CN105102815B - Capacity variable type tilted-plate compressor - Google Patents

Abstract

The present invention provides a kind of compressor, and which utilizes actuator change to discharge capacity, can play high controlling and realize miniaturization.In the compressor of the present invention, moving body (13a) is with rear wall (130), perisporium (131) and links mechanism (14).Link mechanism (14) with being set with first arm (132) of the first towing point (132a), and be set with second arm (133) of the second towing point (133a).In the compressor, when the angle of inclination of swash plate (5) is increased, moving body (13a) draws swash plate by the first arm, the second arm (132,133).Now, in the compressor, pull strength can be given with two positions of the second towing point (133a) in the first towing point (132a).Therefore, in the compressor, even if rear wall (130) and perisporium (131) are maximized, it is also possible to reduce the first arm, the rigidity of the second arm (132,133).

Description

Variable Capacity Inclined Plate Compressor

technical field

The present invention relates to variable capacity inclined plate compressors.

Background technique

Patent Document 1 discloses a conventional variable capacity swash plate compressor (hereinafter, referred to as a compressor). In this compressor, a casing is formed by a front casing, a cylinder block, and a rear casing. A suction chamber and a discharge chamber are respectively formed in the front case and the rear case. A swash plate chamber and a plurality of cylinder holes are formed in the cylinder block. The drive shaft is rotatably supported by the case. A swash plate rotatable by rotation of a drive shaft is provided in the swash plate chamber. A link mechanism is arranged between the drive shaft and the swash plate. The link mechanism allows changes in the inclination angle of the swash plate. Here, the inclination angle refers to the angle of the swash plate with respect to the direction perpendicular to the drive shaft center of the drive shaft. Pistons are reciprocally accommodated in the respective cylinder bores. The sliding shoe paired with each piston acts as a conversion mechanism to reciprocate each piston in the cylinder bore with a stroke corresponding to the inclination angle by the rotation of the swash plate. The actuator has a moving body and a control pressure chamber. This actuator can change the inclination angle by changing the volume of the control pressure chamber. A control mechanism controls the actuator.

A pair of first arms extending toward the front cabinet side and a pair of second arms extending toward the rear cabinet side are formed on the swash plate. In addition, a cantilever is fixed to the drive shaft. Furthermore, each first arm and the cantilever are connected by a first pin. In addition, each second arm and the moving body are connected by a second pin. A link mechanism is formed by the first arm, the second arm, the cantilever, the moving body, the first pin, and the second pin.

In this compressor, the control mechanism increases the pressure in the control pressure chamber by utilizing the pressure of the refrigerant in the discharge chamber, and increases the inclination angle of the swash plate through the link mechanism. At this time, the moving body presses the swash plate through the second arms. In addition, the swash plate pushed by the moving body pushes the cantilever through each first arm. As a result, the axial length in the direction of the drive axis in the link mechanism becomes shorter, and the inclination angle of the swash plate increases. In this way, in this compressor, the discharge capacity per revolution of the drive shaft is increased.

Patent Document 1: Japanese Patent Application Laid-Open No. 5-172052

However, higher controllability is required in a compressor that changes the discharge capacity using an actuator as described above.

Therefore, in the above-mentioned conventional compressor, in order to reliably increase the discharge capacity by controlling the pressure rise of the pressure chamber, it is considered to increase the size of the moving body in the radial direction. However, in this case, in order to avoid interference between the movable body and the swash plate whose inclination angle is increased, the size of the swash plate chamber is increased, and the size of the compressor is further increased.

In addition, in this compressor, since the tilt angle increases when the moving body pushes the swash plate, it is necessary for the moving body to push the slant plate with a large pressing force so as to overcome the increasing compression reaction force and suction reaction force. plate. Therefore, in this compressor, when increasing the inclination angle, a large pressing force acts on each second arm. Therefore, if high rigidity is ensured for each second arm so as to be able to bear such a load of pressing force, each second arm will increase in size. The same applies to each first arm. Here, when the movable body is enlarged in the radial direction as described above, the pressing force acting on each of the first arm and the second arm is further increased, and therefore a higher force is required for each of the first arm and the second arm. rigidity. This enlargement of the first arm and the second arm also leads to enlargement of the inclined plate chamber.

Contents of the invention

The present invention was made in view of the above-mentioned conventional circumstances, and it is a problem to be solved to provide a compressor capable of exhibiting high controllability and realizing miniaturization among compressors that change the discharge capacity using an actuator.

The capacity-variable swash plate compressor of the present invention is characterized in that it comprises: a housing formed with a suction chamber, a discharge chamber, a swash plate chamber and at least one cylinder hole; a drive shaft extending along the center of the drive shaft and rotatable. Supported by the housing; a swash plate capable of rotating in the swash plate chamber through the rotation of the drive shaft; a link mechanism arranged between the drive shaft and the swash plate and allowing the swash plate to change of the inclination angle of the drive shaft in a direction perpendicular to the drive shaft center; a piston reciprocatably accommodated in the cylinder hole; making the piston reciprocate in the cylinder bore; and an actuator disposed in the swash plate chamber and capable of changing the inclination angle; and a control mechanism controlling the actuator, and the suction chamber communicates with the swash plate chamber. , the above-mentioned actuator has: a dividing body, which is provided on the above-mentioned driving shaft; a moving body, which is connected to the above-mentioned swash plate through a connecting mechanism, and moves along the direction of the driving shaft center and can move relative to the above-mentioned dividing body; and a control pressure chamber, which is divided by the partition body and the moving body, and moves the moving body by introducing refrigerant from the discharge chamber, and the moving body is configured to pull the swash plate by increasing the pressure in the control pressure chamber To increase the inclination angle, the link mechanism has a connection portion connected to the swash plate, the connection mechanism has a first arm and a second arm, and they are arranged on the opposite side of the connection portion with respect to the drive shaft, And it is provided on the said mobile body across the said drive shaft center.

In the compressor of the present invention, when the inclination angle of the swash plate is increased, the moving body pulls the swash plate. In other words, in this compressor, when the swash plate is displaced in a direction to increase the inclination angle, the movable body moves away from the swash plate. Therefore, in this compressor, even when the moving body is enlarged in order to reliably increase the discharge capacity by controlling the pressure rise of the pressure chamber, interference between the moving body and the swash plate does not occur. Accordingly, in this compressor, it is possible to suppress enlargement of the swash plate chamber.

Furthermore, in this compressor, the movable body is connected to the swash plate via a connection mechanism. Therefore, when the inclination angle of the swash plate is increased, the moving body applies tractive force to the swash plate through the connection mechanism. Here, when the inclination angle is increased by pulling the swash plate, it is less affected by compression reaction force and suction reaction force than when the inclination angle is increased by pushing the swash plate. Therefore, in this compressor, when increasing the inclination angle of the swash plate, a large pulling force is not required.

And, in this compressor, the connection mechanism has a first arm and a second arm. Furthermore, the first arm and the second arm are arranged on the moving body across the driving axis. Thereby, traction force can be given to the said 1st arm and 2nd arm. Therefore, in this compressor, compared with the case where, for example, the coupling mechanism has only a single arm, the tractive forces respectively applied to the swash plate by the first arm and the second arm can be reduced. In addition, in this compressor, when the inclination angle of the swash plate is reduced, the movable body presses the swash plate through the first arm and the second arm, but the pressing force at this time is not very large. This is because a centrifugal force acts on the rotating body including the swash plate and the moving body in a direction to decrease the inclination angle.

Accordingly, in this compressor, as described above, even when the movable body is increased in size, the rigidity of the first arm and the second arm required thereby can be reduced. Therefore, in this compressor, it is possible to suppress enlargement of the connection mechanism.

Therefore, according to the compressor of the present invention, it is possible to realize high controllability and miniaturization in a compressor that changes the discharge capacity using an actuator.

In the compressor of the present invention, the at least one cylinder hole may be at least the first cylinder hole, the second cylinder hole and the third cylinder hole. The first cylinder hole, the second cylinder hole, and the third cylinder hole may be arranged in the housing at equal angular intervals in concentric circles centered on the drive axis. A first imaginary area and a second imaginary area may be set in the slant plate chamber. The first imaginary area consists of a first tangent drawn from the drive axis to the second cylinder bore side of the first cylinder bore, and a first tangent drawn from the drive axis to the first cylinder bore side of the second cylinder bore. Two tangent divisions. The second imaginary area consists of a third tangent drawn from the drive shaft center to the third cylinder bore side of the second cylinder bore, and a fourth tangent drawn from the drive shaft center to the second cylinder bore side of the third cylinder bore. Tangent division. Furthermore, it is preferable that the first arm is located in the first imaginary area, and the second arm is located in the second imaginary area.

In this case, the first arm and the second arm do not interfere with the piston reciprocating in the first to third cylinder bores. Therefore, the compressor can be reliably downsized.

In addition, the swash plate may be provided with a drawn portion protruding between the first arm and the second arm. Furthermore, it is preferable to transmit a driving force between the first arm and the second arm and the pulled portion. At this time, the moving body rotates stably together with the driving shaft, and the swash plate rotates stably together with the moving body and further rotates stably together with the driving shaft.

In the compressor of the present invention, for example, the first arm and the drawn portion, and the second arm and the drawn portion can be connected by different pins or the like.

In particular, it is preferable that a pin extending in a direction perpendicular to the drive axis be inserted through the first arm, the pulled portion, and the second arm. In this case, the first arm, the pulled portion, and the second arm can be easily connected. In this case, as described above, compared with the case where the first arm, the pulled portion, and the second arm and the pulled portion are connected by different pins, etc., the number of parts can be reduced, and manufacturing can be facilitated. In addition, in this case, it is difficult to remove the pin from the first arm, the second arm, and the pulled portion, and reliability can be improved.

According to the compressor of the present invention, it is possible to realize high controllability and miniaturization in a compressor that changes the discharge capacity using an actuator.

Description of drawings

Fig. 1 is a cross-sectional view of the compressor of the embodiment at the maximum capacity.

Fig. 2 is a schematic diagram showing a control mechanism of the compressor of the embodiment.

FIG. 3 relates to the compressor of the embodiment, and is a cross-sectional view in the direction of the arrow viewed from the III-III direction in FIG. 1 .

Fig. 4A is a front view showing a swash plate related to the compressor of the embodiment.

Fig. 4B is a cross-sectional view showing a swash plate related to the compressor of the embodiment.

Fig. 5 is a cross-sectional view of the compressor of the embodiment at the minimum capacity.

Fig. 6 is a perspective view showing a moving body of the compressor of the embodiment seen from the front.

Fig. 7 is a schematic plan view showing a moving body of the compressor of the embodiment.

detailed description

Hereinafter, embodiments embodying the present invention will be described with reference to the drawings. The compressor of the embodiment is a variable-capacity double-headed inclined-plate compressor. This compressor is mounted on a vehicle and constitutes a refrigeration circuit of the vehicle air conditioner.

As shown in FIG. 1 , the compressor of Embodiment 1 includes: a casing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, a pair of shoes 11a, 11b, an actuator 13, and The control mechanism 15 shown in FIG. 2 .

As shown in FIG. 1 , the housing 1 has: a rear housing 17 located at the rear of the compressor, a front housing 19 located at the front of the compressor, and a first cylinder located between the front housing 19 and the rear housing 17 21 , the second cylinder body 23 , and the first valve forming plate 39 and the second valve forming plate 41 .

The control mechanism 15 described above is provided on the rear case 17 . In addition, the rear housing 17 is formed with a first suction chamber 27 a, a first discharge chamber 29 a, and a pressure adjustment chamber 31 . The pressure adjustment chamber 31 is located at the center portion of the rear case 17 . The first suction chamber 27 a is formed in an annular shape, and is located on the outer peripheral side of the pressure adjustment chamber 31 in the rear housing 17 . The first discharge chamber 29 a is also formed in an annular shape, and is located on the outer peripheral side of the first suction chamber 27 a in the rear housing 17 .

Furthermore, a first rear communication passage 18 a is formed in the rear cabinet 17 . The rear end side of the first rear side communication path 18 a communicates with the first discharge chamber 29 a, and the front end side is opened at the front end of the rear cabinet 17 .

A protrusion 19 a protruding forward is formed on the front case 19 . A shaft seal 25 is arranged in this projection 19a. In addition, a second suction chamber 27 b and a second discharge chamber 29 b are formed in the front housing 19 . The second suction chamber 27 b is located on the inner peripheral side of the front case 19 . The second discharge chamber 29 b is formed in an annular shape, and is located on the outer peripheral side of the second suction chamber 27 b in the front housing 19 .

In addition, a first front communication path 20 a is formed in the front case 19 . The front end side of the first front side communicating path 20 a communicates with the second discharge chamber 29 b, and the rear end side opens at the rear end of the front case 19 .

A swash plate chamber 33 is formed between the first cylinder 21 and the second cylinder 23 . The swash plate chamber 33 is located substantially at the center in the front-rear direction of the casing 1 .

As shown in FIG. 3 , first to fifth rear cylinder holes 21 a to 21 e are respectively formed in parallel at equal angular intervals in the first cylinder block 21 in the circumferential direction. In addition, as shown in FIG. 1 , a first shaft hole 211 through which the drive shaft 3 is inserted is formed in the first cylinder 21 . The first shaft hole 211 communicates with the pressure adjustment chamber 31 on the rear end side. A first sliding bearing 22 a is provided in the first shaft hole 211 . In addition, a rolling bearing may be provided instead of the first slide bearing 22a.

Furthermore, a first recess 212 communicating with the first shaft hole 211 and coaxial with the first shaft hole 211 is formed in the first cylinder 21 . The first recess 212 communicates with the swash plate chamber 33 and becomes a part of the swash plate chamber 33 . The first concave portion 212 is formed in a shape whose diameter gradually decreases toward the rear end. At the rear end of the first concave portion 212, a first thrust bearing 35a is provided. In addition, as shown in FIG. 3 , five connection passages 37 a communicating with the swash plate chamber 33 and the first suction chamber 27 a are formed in the first cylinder block 21 . The respective communicating passages 37a are formed at equal angular intervals in the circumferential direction so as to be respectively arranged between the first to fifth rear cylinder bores 21a to 21e. In addition, as shown in FIG. 1 , first stop grooves 213 for limiting the maximum opening of each first suction reed valve 391 a described later are recessed in the first cylinder 21 .

A discharge hole 160 , a combined discharge chamber 161 , a third front communication passage 20 c , a second rear communication passage 18 b , and a suction hole 330 are formed in the first cylinder block 21 . The front end side of the second rear side communication passage 18 b communicates with the confluence discharge chamber 161 , and the rear end side opens at the rear end of the first cylinder 21 . The discharge hole 160 communicates with the combined discharge chamber 161 . The combined discharge chamber 161 is connected to a condenser (not shown) through the discharge hole 160 to constitute a refrigeration circuit. In addition, the front end side of the third front side communication passage 20 c is opened at the front end of the first cylinder 21 , and the rear end side communicates with the confluence discharge chamber 161 . The suction hole 330 communicates with the swash plate chamber 33 . The suction hole 330 is connected to an evaporator not shown to constitute a refrigeration circuit.

The second cylinder block 23 is formed with a first front cylinder bore 23a corresponding to the first rear cylinder bore 21a. Accordingly, the first rear cylinder bore 21a and the first front cylinder bore 23a form a front-rear pair. The first rear cylinder hole 21a has the same diameter as the first front cylinder hole 23a. In addition, similarly, second to fifth front cylinder bores (not shown) corresponding to the second to fifth rear cylinder bores 21 b to 21 e are formed in the second cylinder block 23 , respectively.

Moreover, the 2nd shaft hole 23b through which the drive shaft 3 penetrates is formed in the 2nd cylinder block 23. As shown in FIG. In addition, a second sliding bearing 23 b is provided in the second shaft hole 23 . In addition, a rolling bearing may be provided instead of the second slide bearing 22b.

Moreover, the 2nd recessed part 23c which communicates with the 2nd shaft hole 23b and is coaxial with the 2nd shaft hole 23b is formed in the 2nd cylinder block 23. As shown in FIG. The second concave portion 23 c also communicates with the swash plate chamber 33 and becomes a part of the swash plate chamber 33 . Thus, the second shaft hole 23b communicates with the swash plate chamber 33 on the rear end side. The second concave portion 23c is formed in a shape whose diameter gradually decreases toward the front end. A second thrust bearing 35b is provided at the front end of the second recessed portion 23c. In addition, a plurality of connection passages 37b that communicate with the swash plate chamber 33 and the second suction chamber 27b are formed in the second cylinder block 23 . In addition, second stopper grooves 23e for limiting the maximum opening degrees of the second suction reed valves 411a described later are recessed in the second cylinder body 23 .

In addition, a second front communication passage 20 b is formed in the second cylinder 23 . The front end of the second front side communication passage 20 b opens on the front end side of the second cylinder 23 , and the rear end opens on the rear end side of the second cylinder 23 . The second front communication passage 20b communicates with the front end side of the third front communication passage 20c by connecting the first cylinder 21 and the second cylinder 23 .

The first valve forming plate 39 is disposed between the rear housing 17 and the first cylinder block 21 . In addition, a second valve forming plate 41 is provided between the front housing 19 and the second cylinder block 23 .

The first valve forming plate 39 has a first valve plate 390 , a first suction valve plate 391 , a first discharge valve plate 392 , and a first baffle plate 393 . A plurality of first suction holes 390 a corresponding to the first to fifth rear cylinder holes 21 a to 21 e are formed in the first valve plate 390 , the first discharge valve plate 392 , and the first damper 393 . In addition, a plurality of first discharge holes 390 b corresponding to the first to fifth rear cylinder holes 21 a to 21 e are formed in the first valve plate 390 and the first suction valve plate 391 . Furthermore, a first suction communication hole 390 c is formed in the first valve plate 390 , the first suction valve plate 391 , the first discharge valve plate 392 , and the first damper 393 . In addition, a first discharge communication hole 390 d is formed in the first valve plate 390 and the first suction valve plate 391 .

The first to fifth rear cylinder holes 21a to 21e communicate with the first suction chamber 27a through the first suction holes 390a, respectively. In addition, the first to fifth rear cylinder holes 21a to 21e communicate with the first discharge chamber 29a through each of the first discharge holes 390b. The first suction chamber 27a communicates with each connection path 37a through the first suction communication hole 390c. The first rear communication passage 18a communicates with the second rear communication passage 18b through the first discharge communication hole 390d.

The first suction valve plate 391 is disposed on the front surface of the first valve plate 390 . The first suction reed valve 391a that can open and close each first suction hole 390a by elastic deformation and has the same number as the first suction holes 390a is formed on the first suction valve plate 391 . In addition, the first discharge valve plate 392 is disposed on the rear surface of the first valve plate 390 . First discharge reed valves 392 a having the same number as the first discharge holes 390 b are formed on the first discharge valve plate 392 to open and close each of the first discharge holes 390 b by elastic deformation. The first baffle 393 is disposed on the rear surface of the first discharge valve plate 392 . The first damper 393 limits the maximum opening of each first discharge reed valve 392a.

The second valve forming plate 41 has a second valve plate 410 , a second suction valve plate 411 , a second discharge valve plate 412 , and a second baffle plate 413 . The second suction holes 410 a having the same number as the first to fifth front cylinder holes 23 a are formed in the second valve plate 410 , the second discharge valve plate 412 , and the second baffle plate 413 . In addition, the second discharge holes 410 b having the same number as the first to fifth front cylinder holes 23 a are formed in the second valve plate 410 and the second suction valve plate 411 . In addition, a second suction communication hole 410 c is formed in the second valve plate 410 , the second suction valve plate 411 , the second discharge valve plate 412 , and the second damper 413 . In addition, a second discharge communication hole 410 d is formed in the second valve plate 410 and the second suction valve plate 411 .

The first to fifth front cylinder holes 23a communicate with the second suction chamber 27b through the second suction holes 410a, respectively. In addition, the first to fifth front cylinder bores 23a communicate with the second discharge chamber 29b through the second discharge holes 410b, respectively. The second suction chamber 27b communicates with each connection path 37b through the second suction communication hole 410c. The first front communication passage 20a communicates with the second front communication passage 20b through the second discharge communication hole 410d.

The second suction valve plate 411 is disposed on the rear surface of the second valve plate 410 . Second suction reed valves 411 a having the same number as the second suction holes 410 a are formed on the second suction valve plate 411 to open and close the respective second suction holes 410 a through elastic deformation. In addition, the second discharge valve plate 412 is disposed on the front surface of the second valve plate 410 . Second discharge reed valves 412 a having the same number as the second discharge holes 410 b are formed on the second discharge valve plate 412 to open and close the respective second discharge holes 410 b by elastic deformation. The second baffle 413 is disposed on the front surface of the second discharge valve plate 412 . The second damper 413 limits the maximum opening of each second discharge reed valve 412a.

In this compressor, the first discharge communication passage 18 is formed by the first rear communication passage 18a, the first discharge communication hole 390d, and the second rear communication passage 18b. In addition, the second discharge communication passage 20 is formed by the first front communication passage 20a, the second discharge communication hole 410d, the second front communication passage 20b, and the third front communication passage 20c.

In addition, in this compressor, the first suction chamber 27a, the second suction chamber 27b, and the swash plate chamber 33 communicate with each other through the respective connection passages 37a, 37b, the first suction communication hole 390c, and the second suction communication hole 410c. Therefore, the pressures in the first suction chamber 27 a and the second suction chamber 27 b are substantially equal to the pressure in the swash plate chamber 33 . Moreover, since the low-pressure refrigerant gas passing through the evaporator flows into the swash plate chamber 33 through the suction hole 330, the pressures in the swash plate chamber 33, the first suction chamber 27a, and the second suction chamber 27b are lower than those in the first discharge chamber 29a. , Low pressure in the second discharge chamber 29b.

The drive shaft 3 is composed of a drive shaft main body 30 extending along the drive shaft center O, a first support member 43a, and a second support member 43b. A first small-diameter portion 30 a is formed on the rear end side of the drive shaft main body 30 , and a second small-diameter portion 30 b is formed on the front end side of the drive shaft main body 30 . The drive shaft main body 30 extends from the front side toward the rear side of the housing 1, and is inserted rearward from the protrusion 19a, thereby being inserted into the first sliding bearing 22a and the second sliding bearing 22b. Accordingly, the drive shaft main body 30 is pivotally supported by the casing 1 so as to be rotatable around the above-mentioned drive axis O, and furthermore, the drive shaft 3 is pivotally supported by the casing 1 so as to be rotatable around the drive axis O. As shown in FIG. The front end of the drive shaft main body 30 is located in the protrusion 19 a, and the rear end protrudes into the pressure adjustment chamber 31 .

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

The first support member 43 a is press-fitted into the rear end side of the first small-diameter portion 30 a of the drive shaft main body 30 and is positioned in the first shaft hole 211 . A flange 430 is formed at the front end of the first support member 43a. The flange 430 protrudes into the first concave portion 212 and abuts on the first thrust bearing 35a. In addition, the rear end of the first support member 43 a protrudes into the pressure adjustment chamber 31 . In addition, a resin-made first slide member 431 and a second slide member 432 are provided at positions on the rear end side of the flange 430 in the first support member 43a. The first sliding member 431 and the second sliding member 432 are capable of slidingly contacting the inner peripheral surface of the first shaft hole 211 .

The second support member 43b is press-fitted into the second small-diameter portion 30b of the drive shaft main body 30, and is positioned between the second sliding bearing 22b in the second shaft hole 23b. Moreover, the flange 433 which abuts on the 2nd thrust bearing 35b is formed in this 2nd support member 43b, and the attachment part (illustration omitted) which penetrates the 2nd pin 47b mentioned later is formed. Moreover, the front-end|tip of the 1st return spring 44a is being fixed to the 2nd support member 43b. The first return spring 44a extends from the second support member 43b side toward the swash plate chamber 33 side in the drive axis O direction.

The swash plate 5 is formed in an annular flat plate shape, and has a front surface 5a and a rear surface 5b. The front surface 5 a faces the front of the compressor in the swash plate chamber 33 . In addition, the rear surface 5 b faces the rear of the compressor in the swash plate chamber 33 .

The swash plate 5 has an annular plate 45 . As shown in FIG. 4 , the annular plate 45 is formed in an annular flat plate shape, and has an insertion hole 45 a formed in the center thereof. The swash plate 5 is attached to the drive shaft 3 by inserting the drive shaft main body 30 into the insertion hole 45 a in the swash plate chamber 33 (see FIG. 1 ).

In addition, as shown in FIG. 4A , a groove portion 45 b is formed on one end side of the annular plate 45 , and a pulled portion 45 c is formed on the other end side of the annular plate 45 . As shown in FIG. 4B , the groove portion 45b penetrates from the front surface 5a of the swash plate 5 to the rear surface 5b. On the other hand, the pulled portion 45c protrudes from the rear surface 5b toward the rear of the swash plate 5 so as to be located between the first arm 132 and the second arm 133 described later. A pin hole 450 is formed in the pulled portion 45c.

As shown in FIG. 1 , the link mechanism 7 has a cantilever 49 . The cantilever 49 is arranged in the front of the swash plate 5 in the swash plate chamber 33, and is located between the swash plate 5 and the second support member 43b. The cantilever 49 is formed in a substantially L-shape from the front end side toward the rear end side. In addition, a weight portion 49 a is formed on the rear end side of the boom 49 . The weight portion 49a extends over approximately half of the circumference of the actuator 13 . In addition, the shape of the weight part 49a can be designed suitably.

The rear end side of the cantilever 49 is connected to one end side of the annular plate 45 by a first pin 47a. This first pin 47a corresponds to the connecting portion in the present invention. Thus, the rear end side of the cantilever 49 is supported such that the axis of the first pin 47a is the first swing axis M1, and the swash plate 5, which is one end side of the ring plate 45, can rotate around the first swing axis M1. swing. The first swing axis M1 extends in a direction perpendicular to the drive axis O of the drive shaft 3 .

The front end side of the cantilever 49 is connected to the second support member 43b via the second pin 47b. Thereby, the front end side of the cantilever 49 is supported so that the axis of the second pin 47b is the second swing axis M2 and can swing around the second swing axis M2 with respect to the drive shaft 3 which is the second support member 43b. The second swing axis M2 extends parallel to the first swing axis M1. In addition to the cantilever 49, the first pin 47a, and the second pin 47b described above, the link mechanism 7 in the present invention is constituted by the first arm 132, the second arm 133, and the third pin 47c described later.

The weight portion 49a is provided so as to extend toward the side opposite to the second swing axis M2 based on the first swing axis M1 which is the rear end side of the boom 49 . Therefore, the cantilever 49 is supported by the ring plate 45 by the first pin 47a, so that the weight portion 49a passes through the groove portion 45b of the ring plate 45 and is positioned behind the ring plate 45, that is, on the rear face 5b side of the swash plate 5. Furthermore, the centrifugal force generated by the rotation of the swash plate 5 around the drive axis O also acts on the weight portion 49 a on the rear surface 5 b side of the swash plate 5 .

In this compressor, the swash plate 5 and the drive shaft 3 are connected by a link mechanism 7 so that the swash plate 5 can rotate together with the drive shaft 3 . In addition, both ends of the cantilever 49 swing around the first swing axis M1 and the second swing axis M2, whereby the swash plate 5 can change the inclination angle.

Each piston 9 has a first head portion 9a on the rear end side and a second head portion 9b on the front end side. Each first head portion 9a is accommodated in each of the first to fifth rear cylinder bores 21a to 21e so as to be reciprocatable. The first compression chambers 210 are defined in the first to fifth rear cylinder bores 21a to 21e by the respective first head portions 9a and the first valve forming plate 39 described above. Each second head portion 9b is accommodated in the first to fifth front cylinder bores 23a so as to be reciprocatable. The second compression chambers 230 are respectively defined in the first to fifth front cylinder bores 23a by the respective second head portions 9b and the second valve forming plate 41 described above.

In addition, an engaging portion 9 c is formed at the center of each piston 9 . Hemispherical shoes 11a, 11b are provided in each engaging portion 9c, respectively. The rotation of the swash plate 5 is converted into the reciprocating motion of the piston 9 by the above-mentioned shoes 11a, 11b. The shoes 11a, 11b correspond to the conversion mechanism in this invention. In this way, each first head 9a can reciprocate in the first to fifth rear cylinder holes 21a to 21e with a stroke corresponding to the inclination angle of the swash plate 5, and each second head 9b can respectively move in the first to fifth rear cylinder holes 21a to 21e. ~ Reciprocating movement in the fifth front cylinder bore 23a.

Here, in this compressor, the stroke of the piston 9 changes with the change of the inclination angle of the swash plate 5, and the respective top dead center positions of the first head 9a and the second head 9b move. Specifically, as shown in FIG. 5, as the inclination angle of the swash plate 5 becomes smaller, the first head 9a and the second head 9b move to the top dead center position, so that the volume of the first compression chamber 210 becomes It is larger than the volume of the second compression chamber 230 .

The actuator 13 is arranged in the swash plate chamber 33 . The actuator 13 is located on the rear side of the swash plate 5 in the swash plate chamber 33 and can enter the first recess 212 . The actuator 13 has a moving body 13a, a partition body 13b, and a control pressure chamber 13c. The control pressure chamber 13c is formed between the moving body 13a and the partition body 13b.

As shown in FIG. 6 , the moving body 13 a has a rear wall 130 , a peripheral wall 131 , and a connection mechanism 14 . The rear wall 130 is positioned behind the moving body 13 a and extends radially in a direction away from the drive axis O. As shown in FIG. In addition, an insertion hole 130 a through which the first small-diameter portion 30 a of the drive shaft main body 30 is inserted is provided through the rear wall 130 . The peripheral wall 131 is continuous with the outer peripheral edge of the rear wall 130, and extends toward the front of the moving body 13a. And the mobile body 13a is formed in the bottomed cylindrical shape by the said rear wall 130, the surrounding wall 131, and the connection mechanism 14. As shown in FIG.

The link mechanism 14 has a first arm 132 and a second arm 133 . Both the first arm 132 and the second arm 133 are formed at the front end of the peripheral wall 131, and protrude toward the front of the moving body 13a. Specifically, the first arm 132 is formed on the left side of the front end of the peripheral wall 131 , and the second arm 133 is formed on the right side of the front end of the peripheral wall 131 . In this way, since the first arm 132 and the second arm 133 protrude toward the front of the moving body 13a, a recess is formed between the first arm 132 and the second arm 133 by the front end surfaces of the first arm 132, the second arm 133 and the peripheral wall 131. 134. A first pulling point 132 a is set on the first arm 132 , and a second pulling point 133 a is set on the second arm 133 . The first pull point 132a and the second pull point 133a also function as pin holes through which the third pin 47c is inserted.

As shown in FIG. 7 , the first arm 132 and the second arm 133 are formed in a symmetrical shape and arranged to straddle the drive axis O. As shown in FIG. More specifically, the first arm 132 and the second arm 133 are disposed across an imaginary plane X determined by the drive axis O, the top dead center position of the swash plate 5, and the bottom dead center position of the swash plate 5, and are mutually arranged. opposite. Thereby, also in the mobile body 13a, the 1st pulling point 132a and the 2nd pulling point 133a are arrange|positioned so that they may straddle the virtual plane X, respectively. In addition, for convenience of description in FIG. 7 , the shapes of the first arm 132 , the second arm 133 , etc. are shown in simplified illustration.

As shown in FIG. 1 , the partition body 13b is formed in a disc shape having substantially the same inner diameter as the moving body 13a. A second return spring 44b is provided between the dividing body 13b and the annular plate 45 . Specifically, the rear end of the second return spring 44 b is fixed to the partition body 13 b, and the front end of the second return spring 44 b is fixed to the other end side of the annular plate 45 .

The first small-diameter portion 30a of the drive shaft main body 30 is inserted through the moving body 13a and the partition body 13b. Thereby, the moving body 13 a is assembled to the drive shaft main body 30 in a state capable of being housed in the first concave portion 212 , and is arranged in a state facing the link mechanism 7 with the swash plate 5 interposed therebetween. On the other hand, the partition body 13b is arranged behind the swash plate 5 and inside the moving body 13a, and is surrounded by the surrounding wall 131 . Thereby, the control pressure chamber 13c is formed between the moving body 13a and the partition body 13b. The control pressure chamber 13c is partitioned from the swash plate chamber 33 by the rear wall 130, the peripheral wall 131, and the partition body 13b of the moving body 13a.

In this compressor, the movable body 13 a can rotate together with the drive shaft 3 and move in the direction of the drive axis O of the drive shaft 3 in the swash plate chamber 33 by inserting the first small-diameter portion 30 a. On the other hand, the partition body 13b is being fixed to the 1st small diameter part 30a in the state penetrated by the 1st small diameter part 30a. Thereby, the partition body 13b can only rotate together with the drive shaft 3, and cannot move like the moving body 13a. In this way, when the moving body 13a moves in the direction of the drive axis O, it relatively moves with respect to the partition body 13b. In addition, the partition body 13b may be provided on the drive shaft main body 30 so as to be movable in the direction of the drive shaft center O. As shown in FIG.

Here, as shown in FIG. 3 , a first virtual area S1 and a second virtual area S2 are set in the swash plate chamber 33 . The first imaginary area S1 is defined by the first tangent line L1 drawn from the drive axis O to the second rear cylinder hole 21b side of the first rear cylinder bore 21a, and the first tangent line L1 drawn from the drive axis O to the second rear cylinder bore 21b. The first rear side cylinder bore 21a side in the bore 21b is divided by the drawn second tangent line L2. The second imaginary area S2 is formed by the third tangent line L3 drawn from the drive axis O to the third rear cylinder hole 21c side of the second rear cylinder bore 21b, and the third rear cylinder bore L3 drawn from the drive axis O to the third rear cylinder bore. The second rear side cylinder bore 21b side in 21c is divided by a drawn fourth tangent line L4.

In this compressor, when the moving body 13a is assembled to the drive shaft main body 30, the first arm 132 is located in the first imaginary area S1, and the second arm 133 is located in the second imaginary area S2. The first arm 132 and the second arm 133 . In addition, for convenience of description in FIG. 3 , the shapes of the first arm 132 and the second arm 133 are shown in simplified illustration.

As shown in FIG. 1, the first arm 132, the second arm 133, and the swash plate 5 are connected by a third pin 47c. Specifically, the first arm 132 and the second arm 133 are connected to the pulled portion 45c by one third pin 47c while fitting the pulled portion 45c shown in FIG. 4 into the concave portion 134 of the moving body 13a. Accordingly, the coupling mechanism 14 is arranged on the side opposite to the above-mentioned first pin 47 a with respect to the drive shaft 3 , that is, the drive shaft center O. As shown in FIG.

The third pin 47c passes through the pin hole 450 of the pulled portion 45c from the side of the first pulling point 132a in a direction perpendicular to the driving axis O and extends to the second pulling point 133a. Thereby, as shown in FIG. 1 , the swash plate 5 is supported by the movable body 13 a so as to be swingable around the operating axis M3 with the axis of the third pin 47 c as the operating axis M3 . The action axis M3 extends parallel to the first swing axis M1 and the second swing axis M2. In this way, the moving body 13a is in a state connected to the swash plate 5 .

In addition, in the first small-diameter portion 30a, an axial path 3a extending from the rear end toward the front in the direction of the drive axis O, and a shaft path 3a extending in the radial direction from the front end of the axial path 3a and opening on the outer peripheral surface of the drive shaft main body 30 are formed. Route 3b. The rear end of the shaft path 3 a is opened in the pressure adjustment chamber 31 . On the other hand, the path 3b is opened in the control pressure chamber 13c. Thereby, the control pressure chamber 13c communicates with the pressure adjustment chamber 31 through the path 3b and the axial path 3a.

A screw portion 3 d is formed at the front end of the drive shaft main body 30 . The drive shaft 3 is connected to an unillustrated pulley or an electromagnetic clutch via the threaded portion 3d.

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, a shaft passage 3a, and a passage 3b.

The low-pressure passage 15a is connected to the pressure adjustment chamber 31 and the first suction chamber 27a. The control pressure chamber 13c, the pressure adjustment chamber 31, and the first suction chamber 27a communicate through the low-pressure passage 15a, the shaft passage 3a, and the passage 3b. The high-pressure passage 15b is connected to the pressure adjustment chamber 31 and the first discharge chamber 29a. The control pressure chamber 13c, the pressure adjustment chamber 31, and the first discharge chamber 29a communicate through the high-pressure passage 15b, the shaft passage 3a, and the passage 3b. In addition, an orifice 15d is provided in the high-pressure passage 15b.

The control valve 15c is provided in the low-pressure passage 15a. The control valve 15c can adjust the opening degree of the low-pressure passage 15a based on the pressure in the first suction chamber 27a.

In this compressor, a pipe leading to the evaporator is connected to the suction hole 330 shown in FIG. 1 , and a pipe leading to the condenser is connected to the discharge hole 160 . The condenser is connected to the evaporator through piping and an expansion valve. The compressor, evaporator, expansion valve, condenser, and the like constitute a refrigeration circuit of the vehicle air conditioner. In addition, illustration of an evaporator, an expansion valve, a condenser, and each piping is omitted.

In the compressor configured as above, when the drive shaft 3 rotates, the swash plate 5 rotates, and the pistons 9 reciprocate in the first to fifth rear cylinder holes 21a to 21e and the first to fifth front cylinder holes 23a. sports. Therefore, the volumes of the first compression chamber 210 and the second compression chamber 230 change according to the stroke of the piston. Therefore, in this compressor, the suction process of sucking the refrigerant gas into the first compression chamber 210 and the second compression chamber 230 and the compression process of compressing the refrigerant gas in the first compression chamber 210 and the second compression chamber 230 are repeated. , and the discharge stroke of discharging the compressed refrigerant gas to the first discharge chamber 29a and the second discharge chamber 29b, and the like.

The refrigerant gas discharged into the first discharge chamber 29 a reaches the confluence discharge chamber 161 through the first discharge communication passage 18 . Similarly, the refrigerant gas discharged into the second discharge chamber 29 b reaches the confluence discharge chamber 161 via the second discharge communication passage 20 . And, the refrigerant gas that has reached the confluence discharge chamber 161 is discharged to the condenser through the discharge hole 160 .

Also, during the suction stroke and the like described above, a piston compression force that reduces the inclination angle of the swash plate 5 acts on the rotating body composed of the swash plate 5, the ring plate 45, the cantilever 49, and the first pin 47a. Furthermore, if the inclination angle of the swash plate 5 is changed, the displacement can be controlled by increasing or decreasing the stroke of the piston 9 .

Specifically, in the control mechanism 15, if the control valve 15c shown in FIG. The pressure in the pressure chamber 13c is substantially equal to the pressure in the first suction chamber 27a. Therefore, the moving body 13 a moves toward the front side of the swash plate chamber 33 in the actuator 13 as shown in FIG. 5 by the piston compression force acting on the swash plate 5 .

Thus, in this compressor, at the working axis M3, the moving body 13a becomes the other end side of the swash plate 5 through the first pulling point 132a and the second pulling point 133a of the first arm 132 and the second arm 133. The state of being pressed toward the front side of the swash plate chamber 33 . Therefore, in this compressor, the other end side of the annular plate 45, that is, the other end side of the swash plate 5, oscillates clockwise around the action axis M3 against the biasing force of the second return spring 44b. In addition, the rear end of the cantilever 49 swings counterclockwise around the first swing axis M1 , and the front end of the cantilever 49 swings counterclockwise around the second swing axis M2 . Therefore, the cantilever 49 approaches the flange 433 of the second support member 43b. As a result, the swash plate 5 swings with the action axis M3 as the action point and the first swing axis M1 as the fulcrum. Therefore, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the drive axis O of the drive shaft 3 decreases, and the stroke of the piston 9 decreases. Therefore, in this compressor, the discharge capacity per revolution of the drive shaft 3 becomes small. In addition, the inclination angle of the swash plate 5 shown in FIG. 5 is the smallest value in this compressor.

Here, in this compressor, the centrifugal force acting on the weight portion 49 a is also applied to the swash plate 5 . Therefore, in this compressor, the swash plate 5 is easily displaced in a direction to decrease the inclination angle.

In addition, as the inclination angle of the swash plate 5 decreases, the annular plate 45 comes into contact with the rear end of the first return spring 44a. Accordingly, the first return spring 44a is elastically deformed, and the rear end of the first return spring 44a approaches the second support member 43b.

Here, in this compressor, the inclination angle of the swash plate 5 becomes smaller, the stroke of the piston 9 is reduced, and the top dead center position of the first head portion 9 a is separated from the first valve forming plate 39 . Therefore, in this compressor, the inclination angle of the swash plate 5 is close to zero, and the compression operation is slightly performed on the second compression chamber 230 side, while no compression operation is performed on the first compression chamber 210 side.

On the other hand, if the control valve 15c shown in FIG. 2 reduces the opening of the low-pressure passage 15a, the pressure in the pressure adjustment chamber 31 rises due to the pressure of the refrigerant gas in the first discharge chamber 29a, and the control pressure chamber 13c internal pressure rises. Therefore, against the piston compression force acting on the swash plate 5 , in the actuator 13 , the moving body 13 a moves toward the rear side of the swash plate chamber 33 as shown in FIG. 1 .

Thus, in this compressor, at the working axis M3, the moving body 13a passes the first traction point 132a and the second traction point 133a of the first arm 132 and the second arm 133 to move the other end of the swash plate 5 sideways. The rear side of the ramp chamber 33 is towed. Therefore, in this compressor, the other end side of the swash plate 5 swings counterclockwise around the operating axis M3. In addition, the rear end of the cantilever 49 swings clockwise around the first swing axis M1 , and the front end of the cantilever 49 swings clockwise around the second swing axis M2 . Therefore, the cantilever 49 is separated from the flange 433 of the second support member 43b. As a result, the swash plate 5 swings in a direction opposite to the above-mentioned case where the inclination angle decreases, using the operating axis M3 and the first swinging axis M1 as an operating point and a fulcrum, respectively. Therefore, the inclination angle of the swash plate 5 with respect to the direction perpendicular to the drive axis O of the drive shaft 3 increases, and the stroke of the piston 9 increases. Therefore, in this compressor, the discharge capacity per revolution of the drive shaft 3 increases. In addition, the inclination angle of the swash plate 5 shown in FIG. 1 is the maximum value in this compressor. In addition, in the state where the inclination angle of the swash plate 5 is at the maximum value, the rear wall 130 of the moving body 13 a comes into contact with the first flange 430 .

Thus, in this compressor, when the inclination angle of the swash plate 5 is increased, the moving body 13a pulls the swash plate 5 by the first pulling point 132a and the second pulling point 133a of the first arm 132 and the second arm 133 . In other words, in this compressor, when the swash plate 5 is displaced in a direction to increase the inclination angle, the movable body 13a moves away from the swash plate 5 . Therefore, in this compressor, even if the rear wall 130 and the peripheral wall 131 are enlarged to securely increase the discharge capacity by controlling the pressure rise of the pressure chamber 13c, interference between the peripheral wall 131 and the swash plate 5 does not occur. Accordingly, in this compressor, the rear wall 130 and the peripheral wall 131 of the movable body 13a can be enlarged in size, while suppressing the increase in size of the swash plate chamber 33 .

Furthermore, in this compressor, the coupling mechanism 14 has a first arm 132 and a second arm 133 . A first traction point 132 a for imparting traction to the swash plate 5 is set in the first arm 132 , and a second traction point 133 a for imparting traction to the swash plate 5 is set in the second arm 133 . Here, when the inclination angle is increased by pulling the swash plate 5 , it is less affected by compression reaction force and suction reaction force than when the inclination angle is increased by pushing the swash plate 5 . Therefore, in this compressor, when increasing the inclination angle of the swash plate 5, a large traction force is not required.

In addition, in this compressor, the first arm 132 and the second arm 133 are set to straddle an imaginary plane determined by the drive axis O, the top dead center position of the swash plate 5, and the bottom dead center position of the swash plate 5. X. A first pulling point 132 a and a second pulling point 133 a are respectively set on the first arm 132 and the second arm 133 . Furthermore, the first arm 132 and the second arm 133 can apply traction force at two positions of the first traction point 132a and the second traction point 133a. Therefore, in this compressor, compared with the case where, for example, the link mechanism 14 has only a single arm, the traction forces respectively given to the swash plate 5 by the first arm 132 and the second arm 133 can be reduced. In addition, in this compressor, when the inclination angle of the swash plate 5 is reduced, the movable body 13a pushes the swash plate 5 through the first arm 132 and the second arm 133, but the pressing force at this time is not very large. This is because a centrifugal force acts on the rotating body including the swash plate 5 and the moving body 13a in a direction to decrease the inclination angle.

Accordingly, in this compressor, as described above, even when the rear wall 130 and the peripheral wall 131 are enlarged, the rigidity of the first arm 132 and the second arm 133 required thereby can be reduced. Therefore, in this compressor, the increase in size of the first arm 132 and the second arm 133 , that is, the increase in size of the coupling mechanism 14 can be suppressed.

In addition, in this compressor, a first virtual area S1 and a second virtual area S2 are set for the swash plate chamber 33 . Furthermore, when the moving body 13a is assembled to the drive shaft main body 30, the first arm 132 is located in the first virtual area S1, and the second arm 133 is located in the second virtual area S2. Therefore, in this compressor, the first arm 132 and the second arm 133 do not reciprocate in the first to fifth rear cylinder bores 21a to 21e and in the first to fifth front cylinder bores 23a. The obstruction of piston 9. Thereby, the first arm 132 and the second arm 133 can be arranged close to the first to fifth rear cylinder holes 21a to 21e and the first to fifth front cylinder holes 23a, that is, the first arm 132 And the second arm 133 is disposed close to each piston 9 .

Therefore, according to the compressor of the embodiment, it is possible to realize high controllability and miniaturization in the compressor in which the displacement is changed by the actuator 13 .

In particular, in this compressor, the swash plate 5 is provided with a drawn portion 45 c protruding between the first arm 132 and the second arm 133 . Then, the first arm 132 and the second arm 133 are connected to the swash plate 5 while the pulled portion 45c is fitted into the concave portion 134 of the moving body 13a. Accordingly, in this compressor, when the movable body 13a rotates together with the drive shaft 3 , a driving force is transmitted between the first arm 132 and the second arm 133 and the drawn portion 45c. Therefore, in this compressor, the moving body 13 a stably rotates together with the drive shaft 3 , and the swash plate 5 also stably rotates together with the moving body 13 a , thereby stably rotating together with the drive shaft 3 .

In addition, a third pin 47 c extending in a direction perpendicular to the drive axis O is inserted through the first arm 132 , the pulled portion 45 c , and the second arm 133 . Therefore, in this compressor, the first arm 132, the drawn portion 45c, and the second arm 133 can be easily connected. In addition, for example, compared with the case where the first arm 132 and the pulled portion 45c are connected to the second arm 133 and the pulled portion 45c with different pins, the number of parts can be reduced, and manufacturing can be facilitated. In addition, in this compressor, it is difficult to remove the third pin 47c from the first arm 132, the second arm 133, and the drawn portion 45c, thereby improving reliability.

As mentioned above, although this invention was demonstrated using an Example, this invention is not limited to the said Example, Of course, it can change suitably and apply in the range which does not deviate from the summary.

For example, a cylinder hole may be formed only in either the first cylinder 21 or the second cylinder 23 to form a capacity-variable single-head swash plate compressor.

In addition, the control valve 15c may be provided for the control mechanism 15 and the high-pressure passage 15b, and the orifice 15d may be provided in the low-pressure passage 15a. At this time, the opening degree of the high-pressure passage 15b can be adjusted by the control valve 15c. Thereby, the pressure of the refrigerant gas in the first discharge chamber 29a can be used to quickly increase the pressure of the control pressure chamber 13c, and the discharge capacity can be rapidly increased.

Industrial feasibility

The present invention can be utilized in air conditioners and the like.

Explanation of reference signs:

1...housing; 3...drive shaft; 5...swash plate; 7...link mechanism; 9...piston; 11a, 11b...slider (conversion mechanism); 13...actuator; 13a...moving body; Body; 13c...control pressure chamber; 14...connecting mechanism; 15...control mechanism; 21a...first rear cylinder hole (first cylinder hole); 21b...second rear cylinder hole (second cylinder hole); 21c... 3rd rear cylinder hole (third cylinder hole); 27a...first suction chamber; 27b...second suction chamber; 29a...first discharge chamber; 29b...second discharge chamber; 33...swash plate chamber; 45c...drawn 47a...the first pin (joint); 47c...the third pin (pin); 132...the first arm; 133...the second arm; 210...the first compression chamber; 230...the second compression chamber; L1...the first Tangent line; L2...second tangent line; L3...third tangent line; L4...fourth tangent line; O...drive axis; S1...first imaginary area; S2...second imaginary area.

Claims (4)

1. a kind of capacity variable type tilted-plate compressor, it is characterised in that possess：

Housing, is formed with suction chamber, discharges room, swash plate room and at least one cylinder holes in the housing；

Drive shaft, which extends and can rotatably be supported on the housing along driving axle center；

Swash plate, which can be rotated in the swash plate room by the rotation of the drive shaft；

Linkage, which is arranged between the drive shaft and the swash plate, and allow the swash plate relative to the driving The change at the angle of inclination in the orthogonal direction in the driving axle center of axle；

Piston, which can reciprocally be accommodated in the cylinder holes；

Shifter, its rotation by the swash plate and the piston is made described with stroke corresponding with the angle of inclination Move back and forth in cylinder holes；And

Actuator, which is configured in the swash plate room, and can change the angle of inclination；And

Controlling organization, its described actuator of control,

The suction chamber is connected with the swash plate room,

The actuator has：

Division body, which is arranged at the drive shaft；

Moving body, its via link mechanism links with the swash plate, and along it is described driving axis direction move and can be relative Move in the division body；And

Control pressure chamber, which is divided with the moving body by the division body, and by importing the cold-producing medium from the discharge room And the moving body movement is made,

The moving body is configured to improve the pressure in the control pressure chamber, and draws the swash plate and described incline to increase Rake angle,

The linkage with the linking part linked with the swash plate,

The link mechanism has the first arm and the second arm, first arm and the second arm relative to by the drive shaft The imaginary plane that the bottom dead center position of the heart, the top dead center position of the swash plate and the swash plate is determined is configured at and the link The contrary side in portion, and the moving body is arranged at across the driving axle center.

2. capacity variable type tilted-plate compressor according to claim 1, it is characterised in that

At least one cylinder holes is at least the first cylinder holes, the second cylinder holes and the 3rd cylinder holes,

First cylinder holes, second cylinder holes and the 3rd cylinder holes are equiangularly spaced in the housing and are configured to institute State drive axle center centered on concentric circles,

The first imaginary area and the second imaginary area are set with the swash plate room, first imaginary area is by from the driving Axle center is to derivative first tangent line in the second cylinder holes side in first cylinder holes and from the driving axle center to described Derivative second tangent line in the first cylinder holes side in two cylinder holes is divided, and second imaginary area is by from the driving axle center To derivative 3rd tangent line in the 3rd cylinder holes side in second cylinder holes and from the driving axle center to the triplex Derivative 4th tangent line in the second cylinder holes side in hole is divided,

First arm is located in first imaginary area, and second arm is located in second imaginary area.

3. capacity variable type tilted-plate compressor according to claim 1 and 2, it is characterised in that

Arrange prominent by tractive unit between oriented first arm and second arm in the swash plate,

Described transmitted in first arm and second arm and between tractive unit driving force.

4. capacity variable type tilted-plate compressor according to claim 3, it is characterised in that

In first arm, described by tractive unit and second arm insert has The pin stretched.