EP3462028A1 - Syst?me hydraulique - Google Patents

Syst?me hydraulique Download PDF

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Publication number
EP3462028A1
EP3462028A1 EP18197332.2A EP18197332A EP3462028A1 EP 3462028 A1 EP3462028 A1 EP 3462028A1 EP 18197332 A EP18197332 A EP 18197332A EP 3462028 A1 EP3462028 A1 EP 3462028A1
Authority
EP
European Patent Office
Prior art keywords
pump
hydraulic
unit
valve unit
arrangement according
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
EP18197332.2A
Other languages
German (de)
English (en)
Other versions
EP3462028B1 (fr
Inventor
Michael Meid
Sebastian TRAUT
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP3462028A1 publication Critical patent/EP3462028A1/fr
Application granted granted Critical
Publication of EP3462028B1 publication Critical patent/EP3462028B1/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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • 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
    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/05—Pressure after the pump outlet
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/09—Flow through the pump

Definitions

  • the invention relates to a hydraulic arrangement with a pump for conveying a hydraulic medium in the direction of a hydraulic workload.
  • the pump of such a hydraulic arrangement usually delivers the hydraulic medium with discrete displacement volume. This can lead to volume flow and thus also to pressure pulsations, which are effectively reduced or avoided by a storage unit connected to the pump.
  • the storage unit may affect the hydraulic behavior of the assembly.
  • the hydraulic arrangement includes a pump for conveying a hydraulic medium (eg oil) in the direction of a hydraulic workload, which acts as a hydraulic consumer.
  • the pump is adjustable by means of an adjustment input, so that they can always provide an adapted flow rate or an adapted flow rate. As a result, the pump can work with respect to the hydraulic medium of a full funding up to a zero promotion.
  • the hydraulic arrangement contains a storage unit (eg diaphragm accumulator), which is hydraulically connected to the pump on the output side. This storage unit reduces any pressure pulsations and associated burdens of Components as well as disturbing noises of the hydraulic arrangement.
  • the hydraulic arrangement has a loading valve unit for loading and unloading the storage unit.
  • the charging valve unit is hydraulically connected at the pump on the output side between the pump and the storage unit and acts with their different switching states as a separable hydraulic connection between the pump and the storage unit.
  • the charging valve unit is bridged by means of a non-return valve which is permeable in the direction of the pump, wherein the non-return valve can be structurally integrated into the charging valve unit.
  • the check valve is closed.
  • Such a charging valve unit provides a technically simple and inexpensive condition for the hydraulic arrangement to exhibit a response at different operating ranges of the pump which is substantially independent of changes in the delivery flow. Any acoustic and / or mechanical vibrations in the hydraulic arrangement or in the hydraulic system are reduced or completely avoided, since a continuous filling and emptying of the storage unit can be actively damped by the charging valve unit.
  • the hydraulic arrangement is used in mobile hydraulics, such as in agricultural machines, construction machines or road construction vehicles.
  • the hydraulic workload is preferably contained in one of the aforementioned mobile machines or one of the aforementioned vehicles.
  • the hydraulic workload can be designed, for example, as a steering or braking unit, hydraulic motor, power lift cylinder be or be used in an attachment for one of the aforementioned machines or vehicles.
  • the loading valve unit has at least two, in particular exactly two different switching positions.
  • the loading valve unit is closed at a maximum delivery flow (full delivery) of the pump, while at a lower flow rate, i. below the maximum flow, is opened.
  • a hydraulic connection between the pump and the storage unit at a delivery flow below the maximum delivery flow.
  • the memory unit then fulfills the desired function for reducing pressure pulsations or for pulsation damping.
  • the pump In the case of a specific delivery flow or pressure requirement of the hydraulic system, the pump is adjusted in particular to full delivery. The loader unit then disconnects the storage unit from the hydraulic system, thereby preventing the storage unit from being filled. This leads to changes in the flow advantageous to a response of the hydraulic system without a memory unit, so that otherwise caused by a memory unit disadvantages such as reduced stiffness or vibration excitations in the hydraulic system can be avoided.
  • the storage unit may also reduce pressure drop due to abrupt volumetric flow or pressure requirements, especially when the loader unit is bridged by means of a non-return valve that is permeable to the pump.
  • the charging valve unit is technically simple in that it is closed in a pressureless state of a hydraulic control input and is open at a pressurized state of the control input with hydraulic pressure.
  • the charging unit can then be opened by means of a so-called pilot pressure at the control input.
  • the loader unit has a conventional spring side (e.g., return spring) while the aforesaid control input is located relative to the spring side on an opposite opposite side of the loader unit.
  • the charging valve unit is formed as a discrete or proportional 2/2-way valve with two ports and two switching positions and can thereby be provided inexpensively as a standard component. Notwithstanding, the directional control valve can also have an exceeding number of switching positions.
  • its adjustment input is preferably connected hydraulically to a regulator output of a hydraulic control unit.
  • control input of the charging valve unit is hydraulically connected to the same controller output to which the adjustment input of the pump is hydraulically connected.
  • control unit includes a hydraulic volume flow controller and / or a hydraulic pressure regulator.
  • the hydraulic system can request a hydraulic volume flow or pressure. This requirement is implemented in the pump by adjusting the flow rate, in particular by full promotion.
  • the volume flow regulator and / or the pressure regulator is preferably designed as a directional control valve, for example a 3/2-way valve.
  • its adjusting input preferably has a restoring element (for example return piston) which can be acted upon by hydraulic pressure.
  • a restoring element for example return piston
  • This adjustment pressure can be controlled by the control unit such that the pump provides the adjusted flow rate.
  • the pump can be adjusted by lowering the adjustment pressure in the direction of full delivery or by increasing the adjustment pressure in the direction of zero delivery.
  • Fig. 1 shows a hydraulic assembly 10 or hydraulic system with a pump 12 for conveying a hydraulic medium (eg oil) in the direction of a hydraulic workload 14.
  • a hydraulic medium eg oil
  • the pump 12 is connected to a suction line 16 to a Hydraulic medium containing hydraulic tank 18 and sump connected.
  • the pump 12 has an adjustment input to adjust a hydraulic flow.
  • the adjustment 20 has a return element 22 in the form of a return piston not shown in detail here.
  • This return element 22 is acted upon at a delivery flow below a full delivery with an adjustment pressure p_V.
  • the adjustment pressure p_V is controlled by a hydraulic volume flow controller 24 and a hydraulic pressure regulator 26 within a control unit 28 such that the pump 12 provides a correspondingly sized flow rate.
  • the pump 12 is adjusted by lowering the adjustment pressure towards full delivery or by increasing the adjustment pressure in the direction of zero promotion.
  • a storage unit 30 is hydraulically connected to the pump 12 on the output side. Between a pump outlet 32 of the pump 12 and a storage port 34 of the storage unit 30, a charging valve unit 36 is hydraulically connected.
  • the charging valve unit 36 is formed as a 2/2-way valve with two ports and two switching positions. By means of the loading valve unit 36, a separable hydraulic connection between the pump 12 and the storage unit 30 is made.
  • the charging valve unit 36 is bridged by means of a permeable in the direction of the pump 12 check valve, the check valve is structurally integrated into the charging valve unit 36.
  • the charging valve unit 36 is closed in the pressureless state of a hydraulic control input 38 and is opened at a pressure state of the control input 38 applied with hydraulic pressure (pilot pressure) p.
  • the control input 38 and the adjustment input 22 are hydraulically connected to a regulator output 40 of the control unit 28.
  • the return element 22 is always acted upon by a specific adjustment pressure p_V and thus limits the flow rate. Consequently, the control input 38 is acted upon by a specific pressure p and the charging valve unit 36 is opened accordingly.
  • the memory unit 30 fulfills the desired function of pulsation damping.
  • the pump 12 is adjusted by discharging the adjustment pressure p_V at the control input 20 to a full delivery (maximum flow).
  • the control input 38 is in a depressurized state and the charging valve unit 36 is accordingly closed.
  • the loading valve unit 36 separates the storage unit 30 from the hydraulic system, thereby preventing the storage unit 30 from being filled. This leads to a response of the hydraulic arrangement or the hydraulic system, which is comparable to a hydraulic system without such a memory unit 30. A negative reaction of the storage unit 30 to the hydraulic system can thus be excluded.
  • the hydraulic arrangement 10 also contains individual damping orifices 42 and 44, which are arranged hydraulically one behind the other between the control output 40 and the hydraulic reservoir 18.
  • the volume flow controller 24 and the pressure regulator 26 are each formed as a 3/2-way valve.
  • a so-called orifice plate 46 is hydraulically connected, at which the control pressure difference of the volume flow controller 24 drops.
  • the metering orifice 46 is so far a simplified control unit.
  • several such control units can be connected in parallel with corresponding workloads or consumers.
  • the metering orifice 46 or the control unit formed by these can be supplemented with a pressure compensator in order to keep the volume flow constant by adapting the control pressure difference applied to the metering orifice 46.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
EP18197332.2A 2017-10-02 2018-09-27 Dispositif hydraulique Active EP3462028B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017217552.4A DE102017217552A1 (de) 2017-10-02 2017-10-02 Hydraulische Anordnung

Publications (2)

Publication Number Publication Date
EP3462028A1 true EP3462028A1 (fr) 2019-04-03
EP3462028B1 EP3462028B1 (fr) 2021-09-15

Family

ID=63708149

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18197332.2A Active EP3462028B1 (fr) 2017-10-02 2018-09-27 Dispositif hydraulique

Country Status (3)

Country Link
US (1) US10731670B2 (fr)
EP (1) EP3462028B1 (fr)
DE (1) DE102017217552A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202007014676U1 (de) * 2007-10-19 2009-02-26 Liebherr-Machines Bulle S.A. Hydraulisches Antriebssystem
WO2011038706A1 (fr) * 2009-09-29 2011-04-07 Schaeffler Technologies Gmbh & Co. Kg Commande hydraulique
DE102010053258A1 (de) * 2009-12-14 2011-06-16 Schaeffler Technologies Gmbh & Co. Kg Hydraulikanordnung
DE102010014071A1 (de) * 2010-04-07 2011-10-13 Hydac Filtertechnik Gmbh Hydraulische Anlage
EP2420626A1 (fr) * 2010-08-19 2012-02-22 Deere & Company Agencement hydraulique
DE102013211986A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Verfahren zum Ermitteln eines Füllstands
DE102014107240A1 (de) * 2014-05-22 2015-11-26 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Hybridantriebseinrichtung für einen hybriden Antriebsstrang
DE102015206403A1 (de) * 2015-04-10 2016-10-13 Robert Bosch Gmbh Hydraulische Anordnung und Verfahren zur Leckagemessung für eine hydraulische Anordnung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5138135B2 (fr) * 1971-09-17 1976-10-20
US4523430A (en) * 1981-03-19 1985-06-18 Daikin Kogyo Co., Ltd. Fluid flow control system
JP2964607B2 (ja) * 1990-10-11 1999-10-18 日産自動車株式会社 油圧供給装置
US6973781B2 (en) * 2003-10-29 2005-12-13 Zf Friedrichshafen Ag Method and apparatus for maintaining hydraulic pressure when a vehicle is stopped
DE102006046127A1 (de) * 2006-09-28 2008-04-03 Robert Bosch Gmbh Energiespeichereinheit
DE102006050873A1 (de) * 2006-10-27 2008-04-30 Robert Bosch Gmbh Hydrostatischer Antrieb mit Bremsenergierückgewinnung
DE102014215567A1 (de) * 2014-08-06 2016-02-11 Robert Bosch Gmbh Hydrostatischer Antrieb

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202007014676U1 (de) * 2007-10-19 2009-02-26 Liebherr-Machines Bulle S.A. Hydraulisches Antriebssystem
WO2011038706A1 (fr) * 2009-09-29 2011-04-07 Schaeffler Technologies Gmbh & Co. Kg Commande hydraulique
DE102010053258A1 (de) * 2009-12-14 2011-06-16 Schaeffler Technologies Gmbh & Co. Kg Hydraulikanordnung
DE102010014071A1 (de) * 2010-04-07 2011-10-13 Hydac Filtertechnik Gmbh Hydraulische Anlage
EP2420626A1 (fr) * 2010-08-19 2012-02-22 Deere & Company Agencement hydraulique
DE102013211986A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Verfahren zum Ermitteln eines Füllstands
DE102014107240A1 (de) * 2014-05-22 2015-11-26 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Hybridantriebseinrichtung für einen hybriden Antriebsstrang
DE102015206403A1 (de) * 2015-04-10 2016-10-13 Robert Bosch Gmbh Hydraulische Anordnung und Verfahren zur Leckagemessung für eine hydraulische Anordnung

Also Published As

Publication number Publication date
EP3462028B1 (fr) 2021-09-15
DE102017217552A1 (de) 2019-04-04
US10731670B2 (en) 2020-08-04
US20190101136A1 (en) 2019-04-04

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