EP2843241A2 - Système hydraulique - Google Patents

Système hydraulique Download PDF

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Publication number
EP2843241A2
EP2843241A2 EP14169672.4A EP14169672A EP2843241A2 EP 2843241 A2 EP2843241 A2 EP 2843241A2 EP 14169672 A EP14169672 A EP 14169672A EP 2843241 A2 EP2843241 A2 EP 2843241A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pump
pressure
constant
line
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
EP14169672.4A
Other languages
German (de)
English (en)
Other versions
EP2843241A3 (fr
EP2843241B1 (fr
Inventor
Norbert Strieker
Valtwies Bernd
Christian Besand
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.)
Claas Selbstfahrende Erntemaschinen GmbH
Original Assignee
Claas Selbstfahrende Erntemaschinen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Claas Selbstfahrende Erntemaschinen GmbH filed Critical Claas Selbstfahrende Erntemaschinen GmbH
Publication of EP2843241A2 publication Critical patent/EP2843241A2/fr
Publication of EP2843241A3 publication Critical patent/EP2843241A3/fr
Application granted granted Critical
Publication of EP2843241B1 publication Critical patent/EP2843241B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/275—Control of the prime mover, e.g. hydraulic control
    • 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
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • 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
    • F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
    • 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 according to the preamble of claim 1, a hydraulic system with at least two hydraulic circuits, which are each associated with hydraulic pumps, wherein in the context of a unit, a drive associated with a first hydraulic circuit constant pump is connected exclusively to an output of the second hydraulic circuit associated hydraulic motor and wherein within the first hydraulic circuit hydraulic consumers are arranged.
  • the invention according to the preamble of claim 5 also relates to a hydraulic system with a hydrostatic drive system which is arranged in a closed working group and having a hydraulic pump and at least one hydraulic motor, wherein a displacement volume of the hydraulic pump and / or a displacement of the at least one hydraulic motor are variable , wherein the working group via a feed pipe arranged in a feed pump pressure medium is supplied and wherein a limited to the tank leading purge line is provided to limit a maximum load pressure and to replace the pressure medium located in the closed working circuit.
  • Hydraulic systems may consist of several hydraulic circuits, in which hydraulic circuits different consumers, such as hydraulic motors, actuators, etc. are arranged and these are usually operated with different operating pressures and flow rates.
  • hydraulic circuits can be designed as open or closed circuits.
  • a hydraulic pump sucks liquid from a tank and displaces it into the connected system, from which the liquid returns to the tank.
  • a closed circuit is understood to mean a system which preferably consists of a hydraulic pump and at least one hydraulic motor, the circulation of the hydraulic fluid from the hydraulic pump via the at least one hydraulic motor leading back into the suction port of the hydraulic pump.
  • Hydraulic pumps and hydraulic motors which are also referred to below as hydrostatic machines, can be a constant or have variable delivery volume or displacement and be designed as gear pumps or motors or as axial pumps or motors. In addition, it is possible to use radial piston or vane pumps as hydraulic pumps. If the delivery or displacement volume is constant, the hydrostatic machines are also referred to as a fixed displacement pump or motor.
  • a hydraulic system of the type specified in the preamble of claim 1 is known from DE 10 2009 029 840 A1 known.
  • the first hydraulic circuit is in each case formed as a closed circuit for a hydrostatic drive system in the different design examples.
  • the closed circuit to a hydraulic pump and a hydraulic motor whose displacement or displacement can be changed.
  • a second hydraulic circuit is provided, which is designed as an open circuit and in which promotes a driven by an internal combustion engine variable fluid. The corresponding volume flow is fed to a hydraulic motor arranged downstream of the variable displacement pump, which has a constant displacement volume.
  • An output shaft of this arranged in the second hydraulic circuit hydraulic motor serves as a drive shaft of a constant-displacement pump, which promotes pressure medium in the first hydraulic circuit as a feed pump.
  • This feed is intended to avoid cavitation in the first hydraulic circuit and for subsequent delivery of hydraulic fluid, which escapes due to external leakage from the hydraulic circuit done.
  • a corresponding outgoing from the feed pump feed line leads to the first hydraulic circuit, the corresponding hydraulic fluid via a double check valve.
  • This document describes a hydrostatic drive serving as a traction drive, in the closed working circuit of which essentially a hydraulic pump with an adjustable delivery volume and two hydraulic motors with a constant displacement volume assigned to each wheel drive are provided.
  • the aforementioned adjustable there is a pump designed as a fixed displacement pump, which is driven together with the adjustable hydraulic pump via a drive shaft. From the feed pump goes from a feed line, which can feed via two provided with check valves fluid paths pressure medium in the closed workgroup.
  • pressure relief valves In the area of these fluid paths are also pressure relief valves, via which the pressure in the high-pressure fluid path of the working circuit should be set to 250 bar, for example.
  • Each of these pressure relief valves can thus flow when exceeding this limit value of the pressure pressure medium, which finally derives via a downstream of the feed line provided further pressure relief valve at a pressure of, for example, 30 bar, the pressure medium in the tank.
  • the designed as a constant-speed motor hydraulic motor is integrated into the second hydraulic circuit, being supplied in this hydraulic circuit consumers, such as hydraulic actuators, other hydraulic motors, etc., with the pressure medium from a hydraulic pump.
  • the hydraulic motor is preferably designed as a circulation displacement machine and is driven by the pressure medium flow supplied from the second hydraulic circuit.
  • the fixed displacement pump may cooperate with the first hydraulic circuit by conveying pressure medium into it via a line, or it may be arranged directly in the first hydraulic circuit. From a rotor of the Hydraulic motor is a mechanical drive connection, which leads to a conveying element of the fixed displacement pump.
  • the output power of the hydraulic motor P ab therefore corresponds to the drive power of the constant pump P on .
  • a high pressure occurring in the second hydraulic circuit and a low volume flow can be translated into a low pressure and a high volume flow in the line associated with the first hydraulic circuit.
  • the hydraulic motor and the fixed displacement pump can also be designed so that at a balance, a low pressure and a high volume flow prevail at the inlet of the hydraulic motor, while at the constant pump on the outlet side, a high pressure and a low flow rate can be realized.
  • the pressure p at the output of the constant pump breaks, in which a high volume flow demand occurs in this hydraulic circuit, the constant-displacement pump is driven to increase the pressure from the hydraulic motor until the system is in equilibrium with the aforementioned requirements.
  • the constant pump can be a feed pump for feeding into a closed circuit of a hydrostatic transmission. If necessary, a freewheel can be provided in the mechanical drive connection, which disengages the drive of the constant pump from the output of the constant motor, if in the fixed displacement pump associated with the hydraulic circuit, a relatively large volume flow is promoted, whereas the volume flow is greatly reduced or blocked on the constant motor.
  • variable displacement pump which is adjusted by a pressure control and thus adjusts a delivery volume and pressure in a line leading to the hydraulic motor line section
  • said line section would be considered as a second hydraulic circuit in the context of the present invention.
  • this line section is used exclusively for supplying the constant pump with pressure medium.
  • a corresponding fixed relationship between the hydraulic power of both hydraulic circuits, especially the volume flow with the help the variable displacement pump is varied, not provided.
  • the previously known device relates to a hydrostatic drive of a feed pump and not arranged between different hydraulic circuits pressure booster.
  • the second hydraulic circuit to be provided for a working hydraulics of a self-propelled combine harvester, while the first hydraulic circuit is part of a hydrostatic drive for the conveying and separating elements of a header, such as a Maispflück anatomy, the self-propelled combine harvester.
  • the first hydraulic circuit via which the harvesting attachment is to be driven at different rotational speeds and in different directions of rotation, can be supplied, if required, with pressure medium via the constant-flow pump designed as a feed pump.
  • the corresponding feed line is connected via check valves or pressure relief valves to the first hydraulic circuit, so that if necessary can be fed in each case in the operated at low pressure portion of the first hydraulic circuit.
  • a corresponding reversing operation of the drive of the header is required, for example, in a corn header, so that it can be switched to reverse operation in the normal direction of rotation, if in the field of conveying and processing elements, such as the collection organs and / or the picking rollers and / or an inclined conveyor a blockage has occurred through the crop.
  • the present invention also relates to a hydraulic system with the generic features of claim 5, wherein the object is achieved by the characterizing features of claim 5.
  • the hydraulic system further comprises a hydraulic circuit of a working or low-pressure hydraulics, with which a second hydrostatic machine promotes pressure medium via a line, which may also be designed as a second feed line, in the first feed line and / or in the working or low-pressure hydraulics.
  • a drive system of the two hydrostatic machines is designed such that the first and the second hydrostatic machine exclusively drive each other, So no separate drive is available.
  • the unit consisting of the two hydrostatic machines forms a pressure booster.
  • the hydrostatic machines are each operated as a hydraulic motor with a constant displacement or as a hydraulic pump with a constant displacement.
  • this working group is flushed out via the flushing line.
  • a pressure and a volumetric flow are applied to the first hydrostatic machine arranged therein, and the volumetric flow drives the first hydrostatic machine as a hydraulic motor.
  • the second hydrostatic machine which is drivingly connected to the hydraulic motor, conveys pressure medium into the working or low-pressure hydraulic system as a constant-displacement hydraulic pump. This condition occurs when an imbalance between the hydraulic powers of the two hydrostatic machines has occurred.
  • the first hydrostatic machine becomes a hydraulic pump and delivers pressure medium from the tank into the flushing line, wherein the drive via the second hydrostatic machine, the to the hydraulic pump is done.
  • the pressure booster works according to the principle already described in connection with the patent claim 1, according to which a balance of the hydraulic power of both line sections, where the two hydrostatic machines are assigned, is produced via the pressure booster. If the pressure of the hydraulic medium in the purge line and the pressure of the hydraulic medium in the line of the working or low-pressure hydraulics due to the function of the pressure booster, ie its pressure gear ratio, in equilibrium so the whole unit is silent. Normally, by delivering a volume flow by means of the hydraulic pump of the pressure booster in the low-pressure or working circuit, a portion of the energy of the over the purge line be removed recovered pressure medium. Only a small part is converted into heat due to the losses of the pressure booster unit.
  • the closed hydraulic circuit to be operated depending on the load conditions with a low pressure section and a high pressure section, wherein the low pressure section via a hydraulically pilot operated 3/3-way valve with the purge line is connectable. Via this directional control valve, a certain quantity of pressure medium is thus diverted into the purge line as a function of the pressure of the closed hydraulic circuit, whereby this pressure medium passes into the pressure booster.
  • the second feed line can open into the first feed line. It is possible, via the feed pump pressure medium, which is supported in an advantageous manner by the pressure intensifier according to the invention, to promote the working or low-pressure hydraulics. Alternatively, it is possible to supply the low-pressure hydraulics via the feed pump, while pressure medium is fed into the working hydraulics via a separate circuit into which the pressure intensifier can feed. In addition, there are a variety of ways to use the pressure fluid provided by the pressure booster in a hydraulic system.
  • FIG. 1 1 denotes a first hydraulic circuit provided for a hydrostatic drive system.
  • the first hydraulic circuit 1 has a hydraulic pump 2, whose displacement volume is variable via an adjusting element 3.
  • the actuator 3 may be part of a power control.
  • the hydraulic pump 2 should be adjustable so that change the flow direction by adjusting the displacement and at a certain pivot angle of the conveying elements, not shown, the flow direction.
  • the pump lines 4 and 5 lead to a hydraulic motor 6, which is provided for example for driving a harvesting attachment, not shown, a self-propelled harvester.
  • This harvesting attachment may be a corn picking device, which has, among other things, conveying elements and picking rollers driven by the hydraulic motor 6.
  • an inclined conveyor of the harvester can be driven by the hydraulic motor.
  • the hydraulic motor 6 has a constant displacement in the present case. Of course, it is also possible to make the hydraulic motor 6 adjustable, that is to change its displacement by means of the aforementioned power control.
  • the first hydraulic circuit 1 which is designed as a closed circuit, several hydraulic motors can be arranged. In this case, the individual hydraulic motors can be used for example as wheel motors for a drive of a working machine.
  • the first hydraulic circuit 1 can also be assigned to a power-split epicyclic gearbox, with the actuating power flowing via the hydrostatic branch.
  • a second hydraulic circuit 7 which is designed as an open circuit.
  • a hydraulic pump 8 delivers from a tank 9 liquid via a pressure line 10 to a plurality of hydraulic consumers 11. From these, the pressure medium passes through line sections 12 and 13 back into the tank 9.
  • a pressure booster 14 assembly is provided, the a arranged between the line sections 12 and 13 constant motor 15 and a fixed displacement pump 16 is.
  • a drive of the constant displacement pump 16 takes place exclusively via the constant-speed motor 15, for which purpose the corresponding rotors of constant-motor 15 and constant-displacement pump 16 are coupled to one another via a mechanical drive connection 17. It may be a direct drive or a mechanical drive connection 17 with components for speed ratio.
  • the constant displacement pump 16 delivers hydraulic fluid from the tank 9 into a feed line 18, from which the pressure medium can be conveyed via check valves 19 and 20 into the first hydraulic circuit 1.
  • pressure booster 14 ensures that between the line sections 12 and 13 on the one hand and the feed line 18 on the other hand, an equilibrium can be established. If the equilibrium exists, ie there is no volume flow requirement in the feed line 18, the rotors of the pressure booster 14 stand still. However, if pressure medium to be promoted via the feed line 18, so a volume flow demand is present, the constant displacement pump 16 is driven until no increase in the volume flow is required.
  • FIG. 2 the arrangement of a pressure booster 19 in a first hydraulic circuit 21 and a second hydraulic circuit 20 is shown in detail.
  • a first hydrostatic machine 23 is arranged, while within the second hydraulic circuit 20, a second hydrostatic machine 22 is located.
  • the two hydrostatic machines 22 and 23 are designed such that they can be operated in each case as a pump or as a motor and their current direction is reversed.
  • a hydraulic fluid in the second hydraulic circuit 20 flows through a consumer 24 or a directional valve associated therewith, it passes through the second hydrostatic machine 22, which operates in this case as a hydraulic motor and enters a tank 25.
  • the first hydrostatic machine 23 acts as a constant pump and delivers pressure fluid from another tank 26 to a consumer 27.
  • the first hydrostatic machine 23 as a hydraulic motor from that of Consumers driven 27 outflowing pressure medium and continues to drive the second hydrostatic machine 22, which then acts as a pump to.
  • FIGS. 3 and 4 each show a use of an inventively designed pressure booster in a hydraulic system having a working group for a hydrostatic drive system.
  • the corresponding working group 28 in this case has a hydraulic pump 29 whose delivery volume is variable.
  • the hydraulic pump 29 is designed such that it can convey in different directions, so that can be achieved with the hydrostatic drive system, a reversal of direction.
  • a hydraulic motor 30 is arranged in the trained as a closed circuit working group 28, the displacement of which is variable. Due to the change in the conveying direction of the hydraulic pump 29 and possibly due to a thrust operation occurring from the wheel drive system of a vehicle, the two branches 31 and 32 of the working group 28 can be operated either as a high-pressure or as a low-pressure line. Between these branches 31 and 32 pressure relief valves 33 and 34 are arranged.
  • a feed pump 35 is driven, sucks the pressure medium from a tank 36 and feeds with a feed pressure of for example 20 to 30 bar via a feed line in each case in the low-pressure branch of the working group 28. This is done via check valves 38 and 39.
  • each of the two branches 31 and 32 of the working group 28 is connected to a hydraulically piloted 3/3-way valve 40, which promotes in its two working positions in each case from one of the branches 31 or 32 pressure medium in a flushing line 41.
  • This purge line 41 is associated with a pressure booster 42, which consists of a first hydrostatic machine 43 and a second hydrostatic machine 44.
  • the pressure booster 42 corresponds in terms of its structure and its operation in connection with the FIG. 2 explained pressure booster 19, that is, the two hydrostatic machines 43 and 44 can be operated with different directions of flow and operate as a fixed displacement pump or a constant motor.
  • FIG. 3 After FIG. 3 is the second hydrostatic machine 44 via a line 45 with a hydraulic circuit 46 in communication, which is designed as an open circuit.
  • the hydraulic circuit 46 has a variable displacement pump 47, the pressure medium from the tank 36th aspirates and feeds consumers 47 and 48. It is a working hydraulics, such as a self-propelled harvester.
  • the feed line 37 which starts from the feed pump 35, also leads to a low-pressure hydraulic 49th
  • the first hydraulic machine 43 operates primarily as a constant motor in the purge line 41
  • the second hydrostatic machine 44 is driven as a fixed displacement pump, which promotes pressure fluid from the tank 36 in the hydraulic circuit 46. This always happens when, via the 3/3-way valve, part of the pressure fluid volume, which is again replaced by the feed pump 35, flows out via the purge line 41.
  • the two hydrostatic machines 43 and 44 change their function and thus current direction. This is the case, for example, when a value of the pressure falls below the purge line 41 and a pressure in the line 45 is exceeded.
  • the second hydrostatic machine 44 to the motor and the first hydrostatic machine 43 to the constant pump the pressure medium via the purge line 41 to the 3/3-way valve promotes and this can thus supply the working group 28.
  • the pilot control of the 3/3-way valve must be designed accordingly.
  • this branch forms a second hydraulic circuit 53, which is designed as an open circuit.
  • a second feed line 52 to the first feed line 37, so that increased by this part of the pressure booster 42 in certain working conditions, the volume flow through the feed line 37 in the direction of feeding into the working circuit 28 and the low-pressure hydraulic 50 and the working hydraulics 51 becomes.
  • the volume flows in the purge line 41 and in the second feed line 52 may change such that the two hydrostatic machines 43 and 44 change their function and current direction.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP14169672.4A 2013-08-15 2014-05-23 Système hydraulique Active EP2843241B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013108843.0A DE102013108843A1 (de) 2013-08-15 2013-08-15 Hydrauliksystem

Publications (3)

Publication Number Publication Date
EP2843241A2 true EP2843241A2 (fr) 2015-03-04
EP2843241A3 EP2843241A3 (fr) 2015-04-29
EP2843241B1 EP2843241B1 (fr) 2018-07-11

Family

ID=50792376

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14169672.4A Active EP2843241B1 (fr) 2013-08-15 2014-05-23 Système hydraulique

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EP (1) EP2843241B1 (fr)
DE (1) DE102013108843A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3067571A1 (fr) * 2015-03-10 2016-09-14 HYDAC Service GmbH Dispositif d'alimentation

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015210350A1 (de) * 2015-06-05 2016-12-08 Robert Bosch Gmbh Hydraulische Schaltung zur Druckmittelversrgung eines hydraulischen Verbrauchers in einem geschlossenen hydraulischen Kreis
CN113389764B (zh) * 2021-06-30 2022-11-15 四川航天烽火伺服控制技术有限公司 一种液压设备及其涡轮泵出口压力控制系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029840A1 (de) 2009-06-22 2011-01-27 Liebherr-Werk Nenzing Gmbh Hydrauliksystem
DE102010045857A1 (de) 2010-09-17 2012-03-22 Robert Bosch Gmbh Hydrostatischer Fahrantrieb

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Publication number Priority date Publication date Assignee Title
FR2259256B1 (fr) * 1974-01-24 1977-06-10 Yumbo
FR2437512A1 (fr) * 1978-09-28 1980-04-25 Ppm Sa Dispositif d'alimentation en fluide sous pression comprenant un joint tournant
DE3202351A1 (de) * 1982-01-26 1983-07-28 Robert Bosch Gmbh, 7000 Stuttgart Hydraulikanlage
US5878569A (en) * 1996-10-21 1999-03-09 Caterpillar Inc. Energy conversion system
GB0005178D0 (en) * 2000-03-06 2000-04-26 Ford New Holland Nv Feeder controls for a forage harvester

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
DE102009029840A1 (de) 2009-06-22 2011-01-27 Liebherr-Werk Nenzing Gmbh Hydrauliksystem
DE102010045857A1 (de) 2010-09-17 2012-03-22 Robert Bosch Gmbh Hydrostatischer Fahrantrieb

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3067571A1 (fr) * 2015-03-10 2016-09-14 HYDAC Service GmbH Dispositif d'alimentation

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Publication number Publication date
EP2843241A3 (fr) 2015-04-29
EP2843241B1 (fr) 2018-07-11
DE102013108843A1 (de) 2015-02-19

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