EP2954215A1 - Système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace - Google Patents

Système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace

Info

Publication number
EP2954215A1
EP2954215A1 EP14705278.1A EP14705278A EP2954215A1 EP 2954215 A1 EP2954215 A1 EP 2954215A1 EP 14705278 A EP14705278 A EP 14705278A EP 2954215 A1 EP2954215 A1 EP 2954215A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
consumer
valve
consumers
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.)
Withdrawn
Application number
EP14705278.1A
Other languages
German (de)
English (en)
Inventor
Philip Nagel
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.)
Karlsruher Institut fuer Technologie KIT
Original Assignee
Karlsruher Institut fuer Technologie KIT
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 Karlsruher Institut fuer Technologie KIT filed Critical Karlsruher Institut fuer Technologie KIT
Publication of EP2954215A1 publication Critical patent/EP2954215A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a hydraulic multi-user system, in particular a constant-pressure system or load-sensing system with energy-efficient hydraulic circuit for reducing energy losses according to the first claim.
  • a general aim is to reduce the above-mentioned systemic energy losses in multi-consumer systems and thus the required energy intake, in particular to counteract increasingly stringent emissions standards and rising raw material prices for ' fuel.
  • the following concepts are known:
  • a hydraulic source delivers a constant volume flow (constant pump) into a circuit to which the consumers are connected depressurized back into the tank
  • a constant-current system open-center systems
  • a hydraulic source delivers a constant volume flow (constant pump) into a circuit to which the consumers are connected depressurized back into the tank
  • the non-pressurized circuit to the tank is partially or completely closed, the inlet to the consumer partially or fully opened
  • Pressure relief valve limited system pressure. A valve to the consumers is opened, so that the maximum pressure on the pressure of the consumer is reduced. The system works with a volume flow and a pressure surplus.
  • variable-pressure systems In constant-pressure systems ("closed-center systems", [1-4]), a source with variable volume flow (variable displacement pumps) is regulated so that a constant system pressure is always present. is ensured.
  • the pressure is preset via a pump controller.
  • the pump controller ensures a system pressure below the pressure of the pressure relief valve, independent of the volume flow.
  • the pump When no consumer is actuated, the pump only delivers as much volume flow in order to compensate for any leakage and losses while maintaining the required pressure. If a consumer is activated, the flow rate of the pump increases, whereby the pressure of the pump is reduced via a valve to the pressure of the consumer.
  • the system operting at a pressure excess, but advantageously not with an additional volume of excess electricity.
  • Load-sensing systems are derived from constant-pressure systems, where, however, the control pressure of the pump (setpoint specification) is not constant .
  • Pump controller with fixed target specification is given, but by another hydraulic signal circuit .- The highest consumer pressure is identified, and reported to the pump, which is adjustable in their performance accordingly. This reduces systemic losses. The system works with the lowest possible variable and thus an energy-optimized pressure surplus and without excess flow. , .
  • Load-sensing systems allow precise adjustment of the variable displacement pump and thus of the total pressure, which is based on the highest load of the consumers in the hydraulic system.
  • a first approach is to divide consumers into several consumer groups with similar load profiles (multi-loop systems). Ideally, each consumer is operated only with a source adapted to it (positive displacement control). Each group is fed by one and each with its own hydraulic source adapted to its load profile. The difference in the energy needs of consumers per source and thus the . generated energy surplus are thus significantly reduced, the expenditure on equipment by additional groups and thus sources adversely increased.
  • hydraulic medium preferably hydraulic oil
  • the object of the invention is to provide a hydraulic multi-user system without additional sensors and with further reduced energy requirement and energy loss.
  • proposal to produce which is characterized by a simple apparatus and does not have the aforementioned disadvantages.
  • the solution of the task provides, an energy-efficient hydraulic circuit in addition to a Mehrckerersystem described above, preferably a constant-pressure system, more preferably a load-sensing system, in which the feed pressures as possible all connected to a source consumers as close as possible maximum required consumer supply pressure of the most heavily loaded consumer are raised.
  • a constant-pressure system preferably a load-sensing system
  • the feed pressures as possible all connected to a source consumers as close as possible maximum required consumer supply pressure of the most heavily loaded consumer are raised.
  • An increase in a consumer feed pressure instead of a throttling of unused pressures in the hydraulic medium in that the consumer a memory or buffer is connected in series, which is converted to another pressure reduction in usable power.
  • a system comprises at least two, preferably three or four consumers.
  • the system pressure is always greater than the maximum consumer pressure required and exceeds the consumer feed pressure of each .
  • a consumer pressure is the pressure that must be applied to a consumer in order to make it suitable for the provision of the respective intended consumer service.
  • the . Consumer pressures change with the activation of the consumer continuously during operation.
  • this maximum consumer pressure of the system forms the maximum consumer feed pressure, ⁇ as this pressure, in contrast to the consumer feed pressure of the other consumer, rather preferably not raised.
  • the property of the highest loaded consumer can change among the consumers of the system.
  • the system pressure in a constant-pressure system is not adjusted according to the maximum required consumer supply pressure.
  • the loss pressure is associated with a power loss.
  • the loss pressure is mainly due to the control valves, which passes through the hydraulic medium before and after passing through the consumer as well as other hydraulic components and resistors such. preferably on upstream pressure compensators.
  • the loss pressures generated by throttling bridge only significantly lower pressure differences compared to the conventional constant-pressure system.
  • An essential feature of the invention is that an existing power surplus (system power minus the consumer power) after leaving the consumer. is not throttled by a pre- or downstream valve by pressure release, ie, as a loss of energy to the hydraulic medium, is transmitted, but is redirected by a hydraulic circuit in a hydraulic accumulator.
  • the hydraulic accumulator is connected in series with the low-load consumers.
  • the memory serves as a buffer; 'The stored energy can be called up again at a later date.
  • the pressure in the memory is the memory pressure.
  • the hydraulic Mehrckerersystem thus comprises a hydraulic source for a flow rate of a hydraulic medium and at least two consumers with control valve, which are connected via a respective feed line and a return line to the source.
  • the system comprises at least one energy-efficient hydraulic circuit with at least one hydraulic pressure accumulator.
  • the latter is connected hydraulically with at least one return line between the consumer and the source, wherein the diversion into the store via a valve control preferably takes place with at least one diverter valve or at least one shut-off valve. A possible return flow from the reservoir back into the return line is preferably avoided via check valves.
  • the accumulator pressure raises the level of the consumer pressure without changing the amount.
  • the consumer feed pressure of such a series circuit is summed up by the consumer pressure and the accumulator pressure; he rises with the accumulator pressure.
  • the consumer feed pressures are increased by the storage pressures and passed to the consumer past residual pressures in the memory 'instead of relaxing by throttling. Power loss is stored in the memory and is therefore available for further utilization.
  • the consumer supply pressures of all consumers are after an increase in the lower consumer supply pressures by the accumulator pressure at a level, so that the required pressure losses and thus power losses are kept as low as possible by the control valves.
  • the hydraulic multi-user system with energy-efficient hydraulic circuit thus comprises a hydraulic source and at least two consumers with control valve, which are connected via a feed line and a return line to the source.
  • the source preferably comprises a hydraulic pump with a tank or another hydraulic pressure source for generating a preferably constant hydraulic medium volume flow (system volume flow Q Sys t) at constant or variable system pressure p Sys t.
  • the control valves are preferably in the form of controllable throttles in front of and behind the consumers Arranged feed lines and ' return lines and are used in particular a reduction of the system pressure on each required for a consumer power consumer pressure.
  • a consumer has its own control valve.
  • the energy-efficient hydraulic circuit comprises at least one hydraulic accumulator (or buffer) for the intermediate storage of pressurized hydraulic medium.
  • the accumulator has a hydraulic connection, preferably a continuous hydraulic line connection to at least one return line, upstream of each return line of each consumer.
  • at least one return line means are provided for the diversion of hydraulic medium in the memory.
  • the reservoir is a hydraulic accumulator which serves as another hydraulic source for at least one other consumer.
  • the diversion means preferably comprise at least one valve.
  • One embodiment provides for an energy efficient hydraulic circuit which is applied to each of the consumers Detects loss pressures and a memory or buffer between the return lines of the consumer switches back and forth so that the consumer leaving the flow rates are passed with the highest-ever .Leverustrate in the memory.
  • means are provided which compares the consumer pressures of all consumers in the system and removes the consumer with the highest consumer pressure (not the consumer supply pressure) from the series connection. The memory is charged until the sum of the accumulator pressure and the consumer pressure of the series connections less losses reaches the system pressure.
  • the hydraulic circuit comprises means for diverting H. hydraulic medium in the return line from the consumer to the source, which does not uselessly relieve a still biased hydraulic medium leaving the consumer, but redirects it into the hydraulic accumulator and / or to another consumer.
  • no throttle valves are provided for complete relaxation in the return line.
  • Hydraulic accumulator preferably comprises a closed rigid volume with a connection for the hydraulic medium, which is introduced into these and presses against a gas cushion and this compresses.
  • Memory is filled by an introduction of hydraulic medium until it settles in the memory with the accumulator pressure an equilibrium state.
  • the in the memory (or buffer) biased under pressure accumulator hydraulic medium forms retrievable and thus advantageously usable energy.
  • the reservoir is used for further use as a hydraulic source.
  • a prerequisite for this is that the accumulator pressure exceeds the consumer pressure required for further use.
  • energy recovery takes place in the system.
  • the following preferred energy uses are proposed:
  • the object is thus achieved by a robust hydraulic circuit which caches an amount of energy leaving the consumer for later use, wherein the circuit works hydraulically self-sufficient. and advantageously without additional control technology or sensors.
  • FIG. 1 shows a schematic representation of a conventional multi-user system
  • 2 a to c are each a graphical representation (pressure P over volume flow Q) of the power losses of a constant-pressure system (a), a load-sensing system (b) and a load-sensing system with energy-efficient hydraulic Circuit (c),
  • FIG. 5 shows by way of example a schematic representation of a multi-user system with memory as well.
  • FIG. 6 shows a schematic representation of a multi-user system with memory and 3/2-way valve on each consumer.
  • Fig.l is a conventional load sensor system as Mehrskeersystem according to the aforementioned prior art again.
  • it comprises three hydraulic piston drives as consumers 1, 2 and 3, each with a control valve 4, 5 and 6, a hydraulic source 7 for a volume flow of a hydraulic medium with tank 8, pump 9 and pump drive 10 as ever a supply line 11 from the source to the consumers and one return line 12 from the consumer in the tank.
  • control pressure of the pump (target specification) is not specified by a constant pump controller with fixed target specification, but is controlled by a further hydraulic signal circuit 13 with pressure relief valve 14 and return 15 in the tank.
  • the illustrated load-sensor system has check valves 20 between the inlets of the consumers 1 to 3, which forwards the maximum consumer pressure retrieved by the consumers hydraulically via a pressure relief valve line 33 to the overpressure valve 14 and thus the system pressure provided by the source via a Actuator 21 for controlling the pump forwards.
  • the consumer pressure is preferably tapped in front of the respective consumers upstream individual pressure compensators 22, 23 and 24 and / or on the control valves 4, 5 and 6.
  • the necessary connection lines are shown in Fig.l dashed lines.
  • FIGS. 2a to c illustrate graphically the integral performances in a constant-pressure system (a), a load-sensing system (b) and a load-sensing system with energy-efficient hydraulic circuit (c) in a representation of the pressure p via the volume flow Q.
  • the output is calculated from the product of the pressure and the volume flow.
  • the maximum possible The volume flow and pressure of the source are indicated in the diagrams with Q max or p max (basic data of the hydraulic source).
  • Q max or p max basic data of the hydraulic source.
  • three consumer services 16, 17 and 18 are shown in the diagrams, the required pressures change continuously during operation and must be covered by the pump performance.
  • the system volume flow Q syst is specified and the system pressure p syst of the hydraulic source in the example of a constant-pressure system (FIG. 2 a) fixed or set to a load-sensing system (FIGS. 2 b and c) is set variably.
  • the power loss 19 is calculated from the system power (product of system volume flow and system pressure) minus the respective load power applied. Even if the power loss - as shown in Fig.2b - can be minimized by a maximum of the pressure requested by the consumer readjustment of the system pressure, there is a power loss through the less loaded consumer, which is usually delivered in conventional systems as heat input into the hydraulic medium ,
  • the supply of the consumer is realized by the pump as in the aforementioned constant-pressure system or load-sensing system.
  • the return line has means, which instead of a return to the tank, a diversion of the hydraulic medium after leaving the consumer in a memory, when the pressure in the memory is less than the pressure of the recycled hydraulic medium.
  • the accumulator pressure thus assumes the function of a backpressure at the outlet of the consumer, whereby the load pressure at the input of the consumers can be increased by an amount resulting from the accumulator pressure, which otherwise leads to an increased power loss due to their load pressures.
  • the pressure difference applied by the consumers remains the same. A large part of the power loss will be is advantageously converted into stored power 25 (see Fig. 2c).
  • the return of the hydraulic medium from the load-sensing system is in the return line 12 after leaving the control valve (4, 5 or 6) in a 3/2-way valve .26 (diverter valve) passed, in which the hydraulic medium either the memory 27th or with the tank 8 is directed.
  • the hydraulic medium must always take the way through the diverter valve after leaving a consumer.
  • a diverter valve is provided for each consumer, which is preferably connected to a common memory. If the pressure of the hydraulic medium in the area in front of the 3/2-way valve is higher than the internal pressure of the reservoir Ps pe ic h e r , preferably the memory is connected in series with the consumer.
  • a check valve 28 is provided as a safety valve '.
  • a circuit gem. 4 in which as means for the diversion of hydraulic medium in the memory by a 2/2-way valve 29 (shut-off valve) is realized and the memory preferably always. hydraulically connected to the return line 12.
  • the branching from the return line takes place before the arrangement of the 2/2-way valve.
  • the shut-off valve is preferably closed when the pressure applied in the hydraulic medium in the return line 12 is greater than the accumulator pressure. It is preferably opened only when the aforementioned switching condition is no longer met, ie the memory is not fillable.
  • the 2/2-way valve prevents unimpeded drainage of prestressed hydraulic fluid in the tank 8.
  • a check valve 28 is provided as a safety valve.
  • differential cylinders are operated in the hydraulic drive system, two piston surfaces act against each other. These piston surfaces may differ, for example due to a piston rod arranged only on one side. In this case, one of the piston surface is reduced around the piston cross section, whereby the accumulator pressure due to a Kolben lake- This is not equal to 1 effective to the pump acting depending on the direction of movement of the piston is increased or decreased. This can be taken into account in the setting, in particular, of the means for deflecting, in particular the deflecting valves according to the aforementioned formula (1). Following the deflection into the memory only in a direction of movement of the piston, a fixed adjustment of the deflection is proposed with consideration. If both directions of movement of the piston are used in a memory charging, depending on the direction of movement is an adjustment via a switchable. Back pressure ⁇ z. B. above. an additional valve circuit proposed on the opposite valve spool side.
  • the means for the diversion of hydraulic medium in the memory as the.
  • Shut-off valves and deflection valves are advantageously controlled only hydraulically and regulated. Additional sensors or electronic control of these means are basically not required and preferably not available.
  • FIG. 5 shows schematically a load-sensing system with upstream individual pressure car of conventional design (see Fig.l),., Supplied by a memory 27, which can be fed via the return line 12 as in the aforementioned manner.
  • the means for diverting hydraulic medium into the reservoir or buffer e.g. Circuits with 3/2 or 2/2-way valves which can be used for this purpose (compare FIGS. 3 and 4) are shown in the schematic
  • Fig.5 Via a drain line 30, the hydraulic medium stored in the memory is led into an optional return valve 31 and passed to a consumer, in the example of the pump drive 10 as needed and / or above a certain pressure.
  • a check valve 32 prevents a direct forwarding into the tank 8 when a pressure difference, which can preferably be set, is exceeded.
  • the check valves 20 and the overpressure valve line 33 load-sensing line, load-signaling line
  • the consumer pressures raised by the accumulator pressure It is not the consumer pressures compared alone or out, but the respective applied maximum consumer pressure of the maximum loaded consumer against the lower consumer pressures plus the accumulator pressure.
  • FIG. 6 discloses the embodiment shown in FIG. 5, in which each of the three consumers 1 to 3 is equipped with one respective own 3/2-way valve 26 in the return lines 12 shown in FIG. Each 3/2-way valve is switched via a hydraulic adjustment.
  • abovementioned formula (1) for the 3/2-way valve required pressures are the consumer demanded maximum consumer pressure, which is tapped hydraulically on the pressure relief valve line 33, the. at the drain line 30 tapped storage pressure and the consumer per consumer between the respective control valve 4-6 and the check valves 20, tillgeriffenen consumer pressure.
  • another embodiment provides a tapping, not shown in the figures, of the system pressure Ps ys t mentioned in formula (1) at the feed line 11 between the pump 9 and the individual pressure compensators 22 to 24.
  • Possible power flow streams in the hydraulic circuit from the pump 9 of the source to the consumer 1-3 and back to the tank 8 of the source of the embodiment illustrated in Fig. 6 are as follows. Starting from the pump 9, the hydraulic medium is conducted through the feed line 11 to the three consumers 1 to 3, whereby, after branching into three consumer paths, there is one individual pressure balance 22 to 24 and one control pressure each. he valve 4 to 6 happens. In the consumer, a relaxation of the hydraulic medium takes place by a pressure difference in the amount of the consumer pressure. From the consumer forwarding via the return line 12 via the control valves 4-6 to the respective consumer assigned 3/2-Wegeven- valves 26 takes place in the directional valves, a check of the switching condition in accordance with. Formula (1) in the aforementioned manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace, comprenant une source hydraulique (7) servant à délivrer un débit volumique d'un fluide hydraulique ainsi qu'au moins deux charges (1, 2, 3), munies d'une vanne de commande (4, 5, 6), qui sont raccordées chacune à la source par le biais d'une ligne d'alimentation (11) et d'une ligne de retour (12). L'invention a pour objet de réaliser un système hydraulique à charges multiples sans capteurs supplémentaires et ayant une consommation d'énergie ainsi qu'une production d'énergie perdue encore réduites. Pour cela, le système comprend au moins un accumulateur hydraulique (27) ou réservoir tampon, l'accumulateur ou le réservoir tampon possède une liaison hydraulique comprenant au moins une conduite de retour et au moins une conduite de retour est dotée de moyens pour dériver le fluide hydraulique dans l'accumulateur ou le réservoir tampon.
EP14705278.1A 2013-02-05 2014-02-03 Système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace Withdrawn EP2954215A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310101107 DE102013101107A1 (de) 2013-02-05 2013-02-05 Hydraulisches Mehrverbrauchersystem mit energieeffizienter hydraulischer Schaltung
PCT/EP2014/000266 WO2014121910A1 (fr) 2013-02-05 2014-02-03 Système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace

Publications (1)

Publication Number Publication Date
EP2954215A1 true EP2954215A1 (fr) 2015-12-16

Family

ID=50137603

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14705278.1A Withdrawn EP2954215A1 (fr) 2013-02-05 2014-02-03 Système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace

Country Status (3)

Country Link
EP (1) EP2954215A1 (fr)
DE (1) DE102013101107A1 (fr)
WO (1) WO2014121910A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015201318A1 (de) * 2015-01-27 2016-08-11 Robert Bosch Gmbh Hydraulische Steueranordnung zur Druckmittelversorgung wenigstens zweier hydraulischer Verbraucher
CN105485069B (zh) * 2016-02-16 2017-04-12 江苏师范大学 一种用于负载敏感比例控制系统的电控液压节能装置及工作方法
DE102016117207A1 (de) 2016-09-13 2018-03-15 Linde Hydraulics Gmbh & Co. Kg Load-Sensing Antriebssystem
DE102016117206A1 (de) 2016-09-13 2018-03-15 Linde Hydraulics Gmbh & Co. Kg Load-Sensing Antriebssystem
DE102016117208A1 (de) * 2016-09-13 2018-03-15 Linde Hydraulics Gmbh & Co. Kg Load-Sensing Antriebssystem
IT202000027561A1 (it) * 2020-11-17 2022-05-17 Walvoil Spa Circuito idraulico con funzione combinata di compensazione e recupero energetico

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7124576B2 (en) * 2004-10-11 2006-10-24 Deere & Company Hydraulic energy intensifier
DE102008048056A1 (de) * 2008-09-19 2010-03-25 Still Gmbh Hydrostatisches Antriebssystem eines Flurförderzeugs
DE102008048054A1 (de) * 2008-09-19 2010-03-25 Still Gmbh Hydrostatisches Antriebssystem

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014121910A1 *

Also Published As

Publication number Publication date
WO2014121910A1 (fr) 2014-08-14
DE102013101107A1 (de) 2014-08-07

Similar Documents

Publication Publication Date Title
WO2014121910A1 (fr) Système hydraulique à charges multiples avec commutation hydraulique énergétiquement plus efficace
EP1588057B1 (fr) Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs
DE102006003414B3 (de) Hydraulische Schaltungsanordnung
AT516316B1 (de) Verfahren zur Steuerung einer hydraulisch angetriebenen Maschine
DE102007018600A1 (de) Hydraulisch/Elektrischer Wandler
DE102012207422A1 (de) Hydraulische Steueranordnung mit Lastdruckminderungund hydraulischer Ventilblock dafür
EP2846942B1 (fr) Presse à filer hydraulique et procédé de fonctionnement d'une presse à filer hydraulique
AT511575B1 (de) Hydrauliksystem für eine maschine zur herstellung einer faserstoffbahn
WO2016041685A1 (fr) Entraînement hydrostatique
DE102011107218A1 (de) Hydrostatisches Antriebssystem
DE102012019665A1 (de) Hydraulische Steueranordnung und Presse mit einer derartigen Steueranordnung
WO2012041497A2 (fr) Entraînement hydrostatique
DE102009047035A1 (de) Steuerungssystem mit aufgelösten Steuerkanten
AT516181B1 (de) Hydraulikaggregat
EP2487390B1 (fr) Système d'entraînement hydrostatique
DE102012016838A1 (de) Hydraulische Steuerschaltung für eine hydraulisch betätigte Gießeinheit
DE102008008102A1 (de) Verfahren und Vorrichtung zur Druckmittelversorgung von zumindest drei hydraulischen Verbrauchern
DE102011108256A1 (de) Hydraulische Antriebsvorrichtung und Austauschvorrichtung für hydraulische Antriebe
DE102008038381B4 (de) Hydrostatisches Antriebssystem
EP3045723B1 (fr) Pompe à pistons axiaux
DE102016117208A1 (de) Load-Sensing Antriebssystem
DE102011107222A1 (de) Hydrostatisches Antriebssystem mit einer im Fördervolumen verstellbaren Pumpe
EP1831573A1 (fr) Dispositif de commande hydraulique
DE102018218218A1 (de) Servohydraulischer Antrieb
EP2551232A1 (fr) Système de commande de grue

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150718

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIN1 Information on inventor provided before grant (corrected)

Inventor name: NAGEL, PHILIP

RIN1 Information on inventor provided before grant (corrected)

Inventor name: NAGEL, PHILIP

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20190319