EP1789682B1 - Pompe hybride - Google Patents

Pompe hybride Download PDF

Info

Publication number
EP1789682B1
EP1789682B1 EP04786956A EP04786956A EP1789682B1 EP 1789682 B1 EP1789682 B1 EP 1789682B1 EP 04786956 A EP04786956 A EP 04786956A EP 04786956 A EP04786956 A EP 04786956A EP 1789682 B1 EP1789682 B1 EP 1789682B1
Authority
EP
European Patent Office
Prior art keywords
rotor
pumping
hybrid pump
pump according
pump
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.)
Not-in-force
Application number
EP04786956A
Other languages
German (de)
English (en)
Other versions
EP1789682A1 (fr
Inventor
Klaus E. Austmeyer
Jörn DOMMEN
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 EP1789682A1 publication Critical patent/EP1789682A1/fr
Application granted granted Critical
Publication of EP1789682B1 publication Critical patent/EP1789682B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable
    • 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/247—Vanes elastic or self-adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/001—Shear force pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the present invention relates to a hybrid pump for conveying a pumping medium according to the preamble of claim 1.
  • a hybrid pump is understood as meaning a pump which operates as a displacement machine in a first operating mode and as a turbomachine in a second operating mode in order to be able to combine the respective advantages of these two types of pump.
  • a popular turbomachine is the centrifugal pump. It is characterized by a robust design and a simple structure and enables low-noise and low-wear operation to handle large flow rates. Frequent applications of centrifugal pumps are the rapid filling and emptying of containers, the pumping of liquids etc ..
  • centrifugal pumps A disadvantage of the use of centrifugal pumps is the fact that a self-priming operation is not possible. For the start of the centrifugal pump therefore additional priming aids in the form of a Kolbenansauglace o. The like. Provided.
  • a popular displacement machine is the vane pump. Although it allows a self-priming operation, but is connected by the system inherent friction performance with a relatively high operating noise and high wear.
  • One approach to reduce the friction performance shows the DE 36 14 349 A1 , This is a vane pump with a rotor whose rotor sides as usual pass by associated side surfaces of a pump chamber. The rotor sides each have a chamfer such that the formation of a hydrodynamic lubricant film between the rotor sides and the associated side walls of the pump chamber is promoted. Despite this measure, the remaining friction performance is considerable.
  • the pump basically has the characteristics of a centrifugal pump and can only work when starting in the manner of a self-priming vane pump.
  • the known pump ( DE 101 58 146 A1 ), from which the present invention proceeds, shows the above-described behavior of a hybrid pump.
  • the hybrid pump is provided with a housing having an inlet and an outlet having a pumping space. In pumping operation, the pumping medium is conveyed in the pumping space, wherein in idle operation, the pumping space is substantially free of pumping medium.
  • the pump chamber has a cross-sectionally round running surface for a rotor with rotor blades, which is arranged eccentrically in the pump chamber.
  • the hybrid pump operates at high speed initially in the manner of a vane pump in self-priming operation - suction -. Due to the inflow of the pumped medium sucked into the pump chamber, the speed of the rotor is reduced to a speed which is in the rated speed range of the pump. Due to the associated reduction in the centrifugal force and by a suitably chosen elasticity of the rotor blades, the rotor blades lose their contact with the tread, at least in part, as seen along the tread. In the case of the pumping operation in the rated speed range which is thus commencing - rated pumping operation - the pump then shows the characteristic of a centrifugal pump.
  • the pump described above also shows a special feature that has nothing to do with the pumping operation itself.
  • the rotor blades are made of an elastically deformable material and In idling mode, when the rotor is operated at low speed, the running surface of the pump chamber does not contact or only temporarily. As a result, the starting resistance of the pump is particularly low and it quickly reaches its high idle speed.
  • the present invention is based on the problem of designing the known hybrid pump with respect to the suction and pumping operation and further, that the transition of the hybrid pump from vane pump operation in the centrifugal pump operation is not necessarily associated with a speed reduction
  • Essential is the fact that in the nominal pumping operation between the wing tips of the rotor and the running surface forms a lubricating film of pumping medium in the manner of a hydrodynamic sliding bearing. This ensures that there is only liquid friction in the nominal pumping operation between the wing tips and the tread.
  • the above mechanism of action is used here to ensure the above-described transition from vane pump operation to centrifugal pump operation.
  • the design of the rotor and tread are tuned to the rated speed range and viscosity such that the rotor blades, which would contact the tread in idle mode and rotor operated at rated speed in the nominal tamping operation, would be effectively lubricated by the formation of the lubricating film from the tread take off.
  • the hybrid pump goes into centrifugal pump operation.
  • the existing in vane pump solid state friction between the wing tips and the tread of the pump chamber is then transferred to liquid friction.
  • One of the above boundary conditions lies in the design of the eccentricity of the rotor in the pump chamber, which determines the movement of the rotor blades in one rotor revolution. Furthermore, the weight of the rotor blades with respect to the resulting centrifugal force of importance.
  • the surface of the wing tips and the tread, in particular the surface roughness there, are important influencing factors for the formation of the above lubricating film.
  • a special shape of the wing tips can promote the formation of the lubricating film. For example, a corresponding chamfering of the wing tips is advantageous.
  • the mobility of the rotor blades relative to the rotor otherwise results preferably by a resilient or elastic configuration of the rotor.
  • the rotor for ensuring the mobility has hinges between the individual rotor components. This is particularly advantageous if the material of the rotor is not sufficiently yielding and / or elastic, as may be the case in the design of the rotor for chemically aggressive pumping media.
  • Fig. 1 shows a hybrid pump 1 for conveying a pumping medium with a housing 2, wherein the housing 2 has an inlet 3 and an outlet 4. Both the inlet 3 and the outlet 4 open into a pump chamber 5 of the housing 2 in which the pumping medium is pumped in pumping operation. In idle mode, the pump chamber 5 is substantially free of pumping medium. In this idling operation, the suction of the pumping medium via the inlet 3 is required. This will be explained in detail below.
  • the pumping space 5 has a cross-sectionally substantially round running surface 6 for a rotor 7 with rotor blades 8.
  • the running surface 6 is configured annularly with an extension perpendicular to the plane of the drawing and with a central axis 9.
  • Fig. 1 results, the rotor blades 8 are movable relative to the rotor 7 in the other. Due to the eccentricity, the rotor blades 8 are stretched in the lower region of the rotor 7 and compressed in the upper part of the rotor 7.
  • the Fig. 1 . 2 now show the hybrid pump in still to be explained Ansaugetrieb in which the pumping medium to be pumped is sucked through the inlet 3. After the suction of the pumping medium, the nominal pumping operation follows in a predetermined nominal speed range of the rotor 7.
  • the arrangement of the rotor 7 in the pump chamber - eccentricity - and the design of the rotor 7 and the tread 6 in the manner described above tuned to the rated speed range and the viscosity of the pumping medium that in the nominal pumping operation between the wing tips 11 of the rotor. 7 and the running surface 6 forms the likewise described lubricating film of pumping medium in the manner of a hydrodynamic slide bearing. This ensures that in the nominal pumping operation between the wing tips 11 and the tread 6 only fluid friction prevails.
  • hybrid pump can be derived from the general design rules for hydrodynamic plain bearings mentioned in the general part of the description, or determined by experiments. Below are still concrete values for the realization of such a hybrid pump called.
  • the hybrid pump 1 according to the invention in idle mode and in the tread 6 contacting wing tips 11 substantially in the manner of a positive displacement machine, in particular a vane pump, works in self-priming operation - suction mode -.
  • the speed of the hybrid pump 1 in the intake operation may be in the rated speed range, or deviate up or down thereof.
  • the hybrid pump 1 then runs in the rated speed range essentially in the manner of a turbomachine, in particular a centrifugal pump.
  • the wing tips 11 on a formation of the lubricating film in the nominal pumping mode promoting shaping may be a correspondingly arranged chamfer, which is arranged in the direction of travel at the front of the wing tip 11.
  • the wing tips 11 each have a rounded shape seen in their cross-section, which in turn promotes the above-described lifting of the rotor blades 8 of the tread 6.
  • a particularly cost-effective production of the rotor 7 is achieved in that the rotor 7 is designed in one piece. Then it is possible, for example, to produce the rotor 7 by injection molding in a single operation.
  • the rotor 7 may also be advantageous to design the rotor 7 in several pieces, in particular when the rotor 7 is to be composed of different materials. This is the case, for example, if the rotor blades 8 are designed to be elastic and the rotor 7 otherwise rigid.
  • the individual rotor components are connected to one another in a form-fitting manner, preferably glued, riveted, screwed and / or inserted into one another.
  • a particularly preferred embodiment results from the fact that the individual rotor components are connected to each other via hinges.
  • the rotor blades 8 are each connected via a hinge to the rotor 7 in the other.
  • the design of the rotor 7 with hinges is advantageous in particular for the use of a hybrid pump 1 in the chemical field.
  • the rotor blades 8 are each designed in several pieces, wherein the rotor blade components 12, 13 are in turn connected to each other via hinges 14.
  • the rotor blades 8 each have a first sub-wing 12 and a second sub-wing 13, wherein the two sub-wings 12, 13 are connected to each other via a double-jointed hinge 14.
  • This embodiment is particularly advantageous in that the two sub-wings 12, 13 in such a way that the rotor blade 8 is fully extended lie against one another in such a way that the rotor blade 8 is bent over in FIG Fig. 4 is prevented to the left.
  • the bias voltage may be provided in a direction towards the tread 6. Then contact the wing tips 11 of the rotor 7, the tread 6 even at a standstill. But it can also be provided that the rotor blades 8 are biased relative to the rotor 7 in the rest in a direction away from the running surface 6. Then, the rotation of the rotor 7 in the suction operation via the centrifugal force first causes the contacting of the tread 6 by the wing tips 11. The nominal pumping operation then runs again as described above.
  • the rotor 7 with its rotor blades 8 and the side surfaces 15, 16 of the pump chamber 5 is tuned to the nominal speed range and the viscosity of the pumping medium, that in the nominal pumping operation, a lubricating film of pumping medium between the rotor sides 17, 18 and the respective side surface 15, 16 of the pump chamber 5 forms in the manner of a hydrodynamic sliding bearing. This ensures that in the nominal pumping operation between the rotor sides 17, 18 and the side surfaces 15, 16 there is exclusively fluid friction.
  • the bearing of the rotor 7 in the axial direction has a bearing clearance such that an automatic centering of the rotor 7 takes place in the axial direction by the resulting lubricant film on the rotor sides 17, 18
  • the rotor sides 17, 18 are preferably provided with a corresponding chamfer. Seen in the direction of rotation, the chamfer is located on the front side of the respective rotor blade 8.
  • a preferred parameterization is presented, which is particularly suitable for the pumping medium water.
  • an operation of the hybrid pump 1 under normal conditions (room temperature, etc.) is provided.
  • the hybrid pump 1 is also applicable to other pumping media. Then it may be necessary to adapt the parameterization to the material properties of the respective pumping medium.
  • the preferred parameterization of the rated speed range in any case comprises a speed of about 8,000 U / min, the diameter of the rotor 7 at the tread 6 contacting wingtips 11 an average Diameter of about 50 mm. This results in a running speed of the wing tips 11 on the tread 6 of about 21 m / s.
  • the rotor material has a Shore A hardness of approximately 75 measured on the rotor 7 in this preferred parameterization.
  • the running speed of the wing tips 11 on the running surface 6 in the nominal rotational speed range is preferably in a range of about 14 m / s to about 28 m / s, more preferably in a range of about 18 m / s to about 24 m / s.
  • the speeds between about 5,300 U / min to about 10,700 U / min and between about 6,900 U / min to about 9,200 U / min.
  • the rotor 7 is preferably made of an elastomer, for example NBR, FKM, PERBUNAN, VITON, EPDM, PEEK or PP.
  • an elastomer for example NBR, FKM, PERBUNAN, VITON, EPDM, PEEK or PP.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)

Claims (20)

  1. Pompe hybride pour refouler un fluide à pomper, comprenant un carter (2), le carter (2) présentant une entrée (3), une sortie (4) et un espace de pompe (5), le fluide à pomper étant refoulé dans l'espace de pompe (5) au cours du fonctionnement de la pompe, l'espace de pompe (5) étant essentiellement exempt de fluide à pomper en mode de fonctionnement à vide, l'espace de pompe (5) présentant une surface de roulement (6) d'estampage essentiellement ronde ou arrondie pour un rotor (7) avec des pales de rotor (8), le rotor (7) étant disposé excentriquement dans l'espace de pompe (5), les pales du rotor (8) pouvant du reste être mobiles respectivement par rapport au rotor (7) et un mode de fonctionnement nominal de la pompe étant prévu dans une plage de régime nominal prédéterminé du rotor (7),
    caractérisée en ce que
    pendant le mode de fonctionnement à vide et lorsque le rotor (7) fonctionne dans la plage de régime nominal, les pales du rotor (8) viennent en contact avec leurs pointes de pale (11) avec la surface de roulement (6) et en ce que l'agencement du rotor (7) dans l'espace de pompe (5) et la configuration du rotor (7) et de la surface de roulement (6) sont adaptés à chaque fois à la plage de régime nominal et à la viscosité du fluide à pomper de telle sorte qu'un film lubrifiant constitué du fluide à pomper se forme pendant le mode de fonctionnement nominal de la pompe entre les pointes de pales (11) du rotor (7) et la surface de roulement (6), à la manière d'un support sur palier lisse hydrodynamique, de sorte qu'il n'existe qu'un frottement liquide entre les pointes de pales (11) et la surface de roulement (6) pendant le fonctionnement nominal de la pompe.
  2. Pompe hybride selon la revendication 1, caractérisée en ce que la pompe hybride (1) fonctionne en mode de fonctionnement à vide et lorsque les pointes de pales (11) viennent en contact avec la surface de roulement (6) essentiellement à la manière d'une machine volumétrique, notamment d'une pompe à palettes, dans le mode de fonctionnement à auto-aspiration - mode d'aspiration - et en ce que la pompe hybride (1) fonctionne, en mode de fonctionnement nominal de la pompe, essentiellement à la manière d'une machine à écoulement, notamment d'une pompe centrifuge.
  3. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que les pointes de pales (11) présentent une forme favorisant la formation du film lubrifiant dans le mode de fonctionnement nominal de la pompe, de préférence en ce qu'elles sont biseautées de manière correspondante, et plus préférablement, que les pointes de pales (11) présentent à chaque fois une forme ronde vue en section transversale.
  4. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que le rotor (7) est configuré au moins en partie sous forme flexible et/ou élastique, et de préférence en ce que les pales du rotor (8) sont configurées de manière flexible et/ou élastique, et/ou, plus préférablement, en ce que les pales du rotor (8) sont du reste connectées de manière flexible et/ou élastique au rotor (7).
  5. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que le rotor (7) est configuré en une partie.
  6. Pompe hybride selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le rotor (7) est configuré en plusieurs parties.
  7. Pompe hybride selon la revendication 6, caractérisée en ce que les composants individuels du rotor sont connectés par engagement par correspondance géométrique les uns aux autres, de préférence sont collés, rivetés, vissés et/ou enfichés les uns aux autres ou dans les autres.
  8. Pompe hybride selon la revendication 6 ou 7, caractérisée en ce que les composants individuels du rotor sont connectés les uns aux autres par le biais de charnières, de préférence en ce que les pales du rotor (8) sont à chaque fois connectées du reste par le biais d'une charnière au rotor (7).
  9. Pompe hybride selon l'une quelconque des revendications 6 à 8, caractérisée en ce que les pales du rotor (8) sont configurées à chaque fois en plusieurs parties et de préférence en ce que les composants des pales du rotor (12, 13) sont connectés les uns aux autres par des charnières (14).
  10. Pompe hybride selon la revendication 9, caractérisée en ce que les pales du rotor présentent chacune une première pale partielle (12) et une deuxième pale partielle (13) et en ce que les deux pales partielles (12, 13) sont connectées l'une à l'autre par le biais d'une charnière à double articulation (14).
  11. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que les pales du rotor (8) sont précontraintes par rapport au rotor (7) par ailleurs dans la direction de la surface de roulement (6).
  12. Pompe hybride selon l'une quelconque des revendications 1 à 10, caractérisée en ce que les pales du rotor (8) sont précontraintes par rapport au rotor (7) par ailleurs dans une direction s'écartant de la surface de roulement (6) et peuvent être pivotées par rotation du rotor (7) au moyen de la force centrifuge dans la direction de la surface de roulement (6).
  13. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que deux surfaces latérales opposées (15, 16) se raccordent à la surface de roulement (6) de l'espace de la pompe (5), s'étendent à chaque fois perpendiculairement à l'axe de rotation (10) du rotor (7) et les côtés du rotor (17, 18) du rotor (7) passent devant celles-ci.
  14. Pompe hybride selon la revendication 13, caractérisée en ce que le rotor (7) avec ses pales de rotor (8) et les surfaces latérales (15, 16) de l'espace de pompe (5) sont adaptés à la plage de régime nominal et à la viscosité du fluide à pomper de telle sorte qu'un film lubrifiant constitué du fluide à pomper se forme pendant le mode de fonctionnement nominal de la pompe entre les côtés du rotor (17, 18) et la surface latérale respective (15, 16) de l'espace de pompe (5) à la manière d'un support sur palier lisse hydrodynamique, de sorte qu'il n'existe qu'un frottement liquide entre les côtés du rotor (17, 18) et les surfaces latérales (15, 16) pendant le fonctionnement nominal de la pompe.
  15. Pompe hybride selon la revendication 14, caractérisée en ce que les côtés du rotor (17, 18) présentent une forme favorisant la formation du film lubrifiant, de préférence en ce qu'ils sont biseautés de manière correspondante.
  16. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que la plage de régime nominal inclut à chaque fois un régime d'environ 8 000 tr/min.
  17. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que le diamètre du rotor (7), lorsque les pointes de pales (11) viennent en contact avec la surface de roulement (6), présente un diamètre moyen d'environ 50 mm.
  18. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que dans la plage de régime nominal, la vitesse de passage des pointes de pales (11) sur la surface de roulement (6) se situe dans une plage d'environ 14 m/s à environ 28 m/s, de préférence en ce que la vitesse de passage se situe dans une plage d'environ 18 m/s à environ 24 m/s, et plus préférablement, se situe à environ 21 m/s.
  19. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que le matériau du rotor présente une dureté Shore-A mesurée au niveau du rotor (7) d'environ 75.
  20. Pompe hybride selon l'une quelconque des revendications précédentes, caractérisée en ce que le rotor (7) est constitué au moins en partie d'un élastomère, de préférence de NBR, de FKM, de PERBUNAN, de VITON, de EPDM, PEEK ou PP, et/ou en ce que le rotor (7) est au moins en partie constitué de PTFE.
EP04786956A 2004-09-16 2004-09-16 Pompe hybride Not-in-force EP1789682B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2004/010401 WO2006029643A1 (fr) 2004-09-16 2004-09-16 Pompe hybride

Publications (2)

Publication Number Publication Date
EP1789682A1 EP1789682A1 (fr) 2007-05-30
EP1789682B1 true EP1789682B1 (fr) 2009-11-11

Family

ID=34958950

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04786956A Not-in-force EP1789682B1 (fr) 2004-09-16 2004-09-16 Pompe hybride

Country Status (5)

Country Link
EP (1) EP1789682B1 (fr)
AT (1) ATE448407T1 (fr)
DE (2) DE202004021643U1 (fr)
ES (1) ES2335890T3 (fr)
WO (1) WO2006029643A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014225778A1 (de) 2014-12-15 2016-06-16 Zf Friedrichshafen Ag Ölpumpe

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202005007789U1 (de) * 2005-05-12 2006-09-21 Horn Gmbh & Co. Kg Pumpe, insbesondere Hybridpumpe
IT1394039B1 (it) * 2009-05-14 2012-05-25 Amato Pompa per fluidi
CA2677006A1 (fr) * 2009-08-28 2011-02-28 Jean Pierre Hofman Generateur hydraulique (generateur de fluide vecteur)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2948227A (en) * 1958-11-19 1960-08-09 Lord Mfg Co Pump
US3080824A (en) * 1961-02-27 1963-03-12 James A Boyd Fluid moving device
US3734638A (en) * 1970-11-06 1973-05-22 Rockwell Mfg Co Flexible vane turbine pump
US4433967A (en) * 1982-05-17 1984-02-28 Craig Lawrence B Pump impeller
EP0221252A1 (fr) * 1985-10-07 1987-05-13 NOTRON Engineering AG Pompe à cellules avec membranes
DE3614349A1 (de) 1986-04-28 1987-10-29 Rexroth Mannesmann Gmbh Fluegelzellenpumpe sowie dafuer geeigneter fluegel
DE19545045A1 (de) 1995-09-06 1997-03-13 Joma Polytec Kunststofftechnik Flügelzellenpumpe
DE10158146A1 (de) 2001-11-28 2003-06-18 Horn Gmbh & Co Kg Selbstansaugende Hybridpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014225778A1 (de) 2014-12-15 2016-06-16 Zf Friedrichshafen Ag Ölpumpe

Also Published As

Publication number Publication date
DE502004010376D1 (de) 2009-12-24
ES2335890T3 (es) 2010-04-06
ATE448407T1 (de) 2009-11-15
DE202004021643U1 (de) 2009-10-22
EP1789682A1 (fr) 2007-05-30
WO2006029643A1 (fr) 2006-03-23

Similar Documents

Publication Publication Date Title
EP1448894B1 (fr) Pompe hybride a amorcage automatique
WO2011086013A2 (fr) Pompe à palettes
DE102008036273B4 (de) Rotationskolbenpumpe mit Taschen für Schmiermittel
EP1766237B1 (fr) Pompe a vide a une ailette
DE3014519A1 (de) Drehkolbenmaschine, insbesondere zellenpumpe
WO2009127281A1 (fr) Palette d'une pompe à palettes ou d'un compresseur à palettes
WO2016173800A1 (fr) Dispositif pompe
EP1789682B1 (fr) Pompe hybride
EP1597459B1 (fr) Ensemble de pompes
DE4011671C2 (de) Regelbare Flügelzellenpumpe
DE202013000976U1 (de) Flügel für eine Flügelzellenvorrichtung sowie Flügelzellenvorrichtung
DE102013104069B4 (de) Kreiselpumpe und Anordnung zur saugseitigen Radialspaltabdichtung
DE102008045440B4 (de) Drehkolben einer Drehkolbenpumpe und Drehkolbenpumpe
EP2176519A1 (fr) Pompe à vide à palette coulissante
DE4008522C2 (fr)
DE19626211C2 (de) Flügelzellenpumpe
WO2016173799A1 (fr) Dispositif pompe
DE102009029293A1 (de) Zahnradförderpumpe mit einer Antriebswelle, einem Antriebszahnrad und einem anzutreibenden Zahnrad
DE2654991C3 (de) Drehschieberkompressor
DE102010049439A1 (de) Außenzahnradpumpe
DE102021128879A1 (de) Innenzahnradpumpe mit einer Druckkammer und eine Pumpeneinheit
DE19500542B4 (de) Drehkolbenpumpe
EP1722104B1 (fr) Paire de rotors pour un compresseur à vis
DE2751384A1 (de) Exzenterpumpe
WO2009019101A1 (fr) Pompe refoulante

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070103

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502004010376

Country of ref document: DE

Date of ref document: 20091224

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2335890

Country of ref document: ES

Kind code of ref document: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100311

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100211

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20100812

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100212

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20100914

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20100913

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100930

BERE Be: lapsed

Owner name: HORN G.M.B.H. & CO. KG

Effective date: 20110930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100512

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100916

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091111

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20120925

Year of fee payment: 9

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 448407

Country of ref document: AT

Kind code of ref document: T

Effective date: 20110916

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120922

Year of fee payment: 9

Ref country code: DE

Payment date: 20120921

Year of fee payment: 9

Ref country code: ES

Payment date: 20120907

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110916

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20121001

Year of fee payment: 9

Ref country code: FR

Payment date: 20121011

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20120917

Year of fee payment: 9

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20140401

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130916

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004010376

Country of ref document: DE

Effective date: 20140401

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140530

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130916

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130930

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140401

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130930

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140401

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130916

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20150407

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130917