WO2022058442A1 - Pompe volumétrique bidirectionnelle - Google Patents

Pompe volumétrique bidirectionnelle Download PDF

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Publication number
WO2022058442A1
WO2022058442A1 PCT/EP2021/075514 EP2021075514W WO2022058442A1 WO 2022058442 A1 WO2022058442 A1 WO 2022058442A1 EP 2021075514 W EP2021075514 W EP 2021075514W WO 2022058442 A1 WO2022058442 A1 WO 2022058442A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
inlet
positive displacement
housing
outlet
Prior art date
Application number
PCT/EP2021/075514
Other languages
English (en)
Inventor
Gilles HERBILLON
Harald HINTERWALLNER
Original Assignee
Vcst Industrial Products Bv
Sala Drive 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
Application filed by Vcst Industrial Products Bv, Sala Drive Gmbh filed Critical Vcst Industrial Products Bv
Publication of WO2022058442A1 publication Critical patent/WO2022058442A1/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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • 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

Definitions

  • the invention relates to a bidirectional positive displacement pump and an electric drive unit comprising said pump.
  • New transmissions e.g. multi-speed transmissions
  • New transmissions which are known to comprise several gears, especially free- running gears, generally require an active lubrication, in particular drip lubrication combined with a dry sump lubrication.
  • Single-speed transmission relying on planetary gear sets which are known to comprise planets supported by needle bearings also requires an active lubrication to guarantee that the oil can be driven to these bearings.
  • an oil pump is foreseen in the bottom transmission housing and pumps oil from the sump towards an oil tank located above the shafts of the gearbox, before being distributed to the components (gears & bearings) by dripping.
  • the oil pump is driven by an electrical motor in a driven-on-demand approach.
  • the main drawbacks of an electrically driven oil pump are its unit cost, the need of complex control electronics, and development costs for complying with Automotive Safety Integrity Level.
  • a “mechanically” driven oil pump can be envisaged.
  • bidirectional oil pump because the shafts of a multispeed transmission for an electric motor can rotate in a forward and reverse direction, contrary to what is seen with multi-speed transmissions for internal combustion engine where there is at least one shaft turning always in the same direction.
  • bidirectional pumps tend to be bulky and expensive. For instance, they can be provided with two separated pumps, each being connected to a dedicated one-clutch mechanism.
  • US8702373 discloses a bidirectional oil pump with a single oil pump connected to a network of one-way valves for the lubrication of a gearing mechanism of turbo-fan engine.
  • Bidirectional oil pumps are also presented in DE 10 2007 022 216 and US 1 ,717,814 for hydraulic applications and lubrication of a propeller shaft of boats, respectively.
  • DE 10 2008 053 318 shows a reversibly operable gear machine disclosed in combination with an electro-hydraulic vehicle steering system.
  • these solutions require a complex piping structure for connecting the oneway valves and other complex adaptations.
  • a single oil pump unit and a single lubrication per EDU electric drive unit, including e-machines, power electronics and e-Drive
  • EDU electric drive unit, including e-machines, power electronics and e-Drive
  • the invention aims to provide a solution to at least one drawback of the teaching provided by the prior art.
  • the invention aims to provide a compact and cost effective solution to ensure the lubrication of e-Drives, namely transmission for pure electric vehicles.
  • the invention is directed to a positive displacement pump for circulating a fluid, in particular oil in one or more electric drive unit elements such as an electric motor or a gearbox, said pump comprising: a pump housing; a rotor assembly disposed within the pump housing, said rotor assembly comprising one rotor or two rotors operatively engaged, to displace the fluid, said rotors comprising a front face, a rear face and one or more lateral surfaces; a first and a second working zones, said zones being delimited by at least one of the lateral surfaces of said rotors, wherein the fluid in the first working zone is pressurized and the fluid in the second working zone is depressurized when said pump is rotating in a first direction, and the fluid in the first working zone is depressurized and the fluid in the second working zone is pressurized when said pump is rotating in a second direction, opposite to the first direction; a first and a second inlet passages in fluid communication with the first and the second working zones
  • the positive displacement pump comprises one or more of the following technical features, taken in isolation, or any combination thereof: the first rotor being an outer gerotor, the second rotor being an inner gerotor, and the at least one of the lateral surfaces comprising the inner surface of the first rotor and the outer surface of the second rotor; the pump housing comprising a central housing, in which a cavity for receiving the rotor assembly being formed, said central housing comprising two opposed faces, said pump housing further comprising at least one intermediate housing covering either one or each of the opposed faces of the central housing, preferably said central housing or intermediate housing being made in one piece; the at least one intermediate housing comprising a first face abutting against the central housing and a second face opposed to said first face, said second face having one or more grooves, said grooves forming lateral surfaces of the corresponding (first/second and/or inlet/outlet) passages; the central housing comprising a plurality of through holes extending between the opposed faces of the central housing, in which a cavity for receiving the rot
  • the central housing comprises two through holes arranged symmetrically in the central housing and extending between the opposed faces of the central housing, wherein the common inlet passage comprises one of said through holes.
  • the invention can also relate to a gearbox for an electric drive unit comprising an electric motor and a gearbox, said gearbox having an oil pump wherein said pump is the above mentioned positive displacement pump, preferably the rotor assembly being mounted on a shaft provided with a driven gear, said gear being meshed with a gear of said gearbox, preferably a final pinion or a final wheel of a differential unit.
  • the invention also relates to an electric drive unit comprising an electric motor and a gearbox, said gearbox or electric motor having an oil pump wherein the pump is the above mentioned positive displacement pump, preferably the rotor assembly being mounted on a shaft provided with a driven gear, said gear being meshed with a gear of said gearbox, preferably a final pinion or a final wheel of a differential unit
  • the present invention is also advantageous since it offers a modular solution that can be adapted to different gearbox sizes.
  • each subject-matter of the invention is also applicable to the other subject-matters of the invention.
  • each subject-matter of the invention is combinable with other subject-matters.
  • the features of the invention are also combinable with the embodiments of the description, which in addition are combinable with each other.
  • Fig. 1A and 1 B represent a schematic representation of a bidirectional positive displacement pump according to the invention.
  • Fig. 2A and 2B represent s possible alternative to the bidirectional positive displacement pump of Fig. 1A and 1 B.
  • Fig.3 shows an exploded view of some elements of a bidirectional positive displacement pump according to the invention.
  • Fig.4A, 4B, 4C and 4D respectively show a front view and three sectional views of a bidirectional positive displacement pump according to the invention.
  • FIG. 5A and 5B show a perspective rear view of a partial assembly of a bidirectional positive displacement pump according to the invention.
  • Fig. 6 represents a schematic representation of an electric drive transmission comprising an electrical motor, a gear box and a bidirectional positive displacement pump according to the invention.
  • Fig. 1A and 1 B disclose schematic representations of a bidirectional positive displacement pump 2 according to the invention, wherein the rotor assembly 6 comprises a gerotor assembly.
  • Fig. 1A schematically shows a fluid circuit connected to the gerotor assembly 6.
  • Fig. 1 B schematically represents the rotor assembly 6 (i.e. gerotor) with an outer gerotor 610 and an inner gerotor 620.
  • the outer gerotor 610 and the inner gerotor 620 define two working zones 10, 20. These zones 10, 20 are delimited by at least lateral surfaces 603 of the first 610 and the second 620 gerotors.
  • the first working zone 10 can be pressurized or depressurised depending on the rotation direction, while the second zone 20 is pressurised when the first zone 10 is depressurised and vice versa.
  • Fig. 2A and 2B represent a possible alternative for the bidirectional oil pump 2 according to the invention, wherein the rotor assembly 6 comprises two meshed gears.
  • Other configurations for the rotor assembly 6 e.g. rotary pump with a single rotor with sliding vanes
  • the rotor assembly 6 can comprise a first and a second rotor (i.e. gear) 610, 620, wherein the first gear 610 is meshed with the second gear 620 to displace the fluid (e.g. oil).
  • the first 610 and second rotor 620 can have teeth or lobes.
  • a rotor assembly 6 with a single rotor can comprise sliding vanes (not shown).
  • Fig. 1 A represents a fluid circuit suitable for operating a bidirectional pump
  • the fluid circuit comprises not only a first and a second inlet passages 110, 120 in fluid communication with the first and the second working zones, 10, 20, respectively, but also a first 210 and a second 220 outlet passages in fluid communication with the first 10 and the second 20 working zones, respectively.
  • Each passage 110, 120, 210, 220 comprises a oneway valve 300 (forming a group of four valves) configured so as to either allow the transfer of oil from the first inlet passage 110 to the second outlet passage 220 and to block the transfer of oil from the second inlet passage 120 to the first outlet passage 210 when the pump 2 is rotating in the first direction, or allow the transfer of oil from the second inlet passage 120 to the first outlet passage 210 and to block the transfer of oil from the first inlet passage 110 to the second outlet passage 220 when the pump 2 is rotating in a second direction, opposite to the first direction.
  • a oneway valve 300 forming a group of four valves
  • the present invention differs from the solutions known from the prior art in that the working zones 10,20 are sandwiched between the downstream ends 112, 122 of the inlet passages and the upstream end of the outlet passages 211 , 221.
  • This configuration allows a spatial (e.g. 3D) arrangement of the fluid circuit, wherein the flows entering and leaving the working zones 10, 20 are substantially parallel to the rotation axis of a rotor assembly 6.
  • the first/second inlet passage downstream ends 112/122 are represented as not being a mirror image of the corresponding the first/second outlet passage upstream ends 211/221 for didactic purpose.
  • the pump 2 illustrated in Fig.3 shows an exploded view of some elements of the pump 2, namely the central housing 410, in which a cavity for receiving the rotor assembly 6 is formed.
  • the central housing 410 has two opposed faces 411 , 412 (only front face 411 is shown in Fig. 3) and a first group of fourthrough holes 418 arranged (symmetrically) and extending between the opposed faces 411 , 412 of the central housing 410.
  • the through holes 418 are configured to receive and/or guide the one-way valves 300, such as ball check valve, each valve 300 comprising for instance a ball 301 and a spring 302.
  • the central housing 410 further comprises a pair of trough holes 419 also arranged symmetrically, wherein one of them serves as a common inlet passage 71. Even if the other hole 419 has no purpose for the use of the pump 2, its presence allows a symmetric design of the central housing, thereby simplifying its assembly.
  • the pump 2 is also provided with two intermediate housings 430, 450 for covering the opposed faces 411 , 412 of the central housing 410 in such a manner that the central housing 410 is sandwiched between the two intermediate housings 430, 450.
  • the central housing 410 and/or the intermediate housings 430, 450 can be made in one piece, using for instance injection molding or additive manufacturing.
  • the intermediate housings 430, 450 can have one or more grooves 434, 454 forming lateral surfaces of the (first or second) inlet or outlet passages 110, 120, 210, 220. Furthermore, the intermediate housings 430, 450 are provided with tongues 436, 456 forming an abutment surface for the corresponding spring 302. Each abutment surface is coaxial with the corresponding through hole 438, 458. Instead of tongues 436, 456 serving as abutment surface (i.e. valve seat), a ring insert (not shown) or an equivalent solution can also be envisaged.
  • the (front) covers 470 can also serve as abutment surface. Even if several options are available for forming an end abutment surface for a biasing means (e.g. spring) of a one-way valve, the selection of a tongue eases the manufacturing of the pump 2.
  • Fig. 4A, 4B, 4C and 4D respectively show a front view and three sectional views of the pump 2.
  • the housing 4 of the pump 2 can comprise five stacked elements: a rear cover 490, a rear intermediate housing 450, a central housing 410, a front intermediate housing 430 and a front cover 470.
  • the front 470 and rear 490 covers can be made of a flat plate.
  • the pump 2 shown in Fig. 4A, 4B, 4C and 4D has a stacked design, easing the pump assembly. Moreover, this design is modular and allows to manufacture pumps with different characteristics in terms of pumping volume while sharing several common components.
  • the covers 470, 490 can have one or more openings for the inlet, the outlet, and/or a recess for the shaft 90 of the pump.
  • Fig. 4B and 4C show that the one-way valves 300 in the passages 120 and 210 are open while the one-way valves 300 in the passages 110 and 220 are closed. This one-way open/closed configuration is caused by the fluid pressure gradients that take place when the pump 2 rotates for instance in the reverse direction.
  • FIG. 5A and 5B show a perspective rear view of a partial assembly of the pump 2, namely the central housing 410, the intermediate housings 430, 450 and the rotor assembly 6.
  • the cross sections of the first and second outlet passage upstream ends 211 , 221 are directly adjacent to the rear face 602 of the rotor assembly 6 (the first rotor being an outer gerotor and the second rotor being an inner gerotor).
  • These cross sections of the first and second outlet passage upstream ends 211 , 221 are kidney-shaped cross section.
  • the cross section of the first outlet passage upstream end 211 and the cross section of the first inlet passage downstream end 112 coincide.
  • the cross section of the second inlet downstream end 122 and the cross section of the second outlet end 221 can also coincide.
  • the cross section of the first outlet passage upstream end 211 can be a mirror image of the cross section of the first inlet passage downstream end 112.
  • the cross section of the second outlet passage upstream end 221 can also be a mirror image of the cross section of the second inlet passage downstream end 122.
  • the nominal flow rate for a given (absolute) rotational speed in a forward rotating direction may be different than that for the reverse rotation.
  • the fluid circuit is then dissymmetric in terms of flow rate capacity.
  • the fluid circuit can be decomposed into circuits: a first one that is active when the pump 2 rotates in a forward direction and a second one when the pump 2 rotates in a reverse direction.
  • the first circuit comprising the first inlet passage 110 and the second outlet passage 220, has a lower fluid pumping capacity than the second circuit comprising the second inlet passage 120 and the first outlet passage 210.
  • the flow rate capacity for the forward rotation or reverse rotation can be adjusted by changing the passage flow sectional areas of the first and second circuit.
  • the size (e.g. arced length of the kidney-shaped section) and/or phasing of the kidney-shaped cross section of the inlet/outlet passage ends 112, 122, 211 , 221 can be adapted to create an asymmetric behavior of the pump 2.
  • the inlet/outlet passage ends 112, 122, 211 , 221 can be configured so that the inlet passage ends 112, 122 are not a mirror image of the outlet passage ends 211 , 221.
  • the pump 2 shown in Fig.4A, 4B, 4C and 4D comprises an inlet port 70 connectable to a suction port of a machine/system such as one or a combination of electric drive unit elements, in particular a gear box and/or electric motor, and an outlet port 80 connectable to a pressure port of said machine/system.
  • the first 110 and second 120 inlet passages can be in fluid communication with the inlet port 70 via a common inlet passage 71.
  • the first 110 and second 120 inlet passages merge into the single common inlet passage 71.
  • the first 210 and second 220 outlet passages can be in fluid communication with the outlet port 80, wherein the first 210 and second 220 outlet passages merge into the single common outlet passage 81.
  • the pump 2 can comprise two inlet ports and/or two outlet ports (these alternatives are not shown).
  • the first and the second inlet/outlet passages can be in direct fluid communication with the or each inlet/outlet port.
  • the inlet port(s) 70 may present a connection for a sump strainer (not shown).
  • a preferred application for the pump 2 is a gearbox, in particular a multispeed gearbox with layshaft for an electric motor as shown in Fig. 6. Possible applications are not restricted to the embodiment shown in Fig. 6 and can also comprise for instance a singlespeed gearbox with planetary gear set or a multi-speed gearbox with planetary gear set.
  • the gearbox may comprise a dry sump as shown in Fig. 6.
  • the outlet port 80 of the pump 2 can be in fluid communication with an oil reservoir (tank) positioned above the gears of the gearbox. The reservoir ensures a drip lubrication of the gears, shafts and/or bearings.
  • the pump 2 may be connected to a pressure closed loop circuit (not shown).
  • the machine to be lubricated may comprise at least two pumps according to the invention that are arranged in series and/or in parallel (not shown).
  • the pump 2 can comprise a pinion mechanically connected to its driving shaft 90.
  • the pinion can be driven by a final wheel of a differential unit as shown in Fig. 6.
  • the lubrication circuit representation in Fig. 6 is restricted to the gearbox.
  • the pump 2 can also supply oil to the electrical motor for ensuring its cooling and/or lubrication (not shown in Fig. 6).
  • the pump 2 according to the invention is adapted for electric drive unit (EDU), said EDU comprising one or more electric motors, power electronics and a gearbox (a.k.a. e-Drive).
  • the rotor assembly 6 is driven by a shaft 90 extending through the front intermediate housing 430 and the front cover 470.
  • the inner rotor 620 of the rotor assembly 6 is mechanically connected to the shaft 90 at one end thereof.
  • a pinion can be rigidly connected to another end of the shaft (not shown).
  • the pinion can be operatively engaged (e.g. meshed with) with a gear of said gearbox, preferably a final pinion or a final wheel of a differential unit.
  • the pump 2 may also comprise a bypass passage (not shown) with a
  • bypass valve for regulating the outlet pressure delivered.
  • a ball seat e.g. insert ring
  • the ball seat can be configured to uncover an opening when the force applied by the check-valve on said seat exceeds a certain threshold.
  • the through hole 419 can serve as a bypass passage and be adapted to accommodate a relief valve.
  • the pump 2 is described as a means for pumping oil. However, this pump can not only be used with other liquids such as fuel, but also with gases.
  • a rotor assembly (6) disposed within the pump housing (4), said rotor assembly (6) comprising one rotor or two rotors (610, 620) operatively engaged, to displace the fluid, said rotors comprising a front face (601), a rear face (602) and one or more lateral surfaces (603);
  • first (10) and a second (20) working zones said zones (10, 20) being delimited by at least one of the lateral surfaces (603) of said rotors (610, 620), wherein the fluid in the first working zone (10) is pressurized and the fluid in the second working zone (20) is depressurized when said pump (2) is rotating in a first direction, and the fluid in the first working zone (10) is depressurized and the fluid in the second working zone (20) is pressurized when said pump (2) is rotating in a second direction, opposite to the first direction;
  • each passage (110, 120, 210, 220) comprises a one-way valve (300) configured to either allow the transfer of the fluid from the first inlet passage (110) to the second outlet passage (220) and to block the transfer of the fluid from the second inlet passage (120) to the first outlet passage (210) when said pump (2) is rotating in the first direction, or allow the transfer of the fluid from the second inlet passage (120) to the first outlet passage (210) and to block the transfer of the fluid from the first inlet passage (110) to the second outlet passage (220) when said pump (2) is rotating in the second direction; characterized in that
  • the first (110) and the second (120) inlet passages each have a downstream end (112, 122) arranged on the front of the rotor assembly (6) and/or the one or two rotors (610, 620);
  • the first (210) and the second (220) outlet passages each have an upstream end (211 , 221) arranged on the rear of the rotor assembly (6) and/or the one or two rotors (610, 620).
  • Positive displacement pump (2) according to Clause 1 , wherein the first rotor (610) is an outer gerotor, the second rotor (620) is an inner gerotor, and the at least one of the lateral surfaces (603) comprises the inner surface of the first rotor (610) and the outer surface of the second rotor (620).
  • the pump housing (4) comprises a central housing (410), in which a cavity (416) for receiving the rotor assembly is formed, said central housing (410) comprising two opposed faces (411 ,412), said pump housing (4) further comprising at least one intermediate housing (430, 450) covering either one or each of the opposed faces (411 , 412) of the central housing (410), preferably said central housing (410) or intermediate housing (430, 450) being made in one piece.
  • the at least one intermediate housing comprises a first face (431 , 451) abutting against the central housing (410) and a second face (432, 452) opposed to said first face (431 , 451), said second face (432, 452) having one or more grooves (434,454), said grooves (434, 454) forming lateral surfaces of the corresponding passages (110,120,210,220).
  • each one-way valve (300) is a ball check valve, said ball check valve comprising a ball (301) and a spring (302).
  • the at least one intermediate housing (430, 450) comprises a rear (450) and a front (430) intermediate housings, the central housing (410) being sandwiched between rear (450) and front (430) intermediate housings.
  • the pump housing (4) further comprises a rear (490) and front (470) covers, wherein the rear intermediate housing (450), central housing (410) and front intermediate housing (430) are sandwiched between the rear (490) and the front (470) covers, preferably at least one of the front and rear covers (470, 490) being a flat plate with one or more openings.
  • Positive displacement pump (2) according to any of the previous clauses, wherein the cross section of the first inlet passage downstream end (112) and the cross section of the first outlet passage upstream end (211) coincide, and wherein the cross section of the second inlet passage downstream end (122) and the cross section of the second outlet passage upstream end (221) coincide, preferably the cross section of the first outlet passage upstream end (211) being a mirror image of the cross section of the first inlet passage downstream end (122), and the cross section of the second outlet passage upstream end (221) being a mirror image of the cross section of the second inlet passage downstream end (122).
  • Positive displacement pump (2) according to any of the previous clauses, wherein either the front face of the rotor or the front faces (601) of the first and second rotors (610, 620) are coplanar with the first (112) and second (122) inlet passage downstream ends, wherein either the rear face of the rotor or the rear faces (602) of the first and the second rotors (610, 620) are coplanar with the first (211) and second (221) outlet passage upstream ends.
  • Positive displacement pump (2) comprising a first circuit and a second circuits, wherein the first circuit comprises the first inlet passage (110) and the second outlet passage (220) and the second circuit comprises the second inlet passage (120) and the first outlet passage (210), the minimal flow section area of the second circuit being smaller than the minimal flow section area of the first circuit.
  • Positive displacement pump (2) comprising an inlet port (70) connectable to a suction port of a lubrication circuit of at least one of the above mentioned electric drive unit elements and an outlet port (80) connectable to a pressure port of said lubrication circuit, wherein the first (110) and second (120) inlet passages are in fluid communication with the inlet port (70) via a common inlet passage (71), and/or wherein the first (210) and second (220) outlet passages are in fluid communication with the outlet port (80), via a common outlet passage (81).
  • a gearbox for an electric drive unit comprising an electric motor and a gearbox, said gearbox or motor having an oil pump characterized in that said pump is a positive displacement pump (2) according to any of the preceding clauses.
  • a gearbox according to the preceding clause wherein the rotor assembly (6) is mounted on a shaft (90) provided with a driven gear, said gear being meshed with a gear of said gearbox, preferably a final pinion or a final wheel of a differential unit.
  • An electric drive unit comprising an electric motor and a gearbox, said gearbox or motor having an oil pump characterized in that said pump is a positive displacement pump (2) according to any of the preceding clauses.
  • An electric drive unit comprising an electric motor and a gearbox according to the preceding clause, wherein the rotor assembly (6) is mounted on a shaft provided (90) with a driven gear, said gear being meshed with a gear of said gearbox, preferably a final pinion or a final wheel of a differential unit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une pompe volumétrique (2) destinée à faire circuler un fluide, en particulier de l'huile dans un ou plusieurs éléments unitaires d'entraînement électriques tels qu'un moteur électrique ou une boîte de transmission, ladite pompe (2) comprenant : un carter de pompe (4) ; un ensemble rotor (6) comprenant deux rotors en prise fonctionnelle, pour déplacer le fluide, lesdits rotors comprenant une face avant, une face arrière et des surfaces latérales ; un premier (110) et un deuxième (120) passage d'entrée, respectivement en communication fluidique avec la première (10) et la deuxième (20) zone de travail ; un premier (210) et un deuxième (220) passage de sortie, respectivement en communication fluidique avec la première (10) et la deuxième (20) zone de travail, chaque passage (110, 120, 210, 220) comprenant une vanne unidirectionnelle (300). L'invention est caractérisée en ce que les premier (110) et deuxième (120) passages d'entrée comportent chacun une extrémité aval (112, 122) disposée à l'avant des deux rotors (610, 620) ; les premier (210) et deuxième (220) passages de sortie comportent chacun une extrémité amont (211, 221) disposée à l'arrière des deux rotors (610, 620).
PCT/EP2021/075514 2020-09-18 2021-09-16 Pompe volumétrique bidirectionnelle WO2022058442A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP20197017 2020-09-18
EP20197017.5 2020-09-18

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WO2022058442A1 true WO2022058442A1 (fr) 2022-03-24

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1717814A (en) 1926-08-25 1929-06-18 Bliss E W Co Lubricating system
DE4338875A1 (de) * 1993-11-13 1995-05-18 Eckerle Rexroth Gmbh Co Kg Reversierbare Innenzahnradmaschine (Pumpe oder Motor)
DE102007022216A1 (de) 2007-05-11 2008-11-13 Robert Bosch Gmbh Hydrauliksystem mit Zahnradpumpe
DE102008053318A1 (de) 2008-10-27 2010-04-29 Trw Automotive Gmbh Reversibel betreibbare Zahnradmaschine, sowie Fahrzeuglenksystem und Verfahren zur Steuerung eines Fahrzeuglenksystems
US8702373B1 (en) 2013-07-15 2014-04-22 United Technologies Corporation Lubrication of journal bearing during clockwise and counter-clockwise rotation

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1717814A (en) 1926-08-25 1929-06-18 Bliss E W Co Lubricating system
DE4338875A1 (de) * 1993-11-13 1995-05-18 Eckerle Rexroth Gmbh Co Kg Reversierbare Innenzahnradmaschine (Pumpe oder Motor)
DE102007022216A1 (de) 2007-05-11 2008-11-13 Robert Bosch Gmbh Hydrauliksystem mit Zahnradpumpe
DE102008053318A1 (de) 2008-10-27 2010-04-29 Trw Automotive Gmbh Reversibel betreibbare Zahnradmaschine, sowie Fahrzeuglenksystem und Verfahren zur Steuerung eines Fahrzeuglenksystems
US8702373B1 (en) 2013-07-15 2014-04-22 United Technologies Corporation Lubrication of journal bearing during clockwise and counter-clockwise rotation

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