KR101729076B1 - Variable displacement swash plate type compressor - Google Patents

Abstract

The present invention provides a variable displacement swash plate type compressor which can reduce the manufacturing cost and exhibit high performance for a long period of time, by using the actuator to change the discharge capacity. In the compressor of the present invention, the throttle hole (57) is formed in the connecting portion (133). The throttle hole 57 extends from the control pressure chamber 13b toward the inside of the outside sliding portion 51c. In the compressor of the present invention, when the pressure in the control pressure chamber 13b is adjusted as well as the opening degree of each of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is discharged from the inside of the control pressure chamber 13b And is discharged to the swash plate chamber 25 through the hole 57. Lubricating oil is discharged together with the refrigerant gas from the throttle hole (57). As a result, in the compressor, the lubricating oil is not easily stored in the control pressure chamber 13b, and the lubricating oil shortage in the swash plate chamber 25 does not easily occur.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a variable displacement swash plate type compressor,

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

A conventional variable displacement swash plate type compressor is disclosed in Patent Document 1. [ In this compressor, a suction chamber, a discharge chamber, a swash plate chamber, a center bore, and a plurality of cylinder bores are formed in the housing. The swash plate chamber and central bore communicate with each other. A driving shaft is rotatably supported on the housing. The swash plate chamber is provided with a swash plate rotatable by rotation of the drive shaft. A link mechanism is provided between the drive shaft and the swash plate. The inclination angle of the swash plate can be changed by the link mechanism. Here, the inclination angle of the swash plate refers to the angle of the swash plate with respect to the direction perpendicular to the drive axis of the drive shaft. A piston is reciprocatively received in each cylinder bore. The pair of shoes per pair of pistons is a switching mechanism that allows each piston to reciprocate in the cylinder bore in a stroke corresponding to the inclination angle by the rotation of the swash plate. The actuator changes the tilt angle. The control mechanism controls the actuator.

The actuator includes a first movable body, a second movable body, and a control pressure chamber. The drive shaft is inserted through the first movable body and the second movable body movable in alignment in the axial direction of the drive shaft. The first movable body is located at the center bore. Further, a thrust bearing is provided between the first movable body and the second movable body. The swash plate is engaged with the second movable body so as to change the inclination angle. The control pressure chamber moves the first movable body and the second movable body by the internal pressure.

The control mechanism performs the communication control between the control pressure chamber and the suction chamber and also performs the communication control between the control pressure chamber and the discharge chamber so that the pressure of the refrigerant in the control pressure chamber is adjusted. Further, the control mechanism includes an O-ring and a pair of seal rings. The O-ring and each seal ring are positioned between the outer peripheral surface of the first movable body and the inner peripheral surface of the central bore. The control pressure chamber and the swash plate chamber are mutually sealed by the O-ring and each seal ring.

In the compressor, the control mechanism introduces the refrigerant in the discharge chamber into the control pressure chamber, thereby increasing the pressure in the control pressure chamber. As a result, the first movable element moves in the axial direction of the drive shaft at the central bore, and also moves the second movable element in the axial direction. The second movable element increases the inclination angle of the swash plate by the link mechanism. As a result, in the compressor, the discharge capacity per revolution of the drive shaft can be increased.

In the conventional compressor, in changing the discharge capacity, the control mechanism adjusts the pressure in the control pressure chamber through the communication control between the suction chamber and the discharge chamber and the control pressure chamber while sealing the control pressure chamber and the swash plate chamber to each other . Therefore, in the conventional compressor, a process or means for preventing the leakage of the refrigerant from the control pressure chamber is required. Thus, the manufacturing cost is increased.

Further, in the compressor, when the refrigerant in the discharge chamber is introduced into the control pressure chamber, the lubricant is introduced into the control pressure chamber together with the refrigerant. The lubricating oil flowing into the control pressure chamber is stored in the control pressure chamber. As a result, in the compressor, the lubricating oil in the swash plate chamber tends to become insufficient. In the swash plate chamber, the lubrication of the thrust bearing or the like tends to become insufficient. Therefore, in the conventional compressor, it is difficult to maintain the performance for a long period of time.

Japanese Patent Application Laid-Open No. 8-105384

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional circumstances, and it is an object of the present invention to provide a compressor which changes a discharge capacity by using an actuator and which is capable of reducing a manufacturing cost and capable of exhibiting high performance for a long period of time A variable swash plate type compressor is provided.

A variable capacity swash plate type compressor according to the present invention includes: a housing having a suction chamber, a discharge chamber, a swash plate chamber, and a cylinder bore; A drive shaft rotatably supported by the housing; A swash plate rotatable in the swash plate chamber in accordance with rotation of the drive shaft; A link mechanism provided between the drive shaft and the swash plate and configured to change an inclination angle of the swash plate with respect to a direction orthogonal to the axis of the drive shaft; A piston reciprocably received within the cylinder bore; A switching mechanism configured to reciprocate the piston in the cylinder bore with a stroke corresponding to the inclination angle in accordance with the rotation of the swash plate; An actuator capable of changing the inclination angle; And a control mechanism configured to control the actuator.

The swash plate chamber communicates with the suction chamber.

The actuator includes a defining body provided on the driving shaft in the swash plate chamber; A movable body movable in the axial direction of the drive shaft in the swash plate chamber; And a control pressure chamber partitioned by the partition and the movable body and configured to move the movable body by internal pressure.

The control mechanism includes a supply passage communicating with the discharge chamber and the control pressure chamber and introducing the refrigerant in the discharge chamber into the control pressure chamber; And a bleed passage communicating with the control pressure chamber and the swash plate chamber and discharging the refrigerant in the control pressure chamber to the swash plate chamber.

The replacement passage is formed in at least one of the movable body and the partition, and includes a communication passage for discharging the lubricating oil together with the refrigerant from the control pressure chamber to the swash plate chamber.

Other aspects and advantages of the present invention will become apparent from the embodiments disclosed in the accompanying drawings, the examples in it, and the principles of the invention.

1 is a sectional view of the compressor of the first embodiment in the maximum capacity state.
2 is a schematic view showing a control mechanism of a compressor in the first embodiment.
3 is an enlarged cross-sectional view of a main portion showing an actuator of the compressor in the first embodiment.
4 is a cross-sectional view of the compressor of the first embodiment in the minimum capacity state.
5 is an enlarged cross-sectional view of a main portion showing an actuator of the compressor in the second embodiment.
6 is an enlarged sectional view of a main portion showing an actuator of the compressor in the third embodiment.
7 is an enlarged cross-sectional view of a main part showing an actuator of the compressor in the fourth embodiment.
8 is a cross-sectional view of the compressor of the fifth embodiment in the maximum capacity state.
9 is a schematic view showing a control mechanism of the compressor in the fifth embodiment.
10 is an enlarged cross-sectional view of a main portion showing an actuator of a compressor in a fifth embodiment.
11 is a cross-sectional view of the compressor of the fifth embodiment in a minimum capacity state.
12 is an enlarged sectional view of a main portion showing an actuator of the compressor in the sixth embodiment.

Best Modes for Carrying Out the Invention Hereinafter, the first to sixth embodiments of the present invention will be described with reference to the drawings. The compressors in the first to fourth embodiments are single head capacity variable swash plate type compressors. On the other hand, the compressors in the fifth and sixth embodiments are doublehead capacity variable swash plate type compressors. These compressors are all mounted on a vehicle and constitute a refrigerant circuit of a vehicle air conditioner.

(Embodiment 1)

1, 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, a pair of shoes 11a and 11b, An actuator 13, and a control mechanism 15 shown in Fig.

1, the housing 1 includes a front housing 17 positioned at a front portion of the compressor, a rear housing 19 positioned at a rear portion of the compressor, a front housing 17 and a rear housing 19 , And a valve-forming plate (23).

The front housing 17 includes a front wall 17a extending in the vertical direction of the compressor from the front side and a peripheral wall 17b integrated with the front wall 17a and extending from the front side to the rear side of the compressor ). By the front wall 17a and the peripheral wall 17b, the front housing 17 forms a substantially cylindrical shape with a bottom. The swash plate chamber 25 is formed in the front housing 17 by the front wall 17a and the peripheral wall 17b.

A boss 17c protruding forward is formed in the front wall 17a. The boss 17c is provided with a shaft seal device 27 which ensures a hermetic seal between the inside and the outside of the housing 1. [ The boss 17c is provided with a first shaft hole 17d extending in the front-rear direction of the compressor. A first plane bearing 29a is provided in the first shaft hole 17d. The first plane bearing 29a receives a radial force acting on the drive shaft 3. The first plane bearing 29a corresponds to a radial bearing in the present invention. In addition, a rolling bearing may be employed in place of the first plane bearing 29a.

An inlet 250 communicating with the swash plate chamber 25 is formed in the peripheral wall 17b. The swash plate chamber 25 is connected through an inlet 250 to an evaporator (not shown). Accordingly, the low-pressure refrigerant gas passing through the evaporator flows into the swash plate chamber 25 through the inlet port 250. Therefore, the pressure in the swash plate chamber 25 is lower than the pressure in the discharge chamber 35, which will be described later.

The rear housing 19 is provided with a part of the control mechanism 15. In the rear housing 19, a first pressure regulating chamber 31a, a suction chamber 33 and a discharge chamber 35 are formed. The first pressure regulating chamber 31a is located at the center of the rear housing 19. [ The discharge chamber 35 is annularly positioned on the outer circumferential side of the rear housing 19. The suction chamber 33 is formed annularly between the first pressure regulating chamber 31a and the discharge chamber 35 in the rear housing 19. [ The discharge chamber 35 is connected to a discharge port (not shown).

In the cylinder block 21, cylinder bores 21a are formed at equal angle intervals in the circumferential direction in the same number as the number of the pistons 9. The front end side of the cylinder bore 21a communicates with the swash plate chamber 25. The cylinder block 21 is also formed with a retainer groove 21b for adjusting a maximum opening degree of a suction reed valve 41a to be described later.

The cylinder block 21 is provided with a second shaft hole 21c communicating with the swash plate chamber 25 and extending in the front-rear direction of the compressor. And the second planar bearing 29b is provided in the second shaft hole 21c. Instead of the second plain bearing 29b, a rolling bearing may be employed.

Further, a spring chamber 21d is formed in the cylinder block 21. The spring chamber 21d is located between the swash plate chamber 25 and the second shaft hole 21c. A return spring 37 is disposed in the spring chamber 21d. The return spring 37 presses the swash plate 5 inclined at the minimum inclination angle toward the front portion of the swash plate chamber 25. [ A suction passage (39) communicating with the swash plate chamber (25) is formed in the cylinder block (21).

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

The number of suction ports 40a equal to the number of the cylinder bores 21a is formed in the valve plate 40, the discharge valve plate 43 and the retainer plate 45. [ The valve plate 40 and the suction valve plate 41 are provided with the same number of discharge ports 40b as the number of the bores 21a of the cylinder. Each of the cylinder bores 21a communicates with the suction chamber 33 through each suction port 40a and communicates with the discharge chamber 35 through each discharge port 40b. The first communication hole 40c and the second communication hole 40d are formed in the valve plate 40, the suction valve plate 41, the discharge valve plate 43 and the retainer plate 45. [ The suction chamber 33 and the suction passage 39 communicate with each other through the first communication hole 40c. As a result, the swash plate chamber 25 and the suction chamber 33 communicate with each other.

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

The drive shaft 3 is inserted from the boss 17c side toward the rear side of the housing 1. [ The front end side of the drive shaft 3 is inserted into the boss 17c through the shaft sealing device 27 and supported in the first axial hole 17d by the first flat bearing 29a in the axial direction. The rear end side of the drive shaft 3 is supported in the second shaft hole 21c in the axial direction by the second planar bearing 29b. In this way, the drive shaft 3 is rotatably supported about the drive axis O1 with respect to the housing 1. [ In the second shaft hole 21c, the second pressure adjusting chamber 31b is partitioned by the rear end of the drive shaft 3 in the second shaft hole 21c. The second pressure regulating chamber 31b communicates with the first pressure regulating chamber 31a through the second communication hole 40d. The first pressure regulating chamber 31 a and the second pressure regulating chamber 31 b form a pressure regulating chamber 31.

The rear end of the drive shaft 3 is provided with O-rings 49a and 49b. As a result, the O-rings 49a and 49b are positioned between the drive shaft 3 and the second shaft hole 21c to seal the space between the swash plate chamber 25 and the pressure regulating chamber 31. [

The link mechanism 7, the swash plate 5, and the actuator 13 are attached to the drive shaft 3. The link mechanism 7 includes a lug plate 51, a pair of lug arms 53 formed on the lug plate 51, and a pair of swash plate arms 53 formed on the swash plate 5, (5e). In the compressor of the present embodiment, the lug plate 51 forms the link mechanism 7 and functions as a partition in the present invention. In Fig. 1, only one lug arm 53 and one swash plate arm 5e are shown. This is also applied to Fig.

The lug plate 51 is formed in a substantially ring shape and disposed in the front portion of the swash plate 5. 3, the lug plate 51 includes a fixed portion 51a, a fixed flange portion 51b, and an outer sliding portion 51c. The fixing portion 51a is located at the center of the lug plate 51. [ An insertion hole 51d is formed through the fixing portion 51a. The drive shaft 3 is press-fitted into the insertion hole 51d. As a result, the lug plate 51 is fixed to the drive shaft 3 and can rotate integrally with the drive shaft 3.

The fixed flange portion 51b is located at the front end of the lug plate 51 and extends radially outward from the fixed portion 51a. The outer slide portion 51c is located on the outer peripheral side of the fixed portion 51a and extends from the tip end of the fixed flange portion 51b in the axial direction O1 which is the drive axis of the drive shaft 3, As shown in Fig. The inside of the outside sliding portion 51c communicates with the swash plate chamber 25 and is part of the swash plate chamber 25. [ Further, a thrust bearing 55 is provided between the lug plate 51 and the front wall 17a. The thrust bearing (55) receives a thrust acting on the drive shaft (3). The thrust bearing 55 corresponds to the thrust bearing in the present invention.

The lug arm 53 extends rearward from the outer sliding portion 51c. The outer sliding portion 51c is provided with a guide surface 51e at a position between the outer sliding portion 51c and the lug arm 53. [ The guide surface 51e is formed to be inclined downward from the front end side to the rear end side.

As shown in Fig. 1, the swash plate 5 is formed in an annular flat plate shape and includes a front face 5a and a rear face 5b. On the front face 5a, a weight portion 5c protruding forward of the swash plate 5 is formed. The weight portion 5c comes into contact with the lug plate 51 when the inclination angle of the swash plate 5 is the maximum. An insertion hole (5d) is formed at the center of the swash plate (5). Further, the drive shaft 5 is inserted through the insertion hole 5d.

The swash plate arm 5e is formed on the front face 5a. The swash plate arm 5e extends forward from the front face 5a. The swash plate 5 is provided with a substantially hemispherical convex portion 5g projecting on the front face 5a. The convex portion 5g is positioned between the swash plate arm 5e and the swash plate arm 5e.

In the compressor of this embodiment, the swash plate arm 5e is inserted between the lug arms 53, whereby the lug plate 51 and the swash plate 5 are connected. As a result, the swash plate 5 is rotatable together with the lug plate 51 in the swash plate chamber 25. The lug plate 51 and the swash plate 5 are connected in this manner so that the leading end side of the swash plate arm 5e comes into contact with the guide surface 51e in the swash plate arm 5e. The swash plate arm 5e slides on the guide surface 51e so that the swash plate 5 is moved in the direction perpendicular to the axial direction O1 while maintaining the top dead center position T The inclination angle of the swash plate 5 can be changed from the inclination angle to the minimum inclination angle shown in FIG.

The actuator 13 includes a lug plate 51, a movable body 13a, and a control pressure chamber 13b.

As shown in Fig. 3, the drive shaft 3 is inserted through the movable body 13a. The movable member 13a can move in the axial direction O1 while sliding in contact with the drive shaft 3. [ The movable member 13a is formed into a cylindrical shape coaxial with the drive shaft 3. [ The movable member 13a includes a first cylindrical portion 131, a second cylindrical portion 132, and a connecting portion 133. [ The first cylindrical portion 131 is located closer to the swash plate 5 from the movable body 13a and is slidable with respect to the drive shaft 3. [ An O-ring 49c is provided on the inner circumferential surface of the first cylindrical portion 131.

A working portion 134 is integrally formed at the rear end of the first cylindrical portion 131. As shown in Fig. 1, the operating portion 134 extends vertically from a position close to the axial direction O1 toward the top dead center position T of the swash plate 5 and is in contact with the convex portion 5g. As a result, the movable body 13a is rotatable integrally with the lug plate 51 and the swash plate 5. [

As shown in Fig. 3, the second cylindrical portion 132 is located in the front portion of the movable body 13a. The second cylindrical portion 132 is formed to have a larger diameter than the diameter of the first cylindrical portion 131. An O-ring 49d is provided on the outer circumferential surface of the second cylindrical portion 132. The connecting portion 133 is positioned between the first cylindrical portion 131 and the second cylindrical portion 132 and extends from the rear of the movable body 13a to the front gradually increasing in diameter. The rear end of the connection portion 133 is connected to the first cylindrical portion 131 and the front end of the connection portion 133 is connected to the second cylindrical portion 132.

The outer sliding portion 51c of the lug plate 51 surrounds the movable member 13a by causing the second cylindrical portion 131 and the connecting portion 133 to enter the inside of the outer sliding portion 51c. The outer sliding portion 51c can receive the second cylindrical portion 132 and the connecting portion 133 therein. As a result, the second cylindrical portion 132 can slide in the outer sliding portion 51c, that is, on the inner wall 510 of the outer sliding portion 51c.

The control pressure chamber 13b is formed by the second cylindrical portion 132, the connecting portion 133 and the drive shaft 3 within the outer sliding portion 51c and is separated from the swash plate chamber 25. [ The control pressure chamber 13b is sealed from the swash plate chamber 25 by O-rings 49c and 49d.

A throttle hole 57 is formed on the front end side of the connecting portion 133, that is, on the side closer to the second cylindrical portion 132 in the connecting portion 133. The throttle hole 57 corresponds to the communication passage in the present invention.

The throttle hole 57 extends obliquely upward from the front end side to the rear end side in the connecting portion 133. [ More specifically, the throttle hole 57 is provided so that the lubricating oil discharged from the throttle hole 57 together with the refrigerant gas is supplied to the sliding portion between the second cylindrical portion 132 and the inner wall 510 of the outer sliding portion 51c . The control pressure chamber 13b and the swash plate chamber 25 communicate with each other through the throttle hole 57 because the inside of the outside sliding portion 51c communicates with the swash plate chamber 25 as described above. The throttle hole 57 may be formed in the second cylindrical portion 132.

1, the drive shaft 3 is provided with an axial path 3a extending in the axial direction O1 from the rear end to the front end of the drive shaft 3 and an axial path 3a extending from the front end of the axial path 3a in the radial direction And a radial path 3b extending to the outer circumferential surface of the drive shaft 3 is formed. The rear end of the axial path (3a) is open to the pressure regulating chamber (31). On the other hand, the radial path 3b is open to the control pressure chamber 13b. The pressure regulating chamber 31 and the control pressure chamber 13b communicate with each other via the axial path 3a and the radial path 3b.

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

Each of the pistons 9 is accommodated in each cylinder bore 21a and reciprocally movable within each cylinder bore 21a. In each cylinder bore 21a, a compression chamber 59 is defined by the pistons 9 and the valve-forming plate 23.

The engaging portion 9a is formed concavely in the piston 9. The coupling portion 9a is provided with hemispherical shoes 11a and 11b, respectively. The shoes 11a and 11b switch the rotation of the swash plate 5 to the reciprocating motion of the piston 9. [ The shoes 11a and 11b correspond to the switching mechanism in the present invention. As a result, the piston 9 can reciprocate in the cylinder bore 21a with a stroke corresponding to the inclination angle of the swash plate 5. [

2, the control mechanism 15 includes a low pressure passage 15a, a high pressure passage 15b, a low pressure control valve 15c, a high pressure control valve 15d, an axial passage 3a, a radial passage 3b, and the throttle hole 57 described above.

The low pressure passage 15a is connected to the pressure regulation chamber 31 and the suction chamber 33. [ As a result, the control pressure chamber 13b, the pressure regulation chamber 31, and the suction chamber 33 communicate with each other through the low pressure passage 15a, the axial passage 3a, and the radial passage 3b . In the present invention, the additional passage is formed by the low-pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 57. [

The high pressure passage 15b is connected to the pressure regulation chamber 31 and the discharge chamber 35. The control pressure chamber 13b, the pressure regulation chamber 31 and the discharge chamber 35 communicate with each other through the high pressure passage 15b, the axial passage 3a, and the radial passage 3b. In the present invention, the supply passage is formed by the high-pressure passage 15b, the axial passage 3a, and the radial passage 3b.

A low-pressure control valve 15c is provided in the low-pressure passage 15a. The low pressure control valve 15c can adjust the opening degree of the low pressure passage 15a based on the pressure of the suction chamber 33. [ Further, a high-pressure control valve 15d is provided in the high-pressure passage 15b. The high-pressure control valve 15d can adjust the opening of the high-pressure passage 15b based on the pressure of the suction chamber 33. [

In the compressor of the present embodiment, a pipe connected to the evaporator is connected to the inlet 250 shown in Fig. A pipe connected to the condenser is connected to the outlet. The condenser is connected to the evaporator through a pipe and an expansion valve. A compressor, an evaporator, an expansion valve, a condenser, and the like constitute a cooling circuit for a vehicle air conditioner. The evaporator, the expansion valve, the condenser and the respective piping are omitted.

In the above-described compressor, the drive shaft 3 rotates, the swash plate 5 rotates, and each piston 9 reciprocates within each cylinder bore 21a. Accordingly, the compression chamber 59 changes the capacity in accordance with the piston stroke. The refrigerant gas sucked into the swash plate chamber 25 by the inlet 250 from the evaporator passes through the suction passage 33 from the suction passage 39 and is compressed in the compression chamber 59. The refrigerant gas compressed in the compression chamber 59 is discharged to the discharge chamber 35, and is discharged from the discharge port to the condenser.

In the compressor of the present embodiment, the inclination angle of the swash plate 5 is changed by the actuator 13, and the stroke of the piston 9 is increased or decreased, whereby the discharge capacity can be changed.

Specifically, in the compressor of the present embodiment, in the control mechanism 15, the high-pressure control valve 15d shown in Fig. 2 adjusts the opening degree of the high-pressure passage 15b so that the pressure in the pressure regulating chamber 31, The pressure in the control pressure chamber 13b is increased by the refrigerant gas in the discharge chamber 35. [ Further, the adjustment of the opening of the low-pressure passage 15a is performed by the low-pressure control valve 15c, so that the pressure in the control-pressure chamber 13b is reduced.

In the compressor of the present embodiment, the refrigerant gas in the control pressure chamber 13b is discharged into the swash plate chamber 25 through the inside of the outer sliding portion 51c and further through the throttle hole 57. [ In this way, in the compressor of the present embodiment, the pressure in the control pressure chamber 13b is controlled by adjusting the opening of each of the high-pressure passage 15b and the low-pressure control valve 15c and the discharge of the refrigerant gas by the throttle hole 57 do.

When the high-pressure control valve 15d reduces the opening of the high-pressure passage 15b or the low-pressure control valve 15c increases the opening of the low-pressure passage 15a, the pressure in the control-pressure chamber 13b is reduced. In this case, as described above, the refrigerant gas in the control-pressure chamber 13b is discharged to the swash plate chamber 25 through the throttle hole 57. [ Therefore, the pressure difference between the control pressure chamber 13b and the swash plate chamber 25 is reduced. 1, in the compressor, the movable body 13a is moved from the position nearer the swash plate 5 to the lug plate 51 from the outer sliding portion 51c by the piston compressive force acting on the swash plate 5 To slide in the axial direction (O1).

At the same time, in the compressor, the swash plate arm 5e slides on the guide surface 51e away from the axial direction O1. Thus, in the swash plate 5, the bottom dead center side rotates clockwise while maintaining the top dead center position T substantially. In this way, in the compressor, the inclination angle of the swash plate 5 with respect to the axial direction O1 of the drive shaft 3 increases. As a result, in the compressor, the stroke of the piston 9 increases, and the discharge capacity per revolution of the drive shaft 3 increases. The inclination angle of the swash plate 5 shown in Fig. 1 is the maximum inclination angle in the compressor.

On the other hand, if the high-pressure control valve 15d shown in Fig. 2 increases the opening of the high-pressure passage 15b or the low-pressure control valve 15c reduces the opening of the low-pressure passage 15a, ) Is increased. Therefore, the pressure difference between the control pressure chamber 13b and the swash plate chamber 25 is increased. In this case, the refrigerant gas is discharged to the swash plate chamber 25 through the throttle hole 57. As a result, as shown in Fig. 4, the movable member 13a slides in the axial direction O1 toward the swash plate plate 5 away from the lug plate 51 at the outer sliding portion 51c.

As a result, in the compressor of this embodiment, the operating portion 134 presses the convex portion 5g toward the rear of the swash plate chamber 25. [ As a result, the swash plate arm 5e slides on the guide surface 51e so as to approach the axial direction O1. As a result, in the swash plate 5, the bottom dead center is rotated counterclockwise while maintaining the top dead center position T substantially. In this way, in the compressor of the present embodiment, the inclination angle of the swash plate 5 with respect to the axial direction O1 of the drive shaft 3 is reduced. As a result, in the compressor, the stroke of the piston 9 decreases, and the discharge capacity per revolution of the drive shaft 3 decreases. The inclination angle of the swash plate 5 shown in Fig. 4 is the minimum inclination angle in the compressor.

As described above, in the compressor of this embodiment, when the pressure in the control pressure chamber 13b is adjusted as well as the opening degree of each of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is supplied to the control pressure chamber 13b, And is discharged to the swash plate chamber 25 through the throttle hole 57 from the inside thereof. Therefore, in the compressor of this embodiment, when the pressure in the control pressure chamber 13b is adjusted, it is not necessary to completely seal the control pressure chamber 13b. It is sufficient that the control pressure chamber 13b is sealed by the O-rings 49c and 49d.

The throttle hole 57 discharges the lubricating oil together with the refrigerant gas from the control pressure chamber 13b to the swash plate chamber 25. Therefore, in the compressor of the present embodiment, even when the lubricant is introduced into the control pressure chamber 13b together with the refrigerant gas when the refrigerant gas in the discharge chamber 35 is introduced into the control pressure chamber 13b, And is discharged from the inside of the control pressure chamber 13b to the swash plate chamber 25 through the throttle hole 57. [

In the compressor of this embodiment, the throttle hole 57 is formed in the connecting portion 133. [ Therefore, in the compressor of the present embodiment, the lubricating oil can appropriately flow out from the throttle hole 57 by the centrifugal force generated when the movable body 13a rotates. Therefore, in the compressor of this embodiment, the lubricating oil is not easily stored in the control pressure chamber 13b. The lack of lubricating oil in the swash plate chamber 25 does not easily occur.

In the compressor of the present embodiment, the throttle hole 57 is formed such that the lubricating oil discharged from the throttle hole 57 together with the refrigerant gas flows from the sliding portion between the second cylindrical portion 132 and the inner wall 510 of the outer sliding portion 51c As shown in Fig. Therefore, in the compressor of the present embodiment, when the inclination angle of the swash plate 5 decreases from the maximum state, that is, when the movable body 13a slides in the axial direction 01 from the outer sliding portion 51c toward the swash plate 5 The sliding portion between the second cylindrical portion 132 and the inner wall 510 of the outer sliding portion 51c is appropriately lubricated by the lubricating oil discharged from the throttle hole 57. [ Therefore, in the compressor of the present embodiment, the second cylindrical portion 132 can appropriately slide on the inner wall 510 of the outer sliding portion 51c. Therefore, in the compressor of the present embodiment, the discharge capacity per revolution of the drive shaft 3 can be appropriately changed over a long period of time.

Therefore, according to the compressor of the first embodiment, in the compressor which changes the discharge capacity by using the actuator 13, the compressor exhibits high performance for a long period of time while realizing the reduction of the manufacturing cost.

(Second Embodiment)

As shown in Fig. 5, in the compressor of the second embodiment, a throttle hole 61 is provided instead of the throttle hole 57 in the compressor of the first embodiment. The throttle hole 61 is formed in the fixed flange portion 51b of the lug plate 51. [ The throttle hole 61 extends from the control pressure chamber 13b toward the front wall 17a so that lubricating oil discharged from the throttle hole 61 together with the refrigerant gas is supplied to the thrust bearing 55. [ The throttle hole (61) opens in the vicinity of the thrust bearing (55). As a result, the control pressure chamber 13b and the swash plate chamber 25 communicate with each other through the throttle hole 61. Further, in the compressor of the present embodiment, the additional passage of the present invention is formed by the low-pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 61. [ The throttle hole 61 may be formed in the fixing portion 51a. Other components of the compressor are the same as those of the compressor of the first embodiment. The same components are denoted by the same reference numerals and symbols. Detailed description of these components will be omitted.

In the compressor of this embodiment, when the pressure in the control pressure chamber 13b is adjusted as well as the opening degree of each of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is supplied from the inside of the control pressure chamber 13b And is discharged to the swash plate chamber 25 through the hole 61. In the compressor of the present embodiment, the throttle hole 61 is formed in the fixed flange portion 51b so that the lubricating oil discharged from the throttle hole 61 together with the refrigerant gas is supplied to the thrust bearing 55. Therefore, in the compressor of the present embodiment, it is possible to lubricate the thrust bearing 55 with the lubricating oil discharged from the throttle hole 61. [ Therefore, in the compressor of the present embodiment, the seizure in the thrust bearing 55 does not easily occur, and the durability can be improved. Other operations of the compressor are the same as those of the compressor of the first embodiment.

(Third Embodiment)

As shown in Fig. 6, in the compressor of the third embodiment, a throttle hole 63 is provided instead of the throttle hole 57 in the compressor of the first embodiment. The throttle hole 63 is formed in the fixed flange portion 51b of the lug plate 51. [ The throttle hole 63 extends from the control pressure chamber 13b toward the drive shaft 3 so that lubricating oil discharged from the throttle hole 63 together with the refrigerant gas is supplied to the first planar bearing 29a. As a result, the control pressure chamber 13b and the swash plate chamber 25 communicate with each other through the throttle hole 63. [ In the compressor of the present embodiment, the additional passage of the present invention is formed by the low-pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 63. [ The throttle hole 63 may be formed in the fixing portion 51a. Other components of the compressor are the same as those of the compressor of the first embodiment.

In the compressor of this embodiment, when the pressure in the control pressure chamber 13b is adjusted as well as the opening degree of each of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is supplied from the inside of the control pressure chamber 13b And is discharged to the swash plate chamber 25 through the hole 63. In the compressor of the present embodiment, the throttle hole 63 is formed in the fixed flange portion 51b so that lubricating oil discharged from the throttle hole 63 together with the refrigerant gas is supplied to the first flat bearing 29a. Therefore, in the compressor of the present embodiment, it is possible to lubricate the first flat bearing 29a with the lubricating oil discharged from the throttle hole 63. [ Therefore, in the compressor of the present embodiment, the sticking phenomenon between the drive shaft 3 and the first planar bearing 29a does not easily occur, and durability can be improved. Other operations of the compressor are the same as those of the compressor of the first embodiment.

(Fourth Embodiment)

7, in the compressor of the fourth embodiment, the shape of the front housing 17 and the lug plate 51 in the compressor of the first embodiment is partially changed, and the shape of the shaft sealing device 27 and the first plane The arrangement of the bearings 29a is changed. Specifically, in the compressor of the present embodiment, as compared with the compressor of the first embodiment, the first shaft hole 17d is formed so as to have a larger diameter in the front housing 17, And is disposed in the shaft hole 17d. As a result, the shaft sealing device 27 faces the swash plate chamber 25. Compared with the compressor of the first embodiment, in the compressor of this embodiment, the lug plate 51 extends forward so that the first flat bearing 29a is located between the front wall 17a and the fixed flange portion 51b .

In the compressor of the present embodiment, the throttle hole 65 is provided instead of the throttle hole 57 in the compressor of the first embodiment. The throttle hole 65 is formed in the fixed flange portion 51b of the lug plate 51. [ The throttle hole 65 extends from the control pressure chamber 13b toward the front housing 17 so that lubricating oil discharged from the throttle hole 65 together with the refrigerant gas is supplied to the shaft sealing device 27. [ As a result, the control pressure chamber 13b and the swash plate chamber 25 communicate with each other through the throttle hole 65. [ In the compressor of the present embodiment, the additional passage of the present invention is formed by the low-pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 65. [ Other components of the compressor are the same as those of the compressor of the first embodiment.

In the compressor of this embodiment, when the pressure in the control pressure chamber 13b is adjusted as well as the opening degree of each of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is supplied from the inside of the control pressure chamber 13b And is discharged to the swash plate chamber 25 through the hole 65. In the compressor of the present embodiment, the throttle hole 65 is formed in the fixed flange portion 51b so that the lubricating oil discharged from the throttle hole 65 together with the refrigerant gas is supplied to the shaft sealing device 27. Therefore, in the compressor of the present embodiment, it is possible to lubricate the shaft sealing device 27 with the lubricating oil discharged from the throttle hole 65. [ Therefore, in the compressor of the present embodiment, the space between the shaft sealing device 27 and the drive shaft 3 is appropriately lubricated.

In the compressor of the present embodiment, the shaft sealing device 27 is disposed in the first shaft hole 17d and the first plane bearing 29a is disposed between the front wall 17a and the fixed flange portion 51b. Therefore, in the compressor of the present embodiment, the shaft sealing device 27 and the lug plate 51 can be arranged close to each other as compared with the compressor of the first embodiment. The length of the boss 17c can be reduced. As a result, the compressor of the present embodiment can reduce the size of the compressor as compared with the compressor of the first embodiment. Other operations of the compressor are the same as those of the compressor of the first embodiment.

(Fifth Embodiment)

8, the compressor of the fifth embodiment includes a housing 10, a drive shaft 30, a swash plate 50, a link mechanism 70, a plurality of pistons 90, a pair of shoes 110a and 110b, An actuator 160, and a control mechanism 150 shown in Fig.

8, the housing 10 includes a front housing 117 positioned at a front portion of the compressor, a rear housing 119 positioned at a rear portion of the compressor, a front housing 117 and a rear housing 119 A first cylinder block 121 and a second cylinder block 123 positioned between the first cylinder block 121 and the second cylinder block 123 and a first valve forming plate 139 and a second valve forming plate 141.

The front housing 117 is formed with a boss 117a protruding forward. The boss 117a is provided with a shaft sealing device 125 which ensures hermetic sealing between the inside and the outside of the housing 10. In the front housing 117, a first suction chamber 127a and a first discharge chamber 129a are formed. The first suction chamber 127a is located radially inward with respect to the first discharge chamber 129a in the front housing 117. [ The first discharge chamber 129a is formed in an annular shape and is positioned radially outward of the first suction chamber 127a in the front housing 117. [

In addition, a first front communication path 118a is formed in the front housing 117. The front end side of the first front communication passage 118a communicates with the first discharge chamber 129a. The rear end side of the first front communication path (118a) opens at the rear end of the front housing (117).

A part of the control mechanism 15 is provided in the rear housing 119. In the rear housing 119, a second suction chamber 127b, a second discharge chamber 129b, and a pressure regulation chamber 131 are formed. The pressure regulating chamber 131 is located at the center of the rear housing 119. The second suction chamber 127b is formed in an annular shape and is located outside the pressure regulation chamber 131 in the radial direction in the rear housing 119. The second discharge chamber 129b is also formed in an annular shape and is located outside the second suction chamber 127b in the radial direction in the rear housing 119.

In addition, a first rear communication path 120a is formed in the rear housing 119. The rear end side of the first rear communication passage 120a communicates with the second discharge chamber 129b. The front end side of the first rear communication path (120a) opens at the front end of the rear housing (119).

A swash plate chamber 330 is formed between the first cylinder block 121 and the second cylinder block 123.

In the first cylinder block 121, a plurality of first cylinder bores 121a are formed at regular intervals in the circumferential direction in parallel with each other. The first cylinder block 121 is formed with a first shaft hole 121b through which the drive shaft 30 is inserted. A first plane bearing 122a is provided in the first shaft hole 121b.

The first cylinder block 121 is formed with a first concave portion 121c communicating with the first shaft hole 121b and coaxial with the first shaft hole 121b. The first concave portion 121c communicates with the swash plate chamber 330 and is a part of the swash plate chamber 330. [ A first thrust bearing 135a is provided at the front end of the first concave portion 121c. The first cylinder block 121 is formed with a first communication path 137a for communicating the swash plate chamber 330 with the first suction chamber 127a. The first cylinder block 121 is also formed with a first retainer groove 121e for adjusting the maximum opening degree of each first suction reed valve 691a to be described later.

The first cylinder block 121 is provided with a second front communication passage 118b. The front end of the second front communication passage 118b is opened at the front end of the first cylinder block 121. [ The rear end of the second front communication path 118b is opened at the rear end of the first cylinder block 121. [

A plurality of second cylinder bores 123a are formed in the second cylinder block 123, as in the first cylinder block 121. Each of the second cylinder bores 123a forms a pair with each of the first cylinder bores 121a in forward and backward directions.

In the second cylinder block 123, a second shaft hole 123b through which the drive shaft 3 is inserted is formed. The rear end of the second shaft hole 123b communicates with the pressure regulating chamber 131. In addition, the second planar bearing 122b is provided in the second shaft hole 123b. Instead of the first plane bearing 122a and the second plane bearing 122b, rolling bearings may be provided, respectively.

The second cylinder block 123 is formed with a second concave portion 123c communicating with the second shaft hole 123b and coaxial with the second shaft hole 123b. The second recess 123c also communicates with the swash plate chamber 330 and is a part of the swash plate chamber 330. A second thrust bearing 135b is provided at the rear end of the second concave portion 123c. The second thrust bearing 135b corresponds to the thrust bearing in the present invention. The second cylinder block 123 is formed with a second communication path 137b for communicating the swash plate chamber 330 and the second suction chamber 127b with each other. The second cylinder block 123 is formed with concave second retainer grooves 123e for adjusting the maximum opening degree of the second suction reed valve 711a to be described later.

The second cylinder block 123 is formed with an outlet 126, a merging discharge chamber 128, a third front communication passage 118c, a second rear communication passage 120b and an inlet port 330a do. The discharge port 126 and the integrated discharge chamber 128 communicate with each other. The integrated discharge chamber 128 is connected to an unillustrated condenser which constitutes the conduit through the outlet 126.

The front end side of the third front communication path 118c is opened at the front end of the second cylinder block 123. [ The rear end side of the third front communication passage 118c communicates with the integrated discharge chamber 128. [ When the first cylinder block 121 and the second cylinder block 123 are connected, the third front communication passage 118c communicates with the rear end side of the second front communication passage 118b.

An unillustrated evaporator constituting the conduit is connected to the inlet 330a. As a result, the swash plate chamber 330 and the evaporator are connected through the inlet 330a.

A first valve forming plate 139 is provided between the front housing 117 and the first cylinder block 121. A second valve forming plate 141 is provided between the rear housing 119 and the second cylinder block 123.

The first valve forming plate 139 includes a first valve plate 690, a first suction valve plate 691, a first discharge valve plate 692, and a first retainer plate 693. The first valve plate 690, the first discharge valve plate 692 and the first retainer plate 693 are formed with the same number of first suction holes 690a as the number of the first cylinder bores 121a . The first valve plate 690 and the first suction valve plate 691 are formed with the same number of first discharge holes 690b as the number of the first cylinder bores 121a. A first suction communication hole 690c is formed in the first valve plate 690, the first suction valve plate 691, the first discharge valve plate 692, and the first retainer plate 693. The first valve plate 690 and the first suction valve plate 691 are provided with a first discharge communication hole 690d.

The first cylinder bore 121a communicates with the first suction chamber 127a through the first suction hole 690a. The first cylinder bore 121a communicates with the first discharge chamber 129a through the first discharge hole 690b. The first suction chamber 127a and the first communication passage 137a communicate with each other through the first suction communication hole 690c. The first front communication passage 118a and the second front communication passage 118b communicate with each other through the first discharge communication hole 690d.

A first intake valve plate 691 is provided on the rear surface of the first valve plate 690. The first suction valve plate 691 is provided with a plurality of first suction reed valves 691a capable of opening and closing each of the first suction holes 690a by elastic deformation. A first discharge valve plate 692 is provided on the front surface of the first valve plate 690. The first discharge valve plate 692 is provided with a plurality of first discharge reed valves 692a capable of opening and closing the first discharge holes 690b by elastic deformation. On the front surface of the first discharge valve plate 692, a first retainer plate 693 is provided. The first retainer plate 693 adjusts the maximum opening degree of each first discharge reed valve 692a.

The second valve forming plate 141 includes a second valve plate 710, a second suction valve plate 711, a second discharge valve plate 712, and a second retainer plate 713. The second number of suction holes 710a are the same as the number of the second cylinder bores 123a in the second valve plate 710, the second discharge valve plate 712, and the second retainer plate 713 . The second valve plate 710 and the second suction valve plate 711 are formed with the same number of second discharge holes 710b as the number of the second cylinder bores 123a. A second suction communication hole 710c is formed in the second valve plate 710, the second suction valve plate 711, the second discharge valve plate 712, and the second retainer plate 713. The second valve plate 710 and the second suction valve plate 711 are provided with a second discharge communication hole 710d.

Each second cylinder bore 123a communicates with the second suction chamber 127b through each second suction hole 710a. In addition, each of the second cylinder bores 123a communicates with the second discharge chamber 129 through each of the second discharge holes 710b. The second suction chamber 127b and the second communication path 137b communicate with each other through the second suction communication hole 710c. The first rear communication passage 120a and the second rear communication passage 120b communicate with each other via the second discharge communication hole 710d.

A second suction valve plate 711 is provided on the front surface of the second valve plate 710. The second suction valve plate 711 is formed with a plurality of second suction reed valves 711a capable of opening and closing the respective second suction holes 710a by elastic deformation. A second discharge valve plate 712 is provided on the rear surface of the second valve plate 710. The second discharge valve plate 712 is formed with a plurality of second discharge reed valves 712a capable of opening and closing the respective second discharge holes 710b by elastic deformation. On the rear surface of the second discharge valve plate 712, a second retainer plate 713 is provided. The second retainer plate 713 regulates the maximum opening degree of each second discharge reed valve 712a.

In the compressor of the present embodiment, the first discharge communication passage 118a, the first discharge communication passage 690d, the second front communication passage 118b, and the third front communication passage 118c form the first discharge communication passage 118 are formed. The second discharge communication passage 120 is formed by the first rear communication passage 120a, the second discharge communication hole 710d, and the second rear communication passage 120b.

In the compressor of the present embodiment, the first suction chamber 127a and the second suction chamber 127b and the swash plate chamber 330 are connected to the first communication path 137a and the second communication path 137b, And communicates with each other through the communication hole 690c and the second suction communication hole 710c. Therefore, the pressures in the first suction chamber 127a and the second suction chamber 127b and the pressure in the swash plate chamber 330 are substantially the same. Also, the low-pressure refrigerant gas passing through the evaporator flows into the swash plate chamber 330 through the inlet port 330a. The respective pressures in the swash plate chamber 330 and the first suction chamber 127a and the second suction chamber 127b are lower than the respective pressures in the first discharge chamber 129a and the second discharge chamber 129b.

The drive shaft 30 is constituted by a drive shaft main body 300, a first support member 143a, and a second support member 143b. The drive shaft main body 300 extends from the front side to the rear side of the housing 10 and is inserted rearward from the boss 117a through the first planar bearing 122a and the second planar bearing 122b. As a result, the drive shaft main body 300 and further the drive shaft 30 are axially supported by the housing 10 so as to be rotatable about the drive axis direction O2. The front end of the drive shaft main body 300 is positioned at the boss 117a. The rear end of the drive shaft main body 300 protrudes into the pressure regulation chamber 131.

The drive shaft main body 300 is also provided with a swash plate 50, a link mechanism 70, and an actuator 160. The swash plate 50, the link mechanism 70, and the actuator 160 are each arranged in the swash plate chamber 330.

The first support member 143a is press-fitted into the front end side of the drive shaft main body 300 and positioned in the first shaft hole 121b. A flange 430 is formed in the first support member 143a to contact the first thrust bearing 135a. The first supporting member 143a is provided with an attaching portion (not shown) through which a second pin 147b to be described later is inserted. Further, the front end of the first return spring 144a is fixed to the first support member 143a. The first return spring 144a extends from the first support member 143a toward the swash plate chamber 330 in the axial direction O2.

10, the second support member 143b is press-fitted into the rear end side of the drive shaft main body 300 and is positioned in the second shaft hole 123b. At the front end of the second support member 143b, a flange 431 is formed which is in contact with the second thrust bearing 135b. Also, O-rings 73a and 73b are provided on the second support member 143b.

As shown in Fig. 8, the swash plate chamber 50 is formed in an annular flat plate shape and includes a front face 50a and a rear face 50b. The front face 50a faces the front of the compressor in the swash plate chamber 330. [ Further, the rear face 50b faces the rear of the compressor in the swash plate chamber 330. [

The swash plate 50 is fixed to the ring plate 145. The ring plate 145 is formed in an annular flat plate shape. At the center of the ring plate 145, an insertion hole 145a is formed. The drive shaft main body 300 is inserted through the insertion hole 145a in the swash plate chamber 330 and the swash plate 50 is attached to the drive shaft 30. [

The link mechanism 70 includes a lug arm 149. The lug arm 149 is disposed further forward than the swash plate 50 in the swash plate chamber 300 and is positioned between the swash plate 50 and the first support member 143a. The lug arm 149 is formed to have a substantial L-shape from the front side to the rear side. A weight portion 149a is formed at the rear end side of the lug arm 149. [ The weight portion 149a extends beyond the half of the circumference of the actuator 160 in the circumferential direction. The shape of the weight portion 149a can be appropriately designed.

The rear end side of the lug arm 149 is connected to the one end side of the ring plate 145 by the first pin 147a. As a result, the rear end side of the lug arm 149 is rotatable about the first rotation axis M1, which is the axis of the first pin 147a, with respect to the one end side of the ring plate 145, . The first rotation axis M1 extends in a direction orthogonal to the axial direction O2 of the drive shaft 30. [

The front end side of the lug arm 149 is connected to the first supporting member 143a by the second pin 147b. As a result, the front end side of the lug arm 149 is rotatable about the second support member 143a, i.e., the drive shaft 30, around the second rotation axis M2, which is the axis of the second pin 147b . The second rotation axis M2 extends parallel to the first rotation axis M1. The link mechanism 70 is constituted by the lug arm 149, the first pin 147a and the second pin 147b.

The weight portion 149a is provided on the rear end side of the lug arm 149, that is, on the opposite side of the second rotation axis M2 with respect to the first rotation axis M1. Since the lug arm 149 is supported by the ring plate 145 by the first pin 147a, the weight portion 149a is moved rearward with respect to the ring plate 145, that is, And is positioned rearward of the rear surface 50b of the swash plate 50 through the groove portion 145b. The centrifugal force generated by the rotation of the swash plate 50 about the axial direction O2 also acts on the weight portion 149a on the rear end side of the rear surface 50b of the swash plate 50. [

In the compressor of this embodiment, the swash plate 50 and the drive shaft 30 are connected by a link mechanism 70, whereby the swash plate 50 and the drive shaft 30 can rotate together. Both ends of the lug arm 149 rotate around the first rotation axis M1 and the second rotation axis M2, respectively, whereby the swash plate 50 can change the inclination angle.

Each of the pistons 90 includes a first head portion 90a on the front end side and a second head portion 90b on the rear end side. Each of the first head portions 90a is reciprocably received in each of the first cylinder bores 121a. The first compression chambers 121d are partitioned by the first head portions 90a and the first valve forming plates 139 in the respective first cylinder bores 121a. Each of the second head portions 90b is reciprocably received in each second cylinder bore 123a. Each of the second compression chambers 123d is partitioned by each second head portion 90b and each second valve forming plate 141 in each second cylinder bore 123a.

In addition, a coupling portion 90c is formed at the center of each piston 90. Each of the engaging portions 90c is provided with hemispherical shoes 110a and 110b. The swash plate 50 is rotated by the shoes 110a and 110b to be reciprocated by the piston 90. [ The shoes 110a and 110b correspond to the switching mechanism in the present invention. In this way, in the compressor of the present embodiment, each of the first head portion 90a and the second head portion 90b is formed so that the stroke corresponding to the inclination angle of the swash plate 90 causes each of the first cylinder bores 121a and the second And is reciprocally movable within the cylinder bore 123a. 11, in the compressor of this embodiment, as the inclination angle of the swash plate 50 decreases, the top dead center position of the second head portion 90b is larger than the top dead center position of the first head portion 90a Move.

The actuator 160 is disposed in the swash plate chamber 330. The actuator 160 is positioned rearward with respect to the swash plate 50 and can enter the interior of the second recess 123c. As shown in Fig. 10, the actuator 160 includes a movable body 160a, a partition body 160b, and a control pressure chamber 160c. The control pressure chamber 160c is formed between the movable body 160a and the partition body 160b.

The movable member 160a includes an inner sliding portion 161, a bottom wall 162, a peripheral wall 163, and a connecting portion 164. The inner sliding portion 161 is located at the rear end of the movable body 160a. The drive shaft main body 300 is inserted through the inner sliding portion 161. [ As a result, the inner sliding portion 161 is slidably provided to the drive shaft main body 300. The inner sliding portion 161 is provided with an O-ring 73c. The bottom wall 162 extends from the rear end of the peripheral wall 163 toward the drive shaft main body 300 at the rear end of the movable body 160a. The bottom wall 162 is connected to the inner sliding portion 161. The circumferential wall 163 extends from the tip of the bottom wall 162 toward the tip in the axial direction O2. Therefore, the peripheral wall 163 is formed into a cylindrical shape concentric with the axial direction O2. As shown in Fig. 8, the connecting portion 164 is formed at the front end of the circumferential wall 163.

As shown in Fig. 10, the partition 160b is formed in a disk shape having a diameter substantially equal to the inner diameter of the peripheral wall 163. A fixing portion 165 is provided on the center side of the partition member 160b. The drive shaft body 300 is press-fitted into the fixed portion 165 and the fixed portion 165 is fixed to the drive shaft 30. [ An O-ring 73d is provided on the outer peripheral surface of the partition member 160b. The partition 160b may be provided movably in the axial direction O2 on the drive shaft 30. [

As shown in Fig. 8, a second return spring 144b is provided between the partition 160b and the ring plate 145. As shown in Fig. Specifically, the rear end of the second return spring 144b is fixed to the partition member 160b. And the front end of the second return spring 144b is fixed to the other end side of the ring plate 145. [

The drive shaft main body 300 is inserted through the inner sliding portion 161 and the fixing portion 165 so that the movable body 160a has the movable body 160a in the second concave portion 123c And is disposed so as to face the link mechanism 70 across the swash plate 50 in the accommodated state. On the other hand, the partition member 160b is disposed in the movable member 160a further rearward than the swash plate 50. [ The outer circumferential surface of the partition member 160b is surrounded by the circumferential wall 163. As a result, a control pressure chamber 160c is formed between the movable body 160a and the partition body 160b. The control pressure chamber 160c is separated from the swash plate chamber 330 by the movable body 160a and the partition body 160b.

As shown in Fig. 10, a throttle hole 75 is formed in the partition member 160b. The throttle hole 75 extends from the control pressure chamber 160c toward the swash plate chamber 330. More specifically, the throttle hole 75 is controlled so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 75 is supplied to the sliding portion between the inner wall 163a of the peripheral wall 163 and the partition member 160b. And extends obliquely upward from the pressure chamber 160c toward the swash plate chamber 330. [ The control pressure chamber 160c and the swash plate chamber 330 communicate with each other through the throttle hole 75. [

As shown in Fig. 8, the other end of the ring plate 145 is connected to the connecting portion 164 of the movable body 160a by the third pin 147c. As a result, the other end side of the ring plate 145, that is, the swash plate 50 is rotatably supported by the movable body 160a around the action axis M3, which is the axis of the third pin 147c. The actuation axis M3 extends parallel to the first rotational axis M1 and the second rotational axis M2. In this way, the movable member 160a is connected to the swash plate 50. [

The drive shaft main body 300 is provided with an axial path 30a extending forward from the rear end in the axial direction O2 and an axial path 30b extending in the radial direction from the front end of the axial path 30a, A radial path 30b that opens to the outer circumferential surface is formed. The rear end of the axial path 30a is opened in the pressure regulating chamber 131. [ On the other hand, the radial path 30b opens into the control pressure chamber 160c. As a result, the control pressure chamber 160c communicates with the pressure regulating chamber 131 via the radial path 30b and the axial path 30a.

A screw portion 30d is formed at the tip of the drive shaft main body 300. [ The drive shaft 30 is connected to a pulley or electromagnetic clutch not shown in the drawing through a threaded portion 30d.

9, the control mechanism 150 includes a low-pressure passage 150a, a high-pressure passage 150b, a low-pressure control valve 150c, a high-pressure control valve 150d, an axial passage 30a, A throttle hole 30b, and the throttle hole 75 described above.

The low pressure passage 150a is connected to the pressure regulation chamber 131 and the second suction chamber 127b. As a result, the control pressure chamber 160c, the pressure regulating chamber 131, and the second suction chamber 127b are communicated with each other through the low-pressure passage 150a, the axial passage 30a, and the radial passage 30b Communicate. In the present invention, the additional passage is formed by the low-pressure passage 150a, the axial passage 30a, the radial passage 30b, and the throttle hole 75. [

The high pressure passage 150b is connected to the pressure regulation chamber 131 and the second discharge chamber 129b. The control pressure chamber 160c, the pressure regulation chamber 131 and the second discharge chamber 129b communicate with each other through the high pressure passage 150b, the axial passage 30a, and the radial passage 30b. In the present invention, the supply passage is formed by the high-pressure passage 150b, the axial passage 30a, and the radial passage 30b.

The low-pressure passage 150a is provided with a low-pressure control valve 150c. The low pressure control valve 150c can adjust the opening of the low pressure passage 150a based on the pressure of the second suction chamber 127b. The high-pressure passage 150b is also provided with a high-pressure control valve 150d. The high-pressure control valve 150d can adjust the opening of the high-pressure passage 150b based on the pressure of the second suction chamber 127b.

In the compressor of the present embodiment, a pipe connected to the evaporator is connected to the inlet 330a shown in Fig. The outlet 126 is connected to a pipe connected to the condenser. The condenser is connected to the evaporator through a pipe and an expansion valve.

In the compressor constructed as described above, the drive shaft 30 rotates to rotate the swash plate, and the piston 90 reciprocates within the first cylinder bore 121a and the second cylinder bore 123a. Therefore, in accordance with the piston stroke, a capacity change occurs in the first compression chamber 121d and the second compression chamber 123d. Thus, the compressor compresses the refrigerant gas in the suction stroke, the first compression chamber 121d and the second compression chamber 123d for sucking the refrigerant gas into the first compression chamber 121d and the second compression chamber 123d A discharge stroke for discharging the compressed refrigerant gas to the first discharge chamber 129a and the second discharge chamber 129b, and the like.

The refrigerant gas discharged into the first discharge chamber 129a reaches the integrated discharge chamber 128 through the first discharge communication path 118. [ Similarly, the refrigerant gas discharged into the second discharge chamber 129d reaches the integrated discharge chamber 128 through the second discharge communication passage 120. [ The refrigerant gas reaching the integrated discharge chamber 128 is discharged from the discharge port 126 to the condenser.

The piston compression force for reducing the inclination angle of the swash plate 50 is transmitted to the swash plate 50 through the swash plate 50, the ring plate 145, the lug arm 149 and the first pin 147a, Lt; / RTI > Further, in the compressor of the present embodiment, as in the above-described compressor, when the inclination angle of the swash plate 50 is changed, the capacity control can be performed by increasing and decreasing the stroke of the piston 90.

More specifically, in the control mechanism 150, the high-pressure control valve 150d shown in Fig. 9 performs opening control of the high-pressure passage 150b, thereby causing the pressure in the pressure control chamber 131, The pressure in the first discharge chamber 160c is increased by the refrigerant gas in the second discharge chamber 129b. Further, opening regulation of the low-pressure passage 150a by the low-pressure control valve 150c is performed, thereby reducing the pressure in the control-pressure chamber 160b.

Further, in the compressor of the present embodiment, as in the above-described compressor, the refrigerant gas in the control pressure chamber 160c is discharged to the swash plate chamber 330 through the throttle hole 75. [ In this way, in the compressor of this embodiment, by controlling the opening of each of the high-pressure passage 150b and the low-pressure control valve 150c and discharging the refrigerant gas by the throttle hole 75, the pressure in the control- .

When the high-pressure control valve 150d reduces the opening of the high-pressure passage 150b or when the low-pressure control valve 150c increases the opening of the low-pressure passage 150a, the pressure in the control-pressure chamber 160c decreases. In this case, as described above, the refrigerant gas in the control pressure chamber 160c is discharged to the swash plate chamber 330 through the throttle hole 75. [ Thus, the pressure in the control pressure chamber 160c decreases, and the pressure difference between the control pressure chamber 160c and the swash plate chamber 330 decreases. 11, the actuator 160 moves the movable member 160a forward from the second recess 123c by the piston compressive force acting on the swash plate 50. As a result,

As a result, the other end side of the ring plate 145, that is, the other end side of the swash plate 50 rotates clockwise around the acting axis M3 while resisting the pressing force of the second return spring 144b. Further, the rear end of the lug arm 149 rotates clockwise around the first rotation axis M1. The front end of the lug arm 149 rotates counterclockwise around the second rotation axis M2. Thus, the lug arm 149 approaches the flange 430 of the first support member 143a. As a result, the swash plate 50 rotates with the acting axis M3 as the acting point and the first rotating axis M1 as the supporting point. Therefore, the inclination angle of the swash plate 50 with respect to the axial direction O2 of the drive shaft 30 is reduced. The stroke of the piston 90 decreases. Therefore, in the compressor of this embodiment, the discharge capacity per rotation of the drive shaft 30 decreases. The inclination angle of the swash plate 50 shown in Fig. 11 is the minimum inclination angle in the compressor.

In the compressor of the present embodiment, the centrifugal force acting on the weight portion 149a is also applied to the swash plate 50. [ Therefore, in the compressor of the present embodiment, the swash plate 50 is easily displaced in the direction for reducing the inclination angle of the swash plate 50. [

Also, the inclination angle of the swash plate 50 is reduced, and the ring plate 145 comes into contact with the rear end of the first return spring 144a. As a result, the first return spring 144a is elastically deformed. The rear end of the first return spring 144a approaches the first support member 143a.

In the compressor of the present embodiment, the inclination angle of the swash plate 50 is reduced and the stroke of the piston 90 is reduced so that the top dead center position of the second head portion 90b is away from the second valve forming plate 141 Move. Therefore, in the compressor of this embodiment, when the inclination angle of the swash plate 50 approaches 0 degree, compression work is slightly performed in the first compression chamber 121d. On the other hand, no compression work is performed in the second compression chamber 123d.

On the other hand, if the high-pressure control valve 150d shown in Fig. 9 increases the opening of the high-pressure passage 150b or the low-pressure control valve 150c reduces the opening of the low-pressure passage 150a, ) Increases. The pressure difference between the control pressure chamber 160c and the swash plate chamber 330 increases. In this case, as described above, the refrigerant gas in the control pressure chamber 160c is discharged to the swash plate chamber 330 through the throttle hole 75. [ 8, in the actuator 160, the movable member 160a moves rearward from the second recess 123c while resisting the piston compression force acting on the swash plate 50. As shown in Fig.

As a result, in the operation axis M3, the movable member 160a pulls back the other end side of the swash plate 50 in the swash plate chamber 330 through the connecting portion 164. As a result, the other end side of the swash plate 50 rotates counterclockwise around the operation axis M3. Further, the rear end of the lug arm 149 rotates counterclockwise around the first rotation axis M1. The front end of the lug arm 149 rotates clockwise around the second rotation axis M2. Thus, the lug arm 149 is separated from the flange 430 of the first support member 143a. As a result, the swash plate 50 rotates in a direction opposite to the direction in which the inclination angle decreases, with the action axis M3 and the first rotation axis M1 as the action point and the support point, respectively. Accordingly, the inclination angle of the swash plate 50 relative to the rotation axis O2 of the drive shaft 30 increases, and the stroke of the piston 90 increases. As a result, the discharge capacity per rotation of the drive shaft 30 increases. The inclination angle of the swash plate 50 shown in Fig. 8 is the maximum inclination angle in the compressor.

As described above, in the compressor of the present embodiment, when the pressure in the control pressure chamber 160c is adjusted as well as the opening degree of each of the high pressure passage 150b and the low pressure control valve 150c, the refrigerant gas is supplied to the control pressure chamber 160c, To the swash plate chamber (330) through the throttle hole (75). Therefore, in the compressor of this embodiment, when the pressure in the control pressure chamber 160c is adjusted, it is not necessary to completely seal the control pressure chamber 160c. It is sufficient that the control pressure chamber 160c is sealed by the O-rings 73c and 73d.

Further, in the compressor of the present embodiment, when the refrigerant gas in the second discharge chamber 129b is introduced into the control pressure chamber 160c, even if the lubricant is introduced into the control pressure chamber 160c together with the refrigerant gas, And is discharged from the inside of the control pressure chamber 160c to the swash plate chamber 330 through the throttle hole 75 together with the gas. Therefore, in the compressor of the present embodiment, as in the compressor of the first embodiment, the lubricating oil is not easily stored in the control pressure chamber 160c. The lubricant shortage in the swash plate chamber 330 does not easily occur.

10, the throttle hole 75 is formed such that the lubricating oil discharged from the throttle hole 75 together with the refrigerant gas flows through the inner wall 163a of the peripheral wall 163 and the partition wall 160b, So as to be fed to the sliding portion between the control pressure chamber 160c and the swash plate chamber 330. [ Therefore, in the compressor of the present embodiment, when the inclination angle of the swash plate 50 increases from the minimum state, that is, when the movable body 160a moves backward from the second concave portion 123c, And lubricates the inside of the circumferential wall 163. In the peripheral wall 163, the front side of the partition 160b communicates with the swash plate chamber 330. In the compressor of the present embodiment, the inner wall 163a of the peripheral wall 163 is appropriately lubricated by the lubricating oil. Therefore, the peripheral wall 163 can appropriately slide on the outer peripheral surface of the partition member 160b. Therefore, in the compressor of the present embodiment, the discharge capacity per rotation of the drive shaft 30 can be appropriately changed over a long period of time.

(Sixth Embodiment)

As shown in Fig. 12, in the compressor of the sixth embodiment, the throttle hole 77 is provided instead of the throttle hole 75 in the compressor of the fifth embodiment. The throttle hole 77 is formed in the bottom wall 162 of the movable body 160a. The throttle hole 77 extends from the control pressure chamber 160c toward the second thrust bearing 135b so that lubricating oil discharged from the throttle hole 77 together with the refrigerant gas is supplied to the second thrust bearing 135b . As a result, the control pressure chamber 160c and the swash plate chamber 330 communicate with each other through the throttle hole 77. [ In the compressor of the present embodiment, the additional passage of the present invention is formed by the low-pressure passage 150a, the axial passage 30a, the radial passage 30b, and the throttle hole 77. [ The other components of the compressor are the same as those of the compressor of the fifth embodiment.

In the compressor of the present embodiment, when the pressure in the control pressure chamber 160c is adjusted as well as the opening degree of each of the high pressure passage 150b and the low pressure control valve 150c, the refrigerant gas is supplied from the inside of the control pressure chamber 160c And is discharged to the swash plate chamber 330 through the hole 77. In the compressor of the present embodiment, the throttle hole 77 is communicated from the control pressure chamber 160c to the second thrust bearing (not shown) so that the lubricating oil discharged from the throttle hole 77 together with the refrigerant gas is supplied to the second thrust bearing 135b 135b. Therefore, in the compressor of the present embodiment, when the movable body 160a moves backward from the second recess 123c, the lubricating oil in the control pressure chamber 160c flows from the throttle hole 77 together with the refrigerant gas to the second thrust bearing (135b). In the compressor of the present embodiment, the movable member 160a moves rearward in the second recess 123c, thereby gradually approaching the movable member 160a and the second thrust bearing 135b. As a result, in the compressor of this embodiment, the second thrust bearing 135b can be appropriately lubricated by the lubricating oil discharged from the throttle hole 77. [ Therefore, in the compressor of this embodiment, the sticking phenomenon in the second thrust bearing 135b does not easily occur, and the durability can be improved. The other operation of the compressor is the same as that of the compressor of the fifth embodiment.

The present invention has been described according to the first to sixth embodiments. However, the present invention is not limited to the first to sixth embodiments. It is needless to say that the present invention can be suitably changed and applied without departing from the gist thereof.

For example, the compressor may be configured by suitably combining the compressors of the first to fourth embodiments. Further, the compressor may be configured by combining the compressor of the fifth embodiment and the compressor of the sixth embodiment.

Further, a three-way valve may be employed in place of the low-pressure control valves 15c and 150c and the high-pressure control valves 15d and 150d. In this case, the three-way valve corresponds to the control valve in the present invention. The high-pressure control valves 15d and 150d may be arranged only in the high-pressure passages 15b and 150b.

Further, in the compressors of the fifth and sixth embodiments, the compression chambers may be configured to be formed by only one first cylinder block 121 and the second cylinder block 123 alone.

Claims (5)

A variable displacement swash plate compressor,
A housing formed with a suction chamber, a discharge chamber, a swash plate chamber, and a cylinder bore;
A drive shaft rotatably supported by the housing;
A swash plate rotatable in the swash plate chamber in accordance with rotation of the drive shaft;
A link mechanism provided between the drive shaft and the swash plate and configured to change an inclination angle of the swash plate with respect to a direction orthogonal to the axis of the drive shaft;
A piston received in the cylinder bore such that the piston reciprocates;
A switching mechanism (11a, 11b) connecting the outer periphery of the swash plate and the piston to reciprocate the piston in the cylinder bore with a stroke corresponding to the inclination angle in accordance with rotation of the swash plate;
An actuator capable of changing the inclination angle; And
A control mechanism configured to control the actuator;
Lt; / RTI >
The swash plate chamber communicates with the suction chamber,
The actuator includes:
A partition provided on the drive shaft in the swash plate chamber;
A movable body movable in the axial direction of the drive shaft in the swash plate chamber; And
A control pressure chamber partitioned by the partition and the movable body and configured to move the movable body by an internal pressure;
Lt; / RTI >
The control mechanism includes:
A supply passage communicating with the discharge chamber and the control pressure chamber and introducing the refrigerant in the discharge chamber into the control pressure chamber; And
A replacement passage communicating with the control pressure chamber and the swash plate chamber for discharging the refrigerant in the control pressure chamber into the swash plate chamber;
Lt; / RTI >
Characterized in that the additional passage includes at least one of the movable body and the partition and a communication passage for discharging the lubricating oil from the control pressure chamber to the swash plate chamber together with the refrigerant, . The method according to claim 1,
Wherein the partition body includes an outer sliding portion that extends in the axial direction of the drive shaft and slidably surrounds the movable body,
Wherein the movable body comprises:
A first cylindrical portion disposed adjacent to the swash plate around the drive shaft;
A second cylindrical portion formed into a cylindrical shape having a larger diameter than the first cylindrical portion; And
A connecting portion connecting the first cylindrical portion and the second cylindrical portion;
Lt; / RTI >
Wherein the communication passage is formed in the second cylindrical portion or the connecting portion so that lubricating oil discharged from the communication path together with the refrigerant is supplied to a sliding portion between the movable body and the outer sliding portion. A swash plate compressor. The method according to claim 1,
The partition is fixed to the drive shaft,
A thrust bearing receiving thrust acting on the drive shaft is provided between the partition and the housing,
A radial bearing for receiving a radial force acting on the drive shaft is provided between the housing and the drive shaft,
A shaft sealing device is provided between the housing and the drive shaft to ensure sealing between the inside and the outside of the housing,
Characterized in that the communication passage is formed in the partition body so that lubricating oil discharged from the communication passage together with the refrigerant is supplied to the thrust bearing, the radial bearing, or the shaft sealing apparatus. . The method according to claim 1,
Wherein the movable body includes a peripheral wall sliding on the partition and extending in the axial direction of the drive shaft and surrounding the partition and a bottom wall extending from the peripheral wall toward the drive shaft,
Wherein the communication passage is formed in the partition body so that lubricating oil discharged from the communication passage together with the refrigerant is supplied to the sliding portion between the peripheral wall and the partition body. The method according to claim 1,
Wherein the movable body includes a peripheral wall sliding on the partition and extending in the axial direction of the drive shaft and surrounding the partition and a bottom wall extending from the peripheral wall toward the drive shaft,
A thrust bearing receiving thrust acting on the drive shaft is provided between the movable body and the housing,
Wherein the communication passage is formed in the movable body so that lubricating oil discharged from the communication path together with the refrigerant is supplied to the thrust bearing.

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