EP1937980B1 - Rotor für eine strömungsmaschine und eine strömungsmaschine - Google Patents

Rotor für eine strömungsmaschine und eine strömungsmaschine Download PDF

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Publication number
EP1937980B1
EP1937980B1 EP06762493A EP06762493A EP1937980B1 EP 1937980 B1 EP1937980 B1 EP 1937980B1 EP 06762493 A EP06762493 A EP 06762493A EP 06762493 A EP06762493 A EP 06762493A EP 1937980 B1 EP1937980 B1 EP 1937980B1
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EP
European Patent Office
Prior art keywords
rotor
rotary machine
impeller
chamber
lateral surface
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.)
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Application number
EP06762493A
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German (de)
English (en)
French (fr)
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EP1937980A1 (de
Inventor
Zeki Akbayir
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Individual
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Priority to SI200630607T priority Critical patent/SI1937980T1/sl
Priority to PL06762493T priority patent/PL1937980T3/pl
Publication of EP1937980A1 publication Critical patent/EP1937980A1/de
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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S416/00—Fluid reaction surfaces, i.e. impellers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a rotor for a turbomachine according to the preamble of patent claim 1 and to a turbomachine according to the preamble of patent claim 11.
  • Turbomachines are characterized in that they generate a pressure difference in a gaseous or liquid medium or are driven by a pressure difference in such a medium.
  • flow machines usually have a rotor which is rotatably mounted in the gaseous or liquid medium relative to a stator and generates a pressure difference by its shape or arrangement or converts the pressure difference in the medium into a rotary motion.
  • Such turbomachines include primarily most types of pumps, compressors, turbomachines, turbines or wind energy converters, which have rotors in various designs and are usually rotatably mounted in a housing as a stator.
  • a turbomachine in the form of a pump is from the DD 293 181 A5 known, which has a cylindrical or conical rotor which is eccentrically mounted in a pump housing.
  • This rotor is connected to a drive and generates a crescent-shaped rotating pump chamber during rotation, which preferably conveys oil as a liquid from an inlet opening into an outlet opening.
  • This pump based on the hydrodynamic principle, generates an oil wedge during rotation in the crescent-shaped circumferential housing which results in an increase in pressure in the pumping chamber and thus conveys the oil from the inlet port to the outlet port.
  • It owns the rotor has a relatively smooth round outer surface, which only due to its eccentric orbit generates the pressure increase in the liquid.
  • such an eccentrically rotating rotor in a cylindrical housing is hardly suitable due to its unstructured lateral surface in a gaseous medium in the pump chamber.
  • a rotor of a wind energy converter by which the wind energy is converted into electrical energy.
  • the rotors consist of a shaft mounted in a stator, are arranged at the equiangular intervals outwardly projecting rotor blades.
  • the rotor blades are designed as a symmetrical wing of a wing of an aircraft, which has a cylindrical surface in the flow direction and thereby has a convex bulge, which converges at an acute angle to the rear.
  • the rotor blades are aligned in the wind direction so that the passing air as a gaseous medium in accordance with the Bernoulli equation causes a pressure difference through which the rotor mounted in the stator is set in a rotary motion. Since such a wing at its acute-angled converging edge causes a disturbing vortex formation, indentations are provided on the airfoil transversely to the wind direction. As a result, on the upper side, a lower pressure than on the bottom, resulting in an additional buoyancy, whereby the vortex formation is reduced and the energy conversion should be feasible with a higher efficiency.
  • such a rotor is provided exclusively for use in air or gaseous media and hardly usable because of its long rotor blades and thus necessary housing diameter with liquid media.
  • turbomachine rotor in which at least one carrier disk is mounted on a supported shaft, on the outer cylindrical surface of which projecting short blades are arranged which circulate in a gaseous medium.
  • This rotor is arranged in a stator housing and is driven by the shaft at a high speed. In this case, the gaseous medium is pressed from an inlet opening with a high compression effect into an outlet opening.
  • such a turbomachine rotor is usually not suitable for liquid media, since these are not compressible and therefore the thin blades could easily be damaged.
  • the pump consists of a housing in which a rotatable eccentric ring is arranged, in which an outer and an inner impeller are rotatably mounted.
  • the inner impeller is an inner rotor with arranged on its outer circumferential surface of a plurality of teeth, which is rotatably disposed in an outer rotor.
  • the outer rotor encloses the inner rotor with its inner circumferential surface, on which also inwardly directed teeth are arranged.
  • both the inner and the outer teeth extend over the entire length of the lateral surface and consist essentially of a convex symmetrical elevation, wherein arranged on the outer surface of the inner rotor six convex elevations and on the inner surface of the outer rotor seven convex elevations are.
  • the inner cavity of the outer rotor is in each case connected to an inlet and an outlet opening, which are located opposite one another.
  • the rotational movement of the inner rotor also causes rotational movement of the outer rotor in the eccentric ring, resulting in a series of variable volume chambers between form the teeth of the inner and outer rotor. Thereby, a fluid in the chambers is sucked into the enlarging chambers and ejected from the decreasing chambers.
  • a hydraulic fluid is provided as the fluid, which is pressed by the pressure differences thus generated from the inlet opening into the outlet opening. Since such a rotor consists of at least two toothed parts arranged coaxially with one another, which still have to have a different number of teeth and engage precisely with one another only at the most accurate design, such a rotor assembly is very complicated to manufacture and is equipped with a series of parts subject to friction are wear-dependent.
  • the invention is therefore an object of the invention to provide a universally applicable rotor for a variety of types of turbomachinery, which is robust and virtually maintenance-free and beyond easy to produce.
  • the invention has the advantage that due to the Bernoulli effect due to the movement of the rotor or the flow of a gaseous or liquid medium creates a negative pressure effect above the airfoil profile by the airfoil on one of the lateral surfaces, so that such a rotor both in turbomachinery for liquid as well as gaseous media can be used. Since the pressure or suction effect is not generated by the formation of circumferential sealing chambers, thus advantageously a medium mixed with solids can be promoted, so that such rotors also a continuous transport of bulk materials or dispersions are well suited.
  • the invention also has the advantage that due to the aerodynamic wing profile only a small vortex formation in the medium used and out of storage no contact with a stator or other rotor parts occurs, so that turbomachinery, which are equipped with such a rotor, operate very quiet and also hardly have flow or friction losses. Since the rotor according to the invention is hollow inside and only by a flat airfoil on one of the lateral surfaces generates the pressure difference, this is produced with very low weight, so that even small masses must be accelerated, which advantageously also overall in connection with the low friction and the low flow turbulences a turbomachine with high efficiency can be achieved.
  • the rotor according to the invention and a turbomachine equipped therewith can be used not only in the driven state for conveying or pressure generation, but can also be used to produce a rotational speed in the flow-correct introduction of a pressurized medium, in order to advantageously generate energy such as electricity from hydropower or wind power.
  • Fig. 1 the drawing is shown as a turbomachine, a pump 1 in perspective, which contains a single-stage hollow rotor 2 as a pump rotor having on an outer surface 4 nine wing profile elements 3, between which passage openings 5 to the inner cavity 6 are arranged.
  • the pump 2 is a version which is preferably operated with water as a liquid medium.
  • the pump 2 consists essentially of a stationary housing 7 as a stator in which the pump rotor 2 is arranged.
  • the rotor is rotatably mounted in the housing 7 in two bearings 8 and has in its center a shaft 9 which is connected to a drive motor 9, not shown.
  • the housing 7 is formed substantially cylindrical and contains on its outer circumferential surface Aüslassö réelle 11 for discharging the water to be pumped.
  • an inlet opening 10 is provided for the inlet of the water to be pumped to the cavity 6, which is connectable to a feed line, not shown.
  • the inlet opening 10 is connected to the cavity 6 of the rotor 2 and forms with this an inlet chamber 12.
  • a pump 1 can basically all liquid media such. As water, oil and the like, as well as all liquids that are mixed with solids, such. As dispersions are transported.
  • the pump 1 described above is shown in front view, from which in detail the arrangement and design of the rotor 2 can be seen.
  • the rotor 2 consists essentially of a cylindrical Impeller 20, which has inside a cylindrical cavity 6, which forms an inlet chamber 12 in the illustrated pump 1.
  • nine convex elevations 3 are arranged distributed in equal angular portions, which form an axially extending airfoil on the outer tangential lateral surface 4 of the rotor 2.
  • the rotor 2 Since the rotor 2 has on its outer tangential lateral surface 4 a plurality of airfoil elements 3, which also form a negative pressure region in a rotation according to the Bernoulli effect in gaseous media such as air, all gaseous media as well as the gaseous media interspersed with bulk materials can thus also be transported, be compressed or sucked.
  • gaseous media such as air
  • passages 5 are provided to the inner cavity 6 or to the inlet chamber 12 of the pump 1, in which there is the medium to be pumped, such as water.
  • the axial design of the pump 1 is in detail in Fig. 3 the drawing shown in plan view.
  • Out Fig. 3 The drawing shows that the rotor 2 is constructed like a lamella in the axial direction. These slats are cut out or punched out of flat sheets, preferably with the aid of a laser, because of the airfoil profile 3.
  • the rotor 2 mainly consists of lamellar rings 13 and an array of lamellar elements 14 which form the impeller 20.
  • the laminar rings 13 are in Fig. 4 the drawing and the lamellar elements 14 in Fig. 5
  • the in Fig. 3 The rotor 1 shown in the drawing consists of three arrangements of lamella elements 14, on whose outer side surfaces in each case a lamellar ring 13 is attached.
  • the lamellar rings 13 and the lamellar elements 14 are usually made of the same material, which may also consist of other metals, hard plastics, synthetic fiber composites or ceramics depending on the medium used.
  • Each lamellar ring 13 has inside a circular bore 23, for example, 250 mm diameter and a smallest outer diameter of about 360 mm.
  • the lamellar ring 13 preferably contains nine identical angular ranges of 40 °, on the outer tangential lateral surface 4 each have a convex elevation 19 is arranged, which merges against the direction of rotation 18 flat with a sloping slope in a discharge area 24 and forms a wing profile 3.
  • the convex elevation 19 preferably has an elevation 19 of approximately 45 mm with respect to the outgoing end and has a radius of approximately 20 mm.
  • the sloping profile region 24, which runs counter to the direction of rotation 18, has a concave curvature with a radius of 167 mm and extends over a length of approximately 70 mm.
  • the convex elevation 19 with the sloping concave outgoing area 24 thus forms on the lateral surface 4 a profile of a wing of aircraft after.
  • the wing profile 3 ends in a slightly rising top 25, which acts as a spoiler and largely prevents turbulence at the tear-off.
  • each lamellar ring 13 of preferably similar Wing profiles 3 are formed, which are arranged in the same angular ranges and the same distance from the axis of rotation 26.
  • lamellar elements 14 are arranged for the execution of the illustrated pump rotor 2, which likewise have the same airfoil profile 3 as the lamellar rings 13 at their outer radial edges.
  • the individual fin elements 14 are congruently aligned with the airfoil 3 with a lamellar ring 13 or with other fin arrangements and thereby represent an axial impeller or an impeller part, the on its outer tangential lateral surface 4 a uniform axially aligned Wing profile 3 forms.
  • the lamellar elements 14 are arranged tangentially spaced from each other and connected in total with the lamellar rings 13, wherein the distance between the lamellar elements forms a passage opening 5, through which the intended medium of the inner cylindrical cavity 6 by the negative pressure along the sloping airfoil profile. 3 is sucked outward by the Bernoulli effect.
  • the individual fin elements 14 are provided in their rear region with a convex curvature 15 and in its front region with a concave curvature 16; which allow a largely eddy-free flow during rotation.
  • the convex curvature 15 at the inner edge is also in a concave curvature, which corresponds to the radius of the bore 23 of the plate ring 13, for example, 125 mm.
  • the rotor 2 forms inside an axially continuous cylindrical cavity 6 as an inlet chamber 12th
  • star-shaped connecting elements are preferably provided, which are torsionally rigid with the drive shaft 9 and preferably connected to at least one of the lamellar rings 13.
  • the airfoil 3 can also be arranged on the inner tangential lateral surface, wherein the rotor 2 then has a circular outer surface 4, whereby the flow direction reverses and the outlet chamber 21 in the cavity 6 of the impeller 20 and the rotor 2 is formed.
  • the rotor 2 is driven at a predetermined rotational speed and direction 18, so that on the outer circumferential surface 4 in the direction of rotation 18 behind the convex elevation 19 after the Bernoulli effect, a negative pressure or a pressure difference to the surrounding gaseous or liquid Medium forms, so that from the pressure higher interior space 6, the medium is sucked to the outside.
  • the pressure difference depends essentially on the speed or the peripheral speed of the impeller 20.
  • the pressure difference increases approximately linearly until the vortex formation at the trailing edge or other turbulence elements becomes so great that it results in a significant backpressure.
  • this can be reduced by an advantageous embodiment, in particular the tear-off edge and by the formation of circular inlet 12 and outlet chambers 21, so that at speeds of at least 10,000 rpm a linear increase in pressure takes place.
  • the flow rate per unit of time can also be increased at the same time, but this is limited by the cross-sectional areas of the passage openings 5.
  • the flow rate or the Flow volume can be increased in a simple manner by increasing the surface of the airfoil 3. Basically, a pressure difference with only one airfoil 3 on the circumference of the rotor 2 and the impeller 20 is already generated.
  • nine airfoils 3 were arranged in a circle around the tangential outer rotor shell 4, but also a smaller as well as a higher number of profile surfaces can be executed.
  • Such a rotor 2 with at least one airfoil profile 3 need not be cylindrical, but may also have a spherical or conical outer surface 4, through which a pressure difference can be generated.
  • such a rotor also requires no closed inlet 12 and outlet chambers 21, since even a rotation within a gaseous or liquid medium without housing part generates a pressure difference, which can only be used by a supply or supply line, which only to one of the inputs or outlet chambers 21 must be connected.
  • a turbomachine with a closed inlet chamber connected to a pipe as a suction machine can also be designed for gaseous media or as a vacuum cleaner.
  • a rotor 2 with a closed outlet chamber 21 can advantageously be used as a compressor or blower for a gaseous medium or as a pump for transporting or equalizing the pressure of liquid media.
  • a rotor 2 can also be used to generate a speed at an existing pressure difference of a surrounding medium and for generating energy in the presence of water or air pressure differences.
  • a plurality of impellers 20 are arranged axially adjacent to each other and separated by separate outlet chambers 21.
  • the four illustrated impellers 20 are arranged on a common drive shaft 9, which is mounted in two bearings 8 on a stator and the housing part. All vanes 20 are surrounded by a multi-part housing 7, which has three partitions 22 and thereby forms four outlet chambers 21, in each of which a similar impeller 20 is rotatably arranged.
  • the impeller 20 described in the drawing is formed and basically consists of nine on the outer surface 4 arranged airfoils 3, between which passage openings 5 are provided to the inner cavity 6.
  • a first inlet opening 10 is provided to the outer region of the housing 7 as a circular recess, which establishes a connection to the cavity 6 of the first impeller 20 as an inlet chamber 12.
  • This first inlet opening 10 the proposed gaseous or liquid medium is supplied so that it passes into the first inlet chamber 12 formed as a cavity 6 of the first impeller 20.
  • an inlet opening is provided to the third impeller, in the subsequent two outlet chambers each have a further equal increase in pressure, so that such a four-stage pump leads to a four times higher pressure increase as in a single-stage pump 1 with only one impeller 20.
  • Such a multi-stage pump As turbomachine can be equipped with a variety of pressure increase stages, so that it can be produced depending on the intended speed almost any pressure increases.
  • Such a multi-stage pump as a turbomachine can also be formed with radial steps.
  • a plurality of impellers 20 are arranged coaxially with each other with different outer diameters and offset by a common drive shaft 9 in rotation.
  • a coaxial turbomachine not only very high pressures can be generated, but also convey high passage volumes per unit time by the high effective surface of the airfoils.
  • a further particular embodiment of the invention is shown, which shows a drive turbine preferably for a liquid medium.
  • a single-stage cylindrical rotor 2 is provided with arranged on its outer circumferential surface airfoils 3 and passage openings 5 to its cavity, which is arranged in a cylindrical housing 7.
  • the housing 7 contains at its one axial end an inlet opening 10 and its other axial end an outlet opening 11 which is formed like a bottle neck.
  • the arranged in the housing 7 rotor 2 is driven by its inlet opening 10 via a shaft 9 through which the preferably liquid medium such.
  • B. Water Water is supplied.
  • the water By a rotation, the water is sucked into the surrounding housing as the outlet chamber 21, so that in this an overpressure arises, which emerges from the streamlined narrow bottleneck-like outlet opening 11 into the surrounding medium.
  • the water flows at a certain outflow velocity into the surrounding standing water, whereby a turbine-like recoil effect is generated.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Insulation, Fastening Of Motor, Generator Windings (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Rotary Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP06762493A 2005-10-19 2006-07-07 Rotor für eine strömungsmaschine und eine strömungsmaschine Active EP1937980B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
SI200630607T SI1937980T1 (sl) 2005-10-19 2006-07-07 Rotor za pretočni stroj in pretočni stroj
PL06762493T PL1937980T3 (pl) 2005-10-19 2006-07-07 Wirnik do maszyny przepływowej i maszyna przepływowa

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005049938A DE102005049938B3 (de) 2005-10-19 2005-10-19 Rotor für eine Strömungsmaschine und eine Strömungsmaschine
PCT/EP2006/006686 WO2007045288A1 (de) 2005-10-19 2006-07-07 Rotor für eine strömungsmaschine und eine strömungsmaschine

Publications (2)

Publication Number Publication Date
EP1937980A1 EP1937980A1 (de) 2008-07-02
EP1937980B1 true EP1937980B1 (de) 2009-12-30

Family

ID=37060347

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06762493A Active EP1937980B1 (de) 2005-10-19 2006-07-07 Rotor für eine strömungsmaschine und eine strömungsmaschine

Country Status (20)

Country Link
US (1) US20090022585A1 (hr)
EP (1) EP1937980B1 (hr)
JP (1) JP2009511824A (hr)
KR (1) KR20080072847A (hr)
CN (1) CN101365882B (hr)
AT (1) ATE453803T1 (hr)
AU (1) AU2006303660B2 (hr)
BR (1) BRPI0617523A2 (hr)
CA (1) CA2626288A1 (hr)
DE (3) DE102005049938B3 (hr)
DK (1) DK1937980T3 (hr)
EA (1) EA012818B1 (hr)
ES (1) ES2343139T3 (hr)
HR (1) HRP20100174T1 (hr)
PL (1) PL1937980T3 (hr)
PT (1) PT1937980E (hr)
RS (1) RS51350B (hr)
SI (1) SI1937980T1 (hr)
UA (1) UA92043C2 (hr)
WO (1) WO2007045288A1 (hr)

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WO2010009544A1 (en) * 2008-07-21 2010-01-28 Dion Andre Wind turbine with side deflectors
US20130164160A1 (en) * 2010-07-12 2013-06-27 Tohoku University Magnetic pump
PL2535558T3 (pl) * 2011-06-16 2017-09-29 Zeki Akbayir Sposób i urządzenie do wytwarzania siły napędowej przez wytwarzanie różnic ciśnienia w zamkniętym układzie gaz/ciecz
UA119134C2 (uk) 2012-08-08 2019-05-10 Аарон Фьюстел Роторні пристрої з розширюваними камерами, що мають регульовані проходи для робочого плинного середовища, а також системи, що мають такі пристрої
CN104421164B (zh) * 2013-08-20 2018-04-27 李刚 旋转式通用流体压缩装置及应用
CN104564802B (zh) * 2015-01-06 2017-02-22 浙江理工大学 一种带有减阻槽的无蜗壳离心通风机
CN105275884B (zh) * 2015-08-15 2019-11-29 何家密 动力式叶泵的增强及其应用

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DE4319291C1 (de) * 1993-06-11 1994-07-21 Hans Erich Gunder Rotor für einen Windenergiekonverter mit einer in einer zur Windrichtung senkrechten Ebene liegenden, vorzugsweise vertikal verlaufenden Drehachse des Rotors
DE4402378C1 (de) * 1994-01-27 1995-03-23 Malchow Gmbh Maschbau Windkraftanlage als Vertikalachsenrotor mit feststehenden, asymmetrisch geformten Rotorblättern
JP2716375B2 (ja) * 1994-10-12 1998-02-18 マルコム・マックロード タービン装置
US5711408A (en) * 1996-05-09 1998-01-27 Dana Corporation Reversible gerotor pump
US5788471A (en) * 1996-06-11 1998-08-04 Eaton Corporation Spool valve wheel motor
CA2219062C (en) * 1996-12-04 2001-12-25 Siegfried A. Eisenmann Infinitely variable ring gear pump
JP3369453B2 (ja) * 1997-12-18 2003-01-20 治生 折橋 圧縮空気発生装置
US6210116B1 (en) * 1998-11-05 2001-04-03 John E. Kuczaj High efficiency pump impeller
US6375412B1 (en) * 1999-12-23 2002-04-23 Daniel Christopher Dial Viscous drag impeller components incorporated into pumps, turbines and transmissions
DE50202167D1 (de) * 2002-03-01 2005-03-10 Hermann Haerle Zahnringmaschine mit Zahnlaufspiel

Also Published As

Publication number Publication date
CN101365882B (zh) 2012-03-21
SI1937980T1 (sl) 2010-05-31
JP2009511824A (ja) 2009-03-19
WO2007045288A1 (de) 2007-04-26
AU2006303660A1 (en) 2007-04-26
US20090022585A1 (en) 2009-01-22
PL1937980T3 (pl) 2010-06-30
HRP20100174T1 (hr) 2010-05-31
ES2343139T3 (es) 2010-07-23
DE102007003088B3 (de) 2007-08-30
BRPI0617523A2 (pt) 2011-07-26
RS51350B (en) 2011-02-28
EA012818B1 (ru) 2009-12-30
DE502006005806D1 (de) 2010-02-11
ATE453803T1 (de) 2010-01-15
PT1937980E (pt) 2010-03-31
DE102005049938B3 (de) 2007-03-01
CN101365882A (zh) 2009-02-11
DK1937980T3 (da) 2010-05-10
EP1937980A1 (de) 2008-07-02
KR20080072847A (ko) 2008-08-07
EA200801103A1 (ru) 2008-10-30
CA2626288A1 (en) 2007-04-26
AU2006303660B2 (en) 2012-02-02
UA92043C2 (ru) 2010-09-27

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