WO2015037637A1 - 容量可変型斜板式圧縮機 - Google Patents
容量可変型斜板式圧縮機 Download PDFInfo
- Publication number
- WO2015037637A1 WO2015037637A1 PCT/JP2014/073985 JP2014073985W WO2015037637A1 WO 2015037637 A1 WO2015037637 A1 WO 2015037637A1 JP 2014073985 W JP2014073985 W JP 2014073985W WO 2015037637 A1 WO2015037637 A1 WO 2015037637A1
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- WIPO (PCT)
- Prior art keywords
- swash plate
- chamber
- drive shaft
- compressor
- movable body
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1072—Pivot mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1045—Cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1063—Actuating-element bearing means or driving-axis bearing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
Definitions
- the present invention relates to a variable capacity swash plate compressor.
- Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter referred to as a compressor).
- the compressor includes a housing, a drive shaft, a swash plate, a link mechanism, a plurality of pistons, a conversion mechanism, and a capacity control mechanism.
- the housing has a suction chamber, a discharge chamber, a swash plate chamber, and a plurality of cylinder bores.
- the drive shaft is rotatably supported by the housing.
- the swash plate can be rotated in the swash plate chamber by the 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 with respect to the direction orthogonal to the drive axis of the drive shaft.
- This link mechanism has a lug member and a transmission member.
- the lug member is fixed to the drive shaft in the swash plate chamber.
- the transmission member is provided integrally with the swash plate in the swash plate chamber, and transmits the rotation of the lug member to the swash plate.
- Each piston is accommodated in each cylinder bore so as to be able to reciprocate.
- the conversion mechanism reciprocates each piston in each cylinder bore with a stroke corresponding to the inclination angle by the rotation of the swash plate.
- the capacity control mechanism has an air supply passage, an extraction passage, and a control valve.
- the air supply passage communicates the discharge chamber and the swash plate chamber.
- the extraction passage communicates the swash plate chamber and the suction chamber.
- the control valve can change the pressure in the swash plate chamber by adjusting the opening of the air supply passage.
- This compressor includes an actuator capable of changing an inclination angle and a control mechanism for controlling the actuator.
- the actuator is partitioned by a lug member, a movable body that engages with the swash plate so as to be integrally rotatable, can move in the direction of the drive axis, and can change an inclination angle, and the lug member and the movable body.
- a control pressure chamber for moving the movable body by the internal pressure.
- the control mechanism has a control passage and a control valve.
- the control passage has a variable pressure passage communicating with the control pressure chamber, a low pressure passage communicating with the suction chamber and the swash plate chamber, and a high pressure passage communicating with the discharge chamber.
- a part of the transformation passage is formed in the drive shaft.
- the control valve adjusts the opening degree of the variable pressure passage, the low pressure passage, and the high pressure passage. That is, the control valve communicates the variable pressure passage with the low pressure passage or the high pressure passage.
- the control valve connects the variable pressure passage to the high pressure passage, the control pressure chamber becomes higher in pressure than the swash plate chamber. Thereby, the movable body of the actuator moves away from the lug member, and the inclination angle decreases. For this reason, the stroke of the piston is reduced and the discharge capacity is reduced.
- the control valve connects the variable pressure passage to the low pressure passage, the control pressure chamber is at a low pressure as much as the swash plate chamber. As a result, the movable body of the actuator approaches the lug member, and the inclination angle increases. For this reason, the stroke of the piston increases and the discharge capacity increases.
- the amount of refrigerant required for changing the tilt angle may be less than that of the compressor that changes the pressure in the swash plate chamber. It is possible to achieve downsizing.
- the movable body of the actuator and the swash plate are orthogonal to the first virtual plane determined by the top dead center corresponding portion defined in the swash plate and the drive axis. Are engaged on the second virtual plane including the drive axis. More specifically, the movable body and the swash plate are engaged by a hinge sphere having a center on the drive axis. The working position where the movable body and the hinge sphere come into contact changes in parallel with the axial direction of the drive shaft as the inclination angle of the swash plate changes. The same applies to the action position where the hinge sphere and the swash plate abut. That is, in this compressor, even if the inclination angle of the swash plate changes, the distance between the operating position and the drive shaft center does not change.
- variable differential pressure the differential pressure between the swash plate chamber and the control pressure chamber (hereinafter referred to as variable differential pressure) and move the movable body with a larger thrust.
- variable differential pressure the differential pressure between the swash plate chamber and the control pressure chamber
- the load on the movable body when the inclination angle is reduced is large.
- the amount of change in the variable differential pressure when changing the inclination angle is large, and it becomes difficult to change the inclination angle quickly according to the driving situation of the vehicle or the like, and the controllability is reduced.
- the present invention has been made in view of the above-described conventional situation, and solves the problem of providing a variable displacement swash plate compressor capable of exhibiting high controllability and exhibiting excellent mountability. It should be a challenge.
- a variable capacity swash plate compressor includes a housing in which a swash plate chamber and a cylinder bore are formed, a drive shaft rotatably supported by the housing, and rotation in the swash plate chamber by rotation of the drive shaft.
- a swash plate a link mechanism provided between the drive shaft and the swash plate and allowing a change in the inclination angle of the swash plate with respect to a direction orthogonal to the drive shaft center of the drive shaft; and reciprocating motion to the cylinder bore
- the link mechanism includes a lug member fixed to the drive shaft in the swash plate chamber, and a transmission member that transmits the rotation of the lug member to the swash plate.
- the actuator can be rotated integrally with the lug member and the swash plate, and is partitioned by a movable body that can move in the drive axis direction and change the tilt angle, and the lug member and the movable body.
- a control pressure chamber that moves the movable body by changing an internal pressure by the control mechanism
- the movable body is formed with an action portion capable of pressing the swash plate by the pressure in the control pressure chamber
- the swash plate is formed with an acted part that is pressed against the acting part, The acting part and the acted part abut at the acting position,
- the action position moves by changing the tilt angle
- the swash plate defines a top dead center corresponding portion that positions the piston at the top dead center, The action position when the inclination angle is maximum is closer to the top dead center corresponding portion than the action position when the inclination angle is minimum.
- the transmission member of the link mechanism transmits the rotation of the lug member to the swash plate.
- the action position where the action part of a movable body and the to-be-acted part of a swash plate contact is moved by the change of the inclination angle of a swash plate. Specifically, the action position when the inclination angle is maximum is closer to the top dead center corresponding portion of the swash plate than the action position when the inclination angle is minimum.
- this compressor when the inclination angle is reduced, a large thrust is ensured as compared with the case where the distance between the operating position and the drive shaft center is constant even if the inclination angle of the swash plate changes.
- the movable body can be moved without increasing the variable differential pressure. That is, in this compressor, the load on the movable body when the inclination angle is reduced can be reduced. For this reason, in this compressor, the change amount of the variable differential pressure when changing the tilt angle is small, and the tilt angle can be easily changed quickly according to the driving situation of the vehicle or the like, and high controllability can be exhibited.
- the compressor of the present invention can exhibit high controllability and exhibits excellent mountability.
- the posture of the movable body may change depending on the configuration of the connecting portion. Further, the increase in the number of parts complicates the configuration of the compressor and increases the manufacturing cost.
- the compressor of the present invention when the inclination angle of the swash plate is changed, the movable body only presses while directly contacting the swash plate, and the posture of the movable body is difficult to change. In addition, in this compressor, it is possible to suppress the complexity of the configuration and to realize a reduction in manufacturing cost.
- the control mechanism can have a control passage and a control valve.
- the control passage may include a variable pressure passage communicating with the control pressure chamber, a low pressure passage communicating with the suction chamber or the swash plate chamber, and a high pressure passage communicating with the discharge chamber.
- the movable body is inserted through the drive shaft and can be fitted to the lug member. In this case, it is possible to suitably secure a space for the movable body to move in the drive axis direction between the lug member and the swash plate.
- the movable body may have a movable cylindrical portion having a cylindrical shape coaxial with the drive axis.
- the lug member preferably has a cylindrical shape coaxial with the drive shaft on the outer peripheral side of the movable cylindrical portion, and has a cylindrical fixed cylindrical portion that secures a control pressure chamber in the movable cylindrical portion.
- the movable body can be fitted to the lug member by fitting the movable cylindrical portion to the fixed cylindrical portion.
- the control pressure chamber since the control pressure chamber is secured in the movable cylinder portion by the fixed cylinder portion, the control pressure chamber can be suitably formed between the lug member and the movable body.
- a first sealing means for sealing the control pressure chamber may be provided between the movable cylindrical portion and the drive shaft.
- the 2nd sealing means which seals a control pressure chamber is provided between the movable cylinder part and the fixed cylinder part.
- the first sealing means and the second sealing means it is possible to employ various sealing materials in addition to an O-ring or the like. Further, the first sealing means and the second sealing means may be the same type or different.
- a thrust bearing that receives a thrust force acting on the piston may be provided between the housing and the lug member.
- the movable cylindrical portion preferably has a smaller diameter than the thrust bearing and can be fitted into the thrust bearing.
- the thrust bearing can favorably support the suction reaction force acting on the piston during the suction stroke and the compression reaction force acting on the piston during the compression stroke.
- the movable cylindrical portion can be fitted into the thrust bearing, it is possible to secure a sufficient space for the movable body to move in the direction of the drive shaft even if the axial length of the compressor is short. Become.
- the action part and the action part are in point contact or line contact with each other at the action position.
- the contact area between the action part and the action part can be reduced.
- the straight line that makes line contact is orthogonal to the first virtual plane determined by the top dead center corresponding portion of the swash plate and the drive axis.
- one of the contact part of the action part with the action part or the contact part of the action part with the action part is formed on a curved surface. It is preferable that
- the position where the action part is formed on the movable body and the position where the action part is formed on the swash plate can be designed as appropriate.
- the action part and the acted part can be eccentric from the drive shaft center to the top dead center corresponding part side. And it is preferable that the action position moves toward the drive shaft center side when the inclination angle becomes smaller.
- the action part may have an action surface extending in a direction perpendicular to the drive axis. And it is preferable that the to-be-acted part has the convex part which protrudes from a swash plate and contact
- the action part protrudes on the top dead center corresponding part side in the movable cylindrical part. In this case, the action part and the acted part can be easily brought into contact with each other.
- the swash plate preferably has a swash plate body in which an insertion hole through which the drive shaft is inserted is formed, and an actuated part formed integrally with the swash plate body. In this case, it is possible to reduce the number of parts in the compressor, which facilitates manufacture and reduces manufacturing costs.
- the swash plate has a swash plate body in which an insertion hole through which the drive shaft is inserted is formed, and an actuated portion fixed to the swash plate body. In this case, it is possible to increase the degree of design freedom in the swash plate body and the acted part.
- a suction chamber and a discharge chamber can be formed in the housing.
- the suction chamber and the swash plate chamber are preferably in communication.
- the swash plate chamber can be set to a low pressure similarly to the suction chamber.
- control mechanism may have a control passage that communicates the control pressure chamber with the suction chamber and / or the discharge chamber, and a control valve that can adjust the opening of the control passage. And it is preferable that at least a part of the control passage is formed in the drive shaft. In this case, it is possible to suitably change the pressure in the control pressure chamber while reducing the size of the control mechanism, and it is possible to suitably move the movable body.
- a pressure adjusting chamber that communicates with the control pressure chamber via the control passage and whose pressure is changed by the control valve.
- the 3rd sealing means which seals a pressure regulation chamber is provided between the housing and the drive shaft.
- control pressure chamber moves the movable body by changing the pressure of the pressure adjustment chamber by the control valve. And it becomes possible to ensure the airtightness of a pressure regulation chamber suitably by a 3rd sealing means.
- the third sealing means can employ various sealing materials in addition to the O-ring and the like, similar to the first and second sealing means. Further, the third sealing means may be the same type as or different from the first and second sealing means.
- the compressor of the present invention can exhibit high controllability and exhibits excellent mountability.
- FIG. 1 is a cross-sectional view of the compressor of the first embodiment at the maximum capacity.
- FIG. 2 is a schematic diagram illustrating a control mechanism according to the compressor of the first embodiment.
- FIG. 3 is an essential part enlarged cross-sectional view illustrating a rear end portion of a drive shaft according to the compressor of the first embodiment.
- FIG. 4 is an essential part enlarged cross-sectional view illustrating the actuator in the compressor according to the first embodiment.
- FIG. 5 is a front perspective view illustrating the swash plate according to the compressor of the first embodiment.
- FIG. 6 is a cross-sectional view of the compressor according to the first embodiment when the capacity is minimum.
- FIG. 7 is an essential part enlarged cross-sectional view showing an action part and an action part in the compressor according to the first embodiment.
- FIG. 5B shows the operation position when the tilt angle is the minimum.
- FIG. 8 is a graph showing the relationship between the tilt angle and the variable differential pressure.
- FIG. 9 is a schematic diagram illustrating the difference in the stroke of the movable body between the compressor of the first embodiment and the compressor of the comparative example.
- FIG. 10 is a cross-sectional view of the compressor of the second embodiment at the maximum capacity.
- Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings.
- the compressors of Examples 1 and 2 are variable capacity single-head swash plate compressors. All of these compressors are mounted on a vehicle, and constitute a refrigeration circuit of a vehicle air conditioner.
- Example 1 As shown in FIG. 1, the compressor according to 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 plurality of pairs of shoes 11a and 11b, and an actuator. 13 and a control mechanism 15 shown in FIG.
- the shape of the swash plate 5 is partially simplified for easy explanation. The same applies to FIGS. 6 and 10 described later.
- the housing 1 includes a front housing 17 located in front of the compressor, a rear housing 19 located behind the compressor, and a cylinder block located between the front housing 17 and the rear housing 19. 21 and a valve unit 23.
- the front housing 17 has a front wall 17a extending in the up-down direction of the compressor in front and a peripheral wall 17b integrated with the front wall 17a and extending rearward from the front of the compressor.
- the front housing 17 has a substantially cylindrical shape with a bottom by the front wall 17a and the peripheral wall 17b.
- a swash plate chamber 25 is formed in the front housing 17 by the front wall 17a and the peripheral wall 17b.
- a boss 17c that protrudes forward is formed on the front wall 17a.
- a shaft seal device 27 is provided in the boss 17c.
- a first shaft hole 17d extending in the front-rear direction of the compressor is formed in the boss 17c.
- a first sliding bearing 29a is provided in the first shaft hole 17d.
- a suction port 250 that communicates with the swash plate chamber 25 is formed in the peripheral wall 17b. Through the suction port 250, the swash plate chamber 25 is connected to an evaporator (not shown).
- the rear housing 19 is provided with a part of the control mechanism 15.
- the rear housing 19 is formed with a first pressure adjustment chamber 31a, a suction chamber 33, and a discharge chamber 35.
- the first pressure adjustment chamber 31 a is located at the center portion of the rear housing 19.
- the discharge chamber 35 is annularly positioned on the outer peripheral side of the rear housing 19.
- the suction chamber 33 is formed in an annular shape between the first pressure adjustment chamber 31 a and the discharge chamber 35 in the rear housing 19.
- the discharge chamber 35 is connected to a discharge port (not shown).
- each cylinder bore 21 a communicates with the swash plate chamber 25.
- the cylinder block 21 is formed with a retainer groove 21b that regulates the lift amount of a suction reed valve 41a, which will be described later.
- the cylinder block 21 is provided with a second shaft hole 21c extending in the front-rear direction of the compressor while communicating with the swash plate chamber 25.
- a second sliding bearing 29b is provided in the second shaft hole 21c.
- the cylinder block 21 has a spring chamber 21d.
- the spring chamber 21d is located between the swash plate chamber 25 and the second shaft hole 21c.
- a return spring 37 is disposed in the spring chamber 21d. The return spring 37 urges the swash plate 5 having the smallest inclination angle toward the front 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 unit 23 is provided between the rear housing 19 and the cylinder block 21.
- the valve unit 23 includes a valve plate 40, a suction valve plate 41, a discharge valve plate 43, and a retainer plate 45.
- valve plate 40, the discharge valve plate 43, and the retainer plate 45 the same number of intake ports 40a as the cylinder bores 21a are formed.
- the valve plate 40 and the intake valve plate 41 are formed with the same number of discharge ports 40b as the cylinder bores 21a.
- Each cylinder bore 21a communicates with the suction chamber 33 through each suction port 40a and also communicates with the discharge chamber 35 through each discharge port 40b.
- the valve plate 40, the suction valve plate 41, the discharge valve plate 43, and the retainer plate 45 are formed with a first communication hole 40c and a second communication hole 40d.
- the suction chamber 33 and the suction passage 39 communicate with each other through the first communication hole 40c.
- 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 each suction port 40a by elastic deformation.
- the discharge valve plate 43 is provided on the rear surface of the valve plate 40.
- the discharge valve plate 43 is formed with a plurality of discharge reed valves 43a capable of opening and closing each 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 lift amount 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 supported by the shaft seal device 27 in the boss 17c, and is supported by the first sliding bearing 29a in the first shaft hole 17d.
- the rear end side of the drive shaft 3 is pivotally supported by the second sliding bearing 29b in the second shaft hole 21c.
- a second pressure adjusting chamber 31b is defined between the rear end of the drive shaft 3 in the second shaft hole 21c.
- the second pressure regulation chamber 31b communicates with the first pressure regulation chamber 31a through the second communication hole 40d.
- ring grooves 3 c and 3 d are formed at the rear end of the drive shaft 3.
- O-rings 49a and 49b are provided in the ring grooves 3c and 3d, respectively.
- the pressure adjustment chamber 31 is sealed by the O-rings 49a and 49b, and the swash plate chamber 25 and the pressure adjustment chamber 31 are not in communication.
- Each of these O-rings 49a and 49b corresponds to the third sealing means in the present invention.
- 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 5e and 5f.
- the lug plate 51 corresponds to the lug member in the present invention.
- the swash plate arms 5e and 5f correspond to the transmission member in the present invention.
- the lug plate 51 is formed in a substantially annular shape.
- the lug plate 51 is press-fitted into the drive shaft 3 and can rotate integrally with the drive shaft 3.
- the lug plate 51 is located on the front end side in the swash plate chamber 25 and is disposed in front of the swash plate 5.
- a thrust bearing 55 is provided between the lug plate 51 and the front wall 17a.
- the lug plate 51 is provided with a cylindrical fixed cylindrical portion 51a extending in the front-rear direction of the lug plate 51. As shown in FIG. 1, the fixed cylindrical portion 51 a extends from the rear end surface of the lug plate 51 to a location inside the thrust bearing 55 in the lug plate 51.
- Each lug arm 53 extends rearward from the lug plate 51.
- the lug plate 51 is formed with a cam surface 51 b at a position between the lug arms 53. In FIG. 1 and the like, only one side of the lug arm 53 is shown for ease of explanation.
- the swash plate 5 has a swash plate body 50, swash plate arms 5e and 5f, and a convex portion 5g.
- This convex part 5g is equivalent to the to-be-acted part in this invention.
- the swash plate main body 50 has an annular flat plate shape, and has a front surface 5a and a rear surface 5b, and defines a top dead center corresponding portion T for positioning each piston 9 at the top dead center.
- the front surface 5 a is formed with a restricting portion 5 c that protrudes toward the front of the swash plate 5. As shown in FIG. 1, the restricting portion 5 c comes into contact with the lug plate 51 when the inclination angle of the swash plate 5 becomes maximum.
- the swash plate body 50 is formed with an insertion hole 5d. The drive shaft 3 is inserted through the insertion hole 5d.
- each swash plate arm 5 e, 5 f is formed on the front surface 5 a of the swash plate body 50 at a position eccentric from the drive axis O toward the top dead center corresponding portion T side of the swash plate 5. Yes.
- Each swash plate arm 5e, 5f extends forward from the front surface 5a.
- the convex portion 5g protrudes forward from the front surface 5a and is integrated with the swash plate body 50.
- the convex portion 5g is formed in a substantially hemispherical shape, and is eccentric to the top dead center corresponding portion T side of the swash plate 5 with respect to the drive axis O, and is located between the swash plate arm 5e and the swash plate arm 5f. ing.
- the swash plate arms 5e and 5f are 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 can rotate in the swash plate chamber 25 together with the lug plate 51.
- Each swash plate arm 5e, 5f is in contact with the cam surface 51b at each tip side.
- the swash plate arms 5 e, 5 f and the convex portion 5 g are offset from the drive axis O toward the top dead center corresponding portion T side of the swash plate 5. is doing.
- the swash plate arms 5e and 5f slide on the cam surface 51b, the swash plate 5 substantially maintains the position of the top dead center corresponding portion T with respect to its own inclination angle with respect to the direction orthogonal to the drive axis O.
- the actuator 13 includes a lug plate 51, a movable body 13a, and a control pressure chamber 13b.
- the movable body 13a is inserted through the drive shaft 3, and is movable in the direction of the drive axis O while being in sliding contact with the drive shaft 3.
- the movable body 13a has a cylindrical shape coaxial with the drive shaft 3, and is formed with a smaller diameter than the thrust bearing 55 shown in FIG.
- the movable body 13 a includes a first movable cylindrical portion 131, a second movable cylindrical portion 132, and a third movable cylindrical portion 133.
- the first movable cylindrical portion 131 is located on the rear end side of the movable body 13a and is formed to have the smallest diameter in the movable body 13a.
- the second movable cylindrical portion 132 is continuous with the front end of the first movable cylindrical portion 131, and is formed so that the diameter gradually increases toward the front of the movable body 13a.
- the third movable cylindrical portion 133 is continuous with the front end of the second movable cylindrical portion 132 and extends toward the front of the movable body 13a.
- the third movable cylindrical portion 133 is formed with the largest diameter in the movable body 13a.
- an action part 134 is integrally formed at the rear end of the first movable cylindrical part 131. As shown in FIG. 1, the action part 134 extends vertically from the drive axis O side toward the top dead center corresponding part T side of the swash plate 5, and the top dead center of the swash plate 5 from the drive axis O. It is eccentric to the corresponding part T side.
- This action part 134 has the action surface 134a formed in the plane. As shown in FIG. 7, the action surface 134 a makes point contact with the convex portion 5 g at the action position F. Thereby, the movable body 13a can rotate integrally with the lug plate 51 and the swash plate 5.
- the movable body 13a can be fitted to the lug plate 51 by causing the second movable cylindrical portion 132 and the third movable cylindrical portion 133 shown in FIG. 4 to enter the fixed cylindrical portion 51a (FIG. 1). In a state where the second movable cylindrical portion 132 and the third movable cylindrical portion 133 are most advanced into the fixed cylindrical portion 51a, the third movable cylindrical portion 133 is located inside the thrust bearing 55 within the fixed cylindrical portion 51a. Will come.
- the control pressure chamber 13 b is formed between the second movable cylindrical part 132, the third movable cylindrical part 133, the fixed cylindrical part 51 a, and the drive shaft 3.
- a ring groove 131a is formed on the inner peripheral surface of the first movable cylindrical portion 131
- a ring groove 133a is formed on the outer peripheral surface of the third movable cylindrical portion 133.
- O-rings 49c and 49d are provided in the ring grooves 131a and 133a, respectively.
- the O-ring 49c corresponds to the first sealing means in the present invention
- the O-ring 49d corresponds to the second sealing means in the present invention.
- the control pressure chamber 13b is sealed by these O-rings 49c and 49d, and the airtightness in the control pressure chamber 13b is secured.
- an axial path 3a extending in the direction of the drive axis O from the rear end to the front end of the drive shaft 3, and a drive shaft extending in the radial direction from the front end of the axial path 3a. 3 is formed on the outer peripheral surface of the main body 3.
- the rear end of the axis 3 a is open to the pressure adjustment chamber 31.
- the path 3b is open to the control pressure chamber 13b.
- the pressure adjusting chamber 31 and the control pressure chamber 13b communicate with each other by 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 screw portion 3e formed at the tip.
- Each piston 9 is housed in each cylinder bore 21a, and can reciprocate in each cylinder bore 21a.
- Each piston 9 and valve unit 23 define a compression chamber 57 in each cylinder bore 21a.
- each piston 9 is provided with an engaging portion 9a.
- hemispherical shoes 11a and 11b are respectively provided.
- Each shoe 11 a, 11 b converts the rotation of the swash plate 5 into the reciprocating motion of each piston 9.
- Each of these shoes 11a and 11b corresponds to a conversion mechanism in the present invention.
- each piston 9 can reciprocate within the cylinder bore 21a with a stroke corresponding to the inclination angle of the swash plate 5.
- a wobble type conversion mechanism that supports the swing plate on the rear surface 5b side of the swash plate main body 50 via a thrust bearing and connects the swing plate and each piston 9 by connecting rods. Can also be adopted.
- the control mechanism 15 includes a low pressure passage 15a, a high pressure passage 15b, a control valve 15c, an orifice 15d, an axial path 3a, and a radial path 3b.
- the low pressure passage 15a, the high pressure passage 15b, the axial passage 3a, and the radial passage 3b form a control passage in the present invention.
- the axial path 3a and the path 3b function as a transformation path.
- the low pressure passage 15 a is connected to the pressure adjusting chamber 31 and the suction chamber 33.
- the control pressure chamber 13b, the pressure adjusting chamber 31, and the suction chamber 33 are in communication with each other by the low pressure passage 15a, the axial passage 3a, and the radial passage 3b.
- the high-pressure passage 15 b is connected to the pressure adjustment chamber 31 and the discharge chamber 35.
- the control pressure chamber 13b, the pressure adjustment chamber 31, and the discharge chamber 35 are communicated with each other by the high pressure passage 15b, the axial path 3a, and the radial path 3b.
- the high pressure passage 15b is provided with an orifice 15d, and the flow rate of the refrigerant flowing through the high pressure passage 15b is reduced.
- the control valve 15c is provided in the low pressure passage 15a.
- the control valve 15c can adjust the flow rate of the refrigerant flowing through the low pressure passage 15a based on the pressure in the suction chamber 33.
- a pipe connected to the evaporator is connected to the suction port 250 shown in FIG. 1, and a pipe connected to the condenser is connected to the discharge port.
- the condenser is connected to the evaporator via a pipe and an expansion valve.
- the compression chamber 57 changes the volume according to the piston stroke. Therefore, the refrigerant sucked into the swash plate chamber 25 from the evaporator through the suction port 250 is compressed in the compression chamber 57 from the suction passage 39 through the suction chamber 33. The refrigerant compressed in the compression chamber 57 is discharged into the discharge chamber 35 and discharged from the discharge port to the condenser.
- a piston compression force that reduces the inclination angle of the swash plate 5 acts on the swash plate 5, the lug plate 51, and the like.
- the capacity control can be performed by changing the inclination angle of the swash plate 5 to increase or decrease the stroke of the piston 9.
- the control mechanism 15 if the control valve 15c shown in FIG. 2 increases the flow rate of the refrigerant flowing through the low-pressure passage 15a, the refrigerant in the discharge chamber 35 is adjusted in pressure through the high-pressure passage 15b and the orifice 15d. It becomes difficult to be stored in the chamber 31. For this reason, the pressure in the control pressure chamber 13 b is substantially equal to that of the suction chamber 33. For this reason, as shown in FIG. 1, the actuator 13 reduces the volume of the control pressure chamber 13 b due to the piston compression force acting on the swash plate 5, and the movable body 13 a moves from the swash plate 5 side in the direction of the drive axis O. It moves toward the lug plate 51 side. In the movable body 13a, the second movable cylindrical portion 132 and the third movable cylindrical portion 133 enter the fixed cylindrical portion 51a.
- the swash plate 5 slides the cam surface 51b so that each swash plate arm 5e, 5f is remote from the drive shaft O by the piston compression force acting on itself and the urging force of the return spring 37. Move. For this reason, in the swash plate 5, the bottom dead center side is swung clockwise while substantially maintaining the position of the top dead center corresponding portion T.
- the inclination angle of the swash plate 5 with respect to the drive axis O of the drive shaft 3 increases. Thereby, in this compressor, the stroke of piston 9 increases and the discharge capacity per one rotation of drive shaft 3 becomes large.
- the inclination angle of the swash plate 5 shown in FIG. 1 is the maximum inclination angle in this compressor. When the swash plate 5 is at the maximum inclination angle, the swash plate arms 5e and 5f and the cam surface 51b come into contact with each other at the first position P1.
- the control valve 15c shown in FIG. 2 reduces the flow rate of the refrigerant flowing through the low pressure passage 15a, the refrigerant in the discharge chamber 35 is easily stored in the pressure adjustment chamber 31 through the high pressure passage 15b and the orifice 15d. .
- the pressure in the control pressure chamber 13 b is substantially equal to that in the discharge chamber 35, and the pressure in the control pressure chamber 13 b is higher than that in the swash plate chamber 25.
- the volume of the control pressure chamber 13b increases, and the movable body 13a moves away from the lug plate 51 toward the swash plate 5 in the direction of the drive axis O. .
- the action surface 134a of the action part 134 acts to press the convex part 5g toward the rear of the swash plate chamber 25 at the action position F.
- the swash plate arms 5e and 5f slide on the cam surface 51b so as to be close to the drive axis O, and the swash plate 5 maintains the position of the top dead center corresponding portion T while maintaining the bottom dead center.
- the inclination angle of the swash plate 5 with respect to the drive axis O of the drive shaft 3 decreases.
- the stroke of the piston 9 is reduced, and the discharge capacity per one rotation of the drive shaft 3 is reduced.
- the inclination angle of the swash plate 5 shown in FIG. 6 is the minimum inclination angle in this compressor.
- the swash plate arms 5e and 5f and the cam surface 51b come into contact with each other at the second position P2.
- the actuator 13 is adopted, and the inclination angle of the swash plate 5 is changed by the pressure change in the control pressure chamber 13b having a smaller volume than the swash plate chamber 25. For this reason, in this compressor, it is possible to reduce the amount of refrigerant required for changing the inclination angle, compared to a compressor that changes the inclination angle by changing the pressure in the swash plate chamber 25. For this reason, in this compressor, it is possible to suppress an increase in the size of the swash plate chamber 25 and consequently the housing 1.
- the swash plate arms 5e and 5f of the link mechanism 7 transmit the rotation of the lug plate 51 to the swash plate 5 and substantially maintains the position of the top dead center corresponding portion T of the swash plate 5.
- the change of the inclination angle is allowed.
- the action part 134 of the movable body 13a and the convex part 5g of the swash plate 5 are eccentric from the drive axis O toward the top dead center corresponding part T side of the swash plate 5.
- the action surface 134a of the action part 134 and the convex part 5g are in point contact at the action position F, and the action surface 134a presses the convex part 5g when the inclination angle of the swash plate 5 is reduced. And this action position F moves by the change of an inclination angle.
- the variable differential pressure when the inclination angle is reduced, the variable differential pressure is not increased so as to ensure a large thrust as compared with the case where the distance between the operating position F and the drive shaft center O is constant.
- the movable body 13a can be moved. That is, in this compressor, the load on the movable body 13a when the inclination angle is reduced can be reduced. For this reason, in this compressor, the amount of change in the variable differential pressure when changing the tilt angle is small, and the tilt angle can be easily changed quickly according to the driving situation of the mounted vehicle, and high controllability can be exhibited.
- the compressor of the comparative example is configured by partially changing the swash plate 5 and the movable body 13a of the compressor of the first embodiment, and without providing the convex portion 5g and the action portion 134.
- the rear end of the first movable cylindrical portion 131 of the movable body 13a comes into contact with the front surface 5a around the insertion hole 5d.
- the movable body 13a and the swash plate 5 will contact
- the swash plate 5 in the compressor of the comparative example, the swash plate 5 (see the two-dot chain line) in the state where the inclination angle is maximum in FIG. 9 is displaced until the inclination angle becomes the minimum state.
- the movable body 13a needs to move in the direction of the drive axis O by a distance S2.
- the movable body 13a when the swash plate 5 having the maximum inclination angle is displaced to the minimum state, the movable body 13a has a distance S1 in the direction of the drive axis O. It is enough to move only. That is, the stroke of the movable body 13a in the direction of the drive axis O of the compressor of the first embodiment is smaller than that of the compressor of the comparative example.
- the compressor of Example 1 can exhibit high controllability and exhibits excellent mountability.
- this compressor when the inclination angle of the swash plate 5 is changed, the movable body 13a only presses while directly contacting the swash plate 5, and the action portion 134 and the convex portion 5g are connected by a connecting pin or the like. There is no consolidation. For this reason, in this compressor, there is no possibility that the posture of the movable body 13a will change depending on the configuration of the connecting portion, and it is difficult for the posture of the movable body 13a to change when the inclination angle is changed. In addition, in this compressor, it is possible to suppress the complexity of the configuration and to realize a reduction in manufacturing cost.
- the movable body 13a is inserted through the drive shaft 3, and the movable body 13a can be fitted to the lug plate 51 by housing the movable body 13a in the fixed cylindrical portion 51a.
- the third movable cylindrical portion 133 of the movable body 13 a enters the fixed cylindrical portion 51 a to a position inside the thrust bearing 55.
- the thrust bearing 55 is provided, so that the suction reaction force and the compression reaction force acting on the piston 9 can be suitably supported.
- control pressure chamber 13b can be suitably formed between the lug plate 51 and the movable body 13a by the fixed cylindrical portion 51a.
- the air tightness of the control pressure chamber 13b is suitably ensured by the O-rings 49c and 49d provided in the first and third movable cylindrical portions 131 and 133, respectively.
- the action part 134 and the convex part 5g are eccentric from the drive axis O toward the top dead center corresponding part T, and the action position F is driven as described above when the inclination angle of the swash plate 5 becomes small. Move toward the axis O side. For this reason, in this compressor, it is easy to ensure a space for the movable body 13a to move in the direction of the drive axis O between the lug plate 51 and the swash plate 5 without hindering the change of the inclination angle. It has become. For this reason, in this compressor, it is possible to increase the diameter of the actuator 13 and move the movable body 13a quickly with sufficient thrust. Also in this respect, in this compressor, the inclination angle can be quickly changed according to the driving situation of the vehicle.
- the action part 134 protrudes from the first movable cylindrical part 131 to the top dead center corresponding part T side of the swash plate 5 and is integrated with the movable body 13a.
- An action surface 134 a is formed on the action part 134.
- the working surface 134a and the convex portion 5g can be easily brought into contact with each other at a position eccentric from the drive axis O toward the top dead center corresponding portion T side.
- the convex part 5g is formed so as to protrude in a substantially hemispherical shape, the working surface 134a and the convex part 5g can be suitably brought into point contact. Therefore, in this compressor, the contact area between the working surface 134a and the convex portion 5g can be reduced, and the swash plate 5 can easily change the inclination angle.
- the convex portion 5g is formed integrally with the front surface 5a of the swash plate body 50. For this reason, in this compressor, the number of parts can be reduced, and the manufacturing is facilitated and the manufacturing cost can be reduced.
- the swash plate chamber 25 and the suction chamber 33 communicate with each other through the suction passage 39.
- the swash plate chamber 25 can be set to a low pressure similarly to the suction chamber 33.
- control mechanism 15 adjusts the pressure in the pressure adjusting chamber 31 and, consequently, the pressure in the control pressure chamber 13b by adjusting the opening of the control valve 15c.
- An axial path 3 a and a radial path 3 b are formed in the drive shaft 3.
- the airtightness of the pressure adjusting chamber 31 is suitably ensured by the O-rings 49a and 49b provided at the rear end of the drive shaft 3.
- the swash plate 5 includes a swash plate body 50, swash plate arms 5 e and 5 f, and a contact member 59.
- This contact member 59 also corresponds to the operated part in the present invention.
- the contact member 59 is formed separately from the swash plate main body 50.
- the contact member 59 is attached to each swash plate arm 5e, 5f on the front surface 5a of the swash plate body 50, and is eccentric to the top dead center corresponding portion T side of the swash plate 5 from the drive axis O. positioned.
- the contact member 59 is formed with a convex portion 59a protruding forward.
- the convex portion 59a is formed in a substantially hemispherical shape.
- the convex part 59a is in point contact with the action surface 134a of the action part 134 at the action position F.
- the action part 134 and the contact member 59 are in contact with each other through the action surface 134a and the convex part 59a at a position eccentric from the drive axis O to the top dead center corresponding part T side of the swash plate 5.
- 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.
- this compressor since the swash plate 5 and the contact member 59 are separate, it is possible to increase the degree of freedom in designing the swash plate body 50 and the contact member 59.
- Other functions of this compressor are the same as those of the compressor of the first embodiment.
- the operating position F moves toward the drive axis O side, and the minimum from the predetermined angle. You may comprise so that the action position F may not move until it becomes an inclination angle.
- the convex portion 5g and the convex portion 59a may be formed in a flat shape, and the action surface 134a of the action portion 134 may be formed in a curved shape. As a result, at the operating position F, the convex portion 5g and the contact member 59 can be brought into line contact with the operating portion 134.
- control mechanism 15 may be configured such that a control valve 15c is provided for the high pressure passage 15b and an orifice 15d is provided for the low pressure passage 15a.
- the flow rate of the high-pressure refrigerant flowing through the high-pressure passage 15b can be adjusted by the control valve 15c.
- the control pressure chamber 13b can be quickly brought to a high pressure by the high pressure in the discharge chamber 35, and the compression capacity can be quickly reduced.
- a three-way valve connected to the low-pressure passage 15a and the high-pressure passage 15b is provided, and by adjusting the opening of the three-way valve, the refrigerant flowing in the low-pressure passage 15a or the high-pressure passage 15b is adjusted. The flow rate may be adjusted.
- the present invention can be used for an air conditioner or the like.
- Discharge chamber 21a Cylinder bore 49a, 49b ... O-ring (third sealing means) 49c ... O-ring (first sealing means) 49d ... O-ring (second sealing means) 51 ... lug plate (lug member) 51a ... fixed cylindrical part 55 ... thrust bearing 59 ... contact member (acting part) 59a ... convex portion 131 ... first movable cylindrical portion (movable cylindrical portion) 132: second movable cylindrical portion (movable cylindrical portion) 133: Third movable cylindrical portion (movable cylindrical portion) 134 ... action part F ... action position O ... drive shaft center T ... top dead center corresponding part
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Abstract
Description
前記リンク機構は、前記斜板室内で前記駆動軸に固定されたラグ部材と、前記ラグ部材の回転を前記斜板に伝達する伝達部材とを有し、
前記アクチュエータは、前記ラグ部材と、前記斜板と一体回転可能であり、前記駆動軸心方向に移動して前記傾斜角度を変更可能な可動体と、前記ラグ部材と前記可動体とにより区画され、前記制御機構により内部の圧力を変更することによって前記可動体を移動させる制御圧室とを有し、
前記可動体には、前記制御圧室内の圧力によって前記斜板を押圧可能な作用部が形成され、
前記斜板には、前記作用部に当接して押圧される被作用部が形成され、
前記作用部と前記被作用部とは作用位置において当接し、
前記作用位置は、前記傾斜角度の変更により移動し、
前記斜板には、前記ピストンを上死点に位置させる上死点対応部が定義され、
前記傾斜角度が最大のときにおける前記作用位置は、前記傾斜角度が最小のときにおける前記作用位置よりも前記上死点対応部に近づくことを特徴とする。
図1に示すように、実施例1の圧縮機は、ハウジング1と、駆動軸3と、斜板5と、リンク機構7と、複数のピストン9と、複数対のシュー11a、11bと、アクチュエータ13と、図2に示す制御機構15とを備えている。なお、図1では説明を容易にするため、斜板5の形状を一部簡略化して図示している。後述の図6、10についても同様である。
図10に示すように、実施例2の圧縮機では、斜板5は、斜板本体50と、斜板アーム5e、5fと、接触部材59とを有している。この接触部材59も本発明における被作用部に相当する。
3…駆動軸
3a…軸路(制御通路)
3b…径路(制御通路)
5…斜板
5d…挿通孔
5e、5f…斜板アーム(伝達部材)
5g…凸部(被作用部)
7…リンク機構
9…ピストン
11a、11b…シュー(変換機構)
13…アクチュエータ
13a…可動体
13b…制御圧室(制御通路)
15…制御機構
15a…低圧通路(制御通路)
15b…高圧通路(制御通路)
15c…制御弁
25…斜板室
31…圧力調整室
33…吸入室
35…吐出室
21a…シリンダボア
49a、49b…Oリング(第3封止手段)
49c…Oリング(第1封止手段)
49d…Oリング(第2封止手段)
51…ラグプレート(ラグ部材)
51a…固定円筒部
55…スラスト軸受
59…接触部材(被作用部)
59a…凸部
131…第1可動円筒部(可動円筒部)
132…第2可動円筒部(可動円筒部)
133…第3可動円筒部(可動円筒部)
134…作用部
F…作用位置
O…駆動軸心
T…上死点対応部
Claims (14)
- 斜板室及びシリンダボアが形成されたハウジングと、前記ハウジングに回転可能に支持された駆動軸と、前記駆動軸の回転によって前記斜板室内で回転可能な斜板と、前記駆動軸と前記斜板との間に設けられ、前記駆動軸の駆動軸心に直交する方向に対する前記斜板の傾斜角度の変更を許容するリンク機構と、前記シリンダボアに往復動可能に収納されたピストンと、前記斜板の回転により、前記傾斜角度に応じたストロークで前記ピストンを前記シリンダボア内で往復動させる変換機構と、前記傾斜角度を変更可能なアクチュエータと、前記アクチュエータを制御する制御機構とを備え、
前記リンク機構は、前記斜板室内で前記駆動軸に固定されたラグ部材と、前記ラグ部材の回転を前記斜板に伝達する伝達部材とを有し、
前記アクチュエータは、前記ラグ部材と、前記斜板と一体回転可能であり、前記駆動軸心方向に移動して前記傾斜角度を変更可能な可動体と、前記ラグ部材と前記可動体とにより区画され、前記制御機構により内部の圧力を変更することによって前記可動体を移動させる制御圧室とを有し、
前記可動体には、前記制御圧室内の圧力によって前記斜板を押圧可能な作用部が形成され、
前記斜板には、前記作用部に当接して押圧される被作用部が形成され、
前記作用部と前記被作用部とは作用位置において当接し、
前記作用位置は、前記傾斜角度の変更により移動し、
前記斜板には、前記ピストンを上死点に位置させる上死点対応部が定義され、
前記傾斜角度が最大のときにおける前記作用位置は、前記傾斜角度が最小のときにおける前記作用位置よりも前記上死点対応部に近づくことを特徴とする容量可変型斜板式圧縮機。 - 前記可動体は、前記駆動軸を挿通しているとともに、前記ラグ部材に嵌合可能である請求項1記載の容量可変型斜板式圧縮機。
- 前記可動体は、前記駆動軸心と同軸の円筒状をなす可動円筒部を有し、
前記ラグ部材は、前記可動円筒部の外周側で前記駆動軸心と同軸の円筒状をなし、前記可動円筒部内に前記制御圧室を確保する円筒状の固定円筒部を有している請求項2記載の容量可変型斜板式圧縮機。 - 前記可動円筒部と前記駆動軸との間には、前記制御圧室を封止する第1封止手段が設けられ、
前記可動円筒部と前記固定円筒部との間には、前記制御圧室を封止する第2封止手段が設けられている請求項3記載の容量可変型斜板式圧縮機。 - 前記ハウジングと前記ラグ部材との間には、前記ピストンに作用するスラスト力を受けるスラスト軸受が設けられ、
前記可動円筒部は、前記スラスト軸受より小径であり、かつ前記スラスト軸受内まで嵌合可能である請求項3又は4記載の容量可変型斜板式圧縮機。 - 前記作用部と前記被作用部とは、前記作用位置で互いに点接触又は線接触する請求項1乃至5のいずれか1項記載の容量可変型斜板式圧縮機。
- 前記作用部及び前記被作用部は、前記駆動軸心から前記上死点対応部側に偏心し、
前記作用位置は、前記傾斜角度が小さくなると前記駆動軸心側に向けて移動する請求項6記載の容量可変型斜板式圧縮機。 - 前記作用部は、前記駆動軸心に直交する方向に延びる作用面を有し、
前記被作用部は、前記斜板から突出し、前記作用面と当接する凸部を有している請求項7記載の容量可変型斜板式圧縮機。 - 前記可動体は、前記駆動軸心と同軸の円筒状をなす可動円筒部を有し、
前記作用部は、前記可動円筒部における前記上死点対応部側に突設されている請求項7又は8記載の容量可変型斜板式圧縮機。 - 前記斜板は、前記駆動軸が挿通される挿通孔が形成された斜板本体と、前記斜板本体に一体で形成された前記被作用部とを有する請求項1乃至9のいずれか1項記載の容量可変型斜板式圧縮機。
- 前記斜板は、前記駆動軸が挿通される挿通孔が形成された斜板本体と、前記斜板本体に固定された前記被作用部とを有する請求項1乃至9のいずれか1項記載の容量可変型斜板式圧縮機。
- 前記ハウジングには、吸入室及び吐出室が形成され、
前記吸入室と前記斜板室とは連通している請求項1乃至11のいずれか1項記載の容量可変型斜板式圧縮機。 - 前記制御機構は、前記制御圧室と前記吸入室及び/又は前記吐出室とを連通する制御通路と、前記制御通路の開度を調整可能な制御弁とを有し、
前記制御通路の少なくとも一部は、前記駆動軸内に形成されている請求項12記載の容量可変型斜板式圧縮機。 - 前記ハウジングと前記駆動軸の一端との間には、前記制御通路を経て前記制御圧室に連通し、前記制御弁によって圧力が変更される圧力調整室が形成され、
前記ハウジングと前記駆動軸との間には、前記圧力調整室を封止する第3封止手段が設けられている請求項13記載の容量可変型斜板式圧縮機。
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JP2015536607A JP6037028B2 (ja) | 2013-09-11 | 2014-09-10 | 容量可変型斜板式圧縮機 |
DE112014004156.4T DE112014004156B4 (de) | 2013-09-11 | 2014-09-10 | Verdichter der Taumelscheibenbauart mit variabler Verdrängung durch eine Steuerungsdruckkammer |
CN201480050320.6A CN105556121B (zh) | 2013-09-11 | 2014-09-10 | 容量可变型斜板式压缩机 |
KR1020167008924A KR101889628B1 (ko) | 2013-09-11 | 2014-09-10 | 용량 가변형 사판식 압축기 |
US14/917,820 US20160222953A1 (en) | 2013-09-11 | 2014-09-10 | Variable displacement swash plate type compressor |
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JP6146263B2 (ja) * | 2013-11-06 | 2017-06-14 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
RU2019142842A (ru) * | 2017-06-27 | 2021-07-27 | СиДаблЮ Хлдингс, Лтд. | Насос с переменным ходом |
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- 2014-09-10 DE DE112014004156.4T patent/DE112014004156B4/de not_active Expired - Fee Related
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- 2014-09-10 US US14/917,820 patent/US20160222953A1/en not_active Abandoned
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DE112014004156T5 (de) | 2016-05-25 |
CN105556121A (zh) | 2016-05-04 |
JPWO2015037637A1 (ja) | 2017-03-02 |
CN105531477A (zh) | 2016-04-27 |
KR101796406B1 (ko) | 2017-12-01 |
KR20160051875A (ko) | 2016-05-11 |
KR101889628B1 (ko) | 2018-08-17 |
KR20160052682A (ko) | 2016-05-12 |
JP6037028B2 (ja) | 2016-11-30 |
JPWO2015037636A1 (ja) | 2017-03-02 |
US20160222953A1 (en) | 2016-08-04 |
US20160222952A1 (en) | 2016-08-04 |
WO2015037636A1 (ja) | 2015-03-19 |
DE112014004156B4 (de) | 2019-11-21 |
JP6037027B2 (ja) | 2016-11-30 |
CN105531477B (zh) | 2017-06-23 |
CN105556121B (zh) | 2017-05-24 |
DE112014004173T5 (de) | 2016-05-25 |
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