WO2014114222A1 - 转动装置及应用其的转子式压缩机和流体马达 - Google Patents
转动装置及应用其的转子式压缩机和流体马达 Download PDFInfo
- Publication number
- WO2014114222A1 WO2014114222A1 PCT/CN2014/070972 CN2014070972W WO2014114222A1 WO 2014114222 A1 WO2014114222 A1 WO 2014114222A1 CN 2014070972 W CN2014070972 W CN 2014070972W WO 2014114222 A1 WO2014114222 A1 WO 2014114222A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rolling
- valve body
- rotating device
- rotary valve
- chamber
- Prior art date
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 53
- 238000005096 rolling process Methods 0.000 claims abstract description 242
- 230000007246 mechanism Effects 0.000 claims abstract description 35
- 238000002955 isolation Methods 0.000 claims abstract description 17
- 238000007789 sealing Methods 0.000 claims description 59
- 229920001971 elastomer Polymers 0.000 claims description 38
- 238000007906 compression Methods 0.000 claims description 30
- 230000006835 compression Effects 0.000 claims description 28
- 239000007789 gas Substances 0.000 claims description 16
- 239000002184 metal Substances 0.000 claims description 8
- 229910052751 metal Inorganic materials 0.000 claims description 8
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 7
- 230000036316 preload Effects 0.000 claims description 6
- 229910001873 dinitrogen Inorganic materials 0.000 claims description 4
- 239000003831 antifriction material Substances 0.000 claims description 3
- 239000002131 composite material Substances 0.000 claims description 3
- 230000002706 hydrostatic effect Effects 0.000 claims description 3
- 229910052757 nitrogen Inorganic materials 0.000 claims description 2
- 230000004308 accommodation Effects 0.000 claims 8
- 229910001111 Fine metal Inorganic materials 0.000 claims 2
- 238000000034 method Methods 0.000 description 19
- 239000003921 oil Substances 0.000 description 14
- 238000013461 design Methods 0.000 description 10
- 239000010687 lubricating oil Substances 0.000 description 10
- 229920001343 polytetrafluoroethylene Polymers 0.000 description 8
- 239000004810 polytetrafluoroethylene Substances 0.000 description 8
- 238000005461 lubrication Methods 0.000 description 7
- 239000007788 liquid Substances 0.000 description 6
- -1 polytetrafluoroethylene Polymers 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 229910000906 Bronze Inorganic materials 0.000 description 4
- 238000004891 communication Methods 0.000 description 4
- 230000005489 elastic deformation Effects 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 239000010974 bronze Substances 0.000 description 3
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000003825 pressing Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 229920001973 fluoroelastomer Polymers 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
- 239000004033 plastic Substances 0.000 description 2
- 229920003023 plastic Polymers 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 238000007514 turning Methods 0.000 description 2
- 229910000851 Alloy steel Inorganic materials 0.000 description 1
- 101001012040 Pseudomonas aeruginosa (strain ATCC 15692 / DSM 22644 / CIP 104116 / JCM 14847 / LMG 12228 / 1C / PRS 101 / PAO1) Immunomodulating metalloprotease Proteins 0.000 description 1
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- ATJFFYVFTNAWJD-UHFFFAOYSA-N Tin Chemical compound [Sn] ATJFFYVFTNAWJD-UHFFFAOYSA-N 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 229910052790 beryllium Inorganic materials 0.000 description 1
- ATBAMAFKBVZNFJ-UHFFFAOYSA-N beryllium atom Chemical compound [Be] ATBAMAFKBVZNFJ-UHFFFAOYSA-N 0.000 description 1
- 235000014121 butter Nutrition 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000012937 correction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 229920006351 engineering plastic Polymers 0.000 description 1
- 238000007667 floating Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- BSPSZRDIBCCYNN-UHFFFAOYSA-N phosphanylidynetin Chemical compound [Sn]#P BSPSZRDIBCCYNN-UHFFFAOYSA-N 0.000 description 1
- 239000002861 polymer material Substances 0.000 description 1
- 235000013824 polyphenols Nutrition 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000011343 solid material Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/38—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/40—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member
- F01C1/46—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member with vanes hinged to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/38—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/02 and having a hinged member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/40—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member
- F04C18/46—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and having a hinged member with vanes hinged to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/38—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/02 and having a hinged member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
- F04C2/46—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—Ball or roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
- F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C19/00—Sealing arrangements in rotary-piston machines or engines
- F01C19/02—Radially-movable sealings for working fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
- F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
- F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
Definitions
- the present invention relates to the field of fluid machinery technology, and more particularly to a rotating device and a rotor compressor and a fluid motor using the same. Background technique
- the most commonly used positive displacement compressors on the market are mainly divided into four types: reciprocating piston type, screw type, scroll type and rotor type.
- reciprocating piston type screw type
- scroll type rotor type
- rotor compressor when the main shaft rotates, the eccentric rotor rotates close to the inner wall of the cylinder, causing the crescent-shaped volume to periodically change, thereby completing the process of suction, compression and exhaust. Due to the smooth and balanced compression process of the rotor compressor, it has been widely used in household refrigeration equipment such as air conditioners and refrigerators.
- the rotor compressor includes a cylinder 1, a rolling rotor 2, an eccentric sleeve 3, a drive shaft 4 having an eccentric shaft portion, a swinging stopper, and a coil spring.
- An eccentric sleeve 3 is provided between the eccentric shaft portion of the drive shaft 4 and the rolling rotor 2 so as to be flexibly rotatable therebetween, so that the eccentricity of the rolling rotor 2 is adjusted and a flexible rolling contact seal is realized in operation.
- the eccentric sleeve 3 rotates around the center of the eccentricity while revolving around the drive shaft.
- the rotating portion of the swinging block is pressed against the outer circumferential surface of the rolling rotor 2 by the spring force of the coil spring to realize the swinging isolation.
- the rotor type compressor shown in Fig. 1 is slidably rubbed under the high-intensity working conditions, especially when the rotational frequency is very high, the sliding shafts of the drive shaft 4 with the eccentric shaft portion and the rolling rotor 2 and the eccentric sleeve 3
- the energy loss is large and must be lubricated with oil.
- the lubricating oil entering the cylinder must be separated from the compressed medium and discharged.
- the lubricating oil in the moving gap is to be sealed, in order to separate the lubricating oil from the exhaust gas, a high pressure is required in the casing of the system.
- the coil spring drives one end of the swinging block to make the pendulum
- the other end of the movable block is pressed against the rolling rotor 2. Since the coil spring works under high-strength conditions for a long time, it is very easy to cause failure and damage, which affects the service life of the entire rotor compressor. It is necessary to find a more sophisticated and reliable swing stopper resetting and pressing mechanism.
- the force between the swinging block and the rolling rotor 2 is not easy to control, and the force is too large, which not only increases the wear of the swinging block, but also consumes the power of the compressor; if the force is too small, it cannot be guaranteed.
- the seal of the cylinder is not only increases the wear of the swinging block, but also consumes the power of the compressor; if the force is too small, it cannot be guaranteed.
- the head of the swinging block is connected with the outer cylindrical surface of the rolling sealing ring 2, and the head of the swinging block is fixed with the position of the outer cylindrical surface of the rolling sealing ring.
- the present invention provides a rotating device and a rotor type compressor and a fluid motor using the same.
- a turning device comprises: a cylinder body; a front end cover and a rear end cover, sealingly connected to the front end and the rear end of the cylinder body, which together with the cylinder body define a cylindrical inner cavity; the main shaft, the cylinder body and/or the front and the rear
- the end cap is rotatably supported, partially located in the cylindrical inner cavity, the central axis of which coincides with the central axis of the cylinder;
- the eccentric rotor assembly is sleeved on the portion of the main shaft located in the cylindrical inner cavity, comprising: an eccentric shaft,
- the central axis of the main shaft is offset from the central axis of the main shaft by a predetermined position;
- the rolling piston wheel is sleeved on the eccentric shaft, and the central axis thereof coincides with the central axis of the eccentric shaft; at least one
- the rolling bearing is symmetrically sleeved on the eccentric shaft, the inner ferrule is fixed to the eccentric shaft, and
- a rotor compressor is also provided.
- the rotor type compressor includes the above rotating device, wherein: the first chamber communicates with the low pressure compressed medium input port through the first group of through holes; the second chamber passes through the second group of through holes and the compressed high pressure compressed medium discharge port
- the main shaft communicates the torque outside the cylindrical inner cavity into the cylindrical inner cavity, and compresses the compressed medium through the eccentric rotor assembly.
- a fluid motor is also provided.
- the fluid motor includes the above rotating device, wherein: the second chamber communicates with the high pressure fluid inlet through the second set of through holes; the first chamber communicates with the low pressure fluid outlet through the first set of through holes; the high pressure fluid pushes the eccentric rotor to rotate The torque generated by the main shaft is transmitted to the outside of the cylindrical cavity.
- the rotating device of the present invention and the rotor compressor and the fluid motor using the same have the following beneficial effects:
- Rolling bearings are used between the eccentric shaft and the rolling piston wheel. After the rolling bearing is used, the rotor compressor achieves no oil or less oil (ie oil lubrication in a small area), thus overcoming the lubrication due to heavy use. Many shortcomings caused by oil, the rotating device can be applied in the field of large compressors and air compressors;
- the balance weight scheme is adopted to reduce the momentum imbalance caused by the eccentric rotation of the rotating device.
- the rotor compressor designed by the rotor momentum balance is more in line with the precision engineering principle, and the vibration is small and the noise is low;
- the rotary valve body reset pin is constructed as a conventional pressure cylinder, or a more powerful, more stable, more precise and longer-life pneumatic component is used to control the swing of the rotary valve body, ensuring reliable operation of the entire rotating device. Sex and maintenance convenience;
- FIG. 1 is a schematic structural view of a prior art rotor compressor
- FIG. 2A is a schematic longitudinal sectional view of a rotor type compressor according to an embodiment of the present invention
- Figure 2B is a cross-sectional view of the rotor compressor of Figure 2A taken along line A-A;
- Figure 3 is a partial right side elevational view of the eccentric rotor assembly of the rotor compressor of Figure 2A;
- Figure 4 is a perspective view of a portion of the eccentric rotor assembly of the rotor compressor of Figure 2A;
- Figure 5A is a rotor compression in accordance with an embodiment of the present invention.
- 5B is a schematic view showing a second assembly manner of a 0-type elastic rubber ring in a rotor type compressor according to an embodiment of the present invention
- Figure 5C is a schematic view showing the assembly of a rectangular elastic rubber ring in a rotor type compressor according to an embodiment of the present invention
- 6A is a schematic view of a spring piece ferrule in an eccentric rotor assembly of a rotor compressor according to an embodiment of the present invention
- Figure 6B is a schematic view showing the assembly of the spring piece ferrule shown in Figure 6A;
- FIG. 7A is a left side view of an eccentric rotor assembly in a rotor type compressor according to an embodiment of the present invention
- FIG. 7B is a schematic view of an eccentric rotor assembly in a rotor type compressor according to an embodiment of the present invention
- FIGS. 8A and 8B are views of an embodiment of the present invention The schematic diagram of the second rotary valve body in the rotor type compressor isolation mechanism in the pressed state and the extended state respectively;
- Figure 9 is a perspective view of a third type of rotary valve body in the rotor type compressor isolation mechanism according to the present invention
- Figures 10A and 10B are schematic views of the rotary valve body shown in Figure 9 in a pressed state and an extended state, respectively;
- 11A is a schematic structural view of a second type of rotary valve body reset mechanism in a rotor type compressor isolation mechanism according to an embodiment of the present invention
- 11B is a schematic structural view of a third rotary valve body reset mechanism in a rotor type compressor isolation mechanism according to an embodiment of the present invention
- FIGS. 12A-12E are schematic views showing the operation of a rotor type compressor according to an embodiment of the present invention.
- Fig. 13 is a cross-sectional view showing a fluid motor according to an embodiment of the present invention.
- 351-0 type elastic rubber ring 352-ratio elastic rubber ring;
- the present invention provides a rotating device and a rotor compressor and a fluid motor using the same.
- a rolling bearing is adopted between the eccentric shaft and the rolling piston wheel, and the cylinder is reliably sealed by the elastic pre-tightening element, and the vibration and noise problems of the rotor compressor are overcome by the balance weight, thereby avoiding
- the use of lubricating oil has increased the size of the compressor.
- a new rotary valve body reset mode is provided, and the rotary valve body is improved to ensure the overall operational reliability of the rotary device and the rotor compressor and fluid motor to which it is applied.
- the present invention provides a turning device comprising: a cylinder block, a front/rear cover, a main shaft, an eccentric rotor assembly, and an isolating mechanism.
- a turning device comprising: a cylinder block, a front/rear cover, a main shaft, an eccentric rotor assembly, and an isolating mechanism.
- the cylinder body and the front/rear cover on the front/rear sides thereof define a cylindrical inner cavity.
- the main shaft is supported by the cylinder or its front/rear cover, partially within the cylindrical inner chamber, the central axis of which coincides with the central axis of the cylinder.
- the eccentric rotor assembly is disposed on the portion of the main shaft located in the cylindrical inner cavity, and comprises: an eccentric shaft disposed on a portion of the main shaft located in the cylindrical inner cavity, wherein a central axis thereof is parallel to the central axis of the main shaft and is offset by a preset distance; a rolling piston wheel is sleeved on the eccentric shaft, the central axis of which coincides with the central axis of the eccentric shaft; at least one rolling bearing is symmetrically sleeved on the eccentric shaft, the inner ferrule is fixed to the eccentric shaft, and the outer ring is fixed to the rolling a piston wheel to isolate the rotation of the two, the pre-tightening elastic force between the at least one rolling bearing and the rolling piston wheel presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity, so that the cylindrical inner cavity
- the inner cylindrical surface and the outer cylindrical surface of the rolling piston wheel form an axially extending sealed chamber.
- the isolation mechanism divides the sealed chamber into mutually independent first chamber
- the rotating device can be applied to a fluid machine such as a compressor or a fluid motor.
- a fluid machine such as a compressor or a fluid motor.
- the settings of the suction through hole and the discharge port are as follows:
- the first chamber communicates with the low-pressure compressed medium input port through the first group of through holes;
- the second chamber passes through the second group of through holes and the compressed high-pressure compressed medium
- the mass discharge port is connected;
- the main shaft transmits the torque outside the cylindrical inner cavity into the cylindrical inner cavity, and compresses the compressed medium through the eccentric rotor assembly;
- the second chamber communicates with the high pressure fluid inlet through the second set of through holes;
- the first chamber communicates with the low pressure fluid outlet through the first set of through holes;
- the eccentric rotor rotates, and the torque generated by the main shaft is transmitted to the outside of the cylindrical inner cavity.
- the number of the through holes in each set of through holes may be one or plural.
- the rolling bearing may be a roller bearing, a ball bearing, a needle bearing, an aerodynamic rolling bearing or a composite bearing.
- the number of rolling bearings is one, but is preferably one set, two sets, three sets, and four sets, and each set includes two rolling bearings symmetrically disposed left and right along the cylindrical inner cavity. Symmetry herein refers to symmetry with respect to a plane that is at the center of the cylindrical inner cavity portion and perpendicular to the central axis of the main shaft.
- Fig. 2A is a schematic longitudinal sectional view of a rotary compressor in accordance with an embodiment of the present invention.
- Figure 2B is a cross-sectional view of the rotor compressor of Figure 2A taken along line A-A.
- the rotor compressor of the present embodiment includes: a cylinder block 110, a front end cover 120/rear end cover 130, a main shaft 200, an eccentric rotor assembly 300, and an isolation mechanism 400. The individual components are described in detail below.
- the cylinder block 110 and the front end cover 120/rear end cover 130 on the front and rear sides thereof define a cylindrical inner cavity.
- the cylindrical inner chamber is the cylinder of the compressor, and the cylinder has a radius of R2 and a height of H.
- the cylinder block 110 includes a cylinder main body 111, and a front cylinder head 112 and a rear cylinder head 113 which are respectively disposed at front/rear end faces of the cylinder main body 111.
- a cylinder head 140 is provided at a predetermined position outside the cylinder main body 111, generally upward.
- the rotary valve body of the subsequent isolation mechanism and its reset mechanism are all set to the position of the cylinder head 140, which will be described in detail below.
- the main shaft 200 is supported by the front and rear cylinder heads (112 and 113) of the cylinder, and its central axis coincides with the central axis of the cylindrical inner chamber, and has a diameter of zero.
- the first portion of the main shaft 200 is located outside the cylindrical inner cavity, is connected to the external power source, and transmits the torque input from the external power source to the cylindrical inner cavity; the second portion is located in the cylindrical inner cavity, using external power Source input torque drives eccentric rotor set
- the piece 300 rotates.
- a spindle bearing 210 is disposed between the spindle 200 and the front and rear cylinder heads (112 and 113), respectively.
- the spindle bearing 210 is preferably a high-capacity, long-life, high-precision tapered roller bearing to ensure that the gap between the rotor side and the cylinder head surface is precisely controlled.
- the position of the spindle bearing 210 is locked by the bearing lock nut 211.
- a main shaft seal ring 212 is provided therebetween.
- a front end cap sealing rubber ring 121 is disposed between the two; in order to achieve a seal between the rear end cover and the rear cylinder head, a rear end cap seal is provided between the two Apron 131.
- main shaft 200 is rotatably supported by the front cylinder head 112 and the rear cylinder head 113 in this embodiment, it may be rotatably supported by the front/rear end cover. Further, although in the present embodiment, only one end of the main shaft extends beyond the cylindrical inner cavity, the present invention also includes the case where both ends of the main shaft extend out of the cylindrical inner cavity, and torque is simultaneously input from the left and right sides. It should be clear to those skilled in the art how to implement the above technical solutions, and details are not described herein again.
- the eccentric rotor assembly 300 is located within the cylindrical inner chamber described above.
- Figure 3 is a partial right side elevational view of the eccentric rotor assembly 300 of the rotor compressor of Figure 2A.
- Figure 4 is a perspective view showing a portion of the eccentric rotor assembly of the rotor type compressor shown in Figure 2A.
- the eccentric rotor assembly includes: an eccentric shaft 310 disposed on the second portion of the main shaft 200 in the cylindrical inner cavity, the central axis of which is parallel to the central axis of the main shaft 200 and is staggered.
- the rolling piston wheel 330 is sleeved on the eccentric shaft 310, and its central axis coincides with the central axis of the eccentric shaft 310, and has a radius R1; at least one rolling bearing 320 is symmetrically sleeved on the eccentric shaft 310.
- the ferrule is fixed to the eccentric shaft 310, and the outer ring is fixed to the rolling piston wheel 330 to isolate the rotation of the two.
- the pre-tightening elastic force between the rolling bearing and the rolling piston wheel presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity, and the inner cylindrical surface of the cylindrical inner cavity and the outer cylinder of the rolling piston wheel
- the face forms an axially extending sealed chamber.
- the magnitude of the eccentricity e of the eccentric shaft 310 depends on factors such as the displacement of the compressor and the fluid pressure. For example, when the displacement is 53 cc and the pressure is IMPa, 4.5 mm can be taken. The larger the displacement, the more the eccentricity e is. Big.
- the spindle 200 drives the eccentric shaft 310 to rotate. Then, under the driving of the eccentric shaft 310, the rolling piston wheel 330 revolves in a manner of rolling along the inner cylindrical surface of the cylinder while revolving along the central axis of the main shaft, the rotation of the rolling piston wheel 330 and the eccentric shaft 310 Rotating by rolling bearing
- the rolling bearing 320 as described above may be a roller bearing, a ball bearing, a needle bearing, an aerodynamic rolling bearing or a composite bearing, preferably a ball bearing.
- two symmetrical (ie, one set) rolling bearings 320 are disposed between the eccentric shaft 310 and the rolling piston wheel 330.
- the rolling bearings can be designed as needed. If the axial distance of the cylindrical inner cavity, that is, the height H of the cylinder, is large, the rolling bearing can be two sets of symmetrical, 3 groups or 4 groups, two in each group. Of course, the rolling bearing may also be one having a larger cross-sectional area, but it should also be symmetrically disposed left and right along the cylindrical inner cavity.
- the rotor compressor By using the contemporary rolling technology of the rotor compressor which is mass-produced by mature industrial technology and is still in the process of rolling forward, it is possible to reduce the friction energy consumption and improve the energy efficiency by rolling friction instead of sliding friction; and after using the rolling bearing, the rotor compressor is It is expected to achieve no oil or less oil (ie, oil lubrication in a small area), and it is expected to overcome many shortcomings caused by the large use of lubricating oil, and it is applied in large compressors and air compressors.
- oil or less oil ie, oil lubrication in a small area
- the experience of mechanical design tells us that the adjacent moving surface can have good air tightness under the gap of 0.01 ⁇ 0.03mm.
- the most ideal low-cost, high-quality basic sealing condition is: no sliding between the moving surfaces, so there is no gap, and even Micro interference fit to achieve zero leakage.
- the rolling piston wheel and the inner wall of the cylinder body The pre-tightening design is used to achieve the best seal.
- the control target of the rolling piston wheel and the cylinder sealing gap in the rotor compressor is that the rolling piston wheel must have zero sealing gap ⁇ at the contact point when rolling along the inner wall of the cylinder.
- the sealing gap is ⁇ ;
- the cylinder inner cylinder radius is R;
- the outer cylinder radius of the rolling piston wheel is r;
- the eccentric amount of the rolling piston wheel and the center of the cylinder is e;
- the radial clearance of the rolling piston wheel support bearing is ⁇ .
- the above parameters should be measured in advance and matched. Due to the cylinder radius R of the cylinder wall, the eccentricity of the rolling piston wheel and the center of the cylinder (ie the eccentric radius of the crankshaft) e, the radial clearance of the rolling bearing, once the machining is not well corrected, the rolling is usually adopted.
- the outer cylinder radius r of the piston wheel is modified and adjusted.
- control target of the rolling piston wheel and the cylinder seal gap of the rotor type compressor may be an interference fit, that is, the seal gap ⁇ is less than zero. This means that the pre-tightening is applied at the contact point of the rolling piston wheel and the cylinder to produce a microscopic elastic deformation, and the resulting air gap seal can be extended from the line to the surface.
- the pre-tightening pressure can not be too large (about 1 ⁇ ⁇ ), can not exceed the allowable elastic range of the assembly size chain system, and can not cause the permanent deformation of the assembly size chain system;
- the micro-elastic deformation caused by the pre-tightening pressure can automatically compensate the friction loss deformation, and ensure that the sealing gap between the rolling piston wheel and the cylinder of the rotor compressor is not greater than zero. Control target.
- the manufacturing site often imposes too severe precision requirements on the radial assembly dimensions of the various components that make up the eccentric rotor.
- the pre-tightening elastic force between the rolling bearing 320 and the rolling piston wheel 330 presses the rolling piston wheel against the inner cylindrical surface of the cylindrical inner cavity to achieve sealing of both.
- the pre-tensioning force can result from an interference fit between the rolling bearing 320 and the rolling piston wheel 330.
- the interference fit is too large, there is a possibility that the rotor compressor may not operate smoothly.
- One or more inlaid grooves are symmetrically distributed in the radial center line of the groove, and an elastic pretensioning element is disposed in the setting groove, and the height of the elastic pretensioning element in a normal state is greater than the depth of the inlay groove to realize the rolling piston wheel Pre-tightening pressure between the inner cylindrical surface of the 330 and the outer cylindrical surface of the rolling bearing 330.
- the elastic pretensioning element is also capable of absorbing and compensating for errors on its own.
- the elastic pretensioning element can adopt a wide-type 0-type elastic rubber ring 351 with a sealing pressure of 1.33 X 10 - 5 Pa to 400 MPa (movable seal up to 35 MPa).
- the material of the 0-type elastic rubber ring is preferably fluororubber.
- the fluororubber has good elastic force, wear resistance and pressure resistance, and its continuous use temperature can reach 210 °C.
- Fig. 5A is a schematic view showing the first assembling manner of the 0-type elastic rubber ring in the rotor type compressor according to the embodiment of the present invention.
- a plurality of inlaid grooves are formed in the inner cylindrical surface of the rolling piston wheel, and the axial positions of the plurality of inlaid grooves are symmetric and evenly distributed with respect to the radial center line of the rolling bearing (steel ball) groove of the rolling bearing.
- a plurality of 0-type elastic rubber rings 351 can be embedded in the mounting groove.
- the outer cylindrical surface of the rolling bearing compresses the 0-type elastic rubber ring 351 to generate an elastic deformation, and the outer cylindrical surface of the rolling piston wheel 330 is tightly pressed against the inner cylindrical surface of the cylinder body, thereby realizing Zero clearance seal for preload.
- the rolling bearing outer ring is pre-tensioned by the 0-type elastic rubber ring 351 to the inner cylindrical surface of the rolling bearing installation positioning, which is floating relative to the center position of the piston wheel bearing mounting positioning inner cylindrical surface, so it is required to be disposed between them There is enough clearance ⁇ to compress the 0-type elastic rubber ring.
- the inner diameter ⁇ of the piston roller installed and positioned by the rolling bearing must be larger than the outer diameter of the rolling bearing ring.
- the size of the clearance ⁇ depends on the bearing size, and its value ranges from 0.1 to 1 mm. .
- the correction of the outer cylinder radius r of the rolling piston wheel is usually carried out to ensure that the sealing gap ⁇ at the contact point of the rotor is zero when the rotor rolls along the inner wall of the cylinder.
- the 0-type elastic rubber ring is used to pre-tighten the rolling piston wheel, there is a gap ⁇ between the outer cylindrical surface of the rolling bearing outer ring and the cylindrical surface of the rolling bearing installation positioning. At this time, the radial clearance of the rolling piston wheel supporting the rolling bearing is zero.
- the sealing gap is ⁇ ;
- the cylinder inner cylinder radius is R;
- the outer cylinder radius of the rolling piston wheel is r;
- the amount of eccentricity of the rolling piston wheel and the center of the cylinder is e;
- the outer cylinder radius r of the rolling piston wheel is pre-incremented to ⁇ .
- the reaction force of the compression deformation of the 0-type elastic rubber ring is proportional to the variation of the gap ⁇ ⁇ , and has the following mathematical expression:
- the ⁇ value must be correctly selected through practical experience. While ensuring that the sealing gap ⁇ is zero, it is necessary to make the outer cylinder of the rolling piston wheel face the cylindrical surface of the cylinder inner wall at a moderate contact point. Elastic preloading pressure can be used to avoid excessive preloading.
- Figure 5 is a schematic view showing a second assembly mode of a 0-type elastic rubber ring in a rotor type compressor according to an embodiment of the present invention.
- the assembly method of the 0-type elastic rubber ring in Fig. 5 ⁇ is similar to that of Fig. 5 ⁇ , except that the inlaid groove is opened on the outer cylindrical surface of the rolling bearing outer ring, and the working principle is the same as that of the elastic rubber ring shown in Fig. 5 ⁇ . It will not be repeated here.
- the sectional size is the key to the design.
- three key conditions are met:
- the rotor system is transmitted through a 0-type elastic rubber ring to a suitable elastic preloading pressure at the contact of the outer cylindrical surface of the rolling piston wheel with the cylindrical surface of the cylinder inner wall;
- the cross-sectional diameter of the 0-type elastic rubber ring should be large enough.
- the contact area between the 0-type elastic rubber ring and the rolling bearing of the rolling piston wheel should be large enough to satisfy the system's soft elasticity. Absorb vibration and noise.
- the cross-sectional area of the 0-type elastic rubber ring is large enough to have sufficient fatigue strength and no permanent Deformation.
- expansion-compensated deep groove ball bearing anti-slip bearing
- AC bearing anti-slip bearing
- the cross-sectional shape of the elastic rubber ring can also be designed as a rectangle or other shape that is advantageous for satisfying the appropriate elastic preload pressure, absorbing vibration and noise, and having sufficient fatigue strength and prolonged service life, one of which is A rectangular elastic toothed rubber ring 352 as shown in Fig. 5C.
- the above-mentioned 0-type or rectangular elastic rubber ring may be softened or destroyed by heat after long-term operation under repeated high-frequency impact pressure, so it is considered to be more heat-resistant.
- High-strength elastic materials such as: elastic rings made of multi-strand fine wire mesh, or metal spring rings, etc., the metal is preferably alloy steel or other elastic metal material.
- the metal spring ferrule includes: a spring piece with a continuous U-shaped smooth arc curved surface, and a rigid base edge supporting the spring piece.
- the rigid base edge As shown in FIG. 6B, a groove is formed in the inner cylindrical surface of the rolling piston wheel, and the center line of the groove coincides with the center line of the rolling bearing.
- the metal spring ring 353 with a U-shaped smooth arc curved surface is assembled in the above-mentioned mosaic. Inside the slot.
- the diameter of the rigid base rim of the metal spring ferrule 353 can be elastically reduced, it can be pre-inlaid into a rectangular groove in which the rolling bearing is mounted and positioned on the inner cylindrical surface to complete the positioning, and after the lubricant is applied, it can be easily Press the rolling bearing outer ring into the assembly. Due to the stamping process, metal spring ferrules are easy to mass-produce, ensuring quality and reducing costs.
- the outer cylindrical surface of the rolling bearing compresses the elastic pretensioning element to generate an elastic deformation force
- the rolling piston is The outer cylindrical surface of the wheel is pressed tightly against the inner cylindrical surface of the cylinder, regardless of the accuracy of the radial assembly dimensions of the various parts constituting the eccentric rotor assembly, and regardless of the radial rotation of the eccentric rotor assembly Any deviations can be randomly absorbed by the elastic deformation of the elastic pretensioning element to ensure a zero gap seal with elastic preload. Therefore, not only can the goal of good and reliable sealing quality of the compressor eccentric rotor assembly be achieved, but also the excessively demanding precision requirements for the radial assembly dimensions of the various components constituting the eccentric rotor assembly can be avoided, and the cost can be reduced.
- an eccentric shoulder 311 is provided at the position where the eccentric shaft is sleeved with the rolling bearing, as shown in FIG.
- the portion of the eccentric shaft other than the eccentric shoulder 311 can be saved to balance the weight, and the specific balance weight method is as follows.
- the balance block 340 is symmetrically disposed along the eccentric axis between the two eccentric shoulders.
- the size and weight of the weight 340 depends on the volume and eccentricity of the cylindrical cavity.
- the present invention provides an additional plurality of balancing weights.
- the weight 341 in the eccentric rotor assembly is no longer a separate piece, but is a curved balance weight region that is connected to the lighter side of the eccentric shaft, as shown in Fig. 7A. .
- This type of counterweight is easy to manufacture and has a good balance.
- the eccentric rotor assembly adopts a weight notch 342 on the heavier side of the eccentric shaft to reduce the weight here, thereby achieving balance during the rotation of the eccentric shaft, as shown in Fig. 7B. Show.
- the invention utilizes the use of a rolling bearing to design a weight structure that is possible to balance the rotor momentum between two symmetrically arranged rolling bearing span spaces.
- the use of a balanced weighting scheme alleviates the problem of momentum imbalance caused by the eccentric rotation of the rotor compressor, and is more in line with the principles of precision engineering.
- the rotor type compressor designed by the rotor momentum balance is of course small in vibration and low in noise.
- the position of the rolling bearing wheel is prevented from shifting during the rotation of the rolling piston wheel.
- the positioning of the inner and outer ring axial positions of the two rolling bearings fixed on the eccentric rotor assembly of the compressor belongs to the pre-tightening position, and the rolling piston wheel is adopted.
- the inner cylindrical surface and the positioning shoulder on the eccentric spindle journal eliminate the axial clearance of the rolling bearing, so that the rolling bearing reduces the axial sway during the rotation.
- the positioning of the rolling piston wheel can be either of the following two:
- the axial position of the inner ring of the two rolling bearings fixed on the inner cylindrical surface of the rolling piston wheel is set by the shoulder provided on the eccentric spindle journal and the spindle journal.
- the bearing compression washer 331 is completed.
- the shoulder shoulders respectively support the inner ring of the bearing from the inner side between the two rolling bearings; the outer side of the inner ring of the rolling piston bearing is pressed and positioned from the two sides of the cylinder by the bearing pressing gasket, thereby realizing the
- the inner rings of two or more rolling bearings are axially positioned.
- the outer ring of the two rolling bearings is positioned by applying a pressure to the inner side of the outer ring by the shoulder provided in the middle of the cylindrical surface of the rolling piston wheel.
- the axial position of the inner ring of the two rolling bearings fixed on the inner cylindrical surface of the rolling piston wheel is completed by a shoulder provided on the eccentric spindle journal, and the shoulders are respectively from two
- the inner side between the rolling bearings bears against the inner ring of the bearing; and the outer ring of the two rolling bearings is positioned, and the shoulder provided at the left end of the cylindrical surface of the rolling piston wheel applies pressure to the side of a bearing outer ring which is in close contact
- the outer side of the outer ring of the other bearing is inwardly locked by a bearing snap ring 325 disposed in the groove at the right end of the cylindrical surface of the rolling piston wheel.
- the positioning method of the rolling bearing of the rotor compressor of the present invention is not limited to the above two types, and other positioning methods are also conceivable by those skilled in the art based on the above description.
- a side sealing piece 321 is provided.
- the sealing sheet elastic rubber ring 322 in the front (rear) cylinder head is pressed against the outer side of the side sealing piece 321 with an appropriate pressure to prevent leakage.
- the lateral sealing sheet 321 may be made of a friction-reducing alloy or a polytetrafluoroethylene (PTFE) material.
- the isolation mechanism 400 divides the axially extending sealed chamber formed by the inner cylindrical surface of the cylinder and the outer cylindrical surface of the rolling piston wheel into a first chamber and a second chamber.
- the first chamber is a suction chamber 430 that communicates with the low pressure compressed medium input port through the suction through hole 401;
- the second chamber is a compression chamber 440, that is, a high pressure chamber, which passes through the discharge through hole 402 is in communication with the discharge port of the compressed high pressure compressed medium.
- the main shaft 200 transmits torque outside the cylindrical inner cavity into the cylindrical inner cavity, and the compressed medium is compressed by the eccentric rotor assembly.
- an opening and closing valve 427 is provided between the discharge through hole 402 and the high pressure compressed medium discharge port 404.
- the opening and closing valve 427 can be opened only when the air pressure of the discharge through hole 402 reaches a predetermined pressure threshold, thereby outputting the compressed compressed medium to the high pressure compressed medium discharge port.
- the on-off valve 427 is always closed when the air pressure of the discharge through hole 402 does not reach the preset pressure threshold.
- the isolation mechanism 400 includes a rotary valve body 410 and a rotary valve body reset mechanism.
- the rotary valve body is preferably a sheet-like structure, that is, a rotary valve piece, and may be a semicircular structure as shown in Fig. 1 or the like.
- other types of valve bodies and their corresponding reset mechanisms can be used, such as: gate valves, etc., refer to the applicant.
- the previously applied patent Patent Application No.: 201110322746.0
- the manner of which it is installed is well known to those skilled in the art, and will not be described in detail herein.
- the position of the cylinder main body 111 corresponding to the cylinder head 140 is formed with an axially extending receiving recess that opens toward the cylindrical inner cavity.
- the rotary valve body 410 is fitted in the receiving recess and rotatably supported by the slot, so that the rotary valve body 410 swings within a predetermined angular range.
- the eccentric rotor assembly is rotated to the upper position, the rotary valve body 410 is pressed into the receiving recess and is pressed into the state.
- the eccentric rotor assembly is rotated to the lower position, the rotary valve body swings to its maximum position and is in an extended state.
- the end of the rotary valve body is always pressed against the outer cylindrical surface of the rolling piston wheel, thereby isolating the first chamber from the second chamber.
- the chamber facing the front side is a second chamber, that is, a compression chamber 440, which communicates with the compressed high-pressure compressed medium discharge port 404 through the discharge through-hole 402;
- the chamber facing the back of the rotary valve body is a first chamber, that is, a suction chamber 430,
- the suction through hole 401 is in communication with the low pressure compressed medium input port.
- the eccentric motion of the rolling piston wheel is a 360-degree process of continuously driving the cam for the rotary valve body.
- the cam's angle of elevation is small. Therefore, the small torque input by the spindle can generate a great thrust to the rotary valve body, and the effect of compressing the high-pressure gas (liquid) body can be achieved, and at the same time, the head of the rotary valve is always kept pressed against the outer cylindrical surface of the rolling piston wheel. Sealed on top.
- the rotary valve body 410 is fitted in the receiving recess, and is rotatably supported by the receiving recess, and includes: a connecting portion located at a root of the rotary valve body and hinged with the receiving recess; The body of the rotary valve body is oscillated within a predetermined angle range with the connecting portion as an axis.
- a sliding cylindrical hole having a circular arc notch is disposed in the receiving groove, and the circular arc notch of the sliding cylindrical hole communicates with the receiving groove.
- the connecting portion is a supporting cylinder.
- the support cylinder is inserted into the sliding cylinder bore and is constrained by the coating of the sliding cylinder bore.
- the rotary valve body has a support cylinder as an axis, and is free to swing between the pressed state and the extended state within a predetermined angle range.
- the angle of the arcuate notch of the sliding cylindrical hole is about 110°, and the corresponding body of the rotary valve body is swingable by more than 250°.
- the height of the supporting cylinder should be slightly shorter than the height H of the cylinder.
- the single-side clearance is preferably about 0.01 mm.
- the movement is flexible and leak-free, and the matching surface of the supporting cylinder and the sliding cylindrical hole should be lubricated, such as adding lubricant, or
- the surface of the supporting cylinder is plated with polytetrafluoroethylene (PTFE).
- PTFE polytetrafluoroethylene
- the rotary valve body 410 can also adopt the mandrel structure in the patent application (Patent Application No. 201010196950.8) filed by the applicant of the present invention.
- the rolling cylinder method of the present embodiment eliminates the need for positioning holes in the cylinder head opening core, thereby greatly improving the ease of processing, simple assembly, improved accuracy, and reduced cost.
- a rolling wheel is further disposed at the head of the rotary valve body.
- the rolling wheel When the rotary valve body and the rolling piston wheel move relative to each other, the rolling wheel generates rolling, thereby minimizing the rotation of the rotary valve body and the rolling piston wheel. Friction between.
- the rolling piston wheel When the eccentric shaft rotates one revolution, the rolling piston wheel is pressed by the rolling bearing and elastically affixed to the inner wall of the cylinder without running for one week. Since the diameter of the cylinder is larger than the diameter of the rolling piston wheel, the rolling piston wheel is revolving. In one week, the bearing outer ring rotates for less than one week (the rotation direction is opposite to the revolution direction), which means that the rotary valve body head structure is in contact with the outer cylindrical surface of the rolling piston wheel. The relative sliding speed at the point can be greatly reduced, which is particularly advantageous for sealing.
- the present invention provides additional plurality of rotary valve body head configurations.
- FIGS. 8A and 8B are schematic views of the second rotary valve body in the press-in state and the extended state, respectively, in the rotor type compressor isolation mechanism according to the embodiment of the present invention.
- the rotary valve body 410' shown in Figs. 8A and 8B the rotary valve body is entirely made of a friction reducing material, or is coated with a friction reducing material on its surface.
- the antifriction material may be SiN ceramic, polytetrafluoroethylene, bronze alloy or the like.
- Figure 9 is a perspective view of a third type of rotary valve body in a rotor type compressor isolation mechanism according to the present invention.
- 10A and 10B are schematic views of the rotary valve body of Fig. 9 in a pressed state and an extended state, respectively.
- the rotary valve body 410 further includes: a swing sealing slider 411.
- the head of the oscillating sealing sliding head has a cylindrical shape and is slidably wrapped to restrict positioning in a sliding cylindrical hole at the end of the body of the rotary valve body.
- the contact surface of the swing sealing slider 411 and the rolling piston wheel 330 is a sealing arc surface which is in close contact with the rolling piston wheel 330 and which is slidable on the surface of the rolling piston wheel 330.
- Figure 10A shows the situation when the rolling piston wheel is rotated to the highest position of the cylinder. At this time, the rotary valve body and the swing seal slider 411 which is fitted to the head of the rotary valve body are retracted into the cylinder recess.
- Figure 10B shows the situation when the rolling piston wheel roller is rotated to the lowest position of the cylinder block. At this time, the rotary valve body and the swinging sealing sliding head 411 embedded in the head of the rotary valve body are under the thrust of the valve plate reset pin, from the cylinder block.
- the groove is unscrewed counterclockwise, and the oscillating sealing slide 411 is always pressed against the outer cylindrical surface of the planetary piston roller.
- the arc-shaped sealing effect of the bottom surface of the oscillating sealing sliding head and the outer cylindrical surface of the planetary piston roller is better.
- the load pressure can be dispersed to the utmost extent.
- the oscillating sealing sliding head 411 may be made of a suitable metal material such as tin bronze, beryllium bronze, tin phosphor bronze or the like, and may also be used to heat-harden engineering plastics such as polyphenol aldehyde and polytetrafluoroethylene.
- a surface of the oscillating sealing slider 411 and the outer cylindrical surface of the planetary piston roller are coated with a layer of Teflon plastic to reduce friction.
- a compressed gas-liquid passage 411a is provided at the head of the rotary valve body sealing slider 411,
- the compressed gas-liquid passage 411a can ensure that the compressed medium can smoothly enter the secondary compression chamber through the moment when the rotary valve body is about to enter the receiving recess.
- a shallow hydrostatic bearing pressure chamber 411b having a depth of between 0.1 mm and 2 mm is formed on the arcuate surface of the oscillating sealing slider 411.
- the gas-liquid fluid distributed in the hydrostatic bearing pressure chamber 411b acts like a lubricating oil, and the outer cylindrical surface of the swing sealing sliding head 411 and the rolling piston wheel 330 can be greatly reduced. The friction between.
- connection manner of the swing sealing sliding head and the rotary valve body is not limited to the above-mentioned rolling cylindrical type, and the same can also be adopted in the form of a pivoting connection, a mandrel, etc., as long as the swing sealing sliding head and the rotary valve body can be rotatably connected. It will not be described in detail.
- the reset mechanism is used to always press the rotary valve body to the outer cylindrical surface of the rolling piston wheel.
- the position of the side-rotating valve body is opened with a blind hole for the pin.
- the head of the reset pin 421 bears against the rotary valve body body 410 in the direction toward the rolling piston wheel, thereby realizing the reset sealing of the rotary valve body.
- the angle between the central axis of the blind hole of the pin and the perpendicular of the rotary valve body being pressed into the receiving recess is between 10 and 20, preferably 13, as shown in Fig. 2B.
- the contact point of the reset pin 421 with the rotary valve body is: The spin valve body is pressed against the end of the rolling piston wheel, and the rotary valve body is 1/5 to 1/2 of the length of the rotary valve body, preferably 2/5.
- the revolving motion of the rotary valve body is performed under the non-leakage sliding condition, and the reset pressure is transmitted to the rotary valve body head, thereby improving the service life of the return spring and the rotary valve body in the rotor compressor. And reliability.
- This design expands the design space of the rotary valve body reset mechanism, unlike the conventional rotor compressor, which is limited only to the narrow space of the support shaft core of the rotary valve body.
- the spring that is the power to reset the rotary valve body uses a compression spring that has been proven to be reliable. Since the pressure point applied by the rotary valve body reset pin is close to the rotary valve body head, the rotary valve body head (for example, the bottom surface of the roller or the swing seal sliding head) pressed against the outer cylindrical surface of the planetary piston roller can be more accurately ensured. The contact pressure achieves a long-life, reliable seal with minimal sliding friction.
- FIG. 11A is a schematic view showing the structure of a second type of rotary valve body reset mechanism in the rotor type compressor isolation mechanism according to the present invention.
- a nitrogen gas spring 423 is disposed in the pin hole, and the free end of the nitrogen gas spring abuts against the moving end of the reset pin 421, and is reset by the reset pin 421 against the rotary valve body to the outer cylindrical surface of the rolling piston wheel 430.
- the nitrogen gas spring has the characteristics of good sealing, high strength and long service life. As a standard part, it can be easily replaced once it is damaged.
- the pin hole may be a through hole, and the pin hole is sealed to the outside of the cylinder by the end of the gas spring 423.
- Figure 11B is a schematic view showing the structure of a third type of rotary valve body reset mechanism in a rotor type compressor according to an embodiment of the present invention.
- the compressed high pressure gas at the high pressure compressed medium discharge port 404 is introduced into the pin hole of the compression spring 425 above the valve plate reset pin by the high pressure gas passage 424.
- the high-pressure gas acts as an elastic member to ensure that sufficient gas pressure is applied to the reset pin 421, and the end of the rotary valve body is always sealed with the outer cylindrical surface of the rolling piston wheel 430.
- the compression spring 425 is only used to withstand the valve plate reset pin when there is no pressure in the high pressure cylinder.
- the compression spring 425 can be omitted under the premise that it can reliably withstand the valve reset pin even when there is no pressure in the high pressure cylinder.
- a pressure regulating device such as a one-way valve or a pressure regulating valve, is provided between the compressor high pressure compressed medium discharge port 404 and the high pressure gas passage 424, thereby ensuring a substantially constant pressure in the pin bore above the valve plate reset pin.
- the rotor type compressor of the present embodiment operates under the condition of sealing sliding by the rotary valve body reset pin, and transmits the reset pressure to the head of the rotary valve body, thereby improving the service life and reliability of the return spring in the rotor type compressor. Thereby providing a highly reliable and practical compressor.
- the suction stroke as shown in Fig. 12A, is located at the uppermost position of the cylindrical inner cavity, thereby completely pressing the rotary valve body into the receiving recess, and the pin is located at the innermost position of the pin hole.
- the diameter thereof is 0° with the vertical direction, and the compression chamber surrounded by the outer cylindrical surface of the rolling piston wheel and the inner cylindrical surface of the cylinder is the largest, and the compression chamber is connected with the suction port of the compressor, thereby Inhaling a gaseous compressed medium into the compression chamber;
- the first-stage compression stroke as shown in Fig. 12B, the eccentricity of the rolling piston wheel is sealed and rolled along the inner surface of the cylinder, and the compression is started after the suction port is passed.
- the rotary valve body is gradually opened first, and then slowly closed, correspondingly, the pin protrudes first in the pin hole and then retracts.
- the volume of the compression chamber becomes smaller and smaller.
- the rolling piston wheel is located at the lowest position of the cylindrical inner cavity. After this point, it reaches as shown in Fig. 12D. Position, the gas in the compression chamber is compressed and pressurized, and gradually enters the cylinder above the rotary valve body;
- the secondary compression stroke as shown in Fig. 12E, the outer circle of the eccentric roller and the inscribed point of the cylinder circle are at 270 degrees. At this time, the inscribed point position is close to the end position, and the eccentricity of the rolling piston wheel is sealed along the inner surface of the cylinder.
- the rotary valve body is quickly closed, the high-pressure gas blows the one-way shut-off valve piece, and the gas is compressed and pressurized to enter the cylinder above the rotary valve body, and is further squeezed into the high-pressure gas storage chamber by the rotary valve body.
- the end position is as shown in Fig. 12A, that is, the position where the rotary valve body returns to the cylinder groove. At this time, the fluid retained in the so-called secondary compression chamber (high pressure chamber) is all pushed into the high pressure gas storage chamber, and is down. The time period is intercepted by the one-way stop valve shown in Fig. 2B.
- FIG. 13 is a schematic cross-sectional view of a fluid motor in accordance with an embodiment of the present invention.
- the second chamber of the rotating device that is, the working chamber 530, communicates with the high pressure fluid inlet 510 through the second set of through holes; the first chamber, that is, the discharge chamber 540, passes through the first group of through holes and the low pressure.
- the fluid outlets 520 are in communication.
- the high pressure fluid pushes the eccentric rotor to rotate, and the torque generated by the main shaft is transmitted to the outside of the cylindrical cavity.
- the high pressure fluid can be a liquid or a gas.
- the working flow of the fluid motor of the present embodiment will be described below.
- the high pressure fluid flows from the high pressure fluid inlet 510, enters the working chamber through the second set of through holes, and drives the eccentric rotor 300 assembly to rotate and revolve in the counterclockwise direction.
- the eccentric rotor assembly 300 The revolution rotates the spindle 200; after the eccentric rotor assembly passes its uppermost end, it enters the next stroke, and the fluid after the work flows out through the first set of through holes to the low pressure fluid outlet 520.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Hydraulic Motors (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/762,609 US10215025B2 (en) | 2013-01-25 | 2014-01-21 | Rotation device and rotor compressor and fluid motor having the same |
JP2015554035A JP2016505769A (ja) | 2013-01-25 | 2014-01-21 | 回動装置及びそれを用いたロータリー圧縮機ならびに流体モータ |
EP14743623.2A EP2942524B1 (en) | 2013-01-25 | 2014-01-21 | Rotating device and rotor compressor using same, and fluid motor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201310030773.XA CN103967787B (zh) | 2013-01-25 | 2013-01-25 | 转动装置及应用其的转子式压缩机和流体马达 |
CN201310030773.X | 2013-01-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014114222A1 true WO2014114222A1 (zh) | 2014-07-31 |
Family
ID=51226931
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CN2014/070972 WO2014114222A1 (zh) | 2013-01-25 | 2014-01-21 | 转动装置及应用其的转子式压缩机和流体马达 |
Country Status (5)
Country | Link |
---|---|
US (1) | US10215025B2 (zh) |
EP (1) | EP2942524B1 (zh) |
JP (1) | JP2016505769A (zh) |
CN (1) | CN103967787B (zh) |
WO (1) | WO2014114222A1 (zh) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104594953A (zh) * | 2014-01-03 | 2015-05-06 | 摩尔动力(北京)技术股份有限公司 | 圆形缸轴向隔离流体机构及包括其的装置 |
CN109209817A (zh) * | 2018-11-20 | 2019-01-15 | 泉州苗亿自动化机械有限公司 | 一种静音无油空压机 |
CN110425136A (zh) * | 2019-07-29 | 2019-11-08 | 黄石东贝电器股份有限公司 | 低背压用无吸气止回阀的滚动转子式压缩机 |
CN113659759A (zh) * | 2021-08-19 | 2021-11-16 | 天津飞旋科技股份有限公司 | 电机 |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104632286A (zh) * | 2014-01-03 | 2015-05-20 | 摩尔动力(北京)技术股份有限公司 | 圆形缸径向隔离流体机构及包括其的装置 |
CN105443159B (zh) * | 2014-08-22 | 2019-01-08 | 北京星旋世纪科技有限公司 | 正反转可调的转动装置 |
CN104612963B (zh) * | 2014-12-15 | 2017-01-18 | 姚镇 | 适用于高压场景的转动装置及应用其的机械装置 |
CN104963860A (zh) * | 2015-06-09 | 2015-10-07 | 安庆卡尔特压缩机有限公司 | 旋转式空气压缩机 |
CN106468178B (zh) * | 2015-08-21 | 2018-06-08 | 北京星旋世纪科技有限公司 | 应用压动闸阀机构的转动装置、转动系统及流体机械 |
WO2017201895A1 (zh) * | 2016-05-25 | 2017-11-30 | 姚镇 | 转动系统及应用其的流体马达、压缩机、泵和发动机 |
CN107435628B (zh) * | 2016-05-25 | 2019-05-10 | 北京星旋世纪科技有限公司 | 定位密封组件及应用其的转动装置、转动系统和流体机械 |
WO2018027801A1 (zh) * | 2016-08-11 | 2018-02-15 | 姚镇 | 转动系统及应用其的流体马达、压缩机、泵和发动机 |
US10655303B2 (en) | 2016-08-05 | 2020-05-19 | Woodward, Inc. | Multi-axis rotary piston actuator |
US10563677B2 (en) | 2016-12-21 | 2020-02-18 | Woodward, Inc. | Butterfly rotary piston type actuator |
CN106768566B (zh) * | 2017-03-15 | 2023-05-05 | 广西大学 | 一种滚动活塞压缩机滑片与滑槽的摩擦力测量装置 |
CN111094764B (zh) | 2017-07-14 | 2022-06-24 | 伍德沃德有限公司 | 具有移动密封件承载件的无支承活塞 |
CN107642381A (zh) * | 2017-09-27 | 2018-01-30 | 重庆华稷新能源科技有限公司 | 一种滚动转子膨胀机或压缩机 |
CN108087251A (zh) * | 2017-12-26 | 2018-05-29 | 宁波新邦工具有限公司 | 一种转子式压缩空气生成装置 |
CN110131308B (zh) * | 2018-02-09 | 2022-08-19 | 舍弗勒技术股份两合公司 | 滑动轴承组件和滑动轴承的安装方法 |
CN109373944B (zh) * | 2018-12-04 | 2021-11-05 | 湖南大学 | 一种基于超声波的空气箔片轴承气膜厚度测量系统及方法 |
CN109654020A (zh) * | 2018-12-13 | 2019-04-19 | 宁波甬微集团有限公司 | 一种压缩机组件及其制备方法 |
BR102019001521A8 (pt) * | 2019-01-24 | 2023-04-04 | Manuel Exposito Carballada | Motor de combustão |
CN110345798A (zh) * | 2019-07-02 | 2019-10-18 | 宁波方太厨具有限公司 | 换热管、热交换器以及燃气热水器 |
CN110345797A (zh) * | 2019-07-02 | 2019-10-18 | 宁波方太厨具有限公司 | 换热管、热交换器以及燃气热水器 |
CN110439814A (zh) * | 2019-08-27 | 2019-11-12 | 黄石东贝电器股份有限公司 | 压缩机用滚动轴承转子组件 |
CN112360877B (zh) * | 2020-09-29 | 2022-03-29 | 中国石油大学(华东) | 一种机械密封加速试验减震装置及其控制方法 |
CN112431861A (zh) * | 2020-11-24 | 2021-03-02 | 温州匡乐步网络科技有限公司 | 一种防止润滑油凝固的中央空调用智能保养装置 |
CN113027760B (zh) * | 2021-03-25 | 2022-08-16 | 北京旋环科技有限公司 | 一种用于空气压缩机的轴式固定活塞及其空气压缩机 |
FR3131762B1 (fr) * | 2022-01-10 | 2023-12-29 | Skf Svenska Kullagerfab Ab | Dispositif de palier à isolation électrique intégrée, notamment pour moteur ou machine électrique |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3639943A1 (de) * | 1985-11-27 | 1987-06-25 | Barmag Barmer Maschf | Fluegelzellenpumpe |
JPH08219034A (ja) * | 1995-02-08 | 1996-08-27 | Nissin Kogyo Kk | ベーンポンプ |
JP2005127306A (ja) * | 2003-10-03 | 2005-05-19 | Hitachi Ltd | 車載用ロータリ圧縮機 |
KR100819948B1 (ko) * | 2007-04-16 | 2008-04-08 | 김진수 | 캠 플레이트형 회전 압축기 |
JP2011174439A (ja) * | 2010-02-25 | 2011-09-08 | Nsk Ltd | ロータリコンプレッサ |
Family Cites Families (44)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1379785A (en) * | 1918-09-16 | 1921-05-31 | Shockley Motor Company | Pump |
US1363451A (en) * | 1919-04-28 | 1920-12-28 | G A Coats Machine Company | Rotary pump |
US1348434A (en) * | 1919-10-31 | 1920-08-03 | Oliver J Marshick | Adapter for electrode-holders |
US1491262A (en) * | 1922-03-17 | 1924-04-22 | Philip R Hatton | Rotary pump |
US1698815A (en) * | 1924-04-29 | 1929-01-15 | Joseph F Jaworowski | Duplex rotary pump |
US1660183A (en) * | 1926-10-21 | 1928-02-21 | Ella M Freeman | Rotary pump |
US1758298A (en) * | 1929-05-06 | 1930-05-13 | John B Teesdale | Rotary pump |
DE1425025A1 (de) * | 1963-06-26 | 1968-12-05 | Geraetebau Eberspaecher Ohg | Elastische Wellenabstuetzung |
US3837631A (en) * | 1972-05-08 | 1974-09-24 | Aeroquip Corp | Spring for composite sealing ring and method of manufacture |
JPS5020314A (zh) * | 1973-06-25 | 1975-03-04 | ||
FR2271443B2 (zh) * | 1974-01-23 | 1977-06-10 | Pitner Alfred | |
JPS5157353A (en) * | 1974-11-15 | 1976-05-19 | Makita Electric Works Ltd | Dendokogu niokeru jikukeno kanshosochi |
JPS5255008A (en) * | 1975-10-31 | 1977-05-06 | Oyahiro Okumura | Rotary compressors |
US4240677A (en) * | 1979-01-25 | 1980-12-23 | Payne Douglas L | Bearing mounting device and bearing |
US4239318A (en) * | 1979-07-23 | 1980-12-16 | International Telephone And Telegraph Corporation | Electrical connector shield |
US4375247A (en) * | 1980-08-18 | 1983-03-01 | Caterpillar Tractor Co. | Roller suspension |
JPS60127497A (ja) | 1983-12-14 | 1985-07-08 | 株式会社東芝 | 原子力発電プラントの復水移送装置 |
US4512623A (en) * | 1984-02-03 | 1985-04-23 | Allied Corporation | Electrical connector assembly having means for shielding electromagnetic interference |
JPS60127497U (ja) * | 1984-02-06 | 1985-08-27 | 株式会社日本自動車部品総合研究所 | ロ−リングピストン型圧縮機 |
US4669963A (en) * | 1984-11-15 | 1987-06-02 | Nippondenso Co., Ltd. | Rolling piston type rotary machine |
US4772185A (en) * | 1985-11-27 | 1988-09-20 | Barmag Ag | Rotary vane pump having a plurality of inlet and outlet slots in a rotating sleeve |
DE3636943A1 (de) | 1986-10-30 | 1988-05-11 | Katimex Cielker Gmbh | Einziehgeraet |
US4772139A (en) * | 1987-09-23 | 1988-09-20 | Bretton Kenneth M | Liner for bearing assemblies and the like |
US5062721A (en) * | 1989-04-28 | 1991-11-05 | Nippon Seiko Kabushiki Kaisha | Rolling bearing with sleeve |
EP0558067B1 (en) * | 1992-02-28 | 1997-05-02 | EG&G SEALOL, INC. | Spring for centering two annular bodies relative to each other |
US5222884A (en) * | 1992-05-20 | 1993-06-29 | Ingersoll-Rand Company | Noise limiters for rolling piston compressor and method |
US5533739A (en) * | 1992-06-10 | 1996-07-09 | Durametallic Corporation | Non-contacting seal with centering spring mounted in dovetailed grooved |
JPH07317679A (ja) * | 1994-05-27 | 1995-12-05 | Shuichi Kitamura | ベーンポンプのシール装置 |
US5882183A (en) * | 1997-03-21 | 1999-03-16 | Triple Aught, Llc | Self-aligning rotary vane |
JPH11252851A (ja) | 1998-03-02 | 1999-09-17 | Nippon Seiko Kk | 電動式パワーステアリング装置用モータ |
JP2000120669A (ja) * | 1998-10-07 | 2000-04-25 | Nsk Ltd | 転がり軸受 |
WO2002061296A1 (de) * | 2001-02-01 | 2002-08-08 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Lageranordnung |
FI112107B (fi) * | 2001-07-31 | 2003-10-31 | Veikko Kalevi Rantala | Moottori, pumppu tai vastaava |
JP2003202018A (ja) | 2001-10-22 | 2003-07-18 | Nsk Ltd | 転がり軸受装置 |
US7618098B2 (en) * | 2004-08-12 | 2009-11-17 | Frear Joseph K | Cutting tool retention apparatuses |
US7118181B2 (en) * | 2004-08-12 | 2006-10-10 | Frear Joseph K | Cutting tool wear sleeves and retention apparatuses |
JP2007291996A (ja) * | 2006-04-26 | 2007-11-08 | Toshiba Kyaria Kk | 密閉型回転式圧縮機及び冷凍サイクル装置 |
WO2007143860A1 (en) * | 2006-06-15 | 2007-12-21 | Zoltech Inc. | Oscillating variable displacement ring pump |
CN101113734B (zh) | 2006-07-26 | 2012-05-02 | 云晓璎 | 转子式压缩机 |
JP2008067552A (ja) | 2006-09-08 | 2008-03-21 | Nsk Ltd | モータ |
JPWO2011135779A1 (ja) * | 2010-04-30 | 2013-07-18 | パナソニック株式会社 | 流体機械および冷凍サイクル装置 |
CN101864991A (zh) * | 2010-06-10 | 2010-10-20 | 姚镇 | 星旋式流体马达或发动机和压缩机及泵 |
US8579615B2 (en) * | 2011-03-01 | 2013-11-12 | Pars Makina Sanayi Ve Ticaret Limited Sirketi | Pivoting, hinged arc vane rotary compressor or expander |
CN103061822B (zh) | 2011-10-21 | 2015-02-11 | 北京星旋世纪科技有限公司 | 采用闸阀结构的星旋式转动装置 |
-
2013
- 2013-01-25 CN CN201310030773.XA patent/CN103967787B/zh active Active
-
2014
- 2014-01-21 EP EP14743623.2A patent/EP2942524B1/en active Active
- 2014-01-21 WO PCT/CN2014/070972 patent/WO2014114222A1/zh active Application Filing
- 2014-01-21 US US14/762,609 patent/US10215025B2/en active Active
- 2014-01-21 JP JP2015554035A patent/JP2016505769A/ja active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3639943A1 (de) * | 1985-11-27 | 1987-06-25 | Barmag Barmer Maschf | Fluegelzellenpumpe |
JPH08219034A (ja) * | 1995-02-08 | 1996-08-27 | Nissin Kogyo Kk | ベーンポンプ |
JP2005127306A (ja) * | 2003-10-03 | 2005-05-19 | Hitachi Ltd | 車載用ロータリ圧縮機 |
KR100819948B1 (ko) * | 2007-04-16 | 2008-04-08 | 김진수 | 캠 플레이트형 회전 압축기 |
JP2011174439A (ja) * | 2010-02-25 | 2011-09-08 | Nsk Ltd | ロータリコンプレッサ |
Non-Patent Citations (1)
Title |
---|
See also references of EP2942524A4 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104594953A (zh) * | 2014-01-03 | 2015-05-06 | 摩尔动力(北京)技术股份有限公司 | 圆形缸轴向隔离流体机构及包括其的装置 |
CN109209817A (zh) * | 2018-11-20 | 2019-01-15 | 泉州苗亿自动化机械有限公司 | 一种静音无油空压机 |
CN109209817B (zh) * | 2018-11-20 | 2023-09-29 | 泉州苗亿自动化机械有限公司 | 一种静音无油空压机 |
CN110425136A (zh) * | 2019-07-29 | 2019-11-08 | 黄石东贝电器股份有限公司 | 低背压用无吸气止回阀的滚动转子式压缩机 |
CN113659759A (zh) * | 2021-08-19 | 2021-11-16 | 天津飞旋科技股份有限公司 | 电机 |
Also Published As
Publication number | Publication date |
---|---|
EP2942524B1 (en) | 2019-12-11 |
US10215025B2 (en) | 2019-02-26 |
CN103967787A (zh) | 2014-08-06 |
JP2016505769A (ja) | 2016-02-25 |
CN103967787B (zh) | 2016-02-17 |
US20150322790A1 (en) | 2015-11-12 |
EP2942524A4 (en) | 2016-03-02 |
EP2942524A1 (en) | 2015-11-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2014114222A1 (zh) | 转动装置及应用其的转子式压缩机和流体马达 | |
US9261094B2 (en) | Rotary compressor | |
US9115716B2 (en) | Vane compressor with vane aligners | |
JP5514319B2 (ja) | 変化作業条件対応の球型膨張圧縮機 | |
WO2014166431A1 (zh) | 转动装置及其相应的流体马达、发动机、压缩机和泵 | |
US9382907B2 (en) | Vane-type compressor having an oil supply channel between the oil resevoir and vane angle adjuster | |
US9267503B2 (en) | Rotary systems lubricated by fluid being processed | |
KR102051094B1 (ko) | 스크롤 압축기 | |
JP2010065635A (ja) | スクロール圧縮機 | |
CN107906003B (zh) | 一种低速自封闭滑片压缩机 | |
CN112460017A (zh) | 泵体组件及具有其的流体机械 | |
JP2008031857A (ja) | 圧縮機 | |
CN211370720U (zh) | 滚筒压缩机和泵及马达 | |
US11655817B2 (en) | Rotary compressor | |
CN214036117U (zh) | 泵体组件及具有其的流体机械 | |
WO2019237690A1 (zh) | 压缩机及具有其的车辆 | |
JP5386566B2 (ja) | スクロール圧縮機 | |
CN111287972B (zh) | 叶旋压缩机 | |
KR20080084220A (ko) | 회전압축기 | |
WO2020125064A1 (zh) | 涡旋压缩机、空调器及涡旋压缩机背压调节方法 | |
KR100539561B1 (ko) | 이중용량 로터리 압축기 | |
KR102447838B1 (ko) | 로터리 압축기 | |
CN114412742B (zh) | 一种双输出轴向柱塞泵 | |
CN221144690U (zh) | 一种限位结构及紧凑型滑盘式柱塞泵 | |
KR102284366B1 (ko) | 압축기 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14743623 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14762609 Country of ref document: US Ref document number: 2014743623 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 2015554035 Country of ref document: JP Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |