WO2021005155A1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
WO2021005155A1
WO2021005155A1 PCT/EP2020/069364 EP2020069364W WO2021005155A1 WO 2021005155 A1 WO2021005155 A1 WO 2021005155A1 EP 2020069364 W EP2020069364 W EP 2020069364W WO 2021005155 A1 WO2021005155 A1 WO 2021005155A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
pump
gear pump
housing
supply device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2020/069364
Other languages
German (de)
English (en)
Inventor
Heinz Leiber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ipgate AG
Original Assignee
Ipgate AG
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 Ipgate AG filed Critical Ipgate AG
Priority to DE112020003261.2T priority Critical patent/DE112020003261A5/de
Publication of WO2021005155A1 publication Critical patent/WO2021005155A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • 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

  • Gear pumps or gerotor pumps are widely used for medium to high flow rates. In the pressure range, the gear pump is limited due to the large number of gap seals; in some cases, multi-stage pumps are used in which the pressure load per pump is lower. Gear pumps are mostly used for applications with a pressure of up to 300 bar.
  • Gear pumps are mostly driven by electric motors. It is widespread here to provide a series connection, i.e. to design the electric motor and pump separately, using a common drive shaft, as disclosed in DE 102017106927 A with a coupling. This requires a lot of installation space, which is particularly disadvantageous when used in a unit with limited space, such as an integrated braking system or a transmission control. Furthermore, in this arrangement, the motor axis is rigidly connected to the pump shaft without a coupling, which results in extremely small tolerances or tension in the bearing. Furthermore, the pump in the pump housing is gela with many parts that require small tolerances in order to keep the leakage-relevant column small.
  • DE 2015017074 shows a pump with a separate drive shaft for the pump and just as many parts, the tolerances of which are small and thus manufacturing costs are high. To reduce the axial gaps, pressure compensation plates are also provided here.
  • DE 102012212686 also shows a separate drive shaft for the pump with sliding bearings.
  • a fuel pump for low pressure levels less than 10 bar is known, with mounting of the pump in a kind of flange, but without a connection to a hydraulic block with control valves.
  • the suction and pressure connections are not located together in the bearing flange.
  • the medium to be pumped flows around the motor, which prevents the pump from being used as a high-pressure pump.
  • the pressure range and efficiency depend on the number of sealing surfaces to be sealed, which are dependent on the play between the teeth of the interlocking gears and the play or distance between the inner wall of the housing and the tooth tips leading along it. It also depends on the tightness between tween the gears and the axially adjacent housing walls. The larger the axial gap between the housing and the gear, the lower the performance and the maximum possible pressure that can be achieved. The storage of the rotating parts also incurs significant costs. This is problematic, for example, when the motor and pump are formed separately.
  • the object of the present invention is to further develop a gear pump in such a way that it is less complex.
  • gear pumps according to the invention are advantageously characterized by a few parts with small necessary tolerances.
  • the gear pump according to the invention can be made as a, in particular closed, structural unit and can be easily and easily integrated or built into a wide variety of units.
  • the aforementioned parts preferably form a structural unit which can be installed in a housing or a recess in a housing part.
  • the remaining parts such as the inner gear, the inner ring gear and, if required, the sickle must be designed in such a way that they can be produced very inexpensively with small tolerances using flat grinding or, for example, cold extrusion.
  • the outer ring is welded to the outer disks or the outer disk to a pot-shaped part which receives the inner gear and the inner ring gear.
  • a material connection can be dispensed with if the elements of the gear pump are compressed in the axial direction by means of an elastic part, such as a ring made of elastic material or a spring.
  • corresponding Exercise appropriate forces so that the gear pump is correspondingly tight at the pressures to be generated.
  • the gear pump is preferably used to support the drive shaft.
  • the drive shaft can be supported entirely or only partially by the gear pump.
  • gear pump can be arranged or mounted within the drive housing in its bearing flange or a separate housing.
  • the drive housing with the gear pump arranged therein can be attached to a hydraulic block with additional hydraulic components, such as valves, and to an electronics housing or directly to the electronics housing without a hydraulic block. This means that the electrical connections between the electronics housing and the drive or the gear pump, in particular for the stator winding and the motor sensor, are easy to make.
  • the gear pump can be designed as a 1-stage as well as a multi-stage, in particular two-stage, gear pump.
  • a two-stage gear pump can be formed by a series connection of two single-stage gear pumps. A compact unit with a small installation volume is thus possible.
  • the gear pump can either be an internal gear pump or a toothed ring pump, which is also called a gerator pump.
  • the gear pump has an internal gear driven via a drive shaft and an internal gear, the axis of the internal gear being arranged coaxially to the axis of the internal gear, and that in the axial direction at least on one side next to the internal gear and the interior Toothed ring an outer disc is arranged.
  • the gear pump is designed as an internal gear pump or as a gerotor pump, the internal gear rim being encompassed by an outer part, e.g. in the form of a ring, the at least one outer disk being materially connected to the outer part.
  • the gear pump is designed as a toothed ring pump, with the at least one outer disk being firmly connected to the internal gear rim.
  • an integral connection is understood to mean a welded, soldered or adhesive connection.
  • the se in the form of an internal gear pump or gerotor pump, the se has an internal gear driven via a drive shaft and an internal gear rim, with an outer disc being arranged in the axial direction at least on one side next to the internal gear wheel and the internal gear rim is.
  • at least one elastic and / or resilient part in particular in the form of a ring made of elastic material, generates a force in the axial direction on an outer disk and / or a cup-shaped part that accommodates the inner gear and the inner ring gear.
  • the part can lie in a circular groove of an outer disk and / or a groove of the cup-shaped part arranged in the flat outer side and be supported on a side surface of an adjacent part, such as the housing of a hydraulic block.
  • the outer part is a sleeve, a cup-shaped part, a bearing, in particular in the form of a roller or ball bearing, or a wall, in particular a housing flange with a recess.
  • the drive shaft, the inner gear, the inner ring gear, as well as the two outer disks or the one outer disk and the cup-shaped part a composite or a structural unit. If the Zahnradpum pe also has an outer ring and / or a radial bearing for the inner ring gear, these parts also belong to the unit or the module.
  • gear pump In order to realize a cohesive connection of two parts with one another without interfering with the installation or assembly of the gear pump, chamfers and / or recesses are advantageously provided in the radial outer wall of the corresponding parts.
  • the turfs or recesses of the parts to be connected must correspond to one another, i.e. to be provided on the opposite edges of the parts. In particular, these can be designed to run around.
  • Gear pump according to one of the preceding claims characterized in that the internal gear (2) is arranged tiltable to the drive shaft (1), in particular is coupled to the drive shaft (1) by means of an elastic and / or flexible connection.
  • the inner gear can preferably be mounted in a tiltable manner relative to the drive shaft, so that tolerances and play between the drive shaft and the inner gear or the inner ring gear can be compensated for.
  • a part made of elastic and / or flexible material can also be arranged between the toothed wheel and the drive shaft to compensate for tolerances and play.
  • Fig. 1 a first possible embodiment of a gear pump of a pressure supply device according to the invention, wherein the gear pump is designed as a 1-stage gear pump, and the drive shaft is supported, inter alia, via the inner gear of the gear pump;
  • FIG. La a section through the internal gear pump according to FIG. 1
  • FIG. 1b a section through the area of the gear pump according to FIG. 1, in which the fixed outer parts of the gear pump are welded together;
  • Fig. Lc a slightly modified embodiment of the gear pump ge compared to the embodiment shown in Figure la with Schllitz ter sickle and its mounting via a bolt;
  • Fig. 2 an embodiment of the gear pump with a ball bearing between the inner ring gear and the outer ring, the drive shaft in the gear pump is also superimposed on the inner gear GE;
  • Fig. 4 an engine mounting both in the drive housing and in the
  • Gear pump wherein the first bearing is formed with magnetic Verspan voltage and the second bearing is arranged in the gear pump;
  • Fig. 5 a mounting device for a gear pump according to the invention pe.
  • FIGS 1 and la show a possible embodiment of an internal gear pump with drive shaft 1, internal gear 2, internal ring gear 3, guide part in the form of a sickle 5, the latter being connected via the bolt 6 to the outer disks 7.1 and 7.2 and thus fixed.
  • the aforementioned parts are embedded in the two outer disks 7.1 and 7.2 together with the outer ring 4, the outer ring 4 being connected to the two outer disks 7.1 and 7.2 by welding LS, which is shown enlarged in FIG.
  • the two outer disks 7.1 and 7.2 together with the outer ring 4 form the pump housing ZG of the gear pump Z, which is mounted in the recess 18b of the wall 18.
  • the wall 18 forms a flange on or with which the drive housing can be fastened to the hydraulic housing.
  • Fig. Lb it is shown that the outer diameter of the areas 7.1a, 7.2a and 4a of the outer disks 7.1, 7.2 and the outer ring 4 provided for the welding LS is smaller than the largest outer diameter D A of the parts so that they can be installed in the recess 18b, which can be formed by means of a bore, is not hindered by the weld LS.
  • the Monta ge and adjustment of these parts is described in FIG.
  • the disks 7.1, 7.2 and the outer ring 4 can be manufactured very precisely by flat grinding, so that small gaps or clearances are possible.
  • the inner gear 2 is guided on the drive shaft 1 through the short collar 11. This has the advantage that small angular tolerances between gear 2 and shaft 1 do not lead to gear 2 jamming in the housing ZG.
  • the torque to gear 2 is transmitted via a driver 10. This torque is also transmitted by the locking bolt 9 to the wall application or the flange 18 transferred.
  • both suction and pressure connections act with seals, which are connected to the hydraulic housing HCU.
  • the outer disk 7.2 is provided with a seal 14 to the hydraulic housing HCU.
  • the shaft seals 13.1 and 13.2 also act.
  • the drive shaft 1 also has a shaft journal 8, which is required for mounting the pump housing ZG, see FIG. 6.
  • a roller bearing, needle or ball bearing 17a can be installed between the latter and the outer ring 4.
  • Fig. La shows the gear pump Z in section.
  • the sickle 5 is here centrally mounted on a pin 6, as is known from the prior art.
  • the connections for suction S and the pressure outlet with pressure P with direction of rotation are also shown in FIG.
  • the direction of flow changes as soon as the gear 2 rotates in the other direction, whereby the suction side S becomes the pressure output P and vice versa.
  • a gerotor pump can also be used, which does not have a sickle and a fixed internal gear rim.
  • the inner gear is mounted eccentrically on an eccentric being driven by the drive shaft and rolls in the stationary internal gear rim.
  • a trochoidal tooth system is preferred as the tooth system.
  • the leakage oil must be diverted to S via the leakage flow channel in order to relieve the seals.
  • FIG. 2 shows the same construction of the gear pump Z according to FIG. 1, with the difference being a sliding bearing 16 on both sides of the drive shaft 1 in the two outer disks 7.1 and 7.2. This eliminates the need for a separate engine mount, as shown in Figures 6 and 6a.
  • the leakage oil channels 15 are modified here.
  • FIG. 3 also shows the similar structure of the pressure supply device according to FIGS. 1 and 2, with the difference in the use of roller bearings 17 to minimize bearing friction.
  • the outer disk 7.1 and the outer ring 4 are replaced by the part 7.1b, which is pot-shaped and accommodates the inner gear 2 and the inner ring gear 3.
  • Fig. 4 shows a representation of the entire assembly consisting of Mo tor 22, pump Z, HCU and ECU, which is able to exercise pressure regulation and control for systems such as brakes, transmissions, etc. The main focus here is on the combination of motor and pump.
  • the pump is arranged in the bearing flange 18, as shown in FIGS.
  • Fig. 4 the simplest version according to Fig. 1 is shown, which requires an additional motor bearing 20 in which the shaft 1 is mounted.
  • the motor consists of a rotor 21, which is connected to the shaft 1 via the driver 10a.
  • the rotor 21 is axially preloaded by its magnetic force F via a permanent magnet 30a in the housing 30.
  • This is a solution for the motor manufacturer who manufactures and tests the motor with housing 22 and stator and winding 23 and delivers it to the system supplier.
  • the motor is tested without a pump with an auxiliary shaft.
  • the permanent magnet 30a can, with its force acting axially on the rotor 21, if it is large enough, compensate for tilting forces of the rotor, so that no further support of the rotor 21 in addition to the bearing 20 is necessary.
  • a sufficiently large clearance can or should be provided in the gear pump.
  • the drive housing must also be joined and fastened here with the flange 18 at 25a - shown in the lower half of the figure, e.g. B. with springs, which are attached in segments over three connections who the.
  • a housing seal 31 is also necessary here. It can be fastened by caulking, at 25 from the engine flange with HCU or ECU, see upper half of the figure 28.
  • the pump version with pump housing is shown here.
  • the motor is shown here as a brushless motor that needs a Mo torsensor for commutation and control of the volume delivery of the pump.
  • This motor sensor is arranged at a distance from the drive housing 22, with a sensor shaft 26 which is net or attached to the drive shaft 1 and carries a sensor target 27. This target 27 acts on the sensor element 28, which is arranged on the circuit board of the ECU.
  • the winding is connected to the ECU via contact bars 24.
  • the motor with bearing flange 18 can be connected directly to the hydraulic housing HCU, which contains valves or other hydraulic components, with the pump. If this is not the case, a connection of the drive housing 22, 18 directly to the housing of the ECU is possible.
  • gear pump Z in a pump housing 40 which is connected directly to the hydraulic housing HCU, as shown in FIG. 4 in the upper half of the drive shaft 1.
  • the gear pump Z is first integrated or mounted in the pump housing 40, the rotor 21 then being pressed onto the shaft 1 and then assembled with the bearing 20.
  • the tensile force of the magnet 30 can also act on the rotor 21 and the bearing 20, so that the bearing acts like a four-point bearing.
  • the motor housing 22 is thus connected to the gear pump Z and its pump housing 40 and, in the next step, can be connected to the hydraulic housing HCU or the electronics housing ECU.
  • the fastening screw 41 is used.
  • the shaft 1 is previously centered in the outer disks 7.1 and 7.2 so that the pump housing 40 is centered with the shaft 1 before the screw connection to the hydraulic housing HCU or the electronics housing ECU.
  • the pressure supply device uses a 2-stage pump with a long sliding or roller bearing according to FIGS. 2 and 3, which does not require a separate motor bearing. Accordingly, the Motorauf construction is simplified with the housing.
  • the rotor 21 sits with driver 10a on the motor shaft and is axially connected to the locking ring.
  • the pump housing protrudes slightly into the HCU here.
  • Fig. 5 shows the assembly device for welding the discs 7.1 and 7.2 together with the outer ring 4.
  • a sleeve 37 is pushed over the drive shaft and axially fixed with the locking ring.
  • the disks 7.1, 7.2 and the outer ring are then centered via the centering sleeve 35.
  • the washers 7.1, 7.2 are axially clamped together with the outer ring with the nut 34 via the assembly washer 33.
  • LS can then preferably be laser welded.
  • the sleeve is clamped in a rotatable manner.
  • Fig. Lb shows, the diameter of the weld is smaller, so that the later assembly in the flange is not hindered.
  • Motor housing in particular as a bearing flange or side wall, is formed

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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 à engrenages (Z) se présentant sous forme d'une pompe à engrenages intérieurs ou d'une pompe à couronnes dentées ou d'une pompe gérotor, pourvue d'une roue dentée intérieure (2) entraînée par l'intermédiaire d'un arbre d'entraînement (1) et d'une couronne (3) à denture intérieure, l'axe (2a) de la roue dentée intérieure (2) étant disposé de manière coaxiale par rapport à l'axe (3a) de la couronne (3) à denture intérieure. La roue dentée intérieure (2) et la couronne (3) à denture intérieure sont disposées dans la direction axiale entre deux parties de carter (7.1, 7.1b, 7.2), les parties de carter (7.1, 7.1b, 7.2) étant reliées l'une à l'autre par liaison de matière de façon directe ou par l'intermédiaire d'au moins une pièce (4) disposée entre celles-ci, en particulier sous forme d'anneau. En variante, les parties de carter (7.1, 7.1a, 7.2) sont pressées l'une contre l'autre au moyen d'au moins une pièce (41) élastique et/ou à ressorts.
PCT/EP2020/069364 2019-07-10 2020-07-09 Pompe à engrenages Ceased WO2021005155A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112020003261.2T DE112020003261A5 (de) 2019-07-10 2020-07-09 Zahnradpumpe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019118697.8 2019-07-10
DE102019118697.8A DE102019118697A1 (de) 2019-07-10 2019-07-10 Zahnradpumpe

Publications (1)

Publication Number Publication Date
WO2021005155A1 true WO2021005155A1 (fr) 2021-01-14

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ID=71614870

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2020/069364 Ceased WO2021005155A1 (fr) 2019-07-10 2020-07-09 Pompe à engrenages

Country Status (2)

Country Link
DE (2) DE102019118697A1 (fr)
WO (1) WO2021005155A1 (fr)

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