WO2022063585A1 - Groupe moteur-pompe - Google Patents

Groupe moteur-pompe Download PDF

Info

Publication number
WO2022063585A1
WO2022063585A1 PCT/EP2021/074761 EP2021074761W WO2022063585A1 WO 2022063585 A1 WO2022063585 A1 WO 2022063585A1 EP 2021074761 W EP2021074761 W EP 2021074761W WO 2022063585 A1 WO2022063585 A1 WO 2022063585A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
rotor
motor
pump rotor
axis
Prior art date
Application number
PCT/EP2021/074761
Other languages
German (de)
English (en)
Inventor
Jernej MUNIH
Klemen PETRIČ
Original Assignee
Kolektor Group D.O.O.
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 Kolektor Group D.O.O. filed Critical Kolektor Group D.O.O.
Priority to EP21777232.6A priority Critical patent/EP4217610B1/fr
Publication of WO2022063585A1 publication Critical patent/WO2022063585A1/fr

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
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C2/084—Toothed wheels
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor

Definitions

  • the present invention relates to a motor-pump unit for pumping a fluid.
  • the present invention relates to such a motor-pump unit serving to convey a (liquid or gaseous) fluid, which has a pump base, a first pump rotor that is rotatably mounted with respect to a first axis and is rotatably coupled to the rotor of an electric motor, and a first pump rotor that is rotatably coupled with respect to a second axis, which intersects the first axis at a non-zero angle, comprises a rotatably mounted second pump rotor, the two pump rotors having mutually meshing teeth with a number of teeth differing from one another by one, such that chambers enclosed between the two teeth when the two rotate Pump rotors increase or decrease their volume around the respective axis.
  • Motor-pump units of this type are part of the prior art in various configurations.
  • the basic functional principle has been known for a long time, for example from US Pat. No. 3,236,186 A, US Pat. No. 3,856,440 A and DE 42 41 320 A1.
  • Pumps of the design discussed here are typically characterized by comparatively smooth running. This applies in particular in comparison to swash plate pumps (cf. for example WO 2015/090730 A1, DE 10 2016 215 474 A1 and WO 2018/054622 A1), in particular at higher speeds, as they are in motor-pump units, which have to deliver comparatively high fluid throughputs with a severely limited size, are often unavoidable.
  • motor-pump units of the design that is decisive here are preferably used in applications (e.g. in the motor vehicle sector) in which a lower noise level is important.
  • the present invention has set itself the task of providing a motor-pump unit of the type described at the outset that is improved in a practice-relevant respect compared to the prior art, insofar as particularly practice-relevant aspects in particular - partially contradicting one another and to be weighed against one another in the context of practice-oriented optimization - aspects such as performance, size, efficiency, service life, reliability and manufacturing costs.
  • the motor-pump unit according to claim 1 is characterized by a characteristic combination of further design features which interact synergistically with one another and with the features specified at the beginning, namely in particular by the following:
  • the first pump rotor has radially outside the associated toothing on a collar with a spherical to the axis intersection point inner wall, on which the second pump rotor with a corresponding, spherically shaped outer surface in such a way that the chambers are delimited radially on the outside by the spherical inner wall of the collar.
  • the second pump rotor has a dome-shaped area radially inside the associated toothing with an outer wall that is spherical to the axis intersection, on which the first pump rotor rests with a corresponding, spherically shaped inner surface in such a way that the chambers radially inward through the spherical outer wall of the dome-shaped Area are limited.
  • the end face of the second pump rotor facing away from the associated toothing is designed as a sliding surface, by means of which the second pump rotor is supported on a support surface designed on the pump base and perpendicular to the second axis.
  • the second pump rotor has a number of fluid openings corresponding to the number of teeth of its toothing, which each open into an interdental space.
  • one of the defining characteristics of the motor-pump unit according to the invention is that the chambers used to convey the fluid are limited exclusively by the first and the second pump rotor. A delimitation of the chambers by non-rotating parts (e.g. parts of the pump base or housing parts) does not occur. In contrast to the case where the chambers are delimited radially outwards (partially implemented according to the prior art) by a fixed component, along which the first and second pump rotors are moved in a sealing manner, according to the invention the radially outer closure of the chambers takes place via only two parts that move comparatively slowly in relation to one another. This helps to minimize leakage losses.
  • the second pump rotor has a dome-shaped area radially inside the associated toothing with an axis intersection point has a spherical outer wall, on which the first pump rotor rests with a corresponding, spherically shaped inner surface in such a way that the chambers are delimited radially on the inside by the spherical outer wall of the dome-shaped area.
  • the radially outer and radially inner tight delimitation of the chambers via interacting surfaces of the first and second pump rotor is also very advantageous because there are only small friction losses due to the comparatively small relative movement of the dynamically sealing parts.
  • Correspondingly low friction not only has a direct effect in terms of particularly high efficiency. Rather, due to correspondingly reduced frictional heat, there is also a heat-related expansion of the components involved in the seal counteracted, which in turn enables particularly small gap dimensions, which - through correspondingly reduced leakage losses - indirectly benefits the ef fi ciency. Since said collar is designed on the first pump rotor, which in this way encloses the second pump rotor, very particularly compact constructions are also possible.
  • the suction of the fluid into the chambers from a first area (suction zone) of the pump and the ejection of the fluid from the chambers into a second area (pressure zone) of the pump are also decisive Slot control in the pairing of support surface (of the pump base) and sliding surface (of the second pump rotor) is implemented by providing two separate recesses on the support surface, which communicate with two different fluid connections on the motor-pump unit, and the second pump rotor has a number of fluid openings corresponding to the number of teeth of its toothing, which each open into an intermediate space between the teeth.
  • This embodiment of the slot control in the manner according to the invention is also particularly favorable because the interacting surfaces (i.e. the sliding surface and the support surface) can be designed to be flat, which is not only very advantageous in terms of production technology, but also (due to minimized leakage losses) the optimal one
  • the second pump rotor is inclined relative to the first axis by being supported on the pump base, ie. H . the inclination of that surface ("support surface") of the pump base, on which the second pump rotor is rotatably supported, with respect to the first axis.
  • the suction of the fluid to be pumped into the enlarging chambers of the pump in a first area of circulation and the pushing out of the fluid to be pumped out of the reducing chambers of the pump in a second area of circulation takes place in a particularly simple and reliable manner by the second Pump rotor through, namely through breakthroughs through which pass through the second pump rotor from its end face (“gliding surface”) interacting with the support surface of the pump base up to the toothing.
  • the openings in question ideally open out in the area of the valleys of the teeth at the respective lowest point or at least adjacent to it.
  • the high reliability of this form of slot control is u. a.
  • the contact pressure of the second pump rotor on the support surface of the pump base which causes a good seal
  • the same device e.g. a mechanical spring and/or hydraulic preload; see below
  • the good seal suffers neither from possible wear nor from temperature-related expansions or expansions. Shrinkage of the interacting components.
  • the ef fi ciency-increasing low gap losses are both over a particularly long operating or Service life as well as over a particularly wide operating range.
  • the first pump rotor and the rotor of the electric motor can be joined to form a rigid structural unit, or the motor rotor can even be an integral part of the first pump rotor.
  • the bearing required for the first pump rotor and motor rotor to be rotatable about the first axis Structural effort and the necessary installation space are particularly small. Use can be made of this construction in particular in the case of motor-pump units according to the invention with compact dimensions and a comparatively low output.
  • first pump rotor and the motor rotor are coupled to one another in a rotationally fixed and axially displaceable manner, with two separate rotary bearings advantageously being used for the first pump rotor and for the motor rotor (with respect to the first axis ), which can be designed in particular in the form of plain bearings, are used.
  • first pump rotor is mounted so that it can be displaced axially with respect to the first axis, with the first pump rotor being pretensioned by means of a mechanical pretensioning spring so that its toothing rests against the toothing of the second pump rotor.
  • This favors a sealing contact of the first and the second pump rotor against one another in the region of the two toothings in such a way that chambers which are at least largely tightly separated from one another are formed between them--by wandering contact lines.
  • the aforesaid preloading spring also promotes the sealing contact of the second pump rotor with its sliding surface on the support surface of the pump base in such a way that there is a fluidic short circuit between the two recesses made on the support surface, one of which with the suction side and the other with the pressure side of the pump communicated , avoided .
  • the motor rotor is also mounted so that it can be displaced axially with respect to the first axis, with the said pretensioning spring acting on the motor rotor at the front.
  • the mechanical contact between the two pump rotors explained above is particularly important for starting the motor-pump unit, when the pressure for a possible hydraulic contact (see below) is not yet available.
  • a hydraulic contact pressure is particularly preferably added, in that the first pump rotor and/or the motor rotor are connected in such a way to a fluid connection that forms its pressure connection during normal operation of the motor-pump unit Communicating pressure chamber immerse that on the first pump rotor a system of teeth of the first pump rotor on the teeth of the second pump rotor increasing hydraulic axial force acts.
  • the pressure chamber is typically realized by the interior of a motor housing—which is sealingly connected to the pump base.
  • the first pump rotor is mounted on its circumference in a slide bearing designed on the pump base, the pressure-side recess of the support surface is particularly preferably over (at least ) a channel incorporated into the plain bearing for the first pump rotor in terms of flow with the
  • the number of teeth of the toothing of the second pump rotor (eg eight teeth) is one greater than the number of teeth of the toothing of the first pump rotor (eg seven teeth). This ensures that the second pump rotor, which is slidably supported on the pump base, rotates at a lower speed than the first pump rotor, which is driven by the electric motor. This is in line with the operating behavior.
  • the second pump rotor is ring-shaped with a central opening, with a bearing pin that is stationary relative to the pump base and coaxial with the first axis being provided, which passes through the central opening of the second pump rotor passes .
  • the central opening provided in the second pump rotor is expediently dimensioned in such a way that contact of the second pump rotor with the bearing journal is avoided.
  • the bearing journal can be rigidly and permanently connected to the pump base, in particular by casting, pressing in or the like, and in particular can be of such a length that it also passes through the first pump rotor, in which case, unless bearing is implemented on the pump base (see above .
  • the first pump rotor and/or the motor rotor is mounted on the bearing journal so as to be rotatable about the first axis.
  • This preferred construction enables a number of additional advantages, which make the motor-pump unit according to the invention even more superior to the prior art.
  • the three main components rotating during operation of the motor-pump unit namely--in this assembly sequence--the second pump rotor, the first pump rotor and the motor rotor, can be threaded onto the bearing journal from the free end thereof.
  • a possibly motor housing mounted on the pump base typically does not contribute to the support of the motor rotor.
  • the fluid conveyed by the motor-pump unit can optionally be used to cool the electric motor, in which case it preferably flows through the annular gap between the stator and the rotor of the electric motor, for which purpose one of the two fluid connections is preferably connected to a the pump base sealingly connected, the stator of the electric motor receiving housing part is executed.
  • a Arrangement of both fluid connections on the pump base advantageous.
  • other criteria such as the specific installation situation of the motor-pump unit also have an influence on the individual arrangement of the two fluid connections.
  • FIG. 1 shows a first axial section through the motor-pump unit according to a first exemplary embodiment, taken according to section line I-I of FIG.
  • FIG. 2 shows a second axial section through the motor-pump unit according to FIG. 1, which is orthogonal to FIG.
  • FIG. 3 shows an angled third axial section through the motor-pump unit according to FIGS. 1 and 2, taken according to section line III-III of FIG.
  • FIGS. 1-3 are plan views of the insulated pump base of the motor-pump unit according to FIGS. 1-3, with the position of the three axial sections concerned being indicated,
  • Fig. 5 shows a first
  • FIGS. 1-4 shows a second perspective exploded view of the motor-pump unit according to FIGS. 1-4 and
  • FIG. 7 shows an angled axial section analogous to FIG. 3 through the motor-pump unit according to a second exemplary embodiment.
  • the motor-pump unit shown in Figures 1-6 of the drawing which is used to convey a fluid, comprises a pump part 1 and a drive part 2, the pump part 1 in turn comprising a pump base 3, a first pump rotor 4 and a second pump rotor 5 and the drive part 2 has an electric motor 6 with a stator 7 and a rotor (motor rotor 8).
  • the first pump rotor 4 is rotatably mounted on the pump base 3 in an axially displaceable manner with respect to a first axis X.
  • it has a cylindrical outer geometry 9 and is slidably received in a corresponding slide-bearing-like receptacle 10, which is designed in the pump base 3 and is cylindrical with respect to the first axis X.
  • the first pump rotor 4 Via its first toothing 12 (with seven teeth 13 in the present case) provided on the face side in an annular toothing zone 11, the first pump rotor 4 interacts with the annular disc-shaped second pump rotor 5, which in turn has a second toothing 15 provided on the face side in an annular toothing zone 14 (with in the present case eight teeth 16 ) which mesh with the first toothing 12 of the first pump rotor 4 .
  • the second toothing 15 provided on the face side in an annular toothing zone 14 (with in the present case eight teeth 16 ) which mesh with the first toothing 12 of the first pump rotor 4 .
  • the second pump rotor 5 has a flat sliding surface
  • the support surface 19 is inclined relative to the first axis X, d. H . it does not extend perpendicularly to the first axis X.
  • the first pump rotor 4 has radially outside the associated first toothing 12, d. H . except for associated ring-shaped toothed zone 11 has a collar 20 with a spherical inner wall 21 .
  • the second pump rotor 5 rests against this with a corresponding, spherically shaped outer surface 22 that runs around like a wave ring.
  • the second pump rotor 5 has radially inside the associated second toothing 15, d. H . within the associated ring-shaped toothing zone 14 has a dome-shaped area 23 with a spherical outer wall 24, on which the first pump rotor 4 rests with a corresponding, spherically shaped, wave ring-like inner surface 25.
  • the center point of the spherical inner wall 21 of the first pump rotor 4 is identical to the center point of the spherical outer wall 24 of the second pump rotor 5; it lies on the first axis X and defines the point of intersection M of the first axis X with a second axis Y, around which the second pump rotor 5 rotates. While the position of the second pump rotor 5 in relation to the direction of the second axis Y is defined by the support surface 19 - executed on the pump base 3 - the position of the second pump rotor 5 is transverse to the second axis Y - via the two respectively interacting spherical surface pairs 21 / 22 and 24 / 25 - defined only by the first pump rotor 4.
  • the two toothings 12 and 15 have a number of teeth 13 or 13 which differs from one another by one. 16 in such a way that enclosed between them, radially outside by the spherical inner wall 21 of the collar 20 of the first pump rotor 4 and radially inside by the spherical outer wall 24 of the dome-shaped portion 23 of the second pump rotor 5 limited chambers 26 at Circulation of the two pump rotors 4 and 5 around the respective axis X and Y increase their volume or reduce (on the function see, for example, WO 2012/084289 A1).
  • fluid openings 27 which pass through the second pump rotor 5 from the sliding surface 18 to the second toothing 15 and there each open into an interdental space.
  • these fluid openings 27 communicate alternately with the two separate recesses 28, 29, which are made on the support surface 19 of the pump base 3 and which are connected to different fluid connections 30 and 30, respectively, made on the pump base 3. 31 are fluidically connected.
  • the motor rotor 8 is constructed in a way that is basically known as such, with a core 32 and a plurality of permanent magnets 33 arranged on its circumference. It is mounted on a bearing journal 34, which extends along the first axis X, in an axially displaceable, rotatable manner.
  • the bearing journal 34 is firmly connected to the pump base 3 .
  • the pump base 3 manufactured from a filled plastic by injection molding—is molded onto an end section 35 of the bearing journal 34 , the relevant end section 35 being correspondingly profiled for a permanently secure hold in the pump base 3 .
  • the bearing journal 34 passes through the annular disk-shaped second pump rotor 5, d. H . it occurs (with play) through its central opening 36 .
  • the bearing journal 34 likewise passes through the first pump rotor 4 by (again with play) passing through whose central bore 37 passes through.
  • the first pump rotor 4 by (again with play) passing through whose central bore 37 passes through.
  • the pump rotor 4 has a projection 38 which (designed with a polygonal cross section) engages as a driver in a corresponding recess 39 in the motor rotor 8 .
  • the first pump rotor 4 On its end face 40 facing the motor rotor 8, the first pump rotor 4 has nubs 41 which, lying against the annular projection 42 of the motor rotor 8, act as spacers and ensure a gap 43 between the end faces of the motor rotor 8 and the first pump rotor 4 facing one another.
  • the motor stator 7 is an integral, cast-in part of this forming part, in a motor housing 46 which is placed sealingly (cf. the seal 44) on the pump base 3 and screwed to it (cf. the screws 45), which is also housed under a motor housing cover 47 - accommodates a motor controller (cf. the circuit board 48 shown schematically) and has an electrical connection 49 . It is constructed in a way that is basically known as such, with pole cores 50 , winding carriers 51 placed thereon, coil windings 52 , etc., received on these and connected to the motor controller via connecting conductors 60 .
  • a spring arrangement with a pretensioning spring 54 which is supported via a pressure piece 55 made of a low-friction material and rotating with the motor rotor 8 on an abutment (disc 57) arranged on the freely projecting end section 56 of the bearing journal 34, and on the free end face of the motor rotor 8 acts to axially prestress the motor rotor 8 - which is also mounted so as to slide axially on the bearing journal 34 - against the first pump rotor 4, whereby the latter is prestressed against the second pump rotor 5 and the latter in turn against the support surface 19 of the pump base 3.
  • This pressure which also acts on the free end face 59 of the motor rotor 8, causes a hydraulic pressure of the motor rotor 8 on the first pump rotor 4, of the first pump rotor 4 on the second pump rotor 5 and of the second pump rotor 5, which is oriented in the same direction as the mechanical pressure exerted by the spring arrangement and reinforces this to the support surface 19 of the pump base 3 .
  • FIG. 4 It can be seen in FIG. 4 a groove 60 formed on the support surface 19 of the pump base 3, via which an annular space 61 formed on the support surface 19 directly around the bearing journal 34 is fluidically connected to the pressure-side recess 28 is connected.
  • the central bore 37 of the first pump rotor 4 which surrounds the bearing journal 34 with play, is also fluidly connected to the pressure-side recess 28 .
  • the one in Fig. The second exemplary embodiment illustrated in FIG. 7 is largely apparent to a person skilled in the art from the above explanation relating to the first exemplary embodiment.
  • the only relevant deviation is the arrangement of the fluid connection 30' forming the pressure connection of the motor-pump unit. Because this is not arranged on the pump base 3', but rather on the motor housing 46'.
  • the fluid channels 58' are part of the flow path of the pumped fluid from the fluid connection 31' forming the suction connection to the fluid connection 30' communicating with the interior of the motor housing 46'. Since there are otherwise no relevant deviations, further explanations are superfluous; the same parts of the two exemplary embodiments are provided with identical reference characters.

Landscapes

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

Abstract

L'invention concerne un groupe moteur-pompe qui comprend une base de pompe (3), un premier rotor de pompe (4) qui monté rotatif par rapport à un premier axe (X), est couplé rotatif au rotor (8) d'un moteur électrique (6) et présente une première denture, et un deuxième rotor de pompe (5) qui est monté rotatif autour d'un deuxième axe (Y) et qui présente une deuxième denture qui s'engrène avec la première denture, les dentures comportant un nombre de dents différent l'un de l'autre de un, de façon que des chambres définies entre les deux dentures augmentent ou réduisent en termes de volume à mesure que les deux rotors de pompe (4, 5) tournent autour de leurs axes (X, Y) respectifs. Les chambres sont délimitées radialement à l'extérieur par une paroi intérieure sphérique d'un collet (20) du premier rotor de pompe (4) et radialement à l'intérieur par une paroi extérieure sphérique d'une région en forme de dôme (23) du deuxième rotor de pompe (5). Le face frontale (17) du deuxième rotor de pompe (5) orientée à l'opposé de la denture associée se présente sous la forme d'une surface de glissement (18) au moyen de laquelle le deuxième rotor de pompe (5) est porté sur une surface de support (19) qui est disposée sur la base de pompe (3) et est perpendiculaire au deuxième axe (Y). Deux évidements séparés l'un de l'autre et qui sont en communication fluidique avec différents raccords de fluide formés sur le groupe moteur-pompe sont présents sur la surface de support. Le deuxième rotor de pompe (5) comprend un nombre d'ouvertures de fluide qui débouchent chacune dans un espace entre les dents, le nombre d'ouvertures correspondant au nombre de dents de la denture dudit rotor.
PCT/EP2021/074761 2020-09-23 2021-09-09 Groupe moteur-pompe WO2022063585A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21777232.6A EP4217610B1 (fr) 2020-09-23 2021-09-09 Groupe moteur-pompe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020124825.3 2020-09-23
DE102020124825.3A DE102020124825A1 (de) 2020-09-23 2020-09-23 Motor-Pumpe-Einheit

Publications (1)

Publication Number Publication Date
WO2022063585A1 true WO2022063585A1 (fr) 2022-03-31

Family

ID=77910760

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2021/074761 WO2022063585A1 (fr) 2020-09-23 2021-09-09 Groupe moteur-pompe

Country Status (3)

Country Link
EP (1) EP4217610B1 (fr)
DE (1) DE102020124825A1 (fr)
WO (1) WO2022063585A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021103306A1 (de) 2021-02-12 2022-08-18 Kolektor Group D.O.O. Handgeführtes Druckflüssigkeitsgerät

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3236186A (en) 1963-04-29 1966-02-22 Wildhaber Ernest Positive-displacement unit
US3856440A (en) 1974-03-19 1974-12-24 E Wildhaber Rotor pair for positive fluid displacement
DE4241320A1 (fr) 1991-12-09 1993-06-17 Arnold Felix
WO2005116403A1 (fr) 2004-05-25 2005-12-08 Cor Pumps + Compressors Ag Commande du courant de fuite d'intervalle d'une machine a engrenages
WO2010018053A2 (fr) 2008-08-12 2010-02-18 Robert Bosch Gmbh Pompe à pignons droits
WO2012084289A2 (fr) 2010-12-20 2012-06-28 Robert Bosch Gmbh Pompe, compresseur ou moteur
WO2013057112A2 (fr) 2011-10-19 2013-04-25 Robert Bosch Gmbh Unité de transport
US8517707B2 (en) 2007-08-31 2013-08-27 Robert Bosch Gmbh Method for converting energy from compressed air into mechanical energy and compressed air motor therefor
WO2015090730A1 (fr) 2013-12-20 2015-06-25 Robert Bosch Gmbh Pompe oscillante avec arbre monté dans le stator
DE102016215474A1 (de) 2016-08-18 2018-02-22 Robert Bosch Gmbh Förderaggregat
DE102016218077A1 (de) * 2016-09-21 2018-03-22 Robert Bosch Gmbh Förderaggregat
WO2018054622A1 (fr) 2016-09-21 2018-03-29 Robert Bosch Gmbh Organe de refoulement présentant un contour étanche

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE352717T1 (de) 2003-09-11 2007-02-15 Cor Pumps & Compressors Ag Drehkolbenmaschine
US9115646B2 (en) 2010-06-17 2015-08-25 Exponential Technologies, Inc. Shroud for rotary engine
DE102010063532A1 (de) 2010-12-20 2012-06-21 Robert Bosch Gmbh Pumpe, Verdichter oder Motor mit kleinem Durchmesser-Längenverhältnis

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3236186A (en) 1963-04-29 1966-02-22 Wildhaber Ernest Positive-displacement unit
US3856440A (en) 1974-03-19 1974-12-24 E Wildhaber Rotor pair for positive fluid displacement
DE4241320A1 (fr) 1991-12-09 1993-06-17 Arnold Felix
WO2005116403A1 (fr) 2004-05-25 2005-12-08 Cor Pumps + Compressors Ag Commande du courant de fuite d'intervalle d'une machine a engrenages
US8517707B2 (en) 2007-08-31 2013-08-27 Robert Bosch Gmbh Method for converting energy from compressed air into mechanical energy and compressed air motor therefor
WO2010018053A2 (fr) 2008-08-12 2010-02-18 Robert Bosch Gmbh Pompe à pignons droits
WO2012084289A2 (fr) 2010-12-20 2012-06-28 Robert Bosch Gmbh Pompe, compresseur ou moteur
WO2013057112A2 (fr) 2011-10-19 2013-04-25 Robert Bosch Gmbh Unité de transport
WO2015090730A1 (fr) 2013-12-20 2015-06-25 Robert Bosch Gmbh Pompe oscillante avec arbre monté dans le stator
DE102016215474A1 (de) 2016-08-18 2018-02-22 Robert Bosch Gmbh Förderaggregat
DE102016218077A1 (de) * 2016-09-21 2018-03-22 Robert Bosch Gmbh Förderaggregat
WO2018054622A1 (fr) 2016-09-21 2018-03-29 Robert Bosch Gmbh Organe de refoulement présentant un contour étanche

Also Published As

Publication number Publication date
DE102020124825A1 (de) 2022-03-24
EP4217610A1 (fr) 2023-08-02
EP4217610B1 (fr) 2024-02-28

Similar Documents

Publication Publication Date Title
EP2921703B1 (fr) Unité pompes-moteur
DE60015018T2 (de) Dichtungslose integrierte Motorpumpe mit Seitenkanallaufrad
EP2921702B1 (fr) Unité pompes-moteur
DE3015628A1 (de) Drucklager/kopplungseinrichtung und damit ausgeruestete schneckenmaschine
EP3657021B1 (fr) Pompe à vide
DE3921221C2 (de) Gekapselter Rotationskolbenkompressor
EP1019637B1 (fr) Moteur oscillant radial
DE102017104063B4 (de) Elektrische Gerotorpumpe mit Steuerspiegel
DE102011051486B4 (de) Pumpenanordnung mit Mikropumpe und Lagerelement
EP2510192B1 (fr) Machine hydrostatique à pistons radiaux
WO2012007125A2 (fr) Pompe à palettes
EP4217610B1 (fr) Groupe moteur-pompe
EP1495227B1 (fr) Groupe motopompe hydraulique
EP0711384B1 (fr) Pompe a vide a palette a deux etages
DE3242983A1 (de) Regelbare fluegelzellenpumpe
DE4220713C2 (de) Rotationskolbenverdichter
WO1992008051A1 (fr) Pompe a pistons, notamment pompe a pistons radiaux
DE4234055C2 (de) Spiralkompressor
DE3322549A1 (de) Fluegelzellenpumpe mit veraenderlichem foerderhub fuer hydraulische betriebsmittel insbesondere von kraftfahrzeugen
DE2748455A1 (de) Hydro-rotationsmaschine
DE3118297A1 (de) Zahnradpumpe
DE3922434C2 (fr)
DE4325285A1 (de) Ölgedichtete Vakuumpumpe
WO2016193260A1 (fr) Pompe volumétrique hydraulique électrique
EP4198260A1 (fr) Pompe à vis

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21777232

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2021777232

Country of ref document: EP

Effective date: 20230424