JP2017166336A - Variable displacement swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor capable of developing high controllability.SOLUTION: The compressor includes a housing 1 in which a first suction chamber 27a, a second suction chamber 27b, a first discharge chamber 29a, and a second discharge chamber 29b are formed. The compressor further includes a control pressure chamber 13c, and a control mechanism 15. The control mechanism 15 has a control path 55 communicated with the control pressure chamber 13c, a first passage 59a communicating the control path 55 with the first discharge chamber 29a, and a second passage 59b communicating the control path 55 with the second suction chamber 27b. The control mechanism 15 also has a control valve 24a capable of changing the opening of the second passage 59b, and a restriction passage 20 as a restriction for restricting the opening of the first passage 59a.SELECTED DRAWING: Figure 1

Description

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

  Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter simply referred to as a compressor). The compressor includes a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a partition body, a moving body, a control pressure chamber, and a control mechanism. The housing includes a front housing, a rear housing, and a cylinder block. The front housing is disposed on one side of the swash plate, and has a first suction chamber and a first discharge chamber. The rear housing is disposed on the other side of the swash plate, and a second suction chamber, a second discharge chamber, and a pressure adjustment chamber are formed. The cylinder block is disposed between the front housing and the rear housing. The cylinder block has a plurality of first cylinder bores communicating with the first suction chamber and the first discharge chamber and a plurality of second cylinder bores communicating with the second suction chamber and the second discharge chamber. A board chamber is formed.

  The drive shaft is rotatably supported on the housing. The swash plate is provided in the swash plate chamber and can be rotated by rotation of the drive shaft. The link mechanism is provided between the drive shaft and the swash plate, and allows the inclination angle of the swash plate to be changed. Here, the inclination angle is an angle of the swash plate with respect to a direction orthogonal to the rotation axis of the drive shaft. Each piston has a first head and a second head. The first head reciprocates in the first cylinder bore to partition the first compression chamber in the first cylinder bore. The second head reciprocates in the second cylinder bore to partition the second compression chamber in the second cylinder bore. A shoe as a conversion mechanism is provided between each piston and the swash plate. The shoe makes a pair for each piston, and reciprocates each piston with a stroke corresponding to the inclination angle by the rotation of the swash plate. The partition is provided on the drive shaft, and can rotate integrally with the drive shaft in the swash plate chamber. The moving body is provided on the drive shaft, can rotate integrally with the drive shaft in the swash plate chamber, and moves in the direction of the rotation axis to change the tilt angle. The control pressure chamber is partitioned by a partition body and a moving body, and moves the moving body by an internal pressure.

  The control mechanism has a control path, an air supply path, an extraction path, a control valve, and an orifice. The control path is formed inside the drive shaft and communicates with the control pressure chamber and the pressure adjustment chamber. The air supply path communicates with the second discharge chamber and the pressure adjustment chamber. The extraction passage communicates with the second suction chamber and the pressure adjustment chamber. The control valve can change its opening degree by the pressure in the second suction chamber. The orifice is provided in the bleed passage. The control mechanism controls the pressure in the control pressure chamber by controlling the pressure in the pressure adjustment chamber.

  In this compressor, if the control valve of the control mechanism increases its own opening, the pressure in the pressure adjustment chamber increases due to the pressure in the second discharge chamber. For this reason, the pressure of the control pressure chamber increases, and the moving body moves in the direction of the rotation axis so as to move away from the partitioning body. Thereby, the link mechanism increases the inclination angle of the swash plate. Thus, in this compressor, the discharge capacity per rotation of the drive shaft increases. On the other hand, if the control valve reduces its own opening, the pressure in the pressure adjustment chamber decreases, so the pressure in the control pressure chamber also decreases. Thereby, since a mobile body moves so that a division body may be approached, a link mechanism reduces the inclination-angle of a swash plate. Thus, in this compressor, the discharge capacity per rotation of the drive shaft is reduced.

JP 2014-92104 A

  This type of compressor is required to have high controllability that can quickly increase or decrease the discharge capacity as needed. In this regard, in the above-described conventional compressor, the control pressure chamber communicates with the second suction chamber and the second discharge chamber via the pressure adjustment chamber. Therefore, when the discharge capacity is increased or decreased, the pressure in the pressure adjustment chamber is reduced. Need to control. For this reason, in this compressor, when the control valve changes the opening, a delay is likely to occur until the discharge capacity is increased or decreased.

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

The capacity variable swash plate compressor of the present invention includes a suction chamber, a discharge chamber, a swash plate chamber and a housing in which a plurality of cylinder bores are formed,
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the rotational axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the rotational axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
The suction chamber comprises a first suction chamber located on one side of the swash plate and a second suction chamber located on the other side of the swash plate,
The discharge chamber is composed of a first discharge chamber located on the one surface side of the swash plate and a second discharge chamber located on the other surface side of the swash plate,
The cylinder bores are provided on the one surface side of the swash plate, provided on the other surface side of the swash plate, a first cylinder bore communicating with the first suction chamber and the first discharge chamber, and the second A second cylinder bore communicating with the suction chamber and the second discharge chamber;
Each piston reciprocates within the first cylinder bore, reciprocates within the first cylinder bore and a first head that defines a first compression chamber, and the second cylinder bore, and the second cylinder bore. A second head that defines a second compression chamber therein,
The control mechanism is formed inside the drive shaft and communicates with the control pressure chamber;
A first passage formed in at least one of the housing and the drive shaft and communicating the control path with the first discharge chamber or the first suction chamber;
If formed in at least one of the housing and the drive shaft, and the first passage communicates with the first discharge chamber, the control passage communicates with the second suction chamber, and the first passage communicates with the first suction chamber. A second passage for communicating the control path with the second discharge chamber if communicating with the second discharge chamber;
A control valve provided in one of the first and second passages and capable of changing an opening of the one passage;
Provided in a passage on the other side of the first passage and the second passage, and has a throttle for restricting the opening of the other passage or the control valve capable of changing the opening of the other passage. It is characterized by that.

  In the compressor according to the present invention, when the first passage communicates the control path with the first discharge chamber, the second passage communicates the control path with the second suction chamber. As a result, the refrigerant in the first discharge chamber that has passed through the first passage and the control passage is directly introduced into the control pressure chamber, and the refrigerant in the control pressure chamber is directly led out to the second suction chamber through the control passage and the second passage. Is done. In addition, if the first passage communicates the control path with the first suction chamber, the second passage communicates the control path with the second discharge chamber. As a result, the refrigerant in the second discharge chamber that has passed through the second passage and the control passage is directly introduced into the control pressure chamber, and the refrigerant in the control pressure chamber is directly led out to the first suction chamber through the control passage and the first passage. Is done. A control valve is provided in one of the first passage and the second passage, and a throttle or control valve is provided in the other passage of the first passage and the second passage. Thereby, the flow rate of the refrigerant introduced into the control pressure chamber and the flow rate of the refrigerant led out to the second suction chamber are adjusted. Thus, in this compressor, the pressure in the control pressure chamber is adjusted.

  Thus, in this compressor, the control pressure chamber communicates with the first suction chamber and the second discharge chamber via the pressure adjustment chamber, or the control pressure chamber communicates with the second suction chamber and the first discharge chamber via the pressure adjustment chamber. The pressure in the control pressure chamber can be quickly adjusted as compared with the case of communicating with the control pressure chamber. For this reason, in this compressor, since a moving body can change the inclination-angle of a swash plate quickly as needed, discharge capacity can be increased / decreased rapidly.

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

  In the compressor of the present invention, the first passage can communicate the control path with the first discharge chamber. The second passage can connect the control path to the second suction chamber. Furthermore, a control valve can be provided in the second passage. The first passage can be provided with a throttle. The control path includes an air supply path for the refrigerant in the first discharge chamber to reach the control pressure chamber, an air extraction path for the refrigerant in the control pressure chamber to the second suction chamber, and a partition that separates the air supply path and the air extraction path. And are preferably formed.

  In this case, when adjusting the pressure in the control pressure chamber, the control valve increases the opening of the second passage, whereby the pressure in the control pressure chamber can be quickly reduced. Further, by forming the partition wall in the control path, it is possible to prevent the refrigerant flowing through the air supply path from flowing into the extraction path without reaching the control pressure chamber. For these reasons, in this compressor, the pressure in the control pressure chamber can be suitably adjusted, and the discharge capacity can be suitably increased or decreased. Further, in this compressor, by providing the throttle in the first passage, the manufacturing cost can be reduced as compared with the case where the control valves are provided in both the first passage and the second passage.

  In the compressor of the present invention, the first passage can connect the control path to the first suction chamber. Further, the second passage can connect the control path to the second discharge chamber. The control valve can be provided in the second passage. Furthermore, a throttle can be provided in the first passage. The control path includes an air supply path for the refrigerant in the second discharge chamber to reach the control pressure chamber, an air extraction path for the refrigerant in the control pressure chamber to the first suction chamber, and a partition that separates the air supply path and the air extraction path. It is also preferable that these are formed.

  In this case, when adjusting the pressure in the control pressure chamber, the control valve increases the opening of the second passage, so that the pressure in the control pressure chamber can be quickly increased. Further, the partition wall can prevent the refrigerant flowing through the air supply path from flowing into the extraction path without reaching the control pressure chamber. For these reasons, even in this compressor, the pressure in the control pressure chamber can be suitably adjusted, and the discharge capacity can be suitably increased or decreased. Further, even in this compressor, it is possible to reduce the manufacturing cost as compared with the case where the control valves are provided in both the first passage and the second passage.

  In this case, the first discharge chamber can be disposed on the outer periphery of the first suction chamber. Further, the drive shaft can be inserted into the first suction chamber. The diaphragm is preferably provided on the drive shaft. Thereby, it is possible to easily provide a restriction in the first passage. Here, in the configuration in which the first discharge chamber is arranged on the outer periphery of the first suction chamber, when the first passage communicates the control path with the first discharge chamber, the refrigerant flowing from the first discharge chamber to the control path is the first. 1 A sealing member for preventing inflow into the suction chamber or the like is required. In this respect, in this compression chamber, the first passage communicates the control path with the first suction chamber, and the drive shaft is inserted into the first suction chamber, so that the sealing member as described above is unnecessary. For these reasons, the compressor can be easily manufactured.

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

FIG. 1 is a cross-sectional view showing a state where the inclination angle is minimum in the compressor of the first embodiment. FIG. 2 is a cross-sectional view showing a state where the inclination angle is maximum in the compressor of the first embodiment. FIG. 3 is a schematic diagram illustrating a control mechanism according to the compressor of the first embodiment. FIG. 4 is a cross-sectional view illustrating the AA cross section in FIG. 1 illustrating the housing according to the compressor of the first embodiment. FIG. 5 is an enlarged cross-sectional view of a main part illustrating the first passage and the like according to the compressor of the first embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating an air supply path, a bleed air path, a partition wall, and the like according to the compressor of the first embodiment. FIG. 7 is a schematic diagram illustrating a control mechanism according to the compressor of the comparative example. FIG. 8 is a cross-sectional view showing a state where the inclination angle is minimum in the compressor of the second embodiment. FIG. 9 is a schematic diagram illustrating a control mechanism according to the compressor of the second embodiment. FIG. 10 is an enlarged cross-sectional view of a main part illustrating a first passage and the like according to the compressor of the second embodiment.

  Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings. All of these compressors are mounted on a vehicle, and constitute a refrigeration circuit of a vehicle air conditioner.

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

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

  The front housing 17 is formed with a boss 17a protruding forward and a first shaft hole 17b through which the drive shaft 3 is inserted. A shaft seal device 25 is provided in the boss 17a.

  In the front housing 17, a first communication chamber 18a, a first suction chamber 27a, a first discharge chamber 29a, and a wall portion 17c are formed. The first communication chamber 18 a is recessed in a columnar shape from the rear end surface 17 d of the front housing 17 toward the front, and is located on the center side of the front housing 17.

  The first suction chamber 27a is recessed in an annular shape from the rear end surface 17d of the front housing 17 toward the front, and is disposed on the outer peripheral side of the first communication chamber 18a as shown in FIG. The first discharge chamber 29a is also recessed in an annular shape from the rear end surface 17d of the front housing 17 toward the front, and is disposed on the outer peripheral side of the first suction chamber 27a. The wall portion 17c is located in the first suction chamber 27a and extends in the vertical direction. A throttle passage 20 is formed in the wall portion 17c so as to vertically penetrate the wall portion 17c. Through the throttle passage 20, the first communication chamber 18a and the first discharge chamber 29a communicate with each other. The throttle passage 20 is an example of a throttle in the present invention.

  As shown in FIGS. 1 and 2, the front housing 17 is formed with a first front communication path 12 a. The first front communication passage 12 a has a front end communicating with the first discharge chamber 29 a and a rear end opening on the rear end surface 17 d of the front housing 17.

  In the second housing 19, a second communication chamber 18b, a second suction chamber 27b, and a second discharge chamber 29b are formed. The second communication chamber 18 b is recessed in a columnar shape from the front end surface 19 a of the rear housing 19 to the rear, and is located on the center side of the rear housing 19. The size and the like of the first communication chamber 18a and the second communication chamber 18b can be appropriately designed.

  The second suction chamber 27b and the second discharge chamber 29b are also recessed in an annular shape from the front end surface 19a of the rear housing 19 to the rear. The second suction chamber 27b is disposed on the outer peripheral side of the second communication chamber 18b. The second discharge chamber 29b is disposed on the outer peripheral side of the second suction chamber 27b.

  The rear housing 19 is provided with a bleed passage 22 and a control valve 24a. The bleed passage 22 includes a first bleed passage 22a and a second bleed passage 22b. The first bleed passage 22a is connected to the second suction chamber 27b and the control valve 24a. The second bleed passage 22b is connected to the control valve 24a and the second communication chamber 18b. The control valve 24a can change the opening degree of the extraction passage 22 by changing its own opening degree based on the pressure in the second suction chamber 27b.

  Further, the rear housing 19 is formed with a first rear communication path 14a. The first rear communication passage 14 a has a rear end communicating with the second discharge chamber 29 b and a front end opening on the front end surface 19 a of the rear housing 19.

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

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

  The first cylinder block 21 is formed with a first communication path 37a and a second front side communication path 12b extending in the front-rear direction. Each of the first communication path 37a and the second front communication path 12b has a front end opened to the front end face 21d of the first cylinder block 21 and a rear end opened to the rear end face 21e of the first cylinder block 21. ing.

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

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

  The second cylinder block 23 is formed with a third shaft hole 23b through which the drive shaft 3 is inserted. Although not shown, sliding bearings are provided in the first shaft hole 17b, the second shaft hole 21b, and the third shaft hole 23b, respectively.

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

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

  Further, the second cylinder block 23 is formed with a discharge port 230, a merged discharge chamber 231, a third front side communication path 12c, and a second rear side communication path 14b. The discharge port 230 and the merged discharge chamber 231 communicate with each other. The merged discharge chamber 231 is connected to a condenser (not shown) that forms a pipe line via a discharge port 230.

  The third front communication path 12c has a front end that opens to the front end surface 23e of the second cylinder block 23, and a rear end that communicates with the merged discharge chamber 231. The third front communication path 12c communicates with the second front communication path 12b by joining the first cylinder block 21 and the second cylinder block 23 together. The second rear communication passage 14 b has a front end communicating with the merged discharge chamber 231 and a rear end opening on the rear end surface 23 d of the second cylinder block 23.

  As shown in FIG. 5, the first valve forming plate 39 is provided between the rear end surface 17 d of the front housing 17 and the front end surface 21 d of the first cylinder block 21. The front housing 17 and the first cylinder block 21 are joined via the first valve forming plate 39.

  The first valve forming plate 39 includes a valve plate 390, a suction valve plate 391, a discharge valve plate 392, and a retainer plate 393. The valve plate 390, the discharge valve plate 392, and the retainer plate 393 are formed with the same number of first suction holes 390a as the first cylinder bores 21a. The valve plate 390 and the intake valve plate 391 are formed with the same number of first discharge holes 390b as the first cylinder bores 21a. Further, the valve plate 390, the suction valve plate 391, the discharge valve plate 392, and the retainer plate 393 are formed with a first suction communication hole 390c and a first discharge communication hole 390d.

  Each first cylinder bore 21a communicates with the first suction chamber 27a through each first suction hole 390a. Each first cylinder bore 21a communicates with the first discharge chamber 29a through each first discharge hole 390b. The first suction chamber 27a and the first communication path 37a communicate with each other through the first suction communication hole 390c. Further, the first front communication path 12a and the second front communication path 12b communicate with each other through the first discharge communication hole 390d.

  The suction valve plate 391 is provided on the rear surface of the valve plate 390. The suction valve plate 391 is formed with a plurality of suction reed valves 391a that can open and close the first suction holes 390a by elastic deformation. The discharge valve plate 392 is provided on the front surface of the valve plate 390. The discharge valve plate 392 is formed with a plurality of discharge reed valves 392a that can open and close each first discharge hole 390b by elastic deformation. The retainer plate 393 is provided on the front surface of the discharge valve plate 392. The retainer plate 393 regulates the maximum opening degree of each discharge reed valve 392a. The first cylinder block 21 is recessed with a retainer 21f that regulates the maximum opening of each suction reed valve 391a. For ease of explanation, illustration of the intake valve plate 391, the discharge valve plate 392, the retainer plate 393, and the retainer groove 21f is omitted in FIGS.

  As shown in FIGS. 1 and 2, the second valve forming plate 41 is provided between the front end surface 19 a of the rear housing 19 and the rear end surface 23 d of the second cylinder block 23. The rear housing 19 and the first cylinder block 23 are joined via the second valve forming plate 41.

  Although not shown in detail, the second valve forming plate 41 includes a valve plate 410 and, similarly to the first valve forming plate 39, includes a suction valve plate, a discharge valve plate, and a retainer plate. Yes. Similarly to the first cylinder block 21, the second cylinder block 23 is also provided with a retainer groove.

  The second valve forming plate 41 is formed with the same number of second suction holes 410a and second discharge holes 410b as the second cylinder bores 23a, and has a second suction communication hole 410c and a second discharge communication hole 410d. Is formed. Each second cylinder bore 23a communicates with the second suction chamber 27b through each second suction hole 410a. Each second cylinder bore 23a communicates with the second discharge chamber 29b through each second discharge hole 410b. The second suction chamber 27b and the second communication path 37b communicate with each other through the second suction communication hole 410c. Further, the first rear communication path 14a and the second rear communication path 14b communicate with each other through the second discharge communication hole 410d.

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

  In this compressor, the first discharge communication passage 12 is formed by the first front communication passage 12a, the first discharge communication hole 390d, the second front communication passage 12b, and the third front communication passage 12c. . Further, a second discharge communication path 14 is formed by the first rear communication path 14a, the second discharge communication hole 410d, and the second rear communication path 14b. The first discharge chamber 29a and the second discharge chamber 29b communicate with each other through the first discharge communication path 12, the second discharge communication path 14, and the merged discharge chamber 231.

  The drive shaft 3 includes a drive shaft main body 30, a first support member 43a, and a second support member 43b. A screw portion 3 a is formed at the front end of the drive shaft 3. The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) via the screw portion 3a. A control path 55 is formed on the drive shaft 3. Details of the control path 55 will be described later.

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

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

  The first support member 43 a is formed in a cylindrical shape with the rotation axis O of the drive shaft 3 as the central axis. The first support member 43 a is press-fitted into the first small diameter portion 30 a of the drive shaft main body 30. A first flange 430 is formed at the rear end of the first support member 43a. As shown in FIG. 5, a first annular groove 431 and a second annular groove 432 are formed on the outer peripheral surface of the first support member 43a. A first sealing member 44 a is provided in the first annular groove 431. A second sealing member 44 b is provided in the second annular groove 432.

  As shown in FIGS. 1 and 2, the second support member 43 b is also formed in a cylindrical shape with the rotation axis O of the drive shaft 3 as the central axis. The second support member 43 b is press-fitted to the rear end side of the second small diameter portion 30 b of the drive shaft main body 30. The second support member 43b is provided with a second flange 433 and an attachment portion (not shown) through which a second pin 47b described later is inserted.

  In the housing 1, the drive shaft 3 includes a shaft sealing device 25, first and second communication chambers 18a and 18b, first to third shaft holes 17b, 21b and 23b, first and second valve forming plates 39 and 41, and a swash plate chamber. 33 and first and second thrust bearings 35a and 35b. As a result, as shown in FIG. 5, in the drive shaft 3, the first support member 43a is inserted into the shaft seal device 25, the first communication chamber 18a, the first valve forming plate 39, and the first thrust bearing 35a. It is supported by the 1 and 2 shaft holes 17b and 21b. The first sealing member 44a is disposed in the first shaft hole 17b, and the second sealing member 44b is disposed in the second shaft hole 21b. Thus, the first and second sealing members 44a and 44b prevent the refrigerant gas in the first communication chamber 18a from leaking outside the first communication chamber 18a such as the swash plate chamber 33.

  On the other hand, as shown in FIGS. 1 and 2, the second support member 43a is supported by the third shaft hole 23b while being inserted through the second thrust bearing 35b and the second valve forming plate 41. The rear end of the drive shaft 3 protrudes into the second communication chamber 18b. Thus, the drive shaft 3 is supported by the housing 1 and can rotate around the rotation axis O parallel to the front-rear direction of the compressor. In addition, when the drive shaft 3 is supported by the housing 1, the first flange 430 sandwiches the first thrust bearing 35a from the axial direction between the first flange 430 and the front wall of the first recess 21c. The second flange 433 sandwiches the second thrust bearing 35b from the axial direction between the second flange 433 and the rear wall of the second recess 23c. Although not shown, a sealing member that seals between the second communication chamber 18b and the swash plate chamber 33 is provided between the second support member 43b and the third bearing 23b.

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

  The swash plate 5 has a ring plate 45. The ring plate 45 is formed in an annular flat plate shape, and an insertion hole 45a is formed at the center. The swash plate 5 is attached to the drive shaft 3 by inserting the drive shaft main body 30 through the insertion hole 45 a in the swash plate chamber 33. Further, the ring plate 45 is formed with a groove portion 45b penetrating from the front surface 5a side to the rear surface 5b side of the swash plate 5. A return spring (not shown) is provided around the drive shaft 3 between the ring plate 45 and the second flange 433 of the second support member 43b.

  The link mechanism 7 has a lug arm 49. The lug arm 49 is disposed behind 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 lug arm 49 is formed so as to be substantially L-shaped from the front to the rear. The lug arm 49 has a weight portion 49a. The shape of the weight portion 49a can be designed as appropriate.

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

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

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

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

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

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

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

  The actuator 13 is disposed in front of the swash plate 5 in the swash plate chamber 33. More specifically, the actuator 13 is located on the first cylinder block 21 side in the swash plate chamber 33 with respect to the swash plate 5. Thereby, the actuator 13 can enter the first recess 21c.

  As shown in FIG. 6, the actuator 13 includes a moving body 13a, a partitioning body 13b, and a control pressure chamber 13c. The control pressure chamber 13c is formed between the movable body 13a and the partition body 13b.

  The moving body 13a includes a front wall 130, a peripheral wall 131, and a pair of connecting arms 132. 1, 2, 6, and 8, only one of the connecting arms 132 is shown.

  As shown in FIG. 6, the front wall 130 is located in front of the moving body 13 a and extends in the radial direction in a direction away from the rotation axis O. Further, an insertion hole 130a is provided in the front wall 130. An O-ring 51a is provided in the insertion hole 130a. The peripheral wall 131 is continuous with the outer peripheral edge of the front wall 130 and extends toward the rear of the movable body 13a. Due to the front wall 130 and the peripheral wall 131, the movable body 13a has a bottomed cylindrical shape. Each connecting arm 132 is formed at the rear end of the peripheral wall 131 and extends from the peripheral wall 131 toward the rear of the compressor. Each connecting arm 132 is formed with an insertion hole 132a through which a third pin 47c described later is inserted.

  The partition body 13b is formed in a substantially disc shape having substantially the same diameter as the inner diameter of the moving body 13a. The partition 13b has an insertion hole 133 extending through the center. An O-ring 51b is provided on the outer periphery of the partition 13b. Further, the partition 13b is formed with a concave surface 134 that is recessed from the front to the rear.

  The drive shaft main body 30 is inserted through the insertion hole 130a of the moving body 13a. Thereby, the moving body 13a can move the drive shaft main body 30 in the direction of the rotation axis O. On the other hand, the drive shaft main body 30 is press-fitted into the insertion hole 133 of the partition 13b. As a result, the partition body 13 b is fixed to the drive shaft main body 30, and the partition body 13 b can rotate together with the drive shaft main body 30. The partition 13b may also be configured to be inserted through the drive shaft main body 30 so as to be movable in the direction of the rotation axis O.

  The partition body 13b is disposed in the moving body 13a and is surrounded by the peripheral wall 131. Thereby, when the moving body 13a moves in the rotation axis O direction, the inner peripheral surface of the peripheral wall 131 and the outer peripheral surface of the partition 13b slide.

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

  As shown in FIGS. 1 and 2, each pulling arm 132 and the ring plate 45 are connected by a third pin 47c. As a result, the swash plate 5 is pivotally connected to the moving body 13a around the third axis M3 with the third pin 47c as the third axis M3. Here, the first pin 47a and the third pin 47c are arranged to face each other with the drive shaft body 30 in between. That is, each traction arm 132 is connected to the ring plate 45 on the side opposite to the groove 45b with the rotation axis O as a reference. In addition, an inclination-decreasing spring (not shown) is provided around the drive shaft 3 between the partition 13b and the ring plate 45.

  The control path 55 includes first and second axial paths 55a and 55b and first and second radial paths 55c and 55d. The first axial path 55 a is formed inside the drive shaft main body 30, and extends from the approximate center of the drive shaft main body 30 in the front-rear direction to the front end side of the drive shaft main body 30 in the axial direction of the drive shaft main body 30. . The second axial path 55 b is also formed in the drive shaft main body 30. The second axial path 55 b is formed to have a larger diameter than the first axial path 55 a and opens on the rear end surface of the drive shaft main body 30. The second axial path 55b is coaxial with the first axial path 55a and extends from the rear end surface of the drive shaft main body 30 to the approximate center in the front-rear direction of the drive shaft main body 30 and is connected to the first axial path 55a. As shown in FIG. 6, a partition wall member 57 is provided in the second axial path 55b. The partition member 57 is disposed at the front end of the second axis 55b, that is, between the first axis 55a and the second axis 55b. The partition member 57 is an example of a partition wall in the present invention. The partition member 57 may be omitted, and the first axial path 55a and the second axial path 55b may be formed to have the same diameter.

  The first path 55 c is formed at the approximate center in the front-rear direction of the drive shaft body 30. The first path 55 c extends in the radial direction of the drive shaft body 30 while being connected to the rear end side of the first axis 55 a, and is open to the outer peripheral surface of the drive shaft body 30. The second path 55d is substantially in the center in the front-rear direction of the drive shaft main body 30, and is formed behind the first path 55c. The second path 55 d extends in the radial direction of the drive shaft body 30 while being connected to the front end side of the second axis 55 b, and is open to the outer peripheral surface of the drive shaft body 30. By providing the actuator 13 on the drive shaft 3 as described above, the first path 55c communicates the first axis 55a and the control pressure chamber 13c. The second path 55d communicates the second axial path 55b and the control pressure chamber 13c.

  As shown in FIG. 5, the drive shaft 3 is formed with a third path 55 e. The third path 55 e is formed on the front end side of the drive shaft 3. The third path 55e extends in the radial direction of the drive shaft main body 30 and the first support member 43a while being connected to the front end side of the first axis 55a, and opens on the outer peripheral surface of the first support member 43a. The third path 55e is located in the first communication chamber 18a by connecting the drive shaft 3 to the housing 1 as described above, and communicates the first communication chamber 18a and the first axis 55a. Yes.

  As shown in FIGS. 1 and 2, in this compressor, the first axial path 55a and the first radial path 55c communicate with the first discharge chamber 29a by the third radial path 55e, the first communication chamber 18a, and the throttle path 20. ing. Further, the second communication passage 18b, the extraction passage 22, and the control valve 24a communicate the second axial passage 55b and the second passage 55d with the second suction chamber 27b. In other words, in this compressor, the third passage 55e, the first communication chamber 18a, and the throttle passage 20 constitute a first passage 59a that communicates the control passage 55 with the first discharge chamber 29a. Further, the second communication chamber 18b, the bleed passage 22 and the control valve 24a constitute a second passage 59b for communicating the control passage 55 with the second suction chamber 27b.

  As shown in FIG. 6, in this compressor, the refrigerant gas in the first discharge chamber 29 a is supplied to the control pressure chamber 13 c by the first axial path 55 a and the first radial path 55 c in the control path 55. An air path 61a is configured. Of the control path 55, the second axial path 55b and the second path 55d constitute an extraction path 61b through which the refrigerant gas in the control pressure chamber 13c reaches the second suction chamber 27b. The air supply path 61a and the extraction path 61b are separated by the partition member 57 described above.

  As shown in FIG. 3, the control mechanism 15 includes a control path 55, a first passage 59a, and a second passage 59b. The control mechanism 15 circulates the first passage 59a and the control passage 55 to introduce the refrigerant gas in the first discharge chamber 29a into the control pressure chamber 13c, and circulates the control passage 55 and the second passage 59b. Then, the refrigerant gas in the control pressure chamber 13c is led out into the second suction chamber 27b. Specifically, the control mechanism 15 causes the refrigerant gas in the first discharge chamber 29a to flow through the throttle passage 20, the first communication chamber 18a, the third passage 55e, the first axial passage 55a, and the first passage 55c. It introduce | transduces in the control pressure chamber 13c. Then, the refrigerant gas in the control pressure chamber 13c is led into the second suction chamber 27b through the second path 55d, the second axial path 55b, the second communication chamber 18b, and the extraction passage 22. At this time, the throttle passage 20 throttles the opening of the first passage 59a, and the control valve 24a changes the opening of the second passage 59b. Thus, the control mechanism 15 controls the pressure in the control pressure chamber 13c. Details of the pressure control in the control pressure chamber 13c by the control mechanism 15 will be described later.

  In this compressor, a pipe connected to the evaporator is connected to the suction port 330 shown in FIGS. 1 and 2, and a pipe connected to the condenser is connected to the discharge port 230. The condenser is connected to the evaporator via a pipe and an expansion valve. These compressors, evaporators, expansion valves, condensers and the like constitute a refrigeration circuit for a vehicle air conditioner. In addition, illustration of an evaporator, an expansion valve, a condenser, and each piping is abbreviate | omitted.

  In the compressor configured as described above, the swash plate 5 rotates as the drive shaft 3 rotates. Thereby, in each piston 9, each 1st head 9a reciprocates within each 1st cylinder bore 21a, and each 2nd head 9b reciprocates within each 2nd cylinder bore 23a. For this reason, the first and second compression chambers 53 a and 53 b change in volume according to the stroke of the piston 9. For this reason, in this compressor, the suction process of sucking the refrigerant gas from the first and second suction chambers 27a and 27b to the first and second compression chambers 53a and 53b, and the refrigerant gas in the first and second compression chambers 53a and 53b. The compression stroke to be compressed and the discharge stroke in which the compressed refrigerant gas is discharged into the first and second discharge chambers 29a and 29b are repeatedly performed. The refrigerant gas discharged into the first discharge chamber 29 a reaches the merged discharge chamber 231 through the first discharge communication path 12. Similarly, the refrigerant gas discharged into the second discharge chamber 29 b reaches the merged discharge chamber 231 through the second discharge communication path 14. Then, the refrigerant gas reaching the merged discharge chamber 231 is discharged from the discharge port 230 to the condenser via the pipe.

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

  Specifically, the control mechanism 15 causes the first passage 59a and the air supply passage 61a, that is, the throttle passage 20, the first communication chamber 18a, the third passage 55e, the first axial passage 55a, and the first passage 55c to circulate. Thus, the refrigerant gas in the first discharge chamber 29a is introduced into the control pressure chamber 13c. At this time, the flow rate of the refrigerant gas introduced from the first discharge chamber 29a into the control pressure chamber 13c is adjusted by the throttle passage 20 to be introduced from the first discharge chamber 29a into the control pressure chamber 13c. The pressure of the refrigerant gas is adjusted. Further, the control mechanism 15 circulates the extraction passage 61b and the second passage 59b, that is, the second passage 55d, the second axial passage 55b, the second communication chamber 18b, and the extraction passage 22, and the refrigerant in the control pressure chamber 13c. The gas is led out into the second suction chamber 27b.

  Here, in the control mechanism 15, if the control valve 24a increases the degree of opening of the extraction passage 22 based on the pressure of the refrigerant gas in the second suction chamber 27b, the control pressure chamber 13c enters the second suction chamber 27b. The flow rate of the derived refrigerant gas increases. As a result, the pressure in the control pressure chamber 13c is substantially equal to the pressure in the second suction chamber 27b, and the variable differential pressure, which is the differential pressure between the control pressure chamber 13c and the swash plate chamber 33, is reduced. Therefore, the moving body 13a of the actuator 13 moves toward the rear of the swash plate chamber 33 by the piston compression force acting on the swash plate 5, as shown in FIG.

  Thereby, in this compressor, the swash plate 5 is urged in a direction in which the inclination angle decreases by the compression reaction force acting on the swash plate 5 via each piston 9. The compression reaction force is a resultant force of piston compression force that acts on the swash plate 5 by each piston 9. For this reason, the movable body 13 a is pulled by the swash plate 5 through each connecting arm 132 and moves to the rear of the swash plate chamber 33 in the direction of the rotation axis O. Then, as the moving body 13a moves to the rear of the swash plate chamber 33, in this compressor, the swash plate 5 swings around the action axis M3. Further, the front end side of the lug arm 49 swings around the first swing axis M1, and the rear end side of the lug arm 49 swings around the second swing axis M2. For this reason, the rear end side of the lug arm 49 approaches the second flange 433 of the second support member 43b. As a result, the swash plate 5 swings with the operating axis M3 as the operating point and the first swinging axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 5 with respect to the direction orthogonal to the rotational axis O of the drive shaft 3 decreases, and the stroke of each piston 9 decreases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 decreases.

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

  In this compressor, the inclination angle of the swash plate 5 is reduced and the stroke of each piston 9 is reduced, whereby the top dead center position of each first head 9 a is moved away from the first valve forming plate 39. For this reason, in this compressor, when the inclination angle of the swash plate 5 approaches zero degrees, the refrigerant gas performs the compression work by slightly opening the discharge reed valve on the second compression chamber 53b side. In the chamber 53a, the refrigerant gas cannot open the discharge reed valve 392a shown in FIG. 5, and does not perform compression work. As described above, in this compressor, the first discharge chamber 29a and the second discharge chamber 29b communicate with each other through the first discharge communication passage 12, the second discharge communication passage 14, and the merged discharge chamber 231. For this reason, the refrigerant gas flows between the first discharge chamber 29a and the second discharge chamber 29b. Thereby, even when the compression work is not performed in the first compression chamber 53a, the refrigerant gas discharged into the second discharge chamber 29b flows into the first discharge chamber 29a.

  On the other hand, in the control mechanism 15, if the control valve 24a reduces the opening degree of the extraction passage 22, the flow rate of the refrigerant gas led out from the control pressure chamber 13c into the second suction chamber 27b decreases. As a result, the pressure in the control pressure chamber 13c increases due to the pressure of the refrigerant gas in the first discharge chamber 29a. For this reason, the variable differential pressure increases. Thereby, in the actuator 13, the moving body 13a moves from the position shown in FIG. 1 to the front in the direction of the rotation axis O against the piston compressive force acting on the swash plate 5, and FIG. As shown in FIG.

  Thereby, in this compressor, the movable body 13 a pulls the swash plate 5 forward of the swash plate chamber 33 in the direction of the rotation axis O through each connecting arm 132. For this reason, in this compressor, the swash plate 5 swings around the action axis M3 in the opposite direction to the case where the inclination angle becomes small. Further, the front end side of the lug arm 49 swings around the first swing axis M1 in the opposite direction to the case where the inclination angle becomes smaller, and the rear end side of the lug arm 49 swings around the second swing axis M2. . For this reason, the rear end side of the lug arm 49 moves away from the second flange 433 of the second support member 43b. As a result, the swash plate 5 swings in the opposite direction to the case where the tilt angle becomes small, with the action axis M3 and the first swing axis M1 as the action point and the fulcrum, respectively. For this reason, the inclination angle of the swash plate 5 with respect to the direction orthogonal to the rotational axis O of the drive shaft 3 increases, and the stroke of each piston 9 increases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 3 increases.

  FIG. 7 shows a compressor of a comparative example. Although the detailed illustration is omitted, the compressor of the comparative example is configured in substantially the same manner as the compressor of the first embodiment. Here, in the compressor of the comparative example, instead of the first and second communication chambers 18a and 18b, the wall portion 17c, and the throttle passage 20 in the compressor of the first embodiment, the pressure adjustment chamber 100 and the supply air are supplied to a housing (not shown). An air passage 101, an extraction passage 102, and a control valve 103 are provided. Further, a control path 104 is formed on a drive shaft (not shown) instead of the control path 55 in the compressor of the first embodiment. In the compressor of the comparative example, the control pressure chamber 13 c and the pressure adjustment chamber 100 communicate with each other through the control path 104. Further, the pressure adjusting chamber 100 and the second discharge chamber 29 b communicate with each other through the air supply path 101. Further, the pressure adjustment chamber 100 communicates with the second suction chamber 27b through the extraction passage 102. The control valve 103 can change the opening degree of the air supply path 101 by changing its own opening degree by the pressure of the second suction chamber 27b. The bleed passage 102 is provided with an orifice 105. In the compressor of the comparative example, a control mechanism 150 is configured by the control path 104, the supply path 101, the extraction path 102, the control valve 103, and the orifice 105.

  In the compressor of the comparative example, the control mechanism 150 controls the pressure in the control pressure chamber 13c by controlling the pressure in the pressure adjustment chamber 100. Specifically, in the control mechanism 150, when the control valve 103 reduces the opening degree of the control valve 103 to reduce the opening degree of the air supply path 101, the pressure in the pressure regulation chamber 100 decreases. For this reason, when the pressure in the control pressure chamber 13c decreases through the control path 104, the discharge capacity decreases as in the compressor of the first embodiment. Further, in the control mechanism 150, if the control valve 103 increases its own opening to increase the opening of the air supply passage 101, the pressure in the pressure regulation chamber 100 increases, so Will also increase. For this reason, the discharge capacity increases as in the compressor of the first embodiment. Thus, in the compressor of the comparative example, it is necessary to adjust the pressure in the pressure adjusting chamber 100 when increasing or decreasing the discharge capacity. For this reason, in the compressor of the comparative example, when the control valve 103 changes the opening, a delay is likely to occur until the discharge capacity is increased or decreased.

  On the other hand, as shown in FIG. 1 and FIG. 2, in the compressor of the first embodiment, the refrigerant gas in the first discharge chamber 29a flows into the control pressure chamber 13c through the first passage 59a and the air supply passage 61a during operation. Introduced directly into. As described above, in this compressor, since the first discharge chamber 29a and the second discharge chamber 29b communicate with each other through the first and second discharge communication passages 12 and 14 and the merged discharge chamber 231, the second compression chamber 53b. The refrigerant gas compressed and discharged into the second discharge chamber 29b can flow to the first discharge chamber 29a. For this reason, in the compressor of the first embodiment, the refrigerant gas in the first discharge chamber 29a can be introduced into the control pressure chamber 13c even if the compression work is not performed in the first compression chamber 53a. It is possible. Then, the refrigerant gas in the control pressure chamber 13c is directly led into the second suction chamber 27b through the extraction passage 61b and the second passage 59b. Thereby, in the compressor of Example 1, compared with the case where the control pressure chamber 13c communicates with the second suction chamber 27b and the second discharge chamber 29b via the pressure adjustment chamber 100 as in the compressor of the comparative example. Thus, the pressure in the control pressure chamber 13c can be quickly adjusted. Here, in the compressor of the first embodiment, the refrigerant gas in the first discharge chamber 29a is introduced into the control pressure chamber 13c via the first communication path 18a, and the refrigerant gas in the control pressure chamber 13c is It is led into the second suction chamber 27b via the two communication passages 18b. However, the first and second communication passages 18a and 18b do not adjust the pressure in the control pressure chamber 13c like the pressure adjustment chamber 100 described above.

  For this reason, in the compressor of Example 1, since the moving body 13a can change the inclination-angle of the swash plate 5 quickly as needed, discharge capacity can be increased / decreased rapidly. Moreover, in this compressor, since the partition member 57 is provided in the control path 55, the air supply path 61a and the extraction path 61b are separated. Thereby, in this compressor, it is prevented that the refrigerant gas which distribute | circulates the 1st axial path 55a distribute | circulates directly to the 2nd axial path 55b, without passing through the 1st path 55c and the control pressure chamber 13c. For this reason, in this compressor, it is possible to adjust the pressure in the control pressure chamber 13c suitably.

  Therefore, the compressor of Example 1 exhibits high controllability.

  Moreover, in this compressor, when adjusting the pressure in the control pressure chamber 13c, it is possible to quickly reduce the pressure in the control pressure chamber 13c by increasing the opening degree of the extraction passage 22 by the control valve 24a. It has become. In this compressor, the flow rate of the refrigerant gas introduced from the first discharge chamber 29 a into the control pressure chamber 13 c is adjusted by the throttle passage 20. Therefore, it is sufficient to adjust only the flow rate of the refrigerant gas led out from the control pressure chamber 13b to the second suction chamber 27b by the control valve 24a. For this reason, in this compressor, it is only necessary to provide one control valve 24a in the rear housing 19, and the manufacturing cost can be reduced.

(Example 2)
As shown in FIGS. 8 and 9, the compressor according to the second embodiment includes a control mechanism 16 instead of the control mechanism 15. Further, as shown in FIG. 10, in this compressor, the first shaft hole 17 b, the first communication chamber 18 a, the wall portion 17 c, and the throttle passage 20 are not formed in the front housing 17. Thus, in this compressor, the first suction chamber 27 a is disposed on the center side of the front housing 17.

  Further, as shown in FIG. 8, in this compressor, an air supply passage 26 and a control valve 24b are provided for the rear housing 19 in place of the extraction passage 22 and the control valve 24a. The air supply path 26 includes a first air supply path 26a and a second air supply path 26b. The first air supply path 26a is connected to the second discharge chamber 29b and the control valve 24b. The second air supply path 26b is connected to the control valve 24b and the second communication chamber 18b. The rear housing 19 is formed with a connection path 28 that connects the second suction chamber 27b and the control valve 24b. The control valve 24b can adjust the opening of the air supply passage 26 by changing its own opening based on the pressure of the refrigerant gas in the second suction chamber 27b.

  In this compressor, in the housing 1, the drive shaft 3 includes a shaft seal device 25, a first suction chamber 27 a, a second communication chamber 18 b, second and third shaft holes 21 b and 23 b, first and second valve forming plates 39. 41, the swash plate chamber 33 and the first and second thrust bearings 35a and 35b. As a result, as shown in FIG. 10, the first support member 43a is inserted into the shaft seal device 25, the first suction chamber 27a, the first valve forming plate 39, and the first thrust bearing 35a, and the second shaft hole 21b. It is supported by. Further, unlike the compressor of the first embodiment, in this compressor, the first and second annular grooves 431 and 432 and the first and second sealing members 44a and 44b are not provided in the first support member 43a.

  Further, the drive shaft 3 is formed with a fourth path 55f and a throttle path 32 instead of the third path 55e. The fourth path 55 f and the throttle path 32 are formed on the front end side of the drive shaft 3. The fourth path 55f extends in the radial direction of the first support portion 43a and opens on the outer peripheral surface of the first support portion 43a. The throttle passage 32 is formed with a smaller diameter than the first axial path 55a and the fourth radial path 55f. The throttle passage 32 is coaxial with the fourth path 55f and extends in the radial direction of the drive shaft main body 30, and is connected to the front end side of the first axis 55a and the fourth path 55f. The throttle passage 32 is also an example of a throttle in the present invention. The fourth passage 55f and the throttle passage 32 are located in the first suction chamber 27a when the drive shaft 3 is supported by the housing 1 as described above.

  As shown in FIG. 8, in this compressor, the first axial path 55a and the first radial path 55c are communicated with the first suction chamber 27a by the fourth path 55f and the throttle path 32. The second axial path 55b and the second radial path 55c communicate with the second discharge chamber 29b by the second communication chamber 18b, the air supply path 26, and the control valve 24b. In other words, in the compressor, the fourth passage 55f and the throttle passage 32 constitute a first passage 60a that allows the control passage 55 to communicate with the first suction chamber 27a. Further, the second communication chamber 18b, the air supply passage 26, and the control valve 24b constitute a second passage 60b that allows the control passage 55 to communicate with the second discharge chamber 29a.

  In this compressor, an air supply path 63a through which the refrigerant gas in the second discharge chamber 29b reaches the control pressure chamber 13c is configured by the second axial path 55b and the second path 55d in the control path 55. Yes. Further, in the control path 55, the first axial path 55a and the first path 55c constitute an extraction path 63b through which the refrigerant gas in the control pressure chamber 13c reaches the first suction chamber 27a. As with the compressor of the first embodiment, the air supply path 63a and the extraction path 63b are also separated by a partition wall member 57.

  As shown in FIG. 9, the control mechanism 16 includes a control path 55, a first passage 60a, and a second passage 60b. The control mechanism 16 circulates the second passage 60b and the control passage 55 to introduce the refrigerant gas in the second discharge chamber 29b into the control pressure chamber 13c, and circulates the control passage 55 and the first passage 60a. Then, the refrigerant gas in the control pressure chamber 13c is led out into the first suction chamber 27a. At this time, the control valve 24b changes the opening degree of the second passage 60b, and the throttle passage 32 restricts the opening degree of the first passage 60a. Thus, the control mechanism 16 controls the pressure in the control pressure chamber 13c. Other configurations of the compressor are the same as those of the compressor according to the first embodiment, and the same components are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, the control mechanism 16 causes the second passage 60b and the air supply path 63a, that is, the air supply path 26, the second communication chamber 18b, the second axial path 55b, and the second path 55d to circulate, and the second. The refrigerant gas in the discharge chamber 29b is introduced into the control pressure chamber 13c. Then, the refrigerant passage in the control pressure chamber 13c is circulated through the extraction passage 63b and the first passage 60a, that is, the first passage 55c, the first axial passage 55a, the throttle passage 32, and the fourth passage 55f. Derived into 27a. At this time, the flow rate of the refrigerant gas led out from the control pressure chamber 13c into the first suction chamber 27a is adjusted by the throttle passage 32.

  Here, in the control mechanism 16, if the control valve 24b reduces the opening of the air supply passage 26 based on the pressure of the refrigerant gas in the second suction chamber 27b, the inside of the control pressure chamber 13c from the second discharge chamber 29b. The flow rate of the refrigerant gas introduced into is reduced. As a result, the pressure in the control pressure chamber 13c decreases and the variable differential pressure becomes smaller. Therefore, like the compressor of the first embodiment, the moving body 13a moves toward the rear of the swash plate chamber 33, the inclination angle of the swash plate 5 decreases, and the discharge capacity per one rotation of the drive shaft 3 decreases. To do.

  On the other hand, in the control mechanism 16, when the control valve 24b increases the opening of the air supply passage 26, the flow rate of the refrigerant gas introduced from the second discharge chamber 29b into the control pressure chamber 13c increases. As a result, the pressure in the control pressure chamber 13c increases due to the pressure of the refrigerant gas in the second discharge chamber 29b, and the variable differential pressure increases. Thereby, the moving body 13a moves toward the front of the swash plate chamber 33, the inclination angle of the swash plate 5 increases, and the discharge capacity per one rotation of the drive shaft 3 increases.

  Thus, in this compressor, the refrigerant gas in the second discharge chamber 29b is directly introduced into the control pressure chamber 13c through the second passage 60b and the air supply path 63a during operation. Further, the refrigerant gas in the control pressure chamber 13c is directly led into the first suction chamber 27a through the extraction passage 63b and the first passage 60a. For this reason, like the compressor of Example 1, also in this compressor, since the moving body 13a can change the inclination-angle of the swash plate 5 quickly as needed, discharge capacity can be increased / decreased quickly. Also in this compressor, since the air supply path 63a and the extraction path 63b are separated by the partition wall member 57, the refrigerant gas flowing through the second axial path 55b passes through the second path 55d and the control pressure chamber 13c. Without flowing, it is prevented from flowing directly to the first axis 55a. For this reason, even in this compressor, it is possible to suitably adjust the pressure in the control pressure chamber 13c.

  Further, in this compressor, when adjusting the pressure in the control pressure chamber 13c, it is possible to quickly increase the pressure in the control pressure chamber 13c by increasing the opening of the air supply passage 26 by the control valve 24b. It has become. Since the flow rate of the refrigerant gas led out from the control pressure chamber 13c into the first suction chamber 27a is adjusted by the throttle passage 32, even if this compressor is provided with one control valve 24b in the rear housing 19. It ’s enough. For this reason, the manufacturing cost can be reduced even with this compressor.

  Further, in this compressor, the drive shaft 3 is inserted into the first suction chamber 27a. In the first suction chamber 27a, the first shaft path 55a passes through the fourth path 55f and the throttle passage 32, and the first suction chamber 27a. It communicates with 27a. Therefore, in this compressor, unlike the compressor of the first embodiment, it is not necessary to provide the first communication chamber 18a, the wall portion 17c, and the throttle passage 20 in the front housing 17a, and the first support member 43a has the first, 2 There is no need to provide the sealing members 44a and 44b. Further, by forming the throttle passage 32 in the drive shaft main body 30, it is possible to easily provide the throttle passage 32 for narrowing the opening degree of the first passage 60a. For this reason, in this compressor, manufacture can be facilitated, and also in this respect, manufacturing cost can be reduced. Other functions of this compressor are the same as those of the compressor of the first embodiment.

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

  For example, in the compressors of the first and second embodiments, the control valve 24a and the control valve 24b may be arranged in the first cylinder block 21 and the second cylinder block 23.

  In the compressors of the first and second embodiments, the actuator 13 may be disposed behind the swash plate 5 and the link mechanism 7 may be disposed forward of the swash plate 5 in the swash plate chamber 33.

  Further, in the compressor according to the first embodiment, the control valve 24 a may be disposed in the front housing 17 and the throttle passage 20 may be provided in the extraction passage 22.

  In the compressor of the first embodiment, the flow rate of the refrigerant gas introduced from the first discharge chamber 29a into the control pressure chamber 13c is adjusted by a control valve different from the control valve 24a, instead of the throttle passage 20. May be.

  Furthermore, in the compressor according to the second embodiment, the control valve 24b may be disposed in the front housing 17 and the throttle passage 32 may be provided in the air supply passage 26.

  In the compressor of the second embodiment, the flow rate of the refrigerant gas led out from the control pressure chamber 13c into the first suction chamber 27a is adjusted by a control valve different from the control valve 24b instead of the throttle passage 32. May be.

  Furthermore, in the compressor of Example 1, the control valve 24a which changes the opening degree of the extraction path 22, ie, the 2nd channel | path 59b based on the pressure in the 2nd suction chamber 27b is employ | adopted. However, the present invention is not limited to this, and the opening degree of the bleed passage 22 may be changed by employing a flow rate control valve. In this case, a first pressure monitoring point is set in the discharge region of the refrigeration circuit, and the first pressure is further downstream in the flow direction of the refrigerant gas than the first pressure monitoring point in the discharge region of the refrigeration circuit. A second pressure monitoring point is set at a location where the pressure is lower than the monitoring point. Thereby, the flow control valve can change the opening degree of the extraction passage 22 based on the differential pressure between the first pressure monitoring point and the second pressure monitoring point. Similarly, in the compressor of the second embodiment, the opening degree of the air supply path 26 may be changed by the flow rate control valve.

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

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 5 ... Swash plate 7 ... Link mechanism 9 ... Piston 9a ... 1st head 9b ... 2nd head 13a ... Moving body 13b ... Partition body 13c ... Control pressure chamber 15, 16 ... Control mechanism 20 ... throttle passage (throttle)
21a ... first cylinder bore 23a ... second cylinder bores 24a, 24b ... control valve 27a ... first suction chamber 27b ... second suction chamber 29a ... first discharge chamber 29b ... second discharge chamber 32 ... throttle passage (throttle)
55 ... Control path 57 ... Partition member (partition wall)
59a, 60a ... 1st passage 59b, 60b ... 2nd passage 61a, 63a ... Air supply route 61b, 63b ... Extraction route

Claims (4)

A housing in which a suction chamber, a discharge chamber, a swash plate chamber and a plurality of cylinder bores are formed;
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism that allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the rotational axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the rotational axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
The suction chamber comprises a first suction chamber located on one side of the swash plate and a second suction chamber located on the other side of the swash plate,
The discharge chamber is composed of a first discharge chamber located on the one surface side of the swash plate and a second discharge chamber located on the other surface side of the swash plate,
The cylinder bores are provided on the one surface side of the swash plate, provided on the other surface side of the swash plate, a first cylinder bore communicating with the first suction chamber and the first discharge chamber, and the second A second cylinder bore communicating with the suction chamber and the second discharge chamber;
Each piston reciprocates within the first cylinder bore, reciprocates within the first cylinder bore and a first head that defines a first compression chamber, and the second cylinder bore, and the second cylinder bore. A second head that defines a second compression chamber therein,
The control mechanism is formed inside the drive shaft and communicates with the control pressure chamber;
A first passage formed in at least one of the housing and the drive shaft and communicating the control path with the first discharge chamber or the first suction chamber;
If formed in at least one of the housing and the drive shaft, and the first passage communicates with the first discharge chamber, the control passage communicates with the second suction chamber, and the first passage communicates with the first suction chamber. A second passage for communicating the control path with the second discharge chamber if communicating with the second discharge chamber;
A control valve provided in one of the first and second passages and capable of changing an opening of the one passage;
Provided in a passage on the other side of the first passage and the second passage, and has a throttle for restricting the opening of the other passage or the control valve capable of changing the opening of the other passage. This is a variable capacity swash plate compressor. The first passage communicates the control path with the first discharge chamber,
The second passage communicates the control path with the second suction chamber,
The control valve is provided in the second passage,
The throttle is provided in the first passage,
The control path includes an air supply path for the refrigerant in the first discharge chamber to reach the control pressure chamber, an air extraction path for the refrigerant in the control pressure chamber to reach the second suction chamber, the air supply path, and the The variable capacity swash plate compressor according to claim 1, wherein a partition wall separating the bleed passage is formed. The first passage communicates the control path with the first suction chamber,
The second passage communicates the control path with the second discharge chamber,
The control valve is provided in the second passage,
The throttle is provided in the first passage,
The control path includes an air supply path for the refrigerant in the second discharge chamber to reach the control pressure chamber, an air extraction path for the refrigerant in the control pressure chamber to reach the first suction chamber, the air supply path, and the The variable capacity swash plate compressor according to claim 1, wherein a partition wall separating the bleed passage is formed. The first discharge chamber is disposed on an outer periphery of the first suction chamber;
The drive shaft is inserted into the first suction chamber;
4. The variable displacement swash plate compressor according to claim 3, wherein the throttle is provided on the drive shaft.

Images