US20090022585A1 - Rotor for a Rotary Machine and a Rotary Machine - Google Patents

Rotor for a Rotary Machine and a Rotary Machine Download PDF

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Publication number
US20090022585A1
US20090022585A1 US12/083,803 US8380306A US2009022585A1 US 20090022585 A1 US20090022585 A1 US 20090022585A1 US 8380306 A US8380306 A US 8380306A US 2009022585 A1 US2009022585 A1 US 2009022585A1
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United States
Prior art keywords
rotor
rotary machine
impeller
chamber
lateral surface
Prior art date
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Abandoned
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US12/083,803
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English (en)
Inventor
Zeki Akbayir
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Individual
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Individual
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Publication of US20090022585A1 publication Critical patent/US20090022585A1/en
Abandoned legal-status Critical Current

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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 rotary machine according to the preamble of claim 1 and to a rotary machine according to the preamble of claim 11 .
  • Rotary machines are distinguished in that they produce a pressure difference in a gaseous or liquid medium or are driven by a pressure difference in a medium of this type.
  • rotary machines of this type generally have a rotor which is rotatably mounted in the gaseous or liquid medium relative to a stator and produces, by way of its shape or arrangement, a pressure difference or converts the pressure difference in the medium into a rotational movement.
  • rotary machines of this type include, in the first place, most types of pumps, compressors, turbomachines, turbines or wind energy converters which have a broad range of designs of rotors and are usually rotatably mounted in a housing as a stator.
  • DD 293 181 A5 discloses a rotary machine in the form of a pump having a cylindrical or conical rotor which is eccentrically mounted in a pump housing.
  • This rotor is connected to a drive and produces on rotation a crescent-shaped revolving pump chamber which conveys preferably oil as a liquid from an inlet opening into an outlet opening.
  • This pump which is based on the hydrodynamic principle, produces during rotation in the crescent-shaped revolving housing an oil wedge which leads to a rise in pressure in the pump chamber and thus conveys the oil from the inlet opening into the outlet opening.
  • the rotor has a relatively smooth round outer lateral surface which produces the rise in pressure in the liquid exclusively owing to its eccentric path of revolution. Nevertheless, an eccentrically revolving rotor of this type in a cylindrical housing is hardly suitable, owing to its unstructured lateral surface, in a gaseous medium in the pump chamber.
  • DE 103 19 003 A1 discloses a rotor of a wind energy converter by means of which wind energy is converted into electrical energy.
  • the rotors consist of a shaft which is mounted in a stator and on which outwardly projecting rotor blades are arranged at constant-angle intervals.
  • the rotor blades are in this case formed as a symmetrical wing of an airfoil of an aircraft that possesses in the flow direction a cylindrical lateral surface and accordingly has a convex protrusion which tapers to the rear at an acute angle.
  • the rotor blades are in this case oriented in the wind direction in such a way that the wind which sweeps past brings about, as a gaseous medium and in accordance with Bernoulli's equation, a pressure difference which causes rotational movement of the mounted rotor in the stator.
  • a wing of this type causes on its edge which tapers at an acute angle a disruptive eddy formation, indentations are provided on the wing profile transversely to the wind direction. This gives rise to a lower pressure on the upper side than on the underside, leading to additional lift, as a result of which the eddy formation is reduced and more efficient energy conversion should be possible.
  • a rotor of this type is provided exclusively for use in aeriform or gaseous media and, owing to its long rotor blades and the housing diameter necessitated thereby, can hardly be used with liquid media.
  • DE 42 23 965 A1 discloses a turbomachine rotor in which at least one support disk is mounted on a mounted shaft and on the outer cylindrical lateral surface of which are arranged projecting short blades which revolve in a gaseous medium.
  • This rotor is arranged in a stator housing and is driven via the shaft at a high rotational speed. In this case, the gaseous medium is pressed from an inlet opening into an outlet opening with a high condensing effect.
  • a turbomachine rotor of this type is generally not suitable for liquid media, as such media are non-compressible, so the thin blades could easily become damaged.
  • a rotor pump which comprises an internally toothed rotor and has a very robust design of an internally toothed rotor.
  • the pump consists of a housing containing a rotatable eccentric ring in which an outer impeller and an inner impeller are rotatably mounted.
  • the inner impeller is an inner rotor which has a plurality of teeth arranged on its outer lateral surface and is rotatably arranged in an outer rotor.
  • the outer rotor encloses the inner rotor with its inner lateral surface on which inwardly directed teeth are likewise arranged.
  • both the inner and the outer teeth extend over the entire length of the lateral surface and consist substantially of a convex symmetrical elevation, six convex elevations being arranged on the outer lateral surface of the inner rotor and seven convex elevations being arranged on the inner lateral surface of the outer rotor.
  • the inner cavity of the outer rotor is in this case respectively connected to an inlet opening and an outlet opening which oppose each other.
  • the rotational movement of the inner rotor also gives rise to a rotational movement of the outer rotor in the eccentric ring, thus forming a series of chambers having variable volumes between the teeth of the inner and outer rotor.
  • a fluid located in the chambers is drawn into the expanding chambers and out of the contracting chambers.
  • the fluid provided is in this case a hydraulic liquid which is pressed from the inlet opening into the outlet opening as a result of the pressure differences thus produced.
  • a rotor of this type consists of at least two toothed parts which are arranged coaxially with one another and must also have a differing number of teeth and mesh with one another with a precise fit only when designed with maximum precision, a rotor arrangement of this type is highly complex to manufacture and equipped with a number of parts which are subject to friction and dependent on wear.
  • the invention is therefore based on the object of providing a universally usable rotor for a large number of designs of rotary machines that is robust and almost maintenance-free while at the same time being simple to manufacture.
  • the invention has the advantage that, as a result of the airfoil profile on one of the lateral surfaces of the rotor, owing to the Bernoulli effect resulting from the movement of the rotor or the flow of a gaseous or liquid medium, a reduced pressure effect is produced above the airfoil profile, thus allowing a rotor of this type to be used in rotary machines both for liquid and for gaseous media.
  • a medium laced with solids can thus advantageously also be conveyed, so rotors of this type are also highly suitable for continuous conveyance of bulk materials or dispersions.
  • the invention has the advantage that the flow-beneficial airfoil profile gives rise to only slight eddy formation in the medium used and, apart from the bearings, there is no contact with a stator or other rotor parts, so rotary machines which are equipped with a rotor of this type operate particularly quietly and display almost no flow or frictional losses.
  • the rotor according to the invention is internally hollow and produces the pressure difference merely by way of a flat airfoil profile on one of the lateral surfaces, the rotor can be manufactured so as to be particularly light, so only low masses have to be accelerated, thus as a whole advantageously allowing a highly efficient rotary machine to be achieved, the low friction and the low flow turbulences notwithstanding.
  • the low rotor mass and the substantially symmetrical formation and centric rotation give rise to only low centrifugal force effects, so a rotor of this type can advantageously be operated at high rotational speeds. This allows even high pressure differences at high flow speeds to be produced, as a result of which high outputs of the gaseous or liquid medium provided or of the solids contained therein can at the same time advantageously be achieved.
  • the rotor according to the invention and a rotary machine equipped therewith can not only be utilized in the driven state for conveyance or producing pressure but can also be used, on flow-correct introduction of a pressurized medium, to produce rotational speed in order to produce energy, such as for example electricity, advantageously from water power or wind power.
  • higher pressures can, in the case of axial stages and at a constant flow rate, advantageously be produced or, in the case of coaxial stages, the raising of the profile surface, while the pressure difference remains constant, advantageously allows still higher flow rates to be conveyed.
  • FIG. 1 is a perspective view of a pump comprising a single-stage pump rotor
  • FIG. 2 is a front view of the pump comprising the pump rotor
  • FIG. 3 is a plan view of the pump comprising the pump rotor
  • FIG. 4 shows a lamella ring of an impeller for the pump rotor
  • FIG. 5 shows an arrangement of lamella elements of an impeller for the pump rotor
  • FIG. 6 is a sectional view of a pump comprising a multistage pump rotor
  • FIG. 7 is a sectional view of a drive turbine.
  • FIG. 1 of the drawings is a perspective view of, as the rotary machine, a pump 1 having a single-stage hollow rotor 2 , as a pump rotor, which has on an outer lateral surface 4 nine airfoil profile elements 3 between which passage openings 5 to the inner cavity 6 are arranged.
  • the pump 2 shown is a design which is operated preferably with water as a liquid medium.
  • the pump 2 consists substantially of a stationary housing 7 as the stator, in which the pump rotor 2 is arranged.
  • the rotor is, in the housing 7 , rotatably mounted 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 substantially cylindrical in its formation and contains on its outer lateral surface an outlet opening 11 for removing the water to be pumped.
  • An inlet opening 10 which is connectable to a feed line (not shown), is provided on the left-hand end face or lateral surface of the housing 7 to allow the water to be pumped to enter the cavity 6 .
  • the inlet opening 10 is connected to the cavity 6 of the rotor 2 and forms therewith an inlet chamber 12 .
  • a pump 1 of this type can in principle be used to convey all liquid media, such as for example water, oil and the like, and also all liquids which are mixed with solids, such as for example dispersions.
  • FIG. 2 of the drawings is a front view, showing in detail also the arrangement and formation of the rotor 2 , of the pump 1 described hereinbefore.
  • the rotor 2 consists substantially of a cylindrical impeller 20 which has on the inside a cylindrical cavity 6 which, in the case of the pump 1 shown, forms an inlet chamber 12 .
  • Nine convex elevations 3 which form an axially extending airfoil profile on the outer tangential lateral surface 4 of the rotor 2 , are arranged on the outer lateral surface 4 of the rotor 2 , distributed in identical angular portions.
  • the rotor 2 has on its outer tangential lateral surface 4 a plurality of airfoil profile elements 3 which, on rotation, form, as a result of the Bernoulli effect, a reduced pressure region even in gaseous media such as for example air, all gaseous media, such as gaseous media permeated with bulk materials, can thus also be conveyed, condensed or drawn in.
  • gaseous media such as for example air
  • FIG. 3 of the drawings is a detailed plan view of the axial formation of the pump 1 .
  • FIG. 3 of the drawings reveals that the rotor 2 is lamellar in its construction in the axial direction. These lamellae are, owing to the airfoil profile 3 made of flat metal sheets, preferably cut out or punched out with the aid of a laser.
  • the rotor 2 consists mainly of lamella rings 13 and an arrangement of lamella elements 14 which form the impeller 20 .
  • FIG. 4 of the drawings is a more detailed view of the lamella rings 13 and FIG. 5 of the drawings is a more detailed view of the lamella elements 14 which, as an axial pack of lamellae, form the impeller 20 with the tangential lateral surfaces 4 .
  • the rotor 1 shown in of lamella elements 14 and a respective lamella ring 13 is fastened to its outer lateral surfaces.
  • the lamella ring 13 preferably consists of a flat steel sheet which is protected against corrosion caused by aqueous liquids or consists of a stainless high-grade steel.
  • Both the lamella rings 13 and the lamella elements 14 are usually made of the same material which, depending on the medium used, can also consist of other metals, hard plastics materials, synthetic fiber composite materials or ceramics.
  • Each lamella ring 13 has on the inside a circular hole 23 having a diameter of, for example, 250 mm and a smallest outer diameter of approx. 360 mm.
  • the lamella ring 13 contains preferably nine similar angular regions, each of 40°, and has arranged on its outer tangential lateral surface 4 in each case a convex elevation 19 which, counter to the direction of rotation 18 , merges flat at a descending inclination with a run-out region 24 and forms an airfoil profile 3 .
  • the convex elevation 19 has relative to the running-out end preferably an elevation 19 of approx. 45 mm and possesses a radius of approx. 20 mm.
  • the descending-profile region 24 which runs out counter to the direction of rotation 18 , has a concave curvature with a radius of 167 mm and extends over a length of approx. 70 mm.
  • the convex elevation 19 with the descending concave running-out region 24 thus imitates on the lateral surface 4 a profile of an airfoil wing of aircraft.
  • the airfoil profile 3 ends in this case in a slightly rising tip 25 which acts as a spoiler and substantially prevents turbulences on the tear-off edge.
  • each lamella ring 13 is formed by preferably similar airfoil profiles 3 which are arranged in identical angular regions and at the same distance from the axis of rotation 26 .
  • the individual lamella elements 14 are connected, in congruent alignment with the airfoil profile 3 , to a lamella ring 13 or to other lamella arrangements and accordingly constitute an axial impeller or an impeller part which forms on its outer tangential lateral surface 4 a uniform, axially oriented airfoil profile 3 .
  • the lamella elements 14 are however arranged tangentially set apart from one another and connected as a whole to the lamella rings 13 , the distance between the lamella elements forming a passage opening 5 through which the medium provided is drawn outward by suction from the inner cylindrical cavity 6 , as a result of the reduced pressure, along the descending airfoil profile 3 , owing to the Bernoulli effect.
  • the individual lamella elements 14 are provided in their rear region with a convex curvature 15 and in their front region with a concave curvature 16 which allow a substantially eddy-free flow during the rotation.
  • the concave curvature 15 on the inner edge also merges with a concave curvature which corresponds to the radius of the hole 23 in the lamella ring 13 of, for example, 125 mm.
  • the rotor 2 forms on the inside an axially continuous cylindrical cavity 6 as the inlet chamber 12 .
  • Star-shaped connecting elements which are connected to the drive shaft 9 in a torsionally rigid manner and preferably to at least one of the lamella rings 13 , are provided for fastening the impeller 20 to the drive shaft 9 .
  • the airfoil profile 3 can also be arranged on the inner tangential lateral surface, the rotor 2 then having on the outside a circular lateral surface 4 , as a result of which the direction of flow is reversed and the outlet chamber 21 is formed in the cavity 6 of the impeller 20 or of the rotor 2 .
  • the rotor 2 is driven at a predetermined rotational speed and in a predetermined direction of rotation 18 , so a reduced pressure or difference in pressure from the surrounding gaseous or liquid medium forms on the outer lateral surface 4 in the direction of rotation 18 after the convex elevation 19 in accordance with the Bernoulli effect, so the medium is drawn outward out of the inner chamber 6 in which the pressure is higher.
  • the pressure difference depends substantially on the rotational speed or the circumferential speed of the impeller 20 .
  • the pressure difference rises approximately linearly until the eddy formation on the tear-off edge or other turbulence elements becomes so great as to yield a significant counterpressure. This can however be reduced by an advantageous formation, in particular, of the torn-off edge and by the formation of a circular inlet 12 and outlet chambers 21 , so at rotational speeds of at least 10,000 rpm the pressure rises linearly.
  • a high pressure difference can at the same time also allow an increase in the flow rate per unit of time, although this is limited by the cross-sectional surface areas of the passage openings 5 . Nevertheless, the flow rate or the flow volume can easily be increased also by enlarging the surface area of the airfoil profile 3 .
  • a pressure difference can be produced with just one airfoil profile 3 on the circumference of the rotor 2 or of the impeller 20 .
  • nine airfoil profiles 3 were preferably arranged circularly around the tangential outer rotor sleeve 4 , although both a smaller and a larger number of profile surfaces can also be embodied.
  • a rotor 2 of this type comprising at least one airfoil profile 3 does not have to be cylindrical but can rather also have a spherical or conical outer lateral surface 4 by means of which a pressure difference can also be produced.
  • a rotor of this type does not require any closed-off inlet 12 or outlet chambers 21 either, as simply rotation within a gaseous or liquid medium without a housing part reduces a pressure difference which can be utilized merely by means of a discharge or feed line which must be connected merely to one of the inlet 12 or outlet chambers 21 .
  • the possibility of utilizing the pressure compensation determines substantially the design of the rotary machine.
  • a rotary machine having a closed-off inlet chamber connected to a line as a suction machine can also be formed for gaseous media or as a vacuum cleaner.
  • a rotor 2 having a closed-off outlet chamber 21 can advantageously be used as a compressor or blower for a gaseous medium or as a pump for the conveyance or for the pressure compensation of liquid media.
  • a rotor 2 of this type can however also be used to produce rotational speed if there is a difference in pressure from a surrounding medium and to produce energy if there are differences in the water or air pressure.
  • a plurality of impellers 20 are arranged axially next to one another and separated from one another by separate outlet chambers 21 .
  • the four impellers 20 shown are arranged on a common drive shaft 9 which is mounted in two-bearings 8 on a stator and the housing part. All of the impellers 20 are surrounded by a multipart housing 7 which has three intermediate walls 22 and accordingly forms four outlet chambers 21 in each of which a similar impeller 20 is rotatably arranged.
  • Each impeller is in this case formed like the impeller 20 described with reference to FIG. 1 to 5 of the drawings and consists basically of nine airfoil profiles 3 which are arranged on the outer lateral surface 4 and between which passage openings 5 to the inner cavity 6 are provided.
  • a first inlet opening 10 to the outer region of the housing 7 is provided as a circular recess which establishes a connection to the cavity 6 of the first impeller 20 as an inlet chamber 12 .
  • the gaseous or liquid medium provided is supplied to this first inlet opening 10 , so the gaseous or liquid medium enters the first inlet chamber 12 , which is formed as the cavity 6 , of the first impeller 20 .
  • a multistage pump of this type as a rotary machine can be equipped with a large number of pressure increase stages, thus allowing almost any desired increases in pressure to be established, depending on the rotational speed provided.
  • a multistage pump of this type as a rotary machine can also be formed with radial stages.
  • a plurality of impellers 20 having outer diameters of different sizes are arranged coaxially in one another and made to rotate by a common drive shaft 9 .
  • a rotary machine of such coaxial construction allows not only very high pressures to be produced but rather also, as a result of the high effective surface area of the airfoil profiles, high flow volumes per unit of time to be conveyed.
  • FIG. 9 of the drawings shows a further particular type of embodiment of the invention showing a drive turbine preferably for a liquid medium.
  • a single-stage cylindrical rotor 2 which has airfoil profiles 3 arranged on its outer lateral surface 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 at its other axial end an outlet opening 11 which is formed in the manner of a bottleneck.
  • the rotor 2 arranged in the housing 7 is driven by means of its inlet opening 10 via a shaft 9 by means of which the preferably liquid medium, such as for example water, is also supplied Rotation causes the water to be drawn into the surrounding housing as an outlet chamber 21 , thus producing therein excess pressure which issues from the flow-beneficial narrow bottleneck-type outlet opening 11 into the surrounding medium.
  • the water flows at a specific outflow speed into the surrounding stagnant water, thus producing a turbine-like recoil effect. This allows preferably water vehicles to be driven or liquids to issue at high pressure as a function of direction into similar or different media.

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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)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Insulation, Fastening Of Motor, Generator Windings (AREA)
  • Rotary Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US12/083,803 2005-10-19 2006-07-07 Rotor for a Rotary Machine and a Rotary Machine Abandoned US20090022585A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005049938.4 2005-10-19
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

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US20090022585A1 true US20090022585A1 (en) 2009-01-22

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US12/083,803 Abandoned US20090022585A1 (en) 2005-10-19 2006-07-07 Rotor for a Rotary Machine and a Rotary Machine

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US8950169B2 (en) 2012-08-08 2015-02-10 Aaron Feustel Rotary expansible chamber devices having adjustable working-fluid ports, and systems incorporating the same
US10077755B2 (en) 2011-06-16 2018-09-18 Zeki Akbayir Method and device for producing a driving force by bringing about differences in a closed gas/liquid system

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Publication number Priority date Publication date Assignee Title
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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US4201512A (en) * 1977-08-23 1980-05-06 Cerla N.V. Radially staged drag turbine
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US20130164160A1 (en) * 2010-07-12 2013-06-27 Tohoku University Magnetic pump
US10077755B2 (en) 2011-06-16 2018-09-18 Zeki Akbayir Method and device for producing a driving force by bringing about differences in a closed gas/liquid system
US8950169B2 (en) 2012-08-08 2015-02-10 Aaron Feustel Rotary expansible chamber devices having adjustable working-fluid ports, and systems incorporating the same
US9080568B2 (en) 2012-08-08 2015-07-14 Aaron Feustel Rotary expansible chamber devices having adjustable arcs of rotation, and systems incorporating the same
US9309766B2 (en) 2012-08-08 2016-04-12 Aaron Feustel Refrigeration system including a rotary expansible chamber device having adjustable working-fluid ports
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EP1937980A1 (de) 2008-07-02
AU2006303660B2 (en) 2012-02-02
ATE453803T1 (de) 2010-01-15
DE502006005806D1 (de) 2010-02-11
EA012818B1 (ru) 2009-12-30
DE102005049938B3 (de) 2007-03-01
WO2007045288A1 (de) 2007-04-26
JP2009511824A (ja) 2009-03-19
DK1937980T3 (da) 2010-05-10
EA200801103A1 (ru) 2008-10-30
CN101365882B (zh) 2012-03-21
PL1937980T3 (pl) 2010-06-30
CA2626288A1 (en) 2007-04-26
RS51350B (en) 2011-02-28
UA92043C2 (ru) 2010-09-27
PT1937980E (pt) 2010-03-31
BRPI0617523A2 (pt) 2011-07-26
AU2006303660A1 (en) 2007-04-26
ES2343139T3 (es) 2010-07-23
HRP20100174T1 (hr) 2010-05-31
CN101365882A (zh) 2009-02-11
KR20080072847A (ko) 2008-08-07
SI1937980T1 (sl) 2010-05-31
DE102007003088B3 (de) 2007-08-30
EP1937980B1 (de) 2009-12-30

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