CN104093987A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN104093987A CN104093987A CN201280061463.8A CN201280061463A CN104093987A CN 104093987 A CN104093987 A CN 104093987A CN 201280061463 A CN201280061463 A CN 201280061463A CN 104093987 A CN104093987 A CN 104093987A
- Authority
- CN
- China
- Prior art keywords
- rotary compressor
- row
- blade
- impeller
- stream
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/021—Units comprising pumps and their driving means containing a coupling
- F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
- F04D13/026—Details of the bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D23/00—Other rotary non-positive-displacement pumps
- F04D23/008—Regenerative pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/18—Lubricating arrangements
- F01D25/22—Lubricating arrangements using working-fluid or other gaseous fluid as lubricant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/026—Units comprising pumps and their driving means with a magnetic coupling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
- F04D29/526—Details of the casing section radially opposing blade tips
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention concerns a rotary compressor for compressing a gaseous medium, comprising an impeller (2), a drive unit (3) and a magnetic coupling (4) comprising a rotating inner rotor (41), a rotating outer rotor (42) and a can (40), wherein the inner rotor (41) is connected to the impeller (2), wherein the impeller (2) comprises a continuous solid portion (25), wherein a first row (21) and a second row (22) of blades (23) are provided at the outer circumference of the solid portion (25) of the impeller, the first and second row of blades being separated by a circumferential middle wall (20), and wherein the blades (23) of the first row (21) are offset in circumferential direction relative to the blades (23) of the second row (22).
Description
Technical field
The present invention relates to a kind of rotary compressor, this rotary compressor, for compression gas medium, the invention still further relates to a kind of gas lubrication mechanical seal structure, and this mechanical seal structure comprises the above-mentioned rotary compressor as auxiliary compressor.
Background technique
The reliability of gas lubrication mechanical seal structure depends on the lasting supply of clean, dry flushing gas to a great extent.Flushing gas prevents that contaminated processing gas from entering in described sealing configuration.In the time of operation, flushing gas is taken from compressor conventionally.Under the idling conditions or dead state of main compressor, by auxiliary compressor supply flushing gas.Auxiliary compressor is reciprocal piston type design.Obstruction, the generation heat etc. of piston during due to height wearing and tearing, startup, piston compressor is easy to leak and be easy to break down.Similarly, described piston compressor provides pulse gas stream, and this pulse gas stream needs ripple damper conventionally.In addition, WO97/01053A discloses a kind of sealing gas supercharger systems, and sealing gas booster system comprises the turbo machine as booster compressor.But, the specific design of this turbo machine is not disclosed.
Summary of the invention
Therefore, the object of the present invention is to provide a kind of rotary compressor and a kind of gas lubrication mechanical seal structure, this gas lubrication mechanical seal structure can guarantee that flushing gas is without leaking and being supplied to reliably in gas lubrication mechanical seal.
By have scheme 1 feature rotary compressor and have scheme 13 feature gas lubrication mechanical seal structure solve above-mentioned purpose.Affiliate program comprises favourable mode of execution of the present invention.
The rotary compressor of the present invention with the feature of scheme 1 has the flow velocity of increase and the increase of the pressure of increase.Rotary compressor comprises impeller, driver element and magnetic coupler for being connected described impeller and described driver element.Described impeller is designed to solid, rigid disk (deflection-free disc).In periphery, described impeller comprises first row and the second row of blade, and wherein said blade by circumferential midfeather separately.Therefore, the blade of described first row staggers along the blade of circumferential and second row.Therefore, according to rotary compressor of the present invention, can provide the Continuous Flow of gas medium, make flushing gas to be supplied to gas lubrication mechanical seal.In addition, rotary compressor of the present invention provides flushing gas after starting in the idle situation of main compressor.In addition, because described magnetic coupler comprises the internal rotor of rotation, external rotor and the tank body of rotation, provide the sealing being hedged off from the outer world, and stopped processing gas and leak to environment.Preferably, described driver element is electric drive unit or hydraulic drive unit or pneumatic drive unit.
Preferably, described rotary compressor comprises housing, and this housing has entrance, outlet and stream, and described stream is positioned at the periphery of described impeller.Described stream connects described entrance and described outlet, and preferably, described stream comprises path element two tubuloses, annular.Preferably, the cross section of the described path element in described housing is semicircle.In addition, described flowpath rings is around at least 300 ° of settings of the periphery of described impeller, and preferably, described flowpath rings is around 315 ° of settings of the periphery of described impeller.
According to another preferred embodiment of the present invention, described stream and/or described entrance and/or described outlet comprise the surface with multiple pits.This pit causes microturbulencd, and this microturbulencd has strengthened flow characteristic.Preferably, described pit has circular outer periphery, and 25% to 30% the round pool that is designed to diameter to be approximately 0.1-0.5mm, the degree of depth be diameter.In addition, preferably, described pit on described stream, be uniformly distributed in described entrance and described outlet.
Preferably, joint between described entrance and/or described outlet and described stream be shaped as fillet, so that obstruction is minimized.
In a preferred embodiment, the quantity of the quantity of the blade of first row and the blade of second row is identical.This supports the constant flow of described gas medium.
Preferably, the first row of blade and second row are along the half of the length of the spacer element that circumferentially staggers, and described spacer element is between two adjacent blades.Preferably, described in, stagger and be similar to the arc length of 4 °.
In order further to increase the efficiency of impeller, described blade is straight radial blade (straight radialblade), and this straight radial blade is taper diametrically.
According to another preferred embodiment of the present invention, the block piece tank body of described magnetic coupler comprises interior block piece and outer block piece, wherein, is provided with static isolation layer, to prevent the electric arc of generation of static electricity between described interior block piece and described outer block piece.Preferably, described static isolation layer is made up of composite (preferably, polyimide).Preferably, described interior block piece comprises and replaces stacking metal ring and teflon (PTFE) insulation paper tinsel.Outer block piece can comprise cannelure.The structure of interior block piece and outer block piece can reduce magnetic eddy current (magnetic eddy current), and low-energy-consumption and efficient magnetic couple are provided.Reduce heating value.
Further preferably, described rotary compressor comprises bearing unit.Described bearing unit comprises upper bearing (metal) and lower bearing.Preferably, lower bearing is duplex bearing, and upper bearing (metal) is single-bearing.Preferably, described bearing is angular contact ball bearing, and therefore the accurate axially locating of described impeller shaft and described impeller can be provided.
Preferably, the circumferential distance between the adjacent blade of described impeller is the arc length of 10 ° or less arc length.
Further preferably, the thickness of the midfeather of described impeller is identical with the outermost thickness of described blade.
In addition, the present invention relates to a kind of gas lubrication mechanical seal structure, this gas lubrication mechanical seal structure comprises rotating ring and retaining ring, between this rotating ring and retaining ring, is limited with seal clearance.In addition, be provided with gas supply unit, this gas supply unit comprises main compressor and auxiliary compressor, and wherein, described auxiliary compressor is according to rotary compressor of the present invention.
Therefore, gas lubrication mechanical seal structure of the present invention (for example, main gas supply system stops or working under low system pressure condition) under special condition is manipulable.Owing to having used rotary compressor of the present invention, can obtain long maintenance shop every, and reliable, leak free operation and without leakage.Further preferably, can use impeller described in standard electrical motor driven.
Brief description of the drawings
Hereinafter, in conjunction with following accompanying drawing, the preferred embodiment of the present invention is described:
Fig. 1 is according to the sectional view of the rotary compressor of an embodiment of the invention;
Fig. 2 to Fig. 4 is the different front elevation of impeller;
Fig. 5 is the general view that comprises the rotary compressor of motor;
Fig. 6 is the schematic diagram that the stream in housing is shown; With
Fig. 7 is the schematic diagram of the rotary compressor structure in gas lubrication mechanical seal.
Embodiment
As shown in fig. 1, comprise impeller 2, electric motor 3 and magnetic coupler 4 according to the rotary compressor 1 of the preferred embodiment of the present invention.Magnetic coupler 4 is connected electric motor 3 with impeller 2.
Magnetic coupler 4 comprises tank body 40, internal rotor 41 and external rotor 42.External rotor 42 is connected with electric motor 3, and internal rotor 41 is connected with impeller 2 by impeller shaft 6.Impeller 2 comprises central opening 26 (seeing Fig. 4), to hold the end of impeller shaft 6.Magnetic coupler 4 is protected by 14, cover.
Tank body 40 comprises interior block piece 43, outer block piece 44 and static isolation layer 45.Static isolation layer 45 is configured between described interior block piece and described outer block piece, to prevent electric arc.Static isolation layer 45 is made up of for example polyimide.
Rotary compressor 1 also comprises housing 7, and this housing 7 has the first housing section 71 and the second housing section 72.Tank body 40 is for example bolted to the second housing section 72.Housing 7 holds stream 5, and stream 5 is the cyclic path of wound impeller 2 partly.As shown in Figure 6, stream 5 is limited between entrance 8 and outlet 9, and covers approximately 315 °., the angle [alpha] between described entrance and described outlet is about 45 °.As shown in Figure 1, stream 5 comprises first portion 51 and second portion 52.Therefore,, in cross section, described first portion and described second portion are the semicircle that radius is equal.As shown in Figure 1, the radius of the radius of first portion 51 and second portion 52 and the profile that is arranged on the spacer element 24 between the adjacent blade 23 of impeller 2 are integrated with closed helical duct (volute channel).
Housing 7 is attached to substrate 10, and by this substrate 10, rotary compressor 1 can be fixed to any structural member.
Impeller shaft 6 is supported by clutch shaft bearing 11 and the second bearing 12.The duplex bearing of clutch shaft bearing 11 for being provided by angular contact ball bearing.Therefore, clutch shaft bearing 11 is for being axially set to the bearing near impeller 2 on X-X (referring to Fig. 1).In addition, pressure compensation opening 13 is set to obtain the pressure balance of bearing unit inside and bearing unit outside.
In Fig. 2 to Fig. 4, show in detail impeller 2.As shown in Figure 3, impeller 2 comprises the first row 21 of blade and the second row 22 of blade, and the described first row of blade and described second row have the blade 23 of equal number.Adjacent blade by corresponding spacer element 24 separately.As shown in Figure 3, the first row 21 of blade staggers along the second row 22 of circumferential and blade.In the present embodiment, the stagger half of arc length of a spacer element 24 of two row's blades, that is, and 4 °.First row 21 and the second row 22 of blade 23 separate vertically by midfeather 20.Therefore, the thickness of the peripheral part of midfeather 20 is identical with the thickness of the outermost end of blade 23.Impeller 2 also comprises solid part 25, and this solid part 25 connects center drilling 26 and two row's blades.Therefore, described impeller has rigid disk.
Impeller shaft 6 is connected with impeller 2 by keyway arrangements.
In addition, pit (dimple) can be set on the first portion of stream 5 51 and second portion 52.This pit enhanced flow dynamic response, and therefore can improve the flow velocity that rotary compressor 1 provides, and therefore improve pressure increase.In addition, the coating of stream 5 (for example, teflon, PTFE) can further improve flow velocity.In addition, stream 5 and entrance 8 and the transition of outlet between 9 be characterized as level and smooth transition, so that the obstruction of the gas flow path in housing 7 is minimized.
Fig. 7 shows the advantageous applications of rotary compressor 1 of the present invention in gas lubrication mechanical seal structure 100.Gas lubrication mechanical seal structure 100 comprises mechanical sealing element, and this mechanical sealing element has the rotating seal ring 101 that is connected to axle 115 and the fixing seal ring 102 that is connected to fixed element.Seal clearance 103 is formed between rotating seal ring 101 and fixing seal ring 102.Mechanical seal separates product side 113 and atmospheric side 114 by the gas medium being provided by sealing gas supply 106 by main compressor 105.In sealing gas supply 106, be provided with filter 110, stop valve 108, aperture 111 and safety check 112.In addition, be provided with bypass 107, this bypass 107 comprises stop valve 109 and according to rotary compressor 1 of the present invention.Therefore, bypass 107 bypass cutoff valves 108, aperture 111 and safety check 112 (referring to Fig. 7).In addition, provide labyrinth sealing (labyrinth seal) 104, this labyrinth sealing 104 is adjacent with rotating seal ring 101, to keep the gas medium 116 of supply near seal clearance 103.
In one case, when main compressor 105 is inoperative or during in idle mode, rotary compressor 1 of the present invention activated as auxiliary compressor, to keep to described mechanical seal supply gas medium 116.Therefore, stop valve 108 is closed, and stop valve 109 opens, and gas medium is sucked through bypass 107.
Rotary compressor 1 of the present invention has very short starting time, and can provide non-pulse air-flow for described mechanical seal.Due to the innovative structure of impeller 2 of the present invention, stream 5 and magnetic coupler 4, very effective gas supply can be provided in a continuous manner, and there is no Leakage Gas to atmosphere.Therefore, can avoid the pollution of the seal clearance 103 between rotating seal ring 101 and fixing seal ring 102.Because impeller 2 places do not rub and accumulate the danger of heat, therefore, rotary compressor 1 of the present invention can long-play.In addition do not use, the risk of the mechanical failure occurring in the situation of piston compressor.
Claims (13)
1. for a rotary compressor for compression gas medium, this rotary compressor comprises:
Impeller (2);
Driver element (3); With
Magnetic coupler (4), this magnetic coupler (4) comprises the internal rotor (41) of rotation, external rotor (42) and the tank body (43) of rotation;
Wherein, described internal rotor (41) is connected with described impeller (2),
Wherein, described impeller (2) comprises continuous solid part (25),
Wherein, the first row (21) of blade (23) and second row (22) are arranged on the periphery of the described solid part (25) of described impeller, the described first row of blade and described second row are separated by circumferential midfeather (20), and
Wherein, the blade (23) of described first row (21) is along circumferentially staggering with the blade (23) of described second row (22).
2. rotary compressor according to claim 1, it is characterized in that, described rotary compressor also comprises housing (7), this housing (7) has entrance (8), outlet (9) and stream (5), wherein, described stream (5) connects described entrance (8) and described outlet (9), and described stream (5) is arranged in the arc of at least 300 ° of periphery of described impeller (2), and be preferably arranged in the arc of 315 ° of periphery of described impeller (2).
3. rotary compressor according to claim 2, is characterized in that, described stream (5) and/or described entrance and/or described outlet comprise the surface with multiple pits.
4. according to the rotary compressor described in claim 2 or 3, it is characterized in that, described stream (5) has cover coat, and preferably, described stream (5) has polytetrafluorethylecoatings coatings.
5. according to the rotary compressor described in any one in claim 2-4, it is characterized in that, the joint between described entrance (8) and/or described outlet (9) and described stream (5) does not have seamed edge.
6. according to the rotary compressor described in any one in the claims, it is characterized in that, the quantity of the blade (23) of described first row is identical with the quantity of the blade of described second row.
7. according to the rotary compressor described in any one in the claims, it is characterized in that, the described first row (21) of blade and described second row (22) are along the half of the length of the spacer element (24) that circumferentially staggers, described spacer element (24) is arranged between two adjacent blades (23), preferably, the described first row (21) of blade and described second row (22) are along circumferentially staggering the arc length of 4 °.
8. according to the rotary compressor described in any one in the claims, it is characterized in that, described blade (23) is straight radial blade, and this straight radial blade is taper in radially outward direction.
9. according to the rotary compressor described in any one in the claims, it is characterized in that, described tank body (40) comprises interior block piece (43) and outer block piece (44), wherein, between described interior block piece and described outer block piece, be provided with static isolation layer (45).
10. according to the rotary compressor described in any one in the claims, it is characterized in that, described rotary compressor also comprises impeller shaft (6), this impeller shaft (6) is supported by clutch shaft bearing (11) and the second bearing (12), wherein, described clutch shaft bearing (11) is duplex bearing.
11. according to the rotary compressor described in any one in the claims, it is characterized in that, adjacent blade has the arc length of 10 ° or less arc length along circumferential distance.
12. according to the rotary compressor described in any one in the claims, it is characterized in that, the thickness of described midfeather (20) of described impeller (2) is identical with the outermost thickness of described blade.
13. 1 kinds of gas lubrication mechanical seal structures, this gas lubrication mechanical seal structure comprises:
Rotating ring (101);
Retaining ring (102); With
Gas supply unit, this gas supply unit comprises main compressor (105) and auxiliary compressor (1);
Wherein, described auxiliary compressor (1) is according to the compressor described in any one in the claims.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP11009817.5A EP2604863B1 (en) | 2011-12-13 | 2011-12-13 | Rotary compessor |
| EP11009817.5 | 2011-12-13 | ||
| PCT/EP2012/004363 WO2013087130A1 (en) | 2011-12-13 | 2012-10-18 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104093987A true CN104093987A (en) | 2014-10-08 |
Family
ID=47115734
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280061463.8A Pending CN104093987A (en) | 2011-12-13 | 2012-10-18 | Rotary compressor |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US20150125324A1 (en) |
| EP (1) | EP2604863B1 (en) |
| CN (1) | CN104093987A (en) |
| AU (1) | AU2012350434B2 (en) |
| BR (1) | BR112014014489A2 (en) |
| CA (1) | CA2861214A1 (en) |
| MX (1) | MX356243B (en) |
| PL (1) | PL2604863T3 (en) |
| WO (1) | WO2013087130A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016210464A1 (en) * | 2016-06-14 | 2017-12-14 | Gardner Denver Deutschland Gmbh | compressor assembly |
| MX2019004713A (en) * | 2016-11-01 | 2019-12-11 | Psg Worldwide Inc | Magnetically coupled sealless centrifugal pump. |
| IT201700052998A1 (en) * | 2017-05-16 | 2018-11-16 | Bosch Gmbh Robert | PROPULSION SYSTEM FOR VEHICLES |
| EP3594498B1 (en) * | 2019-11-06 | 2022-01-05 | Pfeiffer Vacuum Gmbh | System with a recirculation device |
| DE102019219998A1 (en) * | 2019-12-18 | 2021-06-24 | Robert Bosch Gmbh | Side channel compressor for a fuel cell system for conveying and / or compressing a gas |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5891393A (en) * | 1981-11-26 | 1983-05-31 | Nishigaki Pump Seizo Kk | Magnet driven pump |
| US4678409A (en) * | 1984-11-22 | 1987-07-07 | Fuji Photo Film Co., Ltd. | Multiple magnetic pump system |
| US5141396A (en) * | 1990-07-14 | 1992-08-25 | Vdo Adolf Schindling Ag | Regenerating pump with graphite and plastic casing and impeller |
| EP0563957A1 (en) * | 1992-04-03 | 1993-10-06 | Nippondenso Co., Ltd. | Fuel pump |
| US5509779A (en) * | 1994-02-03 | 1996-04-23 | World Chemical Co., Ltd. | Self-priming chemical pump |
| GB2313158A (en) * | 1996-05-13 | 1997-11-19 | Totton Pumps Ltd | Dispensing soda water |
| CN101994681A (en) * | 2009-08-21 | 2011-03-30 | 笹仓机械工程有限公司 | A shaft sealing structure of a steam compressor in a vacuum concentration device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2805626A (en) * | 1954-06-09 | 1957-09-10 | Anthony H Pezzillo | Unitary motor and turbine pump |
| US3111904A (en) * | 1961-12-18 | 1963-11-26 | Shell Oil Co | Turbine pump |
| US3518021A (en) * | 1968-04-04 | 1970-06-30 | Gen Electric | Thrust bearing for compressor |
| DE2745818A1 (en) * | 1977-10-12 | 1979-04-26 | Bosch Gmbh Robert | FUEL FEED PUMP |
| JPS6114495A (en) * | 1984-06-29 | 1986-01-22 | Shibaura Eng Works Co Ltd | Pump apparatus |
| DE3636404A1 (en) * | 1986-10-25 | 1988-04-28 | Richter Chemie Technik Gmbh | MAGNETIC CENTRIFUGAL PUMP |
| DE3818832A1 (en) * | 1988-06-03 | 1989-12-07 | Uranit Gmbh | CLEANER FOR SLEEVELESS ELECTRIC OR MAGNETIC DRIVE UNITS |
| US5137418A (en) * | 1990-12-21 | 1992-08-11 | Roy E. Roth Company | Floating self-centering turbine impeller |
| AU1192897A (en) | 1995-06-23 | 1997-01-22 | Revolve Technologies Inc. | Dry seal contamination prevention system |
| US6261070B1 (en) * | 1998-09-17 | 2001-07-17 | El Paso Natural Gas Company | In-line electric motor driven compressor |
| US6293772B1 (en) * | 1998-10-29 | 2001-09-25 | Innovative Mag-Drive, Llc | Containment member for a magnetic-drive centrifugal pump |
| DE10252141A1 (en) * | 2002-11-09 | 2004-07-01 | Prominent Dosiertechnik Gmbh | Flat sealing ring |
| DE202006005189U1 (en) * | 2006-03-31 | 2007-08-16 | H. Wernert & Co. Ohg | Centrifugal pump with coaxial magnetic coupling |
| JP4889419B2 (en) * | 2006-09-15 | 2012-03-07 | 愛三工業株式会社 | Wesco pump |
| DE102007026533A1 (en) * | 2007-06-08 | 2008-12-11 | Continental Automotive Gmbh | Fuel pump |
| US8974197B2 (en) * | 2010-02-16 | 2015-03-10 | Halla Visteon Climate Control Corporation | Compact structure for an electric compressor |
| US9249806B2 (en) * | 2011-02-04 | 2016-02-02 | Ti Group Automotive Systems, L.L.C. | Impeller and fluid pump |
-
2011
- 2011-12-13 PL PL11009817T patent/PL2604863T3/en unknown
- 2011-12-13 EP EP11009817.5A patent/EP2604863B1/en not_active Not-in-force
-
2012
- 2012-10-18 AU AU2012350434A patent/AU2012350434B2/en not_active Ceased
- 2012-10-18 CN CN201280061463.8A patent/CN104093987A/en active Pending
- 2012-10-18 BR BR112014014489A patent/BR112014014489A2/en not_active IP Right Cessation
- 2012-10-18 MX MX2014007008A patent/MX356243B/en active IP Right Grant
- 2012-10-18 US US14/363,026 patent/US20150125324A1/en not_active Abandoned
- 2012-10-18 WO PCT/EP2012/004363 patent/WO2013087130A1/en active Application Filing
- 2012-10-18 CA CA 2861214 patent/CA2861214A1/en not_active Abandoned
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5891393A (en) * | 1981-11-26 | 1983-05-31 | Nishigaki Pump Seizo Kk | Magnet driven pump |
| US4678409A (en) * | 1984-11-22 | 1987-07-07 | Fuji Photo Film Co., Ltd. | Multiple magnetic pump system |
| US5141396A (en) * | 1990-07-14 | 1992-08-25 | Vdo Adolf Schindling Ag | Regenerating pump with graphite and plastic casing and impeller |
| EP0563957A1 (en) * | 1992-04-03 | 1993-10-06 | Nippondenso Co., Ltd. | Fuel pump |
| US5509779A (en) * | 1994-02-03 | 1996-04-23 | World Chemical Co., Ltd. | Self-priming chemical pump |
| GB2313158A (en) * | 1996-05-13 | 1997-11-19 | Totton Pumps Ltd | Dispensing soda water |
| CN101994681A (en) * | 2009-08-21 | 2011-03-30 | 笹仓机械工程有限公司 | A shaft sealing structure of a steam compressor in a vacuum concentration device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2013087130A1 (en) | 2013-06-20 |
| EP2604863B1 (en) | 2017-07-19 |
| BR112014014489A2 (en) | 2017-06-13 |
| AU2012350434B2 (en) | 2016-05-05 |
| EP2604863A8 (en) | 2013-10-09 |
| MX2014007008A (en) | 2014-07-22 |
| EP2604863A1 (en) | 2013-06-19 |
| MX356243B (en) | 2018-05-21 |
| CA2861214A1 (en) | 2013-06-20 |
| US20150125324A1 (en) | 2015-05-07 |
| PL2604863T3 (en) | 2017-12-29 |
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