WO2014128407A1 - Roue de turbine, de compresseur ou de pompe - Google Patents
Roue de turbine, de compresseur ou de pompe Download PDFInfo
- Publication number
- WO2014128407A1 WO2014128407A1 PCT/FR2014/050348 FR2014050348W WO2014128407A1 WO 2014128407 A1 WO2014128407 A1 WO 2014128407A1 FR 2014050348 W FR2014050348 W FR 2014050348W WO 2014128407 A1 WO2014128407 A1 WO 2014128407A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- wheel
- circle
- compressor
- front face
- turbine
- Prior art date
Links
Classifications
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
-
- 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
- F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
- F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
- F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
- F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
- F01D5/048—Form or construction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2216—Shape, geometry
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/26—Three-dimensional paraboloid
Definitions
- the present invention relates to a rotating machine wheel for a gaseous or liquid fluid, such as a centrifugal compressor, centrifugal pump or centripetal turbine wheel. It also relates to a compressor, a centrifugal pump or a centripetal turbine provided with such a wheel, and a turbocharger at least one of the wheels is of this type.
- Rotating machines such as centripetal type turbines or centrifugal type compressors are widely used in industry, particularly in the field of thermal engines.
- a turbine coupled on the same shaft to a compressor is used to form a turbocharger.
- the turbine is powered by the exhaust gas from an engine and drives the compressor that compresses fresh air for engine boosting.
- Some compressors are driven by an electric motor and some turbines are used as generators of electrical energy.
- FIGS 5 and 6 show a centrifugal compressor 1 1 according to the prior art.
- the compressor 1 1 comprises a compressor body January 1 and a rotating part rotatably mounted on the compressor body January 1.
- the rotating part comprises a compressor wheel January 12 mounted on a shaft 1 14 rotating on a bearing January 13 of the compressor body 1 January.
- the compressor wheel 1 12 comprises a hub 1 120 and a set of blades 1 121 fixed to the hub.
- the compressor body 1 1 1 1 has an axial opening placed opposite the hub 1 120 and which constitutes a inlet duct 1 1 10.
- the compressor body 1 1 1 further comprises a volute 1 1 12 around the compressor wheel 1 12.
- the volute 1 1 12 has a peripheral opening 1 1 1 1 placed on the periphery of the compressor wheel 1 12 and opens through an outlet conduit 1 1 13 which extends substantially in a direction tangential to the compressor wheel 1 12.
- a gaseous fluid flows from the axial opening 1 1 10 to the peripheral opening 1 1 1 1 being driven by the compressor wheel 1 12.
- the geometry of the blades 1 121 is designed so that the compressor wheel January 12 provides mechanical energy to the gases, this mainly by accelerating, the kinetic energy and obtained then being converted into pressure form, mainly in volute 1 1 12.
- a centripetal turbine has a structure quite similar to that of a centrifugal compressor described above, but the flow direction of the gas is reversed and the work is supplied to the machine by the fluid.
- the geometry of the blades is studied so that the gases relax by crossing the wheel of the turbine and return energy to it.
- a significant increase in pressure is obtained by rotating centrifugal machines when the fluid is liquid. These machines are called pumps which are generally distinguished by large diameter wheels with flat flanges on which the blades are implanted. Such machines are limited in rotation speed because of the diameter of the wheels, involving high centrifugal forces.
- the invention therefore aims to provide a rotating machine wheel that achieves high efficiency for a low fluid flow.
- the subject of the invention is a rotating machine wheel for a fluid, the wheel having a wheel axle and having a hub arranged to mount the rotary wheel around the wheel axle, a flange fixed on the hub and extending substantially in a radial plane relative to the wheel axis, the flange having a front face, blades projecting from the front face, each of the blades extending at most between a central circle and a peripheral circle located on the front face, at least one blade extending to the central circle and at least one blade extending to the peripheral circle, characterized in that an inner circle and an outer circle on the face front between the central circle and the peripheral circle have a difference in diameters of at least 70% of the difference in diameters between the central circle and the peripheral circle, the inner and outer circles belonging to a first cone of revolution the tip of which is oriented towards the front and whose angle at the apex is between 154 ° and 170 °, and in that a second cone having for its axis of revolution the wheel axle and the
- the antagonism designated here disappears if the leading edges extend in a direction close to that of the wheel axle: it is thus possible to have leading edges located close to the axis. wheel but long enough to provide a sufficient entrance section.
- the air flow extends substantially in a radial plane as soon as it enters the blading and, consequently, throughout the vein.
- radial a rotating machine wheel whose geometry thus constitutes a fluid flow extending substantially in a radial plane and having a relatively low axial component.
- the flange is generally shaped like a cone whose tip is oriented towards the front of the wheel, the centrifugal forces applied to the flange tend to straighten the flange towards the front, compressing its front, which offsets all or part of the stretching effect described above. Moreover, because of this inclination of the flange, the axial offset of the blades relative to the flange, and therefore the associated bending moment, are reduced compared to the case of a flat flange. This configuration makes it possible to push the speed limits of rotation of the wheel or to enlarge the wheel, and thus to obtain better performances.
- Such a geometric layout if it primarily aims to reduce the mechanical stresses in the most sensitive areas, can also be considered to optimize the deformation of the wheel.
- This secondary objective may aim in particular to ensure sufficient clearance vis-à-vis the body of the rotating machine, in terms of machining and assembly tolerances, thermal deformations, bearing movements and vibratory deformations. In this particular case, it is, contrary to what has been explained above, to choose a slightly larger cone angle than the one offering the best fatigue strength of the wheel.
- most of the front face extends substantially along a cone whose tip is oriented forward and whose angle at the top is between 154 and 170 °, but it is very common that the peripheral circle and the central circle, circles delimiting the area of implantation of the blading, are located outside this characteristic area. Indeed, the profile of the front face is generally rectified peripherally to guide the output velocity of the fluid in a radial plane.
- the portion of the front face close to the wheel axis is generally a form of fillet, constituting the contour of the hub; however, because of the need to maximize the length of the fluid flow in the radial direction, it is common that the implantation of the leading edges (in the case of the compressor or centrifugal pump) or leakage (in the case of the turbine) is in this area, and this even if the leading edges (respectively leakage) extend in a direction close to that of the wheel axis.
- the Applicant has found that it was particularly interesting to tilt the profile of the front panel in the specified range.
- the front face of the flange may be slightly curved over a very large part of the wheel adopting nowhere the exact shape of a section of cone of revolution.
- some of the blades, of a fractionation subassembly extend from an intermediate circle between the central circle and the peripheral circle.
- Such blades also called “splitters”, subdivide the space between the blades that extend from the central circle.
- the invention is particularly advantageous in such a configuration, because the leading edges (in the case of a compressor or a pump) or leakage (in the case of a turbine, respectively) of these intermediate blades are typically located on a radial wheel, in the transition zone between the flange and the hub, or in an area where the bending deformation of the flange tends to concentrate.
- the inner circle and the outer circle have a difference in diameters of at least 85% of the difference in diameters between the central circle and the peripheral circle.
- the flange and the hub are in one piece.
- the invention also relates to a turbine, characterized in that it comprises a wheel as described above.
- the invention also relates to a compressor, characterized in that it comprises a wheel as described above.
- the invention also relates to a turbocharger comprising a turbine and a compressor, the turbine and the compressor each comprising at least one wheel, the wheels being coupled in rotation, characterized in that at least one of the wheels is a wheel such as as previously described.
- FIG. 1 is a perspective view of a wheel according to a first embodiment of the invention
- FIG. 1 is a sectional view of the wheel of Figure 1;
- FIG. 3 is a view similar to FIG. 2 of a wheel according to a second embodiment of the invention.
- FIG. 4 is a sectional view of a turbocharger comprising two wheels according to the invention.
- FIG. 5 is a longitudinal sectional view along the line V-V of Figure 6 of a centrifugal compressor according to the prior art
- FIG. 6 is a sectional view along the line VI-VI of Figure 5; - Figures 7 to 10 are views similar to Figure 2 of wheels according to the prior art.
- FIGS. 1 and 2 A wheel 2 of a rotary machine according to a first embodiment is shown in FIGS. 1 and 2.
- the wheel 2 for example that of a compressor, comprises a hub 20 arranged to mount the rotating wheel about an axis of rotation. wheel A, a flange 21 in one piece with the hub 20 and extending substantially in a plane perpendicular to the wheel axis A, and blades 22 mounted on a front face 210 of the flange 21 so as to protrude a front side of the wheel 2.
- the wheel 2 comprises at the hub 20 a bore 201 for receiving a shaft, not shown.
- All the elements of the wheel 2 are in one piece, the wheel 2 being made for example by molding a metal alloy or a synthetic material, or by machining a block of such material.
- the flange 21, as seen in section in Figure 2 has a greater width near the hub 20 at the periphery, for reasons of mechanical strength and to minimize the overall deformation of the wheel.
- the blades 22 have a blade shape, of substantially constant thickness, and substantially perpendicular to the front face 210. Some blades 22 extend from a leading edge 221 whose base is located on a circle J, near from the hub 20, to a trailing edge 222 located at the periphery 24 of the wheel 2 on the front face 210.
- blades 22 of a fractionation subassembly interposed between those of the preceding group, have an edge driver 223 located on or beyond a circle N of intermediate diameter placed between the circle J and the periphery 24.
- the leading edges 221, 223 are substantially parallel to the wheel axis A.
- the front face 210 comprises a first zone C in the form of a rounded fillet of connection extending from the central circle J, passing through the feet of the leading edges 221, at the intersection of the leading edges 221. and from the front face 210, to an inner circle K, followed by a second zone D of substantially conical shape extending from the inner circle K to an outer circle L, then by a third zone E extending from the outer circle L to a peripheral circle M at the periphery 24 of the wheel 2, the generatrix of the front face 210 on this outer zone E being of rounded shape and tangential to the perpendicular to the wheel axis A to periphery level 24.
- a first zone C in the form of a rounded fillet of connection extending from the central circle J, passing through the feet of the leading edges 221, at the intersection of the leading edges 221. and from the front face 210, to an inner circle K, followed by a second zone D of substantially conical shape extending from the inner circle K to an outer circle L, then by
- the diameter of the central circle represents 18.5% of the diameter of the peripheral circle.
- the diameters of the inner circle K and the outer circle L respectively represent 29 % and 90.5% of the diameter of the circumferential circle M.
- the angle a at the top of the first cone R which contains the inner and outer circles K and L is 164 °. In other words, on the second zone D, the angle between a generatrix of the first cone R and a radial plane is 8 °.
- the difference in diameter between the inner and outer circles K and L represents 74% of the difference in diameter between the peripheral circle M and the central circle J.
- Any cone tangent to the front face 210 in any circle located on the front face 210, between the inner circle K and the outer circle L has an apex angle less than or equal to 170 °.
- This wheel according to the invention has been compared and whose geometric characteristics are listed above at an identical wheel except that it comprises a plane front face from the inner circle.
- the critical stress point being located at the base of the leading edge of the intermediate length intermediate blade, therefore relatively far from the hub, the gain provided by the balancing associated with the optimum inclination the flange of the wheel according to the invention is very consequent.
- the optimization of the inclination of the flange obtained with the characteristics described above, has made it possible to obtain a reduction of about 55% of the stress at the critical point, in other words to increase by approximately 50% the speed maximum fatigue mission profile of the compressor.
- a centripetal turbine wheel 2 ' as shown in FIG. 3, the front face 210' has a profile evolving continuously between the central circle J ', of diameter Di, and the peripheral circle M ', of diameter De.
- the first cone R ' containing the inner circles K' and outer L 'has an apex angle of 1 60 °.
- the second most open cone S ' is the cone of greater angle at the top which is tangent to the front face 210' between the inner and outer circles, K 'and L'. In this configuration, the second cone is tangent to the front face 210 'at the outer circle L'.
- the angle ⁇ at the apex P2 'of the second cone S' is 166 °.
- a set of elementary conditions makes it possible to characterize certain geometrical features peculiar to the invention and to distinguish it from the prior art. It is observed first of all that, on the wheels of centrifugal compressor or centripetal turbine other than those, rare, of radial type, the generating curve of the front face always has, by construction, a quarter-elliptical shape.
- the blades extend, as a whole, from a central circle J to a peripheral circle M.
- two inner and outer circles, K and L, located on the front face are considered between the circle central J and the peripheral circle M, the difference 2X in diameter between the outer circle L and the inner circle K being equal to 70% of the difference (De-Di) in diameter between the peripheral circle M and the central circle J, the positions of the circles K and L being such, moreover, that the apex angle of a first cone R passing through these two circles is maximum.
- the outer circle L coincides with the peripheral circle M. It is observed that the apex angle of the first cone R thus constructed is typically between 130 ° and 145 °, ie outside the characteristic angular range of the invention.
- FIG. 4 shows a turbocharger 3 comprising a turbine 30 and a compressor 31 whose respective wheels 302, 312 are fixed on the same rotary shaft 32 via a bearing 33 placed between the body 31 1 of the compressor 31 and that of the turbine 301.
- the wheels 302, 312 are in accordance with the embodiment as previously described.
- Such a turbocharger 3 provides good efficiency for a low gas flow.
- the wheels made according to the invention being particularly large compared to conventional wheels, this turbocharger 3 operates at a lower speed of rotation of the wheels.
- a bearing 33 can be used with ball bearings.
- the invention is not limited to the embodiments which have just been described by way of examples.
- the rotor shaft may be integral with the wheel.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Supercharger (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201480022601.0A CN105121786A (zh) | 2013-02-21 | 2014-02-20 | 涡轮、压缩机或泵的叶轮 |
US14/769,661 US20150377026A1 (en) | 2013-02-21 | 2014-02-20 | Wheel of a Turbine, Compressor or Pump |
JP2015558529A JP2016511358A (ja) | 2013-02-21 | 2014-02-20 | タービン、圧縮機又はポンプの羽根車 |
EP14713161.9A EP2959107A1 (fr) | 2013-02-21 | 2014-02-20 | Roue de turbine, de compresseur ou de pompe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1351503A FR3002271A1 (fr) | 2013-02-21 | 2013-02-21 | Roue de turbine, de compresseur ou de pompe. |
FR1351503 | 2013-02-21 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014128407A1 true WO2014128407A1 (fr) | 2014-08-28 |
Family
ID=48741304
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2014/050348 WO2014128407A1 (fr) | 2013-02-21 | 2014-02-20 | Roue de turbine, de compresseur ou de pompe |
Country Status (6)
Country | Link |
---|---|
US (1) | US20150377026A1 (fr) |
EP (1) | EP2959107A1 (fr) |
JP (1) | JP2016511358A (fr) |
CN (1) | CN105121786A (fr) |
FR (1) | FR3002271A1 (fr) |
WO (1) | WO2014128407A1 (fr) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TW201617016A (zh) * | 2014-11-14 | 2016-05-16 | 盈太企業股份有限公司 | 渦輪 |
CN107533852B (zh) | 2015-09-17 | 2019-10-01 | 富士电机株式会社 | 垂直磁记录介质 |
FR3062159A1 (fr) * | 2017-01-25 | 2018-07-27 | Thy Eng | Roue biface, compresseur, turbine, turbocompresseur et pompe associes |
US20190313878A1 (en) * | 2018-04-16 | 2019-10-17 | Haier Us Appliance Solutions, Inc. | Wash pump impeller for a dishwashing appliance and a method of additively manufacturing the same |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2860827A (en) * | 1953-06-08 | 1958-11-18 | Garrett Corp | Turbosupercharger |
US2925215A (en) * | 1957-06-20 | 1960-02-16 | United Aircraft Corp | Lubrication system |
EP0283825A1 (fr) * | 1987-03-23 | 1988-09-28 | Philipp Hilge GmbH | Rotor pour une turbomachine |
DE4411678A1 (de) * | 1994-04-05 | 1995-10-12 | Mtu Friedrichshafen Gmbh | Abgasturbolader mit Radialturbine |
US20090297344A1 (en) * | 2008-05-30 | 2009-12-03 | Controlled Power Technologies Limited | Rotors and manufacturing methods for rotors |
FR2935761A1 (fr) * | 2008-09-05 | 2010-03-12 | Alstom Hydro France | Roue de type francis pour machine hydraulique, machine hydraulique comprenant une telle roue et procede d'assemblage d'une telle roue |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB796696A (en) * | 1955-07-19 | 1958-06-18 | Davidson & Co Ltd | Improvements in or relating to centrifugal fans |
US2799445A (en) * | 1955-12-12 | 1957-07-16 | Gen Electric | High speed rotor |
JPS5413003A (en) * | 1977-06-29 | 1979-01-31 | Kawasaki Heavy Ind Ltd | Vane wheel of linear backward inclined flow fan |
FR2393176A1 (fr) * | 1977-06-01 | 1978-12-29 | Alsthom Atlantique | Compresseur centrifuge a haut rapport de pression |
EP0291535A4 (fr) * | 1986-11-28 | 1989-06-14 | Proizv Ob Nevsky Zd Im V I | Roue de travail pour compresseur centrifuge. |
JPH02131099U (fr) * | 1989-04-05 | 1990-10-30 | ||
SE515523C2 (sv) * | 1996-05-24 | 2001-08-20 | Flaekt Ab | Fläkthjul för radialfläkt samt radialfläkt och kanalfläkt innefattande ett dylikt fläkthjul |
DE10020878C2 (de) * | 2000-04-28 | 2002-05-02 | Verax Ventilatoren Gmbh | Lüfter insbesondere zur Belüftung von elektronischen Geräten |
US6499954B1 (en) * | 2000-08-21 | 2002-12-31 | Textron Automotive Company Inc. | Centrifugal impeller and housing |
JP2005155566A (ja) * | 2003-11-28 | 2005-06-16 | Mitsubishi Heavy Ind Ltd | 斜流圧縮機のインペラ |
DE102006009495A1 (de) * | 2006-02-27 | 2007-08-30 | Oase Gmbh | Wasserpumpe |
JP4969433B2 (ja) * | 2007-12-19 | 2012-07-04 | 三菱重工業株式会社 | 遠心圧縮機 |
EP2257709B1 (fr) * | 2008-02-22 | 2019-05-29 | Horton, Inc. | Appareil ventilateur a flux hybride |
-
2013
- 2013-02-21 FR FR1351503A patent/FR3002271A1/fr not_active Withdrawn
-
2014
- 2014-02-20 CN CN201480022601.0A patent/CN105121786A/zh active Pending
- 2014-02-20 JP JP2015558529A patent/JP2016511358A/ja active Pending
- 2014-02-20 EP EP14713161.9A patent/EP2959107A1/fr not_active Withdrawn
- 2014-02-20 WO PCT/FR2014/050348 patent/WO2014128407A1/fr active Application Filing
- 2014-02-20 US US14/769,661 patent/US20150377026A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2860827A (en) * | 1953-06-08 | 1958-11-18 | Garrett Corp | Turbosupercharger |
US2925215A (en) * | 1957-06-20 | 1960-02-16 | United Aircraft Corp | Lubrication system |
EP0283825A1 (fr) * | 1987-03-23 | 1988-09-28 | Philipp Hilge GmbH | Rotor pour une turbomachine |
DE4411678A1 (de) * | 1994-04-05 | 1995-10-12 | Mtu Friedrichshafen Gmbh | Abgasturbolader mit Radialturbine |
US20090297344A1 (en) * | 2008-05-30 | 2009-12-03 | Controlled Power Technologies Limited | Rotors and manufacturing methods for rotors |
FR2935761A1 (fr) * | 2008-09-05 | 2010-03-12 | Alstom Hydro France | Roue de type francis pour machine hydraulique, machine hydraulique comprenant une telle roue et procede d'assemblage d'une telle roue |
Also Published As
Publication number | Publication date |
---|---|
JP2016511358A (ja) | 2016-04-14 |
EP2959107A1 (fr) | 2015-12-30 |
US20150377026A1 (en) | 2015-12-31 |
CN105121786A (zh) | 2015-12-02 |
FR3002271A1 (fr) | 2014-08-22 |
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