EP3462028B1 - Dispositif hydraulique - Google Patents

Dispositif hydraulique Download PDF

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Publication number
EP3462028B1
EP3462028B1 EP18197332.2A EP18197332A EP3462028B1 EP 3462028 B1 EP3462028 B1 EP 3462028B1 EP 18197332 A EP18197332 A EP 18197332A EP 3462028 B1 EP3462028 B1 EP 3462028B1
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EP
European Patent Office
Prior art keywords
hydraulic
pump
unit
valve unit
pressure
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.)
Active
Application number
EP18197332.2A
Other languages
German (de)
English (en)
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EP3462028A1 (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
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Deere and Co
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Filing date
Publication date
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Publication of EP3462028A1 publication Critical patent/EP3462028A1/fr
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Publication of EP3462028B1 publication Critical patent/EP3462028B1/fr
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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
    • F04B49/06—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
    • F04B49/002—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
    • F04B49/08—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 pamphlet EP 2 420 626 A1 shows a hydraulic arrangement in which hydraulic fluid is conveyed from a tank via a hydraulic pump and via a priority control valve to a hydraulic workload in the form of a hydraulic steering device. At the same time, hydraulic fluid is fed into a hydraulic accumulator via a second hydraulic line equipped with a diaphragm, which is loaded with hydraulic fluid parallel to the supply of the hydraulic steering device.
  • the pump of such a hydraulic arrangement conveys the hydraulic medium as a rule with a 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 can, however, influence the hydraulic behavior of the arrangement.
  • the hydraulic arrangement contains a pump for conveying a hydraulic medium (for example oil) in the direction of a hydraulic work load, which acts as a hydraulic consumer.
  • the pump can be adjusted by means of an adjustment input so that it can always provide an adapted flow rate or an adapted flow rate. As a result, the pump can work from full delivery to zero delivery with respect to the hydraulic medium.
  • the hydraulic arrangement also contains a storage unit (for example a diaphragm storage tank) which is hydraulically connected to the pump on the output side. This storage unit reduces any pressure pulsations and the associated loads 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 loading valve unit is hydraulically connected to the pump on the output side between the pump and the storage unit and, with its different switching states, acts as a separable hydraulic connection between the pump and the storage unit. It is possible here for the loading valve unit to be bridged by means of a check valve which is permeable in the direction of the pump, it being possible for the check valve to be structurally integrated into the loading valve unit. The check valve is closed in the direction of the storage unit.
  • Such a loading valve unit creates a technically simple and inexpensive prerequisite for the hydraulic arrangement to show a response behavior in different operating ranges of the pump which is essentially 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 continuous filling and emptying of the storage unit can be actively dampened by the loading valve unit.
  • the hydraulic arrangement is used in a mobile hydraulic system, such as, for example, in agricultural work machines, construction machines or road construction vehicles.
  • the hydraulic workload is accordingly preferably contained in one of the aforementioned mobile machines or one of the aforementioned vehicles.
  • the hydraulic work load can be designed as a steering or braking unit, hydraulic motor, power lift cylinder, for example 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 flow rate (full flow rate) of the pump, while it is open at a lower flow rate, i.e. below the maximum flow rate.
  • the memory unit then fulfills the desired function for reducing pressure pulsations or for pulsation damping.
  • the pump In the event of a specific delivery flow or pressure requirement from the hydraulic system, the pump is adjusted to full delivery in particular.
  • the loading valve unit then separates the storage unit from the hydraulic system and thereby prevents the storage unit from being filled. In the event of changes in the delivery flow, this advantageously leads to a response behavior of the hydraulic system without a storage unit, so that disadvantages otherwise caused by a storage unit, such as reduced rigidity or excitation of vibrations in the hydraulic system, are avoided.
  • the storage unit can also reduce a pressure drop due to abrupt volume flow or pressure requirements, in particular when the loading valve unit is bridged by means of a check valve that is permeable in the direction of the pump.
  • the loading valve unit is preferably designed in a technically simple manner in that it is closed when a hydraulic control input is depressurized and is open when the control input is pressurized with hydraulic pressure. The loading valve unit can then be opened by means of a so-called pilot pressure at the control input.
  • the loading valve unit preferably has a conventional spring side (e.g. return spring), while the aforementioned control input is arranged on an opposite side of the loading valve unit relative to the spring side.
  • the loading valve unit is designed as a discrete or proportional 2/2-way valve with two connections and two switching positions and can thus be provided as a standard component at low cost. Notwithstanding, the directional control valve can also have an additional number of switching positions.
  • its adjustment input is preferably hydraulically connected to a controller output of a hydraulic control unit.
  • control input of the loading valve unit is hydraulically connected to the same controller output with which the adjustment input of the pump is hydraulically connected.
  • control unit contains a hydraulic volume flow controller and / or a hydraulic pressure controller.
  • the hydraulic system can use this controller to request a hydraulic volume flow or pressure. This requirement is implemented in the pump by adjusting the flow rate, in particular by full delivery.
  • the volume flow regulator and / or the pressure regulator is preferably designed as a directional valve, for example a 3/2-way valve.
  • its adjustment input preferably has a return element (e.g. return piston) that can be acted upon by hydraulic pressure. If the flow rate is limited below the full flow rate, an adjustment pressure is applied to this.
  • This adjustment pressure can be regulated by the control unit in such a way that the pump provides the adapted delivery flow. In the event of a volume flow or pressure requirement from the hydraulic system, the pump can be adjusted in the direction of full delivery by releasing the adjustment pressure or in the direction of zero delivery by increasing the adjustment pressure.
  • Fig. 1 shows a hydraulic arrangement 10 or hydraulic system with a pump 12 for conveying a hydraulic medium (for example oil) in the direction of a hydraulic work load 14.
  • a hydraulic medium for example oil
  • the pump 12 is connected to a suction line 16 with a Hydraulic medium containing hydraulic tank 18 or sump connected.
  • the pump 12 has an adjustment input in order to adjust a hydraulic delivery flow.
  • the adjustment input 20 has a restoring element 22 in the form of a restoring piston not shown in detail here.
  • This restoring element 22 is acted upon by an adjustment pressure p_V when the delivery flow is below full delivery.
  • the adjustment pressure p_V is regulated by a hydraulic volume flow controller 24 and a hydraulic pressure controller 26 within a control unit 28 in such a way that the pump 12 provides a correspondingly dimensioned delivery flow.
  • the pump 12 is adjusted in the direction of full delivery by releasing the adjustment pressure or in the direction of zero delivery by increasing the adjustment pressure.
  • a storage unit 30 is hydraulically connected to the pump 12 on the output side.
  • a loading valve unit 36 is hydraulically connected between a pump outlet 32 of the pump 12 and a storage connection 34 of the storage unit 30.
  • the loading valve unit 36 is designed as a 2/2-way valve with two connections and two switching positions.
  • a separable hydraulic connection between the pump 12 and the storage unit 30 is established by means of the loading valve unit 36.
  • the loading valve unit 36 is bridged by means of a check valve which is permeable in the direction of the pump 12, the check valve being structurally integrated into the loading valve unit 36.
  • the loading valve unit 36 is closed when a hydraulic control input 38 is depressurized and is opened when the control input 38 is pressurized with hydraulic pressure (pilot pressure) p.
  • the control input 38 and the adjustment input 22 are hydraulically connected to a controller output 40 of the control unit 28.
  • this results in an advantageous response behavior of the hydraulic arrangement 10 or the hydraulic system.
  • the pump 12 which is critical in terms of acoustics and vibrations, the latter is set to a flow rate below the full flow.
  • the restoring element 22 is always acted upon with a specific adjustment pressure p_V and thus limits the delivery flow. Consequently, the control input 38 is also subjected to a specific pressure p and the loading valve unit 36 is opened accordingly.
  • the memory unit 30 thus fulfills the desired function of damping pulsations.
  • the pump 12 is adjusted to full delivery (maximum delivery flow) by releasing the adjusting pressure p_V at the control input 20.
  • the control input 38 is in a pressureless state and the loading valve unit 36 is accordingly closed. Consequently, the loading valve unit 36 separates the storage unit 30 from the hydraulic system and thereby prevents the storage unit 30 from being filled.
  • the hydraulic arrangement 10 also contains individual damping diaphragms 42 and 44, which are arranged hydraulically one behind the other between the regulator outlet 40 and the hydraulic tank 18.
  • the volume flow regulator 24 and the pressure regulator 26 are each designed as a 3/2-way valve.
  • a so-called measuring orifice 46 is hydraulically connected between the pump outlet 32 and the workload 14, at which the control pressure difference of the volume flow controller 24 drops.
  • the volume flow can be varied by adjusting the measuring orifice 46.
  • the volume flow is thus independent of the workload 14.
  • the measuring orifice 46 represents a simplified control device in this respect.
  • several such control devices with corresponding workloads or consumers can be connected in parallel to the pump outlet 32.
  • the measuring orifice 46 or the control device formed by it can be supplemented with a pressure compensator in order to keep the volume flow constant by adapting the control pressure difference applied to the measuring orifice 46.

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  • 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)

Claims (8)

  1. Agencement hydraulique, comprenant
    - une pompe (12) pour débiter un fluide hydraulique en direction d'une charge de travail hydraulique (14), la pompe (12) présentant une entrée de réglage (20) pour régler un courant de débit de la pompe (12),
    - une unité de stockage (30) raccordée hydrauliquement côté sortie à la pompe (12), et
    - une unité de vanne de charge (36) qui est raccordée hydrauliquement à la pompe (12) côté sortie entre la pompe (12) et l'unité de stockage (30) et agit comme une liaison hydraulique séparable entre la pompe (12) et l'unité de stockage (30),
    caractérisé en ce que l'unité de vanne de charge (36) présente exactement deux positions de commutation différentes, l'unité de vanne de charge (36) étant fermée en cas de courant de débit maximal de la pompe (12), alors que l'unité de vanne de charge (36) est ouverte en cas de courant de débit plus faible, inférieur au courant de débit maximal.
  2. Agencement selon la revendication 1, caractérisé en ce que l'unité de vanne de charge (36) est pontée au moyen d'un clapet antiretour perméable en direction de la pompe (12).
  3. Agencement selon au moins l'une des revendications précédentes, caractérisé en ce que l'unité de vanne de charge (36)
    - est ouverte dans un état de pression mis sous une pression hydraulique (p) d'une entrée de commande hydraulique (38), et
    - est fermée dans un état sans pression de l'entrée de commande (38).
  4. Agencement selon au moins l'une des revendications précédentes, caractérisé en ce que l'unité de vanne de charge (36) est réalisée sous la forme d'un distributeur à 2/2 voies.
  5. Agencement selon au moins l'une des revendications précédentes, caractérisé en ce qu'il présente une unité de régulation hydraulique (28) qui est raccordée hydrauliquement par une sortie de régulateur (40) à l'entrée de réglage (20) de la pompe (12).
  6. Agencement selon la revendication 5, caractérisé en ce que l'entrée de commande (38) de l'unité de vanne de charge (36) est raccordée hydrauliquement à la sortie de régulateur (40) de l'unité de régulation (28).
  7. Agencement selon la revendication 5 ou 6, caractérisé en ce que l'unité de régulation (28) présente un régulateur de débit volumique hydraulique (24) et/ou un régulateur de pression hydraulique (26).
  8. Agencement selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entrée de réglage (20) de la pompe (12) présente un élément de rappel (22) pouvant être mis sous pression par une pression hydraulique (p_V).
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 EP3462028A1 (fr) 2019-04-03
EP3462028B1 true EP3462028B1 (fr) 2021-09-15

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EP18197332.2A Active EP3462028B1 (fr) 2017-10-02 2018-09-27 Dispositif hydraulique

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

Family Cites Families (15)

* 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
DE202007014676U1 (de) * 2007-10-19 2009-02-26 Liebherr-Machines Bulle S.A. Hydraulisches Antriebssystem
DE102010036166A1 (de) 2009-09-29 2011-03-31 Schaeffler Technologies Gmbh & Co. Kg Hydraulische Steuerung
WO2011072639A1 (fr) * 2009-12-14 2011-06-23 Schaeffler Technologies Gmbh & Co. Kg Système hydraulique
DE102010014071B4 (de) * 2010-04-07 2012-12-06 Hydac Filtertechnik Gmbh Hydraulische Anlage
DE102010039509A1 (de) * 2010-08-19 2012-02-23 Deere & Company Hydraulische Anordnung
DE102013211986A1 (de) 2013-06-25 2015-01-08 Robert Bosch Gmbh Verfahren zum Ermitteln eines Füllstands
DE102014107240B4 (de) * 2014-05-22 2024-08-08 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Hybridantriebseinrichtung für einen hybriden Antriebsstrang
DE102014215567A1 (de) * 2014-08-06 2016-02-11 Robert Bosch Gmbh Hydrostatischer Antrieb
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
EP3462028A1 (fr) 2019-04-03
US20190101136A1 (en) 2019-04-04
DE102017217552A1 (de) 2019-04-04
US10731670B2 (en) 2020-08-04

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