EP1744059A1 - Variable displacement compressor - Google Patents
Variable displacement compressor Download PDFInfo
- Publication number
- EP1744059A1 EP1744059A1 EP06117116A EP06117116A EP1744059A1 EP 1744059 A1 EP1744059 A1 EP 1744059A1 EP 06117116 A EP06117116 A EP 06117116A EP 06117116 A EP06117116 A EP 06117116A EP 1744059 A1 EP1744059 A1 EP 1744059A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- passage
- chamber
- supply passage
- suction chamber
- variable displacement
- 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.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—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
- F04B27/1009—Distribution members
- F04B27/1018—Cylindrical distribution members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
-
- 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
- F04B27/109—Lubrication
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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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Definitions
- the present invention relates to a variable displacement compressor whose displacement is variable by changing angle of inclination of a swash plate of the compressor.
- variable displacement compressor (hereinafter referred to merely as a compressor)
- refrigerant gas in a discharge chamber is supplied into a crank chamber through a supply passage while the refrigerant gas in the crank chamber is drawn out to a suction chamber through a bleed passage for controlling pressure in the crank chamber, whereby the angle of inclination of the swash plate is adjusted.
- a control valve is provided in the supply passage. As an opening degree of the control valve is adjusted, flow rate of the refrigerant gas supplied into the crank chamber is adjusted, so that the angle of inclination of the swash plate is adjusted thereby to adjust stroke of a piston and hence the displacement of the compressor.
- a shaft seal chamber is provided in an outer side of a drive shaft in a housing of the compressor.
- a shaft seal member is accommodated in the shaft seal chamber for preventing the refrigerant gas from leaking out of the compressor along the circumferential surface of the drive shaft. Since the shaft seal member is constantly in slide contact with the circumferential surface of the drive shaft, the shaft seal member generates heat during operation of the compressor. To prevent degradation caused by excessive generation of heat of the shaft seal member, the compressor has a structure for cooling the shaft seal member.
- Japanese Unexamined Patent Application Publication (KOKAI) No. 4-179874 discloses one example of the structure.
- the shaft seal chamber is provided in the supply passage, through which the refrigerant gas is supplied from the discharge chamber to the crank chamber.
- the refrigerant gas is decompressed by the control valve to lower its temperature, and then is supplied into the crank chamber through the shaft seal chamber. Therefore, the refrigerant gas is blown to the shaft seal member in the shaft seal chamber thereby to cool the shaft seal member. This prevents the degradation caused by excessive generation of heat of the shaft seal member.
- the present invention is directed to a variable displacement compressor for sufficiently cooling the shaft seal member.
- the present invention provides a variable displacement compressor for forming a refrigerant circuit with an external refrigerant circuit.
- the variable displacement compressor includes a housing, a drive shaft, a swash plate, a shaft seal member, a supply passage, a control valve and a gas passage.
- the housing has a suction chamber, a crank chamber, a discharge chamber and a shaft seal chamber formed therein.
- the drive shaft is rotataby supported by the housing.
- the swash plate is connected to the drive shaft so that angle of inclination of the swash plate relative to the drive shaft is variable.
- the swash plate is accommodated in the crank chamber.
- the shaft seal member is accommodated in the shaft seal chamber.
- the discharge chamber is in communication with the crank chamber through the supply passage.
- the supply passage includes the shaft seal chamber.
- the control valve is disposed in the supply passage. Flow rate of refrigerant gas supplied from the discharge chamber to the crank chamber through the supply passage is adjusted by adjusting an opening degree of the control valve.
- the discharge chamber is in communication with the external refrigerant circuit through the gas passage.
- the supply passage is formed differently from the gas passage. A part of the supply passage is located adjacent to the suction chamber and nearer to the suction chamber than the discharge chamber.
- variable displacement compressor hereinafter referred to merely as a compressor
- FIGs. 1 and 2 The following will describe a variable displacement compressor (hereinafter referred to merely as a compressor) according to a first preferred embodiment of the present invention with reference to FIGs. 1 and 2.
- FIG. 1 shows a longitudinal sectional view of a compressor 10 of the first embodiment.
- the left side and the right side of the drawing correspond to the front side and the right side of the compressor 10, respectively.
- the compressor 10 includes a cylinder block 11, a front housing 12 which is fixedly joined to the front end of the cylinder block 11, and a rear housing 14 which is fixedly joined to the rear end of the cylinder block 11 through a valve plate assembly 13.
- the cylinder block 11, the front housing 12 and the rear housing 14 form a housing of the compressor 10.
- the cylinder block 11 and the front housing 12 define a crank chamber therebetween.
- a drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15.
- the drive shaft 16 includes a cylindrical hollow first shaft portion 16a having an opening at the rear end thereof (at the right end of FIG. 1) and a cylindrical hollow second shaft portion 16b having openings at the opposite ends thereof (at the right and left ends of FIG. 1) and press-fitted (or inserted) into the first shaft portion 16a to form double pipe structure.
- An O-ring 17 is held between the inner circumferential surface of the first shaft portion 16a and the outer circumferential surface of the second shaft portion 16b at the front side of the second shaft portion 16b (at the left side of FIG. 1).
- the drive shaft 16 is rotatably supported at the opposite sides thereof (at the right and left sides of FIG. 1) by radial bearings 18 and 19, respectively
- a shaft seal chamber 20 is formed forward of the radial bearing 18.
- a lip seal 21 that serves as a shaft seal member is provided between the circumferential surface of the front side of the drive shaft 16 (or the first shaft portion 16a) and the shaft seal chamber 20. The lip seal 21 is constantly in slide contact with the drive shaft 16 thereby to prevent refrigerant gas from leaking from the crank chamber 15 to the outside of the compressor 10 along the circumferential surface of the drive shaft 16.
- an accommodation space S is defined rearward of the radial bearing 19.
- the rear side of the drive shaft 16 is accommodated in the accommodation space S.
- a lug plate 22 is secured to the drive shaft 16 for rotation therewith.
- a thrust bearing 23 is provided between the lug plate 22 and the inner wall surface of the front housing 12.
- a swash plate 24 is accommodated.
- An insertion hole 24a is bored in the middle of the swash plate 24, in which the drive shaft 16 is inserted.
- a hinge mechanism 25 is interposed between the lug plate 22 and the swash plate 24.
- the swash plate 24 is connected to the lug plate 22 through the hinge mechanism 25 and supported by the drive shaft 16 through the insertion hole 24a. This permits the swash plate 24 to rotate synchronously with the lug plate 22 and the drive shaft 16 and incline with respect to the drive shaft 16 while sliding in the direction of an axis T of the drive shaft 16.
- the cylinder block 11 has a plurality of cylinder bores 26 (only one of them being shown in FIG. 1) around the drive shaft 16 at equiangular intervals, extending in the direction of the axis T.
- Each cylinder bore 26 receives therein a single-headed piston 27 for reciprocation.
- the front and rear openings of the cylinder bore 26 are closed by the piston 27 and the valve plate assembly 13, respectively.
- a compression chamber (not shown) is defined in the cylinder bore 26, a compression chamber (not shown) is defined.
- the volume of the compression chamber varies in accordance with the reciprocation of the piston 27.
- the piston 27 engages with the outer peripheral portion of the swash plate 24 through a pair of shoes 29.
- the suction chamber 30 and the discharge chamber 31 are defined so as to face the valve plate assembly 13. More specifically, the discharge chamber 31 is provided in the middle of the rear housing 14 and a partition wall 14a is formed radially outward of the discharge chamber 31. In the rear housing 14, the suction chamber 30 is provided radially outward of the discharge chamber 31 through the partition wall 14a in an annular shape so as to surround the discharge chamber 31. In addition, in the rear housing 14, a peripheral wall 14c is formed radially outward of the outer peripheral portion of the suction chamber 30 for forming a part of the rear housing 14. A suction port 32 and a suction valve (not shown) are provided in the valve plate assembly 13 so as to be located between the corresponding compression chamber and the suction chamber 30. In a similar manner, a discharge port 34, a discharge valve (not shown) and a retainer 35 are provided in the valve plate assembly 13 so as to be located between the corresponding compression chamber and the discharge chamber 31.
- an accommodation chamber 50 is defined and is in communication with the discharge chamber 31 through a discharge passage 51.
- the discharge chamber 31 is connected to an external refrigerant circuit 40 through the discharge passage 51 and the accommodation chamber 50, so that high-pressure refrigerant gas discharged to the discharge chamber 31 is led to the external refrigerant circuit 40 through the discharge passage 51 and the accommodation chamber 50.
- the discharge passage 51 and the accommodation chamber 50 form a gas passage for leading the refrigerant gas discharged to the discharge chamber 31 to the external refrigerant circuit 40.
- the refrigerant gas which is led to the external refrigerant circuit 40 through the gas passage is cooled by a condenser 40a which forms the external refrigerant circuit 40. Subsequently, the refrigerant gas is expanded by an expansion valve 40b and then transferred to an evaporator 40c to be evaporated therein. The refrigerant gas returned from the evaporator 40c (which forms the external refrigerant circuit 40) is drawn into the suction chamber 30.
- the compressor 10 of the present embodiment forms a refrigerant circuit with the external refrigerant circuit 40.
- an oil separator 52 is disposed for separating lubricating oil contained in the refrigerant gas discharged to the discharge chamber 31 from the refrigerant gas.
- the oil separator 52 includes an oil separation portion 52a for separating the lubricating oil from the refrigerant gas by centrifugal separation and an oil reservoir 52b in which the oil separated by the oil separation portion 52a is temporarily reserved.
- the oil separation portion 52a has a cylindrical shape, the lower end of which is opened to the oil reservoir 52b.
- the discharge passage 51 is opened to the accommodation chamber 50 at a position facing the oil separation portion 52a.
- the refrigerant gas led from the discharge chamber 31 to the accommodation chamber 50 through the discharge passage 51 is circled around the oil separation portion 52a in the circumferential direction thereof.
- the lubricating oil is separated from the refrigerant gas by centrifugal separation and the separated lubricating oil is temporarily reserved in the oil reservoir 52b.
- a part of the refrigerant gas whose lubricating oil is separated passes through the inside of the oil separation portion 52a and then is supplied to the condenser 40a of the external refrigerant circuit 40.
- an electromagnetic type displacement control valve 60 that serves as a control valve is disposed on the downstream side of the accommodation chamber 50.
- a communication passage 59 is formed in the rear housing 14.
- the oil reservoir 52b and the control valve 60 are in communication with each other through the communication passage 59.
- a first passage 61 is formed in the rear housing 14.
- the control valve 60 and a second passage 62 formed in the valve plate assembly 13 are in communication with each other through the first passage 61.
- a part of the first passage 61 is formed so as to pass through the peripheral wall 14c of the rear housing 14 in the direction of the axis T.
- the part of the first passage 61 is located radially outward of the partition wall 14a which separates the suction chamber 30 and the discharge chamber 31, and is located radially outward of the suction chamber 30 so as to be located adjacent to the suction chamber 30.
- the part of the first passage 61 is located adjacent to the suction chamber 30 so that the refrigerant gas in the part of the first passage 61 is cooled by the refrigerant gas in the suction chamber 30.
- the second passage 62 is in communication with a third passage 63 formed in the cylinder block 11, and the third passage 63 is in communication with the accommodation space S.
- a fourth passage 64 is formed in the second shaft portion 16b so as to pass through the second shaft portion 16b in the direction of the axis T.
- the fourth passage 64 is in communication with the accommodation space S.
- a fifth passage 65 is formed so as to extend on the front side of the first shaft portion 16a in the direction of the axis T and extend in the radial direction of the axis T.
- the fifth passage 65 is in communication with the fourth passage 64 and is in communication with the shaft seal chamber 20 in the front housing 12.
- the shaft seal chamber 20 is in communication with the crank chamber 15 through a sixth passage 66 formed in the front housing 12.
- the discharge passage 51, the accommodation chamber 50 (or the oil reservoir 52b), the communication passage 59, the control valve 60, the first passage 61, the second passage 62, the third passage 63, the accommodation space S, the fourth passage 64, the fifth passage 65, the shaft seal chamber 20 and the sixth passage 66 form a supply passage for supplying the refrigerant gas in the discharge chamber 31 to the crank chamber 15.
- the supply passage is formed differently from the gas passage.
- a controller (not shown) is connected to the control valve 60 for performing control of current supply (duty cycle control).
- the control valve 60 is provided on the upstream side of the first passage 61 located adjacent to the suction chamber 30. That is, in the supply passage, the first passage 61 which forms the part of the supply passage is located downstream from the control valve 60.
- a bleed port 16c is formed in the first shaft portion 16a at a position between the swash plate 24 and the lug plate 22.
- the bleed port 16c is in communication with a seventh passage 67 formed between the inner circumferential surface of the first shaft portion 16a and the outer circumferential surface of the second shaft portion 16b.
- the seventh passage 67 is in communication with the accommodation space S.
- the accommodation space S is in communication with an eighth passage 68 formed in the cylinder block 11, and the eighth passage 68 is in communication with a ninth passage 69 formed in the valve plate assembly 13.
- the ninth passage 69 is in communication with the suction chamber 30.
- the bleed port 16c, the seventh passage 67, the accommodation space S, the eighth passage 68 and the ninth passage 69 form a bleed passage for drawing the refrigerant gas from the crank chamber 15 to the suction chamber 30.
- a lip seal L is interposed between the inner wall surface of the accommodation space S and the outer circumferential surface of the rear end of the second shaft portion 16b of the drive shat 16 in such a way that a part of the supply passage and a part of the bleed passage which are defined in the accommodation space S are shut off from each other.
- the swash plate 24 is rotated and the pistons 27 are reciprocally moved in the respective cylinder bores 26, accordingly.
- the refrigerant gas circulating through the external refrigerant circuit 40 is drawn from the suction chamber 30 into the cylinder bores 26 through the corresponding suction valves and suction ports 32, thereby to be compressed in the compression chambers (not shown), respectively.
- the compressed refrigerant gas is discharged to the discharge chamber 31 through the corresponding discharge ports 34 and discharge valves.
- the refrigerant gas discharged to the discharge chamber 31 is led to the oil separator 52 in the accommodation chamber 50 through the discharge passage 51, and the oil separation portion 52a of the oil separator 52 separates the oil from the refrigerant gas.
- a part of the refrigerant gas whose lubricating oil is separated passes through the inside of the oil separation portion 52a and then is supplied to the condenser 40a of the external refrigerant circuit 40. That is, the part of the refrigerant gas is led to the external refrigerant circuit 40 through the gas passage including the accommodation chamber 50 and the discharge passage 51. Meanwhile, the other part of the refrigerant gas whose lubricating oil is separated in the oil separator 52 passes through the oil reservoir 52b and then is led to the control valve 60 through the communication passage 59 with the lubricating oil in the oil reservoir 52b.
- the refrigerant gas discharged to the discharge chamber 31 is divided into the gas passage for the external refrigerant circuit 40 and the communication passage 59 for the control valve 60 through the discharge passage 51. Therefore, the refrigerant gas is separately led to the external refrigerant circuit 40 and the control valve 60.
- flow rate of the refrigerant gas supplied to the crank chamber 15 through the supply passage is adjusted by adjusting the opening degree of the control valve 60.
- the refrigerant gas passes through the control valve 60, the refrigerant gas is throttled by a valve portion (not shown) of the control valve 60 thereby to be decompressed.
- the temperature of the refrigerant gas is reduced.
- the refrigerant gas whose temperature is reduced passes through the first passage 61.
- the part of the first passage 61 is disposed in the peripheral wall 14c so as to be located adjacent to the suction chamber 30, Meanwhile, the refrigerant gas which circulates through the external refrigerant circuit 40 thereby to be lowered in temperature is drawn into the suction chamber 30.
- the refrigerant gas in the suction chamber 30 is lower in temperature than the refrigerant gas passing through the supply passage (the first passage 61). Therefore, the refrigerant gas passing through the first passage 61 of the supply passage is cooled by the refrigerant gas in the suction chamber 30.
- the refrigerant gas which is discharged to the discharge chamber 31 and then passes through the control valve 60 and a part of the supply passage is cooled by two cooling means, in other words, the control valve 60 and the suction chamber 30.
- the refrigerant gas which is discharged to the discharge chamber 31 and then passes through the control valve 60 and a part of the supply passage is lower in temperature than the refrigerant gas in the discharge chamber 31.
- the seventh passage 67 is formed radially outward of the fourth passage 64 so as to surround the fourth passage 64 which forms a part of the supply passage. Therefore, the refrigerant gas which passes through the seventh passage 67 performs insulation effect for shutting off transfer of heat from the outside of the outer circumferential surface of the drive shaft 16 to the fourth passage 64, thereby to maintain the refrigerant gas in the fourth passage 64 (the supply passage) at low temperature.
- the refrigerant gas which passes through the first passage 61 to be lowered in temperature is drawn into the shaft seal chamber 20 through the second passage 62, the third passage 63, the accommodation space S, the fourth passage 64 and the fifth passage 65, and then is blown to the lip seal 21 in the shaft seal chamber 20.
- the lip seal 21 which generates heat due to constant sliding contact with the drive shaft 16 is thus cooled by the refrigerant gas.
- the refrigerant gas drawn into the shaft seal chamber 20 is supplied from the sixth passage 66 to the crank chamber 15.
- the refrigerant gas in the crank chamber 15 is drawn to the bleed passage, and furthermore drawn to the suction chamber 30.
- the balance between the flow rate of the refrigerant gas supplied into the crank chamber 15 through the supply passage and the flow rate of the refrigerant gas drawn from the crank chamber 15 through the bleed passage is controlled to determine (or adjust) the pressure in the crank chamber 15.
- the pressure in the crank chamber 15 is changed, the pressure difference between the crank chamber 15 and the cylinder bores 26 through the respective pistons 27 is changed thereby to change angle of inclination of the swash plate 24. Consequently, stroke of each piston 27 (displacement of the compressor 10) is adjusted.
- the first embodiment has the following advantageous effects.
- variable displacement compressor hereinafter referred to merely as a compressor
- the third embodiment differs from the first embodiment in that the positions of the discharge chamber and the suction chamber of the first embodiment are reversed and that the positions of the supply passage and the bleed passage of the first embodiment are changed.
- the overlapped description for repeating the same part is omitted.
- the suction chamber 30 is formed in the middle of the rear housing 14. Meanwhile, in the rear housing 14, the partition wall 14a is formed radially outward of the suction chamber 30. In addition, in the rear housing 14, the discharge chamber 31 is provided radially outward of the suction chamber 30 through the partition wall 14a in a annular shape so as to surround the suction chamber 30. Furthermore, in the rear housing 14, an outlet 31 a is formed so as to be in communication with the discharge chamber 31. The discharge chamber 31 is connected to the external refrigerant circuit 40 through the outlet 31a. The high-pressure refrigerant gas discharged to the discharge chamber 31 is led to the external refrigerant circuit 40 through the outlet 31a. Therefore, the outlet 31a forms the gas passage.
- control valve 60 is disposed in the rear housing 14.
- discharge passage 80 is formed so as to communicate the discharge chamber 31 and the control valve 60.
- a first passage 81 is formed so as to communicate the control valve 60 and a second passage 82 formed in the valve plate assembly 13.
- a part of the first passage 81 is formed in the rear housing 14 so as to pass through the partition wall 14a.
- the part of the first passage 81 is located in the inner wall surface of the partition wall 14a which separates the discharge chamber 31 and the suction chamber 30.
- the part of the first passage 81 is located adjacent to the suction chamber 30, that is, the part of the first passage 81 is nearer to the suction chamber than the discharge chamber 31. Therefore, the part of the first passage 81 is arranged in such a position that the refrigerant gas which passes through the first passage 81 is cooled by the refrigerant gas in the suction chamber 30.
- the second passage 82 is in communication with a third passage 83 formed in the cylinder block 11, and the third passage 83 is in communication with a fourth passage 84 formed in the front housing 12.
- the fourth passage 84 is in communication with the shaft seal chamber 20, which is in communication with the crank chamber 15 through a fifth passage 85 formed in the front housing 12. Therefore, the discharge passage 80, the control valve 60, the first passage 81, the second passage 82, the third passage 83, the fourth passage 84, the shaft seal chamber 20 and the fifth passage 85 form the supply passage for supplying the refrigerant gas in the discharge chamber 31 to the crank chamber 15.
- a bleed passage 87 through which the crank chamber 15 and the suction chamber 30 are in communication with each other is formed though the cylinder block 11 and the valve plate assembly 13, thereby to allow the refrigerant gas in the crank chamber 15 to be drawn to the suction chamber 30.
- the third embodiment has the effects similar to the effects (1) and (3) through (6) of the first embodiment.
- modifications of the above embodiments are as follows.
- the first passage 61 which forms a part of the supply passage may be located so as to traverse the suction chamber 30 radially outward of the partition wall 14a and a part of the first passage 61 may be located inside the suction chamber 30.
- the first passage 71 which forms a part of the supply passage may be located so as to traverse the suction chamber 30 radially outward of the partition wall 14a and a part of the first passage 71 may be located inside the suction chamber 30.
- the refrigerant gas in the suction chamber 30 is in contact with entire circumference of each of the first passages 61, 71. Therefore, the entire circumference of each of the first passages 61, 71 is cooled by the refrigerant gas in the suction chamber 30.
- a part of the first passage 61 which forms a part of the supply passage may be located in the inner wall surface of the peripheral wall 14c which is located radially outward of the partition wall 14a.
- a part of the first passage 61 which forms a part of the supply passage may be located in the outer wall surface of the partition wall 14a.
- a part of the first passage 71 which forms a part of the supply passage may be located in the inner wall surface of the peripheral wall 14c which is located radially outward of the partition wall 14a.
- a part of the first passage 71 which forms a part of the supply passage may be located in the outer wall surface of the partition wall 14a.
- contact areas between the outer peripheral surface of the first passage 71 and the refrigerant gas in the suction chamber 30 are increased compared to the case where a part of the first passage 71 is formed so as to pass through the peripheral wall 14c or the partition wall 14a without changing the shape of the peripheral wall 14c or the partition wall 14a. Therefore, the refrigerant gas which passes through the first passage 71 is efficiently cooled by the refrigerant gas in the suction chamber 30.
- the first passage 81 which forms a part of the supply passage may be located so as to traverse the suction chamber 30 radially inward of the partition wall 14a and a part of the first passage 81 may be located inside the suction chamber 30.
- the refrigerant gas in the suction chamber 30 is in contact with entire peripheral wall of the first passage 81. Therefore, the entire peripheral wall of the first passage 81 is cooled by the refrigerant gas in the suction chamber 30.
- control valve 60 may be disposed downstream from the suction chamber 30 in the supply passage.
- the drive shaft 16 may dispense with the bleed port 16c and the seventh passage 67. That is, the drive shaft 16 may be formed to have a part of the supply passage and not to have a part of the bleed passage. In this case, the bleed passage is formed in the cylinder block 11.
- the oil separator 52 is not necessarily needed.
- the refrigerant gas discharged to the discharge chamber 31 may be directly led to the external refrigerant circuit 40 and the control valve 60.
- the first passage 81 which forms a part of the supply passage may be formed so as to traverse the suction chamber 30.
- the supply passage may be formed in the drive shaft 16 such that the crank chamber 15 and the discharge chamber 31 are in communication with each other.
- a variable displacement compressor for forming a refrigerant circuit with an external refrigerant circuit includes a housing, a drive shaft, a swash plate, a shaft seal member, a supply passage, a control valve and a gas passage.
- the housing has a suction chamber, a crank chamber, a discharge chamber and a shaft seal chamber formed therein.
- the discharge chamber is in communication with the crank chamber through the supply passage.
- the supply passage has the shaft seal chamber.
- the discharge chamber is in communication with the external refrigerant circuit through the gas passage.
- the supply passage is formed differently from the gas passage. A part of the supply passage is located adjacent to the suction chamber and nearer to the suction chamber than the discharge chamber.
Abstract
Description
- The present invention relates to a variable displacement compressor whose displacement is variable by changing angle of inclination of a swash plate of the compressor.
- In this type of variable displacement compressor (hereinafter referred to merely as a compressor), refrigerant gas in a discharge chamber is supplied into a crank chamber through a supply passage while the refrigerant gas in the crank chamber is drawn out to a suction chamber through a bleed passage for controlling pressure in the crank chamber, whereby the angle of inclination of the swash plate is adjusted. A control valve is provided in the supply passage. As an opening degree of the control valve is adjusted, flow rate of the refrigerant gas supplied into the crank chamber is adjusted, so that the angle of inclination of the swash plate is adjusted thereby to adjust stroke of a piston and hence the displacement of the compressor.
- A shaft seal chamber is provided in an outer side of a drive shaft in a housing of the compressor. A shaft seal member is accommodated in the shaft seal chamber for preventing the refrigerant gas from leaking out of the compressor along the circumferential surface of the drive shaft. Since the shaft seal member is constantly in slide contact with the circumferential surface of the drive shaft, the shaft seal member generates heat during operation of the compressor. To prevent degradation caused by excessive generation of heat of the shaft seal member, the compressor has a structure for cooling the shaft seal member.
- Japanese Unexamined Patent Application Publication (KOKAI)
No. 4-179874 - In the above-referenced compressor, however, since the refrigerant gas discharged into the discharge chamber is high temperature, even if the refrigerant gas is decompressed by the control valve to lower its temperature, the refrigerant gas blown to the shaft seal member in the shaft seal chamber is still high temperature. Therefore, cooling effect of the shaft seal member caused by the refrigerant gas is not sufficiently performed.
- The present invention is directed to a variable displacement compressor for sufficiently cooling the shaft seal member.
- The present invention provides a variable displacement compressor for forming a refrigerant circuit with an external refrigerant circuit. The variable displacement compressor includes a housing, a drive shaft, a swash plate, a shaft seal member, a supply passage, a control valve and a gas passage. The housing has a suction chamber, a crank chamber, a discharge chamber and a shaft seal chamber formed therein. The drive shaft is rotataby supported by the housing. The swash plate is connected to the drive shaft so that angle of inclination of the swash plate relative to the drive shaft is variable. The swash plate is accommodated in the crank chamber. The shaft seal member is accommodated in the shaft seal chamber. The discharge chamber is in communication with the crank chamber through the supply passage. The supply passage includes the shaft seal chamber. The control valve is disposed in the supply passage. Flow rate of refrigerant gas supplied from the discharge chamber to the crank chamber through the supply passage is adjusted by adjusting an opening degree of the control valve. The discharge chamber is in communication with the external refrigerant circuit through the gas passage. The supply passage is formed differently from the gas passage. A part of the supply passage is located adjacent to the suction chamber and nearer to the suction chamber than the discharge 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 presently preferred embodiments together with the accompanying drawings in which:
- FIG. 1 is a longitudinal sectional view showing a variable displacement compressor according to a first embodiment of the present invention;
- FIG. 2 is a cross sectional view taken in the direction of the arrows substantially along the line 2-2 of FIG. 1;
- FIG. 3 is a longitudinal sectional view showing a variable displacement compressor according to a second embodiment of the present invention;
- FIG. 4 is a longitudinal sectional view showing a variable displacement compressor according to a third embodiment of the present invention;
- FIG. 5 is a cross sectional view taken in the direction of the arrows substantially along the line 5-5 of FIG. 4;
- FIG. 6 is a cross sectional view of a variable displacement compressor showing another example of a position at which a part of a supply passage is arranged;
- FIG. 7 is a cross sectional view of a variable displacement compressor showing another example of a position at which a part of a supply passage is arranged;
- FIG. 8 is a cross sectional view of a variable displacement compressor showing another example of a position at which a part of a supply passage is arranged; and
- FIG. 9 is a cross sectional view of a variable displacement compressor showing another example of a position at which a part of a supply passage is arranged.
- The following will describe a variable displacement compressor (hereinafter referred to merely as a compressor) according to a first preferred embodiment of the present invention with reference to FIGs. 1 and 2.
- FIG. 1 shows a longitudinal sectional view of a
compressor 10 of the first embodiment. In FIG. 1, the left side and the right side of the drawing correspond to the front side and the right side of thecompressor 10, respectively. As shown in FIG 1, thecompressor 10 includes acylinder block 11, afront housing 12 which is fixedly joined to the front end of thecylinder block 11, and arear housing 14 which is fixedly joined to the rear end of thecylinder block 11 through avalve plate assembly 13. Thecylinder block 11, thefront housing 12 and therear housing 14 form a housing of thecompressor 10. - The
cylinder block 11 and thefront housing 12 define a crank chamber therebetween. Adrive shaft 16 is rotatably supported by thecylinder block 11 and thefront housing 12 so as to pass through thecrank chamber 15. Thedrive shaft 16 includes a cylindrical hollowfirst shaft portion 16a having an opening at the rear end thereof (at the right end of FIG. 1) and a cylindrical hollowsecond shaft portion 16b having openings at the opposite ends thereof (at the right and left ends of FIG. 1) and press-fitted (or inserted) into thefirst shaft portion 16a to form double pipe structure. An O-ring 17 is held between the inner circumferential surface of thefirst shaft portion 16a and the outer circumferential surface of thesecond shaft portion 16b at the front side of thesecond shaft portion 16b (at the left side of FIG. 1). - The
drive shaft 16 is rotatably supported at the opposite sides thereof (at the right and left sides of FIG. 1) byradial bearings front housing 12, ashaft seal chamber 20 is formed forward of the radial bearing 18. Alip seal 21 that serves as a shaft seal member is provided between the circumferential surface of the front side of the drive shaft 16 (or thefirst shaft portion 16a) and theshaft seal chamber 20. Thelip seal 21 is constantly in slide contact with thedrive shaft 16 thereby to prevent refrigerant gas from leaking from thecrank chamber 15 to the outside of thecompressor 10 along the circumferential surface of thedrive shaft 16. - In the
cylinder block 11, an accommodation space S is defined rearward of the radial bearing 19. The rear side of thedrive shaft 16 is accommodated in the accommodation space S. - In the
crank chamber 15, alug plate 22 is secured to thedrive shaft 16 for rotation therewith. A thrust bearing 23 is provided between thelug plate 22 and the inner wall surface of thefront housing 12. In thecrank chamber 15, aswash plate 24 is accommodated. An insertion hole 24a is bored in the middle of theswash plate 24, in which thedrive shaft 16 is inserted. Ahinge mechanism 25 is interposed between thelug plate 22 and theswash plate 24. Theswash plate 24 is connected to thelug plate 22 through thehinge mechanism 25 and supported by thedrive shaft 16 through the insertion hole 24a. This permits theswash plate 24 to rotate synchronously with thelug plate 22 and thedrive shaft 16 and incline with respect to thedrive shaft 16 while sliding in the direction of an axis T of thedrive shaft 16. - The
cylinder block 11 has a plurality of cylinder bores 26 (only one of them being shown in FIG. 1) around thedrive shaft 16 at equiangular intervals, extending in the direction of the axis T. Each cylinder bore 26 receives therein a single-headedpiston 27 for reciprocation. The front and rear openings of the cylinder bore 26 are closed by thepiston 27 and thevalve plate assembly 13, respectively. In the cylinder bore 26, a compression chamber (not shown) is defined. The volume of the compression chamber varies in accordance with the reciprocation of thepiston 27. Thepiston 27 engages with the outer peripheral portion of theswash plate 24 through a pair ofshoes 29. - In the
rear housing 14, thesuction chamber 30 and thedischarge chamber 31 are defined so as to face thevalve plate assembly 13. More specifically, thedischarge chamber 31 is provided in the middle of therear housing 14 and apartition wall 14a is formed radially outward of thedischarge chamber 31. In therear housing 14, thesuction chamber 30 is provided radially outward of thedischarge chamber 31 through thepartition wall 14a in an annular shape so as to surround thedischarge chamber 31. In addition, in therear housing 14, aperipheral wall 14c is formed radially outward of the outer peripheral portion of thesuction chamber 30 for forming a part of therear housing 14. Asuction port 32 and a suction valve (not shown) are provided in thevalve plate assembly 13 so as to be located between the corresponding compression chamber and thesuction chamber 30. In a similar manner, adischarge port 34, a discharge valve (not shown) and aretainer 35 are provided in thevalve plate assembly 13 so as to be located between the corresponding compression chamber and thedischarge chamber 31. - In the
rear housing 14, anaccommodation chamber 50 is defined and is in communication with thedischarge chamber 31 through adischarge passage 51. Thedischarge chamber 31 is connected to an externalrefrigerant circuit 40 through thedischarge passage 51 and theaccommodation chamber 50, so that high-pressure refrigerant gas discharged to thedischarge chamber 31 is led to the externalrefrigerant circuit 40 through thedischarge passage 51 and theaccommodation chamber 50. Thus, thedischarge passage 51 and theaccommodation chamber 50 form a gas passage for leading the refrigerant gas discharged to thedischarge chamber 31 to the externalrefrigerant circuit 40. - The refrigerant gas which is led to the external
refrigerant circuit 40 through the gas passage is cooled by acondenser 40a which forms the externalrefrigerant circuit 40. Subsequently, the refrigerant gas is expanded by anexpansion valve 40b and then transferred to an evaporator 40c to be evaporated therein. The refrigerant gas returned from the evaporator 40c (which forms the external refrigerant circuit 40) is drawn into thesuction chamber 30. Thecompressor 10 of the present embodiment forms a refrigerant circuit with the externalrefrigerant circuit 40. - In the
accommodation chamber 50 of the gas passage, anoil separator 52 is disposed for separating lubricating oil contained in the refrigerant gas discharged to thedischarge chamber 31 from the refrigerant gas. Theoil separator 52 includes anoil separation portion 52a for separating the lubricating oil from the refrigerant gas by centrifugal separation and anoil reservoir 52b in which the oil separated by theoil separation portion 52a is temporarily reserved. - In the
oil separator 52, theoil separation portion 52a has a cylindrical shape, the lower end of which is opened to theoil reservoir 52b. Thedischarge passage 51 is opened to theaccommodation chamber 50 at a position facing theoil separation portion 52a. The refrigerant gas led from thedischarge chamber 31 to theaccommodation chamber 50 through thedischarge passage 51 is circled around theoil separation portion 52a in the circumferential direction thereof. At this time, the lubricating oil is separated from the refrigerant gas by centrifugal separation and the separated lubricating oil is temporarily reserved in theoil reservoir 52b. A part of the refrigerant gas whose lubricating oil is separated passes through the inside of theoil separation portion 52a and then is supplied to thecondenser 40a of the externalrefrigerant circuit 40. - In the
rear housing 14, an electromagnetic typedisplacement control valve 60 that serves as a control valve is disposed on the downstream side of theaccommodation chamber 50. In addition, acommunication passage 59 is formed in therear housing 14. Theoil reservoir 52b and thecontrol valve 60 are in communication with each other through thecommunication passage 59. Furthermore, afirst passage 61 is formed in therear housing 14. Thecontrol valve 60 and asecond passage 62 formed in thevalve plate assembly 13 are in communication with each other through thefirst passage 61. As shown in FIG. 2, a part of thefirst passage 61 is formed so as to pass through theperipheral wall 14c of therear housing 14 in the direction of the axis T. That is, the part of thefirst passage 61 is located radially outward of thepartition wall 14a which separates thesuction chamber 30 and thedischarge chamber 31, and is located radially outward of thesuction chamber 30 so as to be located adjacent to thesuction chamber 30. In other words, the part of thefirst passage 61 is located adjacent to thesuction chamber 30 so that the refrigerant gas in the part of thefirst passage 61 is cooled by the refrigerant gas in thesuction chamber 30. - As shown in FIG. 1, the
second passage 62 is in communication with athird passage 63 formed in thecylinder block 11, and thethird passage 63 is in communication with the accommodation space S. In thedrive shaft 16, afourth passage 64 is formed in thesecond shaft portion 16b so as to pass through thesecond shaft portion 16b in the direction of the axis T. Thefourth passage 64 is in communication with the accommodation space S. In addition, in thedrive shaft 16, afifth passage 65 is formed so as to extend on the front side of thefirst shaft portion 16a in the direction of the axis T and extend in the radial direction of the axis T. Thefifth passage 65 is in communication with thefourth passage 64 and is in communication with theshaft seal chamber 20 in thefront housing 12. Theshaft seal chamber 20 is in communication with thecrank chamber 15 through asixth passage 66 formed in thefront housing 12. - Therefore, the
discharge passage 51, the accommodation chamber 50 (or theoil reservoir 52b), thecommunication passage 59, thecontrol valve 60, thefirst passage 61, thesecond passage 62, thethird passage 63, the accommodation space S, thefourth passage 64, thefifth passage 65, theshaft seal chamber 20 and thesixth passage 66 form a supply passage for supplying the refrigerant gas in thedischarge chamber 31 to the crankchamber 15. The supply passage is formed differently from the gas passage. When thecontrol valve 60 is operated, the opening degree of the supply passage is adjusted. A controller (not shown) is connected to thecontrol valve 60 for performing control of current supply (duty cycle control). In the supply passage, thecontrol valve 60 is provided on the upstream side of thefirst passage 61 located adjacent to thesuction chamber 30. That is, in the supply passage, thefirst passage 61 which forms the part of the supply passage is located downstream from thecontrol valve 60. - In the
drive shaft 16, ableed port 16c is formed in thefirst shaft portion 16a at a position between theswash plate 24 and thelug plate 22. Thebleed port 16c is in communication with aseventh passage 67 formed between the inner circumferential surface of thefirst shaft portion 16a and the outer circumferential surface of thesecond shaft portion 16b. Theseventh passage 67 is in communication with the accommodation space S. The accommodation space S is in communication with aneighth passage 68 formed in thecylinder block 11, and theeighth passage 68 is in communication with aninth passage 69 formed in thevalve plate assembly 13. Theninth passage 69 is in communication with thesuction chamber 30. Thebleed port 16c, theseventh passage 67, the accommodation space S, theeighth passage 68 and theninth passage 69 form a bleed passage for drawing the refrigerant gas from thecrank chamber 15 to thesuction chamber 30. In the accommodation space S, a lip seal L is interposed between the inner wall surface of the accommodation space S and the outer circumferential surface of the rear end of thesecond shaft portion 16b of the drive shat 16 in such a way that a part of the supply passage and a part of the bleed passage which are defined in the accommodation space S are shut off from each other. - The operation of the
compressor 10 of the present embodiment will now be described. As thedrive shaft 16 is rotated by a drive source (not shown), theswash plate 24 is rotated and thepistons 27 are reciprocally moved in the respective cylinder bores 26, accordingly. At this time, the refrigerant gas circulating through the externalrefrigerant circuit 40 is drawn from thesuction chamber 30 into the cylinder bores 26 through the corresponding suction valves andsuction ports 32, thereby to be compressed in the compression chambers (not shown), respectively. The compressed refrigerant gas is discharged to thedischarge chamber 31 through the correspondingdischarge ports 34 and discharge valves. The refrigerant gas discharged to thedischarge chamber 31 is led to theoil separator 52 in theaccommodation chamber 50 through thedischarge passage 51, and theoil separation portion 52a of theoil separator 52 separates the oil from the refrigerant gas. - A part of the refrigerant gas whose lubricating oil is separated passes through the inside of the
oil separation portion 52a and then is supplied to thecondenser 40a of the externalrefrigerant circuit 40. That is, the part of the refrigerant gas is led to the externalrefrigerant circuit 40 through the gas passage including theaccommodation chamber 50 and thedischarge passage 51. Meanwhile, the other part of the refrigerant gas whose lubricating oil is separated in theoil separator 52 passes through theoil reservoir 52b and then is led to thecontrol valve 60 through thecommunication passage 59 with the lubricating oil in theoil reservoir 52b. That is, the refrigerant gas discharged to thedischarge chamber 31 is divided into the gas passage for the externalrefrigerant circuit 40 and thecommunication passage 59 for thecontrol valve 60 through thedischarge passage 51. Therefore, the refrigerant gas is separately led to the externalrefrigerant circuit 40 and thecontrol valve 60. - Of the refrigerant gas led to the
control valve 60, flow rate of the refrigerant gas supplied to the crankchamber 15 through the supply passage is adjusted by adjusting the opening degree of thecontrol valve 60. When the refrigerant gas passes through thecontrol valve 60, the refrigerant gas is throttled by a valve portion (not shown) of thecontrol valve 60 thereby to be decompressed. When the refrigerant gas is decompressed, the temperature of the refrigerant gas is reduced. - In addition, the refrigerant gas whose temperature is reduced passes through the
first passage 61. The part of thefirst passage 61 is disposed in theperipheral wall 14c so as to be located adjacent to thesuction chamber 30, Meanwhile, the refrigerant gas which circulates through the externalrefrigerant circuit 40 thereby to be lowered in temperature is drawn into thesuction chamber 30. The refrigerant gas in thesuction chamber 30 is lower in temperature than the refrigerant gas passing through the supply passage (the first passage 61). Therefore, the refrigerant gas passing through thefirst passage 61 of the supply passage is cooled by the refrigerant gas in thesuction chamber 30. That is, the refrigerant gas which is discharged to thedischarge chamber 31 and then passes through thecontrol valve 60 and a part of the supply passage is cooled by two cooling means, in other words, thecontrol valve 60 and thesuction chamber 30. Thus, the refrigerant gas which is discharged to thedischarge chamber 31 and then passes through thecontrol valve 60 and a part of the supply passage is lower in temperature than the refrigerant gas in thedischarge chamber 31. - In the
drive shaft 16, theseventh passage 67 is formed radially outward of thefourth passage 64 so as to surround thefourth passage 64 which forms a part of the supply passage. Therefore, the refrigerant gas which passes through theseventh passage 67 performs insulation effect for shutting off transfer of heat from the outside of the outer circumferential surface of thedrive shaft 16 to thefourth passage 64, thereby to maintain the refrigerant gas in the fourth passage 64 (the supply passage) at low temperature. - The refrigerant gas which passes through the
first passage 61 to be lowered in temperature is drawn into theshaft seal chamber 20 through thesecond passage 62, thethird passage 63, the accommodation space S, thefourth passage 64 and thefifth passage 65, and then is blown to thelip seal 21 in theshaft seal chamber 20. Thelip seal 21 which generates heat due to constant sliding contact with thedrive shaft 16 is thus cooled by the refrigerant gas. Thereafter, the refrigerant gas drawn into theshaft seal chamber 20 is supplied from thesixth passage 66 to the crankchamber 15. - The refrigerant gas in the
crank chamber 15 is drawn to the bleed passage, and furthermore drawn to thesuction chamber 30. The balance between the flow rate of the refrigerant gas supplied into thecrank chamber 15 through the supply passage and the flow rate of the refrigerant gas drawn from thecrank chamber 15 through the bleed passage is controlled to determine (or adjust) the pressure in thecrank chamber 15. When the pressure in thecrank chamber 15 is changed, the pressure difference between thecrank chamber 15 and the cylinder bores 26 through therespective pistons 27 is changed thereby to change angle of inclination of theswash plate 24. Consequently, stroke of each piston 27 (displacement of the compressor 10) is adjusted. - The first embodiment has the following advantageous effects.
- (1) The
discharge chamber 31 and thecrank chamber 15 are in communication with each other through the supply passage. A part of the supply passage (the first passage 61) is located radially outward of thepartition wall 14a, and is located radially outward of the suction chamber 30 (in theperipheral wall 14c) so as to be located adjacent to thesuction chamber 30. The part of the supply passage is nearer to the suction chamber than the discharge chamber. Therefore, the refrigerant gas which is discharged to thedischarge chamber 31 and then passes through thecontrol valve 60 is cooled by the low-temperature refrigerant gas in thesuction chamber 30. The cooled refrigerant gas is supplied into theshaft seal chamber 20 through the supply passage, so that the cooled refrigerant gas is blown to thelip seal 21 in theshaft seal chamber 20. Thus, the refrigerant gas which is supplied into theshaft seal chamber 20 is reduced in temperature compared to the case where the refrigerant gas which is discharged to thedischarge chamber 31 and then passes through thecontrol valve 60 is directly supplied into theshaft seal chamber 20. Consequently, temperature of the refrigerant gas which is blown to thelip seal 21 in theshaft seal chamber 20 is reduced thereby to sufficiently cool thelip seal 21. - (2) The
compressor 10 is so arranged that thedischarge chamber 31 is defined in the middle of therear housing 14 and theannular suction chamber 30 is defined radially outward of thedischarge chamber 31 through thepartition wall 14a. In thecompressor 10, a part of the supply passage (the first passage 61) is located in such a position that thefirst passage 61 and thedischarge chamber 31 sandwich thepartition wall 14a and thesuction chamber 30. Therefore, the refrigerant gas which passes through thefirst passage 61 is not affected by the high-temperature refrigerant gas in thedischarge chamber 31 and is even cooled by the refrigerant gas in thesuction chamber 30 directly. Thus, the refrigerant gas which passes through thefirst passage 61 is efficiently cooled by the refrigerant gas in thesuction chamber 30. - (3) In addition, in the
compressor 10, a part of the supply passage (the first passage 61) is located in theperipheral wall 14c which is located radially outward of thesuction chamber 30. Therefore, the refrigerant gas in thesuction chamber 30 is not directly heated by the refrigerant gas which passes through thefirst passage 61, for example, as in the case where thefirst passage 61 is so arranged as to traverse thesuction chamber 30. Thus, deterioration of the cooling efficiency in the externalrefrigerant circuit 40 caused by the refrigerant gas in thesuction chamber 30 being heated is prevented, - (4) In the
rear housing 14, the gas passage through which a part of the refrigerant gas is led to the externalrefrigerant circuit 40 and thecommunication passage 59 through which the other part of the refrigerant gas is led to thecontrol valve 60 are so formed that thecommunication passage 59 is separated from theaccommodation chamber 50 of the gas passage. That is, although the supply passage shares thedischarge passage 51 with the gas passage, the supply passage is formed differently from the gas passage. Therefore, the refrigerant gas discharged to thedischarge chamber 31 is separately led from thedischarge passage 51 to the externalrefrigerant circuit 40 and the supply passage, and only the refrigerant gas supplied to the supply passage is cooled by the refrigerant gas in thesuction chamber 30. That is, since in thecompressor 10 of the present embodiment all the refrigerant gas discharged to thedischarge chamber 31 is not led to the externalrefrigerant circuit 40 so as to be cooled by the refrigerant gas in thesuction chamber 30 on the way to the externalrefrigerant circuit 40, temperature of the refrigerant gas in thesuction chamber 30 is hard to rise. Consequently, as described in the above effect (3) deterioration of the cooling efficiency in the externalrefrigerant circuit 40 caused by the refrigerant gas in thesuction chamber 30 being heated is prevented. - (5) In the
rear housing 14, the gas passage through which a part of the refrigerant gas is led to the externalrefrigerant circuit 40 and the communication passage 59 (the supply passage) through which the other part of the refrigerant gas is led to thecontrol valve 60 are differently formed. Therefore, for example, compared to the case that the gas passage through which the refrigerant gas discharged to thedischarge chamber 31 is led to the externalrefrigerant circuit 40 also serves as the supply passage, increase of the diameter of a passage which is indispensable for ensuring the flow rate of the refrigerant gas into the externalrefrigerant circuit 40 and the flow rate of the refrigerant gas into thecrank chamber 15 is prevented. - (6) A part of the supply passage (the first passage 61) which is located adjacent to the
suction chamber 30 is located on the downstream side of thecontrol valve 60. Therefore, the refrigerant gas is decompressed by thecontrol valve 60 and then is cooled by the refrigerant gas in thesuction chamber 30. Thus, the refrigerant gas in the supply passage is effectively cooled. - (7) A part of the supply passage (the
fourth passage 64 and the fifth passage 65) is formed in thedrive shaft 16 and a part of the bleed passage (the seventh passage 67) is formed radially outward of the part of the supply passage (thefourth passage 64 and the fifth passage 65). Thus, the refrigerant gas in thecrank chamber 15 passes through the bleed passage at the position between the outer circumferential surface of thedrive shaft 16 and the part of the supply passage so as to perform heat insulation between radially outward area of the outer circumferential surface of thedrive shaft 16 and the inside area of the supply passage and then is drawn out to thesuction chamber 30. Therefore, the refrigerant gas in the supply passage is maintained at low temperature thereby to blow the low-temperature refrigerant gas to thelip seal 21, which furthermore enhances the cooling effect of thelip seal 21.
The following will describe a variable displacement compressor (hereinafter referred to merely as a compressor) according to a second preferred embodiment of the present invention with reference to FIG. 3. The second embodiment differs from the first embodiment in that the positions of the supply passage and the bleed passage of the first embodiment are changed. The overlapped description for repeating the same part is omitted.
As shown in FIG. 3, thedrive shaft 16 of the second embodiment is not provided with the double pipe structure formed by thefirst shaft portion 16a and thesecond shaft portion 16b but is formed in a cylindrical shape. Afirst passage 71 is formed in therear housing 14, which is in communication with thecontrol valve 60. Thefirst passage 71 is in communication with asecond passage 72 formed in thecylinder block 11. A part of thefirst passage 71 is located radially outward of thepartition wall 14a which separates thesuction chamber 30 and thedischarge chamber 31, and is located in theperipheral wall 14c which is located radially outward of thesuction chamber 30 so as to be located adjacent to thesuction chamber 30. That is, the part of thefirst passage 71 is arranged in such a position that the refrigerant gas which passes through thefirst passage 71 is cooled by the refrigerant gas in thesuction chamber 30. Thesecond passage 72 is in communication with athird passage 73 formed in thefront housing 12, and thethird passage 73 is in communication with theshaft seal chamber 20.
Theshaft seal chamber 20 is in communication with thecrank chamber 15 through afourth passage 74 formed in thefront housing 12. Therefore, thedischarge passage 51, the accommodation chamber 50 (theoil reservoir 52b), thecommunication passage 59, thecontrol valve 60, thefirst passage 71, thesecond passage 72, thethird passage 73, theshaft seal chamber 20 and thefourth passage 74 form the supply passage for supplying the refrigerant gas in thedischarge chamber 31 to the crankchamber 15. Ableed passage 77 through which thecrank chamber 15 and thesuction chamber 30 are in communication with each other is formed though thecylinder block 11 and thevalve plate assembly 13, thereby to allow the refrigerant gas in thecrank chamber 15 to be drawn out to thesuction chamber 30.
Therefore, the second embodiment has the following advantageous effects in addition to the effects (1) through (6) of the first embodiment. - (8) In the second embodiment, the supply passage is formed in the housing (the
cylinder block 11, thefront housing 12 and the rear housing 14) of thecompressor 10. Therefore, the supply passage is cooled by air outside the housing of thecompressor 10. Thus, the temperature of the refrigerant gas blown to thelip seal 21 is reduced thereby to sufficiently cool thelip seal 21 in theshaft seal chamber 20. - The following will describe a variable displacement compressor (hereinafter referred to merely as a compressor) according to a third preferred embodiment of the present invention with reference to FIGs. 4 and 5. The third embodiment differs from the first embodiment in that the positions of the discharge chamber and the suction chamber of the first embodiment are reversed and that the positions of the supply passage and the bleed passage of the first embodiment are changed. The overlapped description for repeating the same part is omitted.
- As shown in FIG. 4, the
suction chamber 30 is formed in the middle of therear housing 14. Meanwhile, in therear housing 14, thepartition wall 14a is formed radially outward of thesuction chamber 30. In addition, in therear housing 14, thedischarge chamber 31 is provided radially outward of thesuction chamber 30 through thepartition wall 14a in a annular shape so as to surround thesuction chamber 30. Furthermore, in therear housing 14, anoutlet 31 a is formed so as to be in communication with thedischarge chamber 31. Thedischarge chamber 31 is connected to the externalrefrigerant circuit 40 through theoutlet 31a. The high-pressure refrigerant gas discharged to thedischarge chamber 31 is led to the externalrefrigerant circuit 40 through theoutlet 31a. Therefore, theoutlet 31a forms the gas passage. - In the
rear housing 14, thecontrol valve 60 is disposed. In addition, in therear housing 14, thedischarge passage 80 is formed so as to communicate thedischarge chamber 31 and thecontrol valve 60. Furthermore, in therear housing 14, afirst passage 81 is formed so as to communicate thecontrol valve 60 and asecond passage 82 formed in thevalve plate assembly 13. - As shown in FIG. 5, a part of the
first passage 81 is formed in therear housing 14 so as to pass through thepartition wall 14a. The part of thefirst passage 81 is located in the inner wall surface of thepartition wall 14a which separates thedischarge chamber 31 and thesuction chamber 30. The part of thefirst passage 81 is located adjacent to thesuction chamber 30, that is, the part of thefirst passage 81 is nearer to the suction chamber than thedischarge chamber 31. Therefore, the part of thefirst passage 81 is arranged in such a position that the refrigerant gas which passes through thefirst passage 81 is cooled by the refrigerant gas in thesuction chamber 30. - As shown in FIG. 4, the
second passage 82 is in communication with athird passage 83 formed in thecylinder block 11, and thethird passage 83 is in communication with afourth passage 84 formed in thefront housing 12. Thefourth passage 84 is in communication with theshaft seal chamber 20, which is in communication with thecrank chamber 15 through afifth passage 85 formed in thefront housing 12. Therefore, thedischarge passage 80, thecontrol valve 60, thefirst passage 81, thesecond passage 82, thethird passage 83, thefourth passage 84, theshaft seal chamber 20 and thefifth passage 85 form the supply passage for supplying the refrigerant gas in thedischarge chamber 31 to the crankchamber 15. Ableed passage 87 through which thecrank chamber 15 and thesuction chamber 30 are in communication with each other is formed though thecylinder block 11 and thevalve plate assembly 13, thereby to allow the refrigerant gas in thecrank chamber 15 to be drawn to thesuction chamber 30. - Therefore, the third embodiment has the effects similar to the effects (1) and (3) through (6) of the first embodiment. In addition, modifications of the above embodiments are as follows.
- In a modification of the first embodiment, as shown by alternate long and two short dashes line of FIG. 1 and additionally as shown in FIG. 6, the
first passage 61 which forms a part of the supply passage may be located so as to traverse thesuction chamber 30 radially outward of thepartition wall 14a and a part of thefirst passage 61 may be located inside thesuction chamber 30. In a similar manner, in a modification of the second embodiment, as shown by alternate long and two short dashes line of FIG. 3 and additionally as shown in FIG. 6, thefirst passage 71 which forms a part of the supply passage may be located so as to traverse thesuction chamber 30 radially outward of thepartition wall 14a and a part of thefirst passage 71 may be located inside thesuction chamber 30. In these structures, the refrigerant gas in thesuction chamber 30 is in contact with entire circumference of each of thefirst passages first passages suction chamber 30. - In a modification of the first embodiment, as shown in FIG 7, a part of the
first passage 61 which forms a part of the supply passage may be located in the inner wall surface of theperipheral wall 14c which is located radially outward of thepartition wall 14a. In a modification of the first embodiment, as shown in FIG. 8, a part of thefirst passage 61 which forms a part of the supply passage may be located in the outer wall surface of thepartition wall 14a. In these structures, contact areas between the outer peripheral surface of thefirst passage 61 and the refrigerant gas in thesuction chamber 30 are increased compared to the case where the part of thefirst passage 61 is formed so as to pass through theperipheral wall 14c or thepartition wall 14a without changing the shape of theperipheral wall 14c or thepartition wall 14a. Therefore, the refrigerant gas which passes through thefirst passage 61 is efficiently cooled by the refrigerant gas in thesuction chamber 30. In a similar manner, in a modification of the second embodiment, as shown in FIG. 7, a part of thefirst passage 71 which forms a part of the supply passage may be located in the inner wall surface of theperipheral wall 14c which is located radially outward of thepartition wall 14a. In a modification of the second embodiment, as shown in FIG. 8, a part of thefirst passage 71 which forms a part of the supply passage may be located in the outer wall surface of thepartition wall 14a. In these structures, contact areas between the outer peripheral surface of thefirst passage 71 and the refrigerant gas in thesuction chamber 30 are increased compared to the case where a part of thefirst passage 71 is formed so as to pass through theperipheral wall 14c or thepartition wall 14a without changing the shape of theperipheral wall 14c or thepartition wall 14a. Therefore, the refrigerant gas which passes through thefirst passage 71 is efficiently cooled by the refrigerant gas in thesuction chamber 30. - In a modification of the third embodiment, as shown in FIG. 9, the
first passage 81 which forms a part of the supply passage may be located so as to traverse thesuction chamber 30 radially inward of thepartition wall 14a and a part of thefirst passage 81 may be located inside thesuction chamber 30. In this structure, the refrigerant gas in thesuction chamber 30 is in contact with entire peripheral wall of thefirst passage 81. Therefore, the entire peripheral wall of thefirst passage 81 is cooled by the refrigerant gas in thesuction chamber 30. - In a modification of each embodiment, the
control valve 60 may be disposed downstream from thesuction chamber 30 in the supply passage. - In a modification of the first embodiment, while the
drive shaft 16 has only thefourth passage 64 and thefifth passage 65 formed therein, thedrive shaft 16 may dispense with thebleed port 16c and theseventh passage 67. That is, thedrive shaft 16 may be formed to have a part of the supply passage and not to have a part of the bleed passage. In this case, the bleed passage is formed in thecylinder block 11. - In a modification of each embodiment, the
oil separator 52 is not necessarily needed. In this case, the refrigerant gas discharged to thedischarge chamber 31 may be directly led to the externalrefrigerant circuit 40 and thecontrol valve 60. - In a modification of the third embodiment, the
first passage 81 which forms a part of the supply passage may be formed so as to traverse thesuction chamber 30. In addition, the supply passage may be formed in thedrive shaft 16 such that thecrank chamber 15 and thedischarge chamber 31 are in communication with each other. - Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive, and the invention is not to be limited to the details given herein but may be modified within the scope of the appended claims.
- A variable displacement compressor for forming a refrigerant circuit with an external refrigerant circuit includes a housing, a drive shaft, a swash plate, a shaft seal member, a supply passage, a control valve and a gas passage. The housing has a suction chamber, a crank chamber, a discharge chamber and a shaft seal chamber formed therein. The discharge chamber is in communication with the crank chamber through the supply passage. The supply passage has the shaft seal chamber. The discharge chamber is in communication with the external refrigerant circuit through the gas passage. The supply passage is formed differently from the gas passage. A part of the supply passage is located adjacent to the suction chamber and nearer to the suction chamber than the discharge chamber.
Claims (16)
- A variable displacement compressor for forming a refrigerant circuit with an external refrigerant circuit, including a housing, a drive shaft, a swash plate, a shaft seal member, a supply passage and a control valve, the housing having a suction chamber, a crank chamber, a discharge chamber and a shaft seal chamber formed therein, the drive shaft being rotataby supported by the housing, the swash plate being connected to the drive shaft so that angle of inclination of the swash plate relative to the drive shaft is variable, the swash plate being accommodated in the crank chamber, the shaft seal member being accommodated in the shaft seal chamber, the discharge chamber being in communication with the crank chamber through the supply passage, the supply passage including the shaft seal chamber, the control valve being disposed in the supply passage, flow rate of refrigerant gas supplied from the discharge chamber to the crank chamber through the supply passage being adjusted by adjusting an opening degree of the control valve, characterized in that
the discharge chamber is in communication with the external refrigerant circuit through a gas passage, in that the supply passage is formed differently from the gas passage, and in that a part of the supply passage is located adjacent to the suction chamber and nearer to the suction chamber than the discharge chamber. - The variable displacement compressor according to claim 1, wherein the suction chamber is formed radially outward of the discharge chamber, the part of the supply passage being located radially outward of a partition wall which separates the discharge chamber and the suction chamber.
- The variable displacement compressor according to claim 2, wherein the part of the supply passage is located radially outward of the suction chamber.
- The variable displacement compressor according to claim 2 or 3, wherein the part of the supply passage is located so as to traverse the suction chamber.
- The variable displacement compressor according to claim 1, wherein the suction chamber is formed radially inward of the discharge chamber, the part of the supply passage being located radially inward of a partition wall which separates the discharge chamber and the suction chamber.
- The variable displacement compressor according to claim 5, wherein the part of the supply passage is located so as to traverse the suction chamber.
- The variable displacement compressor according to claim 1, wherein the suction chamber is formed radially outward of the discharge chamber, the part of the supply passage being located in an outer wall surface of a partition wall which separates the discharge chamber and the suction chamber.
- The variable displacement compressor according to claim 1, wherein the suction chamber is formed radially inward of the discharge chamber, the part of the supply passage being located in an inner wall surface of a partition wall which separates the discharge chamber and the suction chamber.
- The variable displacement compressor according to any one of claims 1 through 8, wherein the part of the supply passage is located downstream from the control valve in the supply passage.
- The variable displacement compressor according to any one of claims 1 through 9, wherein another part of the supply passage is formed in the drive shaft.
- The variable displacement compressor according to any one of claims 1 through 9, wherein a bleed passage through which the refrigerant gas in the crank chamber is drawn to the suction chamber is disposed in the housing, and wherein at least parts of the supply passage and the bleed passage are formed in the drive shaft, the part of the supply passage which is formed in the drive shaft being in communication with the shaft seal chamber, the part of the bleed passage which is formed in the drive shaft being formed between the part of the supply passage in the drive shaft and an outer circumferential surface of the drive shaft.
- The variable displacement compressor according to claim 11, wherein the drive shaft includes a cylindrical hollow first shaft portion and a cylindrical hollow second shaft portion inserted in the first shaft portion, the part of the bleed passage formed in the drive shaft being defined by an inner circumferential surface of the first shaft portion and an outer circumferential surface of the second shaft portion, the part of the supply passage formed in the drive shaft being defined by an inner circumferential surface of the second shaft portion.
- The variable displacement compressor according to claim 12, wherein an accommodation space is defined in the housing for accommodating a rear end of the drive shaft therein, parts of the supply passage and the bleed passage being defined in the accommodation space by a seal member disposed on the second shaft portion.
- The variable displacement compressor according to claim 13, wherein the part of the supply passage is in communication with the accommodation space through a valve plate assembly.
- The variable displacement compressor according to any one of claims 1 through 14, wherein the supply passage and the gas passage are partially shared and then are separated from each other.
- The variable displacement compressor according to any one of claims 1 through 14, wherein the supply passage and the gas passage are separately formed.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005207442A JP2007023900A (en) | 2005-07-15 | 2005-07-15 | Variable displacement compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1744059A1 true EP1744059A1 (en) | 2007-01-17 |
EP1744059B1 EP1744059B1 (en) | 2009-03-04 |
Family
ID=37102409
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06117116A Expired - Fee Related EP1744059B1 (en) | 2005-07-15 | 2006-07-13 | Variable displacement compressor |
Country Status (6)
Country | Link |
---|---|
US (1) | US20070014674A1 (en) |
EP (1) | EP1744059B1 (en) |
JP (1) | JP2007023900A (en) |
KR (1) | KR100756578B1 (en) |
CN (1) | CN100476202C (en) |
DE (1) | DE602006005426D1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4924464B2 (en) * | 2008-02-05 | 2012-04-25 | 株式会社豊田自動織機 | Swash plate compressor |
JP2009209910A (en) * | 2008-03-06 | 2009-09-17 | Toyota Industries Corp | Swash plate compressor |
KR20210073894A (en) | 2019-12-11 | 2021-06-21 | 인하대학교 산학협력단 | Highly-durable anodized stainless steel electrode for water eletrolysis and preparation method thereof |
NO20211589A1 (en) * | 2021-12-23 | 2023-06-26 | Heaten As | A working fluid extraction system for a displacement machine and a method of operating the system |
Citations (5)
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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 |
US4174191A (en) * | 1978-01-18 | 1979-11-13 | Borg-Warner Corporation | Variable capacity compressor |
US20030086791A1 (en) | 2001-11-02 | 2003-05-08 | Breindel John A | Variable capacity air conditioning compressor with improved crankcase oil retention |
EP1347173A2 (en) * | 2002-03-20 | 2003-09-24 | Calsonic Kansei Corporation | Lubrication system for swash plate compressor |
Family Cites Families (9)
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US4543043A (en) * | 1982-08-02 | 1985-09-24 | Borg-Warner Corporation | Variable displacement compressor |
JPH01182581A (en) * | 1988-01-14 | 1989-07-20 | Honda Motor Co Ltd | Control device for variable displacement compressor |
JP3585150B2 (en) * | 1997-01-21 | 2004-11-04 | 株式会社豊田自動織機 | Control valve for variable displacement compressor |
JPH1193832A (en) * | 1997-09-25 | 1999-04-06 | Sanden Corp | Variable displacement compressor |
JP4385516B2 (en) * | 2000-11-07 | 2009-12-16 | 株式会社豊田自動織機 | Piston compressor |
JP4399994B2 (en) * | 2000-11-17 | 2010-01-20 | 株式会社豊田自動織機 | Variable capacity compressor |
JP2002225549A (en) * | 2001-02-05 | 2002-08-14 | Toyota Industries Corp | Air-conditioning system for vehicle |
JP3985507B2 (en) * | 2001-11-22 | 2007-10-03 | 株式会社豊田自動織機 | Swash plate compressor |
JP2006022785A (en) * | 2004-07-09 | 2006-01-26 | Toyota Industries Corp | Variable displacement compressor |
-
2005
- 2005-07-15 JP JP2005207442A patent/JP2007023900A/en not_active Withdrawn
-
2006
- 2006-05-01 KR KR1020060039265A patent/KR100756578B1/en not_active IP Right Cessation
- 2006-07-13 EP EP06117116A patent/EP1744059B1/en not_active Expired - Fee Related
- 2006-07-13 DE DE602006005426T patent/DE602006005426D1/en not_active Expired - Fee Related
- 2006-07-14 CN CNB2006101257780A patent/CN100476202C/en not_active Expired - Fee Related
- 2006-07-14 US US11/486,636 patent/US20070014674A1/en not_active Abandoned
Patent Citations (5)
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 |
US4174191A (en) * | 1978-01-18 | 1979-11-13 | Borg-Warner Corporation | Variable capacity compressor |
US20030086791A1 (en) | 2001-11-02 | 2003-05-08 | Breindel John A | Variable capacity air conditioning compressor with improved crankcase oil retention |
EP1347173A2 (en) * | 2002-03-20 | 2003-09-24 | Calsonic Kansei Corporation | Lubrication system for swash plate compressor |
Also Published As
Publication number | Publication date |
---|---|
US20070014674A1 (en) | 2007-01-18 |
CN1896503A (en) | 2007-01-17 |
KR20070009378A (en) | 2007-01-18 |
JP2007023900A (en) | 2007-02-01 |
CN100476202C (en) | 2009-04-08 |
KR100756578B1 (en) | 2007-09-07 |
DE602006005426D1 (en) | 2009-04-16 |
EP1744059B1 (en) | 2009-03-04 |
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