EP0956451A2 - Pompe a rotors a engrenages pour milieux liquides - Google Patents

Pompe a rotors a engrenages pour milieux liquides

Info

Publication number
EP0956451A2
EP0956451A2 EP97952049A EP97952049A EP0956451A2 EP 0956451 A2 EP0956451 A2 EP 0956451A2 EP 97952049 A EP97952049 A EP 97952049A EP 97952049 A EP97952049 A EP 97952049A EP 0956451 A2 EP0956451 A2 EP 0956451A2
Authority
EP
European Patent Office
Prior art keywords
pump
chamber
gerotor
housing
suction
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.)
Withdrawn
Application number
EP97952049A
Other languages
German (de)
English (en)
Inventor
Ludwig Mokesch
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.)
Bavaria Pumpen GmbH
Original Assignee
Bavaria Pumpen GmbH
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
Priority claimed from DE29621361U external-priority patent/DE29621361U1/de
Application filed by Bavaria Pumpen GmbH filed Critical Bavaria Pumpen GmbH
Publication of EP0956451A2 publication Critical patent/EP0956451A2/fr
Withdrawn legal-status Critical Current

Links

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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0046—Internal leakage control
    • 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
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the invention relates to a gerotor pump with a pump housing, a cylindrical chamber in the pump housing, a gerotor barrel set accommodated in the cylindrical chamber and which is to be driven in rotation by a pump drive shaft in order to pump the liquid to be pumped from a suction connection of the pump into a suction area of the chamber aspirate and expel the aspirated pump liquid from an ejection region of the chamber to a pressure connection of the pump, the pump drive shaft coupled to the gerotor drive unit for driving it extending from a drive side of the pump through a bore in the housing into the cylindrical chamber, and wherein the pump has a shaft seal surrounding the pump drive shaft, which seals the pump against leakage of leakage liquid to the drive side.
  • the gerotor pumps are valve-free, compact, self-priming pumps with positive displacement, which produce a continuous pump flow with a minimum of pressure fluctuations.
  • the gerotor liquid pumps have a gerotor pump set, which consists of a ring rotor or outer rotor with internal teeth, which is rotatably mounted in the cylindrical chamber with little radial play to the periphery of the chamber, and an inner rotor with external teeth, which is driven by the pump drive shaft, the number of teeth of the inner rotor is 1 smaller than the number of teeth of the outer rotor.
  • the axis of rotation of the inner rotor runs parallel to the axis of rotation of the outer rotor with an eccentric offset, so that the inner rotor driven by the pump drive shaft is only at a certain angle.
  • the suction angle area of the chamber is connected to a suction connection via a suction slot in a connection cover which closes the end of the chamber on the side opposite the drive side of the pump.
  • the discharge angle range of the chamber is connected via a discharge slot in the connection cover to a pressure connection, so that a flow is generated from the suction connection to the pressure connection of the pump when the gerotor barrel is rotated.
  • the housing consists of at least three housing blocks, namely the connection cover, an eccentric ring receiving the gerotor barrel set and a bearing cover on the drive side of the pump, through which the drive shaft is guided, the drive shaft being outside the housing a shaft coupling is coupled to the shaft of a motor driving the pump.
  • gerotor pumps have been used almost exclusively for pumping mineral oil or similar viscous media, since thinner pump media, especially at high pump pressures, cause sealing problems.
  • Attempts have also already been made to design and use Gerot ⁇ r liquid pumps as water pumps.
  • measures have hitherto been necessary which necessitated a comparatively complicated construction of the pump, a high manufacturing expenditure and a comparatively large number of individual parts.
  • the invention has for its object to provide a gerotor liquid pump of the type mentioned, which can be used as a pump for water or similar low-viscosity media, has a simple and compact structure and yet has a high pumping capacity.
  • the wall surface of the housing which delimits the cylindrical chamber towards the drive side of the pump has a depression which extends along the suction region in the circumferential direction of the chamber and which has a groove in the circumferential surface which surrounds the shaft is connected to the bore in order to be able to discharge leakage liquid located between the bore and the shaft via the groove into the suction area of the chamber.
  • This construction which can be realized with simple means and with little manufacturing effort, has the effect that the inevitable leakage fluid, which is present in particular in the case of thin media with high pressure between the circumference of the shaft and the circumference of the bore, is returned to the suction region of the chamber in an extremely efficient manner and thus the case drain pressure is effectively reduced. Since the groove lies in an area between the chamber and the shaft seal, the case drain pressure on the shaft seal is almost completely reduced, so that a commercially available shaft seal, such as a sealing ring, can be used.
  • the measure according to the invention for reducing the case drain pressure does not require any drainage channels within the shaft, which also benefits the efforts to simplify construction.
  • the depression preferably extends in the shape of an arc in the circumferential direction of the shaft, wherein it is in direct connection with the groove essentially over its entire arc length.
  • the gerotor rotor set has a certain axial play and a certain radial play with the adjacent running surfaces of the chamber.
  • the radial play between the outer circumference of the gerotor barrel and the circumferential surface of the chamber is between 0.025 and 0.06 mm in a preferred embodiment.
  • the axial play between the gerotor barrel set and the respectively opposite end face of the chamber is between 0.02 and 0.035 mm.
  • the pump on the side opposite the drive side, has a connection cover delimiting the cylindrical chamber on the end face with the suction connection and the pressure connection provided thereon, the connection cover having a suction slot connected to the suction connection and the suction region of the chamber. and has an ejection slot in its surface delimiting the chamber, which is connected to the pressure connection and the ejection region of the chamber, and a channel connecting the suction slot to the ejection slot is provided in the connection cover, in which a valve which is to be opened toward the suction slot is arranged.
  • This valve can be a spring-loaded pressure relief valve which opens the channel when a certain maximum opening pressure is reached in the area of the pressure connection and the discharge slot opens against the force of the valve spring.
  • the valve Lst is designed for a certain working pressure and for a certain maximum pressure, which can be up to 60-70 bar in the pump according to the invention. If this maximum pressure is exceeded on the consumer side, the pressure limiting valve ensures that the excess amount is drained off to the suction side and thus forms a reliable overpressure protection integrated in the housing.
  • a desired performance characteristic can be maintained in accordance with the characteristic of the valve spring and the valve construction, in that the valve opens at certain pressures on the pressure side only to such an extent that excess delivery volume reaches the suction side via the channel and the pump otherwise the at the relevant pressure on the pressure side promotes the desired delivery rate according to the desired performance characteristics via the pressure connection to the "consumer". If necessary, the spring can be exchanged for a spring with a different characteristic.
  • the valve has an adjusting mechanism which optionally prestresses the valve spring to a greater or lesser extent and which can be actuated from outside when the valve is installed.
  • the valve is an adjustable flow control valve, which opens the channel more or less depending on the valve position set in order to divert part of the liquid discharged from the discharge area of the chamber and return it to the suction area.
  • the pump housing is constructed in two parts, it consisting of a pump chamber housing block and a connection cover and the cylindrical chamber is formed as a recess in the pump chamber housing block, which is covered on the front side of the pump chamber housing block facing away from the drive side of the pump by the connection cover.
  • the pump housing on the drive side of the pump is connected directly to the housing of a drive motor, in particular an electric motor, the motor shaft of which forms the pump drive shaft.
  • a drive motor in particular an electric motor
  • the motor shaft of which forms the pump drive shaft may also have independent significance in the context of the invention.
  • the motor shaft engages directly in the gerotor barrel, no intermediate shaft coupling is required.
  • the pump housing and the motor housing are preferably connected to one another by common screw arrangements, which already ensure that the motor housing and the pump housing are fixed in the correct position.
  • the gerotor liquid pump according to the invention can be operated at engine speeds between 50 and 6000 rpm, depending on the desired pump output. It is suitable for pumping low-viscosity media such as water, beverages, fuels, HFA hydraulic fluid and the like, although it is not excluded that it can also be used oil pump can be used. It can therefore be used both in the industrial sector and in the private household sector.
  • the pump housing consists of a brass material, in particular special brass or possibly bronze, and the gerotor barrel set consists of a stainless steel.
  • Fig. 1 a shows a first embodiment of the invention in one
  • Fig. 1 b shows a connection cover of the gerotor liquid pump
  • FIG. 1 a in a disassembled state in a plan view (from FIG. 1 a from the left) of an end face to be connected to a pump chamber housing, an area being shown broken away.
  • FIGS. 1 a and 1 b shows a plan view of an end face of the pump chamber housing of the pump according to FIGS. 1 a and 1 b.
  • FIG. 1 d shows a view of the pump chamber housing corresponding to FIG. 1 c, but the gerotor running set has been removed.
  • 2a and 2b show a second embodiment in a representation corresponding to FIGS. 1 a and 1 b.
  • 3a and 3b show a third embodiment in a representation corresponding to FIGS. 1 a and 1 b.
  • FIG. 1 a shows a preferred exemplary embodiment of the invention in a longitudinal section.
  • the gerotor pump 1 has a pump chamber housing 3 with a circular cylindrical recess 5 on the connection face 7 of the pump chamber housing 3.
  • the circular cylindrical recess 5 forms a chamber in which a gerotor running set 9, which is yet to be explained, is received, which is driven by a drive shaft 1 1 of a drive motor 1 3 is driven in rotation.
  • the drive motor 1 3 is arranged with its housing 1 5 directly on the end side 1 7 of the pump chamber housing 3 opposite the connection end face 7.
  • the shaft 1 1 extends through the bore 1 9 into the chamber 5 of the pump chamber housing 3.
  • an inner ring or inner rotor 25 of the gerotor barrel 9 via a coupling 27, e.g. a feather key or the like., coupled for common rotation with the shaft 1 1, wherein the inner ring 25 is arranged coaxially to the shaft 1 1 on the pump-side end portion of the shaft 1 1.
  • the gerotor rotor 9 is held axially movable within its axial play on the shaft 1 1.
  • connection cover 29 which extends over the recess 5 and which has a suction connection 31 and a pressure connection 33.
  • the suction connection 31 is connected to a suction region 37 of the chamber 5 via a suction kidney 35 designed as a ring segment-like recess in the connection cover 29, whereas the pressure connection 33 is connected an ejection kidney 39 designed as a ring segment-like recess in the connection cover 29 is connected to an ejection region 41 of the chamber 5.
  • FIG. 1 c shows in a (not to scale) top view of the connection end face 7 of the pump chamber housing 3, the inner rotor 25 provided with an external toothing and driven by the shaft 11 within an outer rotor 43 formed with an internal toothing.
  • the outer rotor 43 is in the cylindrical chamber 5 is rotatably mounted substantially coaxially to the chamber 5, the common axis of the chamber 5 and the outer rotor 43 being offset parallel to the common axis of the shaft 11 and the inner rotor 25.
  • the inner toothing of the outer rotor 43 has one tooth more than the outer toothing of the inner rotor 25 arranged eccentrically to the outer rotor 43.
  • the position of the suction kidney 35 provided in the connecting cover 29 and the position of the exhaust kidney 39 provided in the connecting cover 29 are approximate indicated at 35 and 39 in projection.
  • a spring-loaded pressure relief valve or pressure relief valve 47 is provided in a channel 49, which is formed in the connection cover 29 and connects the suction connection 31 or the suction kidney 35 with the pressure connection 33 or the discharge kidney 39.
  • the valve body 51 of the pressure relief valve 47 can open against the force of the spring 53 to the suction side (suction kidney 35), depending on the pressure in the area of the pressure connection 33 or the discharge kidney 39.
  • the pressure relief valve 47 then conducts liquid from the pressure side (at 39) to the suction side (at 35).
  • a desired performance characteristic can be maintained in that the valve opens at certain pressures on the pressure side only to such an extent that excess delivery volume reaches the suction side via the channel 49 and the pump otherwise the in which relevant pressure on the pressure side promotes the desired flow rate according to the desired performance characteristics via the pressure connection to the "consumer".
  • the spring 53 can be exchanged for a spring with a different characteristic.
  • the valve 47 has the function of overpressure protection. When a predetermined maximum pressure is reached, the valve opens to maximum passage, so that the channel 49 forms the main flow path and circulates the pump from the pressure side to the suction side.
  • the pressure relief valve 47 also acting as a pressure relief device for the pump 1.
  • valve 47 can alternatively be designed in such a way that it only fulfills the function of overpressure protection.
  • valve spring 53 is supported on the one hand on a shoulder 55 of the valve body 51 - and on the other hand on a screw plug 57 which is screwed into a threaded bore 59 of the connection cover 29.
  • valve tappet connected to the valve body 51 is shown in FIG. 1 a, which is guided with its end remote from the valve body 51 in a bore 63 of the screw plug 57.
  • gerotor pump 1 according to the invention is that despite its simple and compact construction for pumping water or similar thin media, it can be used at pump pressures up to 60-70 bar and pump speeds up to 6000 rpm.
  • the pump 1 according to the invention also has a permanent high performance excellent running properties and a long service life and is also easy to maintain.
  • the running properties of the gerotor pump 1 according to the invention can be optimized when used as a pump for water or aqueous-viscous media if a slight radial play is permitted between the circumference of the outer rotor 43 and the circumference of the cylindrical chamber 5 , this play should preferably be 0.03-0.05 mm.
  • annular groove 68 is provided in the pump chamber housing 3 at a small axial distance from the chamber 5, which surrounds the motor shaft 11.
  • This annular groove 68 is connected to a depression 70 in the bottom of the chamber 5, the depression 70 running in the angular region of the chamber 5 which forms the suction region and over which the suction kidney 35 also extends.
  • the depression 70 preferably has a kidney shape corresponding to the suction kidney 35 and, viewed axially, lies in alignment with the suction kidney 35.
  • This simple construction has the effect that the pressure (approximate operating pressure) occurring via leakage fluid in the small annular gap 72 (gap size, for example 0.2-0.4 mm) between the drive shaft 11 and the bore 19 via the annular groove 68 and the kidney-shaped recess 70 to the suction side of the chamber 5 is reduced to such an extent that in the area between the annular groove 68 and the commercially available shaft sealing ring 23 there is only a small residual liquid pressure, for example 0-0.1 bar, which is present from the sealing ring 23 can be safely accommodated without any sealing problems, especially since commercially available shaft seals are available for pressures of 0.5 - 30 bar.
  • the drive motor 1 3 is arranged directly on the housing block 3 and drives the gerotor running set 9 with its comparatively short motor shaft 1 1.
  • the use of the motor shaft 1 1 directly as a pump shaft avoids the previously usual shaft couplings between the pump shaft and the separate motor shaft.
  • the drive shaft 11 can be centered in a simple manner while avoiding expensive shaft bearings within the pump housing 3, so that low-wear operation is ensured.
  • the direct attachment of the housing of the drive motor 1 3 to the pump housing 3, 29 also leads to the fact that overall a compact, space-saving unit consisting of pump and drive is obtained, the above-mentioned measures for reducing the leakage fluid pressure reliably ensuring that the low-viscosity pump medium is not can penetrate into the motor housing.
  • the relative orientation and centering of the motor 1 3, the pump chamber housing 3 and the connecting cover 29 to one another and the common fastening of these elements to one another is carried out by the screw arrangements 74 which enforce the elements 13, 3 and 29 in the axial direction and fix them to one another reliably and in the correct position.
  • an O-ring seal 76 is provided radially outside the chamber 5 between the connection cover 29 and the connection end face 7 of the pump chamber housing 3.
  • FIGS. 2a and 2b show a second embodiment of a gerotor pump 1 according to the invention in a view corresponding to FIGS. 1 a and 1 b.
  • Elements in FIGS. 2a and 2b which correspond to elements of the pump according to FIGS. 1a-1d are identified with the same reference numerals, so that reference can be made to the description of the first exemplary embodiment.
  • the second exemplary embodiment differs from the first exemplary embodiment in that the structure of the valve 47 is changed.
  • the biasing force of the valve spring 53 can be adjusted without removing the valve 47 in order to adjust the working pressure (performance characteristics) or permissible maximum pressure of pump 1.
  • an adjusting screw 77 passing through the locking screw 57 is provided, on which the axially displaceable guide cylinder 78 of the valve tappet 61 is supported at its end remote from the valve spring 53. If the adjusting screw 77 is now screwed further towards the valve body or valve cone 51, the valve spring 53 supported on the guide cylinder 78 is further compressed and thus increases its biasing force on the valve body 51. The valve body 51 will then lift off its seat at a correspondingly increased pressure on the pressure side of the pump 1 in order to discharge an excess amount of pump liquid to the suction side via the channel 49.
  • 3a and 3b show a third embodiment of a gerotor pump 1 according to the invention, which differs from the first two embodiments by the type of valve 47a.
  • the valve 47a is not designed as a spring-loaded pressure relief valve as in the two previous exemplary embodiments, but rather as an adjustable quantity control valve.
  • the valve body (valve cone) 51 a can be shifted into a position raised from the valve seat 80 by adjusting the adjusting screw 77 a of the adjusting spindle 78 a, in order to be able to variably adjust the gap between valve body 51 a and valve seat 80 and thus the opening width of the valve.
  • a delivery quantity dependent on the setting of the valve can be derived via the channel 49 to the suction side. This changes the maximum delivery rate of the pump at the given pressure.
  • the valve 47a of the third exemplary embodiment of the invention therefore serves to set a respective maximum delivery rate of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention a pour objet une pompe à rotors à engrenages pour milieux aqueux visqueux, présentant de préférence un corps de pompe en deux parties, à savoir l'enveloppe (3) de la chambre de pompe et un couvercle de jonction (29), et comportant, dans l'enveloppe de la chambre de la pompe, une chambre sous forme d'une cavité cylindrique (5), avec des moyens de roulement des rotors à engrenages (9) logés à l'intérieur. Ces moyens (9) sont entraînés en rotation par l'arbre moteur (11) d'un moteur d'entraînement (13) fixé directement sur le corps de pompe. L'arbre moteur (11) est entouré, dans l'enveloppe de la chambre (3), par une rainure (68) qui est directement connectée à une cavité (70) dans la zone d'aspiration de la chambre de pompe, en vue de pouvoir introduire le liquide de fuite, via la rainure (68), dans la zone d'aspiration de la chambre (5). Il est prévu, dans le couvercle de jonction (29), un conduit (49) reliant le côté aspiration au côté refoulement, avec une soupape montée à l'intérieur qui dérive, en fonction de la pression côté refoulement, un débit en excès vers le côté aspiration. La soupape peut être conçue, suivant une variante, comme une soupape de réglage du débit.
EP97952049A 1996-12-11 1997-12-10 Pompe a rotors a engrenages pour milieux liquides Withdrawn EP0956451A2 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE29621361U 1996-12-11
DE29621361U DE29621361U1 (de) 1996-12-11 1996-12-11 Flüssigkeitspumpe nach dem Rotorprinzip
DE29720446U 1997-11-18
DE29720446U DE29720446U1 (de) 1996-12-11 1997-11-18 Gerotorpumpe für flüssige Medien
PCT/EP1997/006902 WO1998026181A2 (fr) 1996-12-11 1997-12-10 Pompe a rotors a engrenages pour milieux liquides

Publications (1)

Publication Number Publication Date
EP0956451A2 true EP0956451A2 (fr) 1999-11-17

Family

ID=26059728

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97952049A Withdrawn EP0956451A2 (fr) 1996-12-11 1997-12-10 Pompe a rotors a engrenages pour milieux liquides

Country Status (3)

Country Link
EP (1) EP0956451A2 (fr)
AU (1) AU5561098A (fr)
WO (1) WO1998026181A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4888158B2 (ja) 2007-02-28 2012-02-29 株式会社ジェイテクト 電動ポンプユニット及び電動オイルポンプ
AT520109B1 (de) * 2017-07-11 2019-09-15 Avl List Gmbh Reversible Pumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2739538A (en) * 1951-12-14 1956-03-27 Eaton Mfg Co Pumping unit with multiple intake ports
DE2333659A1 (de) * 1973-07-02 1975-01-16 Ludwig Mokesch Wasserpumpe
DE8612329U1 (de) * 1986-05-05 1986-08-21 Mokesch, Ludwig, 7570 Baden-Baden Hochleistungsflüssigkeitspumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9826181A3 *

Also Published As

Publication number Publication date
AU5561098A (en) 1998-07-03
WO1998026181A3 (fr) 1998-11-05
WO1998026181A2 (fr) 1998-06-18

Similar Documents

Publication Publication Date Title
DE102007032103B4 (de) Pumpeneinheit mit einer Hauptpumpe und einer in ihrem Fördervolumen verstellbaren Ladepumpe
DE1528949A1 (de) Pumpe mit in der Saugleitung eingebauter,verstellbarer Drossel
WO2000039465A1 (fr) Ensemble de pompes comportant deux pompes hydrauliques
DE4345273C2 (de) Hydraulische Zahnradmaschine (Pumpe oder Motor), insbesondere Innenzahnradmaschine
DE102012001462A1 (de) Innenzahnradpumpe
DE3617732C2 (fr)
DE102005041579B4 (de) Innenzahnradpumpe mit Füllstück
DE19952605A1 (de) Pumpe für ein flüssiges oder gasförmiges Medium
DE3921245A1 (de) Als rotorpumpe ausgebildete kraftstoffoerderpumpe
DE3444392C2 (fr)
EP0956451A2 (fr) Pompe a rotors a engrenages pour milieux liquides
DE102012217484A1 (de) Innenzahnradpumpe, insbesondere für eine hydraulische Fahrzeugbremsanlage
WO1992008051A1 (fr) Pompe a pistons, notamment pompe a pistons radiaux
EP0520286A2 (fr) Pompe à pistons radiaux
DE3242983A1 (de) Regelbare fluegelzellenpumpe
DE102004060554A1 (de) Flügelzellenpumpe
DE4240593A1 (de) Aggregat zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeugs
EP0929743B1 (fr) Pompe a piston radial
DE29720446U1 (de) Gerotorpumpe für flüssige Medien
DE4428410C2 (de) Kompakte Regeleinheit für eine Flügelzellenpumpe
DE3513923C2 (fr)
DE102007039157B4 (de) Flügelzellenpumpe
EP0964159A2 (fr) Pompe du type gerotor
DE3828274A1 (de) Hydraulikpumpe
EP0843096B1 (fr) Dispositif de couplage pour coupler une pompe à vide à une pompe à carburant dans un carter commun

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: 19990608

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20010430

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20010703