EP1744059B1 - Compresseur à capacité variable - Google Patents

Compresseur à capacité variable Download PDF

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Publication number
EP1744059B1
EP1744059B1 EP06117116A EP06117116A EP1744059B1 EP 1744059 B1 EP1744059 B1 EP 1744059B1 EP 06117116 A EP06117116 A EP 06117116A EP 06117116 A EP06117116 A EP 06117116A EP 1744059 B1 EP1744059 B1 EP 1744059B1
Authority
EP
European Patent Office
Prior art keywords
passage
chamber
supply passage
drive shaft
suction chamber
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.)
Not-in-force
Application number
EP06117116A
Other languages
German (de)
English (en)
Other versions
EP1744059A1 (fr
Inventor
Tetsuhiko Fukanuma
Naoya Yokomachi
Shingo Enami
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1744059A1 publication Critical patent/EP1744059A1/fr
Application granted granted Critical
Publication of EP1744059B1 publication Critical patent/EP1744059B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • 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
    • 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.
  • Document US 2003-086791 A1 shows a compressor for forming a refrigerant circuit with an external refrigerant circuit.
  • the compressor includes a housing, a drive shaft, a swash plate, a shaft seal member, a supply passage and a control valve.
  • the housing has a suction chamber, a crank chamber, a discharge chamber and a shaft seal chamber.
  • the drive shaft is rotatably supported by the housing and connected to the swash plate.
  • the angle of inclination of the swash plate relative to the drive shaft is variable.
  • the flow rate of the 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 wherein the discharge chamber is in communication with the external refrigerant circuit through a gas passage.
  • the supply passage is formed differently from the gas passage communicating the discharge chamber and the external refrigerant circuit, wherein a part of the supply passage is located adjacent to the suction chamber and nearer to the suction chamber than to the discharge
  • variable displacement compressor comprising a control valve for controlling the flow rate of refrigerant gas which, on the one hand, shall have a compact design and, on the other hand, shall enable a reliable operation of the compressor.
  • the charactering key features of the invention are directed to the idea to form the suction chamber radially outward or inward of the discharge chamber and to provide a partition wall to separate the discharge chamber and the suction chamber. Furthermore, a part of the supply passage is located outward the partition wall in case that the suction chamber is formed radially outward of the discharge chamber, or in case that the suction chamber is formed radially inward of the discharge chamber, a part of the supply passage is located inward the partition wall and, thus, to locate the mentioned part of the supply passage nearer to the suction chamber than to 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 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (12)

  1. Compresseur à déplacement variable destiné à former un circuit de réfrigérant avec un circuit de réfrigérant extérieur incluant un boîtier (12, 14), un arbre d'entraînement (16), un plateau oscillant (24), un élément de joint d'arbre (21), un passage d'alimentation (61-66) et une soupape de commande (60), le boîtier (12, 14) ayant une chambre d'aspiration (30), un carter (15), une chambre de refoulement (31) et une chambre d'étanchéité d'arbre (20) formée dans celui-ci, l'arbre d'entraînement (16) étant supporté pour tourner par le boîtier (12, 14), le plateau oscillant (24) étant raccordé à l'arbre d'entraînement (16), de telle sorte que l'angle d'inclinaison du plateau oscillant (24) par rapport à l'arbre d'entraînement (16) est variable, le plateau oscillant (24) étant logé dans le carter (15), l'élément d'étanchéité d'arbre (21) étant logé dans la chambre d'étanchéité d'arbre (20), la chambre de refoulement (31) étant en communication avec le carter (15) par l'intermédiaire du passage d'alimentation (61-66), le passage d'alimentation (61-66) incluant la chambre d'étanchéité d'arbre (20), la soupape de commande (60) étant disposée dans le passage d'alimentation (61-66), le débit du gaz réfrigérant fourni à partir de la chambre de refoulement (31) dans le carter (15), par l'intermédiaire du passage d'alimentation (61-66), étant réglé en réglant un degré d'ouverture de la soupape de commande (60), dans lequel la chambre de refoulement (31) est en communication avec le circuit de réfrigérant extérieur par l'intermédiaire d'un passage de gaz (51), dans lequel le passage d'alimentation (61-66) est formé différemment du passage de gaz (51), dans lequel une partie du passage d'alimentation (61-66) est située de manière adjacente à la chambre d'aspiration (30) et plus près de la chambre d'aspiration (30) que de la chambre de refoulement (31),
    caractérisé en ce que :
    la chambre d'aspiration (30) est formée radialement à l'extérieur de la chambre de refoulement (31) et en ce qu'une partie du passage d'alimentation (61-66) est située à l'extérieur de la paroi de séparation (14a) qui sépare la chambre de refoulement (31) et la chambre d'aspiration (30), dans la direction radiale de l'arbre d'entraînement (16) ; ou en ce que
    la chambre d'aspiration est formée radialement à l'intérieur de la chambre de refoulement, et en ce qu'une partie du passage d'alimentation est située à l'intérieur d'une paroi de séparation qui sépare la chambre de refoulement et la chambre d'aspiration dans une direction radiale de l'arbre d'entraînement.
  2. Compresseur à déplacement variable selon la revendication 1, dans lequel la partie du passage d'alimentation (61-66) est située de façon à traverser la chambre d'aspiration (30).
  3. Compresseur à déplacement variable selon la revendication 1, dans lequel la chambre d'aspiration (30) est formée radialement à l'extérieur de la chambre de refoulement (31), la partie du passage d'alimentation (61-66) étant située dans une surface de paroi extérieure d'une paroi de séparation qui sépare la chambre de refoulement (31) et la chambre d'aspiration (30).
  4. Compresseur à déplacement variable selon la revendication 1, dans lequel la chambre d'aspiration (30) est formée radialement à l'intérieur de la chambre de refoulement (31), la partie du passage d'alimentation (61-66) étant située dans une surface de paroi interne d'une paroi de séparation qui sépare la chambre de refoulement (31) et la chambre d'aspiration (30).
  5. Compresseur à déplacement variable selon les revendications 1 à 4, dans lequel la partie du passage d'alimentation (61-66) est située en aval de la soupape de commande (60) dans le passage d'alimentation (61-66).
  6. Compresseur à déplacement variable selon les revendications 1 à 5, dans lequel une autre partie du passage d'alimentation (61-66) est formée dans l'arbre d'entraînement (16).
  7. Compresseur à déplacement variable selon les revendications 1 à 6, dans lequel le passage de purge (87) par l'intermédiaire duquel le gaz réfrigérant dans le carter (15) est aspiré dans la chambre d'aspiration (30) est disposé dans le boîtier (12, 14), et dans lequel au moins les parties du passage d'alimentation (61-66) et du passage de purge (87) sont formées dans l'arbre d'entraînement (16), la partie du passage d'alimentation (61-66) qui est formée dans l'arbre d'entraînement (16) étant en communication avec la chambre d'étanchéité d'arbre (21), la partie du passage de purge (87) qui est formée dans l'arbre d'entraînement (16) étant formée entre la partie du passage d'alimentation (61-66) dans l'arbre d'entraînement (16) et une surface de circonférence extérieure de l'arbre d'entraînement (16).
  8. Compresseur à déplacement variable selon la revendication 7, dans lequel l'arbre d'entraînement (16) inclut une première partie d'arbre creuse cylindrique et une seconde partie d'arbre creuse cylindrique insérée dans la première partie d'arbre, la partie du passage de purge (87) formée dans l'arbre d'entraînement (16) étant définie par une surface de circonférence interne de la première partie d'arbre et une surface de circonférence externe de la seconde partie d'arbre, la partie du passage d'alimentation (61-66) formée dans l'arbre d'entraînement (16) étant définie par une surface de circonférence interne de la seconde partie d'arbre.
  9. Compresseur à déplacement variable selon la revendication 8, dans lequel un espace de logement est défini dans le boîtier (12, 14) afin de loger une extrémité arrière de l'arbre d'entraînement (16) dans celui-ci, les parties du passage d'alimentation (61-66) et du passage de purge (87) étant définies dans l'espace de logement par un élément d'étanchéité disposé sur la seconde partie d'arbre.
  10. Compresseur à déplacement variable selon la revendication 9, dans lequel la partie du passage d'alimentation (61-66) est en communication avec l'espace de logement par l'intermédiaire d'un ensemble de plateau de soupape (13).
  11. Compresseur à déplacement variable selon l'une quelconque des revendications 1 à 10, dans lequel le passage d'alimentation (61-66) et le passage de gaz sont partiellement partagés et sont ensuite séparés l'un de l'autre.
  12. Compresseur à déplacement variable selon l'une quelconque des revendications 1 à 10, dans lequel le passage d'alimentation (61-66) et le passage de gaz sont formés séparément.
EP06117116A 2005-07-15 2006-07-13 Compresseur à capacité variable Not-in-force EP1744059B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005207442A JP2007023900A (ja) 2005-07-15 2005-07-15 可変容量型圧縮機

Publications (2)

Publication Number Publication Date
EP1744059A1 EP1744059A1 (fr) 2007-01-17
EP1744059B1 true EP1744059B1 (fr) 2009-03-04

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EP06117116A Not-in-force EP1744059B1 (fr) 2005-07-15 2006-07-13 Compresseur à capacité variable

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US (1) US20070014674A1 (fr)
EP (1) EP1744059B1 (fr)
JP (1) JP2007023900A (fr)
KR (1) KR100756578B1 (fr)
CN (1) CN100476202C (fr)
DE (1) DE602006005426D1 (fr)

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JP4924464B2 (ja) * 2008-02-05 2012-04-25 株式会社豊田自動織機 斜板式圧縮機
JP2009209910A (ja) * 2008-03-06 2009-09-17 Toyota Industries Corp 斜板式圧縮機
KR20210073894A (ko) 2019-12-11 2021-06-21 인하대학교 산학협력단 양극산화 처리된 고내구성 수전해용 스테인레스 강 전극 및 이의 제조방법
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

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Publication number Publication date
US20070014674A1 (en) 2007-01-18
JP2007023900A (ja) 2007-02-01
KR20070009378A (ko) 2007-01-18
DE602006005426D1 (de) 2009-04-16
EP1744059A1 (fr) 2007-01-17
KR100756578B1 (ko) 2007-09-07
CN100476202C (zh) 2009-04-08
CN1896503A (zh) 2007-01-17

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