EP4217610B1 - Groupe moteur-pompe - Google Patents

Groupe moteur-pompe Download PDF

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Publication number
EP4217610B1
EP4217610B1 EP21777232.6A EP21777232A EP4217610B1 EP 4217610 B1 EP4217610 B1 EP 4217610B1 EP 21777232 A EP21777232 A EP 21777232A EP 4217610 B1 EP4217610 B1 EP 4217610B1
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EP
European Patent Office
Prior art keywords
pump
motor
rotor
pump rotor
axis
Prior art date
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EP21777232.6A
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German (de)
English (en)
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EP4217610A1 (fr
Inventor
Jernej MUNIH
Klemen PETRIC
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Kolektor Mobility d o o
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Kolektor Mobility d o o
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Publication of EP4217610A1 publication Critical patent/EP4217610A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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 conveying a fluid.
  • the present invention relates to such a motor-pump unit used to convey a (liquid or gaseous) fluid, which has a pump base, a first pump rotor rotatably mounted with respect to a first axis and rotationally coupled to the rotor of an electric motor, and a first pump rotor with respect to a second axis, which intersects with the first axis at an angle other than zero, comprises a rotatably mounted second pump rotor, the two pump rotors having meshing teeth with a number of teeth that differ from one another by one in such a way that chambers enclosed between the two teeth rotate when the two rotate Pump rotors increase or decrease their volume around the respective axis.
  • Such motor-pump units are part of the state of the art in various designs. Reference should be made in particular to: WO 2005/116403 A1 , US 8,517,707 B2 , WO 2010/018053 A2 , WO 2012/084289 A2 and WO 2013/057112 A2 .
  • the basic operating principle has been known for a long time, for example from US 3,236,186 A , US 3,856,440 A and DE 42 41 320 A1 .
  • Pumps of the design in question here are typically characterized by a comparatively smooth running. This is particularly true in comparison to swashplate pumps (cf. for example WO 2015/090730 A1 , DE 10 2016 215 474 A1 and WO 2018/054622 A1 ), especially at higher speeds, as is often unavoidable in motor-pump units that have to pump comparatively high fluid throughputs with a very limited size.
  • motor-pump units of the relevant design are preferably used in applications (for example in the automotive sector) in which lower noise development is important.
  • the present invention has set itself the task of providing a motor-pump unit of the type set out at the outset that is improved from a practical point of view compared to the prior art, with aspects that are particularly relevant to practice in particular - partially contradicting each other and having to be weighed up against one another in the context of practice-oriented optimization such as performance, size, efficiency, service life, reliability and manufacturing costs.
  • the present invention aims to provide a solution compared to the prior art WO 2012/084289 A2 , which discloses a motor-pump unit according to the preamble of claim 1, to provide improved motor-pump unit in terms of efficiency.
  • 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 second pump rotors. A boundary of chambers This does not occur due to non-rotating parts (e.g. parts of the pump base or housing parts). Unlike in the case of the chambers being limited 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 moving comparatively slowly against each other. This helps minimize leakage losses.
  • the second pump rotor has a dome-shaped area radially within the associated toothing with an outer wall that is spherical to the axis intersection has, 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 rotors is also very advantageous because the comparatively small relative movement of the dynamic sealing parts results in only small friction losses.
  • Correspondingly low friction not only has a direct effect in terms of particularly high efficiency. Rather, due to a correspondingly reduced frictional heat, there is also a heat-related expansion of the components involved in the sealing counteracted, which in turn enables particularly small gap dimensions, which - through correspondingly reduced leakage losses - indirectly benefits efficiency. Because the said collar is designed on the first pump rotor, which in this way encloses the second pump rotor, particularly compact designs are possible.
  • Another very advantageous effect is that - while the axial position (with respect to the second axis) of the second pump rotor is defined by the support surface of the pump base, in that the sliding surface of the second pump rotor rests on the support surface - the guidance of the second pump rotor is transverse to the second Axis takes place through the first pump rotor.
  • an internal centering or “self-centering”
  • This is an extremely important aspect from a manufacturing perspective; This makes it possible to produce the two pump rotors cost-effectively (with rather rough tolerances), for example by plastic injection molding.
  • the decisive factor is also the suction of the fluid into the chambers from a first area (suction zone) of the pump and the expulsion of the fluid from the chambers into a second area (pressure zone) of the pump
  • Slot control in the pairing of support surface (the pump base) and sliding surface (of the second pump rotor) is realized by providing two separate recesses on the support surface, which communicate fluidly with two different fluid connections designed on the motor-pump unit, and the second pump rotor has a number of fluid breakthroughs corresponding to the number of teeth of its toothing, each of which opens into an interdental space.
  • This design of the slot control in the manner according to the invention is particularly favorable because the interacting surfaces (ie the sliding surface and the support surface) can be made flat, which is not only very advantageous in terms of manufacturing technology, but also (as a result of minimized leakage losses) achieves the optimal effect and results in high efficiency.
  • the second pump rotor experiences its inclination relative to the first axis through its support on the pump base, ie the inclination of that surface ("support surface") of the pump base on which the second pump rotor is rotatably supported relative to the first axis.
  • the suction of the fluid to be delivered into the enlarging chambers of the pump in a first area of the circulation and the pushing out of the fluid to be delivered from the decreasing chambers of the pump in a second area of the circulation are carried out in a particularly simple and reliable manner by the second Pump rotor through, namely through openings through which pass through the second pump rotor from its end face ("sliding surface"), which interacts with the support surface of the pump base, into the teeth.
  • the openings in question ideally open in the area of the valleys of the toothing at the respective lowest point or at least adjacent to it.
  • the high reliability of this form of slot control is achieved, among other things, by the fact that the contact pressure of the second pump rotor on the support surface of the pump base, which creates a good seal, is provided by the same device (e.g. a mechanical spring and/or a hydraulic preload; see below). can, which also ensures tight contact between the teeth of the first and second pump rotors. Due to an at least essentially flat design of the surfaces on the pump base and second pump rotor that cooperate for the slot control and slide against one another, the good seal suffers neither from possible wear nor from temperature-related expansion or shrinkage of the interacting components. As a result, in this case, the low gap losses that increase efficiency are present both over a particularly long operating life or service life and 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 bearings required for the first pump rotor and motor rotor to be rotatable about the first axis can be used The construction effort and the required installation space are particularly small. This design can be used in particular in motor-pump units according to the invention with compact dimensions and a comparatively low power.
  • first pump rotor and the motor rotor are coupled to one another in a rotationally fixed and axially displaceable manner, in which case two separate rotary bearings (with respect to the first axis) are advantageously used for the first pump rotor and for the motor rotor ), which can be designed in particular in the form of plain bearings, are used.
  • first pump rotor is mounted axially displaceably with respect to the first axis, the first pump rotor being pretensioned by means of a mechanical biasing spring so that its teeth rest on the teeth of the second pump rotor. This promotes a sealing contact of the first and second pump rotors against one another in the area of the two teeth in such a way that chambers that are at least largely sealed off from one another are formed between them - by moving contact lines.
  • the said biasing spring further 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 a fluidic short circuit occurs between the two recesses made on the support surface, one of which communicates with the suction side and the other with the pressure side of the pump. is avoided.
  • the motor rotor is also mounted so that it can move axially with respect to the first axis, with the said biasing spring acting on the front side of the motor rotor.
  • the above-explained mechanical pressure of the two pump rotors against one another is particularly important for the start-up of the motor-pump unit, namely when there is no pressure yet available for possible hydraulic pressure (see below).
  • a hydraulic pressure is particularly preferably added in that the first pump rotor and / or the motor rotor is connected to the fluid connection which forms its pressure connection when the motor-pump unit is operated as intended. into the communicating pressure chamber so that a hydraulic axial force which increases the contact of the teeth of the first pump rotor with the teeth of the second pump rotor acts on the first pump rotor.
  • the pressure chamber is typically implemented through 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 plain bearing designed on the pump base, then the pressure-side recess of the support surface is particularly preferred over (at least) one In terms of flow, the channel incorporated into the plain bearing for the first pump rotor communicates with the interior of the motor housing or other pressure chamber connected, so that the pressure prevailing at the pressure-side fluid connection is established in this during operation.
  • the number of teeth in the toothing of the second pump rotor (e.g. eight teeth) is one larger than the number of teeth in the toothing of the first pump rotor (e.g. 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 driven by the electric motor. This suits the operational behavior.
  • the second pump rotor is designed in a ring shape with a central opening, with a bearing pin which is fixed relative to the pump base and is coaxial with the first axis and which passes through the central opening of the second pump rotor passes through.
  • the central opening provided in the second pump rotor is expediently dimensioned so that contact of the second pump rotor with the bearing journal is avoided.
  • the bearing pin can in particular be rigidly and permanently connected to the pump base by casting, pressing in or the like and in particular have such a length that it also passes through the first pump rotor, whereby, unless a 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 that it can rotate about the first axis.
  • This preferred design 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 that rotate during operation of the motor-pump unit, namely - in this assembly order - the second pump rotor, the first pump rotor and the motor rotor can be threaded onto the bearing journal from the free end.
  • a motor housing (see below) that may be placed on the pump base typically does not make any contribution in terms of supporting the motor rotor.
  • a preload spring (see above), which may be provided and acts on the front side of the motor rotor, is supported on an abutment arranged on the bearing journal, the motor housing is not subjected to mechanical stress.
  • 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 existing between the stator and the rotor of the electric motor, for which purpose one of the two fluid connections is preferably connected to one
  • the housing part is sealingly connected to the pump base and accommodates the stator of the electric motor. Particularly when cooling of the electric motor is not necessary or is implemented in another way, one is Arrangement of both fluid connections on the pump base is advantageous. However, other criteria such as the specific installation situation of the motor-pump unit also influence the individual arrangement of the two fluid connections.
  • the motor-pump unit shown in 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 having an electric motor 6 a stator 7 and a rotor (motor rotor 8).
  • the first pump rotor 4 is mounted on the pump base 3 so that it can rotate in an axially displaceable manner with respect to a first axis X.
  • it has a cylindrical external 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 (in the present case with seven teeth 13) provided on the front side in an annular toothing zone 11, the first pump rotor 4 interacts with the second pump rotor 5, which is designed in the shape of an annular disk, which in turn has a second toothing 15 (in the present case with eight) provided on the front side in an annular toothing zone 14 Teeth 16) which meshes with the first toothing 12 of the first pump rotor 4.
  • the second pump rotor 5 On its end face 17 applied to the second toothing 15, the second pump rotor 5 has a flat sliding surface 18, via which it is slidably supported on a support surface 19 designed on the pump base 3.
  • the support surface 19 is inclined relative to the first axis X, i.e. H. it does not extend perpendicular to the first axis X.
  • the first pump rotor 4 points radially outside the associated first toothing 12, ie outside the associated annular toothing 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, wave ring-like outer surface 22.
  • the second pump rotor 5 has a dome-shaped region 23 with a spherical outer wall 24 radially within the associated second toothing 15, ie within the associated annular toothing zone 14, on which the first pump rotor 4 has a corresponding, spherically shaped, wave ring-like inner surface 25 applied.
  • the center of the spherical inner wall 21 of the first pump rotor 4 is identical to the center of the spherical outer wall 24 of the second pump rotor 5; it lies on the first axis X and defines the intersection M of the first axis X with a second axis Y, about which the second pump rotor 5 rotates. While the position of the second pump rotor 5 is defined in relation to the direction of the second axis Y by the support surface 19 - which is carried out on the pump base 3 - the position of the second pump rotor 5 is thus transverse to the second axis Y - via the two interacting spherical ones Surface pairs 21/22 and 24/25 - only defined by the first pump rotor 4.
  • the two toothings 12 and 15 have a number of teeth 13 and 16 that differ from each other by one in such a way that, enclosed between them, radially on the outside through the spherical inner wall 21 of the collar 20 of the first pump rotor 4 and radially on the inside through the spherical outer wall 24 of the Dome-shaped area 23 of the second pump rotor 5 has limited chambers 26 Circulation of the two pump rotors 4 and 5 around the respective axis X and Y increases or decreases their volume (cf. for the function, 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 a space between the teeth.
  • these fluid openings 27 communicate alternately with the two separate recesses 28, 29 made on the support surface 19 of the pump base 3, which are fluidly connected to different fluid connections 30 and 31 made on the pump base 3.
  • the motor rotor 8 is constructed in a manner known in principle as such with a core 32 and a plurality of permanent magnets 33 arranged on its circumference. It is mounted in an axially displaceable, rotatable manner on a bearing pin 34 which extends along the first axis X.
  • the bearing pin 34 is firmly connected to the pump base 3.
  • the pump base 3 - made by injection molding from a filled plastic - is molded onto an end section 35 of the bearing pin 34, the end section 35 in question being correspondingly profiled for a permanently firm hold in the pump base 3.
  • the bearing pin 34 passes through the annular disk-shaped second pump rotor 5, ie it passes (with play) through its central opening 36.
  • the bearing journal 34 also passes through the first pump rotor 4 (again with play). whose central bore 37 passes through.
  • the first pump rotor 4 has a projection 38, which (designed with a polygonal cross section) engages as a driver in a corresponding recess 39 of 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 knobs 41, which, resting on the annular projection 42 of the motor rotor 8, act as spacers and provide a gap 43 between the facing end faces of the motor rotor 8 and the first pump rotor 4.
  • the motor stator 7, forming an integral, cast part of it, is housed in a motor housing 46 which is sealingly placed (see the seal 44) on the pump base 3 and screwed to it (see the screws 45), which is also located under a motor housing cover 47 - accommodates a motor control (see the schematically shown circuit board 48) and has an electrical connection 49. It is constructed in a manner known as such with pole cores 50, winding supports 51 placed thereon, coil windings 52 received on these and connected to the motor control via connecting conductors 60, etc.
  • a spring arrangement with a preload spring 54 which is supported on an abutment (disc 57) arranged on the freely projecting end section 56 of the bearing pin 34 via a pressure piece 55 which rotates with the motor rotor 8 and is made of a low-friction material, and on the free end face of the motor rotor 8 acts to axially pretension the motor rotor 8 - which is also axially slidably mounted on the bearing journal 34 - against the first pump rotor 4, whereby the latter is pretensioned against the second pump rotor 5 and the latter in turn against the support surface 19 of the pump base 3.
  • a hydraulic pressure is added in that the pressure-side recess 28 of the support surface 19 is fluidly connected to the interior of the motor housing 46 via two channels (fluid grooves 58) incorporated into the receptacle 10, which form the sliding bearing for the first pump rotor 4.
  • the pressure prevailing at the pressure-side fluid connection 30 is thus established during operation.
  • 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 the second pump rotor 5, which is in the same direction as the mechanical pressure by the spring arrangement and reinforces this to the support surface 19 of the pump base 3.
  • the central bore 37 of the first pump rotor 4 - which surrounds the bearing pin 34 with play - is also fluidly connected to the pressure-side recess 28 through the central opening 36 of the second pump rotor 5.
  • FIG. 7 illustrated second exemplary embodiment 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. This is because it is not arranged on the pump base 3', but rather on the motor housing 46'.
  • the fluid channels 58' are therefore part of the flow path of the conveyed fluid from the fluid connection 31' forming the suction connection to the fluid connection 30' which communicates with the interior of the motor housing 46'. Since there are no other relevant deviations, further explanations are unnecessary; the same parts of the two exemplary embodiments are provided with identical reference numbers.

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

Claims (15)

  1. Groupe moteur-pompe pour le transport d'un fluide, comprenant une base de pompe (3 ; 3'), un premier rotor de pompe (4) logé pouvant tourner par rapport à un premier axe (X), lequel est couplé en rotation au rotor (8) d'un moteur électrique (6) dont le stator (7) est fixé par rapport à la base de pompe (3 ; 3') et un deuxième rotor de pompe (5) pouvant tourner autour d'un deuxième axe (Y), lequel coupe à un point d'intersection axial (M) le premier axe (X) dans un angle différent de zéro, sachant que
    - les deux rotors de pompe (4, 5) comportent des dentures (12, 15) s'engrenant l'une avec l'autre avec un nombre de dents (13, 16) avec une différence de une dent l'une par rapport à l'autre de telle manière que les chambres (26) comprises entre les deux dentures (12, 15) augmentent ou diminuent leur volume lors de la rotation des deux rotors de pompe (4, 5) autour de l'axe respectif (X, Y),
    - le premier rotor de pompe (4) comporte radialement en dehors de la denture attribuée (12) une collerette (20) avec une paroi intérieure (21) sphérique par rapport au point d'intersection axial (M) à laquelle vient s'appliquer le deuxième rotor de pompe (5) avec une surface extérieure (22) correspondante, de conformation sphérique de telle manière que les chambres (26) sont délimitées radialement à l'extérieur par la paroi intérieure sphérique (21) de la collerette (20),
    - le deuxième rotor de pompe (5) comporte radialement à l'intérieur de la denture attribuée (15) une zone en forme de calotte (23) avec une paroi extérieure sphérique (24) par rapport au point d'intersection axial (M) à laquelle vient s'appliquer le premier rotor de pompe (4) avec une surface intérieure (25) correspondante, de conformation sphérique de telle manière que les chambres (26) sont délimitées radialement à l'intérieur par la paroi extérieure sphérique (24) de la zone en forme de calotte (23),
    caractérisé en ce que
    - la face avant (17) opposée à la denture attribuée (15) du deuxième rotor de pompe (5) est exécutée sous la forme d'une surface de glissement (18) au moyen de laquelle le deuxième rotor de pompe (5) s'appuie sur une surface d'appui (19), exécutée sur la base de pompe (3 ; 3'), perpendiculaire au deuxième axe (Y),
    - le deuxième rotor de pompe (5) comporte un nombre de passages de fluide (27) correspondant au nombre des dents (16) de la denture (15) de celui-ci, lesquels débouchent respectivement dans un espace intermédiaire de dent, et
    - deux évidements (28, 29) séparés l'un de l'autre sont prévus sur la surface d'appui (19), lesquels communiquent selon la technique des fluides avec les raccords de fluide (30, 31 ; 30', 31') différents exécutés sur le groupe moteur-pompe.
  2. Groupe moteur-pompe selon la revendication 1, caractérisé en ce que le premier rotor de pompe (4) et le rotor de moteur (8) sont assemblés en un ensemble de construction rigide ou le rotor de moteur (8) fait partie intégrante du premier rotor de pompe (4).
  3. Groupe moteur-pompe selon la revendication 1, caractérisé en ce que le premier rotor de pompe (4) et le rotor de moteur (8) sont couplés l'un à l'autre axialement mobiles de façon solidaire en rotation.
  4. Groupe moteur-pompe selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le premier rotor de pompe (4) est logé de façon axialement mobile eu égard au premier axe (X), sachant que le premier rotor de pompe (4) est précontraint au moyen d'un ressort de précontrainte mécanique (54) pour l'appui de la denture (12) de celui-ci sur la denture (15) du deuxième rotor de pompe (5).
  5. Groupe moteur-pompe selon la revendication 4, caractérisé en ce que le rotor de moteur (8) est également logé de façon axialement mobile eu égard au premier axe (X), sachant que le ressort de précontrainte (54) agit frontalement sur le rotor de moteur (8).
  6. Groupe moteur-pompe selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le premier rotor de pompe (4) et/ou le rotor de moteur (8) plongent dans un espace sous pression communiquant avec le raccord de fluide (30 ; 30') qui forme le raccord de pression de celui-ci lors du fonctionnement conforme du groupe moteur-pompe, de telle manière qu'une force axiale hydraulique augmentant l'appui de la denture (12) du premier rotor de pompe (4) sur la denture (15) du deuxième rotor de pompe (5) agit sur le premier rotor de pompe (4).
  7. Groupe moteur-pompe selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le premier rotor de pompe (4) est logé sur sa périphérie dans un logement de type palier lisse (10) exécuté sur la base de pompe (3 ; 3').
  8. Groupe moteur-pompe selon la revendication 7, caractérisé en ce qu'au moins un conduit relié selon la technique des fluides à l'espace intérieur d'un carter de moteur (46), exécuté en particulier sous la forme d'une rainure de fluide (58 ; 58') est aménagé dans le logement de type palier lisse (10).
  9. Groupe moteur-pompe selon l'une quelconque des revendications 1 à 8, caractérisé en ce que le deuxième rotor de pompe (5) est exécuté de forme annulaire avec un passage central (36) et en ce qu'un tourillon (34) fixe par rapport à la base de pompe (3 ; 3'), coaxial par rapport au premier axe (X) est prévu, qui traverse le passage central (36) du deuxième rotor de pompe (5).
  10. Groupe moteur-pompe selon la revendication 9, caractérisé en ce que le tourillon (34) traverse également le premier rotor de pompe (4) et en ce que le premier rotor de pompe (4) et/ou le rotor de moteur (8) est logé sur lui pouvant tourner autour du premier axe (X) .
  11. Groupe moteur-pompe selon la revendication 10, caractérisé en ce que le tourillon (34) fait saillie librement à son extrémité (56) éloignée de la base de pompe (3 ; 3').
  12. Groupe moteur-pompe selon l'une quelconque des revendications 9 à 11, caractérisé en ce qu'un ressort de précontrainte (54) agissant frontalement sur le rotor de moteur (8) s'appuie sur le tourillon (34).
  13. Groupe moteur-pompe selon l'une quelconque des revendications 1 à 12, caractérisé en ce qu'au moins un des deux raccords de fluide (30') est exécuté sur un carter de moteur (46') relié hermétiquement à la base de pompe (3 ; 3'), logeant le stator (7) du moteur électrique (6).
  14. Groupe moteur-pompe selon la revendication 13, caractérisé en ce que le rotor de moteur (8) est entouré par un fluide en circulation, lequel est transporté par le groupe moteur-pompe lors du fonctionnement de celui-ci .
  15. Groupe moteur-pompe selon l'une quelconque des revendications 1 à 14, caractérisé en ce qu'aucun logement radial du deuxième rotor de pompe (5) ayant pour effet un guidage du deuxième rotor de pompe (5) transversalement au deuxième axe (Y) n'est prévu sur la base de la pompe (3 ; 3') ou une partie du carter.
EP21777232.6A 2020-09-23 2021-09-09 Groupe moteur-pompe Active EP4217610B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020124825.3A DE102020124825A1 (de) 2020-09-23 2020-09-23 Motor-Pumpe-Einheit
PCT/EP2021/074761 WO2022063585A1 (fr) 2020-09-23 2021-09-09 Groupe moteur-pompe

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EP4217610A1 EP4217610A1 (fr) 2023-08-02
EP4217610B1 true EP4217610B1 (fr) 2024-02-28

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WO (1) WO2022063585A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102021103306A1 (de) 2021-02-12 2022-08-18 Kolektor Group D.O.O. Handgeführtes Druckflüssigkeitsgerät

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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
DE4241320C2 (de) 1991-12-09 2002-01-17 Arnold Felix Drehkolbenmaschine
BRPI0414235A (pt) 2003-09-11 2006-10-31 Cor Pumps & Compressors Ag máquina de êmbolo rotativo
DE102004026048A1 (de) 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Spaltverluststromsteuerung
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
DE102008038625A1 (de) 2008-08-12 2010-02-18 Cor Pumps + Compressors Ag Stirnzahnradpumpe
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
DE102010063522A1 (de) 2010-12-20 2012-06-21 Robert Bosch Gmbh Pumpe, Verdichter oder Motor
DE102011084828B4 (de) 2011-10-19 2024-02-15 Robert Bosch Gmbh Förderaggregat
DE102013226974A1 (de) 2013-12-20 2015-06-25 Robert Bosch Gmbh Taumelpumpe mit im Stator gelagerter Welle
DE102016215474A1 (de) 2016-08-18 2018-02-22 Robert Bosch Gmbh Förderaggregat
DE102016218077A1 (de) * 2016-09-21 2018-03-22 Robert Bosch Gmbh Förderaggregat
DE102016218128A1 (de) 2016-09-21 2018-03-22 Robert Bosch Gmbh Förderaggregat

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EP4217610A1 (fr) 2023-08-02
DE102020124825A1 (de) 2022-03-24
WO2022063585A1 (fr) 2022-03-31

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