EP1448894B1 - Selbstansaugende hybridpumpe - Google Patents

Selbstansaugende hybridpumpe Download PDF

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Publication number
EP1448894B1
EP1448894B1 EP02787368A EP02787368A EP1448894B1 EP 1448894 B1 EP1448894 B1 EP 1448894B1 EP 02787368 A EP02787368 A EP 02787368A EP 02787368 A EP02787368 A EP 02787368A EP 1448894 B1 EP1448894 B1 EP 1448894B1
Authority
EP
European Patent Office
Prior art keywords
rotor
pump
hybrid pump
hybrid
rotor blades
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.)
Expired - Lifetime
Application number
EP02787368A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1448894A1 (de
Inventor
Thomas Salomon
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tecalemit GmbH and Co KG
Original Assignee
Horn GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Horn GmbH and Co KG filed Critical Horn GmbH and Co KG
Publication of EP1448894A1 publication Critical patent/EP1448894A1/de
Application granted granted Critical
Publication of EP1448894B1 publication Critical patent/EP1448894B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable

Definitions

  • the invention relates to a hybrid pump according to the preamble of claim 1.
  • centrifugal pumps In the construction of pumps for the promotion of fluids, especially liquids, the problem is that can be achieved with known centrifugal pumps, although a high efficiency and low operating noise of the pump, but these pumps are not self-priming, so a column of liquid from the Standstill out can not suck itself when the centrifugal pump is vented. This is particularly disadvantageous if such pumps have only short operating times and the pumped liquid column at standstill due to a height difference again runs out of the interior of the pump. Therefore, centrifugal pumps often have additional units with which before the actual operation of the centrifugal pump, the liquid column can be conveyed into the housing interior and thus the centrifugal pump does not run dry, but the housing interior is filled with liquid from the beginning.
  • Such a further developed vane pump is shown in DE 195 45 045 A1, in which the blades of the vane pump are mounted on a rotor and formed elastically, so that the aerodynamically curved wings of the rotor move during the entire rotational movement of the rotor along the inner surface of the housing interior and abut on this under variable bias.
  • the wings of the rotor separate individual volumes within the housing interior from each other, wherein the eccentricity between the rotor and the housing interior a corresponding delivery of a fluid and a pressure build-up in principle known for vane pump is possible.
  • the flexibility of the aerodynamically shaped wing of the rotor in this case has the advantage that only slight wear between the Gescouseinnenwandung and the blades of the rotor occurs because the wings adapt under elastic bias to the different distances to the housing inner wall and create the Gescouseinnenwandung.
  • the efficiency of this pump is by design not particularly high and the wear against e.g. Centrifugal pumps much higher.
  • Object of the present invention is therefore to develop a pump which is on the one hand self-priming and at the same time can work at high efficiencies and, moreover, is inexpensive to manufacture.
  • the invention relates to a pump with a housing, in each of which at least one suction port and a pressure port opens and in whose substantially circular enclosed housing interior, a rotor is arranged eccentrically, the periphery of a number of spaced, at least partially radially arranged rotor blades Has a resiliently deformable under the influence of centrifugal force elastically deformable material.
  • Such a pump is further developed in that the eccentricity of the rotor relative to the housing interior and the elasticity of the rotor blades are selected such that each rotor blade in a first range of low speed with its radially projecting end portion in the course of one revolution of the rotor is not or only temporarily applied to peripheral portions of the housing interior, whereas in a second region of higher speed all rotor blades with their radially projecting end under centrifugal force substantially during the entire revolution of the rotor abut against the inner wall of the housing interior.
  • This makes it possible to operate in the first range of low speed, the hybrid pump so that it works mainly as a pure flow pump substantially corresponding to a centrifugal pump.
  • the hybrid pump After exceeding a threshold value for the speed, however, the hybrid pump changes its operating behavior by deforming the rotor blades under the influence of centrifugal force elastically so that they rest with their radially projecting end portions substantially during the entire revolution of the rotor to the inner wall of the housing interior and thus partial volumes of Separate housing interior from each other liquid-tight.
  • This makes it possible to ensure self-priming of a liquid column with the hybrid pump operating essentially in accordance with a conventional vane pump, even if the hybrid pump has previously been in a ventilated state, for example due to a standstill.
  • a drive motor will accelerate the liquid pump operating without liquid content very quickly to its maximum speed, so that the hybrid pump is operated almost immediately in the second region of higher speed and works in this operating state so-to-speak as a vane pump self-priming and promotes fluid into the housing interior. If the pump is then filled with liquid as a result, the rotational speed of the drive motor will decrease to such an extent due to the acting counterrotating torques and the influence of the liquid that the operating state of the hybrid pump passes into the first low-speed region in which the hybrid pump operates quasi according to a centrifugal pump and promotes fluid at high efficiency.
  • the hybrid pump according to the invention therefore offers two essential functions of pumps, namely the self-priming and the operation with the highest possible efficiencies, in a single pump design.
  • the hybrid pump according to the invention is particularly for applications of great advantage in which often only briefly the operation at full capacity is required, but at the same time due to frequent downtime slumping of the liquid column from the pump can not be avoided.
  • this otherwise expensive constructions with check valves or the like. Must be provided to keep the liquid column in the pump, which are expensive and prone and beyond also negatively affect the efficiency of the pump, as the suction line by such internals no longer can be designed so freely throughout.
  • an advantageous embodiment provides that the elastic deformability of the rotor blades is selected such that from a certain speed of the rotor, the deformation of the rotor blades due to the centrifugal force compensates for the eccentricity, so that substantially all ends of the rotor blades abut the inner wall of the housing interior and each other form separated compression spaces.
  • the resulting due to the eccentricity of the hybrid pumping behavior can be adjusted depending on the elasticity of the rotor blades so that abut from a limit speed, the rotor blades not only on parts of the peripheral surface of the housing interior, but during the entire rotation with this in contact and thus the Partial volumes of the housing interior separate from each other, as is basically known in conventional vane pumps.
  • the hybrid pump can also promote particles contaminated with particles, since the deformability of the rotor blades permits corresponding deformations in the passage of even larger particles in which rigid rotor blades would break.
  • each rotor blade has an aerodynamically curved cross-sectional shape in which each rotor blade touches the inner wall of the housing interior under elastic prestressing, even at a slow rotation of the rotor at least at one point.
  • the interior of the hybrid pump is divided into two separate areas, at the same time can be adapted by the cross-sectional shape of both the elasticity of the rotor blades and their investment on the Gescouseinnenwandung under bias in wide limits to different operating conditions.
  • the rotor blades have a blade-shaped curvature and are resiliently deformable in the circumferential direction.
  • An improved effect on the elastic deformation of the rotor blades can be achieved if, during operation of the hybrid pump in the first region of low speed tribological forces of the fluid to be delivered act on each rotor blade, which deform the rotor blades in the direction of the axis of rotation of the rotor.
  • the limit speed may be relatively high, so that in the operating state of the hybrid pump according to a centrifugal pump and adequate flow rates can be realized.
  • the operating behavior of the hybrid pump also depends on the conveyed medium because of the deformability of the rotor blades.
  • Low viscosity fluids will be different due to different Toughness set a different deformation of the rotor blades at the same speed as in highly viscous fluids or gases, with the centrifugal force effects play a role.
  • the rotor blades are made of a plastic material, preferably of thermoplastic materials or polyurethane or EPDM or nitrile or neoprene.
  • a plastic material preferably of thermoplastic materials or polyurethane or EPDM or nitrile or neoprene.
  • Such materials provide sufficient deformability with high dimensional stability even over permanent load.
  • such materials are inexpensive to process, for example by means of injection molding and thus to produce the rotor blades or even the whole rotor inexpensively.
  • the running behavior of the hybrid pump is very quiet.
  • rotor and rotor blades are integrally formed.
  • the rotor and the rotor blades can be shaped simultaneously and integrally in one processing step, for example by means of injection molding or other production methods.
  • the number of parts of the pump is drastically reduced, which also reduces assembly costs and increased reliability.
  • the rotor blades are used from the resilient material in associated recesses of the rotor and fixed thereto. This allows the rotor itself to be made of a different material than the rotor blades, for instance with regard to strength properties or other boundary conditions.
  • substantially cylindrical thickenings are arranged on the radially projecting from the rotor ends of the rotor blades, which create a sealing against the inner wall of the housing interior and separate individual cells of the hybrid pump in the operating state corresponding to a vane pump.
  • the eccentricity of the arrangement of the rotor in the range up to 20%, preferably up to 2% of the outer diameter of the rotor including the rotor blades. Such a value for the eccentricity can be bridged without problems with the deformation of the rotor blades and without endangering the strength properties of the rotor blades.
  • a particularly simple construction of the hybrid pump can be realized if the rotor and the housing consist of essentially disc-shaped basic shapes which can be connected to one another in a fluid-tight manner.
  • prefabricated components can be mounted simplified, and the fluidic sealing of the individual parts to each other over the large contact surfaces of the individual disk-shaped basic shapes is easy to implement.
  • the inlet and / or the outlet of the fluid in the housing interior is perpendicular to the axis of rotation of the rotor of the hybrid pump. In this case, the fluid flows substantially tangentially to the circumference of the rotor blades. In another embodiment, it is also conceivable that the inlet and / or the outlet of the fluid into the housing interior takes place at least with a component parallel to the axis of rotation of the rotor of the hybrid pump.
  • FIG. 1 shows a schematic representation of a section through a hybrid pump 1 according to the invention, wherein the section extends approximately in the dividing plane of the plate-shaped housing 2 of the hybrid pump 1.
  • a rotor 5 is mounted rotatably with rotor blades 6 arranged thereon about an axis of rotation 8.
  • the axis of rotation 8 in this case has an eccentric arrangement to the symmetry axis 9 of the housing interior 3, wherein the size of the eccentricity is shown under the item number 14.
  • the arrangement of the axis of rotation 8 and the axis of symmetry 9 and the essential structure of such a hybrid pump 1 is basically known from DE 195 45 045 A1 and should therefore be explained only insofar as is relevant to the present invention.
  • the rotor blades 6 are in this case formed of an elastically deformable material which can deform from the blade-like configuration according to the figure 1 under the action of centrifugal force during rotation of the rotor 5 along the direction of rotation 17 such that the cylindrical thickenings 7 at the ends of Rotor blades 6 move more and more radially outward as the speed increases and during create the rotation over an ever longer circumferential length of the inner wall 4 of the housing interior 3.
  • the thickenings 7 of the rotor blades 6 are then in constant contact with the inner wall 4 of the housing interior 3, as can be seen in more detail in FIG.
  • the rotor blades 6 spread radially outward from the axis of rotation 8, and more and more contact the inner wall 4.
  • the rotor blades 6 also change their curved cross-sectional shape a little, in that in the regions along the circumferential direction of the Gezzauseinnenwandung 4, which are farther away from the axis of rotation 8 of the rotor 5, the rotor blades 6 in a stretched configuration.
  • this elongated configuration will then spring back in and return to the configuration which in this area in FIG. 1 or in FIG recognize.
  • the material of the rotor blades 6 may consist for example of thermoplastic materials, polyurethanes, EPDM, nitrile or neoprene, such materials having both a relatively large elastic deformability and high strength and low abrasion under load due to frictional contact.
  • the rotor 5 with the rotor blades 6 arranged thereon is, as can better be seen in FIG. 2, fixed on a drive shaft 13 on which a drive motor (not shown) can be flanged.
  • hybrid pump 1 The function of the hybrid pump 1 according to the invention can be described as follows in comparison with the combined in the hybrid pump 1 principles of centrifugal pump and vane pump.
  • a conventional centrifugal pump is not self-priming, so that before starting such a centrifugal pump, a fluid must be introduced into the suction side 10 and through the inlet 12 in the centrifugal pump. If the centrifugal pump is then put into operation, a volumetric flow of the fluid is fed in via the rotor 5 and the rotor blades 6 through the suction side 10 in the inflow direction 15, so that the centrifugal pump does not dry anymore. This volume flow occurs after passing through the housing interior through the pressure side 11 in the outflow 16 again from the centrifugal pump. At relatively low speeds below the limit speed, the hybrid pump according to the invention substantially exhibits these properties, since the rotor blades 6 have no or only a temporary contact with the housing inner wall 4, as in a centrifugal pump.
  • This self-priming property of the hybrid pump 1 according to the invention has the significant advantage that the use of the hybrid pump 1 requires no previous filling of the pump interior, which otherwise must be done either manually or by additional means. Without a user of such a hybrid pump 1 notices this, is sucked in the ventilated state of the hybrid pump 1 fluid in the operating state of the hybrid pump 1 according to a vane pump because the drive motor runs virtually empty and thus reaches a high speed above the limit speed, and then goes the hybrid pump 1 after successful suction automatically in the conveying operation according to a centrifugal pump, which allows high efficiency with low wear. This is always particularly useful when such pumps are only a short time in operation and then put into operation again after a long period of inactivity.
  • FIG. 4 shows in a sectional view and in the associated FIG. 5 a side view of a corresponding hybrid pump 1 according to the invention, in which the suction channel 10 is not within the plane perpendicular to the axis of rotation of the rotor 5 runs.
  • This makes it possible to make the inflow of the fluid through the suction channel 10 in the inflow 15 either as shown in solid lines in Figure 5 at an angle of eg 45 degrees, which of course is also possible, an inflow 15 'by a dashed lines shown intake passage 10 'substantially parallel to the axis of rotation 8 of the rotor 5 to realize. This may be fluidly interesting for certain applications.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP02787368A 2001-11-28 2002-11-17 Selbstansaugende hybridpumpe Expired - Lifetime EP1448894B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10158146A DE10158146A1 (de) 2001-11-28 2001-11-28 Selbstansaugende Hybridpumpe
DE10158146 2001-11-28
PCT/DE2002/004241 WO2003048582A1 (de) 2001-11-28 2002-11-17 Selbstansaugende hybridpumpe

Publications (2)

Publication Number Publication Date
EP1448894A1 EP1448894A1 (de) 2004-08-25
EP1448894B1 true EP1448894B1 (de) 2007-05-09

Family

ID=7707124

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02787368A Expired - Lifetime EP1448894B1 (de) 2001-11-28 2002-11-17 Selbstansaugende hybridpumpe

Country Status (12)

Country Link
US (1) US7014417B2 (ja)
EP (1) EP1448894B1 (ja)
JP (1) JP2005511959A (ja)
CN (1) CN1596343A (ja)
AT (1) ATE362050T1 (ja)
AU (1) AU2002351678A1 (ja)
BR (1) BR0214484A (ja)
CZ (1) CZ2004654A3 (ja)
DE (2) DE10158146A1 (ja)
ES (1) ES2286306T3 (ja)
PL (1) PL368880A1 (ja)
WO (1) WO2003048582A1 (ja)

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EP1789682B1 (de) * 2004-09-16 2009-11-11 Horn GmbH & Co. KG Hybridpumpe
US7393181B2 (en) 2004-09-17 2008-07-01 The Penn State Research Foundation Expandable impeller pump
US7355199B2 (en) * 2004-11-02 2008-04-08 E.I. Du Pont De Nemours And Company Substituted anthracenes and electronic devices containing the substituted anthracenes
DE202005007789U1 (de) * 2005-05-12 2006-09-21 Horn Gmbh & Co. Kg Pumpe, insbesondere Hybridpumpe
EP3115070B8 (en) 2006-03-23 2019-05-08 The Penn State Research Foundation Heart assist device with expandable impeller pump
EP2005376A2 (en) 2006-03-31 2008-12-24 Orqis Medical Corporation Rotary blood pump
DE202007012565U1 (de) * 2007-09-07 2009-01-22 Horn Gmbh & Co. Kg Hybridpumpe zum Fördern eines flüssigen Pumpmediums
DE202007013162U1 (de) 2007-09-19 2009-02-12 Horn Gmbh & Co. Kg Pumpenbaugruppe zum Fördern von Flüssigkeiten
AU2010266166B2 (en) * 2009-07-01 2015-09-03 The Penn State Research Foundation Blood pump with expandable cannula
DE102010028061A1 (de) * 2010-04-22 2011-10-27 Robert Bosch Gmbh Flügelzellenpumpe
US8597170B2 (en) 2011-01-05 2013-12-03 Thoratec Corporation Catheter pump
US8485961B2 (en) 2011-01-05 2013-07-16 Thoratec Corporation Impeller housing for percutaneous heart pump
WO2012094641A2 (en) 2011-01-06 2012-07-12 Thoratec Corporation Percutaneous heart pump
US8591393B2 (en) 2011-01-06 2013-11-26 Thoratec Corporation Catheter pump
US8721517B2 (en) 2012-05-14 2014-05-13 Thoratec Corporation Impeller for catheter pump
US9327067B2 (en) 2012-05-14 2016-05-03 Thoratec Corporation Impeller for catheter pump
GB2504176A (en) 2012-05-14 2014-01-22 Thoratec Corp Collapsible impeller for catheter pump
US9872947B2 (en) 2012-05-14 2018-01-23 Tc1 Llc Sheath system for catheter pump
US9446179B2 (en) 2012-05-14 2016-09-20 Thoratec Corporation Distal bearing support
US9358329B2 (en) 2012-07-03 2016-06-07 Thoratec Corporation Catheter pump
US9421311B2 (en) 2012-07-03 2016-08-23 Thoratec Corporation Motor assembly for catheter pump
EP4186557A1 (en) 2012-07-03 2023-05-31 Tc1 Llc Motor assembly for catheter pump
KR101491211B1 (ko) * 2012-10-30 2015-02-06 현대자동차주식회사 차량용 가변 오일 펌프
US11033728B2 (en) 2013-03-13 2021-06-15 Tc1 Llc Fluid handling system
JP6530367B2 (ja) 2013-03-13 2019-06-12 ティーシーワン エルエルシー 流体導出入システム
US11077294B2 (en) 2013-03-13 2021-08-03 Tc1 Llc Sheath assembly for catheter pump
US9308302B2 (en) 2013-03-15 2016-04-12 Thoratec Corporation Catheter pump assembly including a stator
EP3797810A1 (en) 2013-03-15 2021-03-31 Tc1 Llc Catheter pump assembly including a stator
KR101669519B1 (ko) * 2014-02-28 2016-10-26 동아대학교 산학협력단 Orc 발전 시스템용 터빈
WO2015160990A1 (en) 2014-04-15 2015-10-22 Thoratec Corporation Catheter pump introducer systems and methods
EP3131599B1 (en) 2014-04-15 2019-02-20 Tc1 Llc Catheter pump with access ports
WO2015160942A1 (en) 2014-04-15 2015-10-22 Thoratec Corporation Catheter pump with off-set motor position
EP3131615B1 (en) 2014-04-15 2021-06-09 Tc1 Llc Sensors for catheter pumps
US10449279B2 (en) 2014-08-18 2019-10-22 Tc1 Llc Guide features for percutaneous catheter pump
WO2016118781A2 (en) 2015-01-22 2016-07-28 Thoratec Corporation Motor assembly with heat exchanger for catheter pump
WO2016118784A1 (en) 2015-01-22 2016-07-28 Thoratec Corporation Attachment mechanisms for motor of catheter pump
WO2016118777A1 (en) 2015-01-22 2016-07-28 Thoratec Corporation Reduced rotational mass motor assembly for catheter pump
US9907890B2 (en) 2015-04-16 2018-03-06 Tc1 Llc Catheter pump with positioning brace
WO2018017678A1 (en) 2016-07-21 2018-01-25 Thoratec Corporation Fluid seals for catheter pump motor assembly
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Also Published As

Publication number Publication date
US20050019198A1 (en) 2005-01-27
WO2003048582A1 (de) 2003-06-12
DE10158146A1 (de) 2003-06-18
DE50210134D1 (de) 2007-06-21
CN1596343A (zh) 2005-03-16
JP2005511959A (ja) 2005-04-28
US7014417B2 (en) 2006-03-21
EP1448894A1 (de) 2004-08-25
PL368880A1 (en) 2005-04-04
ES2286306T3 (es) 2007-12-01
CZ2004654A3 (cs) 2004-08-18
ATE362050T1 (de) 2007-06-15
BR0214484A (pt) 2004-09-14
AU2002351678A1 (en) 2003-06-17

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