US20150086391A1 - Swash plate type variable displacement compressor - Google Patents
Swash plate type variable displacement compressor Download PDFInfo
- Publication number
- US20150086391A1 US20150086391A1 US14/492,441 US201414492441A US2015086391A1 US 20150086391 A1 US20150086391 A1 US 20150086391A1 US 201414492441 A US201414492441 A US 201414492441A US 2015086391 A1 US2015086391 A1 US 2015086391A1
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- United States
- Prior art keywords
- chamber
- pressure
- drive shaft
- swash plate
- pressure regulation
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
-
- 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
- F04B27/1804—Controlled by crankcase pressure
-
- 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
- F04B27/14—Control
-
- 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
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- 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
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
-
- 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
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
-
- 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
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1886—Open (not controlling) fluid passage
- F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber
Definitions
- the present invention relates to a swash plate type variable displacement compressor.
- Japanese Unexamined Patent Application Publication No. 5-172052 discloses a swash plate type variable displacement compressor (hereinafter, referred to as the compressor).
- the compressor has a housing which includes a front housing, a cylinder block and a rear housing. Each of the front housing and the rear housing has therein a suction chamber and a discharge chamber.
- the rear housing has therein a pressure regulation chamber which is formed in the center of the rear housing.
- the suction chamber is formed radially outward of the pressure regulation chamber and the discharge chamber is formed radially outward of the suction chamber.
- the cylinder block has therein a swash plate chamber, a plurality of cylinder bores and a main shaft insertion hole.
- Each cylinder bore has a first cylinder bore which is formed in the rear of the cylinder block and a second cylinder bore which is formed in the front of the cylinder block.
- the main shaft insertion hole is formed in the rear of the cylinder block and communicates with the swash plate chamber and the pressure regulation chamber.
- a drive shaft is disposed extending in the housing and rotatably supported in the cylinder block.
- a swash plate is mounted on the drive shaft for rotation therewith in the swash plate chamber.
- a link mechanism is provided between the drive shaft and the swash plate which permits the inclination of the swash plate.
- the angle of inclination refers to an angle of the swash plate with respect to a plane extending perpendicular to the axis of rotation of the drive shaft.
- a plurality of pistons is received in the respective cylinder bores so that the pistons are movable in the reciprocating manner.
- each piston has a first piston head which reciprocates in the first cylinder bore and a second piston head which reciprocates in the second cylinder bore. Therefore, the compressor has a first compression chamber formed by the first cylinder bore and the first piston head and a second compression chamber formed by the second cylinder bore and the second piston head.
- the compressor further includes a conversion mechanism that converts the rotation of the swash plate into reciprocal movement of the pistons in the respective cylinder bores with a stroke length that is determined by the inclination angle of the swash plate.
- the inclination angle of the swash plate can be controllably changed by an actuator, which is controlled by a control mechanism of the compressor.
- the actuator is disposed on the first cylinder bore side of the swash plate chamber.
- the actuator includes a non-rotating movable body, a movable body and a thrust bearing.
- the actuator has therein a pressure control chamber.
- the non-rotating movable body is disposed in the main shaft insertion hole so that the non-rotating movable body is not rotatable with the drive shaft and covers the rear end of the drive shaft.
- This non-rotating movable body rotatably supports on the inner peripheral surface thereof the rear end of the drive shaft.
- the non-rotating movable body is movable back and forth in the main shaft insertion hole in the axial direction of the rotating shaft in sliding contact with the inner peripheral surface of the main drive shaft hole.
- the non-rotating movable body is configured so as not to slide about the axial center of rotation.
- the movable body is connected to the swash plate and is movable therewith in the axial direction of the drive shaft.
- the thrust bearing is disposed between the non-rotating movable body and the movable body.
- the main shaft insertion hole in the cylinder block is partitioned by the non-rotating movable body, thereby forming the pressure control chamber on the rear end side of the main shaft insertion hole.
- the rear end of the drive shaft is rotatably supported on the inner peripheral surface of the non-rotating movable body at a position frontward of the pressure control chamber.
- the pressure control chamber communicates with the pressure regulation chamber in the rear housing.
- a pressure spring is provided in the pressure control chamber so as to urge the non-rotating movable body in the frontward direction.
- the control mechanism includes a control passage and a control valve provided in the control passage.
- the control passage provides communication between the discharge chamber and the pressure regulation chamber. By regulating the opening of the control passage, the control valve varies the pressure in the pressure control chamber thereby to move the non-rotating movable body and the movable body move together in the axial direction of the drive shaft.
- the link mechanism has the movable body and a lug arm fixed on the drive shaft.
- the lug arm has at the rear end thereof an elongated hole that extends in the direction perpendicular to the axis of the drive shaft and also radially inwardly from the outer periphery thereof to the axial center.
- the swash plate is supported at the front thereof such that the swash plate is allowed to pivot about a first pivot pin inserted through the elongated hole.
- the movable body also has at the front end thereof an elongated hole which extends in the direction perpendicular to the axis of the drive shaft and also in the direction approaching the axis of the drive shaft from the outer periphery thereof.
- the swash plate is also supported at the rear end thereof such that the swash plate is allowed to pivot about a second pivot pin which is parallel to the center of the first pivot pin and inserted through the elongated hole.
- the pressure in the pressure regulation chamber and hence the pressure in the pressure control chamber can be controlled by the pressure of the refrigerant gas in the discharge chamber.
- the pressure in the pressure control chamber becomes almost the same as the pressure in the swash plate chamber. Accordingly, the non-rotating movable body and the movable body in the main shaft insertion hole retreat in the axial direction of the rotating shaft. Therefore, the inclination angle of the swash plate is reduced and hence the stroke of the pistons is reduced, with the result that the displacement of the compressor per one rotation of the drive shaft is decreased.
- the suction chamber is disposed radially outward of the pressure regulation chamber. Since the temperature of the refrigerant gas in the suction chamber is lower, the pressure regulation chamber is cooled and, therefore, the temperature of the refrigerant gas in the pressure regulation chamber drops, thus liquefying part of the refrigerant gas in the pressure regulation chamber.
- refrigerant of two phases namely gaseous refrigerant and liquefied refrigerant is present in the pressure regulation chamber. If the proportion of the liquefied refrigerant increases, the pressure in the pressure regulation chamber increases less quickly by the refrigerant flowing from the discharge chamber into the pressure regulation chamber.
- the pressure in the pressure regulation chamber decreases less quickly by the refrigerant flowing from the pressure regulation chamber into the suction chamber.
- the compressor of the above-cited publication therefore, it is difficult to move the non-rotating movable body and the movable body in a desirable manner. Specifically, in the compressor, it is difficult to vary the inclination angle of the swash plate quickly according to a change of the operating conditions of the vehicle on which the compressor is mounted and also the discharge displacement of the compressor is less controllable.
- the present invention which has been made in view of the above-identified circumstances, is directed to providing a swash plate type variable displacement compressor that offers improved controllability.
- the swash plate type variable displacement compressor includes a housing having therein a suction chamber, a discharge chamber, a swash plate chamber, and a plurality of cylinder bores; a drive shaft rotatably supported in the housing; a swash plate which is rotatable in the swash plate chamber with the rotation of the drive shaft; a link mechanism which is disposed between the drive shaft and the swash plate and allows a change in an inclination angle of the swash plate with respect to the direction perpendicular to the axis of the drive shaft; a plurality of pistons which is reciprocally received in the respective cylinder bores; a conversion mechanism which converts the rotation of the drive shaft into reciprocal movement of the pistons in the respective cylinder bores in conjunction with the swash plate with a stroke length according to the inclination angle of the swash plate; an actuator for changing the inclination angle of the swash plate; and a control mechanism which controls the actuator.
- the housing has therein a pressure regulation chamber.
- the pressure regulation chamber is disposed radially inward of the discharge chamber, which is disposed radially inward of the suction chamber.
- the actuator includes a fixed body, a movable body, and a pressure control chamber.
- the fixed body is fixed on the drive shaft in the swash plate chamber.
- the movable body is connected to the swash plate and movable relative to the fixed body in the direction of the axis of rotation.
- the pressure control chamber is defined by the fixed body and the movable body and the pressure in the pressure control chamber is changed by introducing the pressure in the discharge chamber into the pressure control chamber such that the movable body is moved.
- the control mechanism has a control passage and a control valve.
- the control passage provides communication between the discharge chamber and the pressure control chamber via the pressure regulation chamber.
- the control valve adjusts an opening of the control passage to vary pressure in the pressure regulation chamber such that the movable body is moved.
- At least a part of the control passage is formed in the drive shaft, and the drive shaft projects into the pressure regulation chamber such that the control passage connects the pressure regulation chamber and the pressure control chamber.
- FIG. 1 is a longitudinal sectional view of a compressor according to an embodiment of the present invention, showing the maximum displacement of the compressor;
- FIG. 2 is a schematic diagram of a control mechanism of the compressor of FIG. 1 ;
- FIG. 3 is a transverse sectional view of the compressor as viewed in arrow direction III-III in FIG. 1 ;
- FIG. 4 is a longitudinal sectional view of the compressor of FIG. 1 in the minimum displacement.
- the compressor of the embodiment is a swash plate type variable displacement compressor which is mounted on a vehicle and forms a part of a refrigeration circuit for an air conditioning system of the vehicle.
- the compressor includes a housing 1 , a drive shaft 3 , a swash plate 5 , a link mechanism 7 , a plurality of double-headed pistons 9 , pairs of shoes 11 A, 11 B, an actuator 13 and a control mechanism 15 which is shown in FIG. 2 .
- the housing 1 includes a front housing 17 disposed on the front side of the compressor, a rear housing 19 disposed on the rear side of the compressor, first and second cylinder blocks 21 , 23 disposed between the front housing 17 and the rear housing 19 , and first and second valve forming plates 39 , 41 .
- the front housing 17 has a boss 17 A projecting frontward.
- the boss 17 A has a shaft sealing device 25 .
- the front housing 17 has therein a first suction chamber 27 A and a first discharge chamber 29 A.
- the first suction chamber 27 A is formed in a radially inner region inward of the front housing 17 .
- the first discharge chamber 29 A is formed in an annular shape and disposed outward of the first suction chamber 27 A in the front housing 17 .
- the front housing 17 has therein a first front communication passage 18 A which communicates at the front end thereof with the first discharge chamber 29 A and opens at the rear end thereof at the rear end of the front housing 17 .
- the control mechanism 15 is disposed in the rear housing 19 .
- the rear housing 19 has therein a second suction chamber 27 B, a second discharge chamber 29 B, and a pressure regulation chamber 31 .
- the pressure regulation chamber 31 is disposed in the center of the rear housing 19 .
- the second discharge chamber 29 B is formed in an annular shape and formed radially outward of the pressure regulation chamber 31 in the rear housing 19 so as to surround the pressure regulation chamber 31 .
- the second suction chamber 27 B is formed into a substantially C shape and disposed radially outward of the second discharge chamber 29 B in the rear housing 19 .
- the rear housing 19 has therein a first rear communication passage 20 A which communicates at the rear end thereof with the second discharge chamber 29 B. As shown in FIG. 1 , the front end of the first rear communication passage 20 A is open at the front end of the rear housing 19 .
- a swash plate chamber 33 is formed between a first cylinder block 21 and the second cylinder block 23 .
- the swash plate chamber 33 is disposed substantially in the center of the housing 1 as seen in the longitudinal direction of the compressor.
- a plurality of first cylinder bores 21 A is formed substantially at an equal angular distance in the circumferential direction of the first cylinder block 21 .
- the first cylinder block 21 has therethrough a first shaft hole 21 B through which the drive shaft 3 is inserted.
- the first shaft hole 21 B has a first sliding bearing 22 A, although a rolling bearing may alternatively be used.
- the first cylinder block 21 further has therein a first recessed portion 21 C which is annular and coaxial with the first shaft hole 21 B.
- the first recessed portion 21 C communicates with the swash plate chamber 33 .
- the inner diameter of the annular first recessed portion 21 C is reduced in the form of a step toward the front end thereof.
- a first thrust bearing 35 A is provided in the first recessed portion 21 C at the front end thereof.
- the first cylinder block 21 further has therein a first connecting passage 37 A which provides communication between the swash plate chamber 33 and the first suction chamber 27 A.
- the first cylinder block 21 has therein a first retaining groove 21 E for regulating the maximum opening of first suction reed valves 391 A, which will be described later.
- the first cylinder block 21 further has therein a second front communication passage 18 B which is open at the opposite front and rear ends thereof.
- the second cylinder block 23 has therein a plurality of second cylinder bores 23 A as in the case of the first cylinder block 21 .
- Each second cylinder bore 23 A on the rear side is paired with its associated first cylinder bore 21 A on the front side.
- the first cylinder bores 21 A and the second cylinder bores 23 A are of the same diameter. It is to be noted that the second cylinder block 23 corresponds to the cylinder block of the present invention.
- the second cylinder block 23 has a projection 23 F extending rearward. With the second cylinder block 23 , the second valve forming plate 41 and the rear housing 19 joined together, the projection 23 F projects into the pressure regulation chamber 31 projecting beyond the second valve forming plate 41 . The distance for which the projection 23 F projects into the pressure regulation chamber 31 may appropriately be changed according to the design.
- the second cylinder block 23 has therein a second shaft hole 23 B through which the drive shaft 3 is inserted.
- the second shaft hole 23 B extends also in the projection 23 F and is opened to the pressure regulation chamber 31 .
- the second shaft hole 23 B has therein a second sliding bearing 22 B the rear end of which projects to the pressure regulation chamber 31 .
- the second sliding bearing 22 B corresponds to the radial bearing of the present invention. It is to be noted that the second sliding bearing 22 B may be replaced with a roller bearing.
- the second cylinder block 23 has therein a second recessed portion 23 C which is annular and coaxial with the second shaft hole 23 B.
- the second recessed portion 23 C also communicates with the swash plate chamber 33 .
- the inner diameter of the second annular recessed portion 23 C is reduced in the form of a step toward the rear end thereof.
- a second thrust bearing 35 B is provided in the second recessed portion 23 C at the rear end thereof.
- the second thrust bearing 35 B corresponds to the thrust bearing of the present invention.
- the second cylinder block 23 further has therein a second connecting passage 37 B which provides communication between the swash plate chamber 33 and the second suction chamber 27 B.
- the second cylinder block 23 has therein a second retaining groove 23 E for regulating the maximum opening of second suction reed valves 411 A, which will be described later.
- the second cylinder block 23 has therein an outlet port 230 , a combined discharge chamber 231 , a third front communication passage 18 C, a second rear communication passage 20 B and an inlet port 330 .
- the outlet port 230 and the combined discharge chamber 231 are in direct communication with each other.
- the outlet port 230 and the combined discharge chamber 231 are formed in the second cylinder block 23 at positions adjacent to the front end of the second cylinder block 23 so that they are disposed substantially in the longitudinal center of the housing 1 .
- the combined discharge chamber 231 is connected through the discharge port 230 to a condenser (not shown).
- the third front communication passage 18 C is open at the front end thereof in the front end of the second cylinder block 23 and communicates directly at the rear end thereof with the combined discharge chamber 231 . With the first cylinder block 21 and the second cylinder block 23 joined together, the third front communication passage 18 C communicates with the second front communication passage 18 B at the rear end thereof.
- the second rear communication passage 20 B communicates directly at the front end thereof with the combined discharge chamber 231 and open at the rear end thereof in the rear end of the second cylinder block 23 .
- the inlet port 330 is formed at a position adjacent to the front end of the second cylinder block 23 so that the inlet port 330 is disposed substantially in the longitudinal center of the housing 1 .
- the swash plate chamber 33 is connected through the suction port 330 to an evaporator (not shown) connected in the external refrigeration circuit.
- the first valve forming plate 39 is interposed between the front housing 17 and the first cylinder block 21 .
- the second valve forming plate 41 is provided between the rear housing 19 and the second cylinder block 23 .
- the second valve forming plate 41 corresponds to the valve unit of the present invention.
- the first and second valve forming plates 39 , 41 are formed in an annular shape.
- the first valve forming plate 39 is mounted on a projection at the front end of the first cylinder block 21 and the second valve forming plate 41 is mounted on the projection 23 F of the second cylinder block 23 .
- the first valve forming plate 39 includes a first valve plate 390 , a first suction valve plate 391 , a first discharge valve plate 392 , and a first retainer plate 393 .
- At least one first suction hole 390 A is formed through the first valve plate 390 , the first discharge valve plate 392 , and the first retainer plate 393 .
- the first suction hole 390 A corresponds to each first cylinder bore 21 A.
- At least one first discharge hole 390 B is formed through the first valve plate 390 and the first suction valve plate 391 .
- the first discharge hole 390 B corresponds to each first cylinder bore 21 A.
- At least one first suction communication hole 390 C is formed through the first valve plate 390 , the first suction valve plate 391 , the first discharge valve plate 392 , and the first retainer plate 393 .
- At least one first discharge communication hole 390 D is formed through the first valve plate 390 and the first suction valve plate 391 .
- Each first cylinder bore 21 A is communicable with the first suction chamber 27 A through its associated first suction hole 390 A.
- Each first cylinder bore 21 A is communicable with the first discharge chamber 29 A through its associated first discharge hole 390 B.
- the first suction chamber 27 A and the first connecting passage 37 A are communicable with each other through the first suction communication hole 390 C.
- the first front communication passage 18 A and the second front communication passage 18 B are communicable with each other through the first discharge communication hole 390 D.
- the first suction valve plate 391 is provided on a rear surface of the first valve plate 390 and has the plurality of first suction reed valves 391 A which are elastically deformable to open and close the first suction holes 390 A.
- the first discharge valve plate 392 is provided on a front surface of the first valve plate 390 and has a plurality of first discharge reed valves 392 A which are elastically deformable to open and close the first discharge holes 390 B.
- the first retainer plate 393 is provided on the front surface of the first discharge plate 392 for regulating the maximum opening of the first discharge reed valves 392 A.
- the second valve forming plate 41 includes a second valve plate 410 , a second suction valve plate 411 , a second discharge valve plate 412 and a second retainer plate 413 .
- At least one second suction hole 410 A is formed through the second valve plate 410 .
- the second suction hole 410 A corresponds to each second cylinder bore 23 A.
- At least one second discharge hole 410 B is formed through the second valve plate 410 and the second suction valve plate 411 .
- the second discharge hole 410 B corresponds to each second cylinder bore 23 A.
- at least one second suction communication hole 410 C and at least one second discharge communication hole 410 D are formed through the second valve plate 410 and the second suction valve plate 411 .
- Each second cylinder bore 23 A is communicable with the second suction chamber 27 B through its associated second suction hole 410 A.
- Each second cylinder bore 23 A is communicable with the second discharge chamber 29 B through its associated second discharge hole 410 B.
- the second suction chamber 27 B and the second connecting passage 37 B are communicable with each other through the second suction communication hole 410 C.
- the first rear communication passage 20 A and the second rear communication passage 20 B are communicable with each other through the second discharge communication hole 410 D.
- the second suction valve plate 411 is provided on the front surface of the second valve plate 410 and has a plurality of second suction reed valves 411 A which are elastically deformable to open and close the second suction holes 410 A.
- the second discharge valve plate 412 is provided on the rear surface of the second valve plate 410 and has a plurality of second discharge reed valves 412 A which are elastically deformable to open and close the second discharge holes 410 B.
- the second retainer plate 413 is provided on the rear surface of the second discharge valve plate 412 for regulating the maximum opening of the second discharge reed valves 412 A.
- a first communication passage 18 is formed by the first front communication passage 18 A, the first discharge communication hole 390 D, the second front communication passage 18 B, and the third front communication passage 18 C.
- a second communication passage 20 is formed by the first rear communication passage 20 A, the second discharge communication hole 410 D, and the second rear communication passage 20 B.
- the swash plate chamber 33 communicates with the first and second suction chambers 27 A, 27 B via the first and second connection passage 37 A, 37 B and the first and second suction communication holes 390 C, 410 C. Therefore, the pressures are substantially the same among the first suction chamber 27 A, the second suction chamber 27 B, and the swash plate chamber 33 . Since the refrigerant gas which has passed through the evaporator is introduced into the swash plate chamber 33 through the inlet port 330 , the pressures in the first and second suction chambers 27 A, 27 B and the swash plate chamber 33 are lower than the pressures in the first and second discharge chambers 29 A, 29 B.
- the drive shaft 3 includes a drive shaft body 30 (a drive shaft main body 30 ), a first support member 43 A and a second support member 43 B.
- the drive shaft body 30 extending rearward from the boss 17 A is inserted through the first and second sliding bearings 22 A, 22 B.
- the drive shaft 3 is supported in the first and second cylinder blocks 21 , 23 so as to be rotatable about the axis of rotation O.
- the front end of the drive shaft body 30 extends into the boss 17 A, and the rear end of the drive shaft body 30 projects beyond the projection 23 F and the second sliding bearing 22 B and into the pressure regulation chamber 31 .
- the first support member 43 A is press-fitted on the front end part of the drive shaft body 30 . With the rotation of the drive shaft 3 about the axis of rotation O, the first support member 43 A is rotated with the drive shaft 3 in sliding contact with the first sliding bearing 22 A.
- the first support member 43 A is formed at the rear end part thereof with a flange 430 and a mounting (not shown) into which a second pin 47 B, which will be described later, is inserted.
- the flange 430 serves as a retainer for the first thrust bearing 35 A. Specifically, the flange 430 and the inner wall surface of the first recessed portion 21 C cooperate to hold therebetween the first thrust bearing 35 A.
- the front end of a first return spring 44 A is fixed on the first support member 43 A. The first return spring 44 A extends in the direction of the axis of rotation O toward the swash plate chamber 33 from the flange 430 of the first support member 43 A.
- the second support member 43 B is press-fitted on the rear end part of the drive shaft body 30 so that the rear end surface of the second support member 43 B is flush with the rear end surface of the drive shaft body 30 .
- the rear end of the second support member 43 B projects beyond the projection 23 F and the second sliding bearing 23 B and into the pressure regulation chamber 31 .
- the second support member 43 B With the rotation of the drive shaft 3 about the axis of rotation O, the second support member 43 B is rotated in sliding contact with the second sliding bearing 22 B.
- a flange 431 is formed at the front end of the second support member 43 B.
- the flange 431 is disposed between the second thrust bearing 35 B and the actuator 13 and serves as a retainer for the second thrust bearing 35 B.
- the flange 431 and the inner wall surface of the first recessed portion 21 C cooperate to hold therebetween the second thrust bearing 35 B.
- the second support member 43 B corresponds to the cap of the present invention.
- the swash plate 5 is a circular, flat plate having a front surface 5 A and a rear surface 5 B.
- the front surface 5 A faces frontward and the rear surface 5 B faces rearward.
- the swash plate 5 is fixed to a ring plate 45 .
- the ring plate 45 is a circular, flat plate having an insertion hole 45 A in the center thereof.
- the swash plate 5 is mounted to the drive shaft 3 with the drive shaft body 30 passed through the insertion hole 45 A of the swash plate 5 .
- the aforementioned link mechanism 7 includes a lug arm 49 .
- the lug arm 49 is disposed frontward of the swash plate 5 in the swash plate chamber 33 and located between the swash plate 5 and the first support member 43 A.
- the lug arm 49 is formed substantially in an L shape as viewed toward the rear end thereof.
- the lug arm 49 is in contact the flange 430 of the first support member 43 A, as shown in FIG. 4 .
- the minimum inclination angle position of the swash plate 5 is determined by the contact of the lug arm 49 with the flange 430 .
- the lug arm 49 has in the rear part thereof a weight portion 49 A extending for half the circumference of the actuator 13 . It is to be noted that the weight portion 49 A may be formed in any shape appropriately through design.
- the lug arm 49 is connected at the rear end thereof to one end of the ring plate 45 through a first pin 47 A.
- the lug arm 49 is supported at the front end thereof so as to be swingable about a first pivot axis M1 which is the axial center of the first pin 47 A with respect to the one end of the ring plate 45 , i.e., the swash plate 5 .
- the first pivot axis M1 extends in the direction perpendicular to the axis of rotation O of the drive shaft 3 .
- the lug arm 49 is connected at the front end thereof to the first support member 43 A through the second pin 47 B. With this configuration, the lug arm 49 is supported at the rear end thereof so as to be swingable about a second pivot axis M2 which is the axial center of the second pin 47 B with respect to the first support member 43 A, i.e., the drive shaft 3 .
- the second pivot axis M2 extends parallel to the with the first pivot axis M1.
- the lug arm 49 , the first pin 47 A and the second pin 47 B correspond to the link mechanism 7 of the present invention.
- the weight portion 49 A extends rearward from the first pivot axis M1, and therefore, the weight portion 49 A of the lug arm 49 is supported on the ring plate 45 with the first pin 47 A.
- the weight portion 49 A is passed through a groove portion 45 B of the ring plate 45 and positioned behind the ring plate 45 , that is, on the rear surface 5 B side of the swash plate 5 .
- the centrifugal force generated by the rotation of the swash plate 5 about the axis of rotation O acts on the weight portion 49 A on the rear surface 5 B side of the swash plate 5 .
- the swash plate 5 is connected to the drive shaft 3 via the link mechanism 7 for rotation with the drive shaft 3 .
- the inclination angle of the swash plate 5 is variable with the swinging motion of the opposite ends of the lug arm 49 about the first pivot axis M1 and the second pivot axis M2, respectively.
- Each piston 9 has a first piston head 9 A at the front end thereof and a second piston head 9 B at the rear end thereof.
- Each first piston head 9 A is received in its associated first cylinder bore 21 A so as to be reciprocally movable.
- Each first cylinder bore 21 A has therein a first compression chamber 21 D which is formed between the first piston head 9 A and the first valve forming plate 39 .
- Each second piston head 9 B is received in its associated second cylinder bore 23 A so as to be reciprocally movable.
- Each second cylinder bore 23 A has therein a second compression chamber 23 D which is formed between the second piston head 9 B and the second valve forming plate 41 . Since the first cylinder bores 21 A and the second cylinder bores 23 A have the same diameter as mentioned above, the first piston head 9 A and the second piston head 9 B are formed to have the same diameter.
- Each piston 9 has at the longitudinal center thereof a recessed portion 9 C and the pair of hemispherical shoes 11 A, 11 B is received in the recessed portion 9 C.
- the shoes 11 A, 11 B convert the rotation of the swash plate 5 into the reciprocating motion of the pistons 9 in the respective cylinder bores 21 A, 23 A.
- the shoes 11 A, 11 B correspond to the conversion mechanism of the present invention.
- the first and second piston heads 9 A, 9 B are reciprocable in the first and second cylinder bores 21 A, 23 A, respectively, for a stroke length according to the inclination angle of the swash plate 5 .
- the top dead center of the respective first piston heads 9 A and the second piston heads 9 B is shifted. Specifically, in the state of FIG. 1 where the inclination angle of the swash plate 5 and the stroke length of the pistons 9 are the maximum, the top dead centers of the first piston heads 9 A and the second piston head 9 B are located at positions closest to the first valve forming plate 39 and the second valve forming plate 41 , respectively. As will be appreciated from comparison of FIGS.
- the top dead center of the second piston heads 9 B becomes more distant from the second valve forming plate 41 with a decrease of the inclination angle of the swash plate 5 and hence of the stroke length of the pistons 9 .
- the top dead center of the first piston heads 9 A is shifted very little when the stroke of the pistons 9 is the maximum and the position which is close to the first valve forming plate 39 is maintained.
- the shifting of the top dead center of the second piston head 9 B becomes greater than that of the first piston head 9 A.
- the actuator 13 is disposed in the swash plate chamber 33 .
- the actuator 13 is located behind the swash plate 5 and movable into the second recessed portion 23 C.
- the actuator 13 includes a movable body 13 A and a fixed body 13 B and a pressure control chamber 13 C is formed between the movable body 13 A and the fixed body 13 B.
- the movable body 13 A includes a body 130 and a peripheral wall 131 .
- the body 130 forms the rear part of the movable body 13 A and extends radially from the drive shaft 3 .
- the peripheral wall 131 is connected to the outer circumferential edge of the body 130 and extends in the axial direction of the drive shaft 3 .
- the peripheral wall 131 has at the front end thereof a connecting portion 132 .
- the body 130 , the peripheral wall 131 and the connecting portion 132 cooperate to form the movable body 13 A of a shape of a closed-end cylinder.
- the fixed body 13 B is formed of a circular plate having substantially the same diameter as the inner diameter of the movable body 13 A.
- a second return spring 44 B is provided between the fixed body 13 B and the ring plate 45 .
- the return spring 44 B is fixed at the rear end thereof to the fixed body 13 B and fixed at the front end thereof to the other end of the ring plate 45 , or the end of the ring plate 45 that is opposite from the end thereof to which the lug arm 49 is connected.
- the drive shaft body 30 extends through the center holes of the movable body 13 A and the fixed body 13 B, so that the movable body 13 A in the second recessed portion 23 C is located opposite from the link mechanism 7 with respect to the swash plate 5 .
- the fixed body 13 B is disposed within the movable body 13 A at a position rearward of the swash plate 5 and the periphery of the fixed body 13 B is covered by the peripheral wall 131 of the movable body 13 A.
- the pressure control chamber 13 C is formed between the movable body 13 A and the fixed body 13 B.
- the pressure control chamber 13 C is defined by the body 130 and the peripheral wall 131 of the movable body 13 A and the fixed body 13 B, thereby being separated from the swash plate chamber 33 .
- the movable body 13 A is mounted on the drive shaft body 30 in such a way that the movable body 13 A is rotatable with the drive shaft 3 and also slidable in the swash plate chamber 33 in the axial direction O of the drive shaft 3 .
- the fixed body 13 B is fixedly mounted on the drive shaft body 30 with the drive shaft body 30 inserted in the fixed body 13 B, so that the fixed body 13 B is rotatable with the drive shaft 3 , but immovable in the axial direction O. Therefore, the movable body 13 A is movable relative to the fixed body 13 B in the axial direction O of the drive shaft 3 .
- the connecting portion 132 of the movable body 13 A is connected to the other end of the ring plate 45 through a third pin 47 C, so that the other end of the ring plate 45 is supported, that is, the swash plate 5 is supported by the movable body 13 A so as to be swingable about a pivot axis M3 of the third pin 47 C.
- the pivot axis M3 extends parallel to the first and second pivot axes M1, M2.
- the movable body 13 A is thus connected to the swash plate 5 .
- the movable body 13 A is in contact with the flange 431 of the second support member 43 B when the swash plate 5 is placed at the maximum inclination angle position.
- the drive shaft body 30 has therein an axial passage 3 B extending in the axial direction O and opened in the rear end surface of the drive shaft body 30 and a radial passage 3 C extending from the front end of the axial passage 3 B and opened in the peripheral surface of the drive shaft body 30 . Because the rear end of the drive shaft body 30 projects into the pressure regulation chamber 31 , the rear end of the axial passage 3 B is also located and is opened to the pressure regulation chamber 31 . The radial passage 3 C is opened to the control chamber 13 C. With this configuration, the pressure control chamber 13 C communicates with the pressure regulation chamber 31 through the radial passage 3 C and the axial passage 3 B.
- the drive shaft body 30 has at the front end thereof a threaded portion 3 D.
- the drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) at the threaded portion 3 D.
- the control mechanism 15 includes a low-pressure passage 15 A, a high-pressure passage 15 B, a control valve 15 C, an orifice 15 D and the aforementioned axial and radial passages 3 B, 3 C.
- the axial passage 3 B and the radial passage 3 C correspond to the pressure-changing passages of the present invention.
- the low-pressure passage 15 A, the high-pressure passage 15 B, the axial passage 3 B and the radial passage 3 C correspond to the control passages of the present invention.
- the low-pressure passage 15 A is connected to the pressure regulation chamber 31 and the second suction chamber 27 B.
- the pressure control chamber 13 C, the pressure regulation chamber 31 and the second suction chamber 27 B communicate with each other through the low-pressure passage 15 A, the axial passage 3 B and the radial passage 3 C.
- the high-pressure passage 15 B is connected to the pressure regulation chamber 31 and the second discharge chamber 29 B.
- the pressure control chamber 13 C, the pressure regulation chamber 31 and the second discharge chamber 29 B communicate with each other through the high-pressure passage 15 B, the axial passage 3 B and the radial passage 3 C.
- the orifice 15 D is formed in the high-pressure passage 15 B for restricting the flow rate of the refrigerant gas flowing in the high-pressure passage 15 B.
- the control valve 15 C is formed in the low-pressure passage 15 A and regulates the opening of the low-pressure passage 15 A based on the pressure in the second suction chamber 27 B.
- the aforementioned evaporator is connected to the inlet port 330 of the compressor through a tube and the condenser is connected to the outlet port 230 through a tube.
- the condenser is connected to the evaporator through a tube and an expansion valve.
- the compressor, the evaporator, the expansion valve, the condenser and the like cooperate to form the refrigeration circuit of a vehicle air conditioning system. It is to be noted that the evaporator, the expansion valve, the condenser and the tubes are omitted from illustration in the drawings.
- the rotation of the drive shaft 3 rotates the swash plate 5 , causing the pistons 9 to reciprocate in the first and second cylinder bores 21 A, 23 A, so that compression of refrigerant gas is performed in the first and second compression chambers 21 D, 23 D.
- the displacement of the compressor varies according to the stroke length of the pistons 9 .
- the suction phase in which refrigerant gas is drawn into the first and second cylinder bores 21 A, 23 A, the compression phase in which compressing the refrigerant gas is performed in the first and second cylinder bores 21 A, 23 A, and the discharge phase in which the compressed refrigerant gas is discharged from the first and second cylinder bores 21 A, 23 A are repeated.
- the refrigerant gas which is drawn from the evaporator into the swash plate chamber 33 through the inlet port 330 is flowed into the first suction chamber 27 A through the first connecting passage 37 A.
- the refrigerant gas in the first suction chamber 27 A is then drawn into the first cylinder bore 21 A through the first suction hole 390 A due to the pressure difference which is created between the first cylinder bore 21 A and the first suction chamber 27 A and opens the first suction reed valves 391 A.
- the refrigerant gas in the swash plate chamber 33 is also flowed into the second suction chamber 27 B through the second connecting passage 37 B and then drawn into the second cylinder bore 23 A through the second suction hole 410 A due to the pressure difference which is created between the second cylinder bore 23 A and the second suction chamber 27 B and opens the second suction reed valves 411 A.
- the refrigerant gas compressed in the first compression chamber 21 D is discharged into the first discharge chamber 29 A and flowed toward the combined discharge chamber 231 through the first communication passage 18 .
- the refrigerant gas compressed in the second compression chamber 23 D is discharged into the second discharge chamber 29 B and flowed toward the combined discharge chamber 231 through the second communication passage 20 .
- the refrigerant gas in the combined discharge chamber 231 is discharged out through the outlet port 230 toward the condenser.
- the compression force of the pistons 9 acts on the swash plate 5 , the ring plate 45 , the lug arm 49 , and the first pin 47 A in such a way that reduces the inclination angle of the swash plate 5 .
- a change in the inclination angle of the swash plate 5 increases or decreases the stroke length of the pistons 9 thereby to change the discharge displacement.
- the inclination angle of the swash plate 5 with respect to a plane extending perpendicular to the axis of rotation O of the drive shaft 3 decreases and the stroke length of the pistons 9 decreases. Accordingly, the displacement of the compressor per one rotation of the drive shaft 3 is decreased. It is to be noted that the inclination angle of the swash plate 5 shown in FIG. 4 corresponds to the minimum inclination angle.
- the centrifugal force acting on the weight portion 49 A is imparted to the swash plate 5 in such a way that the swash plate 5 tends to shift easily in the direction that reduces the inclination angle of the swash plate 5 .
- the movable body 13 A moves frontward in the swash plate chamber 33 to a position where the front end of the movable body 13 A is located radially inner side of the weight portion 49 A.
- the inclination angle of the swash plate 5 is reduced to minimum, about front half of the front end of the movable body 13 A is covered with the weight portion 49 A.
- the ring plate 45 is brought into contact with the rear end of the first return spring 44 A. Then the first return spring 44 A is elastically deformed and the rear end of the first return spring 44 A approaches the first support member 43 A.
- the pressure in the pressure control chamber 13 C becomes substantially the same as the pressure in the second discharge chamber 29 B. Accordingly, the movable body 13 A moves rearward in the swash plate chamber 33 against the compression force of the pistons acting on the swash plate 5 , so that the movable body 13 A is moved away from the lug arm 49 .
- the lug arm 49 moves away from the flange 430 of the first support member 43 A and the swash plate 5 swings about the first pivot axis M1 with the pivot axis M3 as the point of action and the pivot axis M1 as the fulcrum point in the direction that is opposite to the direction that decreases the inclination angle of the swash plate 5 . Therefore, the inclination angle of the swash plate 5 increases and the stroke length of the pistons 9 is lengthened, with the result that the displacement of the compressor per one rotation of the drive shaft 3 is increased. It is to be noted that the inclination angle of the swash plate 5 shown in FIG. 1 corresponds to the maximum inclination angle.
- the refrigerant gas in the second discharge chamber 29 B is drawn into the pressure regulation chamber 31 through the high-pressure passage 15 B of the control mechanism 15 .
- the refrigerant gas in the second discharge chamber 29 B which has been just compressed in the second compression chamber 23 D, has a high temperature and a high pressure.
- the pressure regulation chamber 31 is disposed in the rear housing 19 at a position radially inward of the second discharge chamber 29 B and surrounded by the second discharge chamber 29 B.
- the refrigerant in the pressure regulation chamber 31 is heated by high-temperature refrigerant gas in the second discharge chamber 29 B and part of the rear housing 19 in the vicinity of the second discharge chamber 29 B and, therefore, the refrigerant gas in the pressure regulation chamber 31 will also be heated.
- the refrigerant gas in the pressure regulation chamber 31 tends to be less cooled by the second suction chamber 27 B because the refrigerant gas in the pressure regulation chamber 31 is less susceptible to the influence of low-temperature refrigerant gas in the second suction chamber 27 B.
- the first and second cylinder blocks 21 , 23 , the first and second sliding bearings 22 A, 22 B, and the first and second support members 43 A, 43 B are heated by friction.
- the drive shaft body 30 is also heated by the heat transmitted from the second support member 43 B and the like.
- the first and second thrust bearings 35 A, 35 B are also heated by the friction caused during the rotation of the drive shaft 3 .
- the second thrust bearing 35 B is provided between the second recessed portion 23 C of the second cylinder block 23 and the flange 431 of the second support member 43 B, the heat generated in the second thrust bearing 35 B is transmitted to the second cylinder block 23 and the second support member 43 B.
- the refrigerant gas in the pressure regulation chamber 31 may be heated directly by the members projecting into the pressure regulation chamber 31 , such as the projection 23 F of the second cylinder block 23 , the second sliding bearing 22 B, the rear end of the second support member 43 B and the rear end of the drive shaft body 30 that project into the pressure regulation chamber 31 .
- the temperature of the refrigerant gas which is drawn from the second discharge chamber 29 B into the pressure regulation chamber 31 is hard to drop. Therefore, in the compressor wherein the drive shaft body 30 is heated as described above and the rear end of the axial passage 3 B is located in the pressure regulation chamber 31 , the refrigerant gas flowed from the pressure regulation chamber 31 into the pressure control chamber 13 C is hard to be cooled in the axial passage 3 B and the radial passage 3 C. If liquefied refrigerant exists in the pressure regulation chamber 31 due to cooling, the pressure change in the pressure control chamber 13 C is inhibited.
- the refrigerant in the pressure regulation chamber 31 is hardly to be liquefied, with the result that the pressure of the refrigerant gas flowed into the pressure control chamber 13 C through the pressure regulation chamber 31 is varied quickly and the movable body 13 A is moved smoothly in response to a change of the pressure in the pressure control chamber 13 C and, therefore, the inclination angle of the swash plate is changed quickly according to a change of the operating condition of the compressor.
- the compressor according to the embodiment exhibits good controllability.
- the drive shaft including the drive shaft body and the cap maintains the simple form of the drive shaft main body to thereby provide a simplified manufacturing process of the compressor, while heating the refrigerant with the cap.
- the first discharge chamber 29 A may be formed radially inward of the front housing 17 and the first suction chamber 27 A radially outward of the first discharge chamber 29 A.
- the configuration of the control mechanism 15 may be such that the control valve 15 C is formed in the high-pressure passage 15 B and the orifice 15 D is formed in the low-pressure passage 15 A. In this case, the opening of the high-pressure passage 15 B is regulated by the control valve 15 C. In the compressor of such configuration, the pressure in the pressure control chamber 13 C is raised quickly by the high pressure in the second discharge chamber 29 B, so that an increase of the displacement of the compressor may be accomplished quickly.
- the compressor may be configured such that the actuator 13 is disposed on the front surface 5 A side and the lug arm 49 on the rear surface 5 B side of the swash plate 5 .
- the compressor may further be configured such that the compression chamber is formed in either the first cylinder block 21 or the second cylinder block 23 .
- the present invention is applicable to an air conditioning apparatus or and the like.
Abstract
In a swash plate type variable displacement compressor, a rear housing has a pressure regulation chamber into which a rear end of a drive shaft body, a projection of a second cylinder block, a second sliding bearing, and a rear end of a second support member project. In the compressor, when a drive shaft is rotated, heat is generated in the drive shaft body, the projection, the second sliding bearing, and the second support member to heat the refrigerant gas in the pressure regulation chamber. Accordingly, in the compressor, temperature of the refrigerant gas in the pressure regulation chamber is hard to drop. Therefore, the pressure of the refrigerant gas flowing from the pressure regulation chamber to the pressure control chamber is varied quickly and a movable body is preferably moved with the pressure in the pressure control chamber.
Description
- The present invention relates to a swash plate type variable displacement compressor.
- Japanese Unexamined Patent Application Publication No. 5-172052 discloses a swash plate type variable displacement compressor (hereinafter, referred to as the compressor). The compressor has a housing which includes a front housing, a cylinder block and a rear housing. Each of the front housing and the rear housing has therein a suction chamber and a discharge chamber. The rear housing has therein a pressure regulation chamber which is formed in the center of the rear housing. The suction chamber is formed radially outward of the pressure regulation chamber and the discharge chamber is formed radially outward of the suction chamber.
- The cylinder block has therein a swash plate chamber, a plurality of cylinder bores and a main shaft insertion hole. Each cylinder bore has a first cylinder bore which is formed in the rear of the cylinder block and a second cylinder bore which is formed in the front of the cylinder block. The main shaft insertion hole is formed in the rear of the cylinder block and communicates with the swash plate chamber and the pressure regulation chamber.
- A drive shaft is disposed extending in the housing and rotatably supported in the cylinder block. A swash plate is mounted on the drive shaft for rotation therewith in the swash plate chamber. A link mechanism is provided between the drive shaft and the swash plate which permits the inclination of the swash plate. The angle of inclination refers to an angle of the swash plate with respect to a plane extending perpendicular to the axis of rotation of the drive shaft.
- A plurality of pistons is received in the respective cylinder bores so that the pistons are movable in the reciprocating manner. Specifically, each piston has a first piston head which reciprocates in the first cylinder bore and a second piston head which reciprocates in the second cylinder bore. Therefore, the compressor has a first compression chamber formed by the first cylinder bore and the first piston head and a second compression chamber formed by the second cylinder bore and the second piston head. The compressor further includes a conversion mechanism that converts the rotation of the swash plate into reciprocal movement of the pistons in the respective cylinder bores with a stroke length that is determined by the inclination angle of the swash plate. The inclination angle of the swash plate can be controllably changed by an actuator, which is controlled by a control mechanism of the compressor.
- The actuator is disposed on the first cylinder bore side of the swash plate chamber. The actuator includes a non-rotating movable body, a movable body and a thrust bearing. The actuator has therein a pressure control chamber. The non-rotating movable body is disposed in the main shaft insertion hole so that the non-rotating movable body is not rotatable with the drive shaft and covers the rear end of the drive shaft. This non-rotating movable body rotatably supports on the inner peripheral surface thereof the rear end of the drive shaft. The non-rotating movable body is movable back and forth in the main shaft insertion hole in the axial direction of the rotating shaft in sliding contact with the inner peripheral surface of the main drive shaft hole. The non-rotating movable body is configured so as not to slide about the axial center of rotation. The movable body is connected to the swash plate and is movable therewith in the axial direction of the drive shaft. The thrust bearing is disposed between the non-rotating movable body and the movable body.
- The main shaft insertion hole in the cylinder block is partitioned by the non-rotating movable body, thereby forming the pressure control chamber on the rear end side of the main shaft insertion hole. The rear end of the drive shaft is rotatably supported on the inner peripheral surface of the non-rotating movable body at a position frontward of the pressure control chamber. The pressure control chamber communicates with the pressure regulation chamber in the rear housing. A pressure spring is provided in the pressure control chamber so as to urge the non-rotating movable body in the frontward direction.
- The control mechanism includes a control passage and a control valve provided in the control passage. The control passage provides communication between the discharge chamber and the pressure regulation chamber. By regulating the opening of the control passage, the control valve varies the pressure in the pressure control chamber thereby to move the non-rotating movable body and the movable body move together in the axial direction of the drive shaft.
- The link mechanism has the movable body and a lug arm fixed on the drive shaft. The lug arm has at the rear end thereof an elongated hole that extends in the direction perpendicular to the axis of the drive shaft and also radially inwardly from the outer periphery thereof to the axial center. The swash plate is supported at the front thereof such that the swash plate is allowed to pivot about a first pivot pin inserted through the elongated hole. The movable body also has at the front end thereof an elongated hole which extends in the direction perpendicular to the axis of the drive shaft and also in the direction approaching the axis of the drive shaft from the outer periphery thereof. The swash plate is also supported at the rear end thereof such that the swash plate is allowed to pivot about a second pivot pin which is parallel to the center of the first pivot pin and inserted through the elongated hole.
- In the compressor, by adjusting the opening of the control passage with the control valve, the pressure in the pressure regulation chamber and hence the pressure in the pressure control chamber can be controlled by the pressure of the refrigerant gas in the discharge chamber.
- Specifically, increasing the pressure in the pressure regulation chamber by the control valve increases the pressure in the pressure control chamber higher than the pressure in the swash plate chamber. As a result, the non-rotating movable body and the movable body in the main shaft insertion hole advance in the axial direction of the rotating shaft. Then, the inclination angle of the swash plate is increased and the stroke of the pistons is increased. Accordingly, the displacement of the compressor per one rotation of the drive shaft is increased.
- By reducing the pressure in the pressure regulation chamber by the control valve, the pressure in the pressure control chamber becomes almost the same as the pressure in the swash plate chamber. Accordingly, the non-rotating movable body and the movable body in the main shaft insertion hole retreat in the axial direction of the rotating shaft. Therefore, the inclination angle of the swash plate is reduced and hence the stroke of the pistons is reduced, with the result that the displacement of the compressor per one rotation of the drive shaft is decreased.
- In the above-described swash plate type variable displacement compressor, the suction chamber is disposed radially outward of the pressure regulation chamber. Since the temperature of the refrigerant gas in the suction chamber is lower, the pressure regulation chamber is cooled and, therefore, the temperature of the refrigerant gas in the pressure regulation chamber drops, thus liquefying part of the refrigerant gas in the pressure regulation chamber. Thus, refrigerant of two phases, namely gaseous refrigerant and liquefied refrigerant is present in the pressure regulation chamber. If the proportion of the liquefied refrigerant increases, the pressure in the pressure regulation chamber increases less quickly by the refrigerant flowing from the discharge chamber into the pressure regulation chamber. Due to an increase of the proportion of the liquefied refrigerant, the pressure in the pressure regulation chamber decreases less quickly by the refrigerant flowing from the pressure regulation chamber into the suction chamber. In the compressor of the above-cited publication, therefore, it is difficult to move the non-rotating movable body and the movable body in a desirable manner. Specifically, in the compressor, it is difficult to vary the inclination angle of the swash plate quickly according to a change of the operating conditions of the vehicle on which the compressor is mounted and also the discharge displacement of the compressor is less controllable.
- The present invention, which has been made in view of the above-identified circumstances, is directed to providing a swash plate type variable displacement compressor that offers improved controllability.
- In accordance with an aspect of the present invention, the swash plate type variable displacement compressor includes a housing having therein a suction chamber, a discharge chamber, a swash plate chamber, and a plurality of cylinder bores; a drive shaft rotatably supported in the housing; a swash plate which is rotatable in the swash plate chamber with the rotation of the drive shaft; a link mechanism which is disposed between the drive shaft and the swash plate and allows a change in an inclination angle of the swash plate with respect to the direction perpendicular to the axis of the drive shaft; a plurality of pistons which is reciprocally received in the respective cylinder bores; a conversion mechanism which converts the rotation of the drive shaft into reciprocal movement of the pistons in the respective cylinder bores in conjunction with the swash plate with a stroke length according to the inclination angle of the swash plate; an actuator for changing the inclination angle of the swash plate; and a control mechanism which controls the actuator. The housing has therein a pressure regulation chamber. The pressure regulation chamber is disposed radially inward of the discharge chamber, which is disposed radially inward of the suction chamber. The actuator includes a fixed body, a movable body, and a pressure control chamber. The fixed body is fixed on the drive shaft in the swash plate chamber. The movable body is connected to the swash plate and movable relative to the fixed body in the direction of the axis of rotation. The pressure control chamber is defined by the fixed body and the movable body and the pressure in the pressure control chamber is changed by introducing the pressure in the discharge chamber into the pressure control chamber such that the movable body is moved. The control mechanism has a control passage and a control valve. The control passage provides communication between the discharge chamber and the pressure control chamber via the pressure regulation chamber. The control valve adjusts an opening of the control passage to vary pressure in the pressure regulation chamber such that the movable body is moved. At least a part of the control passage is formed in the drive shaft, and the drive shaft projects into the pressure regulation chamber such that the control passage connects the pressure regulation chamber and the pressure control chamber.
- Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
- The features of the present invention that are believed to be novel are set forth with particularity in the appended claims. The invention together with objects and advantages thereof, may best be understood by reference to the following description of the embodiments together with the accompanying drawings in which:
-
FIG. 1 is a longitudinal sectional view of a compressor according to an embodiment of the present invention, showing the maximum displacement of the compressor; -
FIG. 2 is a schematic diagram of a control mechanism of the compressor ofFIG. 1 ; -
FIG. 3 is a transverse sectional view of the compressor as viewed in arrow direction III-III inFIG. 1 ; and -
FIG. 4 is a longitudinal sectional view of the compressor ofFIG. 1 in the minimum displacement. - The following will describe a compressor embodying the present invention with reference to the drawings. The compressor of the embodiment is a swash plate type variable displacement compressor which is mounted on a vehicle and forms a part of a refrigeration circuit for an air conditioning system of the vehicle.
- Referring to
FIG. 1 , the compressor according to the present embodiment includes ahousing 1, adrive shaft 3, aswash plate 5, alink mechanism 7, a plurality of double-headedpistons 9, pairs ofshoes actuator 13 and acontrol mechanism 15 which is shown inFIG. 2 . - The
housing 1 includes afront housing 17 disposed on the front side of the compressor, arear housing 19 disposed on the rear side of the compressor, first and second cylinder blocks 21, 23 disposed between thefront housing 17 and therear housing 19, and first and secondvalve forming plates - The
front housing 17 has aboss 17A projecting frontward. Theboss 17A has ashaft sealing device 25. Thefront housing 17 has therein afirst suction chamber 27A and afirst discharge chamber 29A. Thefirst suction chamber 27A is formed in a radially inner region inward of thefront housing 17. Thefirst discharge chamber 29A is formed in an annular shape and disposed outward of thefirst suction chamber 27A in thefront housing 17. - The
front housing 17 has therein a firstfront communication passage 18A which communicates at the front end thereof with thefirst discharge chamber 29A and opens at the rear end thereof at the rear end of thefront housing 17. - The
control mechanism 15 is disposed in therear housing 19. As shown inFIG. 3 , therear housing 19 has therein asecond suction chamber 27B, asecond discharge chamber 29B, and apressure regulation chamber 31. Specifically, thepressure regulation chamber 31 is disposed in the center of therear housing 19. Thesecond discharge chamber 29B is formed in an annular shape and formed radially outward of thepressure regulation chamber 31 in therear housing 19 so as to surround thepressure regulation chamber 31. Thesecond suction chamber 27B is formed into a substantially C shape and disposed radially outward of thesecond discharge chamber 29B in therear housing 19. - Furthermore, the
rear housing 19 has therein a firstrear communication passage 20A which communicates at the rear end thereof with thesecond discharge chamber 29B. As shown inFIG. 1 , the front end of the firstrear communication passage 20A is open at the front end of therear housing 19. - A
swash plate chamber 33 is formed between afirst cylinder block 21 and thesecond cylinder block 23. Theswash plate chamber 33 is disposed substantially in the center of thehousing 1 as seen in the longitudinal direction of the compressor. - A plurality of first cylinder bores 21A is formed substantially at an equal angular distance in the circumferential direction of the
first cylinder block 21. Thefirst cylinder block 21 has therethrough afirst shaft hole 21B through which thedrive shaft 3 is inserted. Thefirst shaft hole 21B has a first sliding bearing 22A, although a rolling bearing may alternatively be used. - The
first cylinder block 21 further has therein a first recessedportion 21C which is annular and coaxial with thefirst shaft hole 21B. The first recessedportion 21C communicates with theswash plate chamber 33. The inner diameter of the annular first recessedportion 21C is reduced in the form of a step toward the front end thereof. A first thrust bearing 35A is provided in the first recessedportion 21C at the front end thereof. Thefirst cylinder block 21 further has therein a first connectingpassage 37A which provides communication between theswash plate chamber 33 and thefirst suction chamber 27A. Thefirst cylinder block 21 has therein afirst retaining groove 21E for regulating the maximum opening of firstsuction reed valves 391A, which will be described later. - The
first cylinder block 21 further has therein a secondfront communication passage 18B which is open at the opposite front and rear ends thereof. - The
second cylinder block 23 has therein a plurality of second cylinder bores 23A as in the case of thefirst cylinder block 21. Each second cylinder bore 23A on the rear side is paired with its associatedfirst cylinder bore 21A on the front side. The first cylinder bores 21A and the second cylinder bores 23A are of the same diameter. It is to be noted that thesecond cylinder block 23 corresponds to the cylinder block of the present invention. - Furthermore, the
second cylinder block 23 has aprojection 23F extending rearward. With thesecond cylinder block 23, the secondvalve forming plate 41 and therear housing 19 joined together, theprojection 23F projects into thepressure regulation chamber 31 projecting beyond the secondvalve forming plate 41. The distance for which theprojection 23F projects into thepressure regulation chamber 31 may appropriately be changed according to the design. - Furthermore, the
second cylinder block 23 has therein asecond shaft hole 23B through which thedrive shaft 3 is inserted. Thesecond shaft hole 23B extends also in theprojection 23F and is opened to thepressure regulation chamber 31. Thesecond shaft hole 23B has therein a second sliding bearing 22B the rear end of which projects to thepressure regulation chamber 31. The second sliding bearing 22B corresponds to the radial bearing of the present invention. It is to be noted that the second slidingbearing 22B may be replaced with a roller bearing. - The
second cylinder block 23 has therein a second recessedportion 23C which is annular and coaxial with thesecond shaft hole 23B. The second recessedportion 23C also communicates with theswash plate chamber 33. The inner diameter of the second annular recessedportion 23C is reduced in the form of a step toward the rear end thereof. A second thrust bearing 35B is provided in the second recessedportion 23C at the rear end thereof. The second thrust bearing 35B corresponds to the thrust bearing of the present invention. Thesecond cylinder block 23 further has therein a second connectingpassage 37B which provides communication between theswash plate chamber 33 and thesecond suction chamber 27B. Thesecond cylinder block 23 has therein asecond retaining groove 23E for regulating the maximum opening of secondsuction reed valves 411A, which will be described later. - The
second cylinder block 23 has therein anoutlet port 230, a combineddischarge chamber 231, a thirdfront communication passage 18C, a secondrear communication passage 20B and aninlet port 330. Theoutlet port 230 and the combineddischarge chamber 231 are in direct communication with each other. Theoutlet port 230 and the combineddischarge chamber 231 are formed in thesecond cylinder block 23 at positions adjacent to the front end of thesecond cylinder block 23 so that they are disposed substantially in the longitudinal center of thehousing 1. The combineddischarge chamber 231 is connected through thedischarge port 230 to a condenser (not shown). - The third
front communication passage 18C is open at the front end thereof in the front end of thesecond cylinder block 23 and communicates directly at the rear end thereof with the combineddischarge chamber 231. With thefirst cylinder block 21 and thesecond cylinder block 23 joined together, the thirdfront communication passage 18C communicates with the secondfront communication passage 18B at the rear end thereof. - The second
rear communication passage 20B communicates directly at the front end thereof with the combineddischarge chamber 231 and open at the rear end thereof in the rear end of thesecond cylinder block 23. - The
inlet port 330 is formed at a position adjacent to the front end of thesecond cylinder block 23 so that theinlet port 330 is disposed substantially in the longitudinal center of thehousing 1. Theswash plate chamber 33 is connected through thesuction port 330 to an evaporator (not shown) connected in the external refrigeration circuit. - The first
valve forming plate 39 is interposed between thefront housing 17 and thefirst cylinder block 21. The secondvalve forming plate 41 is provided between therear housing 19 and thesecond cylinder block 23. The secondvalve forming plate 41 corresponds to the valve unit of the present invention. - The first and second
valve forming plates valve forming plate 39 is mounted on a projection at the front end of thefirst cylinder block 21 and the secondvalve forming plate 41 is mounted on theprojection 23F of thesecond cylinder block 23. - The first
valve forming plate 39 includes afirst valve plate 390, a firstsuction valve plate 391, a firstdischarge valve plate 392, and afirst retainer plate 393. At least onefirst suction hole 390A is formed through thefirst valve plate 390, the firstdischarge valve plate 392, and thefirst retainer plate 393. Thefirst suction hole 390A corresponds to eachfirst cylinder bore 21A. At least onefirst discharge hole 390B is formed through thefirst valve plate 390 and the firstsuction valve plate 391. Thefirst discharge hole 390B corresponds to eachfirst cylinder bore 21A. Furthermore, at least one firstsuction communication hole 390C is formed through thefirst valve plate 390, the firstsuction valve plate 391, the firstdischarge valve plate 392, and thefirst retainer plate 393. At least one firstdischarge communication hole 390D is formed through thefirst valve plate 390 and the firstsuction valve plate 391. - Each
first cylinder bore 21A is communicable with thefirst suction chamber 27A through its associatedfirst suction hole 390A. Eachfirst cylinder bore 21A is communicable with thefirst discharge chamber 29A through its associatedfirst discharge hole 390B. Thefirst suction chamber 27A and the first connectingpassage 37A are communicable with each other through the firstsuction communication hole 390C. The firstfront communication passage 18A and the secondfront communication passage 18B are communicable with each other through the firstdischarge communication hole 390D. - The first
suction valve plate 391 is provided on a rear surface of thefirst valve plate 390 and has the plurality of firstsuction reed valves 391A which are elastically deformable to open and close the first suction holes 390A. The firstdischarge valve plate 392 is provided on a front surface of thefirst valve plate 390 and has a plurality of firstdischarge reed valves 392A which are elastically deformable to open and close the first discharge holes 390B. Thefirst retainer plate 393 is provided on the front surface of thefirst discharge plate 392 for regulating the maximum opening of the firstdischarge reed valves 392A. - The second
valve forming plate 41 includes asecond valve plate 410, a secondsuction valve plate 411, a seconddischarge valve plate 412 and asecond retainer plate 413. At least onesecond suction hole 410A is formed through thesecond valve plate 410. Thesecond suction hole 410A corresponds to each second cylinder bore 23A. At least onesecond discharge hole 410B is formed through thesecond valve plate 410 and the secondsuction valve plate 411. Thesecond discharge hole 410B corresponds to each second cylinder bore 23A. Furthermore, at least one secondsuction communication hole 410C and at least one seconddischarge communication hole 410D are formed through thesecond valve plate 410 and the secondsuction valve plate 411. - Each second cylinder bore 23A is communicable with the
second suction chamber 27B through its associatedsecond suction hole 410A. Each second cylinder bore 23A is communicable with thesecond discharge chamber 29B through its associatedsecond discharge hole 410B. Thesecond suction chamber 27B and the second connectingpassage 37B are communicable with each other through the secondsuction communication hole 410C. The firstrear communication passage 20A and the secondrear communication passage 20B are communicable with each other through the seconddischarge communication hole 410D. - The second
suction valve plate 411 is provided on the front surface of thesecond valve plate 410 and has a plurality of secondsuction reed valves 411A which are elastically deformable to open and close the second suction holes 410A. The seconddischarge valve plate 412 is provided on the rear surface of thesecond valve plate 410 and has a plurality of seconddischarge reed valves 412A which are elastically deformable to open and close the second discharge holes 410B. Thesecond retainer plate 413 is provided on the rear surface of the seconddischarge valve plate 412 for regulating the maximum opening of the seconddischarge reed valves 412A. - In the compressor, a
first communication passage 18 is formed by the firstfront communication passage 18A, the firstdischarge communication hole 390D, the secondfront communication passage 18B, and the thirdfront communication passage 18C. Asecond communication passage 20 is formed by the firstrear communication passage 20A, the seconddischarge communication hole 410D, and the secondrear communication passage 20B. - In the compressor, the
swash plate chamber 33 communicates with the first andsecond suction chambers second connection passage first suction chamber 27A, thesecond suction chamber 27B, and theswash plate chamber 33. Since the refrigerant gas which has passed through the evaporator is introduced into theswash plate chamber 33 through theinlet port 330, the pressures in the first andsecond suction chambers swash plate chamber 33 are lower than the pressures in the first andsecond discharge chambers - The
drive shaft 3 includes a drive shaft body 30 (a drive shaft main body 30), afirst support member 43A and asecond support member 43B. Thedrive shaft body 30 extending rearward from theboss 17A is inserted through the first and second slidingbearings drive shaft 3 is supported in the first and second cylinder blocks 21, 23 so as to be rotatable about the axis of rotation O. The front end of thedrive shaft body 30 extends into theboss 17A, and the rear end of thedrive shaft body 30 projects beyond theprojection 23F and the second sliding bearing 22B and into thepressure regulation chamber 31. - The
first support member 43A is press-fitted on the front end part of thedrive shaft body 30. With the rotation of thedrive shaft 3 about the axis of rotation O, thefirst support member 43A is rotated with thedrive shaft 3 in sliding contact with the first slidingbearing 22A. Thefirst support member 43A is formed at the rear end part thereof with aflange 430 and a mounting (not shown) into which asecond pin 47B, which will be described later, is inserted. Theflange 430 serves as a retainer for the first thrust bearing 35A. Specifically, theflange 430 and the inner wall surface of the first recessedportion 21C cooperate to hold therebetween the first thrust bearing 35A. The front end of afirst return spring 44A is fixed on thefirst support member 43A. Thefirst return spring 44A extends in the direction of the axis of rotation O toward theswash plate chamber 33 from theflange 430 of thefirst support member 43A. - The
second support member 43B is press-fitted on the rear end part of thedrive shaft body 30 so that the rear end surface of thesecond support member 43B is flush with the rear end surface of thedrive shaft body 30. The rear end of thesecond support member 43B projects beyond theprojection 23F and the second sliding bearing 23B and into thepressure regulation chamber 31. - With the rotation of the
drive shaft 3 about the axis of rotation O, thesecond support member 43B is rotated in sliding contact with the second sliding bearing 22B. Aflange 431 is formed at the front end of thesecond support member 43B. Theflange 431 is disposed between the second thrust bearing 35B and theactuator 13 and serves as a retainer for the second thrust bearing 35B. Specifically, theflange 431 and the inner wall surface of the first recessedportion 21C cooperate to hold therebetween the second thrust bearing 35B. Thesecond support member 43B corresponds to the cap of the present invention. - The
swash plate 5 is a circular, flat plate having afront surface 5A and arear surface 5B. In theswash plate chamber 33, thefront surface 5A faces frontward and therear surface 5B faces rearward. - The
swash plate 5 is fixed to aring plate 45. Thering plate 45 is a circular, flat plate having aninsertion hole 45A in the center thereof. Theswash plate 5 is mounted to thedrive shaft 3 with thedrive shaft body 30 passed through theinsertion hole 45A of theswash plate 5. - The
aforementioned link mechanism 7 includes alug arm 49. Thelug arm 49 is disposed frontward of theswash plate 5 in theswash plate chamber 33 and located between theswash plate 5 and thefirst support member 43A. Thelug arm 49 is formed substantially in an L shape as viewed toward the rear end thereof. When theswash plate 5 is positioned at the minimum inclination angle with respect to a plane extending perpendicular to the axis of rotation O of thedrive shaft 3, thelug arm 49 is in contact theflange 430 of thefirst support member 43A, as shown inFIG. 4 . Thus, the minimum inclination angle position of theswash plate 5 is determined by the contact of thelug arm 49 with theflange 430. Thelug arm 49 has in the rear part thereof aweight portion 49A extending for half the circumference of theactuator 13. It is to be noted that theweight portion 49A may be formed in any shape appropriately through design. - As shown in
FIG. 1 , thelug arm 49 is connected at the rear end thereof to one end of thering plate 45 through afirst pin 47A. With this configuration, thelug arm 49 is supported at the front end thereof so as to be swingable about a first pivot axis M1 which is the axial center of thefirst pin 47A with respect to the one end of thering plate 45, i.e., theswash plate 5. The first pivot axis M1 extends in the direction perpendicular to the axis of rotation O of thedrive shaft 3. - The
lug arm 49 is connected at the front end thereof to thefirst support member 43A through thesecond pin 47B. With this configuration, thelug arm 49 is supported at the rear end thereof so as to be swingable about a second pivot axis M2 which is the axial center of thesecond pin 47B with respect to thefirst support member 43A, i.e., thedrive shaft 3. The second pivot axis M2 extends parallel to the with the first pivot axis M1. Thelug arm 49, thefirst pin 47A and thesecond pin 47B correspond to thelink mechanism 7 of the present invention. - The
weight portion 49A extends rearward from the first pivot axis M1, and therefore, theweight portion 49A of thelug arm 49 is supported on thering plate 45 with thefirst pin 47A. Theweight portion 49A is passed through agroove portion 45B of thering plate 45 and positioned behind thering plate 45, that is, on therear surface 5B side of theswash plate 5. With this configuration, the centrifugal force generated by the rotation of theswash plate 5 about the axis of rotation O acts on theweight portion 49A on therear surface 5B side of theswash plate 5. - In the compressor, the
swash plate 5 is connected to thedrive shaft 3 via thelink mechanism 7 for rotation with thedrive shaft 3. The inclination angle of theswash plate 5 is variable with the swinging motion of the opposite ends of thelug arm 49 about the first pivot axis M1 and the second pivot axis M2, respectively. - Each
piston 9 has afirst piston head 9A at the front end thereof and asecond piston head 9B at the rear end thereof. Eachfirst piston head 9A is received in its associatedfirst cylinder bore 21A so as to be reciprocally movable. Eachfirst cylinder bore 21A has therein afirst compression chamber 21D which is formed between thefirst piston head 9A and the firstvalve forming plate 39. Eachsecond piston head 9B is received in its associated second cylinder bore 23A so as to be reciprocally movable. Each second cylinder bore 23A has therein asecond compression chamber 23D which is formed between thesecond piston head 9B and the secondvalve forming plate 41. Since the first cylinder bores 21A and the second cylinder bores 23A have the same diameter as mentioned above, thefirst piston head 9A and thesecond piston head 9B are formed to have the same diameter. - Each
piston 9 has at the longitudinal center thereof a recessedportion 9C and the pair ofhemispherical shoes portion 9C. Theshoes swash plate 5 into the reciprocating motion of thepistons 9 in the respective cylinder bores 21A, 23A. Theshoes swash plate 5. - With the change of the stroke length of the
respective pistons 9 according to the change of the inclination angle of theswash plate 5, the top dead center of the respective first piston heads 9A and the second piston heads 9B is shifted. Specifically, in the state ofFIG. 1 where the inclination angle of theswash plate 5 and the stroke length of thepistons 9 are the maximum, the top dead centers of the first piston heads 9A and thesecond piston head 9B are located at positions closest to the firstvalve forming plate 39 and the secondvalve forming plate 41, respectively. As will be appreciated from comparison ofFIGS. 1 and 4 , the top dead center of the second piston heads 9B becomes more distant from the secondvalve forming plate 41 with a decrease of the inclination angle of theswash plate 5 and hence of the stroke length of thepistons 9. Whereas, the top dead center of the first piston heads 9A is shifted very little when the stroke of thepistons 9 is the maximum and the position which is close to the firstvalve forming plate 39 is maintained. In other words, in the compressor of the present embodiment, as the inclination angle of theswash plate 5 decreases, the shifting of the top dead center of thesecond piston head 9B becomes greater than that of thefirst piston head 9A. - As shown in
FIG. 1 , theactuator 13 is disposed in theswash plate chamber 33. Theactuator 13 is located behind theswash plate 5 and movable into the second recessedportion 23C. Theactuator 13 includes amovable body 13A and afixed body 13B and apressure control chamber 13C is formed between themovable body 13A and the fixedbody 13B. - The
movable body 13A includes abody 130 and aperipheral wall 131. Thebody 130 forms the rear part of themovable body 13A and extends radially from thedrive shaft 3. Theperipheral wall 131 is connected to the outer circumferential edge of thebody 130 and extends in the axial direction of thedrive shaft 3. Furthermore, theperipheral wall 131 has at the front end thereof a connectingportion 132. Thebody 130, theperipheral wall 131 and the connectingportion 132 cooperate to form themovable body 13A of a shape of a closed-end cylinder. - The fixed
body 13B is formed of a circular plate having substantially the same diameter as the inner diameter of themovable body 13A. Asecond return spring 44B is provided between thefixed body 13B and thering plate 45. Specifically, thereturn spring 44B is fixed at the rear end thereof to the fixedbody 13B and fixed at the front end thereof to the other end of thering plate 45, or the end of thering plate 45 that is opposite from the end thereof to which thelug arm 49 is connected. - The
drive shaft body 30 extends through the center holes of themovable body 13A and the fixedbody 13B, so that themovable body 13A in the second recessedportion 23C is located opposite from thelink mechanism 7 with respect to theswash plate 5. The fixedbody 13B is disposed within themovable body 13A at a position rearward of theswash plate 5 and the periphery of the fixedbody 13B is covered by theperipheral wall 131 of themovable body 13A. With such configuration of theactuator 13, thepressure control chamber 13C is formed between themovable body 13A and the fixedbody 13B. Specifically, thepressure control chamber 13C is defined by thebody 130 and theperipheral wall 131 of themovable body 13A and the fixedbody 13B, thereby being separated from theswash plate chamber 33. - The
movable body 13A is mounted on thedrive shaft body 30 in such a way that themovable body 13A is rotatable with thedrive shaft 3 and also slidable in theswash plate chamber 33 in the axial direction O of thedrive shaft 3. Whereas, the fixedbody 13B is fixedly mounted on thedrive shaft body 30 with thedrive shaft body 30 inserted in the fixedbody 13B, so that the fixedbody 13B is rotatable with thedrive shaft 3, but immovable in the axial direction O. Therefore, themovable body 13A is movable relative to the fixedbody 13B in the axial direction O of thedrive shaft 3. - The connecting
portion 132 of themovable body 13A is connected to the other end of thering plate 45 through athird pin 47C, so that the other end of thering plate 45 is supported, that is, theswash plate 5 is supported by themovable body 13A so as to be swingable about a pivot axis M3 of thethird pin 47C. The pivot axis M3 extends parallel to the first and second pivot axes M1, M2. Themovable body 13A is thus connected to theswash plate 5. Themovable body 13A is in contact with theflange 431 of thesecond support member 43B when theswash plate 5 is placed at the maximum inclination angle position. - Furthermore, the
drive shaft body 30 has therein anaxial passage 3B extending in the axial direction O and opened in the rear end surface of thedrive shaft body 30 and aradial passage 3C extending from the front end of theaxial passage 3B and opened in the peripheral surface of thedrive shaft body 30. Because the rear end of thedrive shaft body 30 projects into thepressure regulation chamber 31, the rear end of theaxial passage 3B is also located and is opened to thepressure regulation chamber 31. Theradial passage 3C is opened to thecontrol chamber 13C. With this configuration, thepressure control chamber 13C communicates with thepressure regulation chamber 31 through theradial passage 3C and theaxial passage 3B. - The
drive shaft body 30 has at the front end thereof a threadedportion 3D. Thedrive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) at the threadedportion 3D. - As shown in
FIG. 2 , thecontrol mechanism 15 includes a low-pressure passage 15A, a high-pressure passage 15B, acontrol valve 15C, anorifice 15D and the aforementioned axial andradial passages axial passage 3B and theradial passage 3C correspond to the pressure-changing passages of the present invention. The low-pressure passage 15A, the high-pressure passage 15B, theaxial passage 3B and theradial passage 3C correspond to the control passages of the present invention. - The low-
pressure passage 15A is connected to thepressure regulation chamber 31 and thesecond suction chamber 27B. Thepressure control chamber 13C, thepressure regulation chamber 31 and thesecond suction chamber 27B communicate with each other through the low-pressure passage 15A, theaxial passage 3B and theradial passage 3C. The high-pressure passage 15B is connected to thepressure regulation chamber 31 and thesecond discharge chamber 29B. Thepressure control chamber 13C, thepressure regulation chamber 31 and thesecond discharge chamber 29B communicate with each other through the high-pressure passage 15B, theaxial passage 3B and theradial passage 3C. Theorifice 15D is formed in the high-pressure passage 15B for restricting the flow rate of the refrigerant gas flowing in the high-pressure passage 15B. - The
control valve 15C is formed in the low-pressure passage 15A and regulates the opening of the low-pressure passage 15A based on the pressure in thesecond suction chamber 27B. - The aforementioned evaporator is connected to the
inlet port 330 of the compressor through a tube and the condenser is connected to theoutlet port 230 through a tube. The condenser is connected to the evaporator through a tube and an expansion valve. The compressor, the evaporator, the expansion valve, the condenser and the like cooperate to form the refrigeration circuit of a vehicle air conditioning system. It is to be noted that the evaporator, the expansion valve, the condenser and the tubes are omitted from illustration in the drawings. - During the operation of the above-described compressor, the rotation of the
drive shaft 3 rotates theswash plate 5, causing thepistons 9 to reciprocate in the first and second cylinder bores 21A, 23A, so that compression of refrigerant gas is performed in the first andsecond compression chambers pistons 9. In the compressor, the suction phase in which refrigerant gas is drawn into the first and second cylinder bores 21A, 23A, the compression phase in which compressing the refrigerant gas is performed in the first and second cylinder bores 21A, 23A, and the discharge phase in which the compressed refrigerant gas is discharged from the first and second cylinder bores 21A, 23A are repeated. - In the suction phase, the refrigerant gas which is drawn from the evaporator into the
swash plate chamber 33 through theinlet port 330 is flowed into thefirst suction chamber 27A through the first connectingpassage 37A. The refrigerant gas in thefirst suction chamber 27A is then drawn into the first cylinder bore 21A through thefirst suction hole 390A due to the pressure difference which is created between the first cylinder bore 21A and thefirst suction chamber 27A and opens the firstsuction reed valves 391A. On the other hand, the refrigerant gas in theswash plate chamber 33 is also flowed into thesecond suction chamber 27B through the second connectingpassage 37B and then drawn into the second cylinder bore 23A through thesecond suction hole 410A due to the pressure difference which is created between the second cylinder bore 23A and thesecond suction chamber 27B and opens the secondsuction reed valves 411A. - In the discharge phase, the refrigerant gas compressed in the
first compression chamber 21D is discharged into thefirst discharge chamber 29A and flowed toward the combineddischarge chamber 231 through thefirst communication passage 18. Similarly, the refrigerant gas compressed in thesecond compression chamber 23D is discharged into thesecond discharge chamber 29B and flowed toward the combineddischarge chamber 231 through thesecond communication passage 20. The refrigerant gas in the combineddischarge chamber 231 is discharged out through theoutlet port 230 toward the condenser. - During the suction phase, the compression force of the
pistons 9 acts on theswash plate 5, thering plate 45, thelug arm 49, and thefirst pin 47A in such a way that reduces the inclination angle of theswash plate 5. A change in the inclination angle of theswash plate 5 increases or decreases the stroke length of thepistons 9 thereby to change the discharge displacement. - Specifically, when the opening of the low-
pressure passage 15A is increased by thecontrol valve 15C shown inFIG. 2 , the pressures in thepressure regulation chamber 31 and hence thepressure control chamber 13C become substantially the same as the pressure in thesecond suction chamber 27B. As a result, themovable body 13A of theactuator 13 moves frontward in theswash plate chamber 33 and, therefore, toward thelug arm 49, as shown inFIG. 4 , due to the compression force of thepistons 9 acting on theswash plate 5. - The end of the
ring plate 45 that is opposite from the end thereof to which thelug arm 49 is connected, that is, the other end of theswash plate 5 swings clockwise about the pivot axis M3 while overcoming against the urging force of thesecond return spring 44B. Furthermore, the rear end of thelug arm 49 swings clockwise about the first pivot axis M1, while the front end of thelug arm 49 swings counterclockwise about the second pivot axis M2. Accordingly, thelug arm 49 moves toward theflange 430 of thefirst support member 43A and theswash plate 5 swings about the first pivot axis M1 with the pivot axis M3 as the point of action and the first pivot axis M1 as the fulcrum point. The inclination angle of theswash plate 5 with respect to a plane extending perpendicular to the axis of rotation O of thedrive shaft 3 decreases and the stroke length of thepistons 9 decreases. Accordingly, the displacement of the compressor per one rotation of thedrive shaft 3 is decreased. It is to be noted that the inclination angle of theswash plate 5 shown inFIG. 4 corresponds to the minimum inclination angle. - In this case, the centrifugal force acting on the
weight portion 49A is imparted to theswash plate 5 in such a way that theswash plate 5 tends to shift easily in the direction that reduces the inclination angle of theswash plate 5. Themovable body 13A moves frontward in theswash plate chamber 33 to a position where the front end of themovable body 13A is located radially inner side of theweight portion 49A. In the compressor, when the inclination angle of theswash plate 5 is reduced to minimum, about front half of the front end of themovable body 13A is covered with theweight portion 49A. - As the inclination angle of the
swash plate 5 is decreased, thering plate 45 is brought into contact with the rear end of thefirst return spring 44A. Then thefirst return spring 44A is elastically deformed and the rear end of thefirst return spring 44A approaches thefirst support member 43A. - With a decrease of the inclination angle of the
swash plate 5 and hence of the stroke length of thepistons 9, the top dead center of the second piston heads 9B is shifted away from the secondvalve forming plate 41. Therefore, when the inclination angle of theswash plate 5 is approximately zero, compression for a small displacement is performed in thefirst compression chamber 21D, and no compression is performed in thesecond compression chamber 23D. - As the
control valve 15C shown inFIG. 2 reduces the opening of the low-pressure passage 15A, the pressure in thepressure control chamber 13C becomes substantially the same as the pressure in thesecond discharge chamber 29B. Accordingly, themovable body 13A moves rearward in theswash plate chamber 33 against the compression force of the pistons acting on theswash plate 5, so that themovable body 13A is moved away from thelug arm 49. - Consequently, the lower end of the
swash plate 5 is pulled at the pivot axis M3 by themovable body 13A rearward in theswash plate chamber 33 through the connectingportion 132, so that the other end of theswash plate 5 swings counterclockwise about the pivot axis M3. Furthermore, the rear end of thelug arm 49 swings counterclockwise about the first pivot axis M1, while the front end of thelug arm 49 swings clockwise about the second pivot axis M2. Accordingly, thelug arm 49 moves away from theflange 430 of thefirst support member 43A and theswash plate 5 swings about the first pivot axis M1 with the pivot axis M3 as the point of action and the pivot axis M1 as the fulcrum point in the direction that is opposite to the direction that decreases the inclination angle of theswash plate 5. Therefore, the inclination angle of theswash plate 5 increases and the stroke length of thepistons 9 is lengthened, with the result that the displacement of the compressor per one rotation of thedrive shaft 3 is increased. It is to be noted that the inclination angle of theswash plate 5 shown inFIG. 1 corresponds to the maximum inclination angle. - As described above, the refrigerant gas in the
second discharge chamber 29B is drawn into thepressure regulation chamber 31 through the high-pressure passage 15B of thecontrol mechanism 15. The refrigerant gas in thesecond discharge chamber 29B, which has been just compressed in thesecond compression chamber 23D, has a high temperature and a high pressure. - As shown in
FIG. 3 , thepressure regulation chamber 31 is disposed in therear housing 19 at a position radially inward of thesecond discharge chamber 29B and surrounded by thesecond discharge chamber 29B. In such structure of the compressor, the refrigerant in thepressure regulation chamber 31 is heated by high-temperature refrigerant gas in thesecond discharge chamber 29B and part of therear housing 19 in the vicinity of thesecond discharge chamber 29B and, therefore, the refrigerant gas in thepressure regulation chamber 31 will also be heated. In the compressor wherein thesecond suction chamber 27B is disposed radially outward of thesecond discharge chamber 29B in therear housing 19, the refrigerant gas in thepressure regulation chamber 31 tends to be less cooled by thesecond suction chamber 27B because the refrigerant gas in thepressure regulation chamber 31 is less susceptible to the influence of low-temperature refrigerant gas in thesecond suction chamber 27B. - Furthermore, during the operation of the compressor when the
drive shaft 3 is being rotated, the first and second cylinder blocks 21, 23, the first and second slidingbearings second support members drive shaft body 30 is also heated by the heat transmitted from thesecond support member 43B and the like. The first andsecond thrust bearings drive shaft 3. In the compressor wherein the second thrust bearing 35B is provided between the second recessedportion 23C of thesecond cylinder block 23 and theflange 431 of thesecond support member 43B, the heat generated in the second thrust bearing 35B is transmitted to thesecond cylinder block 23 and thesecond support member 43B. - In the compressor, the refrigerant gas in the
pressure regulation chamber 31 may be heated directly by the members projecting into thepressure regulation chamber 31, such as theprojection 23F of thesecond cylinder block 23, the second sliding bearing 22B, the rear end of thesecond support member 43B and the rear end of thedrive shaft body 30 that project into thepressure regulation chamber 31. - In the compressor according to the present embodiment, the temperature of the refrigerant gas which is drawn from the
second discharge chamber 29B into thepressure regulation chamber 31 is hard to drop. Therefore, in the compressor wherein thedrive shaft body 30 is heated as described above and the rear end of theaxial passage 3B is located in thepressure regulation chamber 31, the refrigerant gas flowed from thepressure regulation chamber 31 into thepressure control chamber 13C is hard to be cooled in theaxial passage 3B and theradial passage 3C. If liquefied refrigerant exists in thepressure regulation chamber 31 due to cooling, the pressure change in thepressure control chamber 13C is inhibited. In the compressor according to the present embodiment, the refrigerant in thepressure regulation chamber 31 is hardly to be liquefied, with the result that the pressure of the refrigerant gas flowed into thepressure control chamber 13C through thepressure regulation chamber 31 is varied quickly and themovable body 13A is moved smoothly in response to a change of the pressure in thepressure control chamber 13C and, therefore, the inclination angle of the swash plate is changed quickly according to a change of the operating condition of the compressor. - Thus, the compressor according to the embodiment exhibits good controllability.
- Furthermore, in the compressor, the drive shaft including the drive shaft body and the cap maintains the simple form of the drive shaft main body to thereby provide a simplified manufacturing process of the compressor, while heating the refrigerant with the cap.
- The present invention has been described according to the embodiment shown in the drawings. However, the present invention is not limited to the embodiment above, but it may appropriately be modified without departing from the gist of the invention.
- For example, as in the case of the
rear housing 19, thefirst discharge chamber 29A may be formed radially inward of thefront housing 17 and thefirst suction chamber 27A radially outward of thefirst discharge chamber 29A. - The configuration of the
control mechanism 15 may be such that thecontrol valve 15C is formed in the high-pressure passage 15B and theorifice 15D is formed in the low-pressure passage 15A. In this case, the opening of the high-pressure passage 15B is regulated by thecontrol valve 15C. In the compressor of such configuration, the pressure in thepressure control chamber 13C is raised quickly by the high pressure in thesecond discharge chamber 29B, so that an increase of the displacement of the compressor may be accomplished quickly. - The compressor may be configured such that the
actuator 13 is disposed on thefront surface 5A side and thelug arm 49 on therear surface 5B side of theswash plate 5. - The compressor may further be configured such that the compression chamber is formed in either the
first cylinder block 21 or thesecond cylinder block 23. - The present invention is applicable to an air conditioning apparatus or and the like.
Claims (6)
1. A swash plate type variable displacement compressor comprising:
a housing having therein a suction chamber, a discharge chamber, a swash plate chamber, and a plurality of cylinder bores;
a drive shaft rotatably supported in the housing;
a swash plate which is rotatable in the swash plate chamber with the rotation of the drive shaft;
a link mechanism which is disposed between the drive shaft and the swash plate and allows a change in an inclination angle of the swash plate with respect to the direction perpendicular to the axis of the drive shaft;
a plurality of pistons which is reciprocally received in the respective cylinder bores;
a conversion mechanism which converts the rotation of the drive shaft into reciprocal movement of the pistons in the respective cylinder bores in conjunction with the swash plate with a stroke length according to the inclination angle of the swash plate;
an actuator for changing the inclination angle of the swash plate; and
a control mechanism which controls the actuator, wherein
the housing has therein a pressure regulation chamber, the pressure regulation chamber is disposed radially inward of the discharge chamber, which is disposed radially inward of the suction chamber,
the actuator includes a fixed body, a movable body, and a pressure control chamber, wherein the fixed body is fixed on the drive shaft in the swash plate chamber, the movable body is connected to the swash plate and movable relative to the fixed body in the direction of the axis of rotation, and the pressure control chamber is defined by the fixed body and the movable body and the pressure in the pressure control chamber is changed by introducing the pressure in the discharge chamber into the pressure control chamber such that the movable body is moved,
the control mechanism has a control passage and a control valve, the control passage providing communication between the discharge chamber and the pressure control chamber via the pressure regulation chamber, the control valve adjusting an opening of the control passage to vary pressure in the pressure regulation chamber such that the movable body is moved,
at least a part of the control passage is formed in the drive shaft, and the drive shaft projects into the pressure regulation chamber such that the control passage connects the pressure regulation chamber and the pressure control chamber.
2. The compressor according to claim 1 , wherein
the housing has therein a cylinder block and a rear housing, the cylinder block having the cylinder bores, rotatably supporting the drive shaft, the rear housing being connected to the cylinder block through a valve unit and having at least the discharge chamber, wherein
the cylinder block projects into the pressure regulation chamber.
3. The compressor according to claim 2 , wherein
the drive shaft includes a drive shaft body and a cap which is fitted on the drive shaft body and disposed between the drive shaft body and the cylinder block, the drive shaft body and the cap projecting into the pressure regulation chamber.
4. The compressor according to claim 3 , wherein
a radial bearing is provided between the cylinder block and the cap and projects into the pressure regulation chamber.
5. The compressor according to claim 3 , wherein a thrust bearing is provided between the cylinder block and the cap.
6. The compressor according to claim 1 , wherein
the suction chamber and the swash plate chamber form a low-pressure chamber;
the control passage includes a high-pressure passage which provides communication between the discharge chamber and the pressure regulation chamber, a low-pressure passage which has the control valve and provides communication between the low-pressure chamber and the pressure regulation chamber, and a pressure-changing passage which is formed in the drive shaft and provides communication between the pressure regulation chamber and the pressure control chamber; and
a part of the pressure-changing passage projects into the pressure regulation chamber together with the drive shaft.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013198814A JP6015614B2 (en) | 2013-09-25 | 2013-09-25 | Variable capacity swash plate compressor |
JP2013-198814 | 2013-09-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150086391A1 true US20150086391A1 (en) | 2015-03-26 |
Family
ID=51627964
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/492,441 Abandoned US20150086391A1 (en) | 2013-09-25 | 2014-09-22 | Swash plate type variable displacement compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150086391A1 (en) |
EP (1) | EP2853740A1 (en) |
JP (1) | JP6015614B2 (en) |
KR (1) | KR101597266B1 (en) |
CN (1) | CN104454437B (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11073142B2 (en) | 2016-11-02 | 2021-07-27 | Hyundai Motor Company | Air-conditioner compressor for vehicle |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11015587B2 (en) * | 2018-03-30 | 2021-05-25 | Kabushiki Kaisha Toyota Jidoshokki | Piston compressor |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4037993A (en) * | 1976-04-23 | 1977-07-26 | Borg-Warner Corporation | Control system for variable displacement compressor |
US4061443A (en) * | 1976-12-02 | 1977-12-06 | General Motors Corporation | Variable stroke compressor |
JPS61145379A (en) * | 1984-12-17 | 1986-07-03 | Nippon Denso Co Ltd | Variable displacement compressor |
JPH037583Y2 (en) * | 1985-05-20 | 1991-02-25 | ||
JPH0518355A (en) * | 1991-07-15 | 1993-01-26 | Toyota Autom Loom Works Ltd | Variable capacity type compressor |
JPH05172052A (en) | 1991-12-18 | 1993-07-09 | Sanden Corp | Variable displacement swash plate type compressor |
JPH05312144A (en) * | 1992-05-08 | 1993-11-22 | Sanden Corp | Variable displacement swash plate type compressor |
JP2932952B2 (en) * | 1994-12-07 | 1999-08-09 | 株式会社豊田自動織機製作所 | Clutchless variable displacement compressor |
JPH1037863A (en) * | 1996-07-22 | 1998-02-13 | Toyota Autom Loom Works Ltd | Variable displacement compressor |
JP3585148B2 (en) * | 1996-12-16 | 2004-11-04 | 株式会社豊田自動織機 | Control valve for variable displacement compressor |
-
2013
- 2013-09-25 JP JP2013198814A patent/JP6015614B2/en not_active Expired - Fee Related
-
2014
- 2014-09-22 US US14/492,441 patent/US20150086391A1/en not_active Abandoned
- 2014-09-22 EP EP14185744.1A patent/EP2853740A1/en not_active Withdrawn
- 2014-09-23 KR KR1020140127150A patent/KR101597266B1/en not_active IP Right Cessation
- 2014-09-24 CN CN201410493895.7A patent/CN104454437B/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11073142B2 (en) | 2016-11-02 | 2021-07-27 | Hyundai Motor Company | Air-conditioner compressor for vehicle |
Also Published As
Publication number | Publication date |
---|---|
JP6015614B2 (en) | 2016-10-26 |
JP2015063966A (en) | 2015-04-09 |
EP2853740A1 (en) | 2015-04-01 |
KR101597266B1 (en) | 2016-02-24 |
CN104454437B (en) | 2016-10-26 |
CN104454437A (en) | 2015-03-25 |
KR20150034108A (en) | 2015-04-02 |
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Legal Events
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AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:YAMAMOTO, SHINYA;OTA, MASAKI;NAKAIMA, HIROYUKI;AND OTHERS;REEL/FRAME:033789/0988 Effective date: 20140910 |
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STCB | Information on status: application discontinuation |
Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION |