WO2021204542A1 - Ensemble constitué d'un système de travail pour réaliser un travail à l'aide d'un fluide hydraulique sous pression et d'un dispositif de pompe - Google Patents

Ensemble constitué d'un système de travail pour réaliser un travail à l'aide d'un fluide hydraulique sous pression et d'un dispositif de pompe Download PDF

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Publication number
WO2021204542A1
WO2021204542A1 PCT/EP2021/057560 EP2021057560W WO2021204542A1 WO 2021204542 A1 WO2021204542 A1 WO 2021204542A1 EP 2021057560 W EP2021057560 W EP 2021057560W WO 2021204542 A1 WO2021204542 A1 WO 2021204542A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
hydraulic fluid
displacement
volume flow
group
Prior art date
Application number
PCT/EP2021/057560
Other languages
German (de)
English (en)
Inventor
Christian Hans REESE JIMENEZ
Felix Fischer
Markus Gärtner
Katharina Schmitz
Original Assignee
Rheinisch-Westfälische Technische Hochschule (Rwth) Aachen
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 Rheinisch-Westfälische Technische Hochschule (Rwth) Aachen filed Critical Rheinisch-Westfälische Technische Hochschule (Rwth) Aachen
Publication of WO2021204542A1 publication Critical patent/WO2021204542A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/34—Control not provided for in groups F04B1/02, F04B1/03, F04B1/06 or F04B1/26
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing

Definitions

  • the invention relates to an arrangement of a work system for performing work by means of a pressurized hydraulic fluid and a displacement pump with a control device for discreetly changing the system volume flow to be supplied to the work system as a proportion of its total volume flow, the work volume flow in the work system doing work and no work performing excess volume flow is divisible.
  • Positive displacement pumps with discretely variable displacement units have the potential to be a more energy-efficient alternative to conventional adjustable units.
  • a discretely adjustable displacement unit e.g. individual pistons are excluded from being conveyed into the work system to be operated during the conveying phase.
  • the arrangement of the type mentioned at the beginning is characterized in that the at least one displacement pump comprises several displacement units, in particular displacement spaces, the total number of all displacement units being divided into several displacement groups and each displacement group at least one displacement unit, preferably comprises at least two displacer units, and all displacer units are connected on the input side to a hydraulic fluid tank for the supply of hydraulic fluid, and the high-pressure lines of the displacer units on the output side are merged into a respective common group line in a respective displacer group, and all group lines open into a supply line, in particular directly or via a check valve, via which a system volume flow from the total volume flow of hydraulic fluid can be conveyed to the working system, and at least one group enline a switching valve is assigned, preferably a switching valve is assigned to all group lines, with which the respective assigned group line can be switched to the hydraulic fluid tank via a bypass to bypass the working system and via a throttle valve, preferably adjustable throttle valve common to all switchable group lines, with the switch
  • the invention provides that the system volume flow can be changed discretely to the extent that part of the total volume flow of the displacement pump of such an arrangement can be branched off by means of at least one switching valve, which is then used as the tank volume flow named in this description, i.e., bypassing the working system again Hydraulic fluid tank is supplied.
  • the system volume flow thus results from the total volume flow minus the tank volume flow diverted via at least one bypass.
  • the discretization takes place with the number of possible bypass connections of group lines to which a switching valve is assigned.
  • group lines that always feed into the work system without the option to switch to a bypass, and group lines to which a switching valve is assigned and whose volume flow can thus be bypassed the work system.
  • the invention preferably provides that all group lines provided have a respectively assigned switching valve with which the volume flow of the assigned group line can alternatively be switched to the bypass instead of to the working system.
  • Displacement pumps have displacement units, e.g. displacement spaces in piston pumps.
  • Displacement pumps can preferably be designed as piston pumps, the displacement units of which are formed by piston spaces.
  • Displacement pumps can, for example, also be designed as vane pumps, with a respective cell space between two vanes forming a displacement unit.
  • Displacement pumps can, for example, also be designed as gear pumps, the spaces enclosed between the gear wheels forming displacement units.
  • a displacer unit or several displacer units can form a displacer group. It is also possible for all displacement units of a displacement pump to form a displacement group. In such a case, the invention thus has at least two positive displacement pumps.
  • the invention provides at least one positive displacement pump in the arrangement, so it is also possible to use several, in particular several identical, but also several different displacement pumps in the arrangement.
  • displacement pumps can differ, for example, in terms of their delivery rate.
  • a displacement group has at least one displacement unit in each case, preferably at least two displacement units, in particular the same displacement pump, if several are used.
  • the invention can, for example, provide that the control pressure generated by the throttle valve, for example the differential pressure, is around the throttle valve results around or is a back pressure that prevails in the direction of fluid flow in front of the throttle valve.
  • control pressure is measured, e.g. as an electrical variable and converted into a control signal for controlling the switching valves by means of electronics.
  • a control signal can then be an electrical switching signal.
  • the invention makes the regulation accessible in a purely hydraulic manner.
  • the control pressure can be recorded hydraulically and used in the arrangement, e.g. directly or after conversion / conversion, hydraulically to control a respective valve, i.e. to trigger the switchover.
  • each switching valve can be hydraulically actuatable, in particular by the control pressure itself or by a switching pressure which acts on the respective valve as a function of the control pressure.
  • the pressure acting in the direction of fluid flow upstream of the throttle valve, in particular dynamic pressure, or the pressure difference acting around the throttle valve as control pressure can thus directly form the pressure for triggering the switching process of at least one, in particular all of the switching valves.
  • the control pressure can act, for example, by fluid connection of a line area upstream and / or downstream of the throttle valve with at least one of the switching valves, preferably with all switching valves in the respective piston chamber of the switching valve, in particular by virtue of the fluid connection opening directly into the respective piston chamber.
  • the control pressure at the throttle prevails directly in the piston chamber.
  • the switching valves can preferably be set up to effect the switching process in each case at different control pressures.
  • control valves of the invention can be constructed in such a way that they have a piston which is guided in a cylinder and which, by reversing its position in the control valve, redirects the volume flow of a group line instead of to the working system in the direction of the hydraulic tank via the bypass, in particular actually short-circuits it .
  • the piston can, for example, close a valve inlet to which an assigned group line is connected or switch to the bypass or at least in the direction of a bypass.
  • the piston can be moved against a restoring force by the control pressure or the force exerted by it on the piston, in particular with different large restoring forces or piston area sizes in the control valves that they trigger the switching process at different control pressures.
  • all control valves can have the same control pressure applied to them, but switch at different control pressures.
  • each switching valve can be assigned its own bypass line, which opens directly or via the bypass line of another switching valve into a line section common to all bypass lines in the flow direction upstream of the throttle valve.
  • At least one of the switching valves assigned to a group line is indirectly connected to the bypass line via another switching valve, in particular when the other switching valve is in a position blocking the connection between the bypass and its assigned group line.
  • this can be provided if there are only two switching valves in the arrangement, each of which is assigned to a group line.
  • the two group lines can, for example, convey differently large flow rates, for example by having these from two displacement groups with different numbers of displacement units are acted upon or by the fact that the group lines are acted upon by different displacement pumps (eg with different delivery rates).
  • operation can be carried out in such a way that when a first control pressure level is reached by initially two group lines conveying to the working system, one group line, preferably the one with the lower volume flow, is switched on by switching its assigned switching valve to the bypass via the second control valve of the other group line is switched.
  • one group line preferably the one with the lower volume flow
  • the group line preferably the one with the higher volume flow
  • the group line can be switched in the direction of the bypass by switching the second switching valve, whereby the other group line, in particular with the lower flow rate of both group lines, is separated from the bypass at the same time as this control valve is switched and promotes again in the direction of the work system, in particular what causes a switch between the group leaders.
  • An embodiment of the invention can also provide that the arrangement comprises an analog-digital converter unit which is set up to generate control signals as the control pressure rises, in particular, depending on which the group lines of different displacement groups can be successively connected to the bypass with the switching valves and / or the analog-digital converter unit is set up to generate control signals with falling control pressure, depending on which the group lines of different displacer groups can be switched off from the bypass successively with the switching valves.
  • the control pressure does not act directly in the control valves, but is preferably converted hydraulically in the converter unit in order to switch the control valves with the converted pressure as a control signal. This converted or converted pressure thus forms a switching pressure with which the switching of the respective switching valve is triggered.
  • this version with an analog-digital converter unit can also work electrically / electronically instead of hydraulically.
  • the control pressure is recorded by measurement and converted in the converter unit into an electrical control signal for controlling the respective electrical control valves.
  • each switching valve can furthermore preferably be actuated hydraulically and the analog-digital converter can therefore be used to generate a converted hydraulic switching pressure for each switching valve as a function of the control pressure dropping across the throttle valve.
  • the analog-digital converter is designed as a valve for generating a respective hydraulic switching pressure, with which either the low pressure level of the hydraulic fluid tank or the high pressure level as a converted switching pressure or control signal depending on the control pressure at a respective switching valve a pressure source can be switched on.
  • a pressure accumulator in particular a pressure accumulator charged by the hydraulic fluid of the system volume flow, preferably a pressure accumulator integrated in the working system, can be used as the pressure source.
  • the at least one displacement group conveying into the working system can be used as the pressure accumulator.
  • the valve in the analog-digital converter unit preferably comprises a valve element which is movable as a function of the control pressure and with which, depending on its position, the low pressure level of the hydraulic fluid tank or the high pressure level of the pressure source can be connected to the respective switching valve as switching pressure.
  • This is the varying, in particular, continuously varying control pressure at the throttle valve is converted into only two different pressure levels, with which the switching of a respective control valve takes place. Which of the multiple control valves is acted upon by the converted pressure level, in particular next, depends on the control pressure at the throttle valve with which the position, in particular the range of movement of the valve element in the converter unit is determined.
  • valve element can preferably be designed as a piston that is axially movable in a cylinder bore of the converter unit, with two axially spaced cylinder spaces being formed between the piston and the cylinder bore wall, one of which is connected to the hydraulic fluid tank by a line section in the flow direction upstream of the throttle and the other with the pressure source is connected and by displacement of the piston in the cylinder bore wall openings of control lines of the switching valves can be connected to one of the two cylinder chambers depending on the control pressure acting on an axial end face of the piston.
  • the openings can be successively connected to the cylinder space having the high pressure level with increasing control pressure and can be successively connected to the cylinder space having the low pressure level with falling control pressure.
  • the piston can preferably be axially movable against an acting counterforce, in particular with the counterforce being changeable as a function of the piston position, e.g. by a spring element exerting the counterforce with a non-linear characteristic.
  • the invention can provide that the working system is a working machine driven with pressurized hydraulic fluid of the at least one displacement group, one with pressurized one standing hydraulic fluid of the at least one displacement group of chargeable pressure accumulator and a pressure relief valve, preferably an adjustable pressure relief valve, wherein the system volume flow with the pressure relief valve can be divided into the working volume flow, which is performed while performing work through the working system to the hydraulic fluid tank and the excess volume flow, which bypassing the Working system is performed via the throttle valve to the hydraulic fluid tank.
  • a work machine is preferably a prime mover in which hydraulic energy can be converted into mechanical work, for example a hydraulic motor.
  • control pressure generated with the throttle valve is preferably generated by the excess volume flow alone when all displacement groups feed into the working system, or generated by the total volume flow from the excess volume flow and the tank volume flow when at least some of the displacement groups are connected to the bypass.
  • the switching pressure of the analog-digital converter converted from the control pressure acts against a counter pressure that is at most 5 to 20% less than the pressure of the pressure relief valve.
  • FIG. 1 shows an embodiment with a positive displacement pump P1, for example a piston pump.
  • This has several displacement units VE, for example piston chambers VE, which are numbered consecutively in the displacement pump P1.
  • three displacement units VE are combined to form a displacement group and convey into a common group line G1, G2 or G3, in particular each via a check valve RV.
  • the displacement units 9, 3 and 6 promote in the group line G1, the displacement units 2, 8 and 5 promote in the Group management G2 and displacement units 1, 7 and 4 feed into group management G3.
  • Each group line G1, G2, G3 is connected to an assigned switching valve V1, V2 or V3 with the same number, with which the respectively assigned group line can be switched, in particular short-circuited, to the hydraulic fluid tank H via a respective bypass B1, B2 and B3 with the same number.
  • each switching valve V1, V2, V3 is connected with its piston chamber to an assigned control line K1, K2, K3 of an analog / digital converter unit ADW.
  • the control lines K3, K2 and K1 are switched on one after the other in this order from the low pressure level of the hydraulic tank H to the high pressure level of a pressure source DQ when the piston KO is in the Figure 1 is shifted to the right.
  • the control pressure in the piston chamber KR acts through a direct control pressure line connection SDL between the piston chamber KR and the throttle valve DR, the throttling effect of which can be adjusted.
  • the control pressure can be given by the back pressure which is generated with the throttle valve in the fluid flow direction upstream of the throttle valve.
  • the respective switching valve V1, V2 and V3 switches the assigned group line G1, G2, G3 to the bypass B1, B2, B3.
  • the volume flow in the group line is then passed as a tank volume flow via the respective bypass to the hydraulic fluid tank and adds up to the excess volume flow that is present in the working system AS Working machine AM, which is led from the circulation line U via the same throttle DR.
  • the pressure source DQ can be part of the work system AS, e.g. a membrane vessel, and can be charged by the pressure level that is present in the group lines G1, G2, G3 when these are connected to the work system AS.
  • This pressure level can preferably be defined by the pressure limiting valve.
  • all group lines G1, G2, G3 could initially be connected to the work system AS and, in total, provide the system volume flow.
  • the working system AS branches off the working volume flow required to carry out the work and sends the excess volume flow that is not required via the circulation line U and the throttle DR back to the hydraulic fluid tank H.
  • the control pressure at the throttle DR is generated from the excess volume flow. This is initially low and thus the piston KO is in the left position, all switching valves V1, V2, V3 are switched on to low pressure.
  • the excess volume flow then initially decreases. If the demand for the working volume flow continues to fall, the excess volume flow increases again and the next switching valve is switched in the same way, in particular until all group lines are switched to the bypass. In this condition the entire volume flow flows to the tank as a tank volume flow. The system volume flow is zero and therefore the excess volume flow is also zero.
  • the control pressure generated by the throttle is at its maximum, so that the piston KO of the analog-digital converter unit ADW Wert is shifted all the way to the right and the high pressure level from the pressure source DQ is applied to the switching valves V1, V2 and V3 via the cylinder chamber Z1. The regulation is then inactive.
  • the working system AS can then initially serve a new request from the pressure source DQ, as a result of which the pressure source DQ, which is designed as a pressure accumulator, is discharged. Therefore, the switching pressure applied to the valves V1 to V3 falls, since it comes from this pressure source DQ via the cylinder space Z1.
  • the control pressure generated at the throttle valve DR remains constant at its maximum value. The regulation therefore remains unaffected for the time being.
  • the switching pressure falls by an amount that corresponds to the counter pressure against which the switching pressure of one of the switching valves, in particular V1, acts, preferably falls by the aforementioned amount of 5-20%, because the pressure source DQ has discharged so far, then opens that concerning switching valve, in particular switching valve V1, whereby the volume flow from the group line G1 flows as a system volume flow to the working system.
  • the regulation starts again.
  • the switching valves will switch the group lines back on to the working system in reverse order, for which the low pressure in the cylinder chamber Z2 is switched on to the control lines K1, K2 and K3 in this order.
  • FIG. 1 shows another embodiment.
  • both pumps P1 and P2 initially convey the entire volume flow as a system volume flow to the working system AS via their group lines. It can be any work system AS that does not have to correspond to the work system of FIG. From this, the unused excess volume flow comes back via the circulation line U, which guides this excess volume flow via the throttle DR and generates the control pressure.
  • the system volume flow is thereby reduced by the volume flow of the displacement group of pump P2.
  • the second switching threshold of the switching valve V1 which is above the first switching threshold, is exceeded and the switching valve V1 is also switched, which causes the group line G1 to be switched to the bypass and, at the same time, the group line G2 to be switched back to the working system.
  • the working system acts as the system flow rate, i.e. first the flow rate from G1 and G2, then G2 is switched off, then G2 and G1 are switched over.
  • FIG. 3 shows a modified version compared to FIG. 2, in which the control pressure is generated by the differential pressure that is generated around the throttle valve DR.
  • Line areas L1 in front of and L2 behind the throttle valve DR are led into the respective piston chambers on both sides of the piston of the respective switching valve V1, V2, so that the differential pressure that is generated around the throttle valve DR also acts directly on the piston of each valve V1, V2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un ensemble constitué d'un système de travail (AS) pour réaliser un travail à l'aide d'un fluide hydraulique sous pression et d'une pompe de déplacement (P1), comprenant un dispositif de régulation permettant de modifier de manière discrète le débit volumétrique de système à fournir au système de travail (AS) en tant que proportion du débit volumétrique total du système, ledit débit volumétrique de système pouvant être séparé dans le système de travail (AS) en un débit volumique de travail qui réalise un travail et un débit volumétrique en excès qui ne réalise pas de travail. La ou les pompes à déplacement (P1) comprennent de multiples unités de déplacement (VE), le nombre total d'unités de déplacement (VE) étant divisé en de multiples groupes de déplacement, et chaque groupe de déplacement comprenant au moins une unité de déplacement. Toutes les unités de déplacement (VE) sont reliées à un réservoir de fluide hydraulique (H) respectif côté entrée pour être alimenté en fluide hydraulique, et les conduites haute pression côté sortie des unités de déplacement (VE) dans chaque groupe de déplacement sont combinées pour former une conduite de groupe commune respective (G1, G2, G3). Toutes les conduites de groupe (G1, G2, G3) débouchent dans une conduite d'alimentation, par l'intermédiaire de laquelle un débit volumique de système peut être acheminé à partir du débit volumétrique total de fluide hydraulique vers le système de travail (AS), et au moins une conduite de groupe (G1, G2, G3) est appariée à une vanne de commutation (V1, V2, V3), au moyen de laquelle la conduite de groupe appariée respective (G1, G2, G3) peut être commutée vers le réservoir de fluide hydraulique (H) par l'intermédiaire d'une dérivation (B1, B2, B3) afin de dévier le système de travail (AS) et par l'intermédiaire d'une soupape d'étranglement (DR) commune à toutes les conduites de groupes commutables (G1, G2, G3). Après avoir été reliées à la dérivation (B1, B2, B3), les conduites de groupe commutables (G1, G2, G3) permettent à un débit volumétrique de réservoir d'être transporté depuis la totalité du débit volumétrique de fluide hydraulique jusqu'au réservoir de fluide hydraulique (H). Le système de travail (AS) est relié à une conduite de circulation (U) au moyen de laquelle le fluide hydraulique du débit volumique en excès peut être remis en circulation dans le réservoir de fluide hydraulique (H) par l'intermédiaire de la même soupape d'étranglement (DR). Chaque vanne de commutation (V1, V2, V3) peut être commutée sur la base d'une pression de commande générée par la soupape d'étranglement (DR) à l'aide de la somme du débit volumique de réservoir et du débit volumétrique en excès.
PCT/EP2021/057560 2020-04-09 2021-03-24 Ensemble constitué d'un système de travail pour réaliser un travail à l'aide d'un fluide hydraulique sous pression et d'un dispositif de pompe WO2021204542A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020110002.7A DE102020110002A1 (de) 2020-04-09 2020-04-09 Anordnung aus einem Arbeitssystem zur Verrichtung von Arbeit mittels eines unter Druck stehenden Hydraulikfluids und einer Pumpvorrichtung
DE102020110002.7 2020-04-09

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WO2021204542A1 true WO2021204542A1 (fr) 2021-10-14

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PCT/EP2021/057560 WO2021204542A1 (fr) 2020-04-09 2021-03-24 Ensemble constitué d'un système de travail pour réaliser un travail à l'aide d'un fluide hydraulique sous pression et d'un dispositif de pompe

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5259738A (en) 1988-09-29 1993-11-09 University Of Edinburgh Fluid-working machine
EP2664804A2 (fr) * 2012-05-15 2013-11-20 Robert Bosch Gmbh Régulateur de pression et de débit, unité de réglage pour une machine de refoulement hydraulique réglable dotée d'un régulateur de pression et de débit et procédé de régulation d'une telle unité de réglage
EP3620581A1 (fr) * 2018-09-10 2020-03-11 Artemis Intelligent Power Limited Appareil comportant un circuit hydraulique

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US6681571B2 (en) 2001-12-13 2004-01-27 Caterpillar Inc Digital controlled fluid translating device
JP5062492B2 (ja) 2005-09-23 2012-10-31 イートン コーポレーション 流体モーターとポンプの正味変位制御方法
DE102007041021A1 (de) 2006-09-01 2008-03-06 Robert Bosch Gmbh Steuereinrichtung für eine hydraulische Kolbenmaschine mit veränderbarem Volumenstrom
US8292605B2 (en) 2008-09-30 2012-10-23 Eaton Corporation Rotary fluid device with multi-level phase shift control
DE102009021832A1 (de) 2009-05-19 2010-11-25 Robert Bosch Gmbh Hydropumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5259738A (en) 1988-09-29 1993-11-09 University Of Edinburgh Fluid-working machine
EP2664804A2 (fr) * 2012-05-15 2013-11-20 Robert Bosch Gmbh Régulateur de pression et de débit, unité de réglage pour une machine de refoulement hydraulique réglable dotée d'un régulateur de pression et de débit et procédé de régulation d'une telle unité de réglage
EP3620581A1 (fr) * 2018-09-10 2020-03-11 Artemis Intelligent Power Limited Appareil comportant un circuit hydraulique

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