EP3504433A1 - Ensemble motopompe - Google Patents

Ensemble motopompe

Info

Publication number
EP3504433A1
EP3504433A1 EP17761804.8A EP17761804A EP3504433A1 EP 3504433 A1 EP3504433 A1 EP 3504433A1 EP 17761804 A EP17761804 A EP 17761804A EP 3504433 A1 EP3504433 A1 EP 3504433A1
Authority
EP
European Patent Office
Prior art keywords
pump
motor
supply
electric motor
pump 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.)
Granted
Application number
EP17761804.8A
Other languages
German (de)
English (en)
Other versions
EP3504433B2 (fr
EP3504433B1 (fr
Inventor
Andreas Böhler
Christian Repplinger
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=59791023&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3504433(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP3504433A1 publication Critical patent/EP3504433A1/fr
Application granted granted Critical
Publication of EP3504433B1 publication Critical patent/EP3504433B1/fr
Publication of EP3504433B2 publication Critical patent/EP3504433B2/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/007—General arrangements of parts; Frames and supporting elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F04B23/025—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir
    • F04B23/026—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir a pump-side forming a wall of the reservoir
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • 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
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • 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
    • F04C2240/70—Use of multiplicity of similar components; Modular construction

Definitions

  • the invention relates to a motor pump device.
  • motor-pump units serve primarily to supply hydraulic circuits with hydraulic oil specifiable pressure.
  • the units mentioned are usually characterized by a high power density with small dimensions and can be made available for the mentioned pressure oil supply oil hydraulic systems this as a functional unit.
  • Such a compact hydraulic unit is exemplified in DE 196 52 706 A1, which has a ring-cylindrical pressure medium container as a tank unit, which has an outer outer wall and an inner outer wall and two frontal flanges, with a closed by the pressure fluid container, cooled by a cooling air flow closed Electric motor and with a drivable by the electric motor hydraulic pump as a supply pump of the respective hydraulic circuit.
  • the aim here is that such an aggregate builds in a very compact for continuous operation sufficient cooling of the electric motor, in particular in the form of an attachment.
  • the object of the invention is to further improve the abovementioned units in such a way that, despite their compact design and high specific power, they are designed to be thermally advantageous in such a way that they operate in uninterrupted periodic operation (S6). up to continuous operation (S1) can be used informally.
  • a related object solves a motor-pump device, which is designed as a modular system, according to the feature configuration of patent claim 1 and a motor-pump device according to the feature configuration of claim 7.
  • a motor-pump device for obtaining a variety of pressure combinations can be built in practice. Due to the mentioned use of different supply pumps, pump sizes, motors, mounting positions, tank lengths, etc., results in a very high variety of variants, which can be designed depending on the present application for the unit from a thermal point of view such that an uninterrupted periodic operation (S6) to for continuous operation (S1) is possible.
  • the exact duty cycle is to be selected depending on the output power of the unit and the operating and environmental conditions such that a maximum allowable operating temperature, for example in the form of oil temperature in the unit, preferably not exceeded 80 ° C.
  • a temperature switch can be used in or outside the unit.
  • the peculiarities of the motor-pump device are based on the inventive flexible modular system according to the feature configuration of claim 1, which, inter alia, allows the combination of high and / or low pressure with only one unit. In this way, the realization of so-called.
  • One to two-circle supply systems is possible.
  • the unit according to the invention can be used both horizontally and vertically and the tank unit in the form of the oil tank can be flexibly adjusted to the respective required oil volume.
  • Fig. 2 in the manner of a longitudinal section a side view of the
  • Fig. 3 is a view through the motor-pump device along the
  • FIGS. 4 to 6 in various views parts of a tank unit, as used for the motor-pumping device according to Figures 1 and 2 ..; and FIGS. 7 to 12 are different in the manner of hydraulic circuit diagrams
  • the motor-pump device according to the invention is suitable as a high-low-pressure unit especially for:
  • the motor-pump device shown as a whole from the outside in FIG. 1, as shown, can be used horizontally as well as vertically according to the longitudinal section of FIG. 2.
  • the motor-pump device shown in FIG. 2 is designed as a modular system and has a designated as a whole with 10 electric motor.
  • the electric motor 10 may consist of a conventional asynchronous machine with an outer stator 12 and an inner rotor 14 (see Fig. 2).
  • the rotor 14 is connected in the usual way with a drive shaft 1 6 of the electric motor 10, which is rotatably mounted end in bearings 18. Between the end Lagerlager- len 18 yet another third bearing 20 is present, which is accommodated in the multi-part motor housing 22 of the electric motor 10 on an inner wall.
  • the electric motor 10 can be equipped with or without fan; shown here in Fig. 1 and 2 with fan. 2, a radial piston pump 24 is installed below the motor housing 22 with a total of three pump elements 26 as shown in FIG. 3.
  • a radial piston pump 24 is installed below the motor housing 22 with a total of three pump elements 26 as shown in FIG. 3.
  • the mentioned three or six valve spring-controlled radial piston pump elements 26 are actuated independently of direction by an eccentric drive 28 which is driven by the external electric motor 10, via its drive shaft 16.
  • the pump elements 26 shown in FIG. 3 are accommodated in a pump housing in the manner of an annular flange 30. This ring flange 30 is, as shown particularly in FIG.
  • a gear pump 34 is integrated within the tank unit 32, the technical structure is customary and therefore not shown in detail.
  • the gear pump 34 removes, seen in the direction of FIG. 2, on its underside via a removal nozzle 36 with filter element 45 fluid from the tank unit 32 for further promotion from the unit out in a single or dual circuit system of a hydraulic system (not dargestel lt ).
  • the radial piston pump 24 has a suction line 38 with filter element 39 for the purpose of filtering the oil removed from the tank 32 by means of the radial piston pump 24, which is also discharged from the hydraulic unit to the outside to a hydraulic consumers, as described above.
  • the output shaft 42 of the gear pump 34 which is shown only schematically and schematically in Fig. 2, is driven by the Antriebswel le 1 6 of the electric motor 1 0 via a so-called. Oldham coupling 44.
  • the nozzle-like fluid-removal parts, including the suction lines 36 and 38 designed so that a fluid removal from the tank 32 can be carried out both in a horizontal mounting position of the unit according to the illustration of FIG. 1 and a vertical uprisings - tion of the unit as shown in FIG. 2 is possible.
  • the ventilation fi lter 40 can be seen (Fig. 1, 3).
  • the motor-pump device can be equipped with radial piston pumps 24 and / or with gear pumps 34 that a pressure supply for hydraulic single and dual circuit systems is possible, and only in Low pressure (ND) or only in high pressure (HD) or according to low pressure (ND) and high pressure (HD) combined.
  • the respective radial piston pump 24 of the high pressure supply and the respective used gear pump 34 is to serve the low pressure supply of a hydraulic circuit.
  • this may be formed two- or four-pole, and is the unit shown in FIG. 1 only for pure low-pressure applications provided in continuous operation, shown in Fig. 1 from the outside damping ring 46 between the annular flange 30 and the housing 22 of the electric motor 10 also omitted or replaced due to another pump control.
  • this can be supplied with high pressure (HD), low pressure (LP), high and low pressure (HN) and low pressure / low pressure (NN).
  • HD high pressure
  • LP low pressure
  • HN high and low pressure
  • NN low pressure / low pressure
  • only one radial piston pump 24 can be used as a high-pressure pump or only one gear pump 34 as a low-pressure pump; Otherwise, all other structural components, as shown by way of example in FIG. 2, are retained. Only in the case of pure low-pressure variants (N, NN, N-N) can a different motor-pump connection be used, depending on the application.
  • the mentioned high-pressure pump can at flow rates of about
  • the low-pressure pump has a higher flow rate up to, for example, 8.6 l / min at 250 bar or, for example, 20 l / min at 1 10 bar supply pressure. If two low-pressure supply pumps are combined with each other, one of the pumps can be switched to the non-pressurized circulation as needed in single-circuit operation (NN) to save energy become. Furthermore, the pumps can be operated alternately or in parallel in the two-circuit system (NN, HN, Hihi). The values are only examples and can be adjusted according to the application.
  • an electrical connection box 50 is present on the outer circumference of the motor housing 22.
  • At the pump flange 30 is at least one longitudinal linkage, designated as a whole with 48, including valves attached.
  • a level indicator of the container contents can be integrated for horizontal construction on a tank foot 62 and for vertical construction on the tank housing 52.
  • FIGS. 4 to 6 the tank unit 32 is now reproduced in more detail.
  • Fig. 4 shows the tank unit 32 in the manner of an exploded view with a housing 52 which is formed as an extruded profile, preferably made of aluminum.
  • the housing 52 along its outer periphery, the housing 52 on axially continuous cooling ribs 54, which are integral part of the extruded profile.
  • the aforementioned cooling ribs 54 are interrupted by two flat profiles 56 and a flange plate 58 on the underside of the housing 52 in the circumferential direction.
  • the two flat profiles 56 and a flange plate 58 on the underside of the housing 52 in the circumferential direction.
  • Flat profiles 56 can be used to carry a machine plate unspecified by the manufacturer and as a further attachment a level gauge or sensor (not shown).
  • the flange plate 58 serves for the horizontal elevation of the presented unit, as shown by way of example in FIG.
  • Said flange plate 58 is an integral part of the inherently cylindrical housing body 52 of the tank unit 32 and is designed as a hollow profile, as shown in particular the representations of FIGS. 5 and 6, designed.
  • two cooling channels 60th 4 Between the flange plate 58 and the cylindrical shell of the housing 52 extend along the tank unit 32, two cooling channels 60th 4, the housing 52 is accommodated between two add-on components 62, 64, wherein the right-hand connection component (tank foot) 62 seen in the viewing direction in FIG.
  • the left-hand connection component (tank adapter) 64 seen in the viewing direction in FIG. 4 carries at its upper right end the filling nozzle 40 for the tank unit 32 and closes in succession, as shown in FIG. 1, against the annular flange 30 with the radial piston pump 24 at.
  • the two flanges 62, 64 have connection points 68 with which a cooling circuit (not shown in detail) can be realized, in which the coolant enters the connection point 68 of the tank foot 62 according to the arrow representations. is then forwarded to the two cooling channels 60 and collected by the tank adapter 64, the corresponding heated coolant on the junction 68, the tank unit 32 in turn leaves.
  • a cooling circuit not shown in detail
  • the cooling channels 60 enable integrated liquid cooling for the tank contents of the tank unit 32.
  • cooling lubricant As cooling medium, it would be advisable to use the cooling lubricant when using the aggregate in machine tools, since a cooling lubricant supply as a unit is often already integrated in the machine tool.
  • other cooling media such as water, glycol, etc. are used.
  • the cooling medium along the tank profile due to the temperature difference, the heat of the oil tank and thus also the hydraulic oil, which is stored in the tank unit 32.
  • the coolant inlet is located at the tank foot 62 and the outlet at the tank adapter 64.
  • this cooling method is in certain cases a saturation of the oil temperature below the permitted max. Temperature reached.
  • electric motors with appropriate operating mode are used for the periodic uninterrupted operation up to continuous operation.
  • the two thermal problem areas (oil temperature and engine temperature) of the hydraulic unit for the two modes mentioned are solved. Due to the integrated liquid cooling and a raised surface by the cooling fins 54 and good heat conduction through the use of the aluminum material for the housing 52 is a very good cooling of the hydraulic fluid before and it can be achieved higher operating modes and switch-on with the unit during operation. These cooling methods can be used both in the horizontal (FIG. 1) and in the vertical (FIG. 2) alignment of the unit. For a vertical installation situation, the through-holes 70 on the tank foot 62 can also be provided with screw connections, not shown. In the following, the individual system solutions will now be presented by means of examples according to FIGS. 7 to 12.
  • FIG. 7 shows a low-pressure recirculation system, wherein the gear pump designed as a low-pressure pump 34 feeds into a single supply port P of the hydraulic recirculation system (not shown).
  • the fluid coming from the low-pressure system is returned to the tank unit 32 via the tank connection T for a new removal.
  • the removal takes place via the removal nozzle 36 and the low-pressure filter element 45 connected thereto, so that the fluid then reaches the suction side of the gear pump 34.
  • the ports P, T serve as an interface for fluid continuity to a not closer illustrated linking system of a hydraulic circuit, which is designed here as Einniksystem.
  • the gear pump 34 delivers the fluid to the supply port P of the single-circuit system on its pressure side.
  • the solution according to FIG. 8 is modified compared to the embodiment according to FIG. 7 insofar as now two low-pressure gear pumps 34 supply a common supply connection P.
  • one of the two pumps 34 can be switched to the non-pressurized circuit as needed to save energy, to work more efficiently and to enable a variable volume flow in two operating points.
  • gear pumps 34 for the low pressure are present and each pump 34 as a supply pump supplies its own supply connection P1 and P2.
  • two gear pumps are to be provided. But it is also possible, right from the start to integrate several gear pumps 34 in the tank unit 32 and then take to implement the solution of FIG. 7, only one of the available gear pumps 34 in operation.
  • only one radial piston pump 24 is used for a high-pressure supply of the single-circuit system, so that the gear pumps 34 provided for the low-pressure region are not provided within the unit.
  • the radial piston pump 24 according to FIG. 10 conveys pressurized fluid into the pressure supply connection P with only one supply branch 72.
  • a supply port P1 is supplied via a supply line 72 of the high-pressure radial piston pump 24, whereas the low-pressure gear pump 34 charges the further pressure supply port P2 with presettable pressure fluid.
  • a two-circuit system is realized via the pressure supply connections PI, P2, once with high pressure (P1), once with low pressure (P2).
  • the two supply ports P1, P2 in turn fluidly connect to each other via a valve within the concatenation, so that overall an increased volume flow (HN) is achieved compared to a solution Only a high-pressure pump, for example in the form of the radial piston pump 24 according to FIG. 10.
  • each supply connection P1, P2 is assigned its own supply line 72, which is supplied by the radial piston pump 24.
  • a number of pistons, for example, three pistons or pump elements 26 can be assigned to the circle with the supply port P1 and the remaining piston or pump elements 26 then provide the second circle on the other Supply connection P2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

Ensemble motopompe conçu sous forme de système modulaire, constitué d'au moins un moteur électrique (10), d'une pompe à pistons radiaux (24) pouvant être entraînée par le moteur électrique (10), servant de préférence à une alimentation haute pression, et/ou une pompe à engrenages (34) servant de préférence à une alimentation base pression, d'un ensemble réservoir (32), d'éléments annexes tels que des soupapes (48) en enchaînement modulaire longitudinal, d'un dispositif de mesure de niveau de remplissage, et de boîte de jonction. Pour la réalisation d'un système hydraulique à un ou plusieurs circuits, chaque pompe d'alimentation (24, 34) comporte un raccord d'alimentation individuel pour le circuit respectif du système utilisé, ou plusieurs pompes d'alimentation (24, 34) utilisées débitent dans un raccord d'alimentation commun (P), ou une seule pompe d'alimentation (24), servant de préférence à une alimentation haute pression, présente plusieurs lignes d'alimentation qui sont chacune raccordées à un raccord d'alimentation.
EP17761804.8A 2016-08-29 2017-08-29 Ensemble motopompe Active EP3504433B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016010669.7A DE102016010669A1 (de) 2016-08-29 2016-08-29 Motor-Pumpenvorrichtung
PCT/EP2017/001026 WO2018041401A1 (fr) 2016-08-29 2017-08-29 Ensemble motopompe

Publications (3)

Publication Number Publication Date
EP3504433A1 true EP3504433A1 (fr) 2019-07-03
EP3504433B1 EP3504433B1 (fr) 2020-04-22
EP3504433B2 EP3504433B2 (fr) 2024-01-17

Family

ID=59791023

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17761804.8A Active EP3504433B2 (fr) 2016-08-29 2017-08-29 Ensemble motopompe

Country Status (3)

Country Link
EP (1) EP3504433B2 (fr)
DE (1) DE102016010669A1 (fr)
WO (1) WO2018041401A1 (fr)

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DE102018001725A1 (de) * 2018-03-05 2019-09-05 Hydac Fluidtechnik Gmbh Anschlussvorrichtung
DE102018111059A1 (de) * 2018-05-08 2019-11-14 Speck-Kolbenpumpenfabrik Otto Speck Gmbh & Co Kg Antrieb für eine kolbenpumpe oder einen -kompressor
FR3091561B1 (fr) * 2019-01-03 2021-05-28 Automatisation Et Controle Du Serrage Microcentrale hydraulique
DE102019200703A1 (de) * 2019-01-21 2020-07-23 Hawe Hydraulik Se Sensoreinheit, Fluidaggregat mit Sensoreinheit und Verfahren zur Messung von Parametern eines Fluids
DE102019206326A1 (de) * 2019-05-03 2020-11-05 Hawe Hydraulik Se Pumpengehäuse mit Kühlmittelkanal und Pumpenaggregat
DE102019212074A1 (de) * 2019-08-13 2021-02-18 Robert Bosch Gmbh Motor-Hydromaschinen-Einheit zum Anbau an ein Hydraulikaggregat
CN112032015A (zh) * 2020-09-03 2020-12-04 王萍 一种逐步驱动式高效水泵
CN115681067A (zh) * 2022-09-30 2023-02-03 北京精密机电控制设备研究所 一种集驱动控制功能同轴一体化伺服电机泵

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DE2021210A1 (de) 1970-04-30 1971-11-11 Bbc Brown Boveri & Cie Anordnung fuer den Anbau eines Elektromotors an eine Hydraulik-Pumpe
CH596697A5 (en) † 1975-05-26 1978-03-15 Theodor Meier Pump set with air-cooled flanged electric motor
DE9405871U1 (de) 1994-04-08 1994-06-01 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulisches Motorpumpenaggregat
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DE19615053A1 (de) 1996-04-17 1997-10-23 Teves Gmbh Alfred Elektromotor-/Pumpenaggregat
DE29609702U1 (de) 1996-05-31 1996-08-29 Fa. Ursula Schickedanz, 73033 Göppingen Bügeleisen
DE29906881U1 (de) * 1999-04-16 1999-07-01 Heilmeier & Weinlein Elektrohydraulisches Motorpumpenaggregat
DE19942567A1 (de) 1999-09-07 2001-03-22 Fluidtech Gmbh Vorrichtung zum Pumpen von Fluid
DE20007554U1 (de) 2000-04-26 2000-08-10 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Motor-Pumpenaggregat
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Also Published As

Publication number Publication date
EP3504433B2 (fr) 2024-01-17
WO2018041401A1 (fr) 2018-03-08
EP3504433B1 (fr) 2020-04-22
DE102016010669A1 (de) 2018-03-01

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