the movable body 13a and the fixed body 13b. The control pressure chamber 13c is partitioned from the swash plate chamber 33 by the main body section 130 and the peripheral wall 131 of the movable body 13a, and the fixed body 13b. As described above, the radial passage 3c is opened in the control pressure chamber 13c, and the control pressure chamber 13c is made to communicate with the pressure regulation chamber 25 through the radial passage 3c and the shaft passage 3b.

The other end side of the ring plate 45 is connected to the connection section 132 of the movable body 13a by a third pin 47c. Thereby, the other end side of the ring plate 45, that is, the swash plate 5 is supported by the movable body 13a so as to be pivotable around an action axis M3 by using the shaft center of the third pin 47c as the action axis M3. The action axis M3 extends in parallel with the first and second pivotal axes M1 and M2. In this way, the movable body 13a is in a state of being connected to the swash plate 5. Further, it is configured such that the movable body 13a is brought into contact with the flange 42a of the first support member 42 at the time when the inclination angle of the swash plate 5 is maximized.

Further, the drive shaft 3 is inserted into the movable body 13a so that the movable body 13a can be rotated together with the drive shaft 3 and can be moved in the direction of the rotational axis O3 of the drive shaft 3 in the swash plate chamber 33. The fixed body 13b is fixed to the drive shaft 3 in a state in which the drive shaft 3 is inserted into the fixed body 13b. Therefore, the fixed body 13b can be only rotated together with the drive shaft 3, and it is impossible that the fixed body 13b is moved similarly to the movable body 13a. Thereby, when the movable body 13a is moved in the direction of the rotational axis O3, the movable body 13a is moved relative to the fixed body 13b.

As shown in FIG. 2, the control mechanism 15 includes a release passage 15a, a supply passage 15b, a control valve 15c, and an orifice 15d.

The release passage 15a is connected to the pressure regulation chamber 25 and the first suction chamber 27a. Thereby, the control pressure chamber 13c, the pressure regulation chamber 25, and the first suction chamber 27a are made to communicate with each other by the release passage 15a, the shaft passage 3b, and the radial passage 3c. The supply passage 15b is connected to the pressure regulation chamber 25 and the first discharge chamber 29a. The control pressure chamber 13c, the pressure regulation chamber 25, and the first discharge chamber 29a are made to communicate with each other by the supply passage 15b, the shaft passage 3b, and the radial passage 3c. Further, the orifice 15d is provided in the supply passage 15b, so as to regulate the flow rate of refrigerating gas flowing through the supply passage 15b.

The control valve 15c is provided at the release passage 15a. The control valve 15c is configured to adjust the opening degree of the release passage 15a on the basis of the pressure in the first suction chamber 27a. Thereby, the control valve 15c is configured to be able to adjust the flow rate of refrigerating gas flowing through the release passage 15a.

In this compressor, a pipe connected to an evaporator is connected to the inlet port 330 shown in FIG. 1, and a pipe connected to a condenser is connected to the outlet port. The condenser is connected to the evaporator via a pipe and an expansion valve. The refrigeration circuit of a vehicle air conditioner is configured by the compressor, the evaporator, the expansion valve, the condenser, and the like. It should be noted that the evaporator, the expansion valve, the condenser, and each of the pipes are not shown.

In the compressor configured as described above, when the drive shaft 3 is rotated, the swash plate 5 is rotated to reciprocate each of the pistons 9 in the first and second cylinder bores 21a and 23a. For this reason, the capacity of each of the first and second compression chambers 21d and 23d is changed according to the piston strokes. Therefore, the refrigerating gas sucked from the evaporator into the swash plate chamber 33 through the inlet port 330 is compressed in the first and second compression chambers 21d and 23d after passing through the first and second suction chambers 27a and 27b, and is then discharged into the first and second discharge chambers 29a and 29b. The refrigerating gas in the first and second discharge chamber 29a and 29b is discharged into the condenser through the outlet port.

During this period, in this compressor, piston compression force for reducing the inclination angle of the swash plate 5 acts on the rotating body configured by the swash plate 5, the ring plate 45, the lug arm 49, and the first pin 47a. Then, when the inclination angle of the swash plate 5 is changed, it is possible to perform the capacity control by the change in the strokes of the pistons 9.

Specifically, in the control mechanism 15, when the flow rate of refrigerating gas flowing through the release passage 15a is increased by the control valve 15c shown in FIG. 2, it becomes difficult that the refrigerating gas in the first discharge chamber 29a is stored in the pressure regulation chamber 25 through the supply passage 15b and the orifice 15d. For this reason, the pressure of the control pressure chamber 13c becomes almost equal to the pressure of the first suction chamber 27a. Therefore, as shown in FIG. 4, the actuator 13 is displaced by the piston compression force acting on the swash plate 5, so that the movable body 13a is moved toward the front side of the swash plate chamber 33, that is, toward the outside of the first storage chamber 21c, so as to become close to the lug arm 49.

Thereby, in this compressor, the other end side of the ring plate 45, that is, the other end side of the swash plate 5 is pivoted around the action axis M3 in the clockwise direction against the urging force of the second return spring 44b. Further, the rear end of the lug arm 49 is pivoted around the first pivotal axis M1 in the counter clockwise direction, and the front end of lug arm 49 is pivoted around the second pivotal axis M2 in the counter clockwise direction. As a result, the lug arm 49 is brought close to the flange 43a of the second support member 43. Thereby, the swash plate 5 is pivoted by using the action axis M3 as an action point, and by using the first pivotal axis M1 as a fulcrum. As a result, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the rotational axis O3 of the drive shaft 3 becomes close to 0 degree, so that the strokes of the pistons 9 are reduced. Thereby, in this compressor, the suction and discharge volume per one revolution is reduced. It should be noted that the inclination angle of the swash plate 5 shown in FIG. 4 is a minimum inclination angle in this compressor.

Here, in this compressor, the centrifugal force acting on the weight section 49a is also applied to the swash plate 5. For this reason, in this compressor, the swash plate 5 is easily displaced in the direction in which the inclination angle is reduced. Further, the movable body 13a is moved to the front side of the swash plate chamber 33, so that the front end of the movable body 13a is located inside the weight section 49a. Thereby, in this compressor, when the inclination angle of the swash plate 5 is reduced, the movable body 13a is brought in a state in which about half of the front end side of the movable body 13a is covered by the weight section 49a.

Further, when the inclination angle of the swash plate 5 is reduced, the ring plate 45 is brought into contact with the rear end of the first return spring 44a. Thereby, the first return spring 44a is elastically deformed, and is compressed by the ring plate 45.

Then, as described above, in this compressor, when the inclination angle of the swash plate 5 is reduced to reduce the strokes of the pistons 9, the top dead center position of the first head section 9b is located away from the first valve plate 39. Thereby, in this compressor, when the inclination angle of the swash plate 5 is brought close to 0 degree, slight compression work is performed on the side of the second compression chambers 23d, and no compression work is performed on the side of the first compression chambers 21d.

When the flow rate of refrigerating gas flowing through the release passage 15a is reduced by the control valve 15c shown in FIG. 2, the refrigerating gas in the first discharge chamber 29a is easily stored in the pressure regulation chamber 25 through the supply passage 15b and the orifice 15d. Thereby, the pressure of the control pressure chamber 13c becomes almost equal to the pressure of the first discharge chamber 29a. As a result, the actuator 13 is displaced against the piston compression force acting on the swash plate 5, so that, as shown in FIG. 1, the movable body 13a is moved toward the rear side of the swash plate chamber 33, that is, toward the inside of the first storage chamber 21c, so as to be located away from the lug arm 49.

As a result, in this compressor, the other end side of the swash plate 5 is in a state of being pulled at the action axis M3 toward the rear side of the swash plate chamber 33 by the movable body 13a via the connection section 132. Thereby, the other end side of the swash plate 5 is pivoted around the action axis M3 in the counter clockwise direction. Further, the rear end of the lug arm 49 is pivoted around the first pivotal axis M1 in the clockwise direction, and the front end of the lug arm 49 is pivoted around the second pivotal axis M2 in the clockwise direction. Thereby, the lug arm 49 is separated from the flange 43a of the second support member 43. As a result, by respectively using the action axis M3 and the first pivotal axis M1 as an action point and a fulcrum, the swash plate 5 is pivoted in the direction opposite to the direction in the above-described case where the inclination angle is reduced. For this reason, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the rotational axis O3 of the drive shaft 3 is increased. Thereby, in this compressor, the strokes of the pistons 9 are increased, so that the suction and discharge volume per one revolution of the compressor is increased. It should be noted that the inclination angle of the swash plate 5 shown in FIG. 1 is a maximum inclination angle in this compressor.

In this compressor, each of the first cylinder bores 21a is formed to be smaller in diameter than each of the second cylinder bores 23a, and also, in each of the pistons 9, the first head section 9b is formed to be smaller in diameter than the second head section 9c. Therefore, as shown in FIG. 3, in this compressor, without increasing the size of the first cylinder block 21, the first storage chamber 21c can be formed to be larger than the second storage chamber 23c in correspondence with the amount by which the diameter of the first cylinder bores 21a is smaller than the diameter of the second cylinder bores 23a, that is, in correspondence with the difference between the diameter D2 of the second cylinder bores 23a and the diameter D1 of the first cylinder bores 21a.

Therefore, as shown in FIG. 1, in this compressor, the size of the control pressure chamber 13c can be increased by increasing the size of the movable body 13a and the fixed body 13b. Thereby, in this compressor, the size of the control pressure chamber 13c is increased, so that the movable body 13a can be moved by a large thrust force. As a result, in this compressor, the compression capacity can be rapidly increased or reduced in a configuration in which the size of the compressor is prevented from being increased.

Further, in this compressor, as shown in FIG. 4, when the inclination angle of the swash plate 5 becomes close to 0 degree, slight compression work is performed in the second compression chambers 23d, and no compression work is performed in the first compression chambers 21d. For this reason, in this compressor, even when each of the first cylinder bores 21a and the first head section 9b is reduced in diameter, desired compression capacity can be secured on the side of the second compression chambers 23d.

Therefore, the compressor of Embodiment 1 has high controllability, and also can exhibit high mounting performance and secure sufficient compression capacity.

In particular, in this compressor, the first and second cylinder blocks 21 and 23 are formed so that each of the first cylinder bores 21a and each of the second cylinder bores 23a are coaxial with each other. Therefore, in this compressor, each of the first cylinder bores 21a can be easily formed in the first cylinder block 21, and also each of the second cylinder bores 23a can be easily formed in the second cylinder block 23. Further, in this compressor, the first head section 9b and the second head section 9c are arranged coaxially with each other in each of the pistons 9, and hence the pistons 9 can also be easily formed.

Further, as shown in FIG. 5, in this compressor, the front-rear direction length of the first head section 9b is set to be equal to the front-rear direction length of the second head section 9c, so that the length β1 of the first cylindrical surface 900c is set to be equal to the length β2 of the second cylindrical surface 901c for each of the pistons 9. Further, in this compressor, the length α1 of the first neck section 92 is also set to be equal to the length α2 of the second neck section 93 for each of the pistons 9. With this configuration, in this compressor, the distance L1 from the center of the engagement section 91 to the tip end of the first head section 9b and the distance L2 from the center of the engagement section 91 to the tip end of the second head section 9c are set to be equal to each other for each of the pistons 9. Thereby, in this compressor, the piston main body 9a, and the first and second head sections 9b and 9c are easily formed, so that each of the pistons 9 can be easily formed.

Embodiment 2

As shown in FIG. 6, in a compressor of Embodiment 2, each of the first cylinder bores 21a is formed at a position closer to the radially outer side of the first cylinder block 21 as compared with the compressor of Embodiment 1. Thereby, in this compressor, the position of the first center line O1 of each of the first cylinder bores 21a is different from the position of the second center line O2 of each of the second cylinder bores 23a. That is, in this compressor, each of the first cylinder bores 21a and each of the second cylinder bores 23a are formed non-coaxially with each other.

Further, in each of the pistons 9, when the first cylinder bore 21a is not coaxial with the second cylinder bore 23a, the position of the center line O4 of the first head section 9b is different from the position of the center line O5 of the second head section 9c as shown in FIG. 7. That is, in each of the pistons 9, the first head section 9b and the second head section 9c are formed in the piston main body 9a non-coaxially with each other. The other configurations of this compressor are the same as the configurations of the compressor of Embodiment 1, and the same configurations are denoted by the same reference numerals and characters, and the detailed description thereof is omitted.

In this compressor, since each of the first cylinder bores 21a and each of the second cylinder bores 23a are formed non-coaxially with each other, the degree of freedom in design related to the position of each of the first cylinder bores 21a in the first cylinder block 21 can be enhanced. Further, in this compressor, since each of the first cylinder bores 21a is formed at a position close to the radially outer side of the first cylinder block 21, the first storage chamber 21c in the first cylinder block 21 can be formed in a larger size as compared with the compressor of Embodiment 1.

For this reason, in this compressor, the movable body 13a and the fixed body 13b are formed in a larger size, so that the size of the control pressure chamber 13c can be further increased. As a result, in this compressor, the movable body 13a can be moved by a larger thrust force, and thereby the compression capacity can be rapidly increased or reduced in a configuration in which the size of the compressor is prevented from being increased. The other effects of this compressor are the same as those of the compressor of Embodiment 1.

Embodiment 3

A compressor of Embodiment 3 comprises a plurality of pistons 12 shown in FIG. 8 instead of the pistons 9 in the compressor of Embodiment 1. Each of the pistons 12 has a piston main body 12a, and also has the first head section 9b and the second head section 9c similarly to the compressor of Embodiment 1. It should be noted that, as for the length β1 of the first cylindrical surface 900c, and the length β2 of the second cylindrical surface 901c, the axial direction of the piston 9 is set as the axial direction of the piston 12 in the present embodiment.

In each of the pistons 12, the first head section 9b is connected to the piston main body 12a at the first front end surface 900a. Thereby, the first head section 9b is located at the rear end of the piston main body 12a, so as to be able to reciprocate in each of the first cylinder bores 21a. Further, the second head section 9c is connected to the piston main body 12a at the second rear end surface 901b. Thereby, the second head section 9c is located at the front end of the piston main body 12a, so as to be able to reciprocate in each of the second cylinder bores 23a. Further, each of the pistons 12 is also configured such that the centerline O4 passing through the center of the first head section 9b is located on the extension line of the center line O5 passing through the center of the second head section 9c, and such that the first head section 9b and the second head section 9c are coaxial with respect to the piston main body 12a.

In each of the pistons 12, the piston main body 12a is configured by an engagement section 120, a first neck section 121 extending from the engagement section 120 toward the first head section 9b, and a second neck section 122 extending from the engagement section 120 toward the side of the second head section 9c. Here, the piston main body 12a is formed so that the length α3 of the second neck section 122 in the axial direction of the piston 12 (hereinafter referred to as the length α3 of the second neck section 122) is equal to the length α2 of the second neck section 93 in the piston 9. The piston main body 12a is formed so that the length α4 of the first neck section 121 in the axial direction of the piston 12 (hereinafter referred to as the length α4 of the first neck section 121) is longer than the length α3 of the second neck section 122. Therefore, in each of the pistons 12, the value of the sum of the length α4 of the first neck section 121 and the length β1 of the first cylindrical surface 900c is larger than the value of the sum of the length α3 of the second neck section 122 and the length β2 of the second cylindrical surface 901c. As a result, in each of the pistons 12, the distance L1 from the center of the engagement section 120 to the tip end of the first head section 9b is larger than the distance L2 from the center of the engagement section 120 to the tip end of the second head section 9c.

As described above, in each of the pistons 12, the distance L1 from the center of the engagement section 120 to the tip end of the first head section 9b is larger than the distance L2 from the center of the engagement section 120 to the tip end of the second head section 9c. Thereby, although not shown, in this compressor, the first cylinder block 21 is formed to be longer in the front and rear direction as compared with the compressor of Embodiment 1. Thereby, in this compressor, each of the first cylinder bores 21a is formed to be long in the front and rear direction. The other configurations of this compressor are the same as those of the compressor of Embodiment 1.

In this way, in this compressor, the length α4 of the first neck section 121 is longer than the length α3 of the second neck section 122, and thereby, in each of the pistons 12, the distance L1 from the center of the engagement section 120 to the tip end of the first head section 9b is longer than the distance L2 from the center of the engagement section 120 to the tip end of the second head section 9c. For this reason, in this compressor, even in a case where the diameter of the first head section 9b is made smaller than the diameter of the second head section 9c, the weight on the side of the first head section 9b can be easily made larger than the weight on the side of the second head section 9c in each of the pistons 12, and hence the weight on the side of the first head section 9b and the weight on the side of the second head section 9c can be easily balanced in each of the pistons 12. In this way, in this compressor, each of the pistons 12 can be made to suitably reciprocate in each pair of the first and second cylinder bores 21a and 23a. The other effects of the compressor are the same as those of the compressor of Embodiment 1.

Embodiment 4

A compressor of Embodiment 4 includes a plurality of pistons 14 shown in FIG. 9 instead of each of the pistons 9 in the compressor of Embodiment 1. Similarly to the compressor of Embodiment 1, each of the pistons 14 includes the piston main body 9a and the second head section 9c, and also includes a first head section 14a. The first head section 14a is also formed in a substantially columnar shape and includes a first front end surface 140a, a first rear end surface 140b, and a first cylindrical surface 140c. The first head section 14a is formed to have a diameter smaller than the diameter of the second head section 9c.

In each of the pistons 14, the first head section 14a is connected to the piston main body 9a at the first front end surface 140a. Thereby, the first head section 14a is located at the rear end of the piston main body 9a, so as to be able to reciprocate in each of the first cylinder bores 21a. Further, the second head section 9c is connected to the piston main body 9a at the second rear end surface 901b. Thereby, the second head section 9c is located at the front end of the piston main body 9a, so as to be able to reciprocate in each of the second cylinder bores 23a. Further, each of the pistons 14 is also configured such that the center line O4 passing through the center of the first head section 14a is located on the extension line of the center line O5 passing through the center of the second head section 9c, and such that the first head section 14a and the second head section 9c are coaxial with respect to the piston main body 9a.

Here, the first head section 14a is formed to be longer in the front and rear direction than the second head section 9c. Therefore, the length β3 of the first cylindrical surface 140c in the axial direction of the piston 14 (hereinafter referred to as the length β3 of the first cylindrical surface 140c) is longer than the length β2 of the second head section 9c in the piston 14 of the compressor of Embodiment 4.

Thereby, in each of the pistons 14 (the axial direction of the piston 9 is set in the axial direction of the piston 14 in the present embodiment), the value of the sum of the length α1 of the first neck section 92 and the length β3 of the first cylindrical surface 140c is larger than the value of the sum of the length α2 of the second neck section 93 and the length β2 of the second cylindrical surface 901c. In this way, in each of the pistons 14, the distance L1 from the center of the engagement section 91 to the tip end of the first head section 14a is longer than the distance L2 from the center of the engagement section 91 to the tip end of the second head section 9c. It should be noted that, similarly to the compressor of Embodiment 3, the first cylinder block 21 is also formed to be long in the front and rear direction in this compressor, and hence each of the first cylinder bores 21a is formed to be long in the front and rear direction (not shown). The other configurations of this compressor are the same as those of the compressor of Embodiment 1.

In this way, in this compressor, in order that, in each of the pistons 14, the distance L1 from the center of the engagement section 91 to the tip end of the first head section 14a is made longer than the distance L2 from the center of the engagement section 91 to the tip end of the second head section 9c, the length β3 of the first cylindrical surface 140c is made longer than the length β2 of the second cylindrical surface 901c. This makes it possible that, in this compressor, even when the first head section 14a is formed to have a diameter smaller than the diameter of the second head section 9c, the weight on the side of the first head section 14a is easily made larger than the weight on the side of the second head section 9c in each of the pistons 14. Thereby, even in this compressor, the weight on the side of the first head section 14a and the weight on the side of the second head section 9c can be easily balanced in each of the pistons 14. The other effects of this compressor are the same as those of the compressor of Embodiment 1.

In the above, the present invention has been described by way of Embodiments 1 to 4. However, the present invention is not limited to Embodiments 1 to 4 described above, and it goes without saying that the present invention can be practiced with proper modification without departing from the scope of the present invention.

For example, in the piston 14 in the compressor of Embodiment 4, the length α1 of the first neck section 92 can be made smaller than the length α2 of the second neck section 93 so that the sum of the length α1 of the first neck section 92 and the length β3 of the first cylindrical surface 140c is equal to the sum of the length α2 of the second neck section 93 and the length β2 of the second cylindrical surface 901c. This makes it possible that, in each of the pistons 14, in a state in which the first head section 14a is formed to be longer in the front and rear direction than the second head section 9c, the distance L1 from the center of the engagement section 91 to the tip end of the first head section 14a is made equal to the distance L2 from the center of the engagement section 91 to the tip end of the second head section 9c.

Further, the control mechanism 15 may also be configured such that the control valve 15c is provided at the supply passage 15b, and such that the orifice 15d is provided at the release passage 15a. In this case, the flow rate of the high-pressure refrigerating gas flowing through the supply passage 15c can be adjusted by the control valve 15c. Thereby, the pressure in the control pressure chamber 13c can be rapidly increased by the high pressure in the first discharge chamber 29a, so that the compression capacity can be rapidly reduced.

VARIABLE DISPLACEMENT SWASH PLATE TYPE COMPRESSOR

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CPC

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