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EP2513491B1 - Systeme de vanne pour commander un consommateur - Google Patents

Systeme de vanne pour commander un consommateur Download PDF

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Publication number
EP2513491B1
EP2513491B1 EP10784445.8A EP10784445A EP2513491B1 EP 2513491 B1 EP2513491 B1 EP 2513491B1 EP 10784445 A EP10784445 A EP 10784445A EP 2513491 B1 EP2513491 B1 EP 2513491B1
Authority
EP
European Patent Office
Prior art keywords
valve
consumer
pressure
brake
valve arrangement
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.)
Not-in-force
Application number
EP10784445.8A
Other languages
German (de)
English (en)
Other versions
EP2513491A1 (fr
Inventor
Winfried Rueb
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.)
Hydac Filtertechnik GmbH
Original Assignee
Hydac Filtertechnik 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 Hydac Filtertechnik GmbH filed Critical Hydac Filtertechnik GmbH
Publication of EP2513491A1 publication Critical patent/EP2513491A1/fr
Application granted granted Critical
Publication of EP2513491B1 publication Critical patent/EP2513491B1/fr
Not-in-force 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control

Definitions

  • the invention relates to a hydraulic valve arrangement for controlling a consumer with an acting as inlet throttle, continuously adjustable directional control valve, via which a pump connection with consumer connections is connected, the consumer is connected via working lines to the directional control valve and a drain volume flow of a pressure medium from the consumer via a throttle device is adjustable in response to a load signal of the consumer, wherein the throttle device is adjustable by a derived from the load signal back pressure.
  • Valve arrangements are used in the mobile hydraulics of working machines, for example, for the control of single or double-acting consumers or of rotating mechanisms, such as hydraulic motors and power lifts.
  • a throttle device in each case leading to the respective consumer working lines a throttle device is knotted, via which the incoming or outgoing hydraulic oil flow rate can be throttled.
  • valve throttle For throttling the pressure medium inlet and the pressure medium outlet a valve throttle are arranged in the working lines, the valve members are mechanically coupled.
  • the ratio of the inlet and outlet openings of the valve throttles is determined by the mechanical coupling of the opening edges of the common valve spool, so that a certain setting of the respective valve throttle a certain pressure loss in the drain line corresponds.
  • This pressure loss is particularly undesirable when connecting single-acting consumers, as it does not represent a useful function.
  • the pressure loss leads to energy losses, to an increase in the pressure medium temperature and possibly to premature wear of the valve throttle.
  • Lowering brake valves prevent not only an uncontrolled slump but also a lack of filling on the inlet side and thus cavitation.
  • the lowering brake valve In a working phase or lifting phase of a working cylinder, the lowering brake valve is bypassed by a check valve.
  • the flow through the check valve causes high pressure losses.
  • a valve assembly of the type described above is made DE 10 2007 020 558 A1 known.
  • the known valve arrangement serves to supply pressure medium to a hydraulic consumer with a directional control valve, which has a pressure measuring medium volume flow predetermining inflow orifice and a directional part.
  • the directional valve is associated with an individual pressure compensator.
  • a lowering brake valve is provided, which is acted upon in the opening direction by a pilot pressure and the opening towards the consumer
  • Check valve is connected in parallel, wherein the pilot pressure is tapped in a channel between the pressure compensator and the directional part.
  • the channel is a bow channel between a pressure compensator outlet and in each case an intermediate chamber of a flow-side or return-side directional part of the directional control valve.
  • both in the flow and in the course of a lowering brake valve can be provided and both acted upon by the same pilot pressure.
  • the known valve arrangement is preferably a directional control valve element of a mobile control block.
  • the invention has for its object to provide a valve assembly for controlling a consumer whose drive signal of a brake valve is decoupled from cylinder pressures or pressures at another consumer, with a high reliability and an improved switching behavior should be guaranteed.
  • a hydraulic valve assembly having the features of claim 1 in its entirety.
  • the throttle device is controlled via a hydraulic circuit, which detects the size and direction of a pressure medium flow to the consumer.
  • a device which detects the size and the direction of the pressure medium flow in the valve arrangement to the consumer. This makes it possible that the dynamic pressure signal for the brake slide, a signal of this device is superimposed for measuring the size and direction of the pressure medium flow.
  • the pertinent device detects, for example, the switching position of the spool of the directional control valve. If the spool is switched back from a switching position corresponding to a working position of the consumer in a neutral position, the brake slide is in a switching position passed through this device, which corresponds to a closed position.
  • the device or the hydraulic circuit which detects the size and direction of the pressure medium flow to the consumer, acts by means of a pressure divider circuit in the process of the brake slide in a closed position such that a derived from the control pressure for the valve assembly, the reduced pressure controls the brake slide.
  • the dynamic pressure signal for the brake slide is superimposed on a displacement of the spool in a switching position corresponding to the open position in terms of a working position of the consumer, by a signal of said device, in the sense that a disproportionately rapid opening position of the Brake slider is taken.
  • the throttle device is set by a derived from a load signal or load-sensing signal back pressure, a constructive measure is taken to prevent Mitkoppelung of pressure increases in the consumer in the drive pressure or the drive signal for the brake valve.
  • the dynamic pressure derived from a load-sensing signal is taken from a metering orifice of the directional spool or control piston of a directional control valve.
  • a pressure compensator of such a directional control valve is able to generate the dynamic pressure correlated with the load signal.
  • the throttle device can be designed as a metering diaphragm, in particular as a variable diaphragm. To a particularly compact To achieve construction of the valve assembly, it may be appropriate to integrate a brake valve of a Senkbremsventils in an existing spool of the directional control valve.
  • a dynamic pressure signal basically represents a physical quantity which is available only outside short-term pressure fluctuations or pressure increases in a hydraulic system; unlike the pressures themselves. It is a filtered signal per se.
  • a standard directional control valve can be inexpensively extended to a directional control valve with load braking function.
  • short control channels are possible and logical switch positions of the spool can be used to control the brake slide.
  • throttle notches of the brake valve only allow a pressure fluid drain when the directional control valve spool is moved from a neutral position.
  • the throttle notches in the interior of the brake valve spool are in fluid-carrying connection with openings of the spool in its inner through hole. The brake slide or brake valve spool can thus be acted upon by dynamic pressure on its two end faces.
  • the valve arrangement according to the invention reduces the pressure loss during operation of a hydraulic consumer in both flow directions of a pressure medium to the consumer. If the consumer presents itself as a single-acting hydraulic cylinder, the pressure loss during lifting is reduced by the fact that no check valve must be overflowed. In addition, the pressure loss decreases when lowering the hydraulic cylinder, since only the pressure in an inlet chamber of the hydraulic cylinder must be considered and a spring force of a return spring for the brake valve can be reduced to about 1/5 of the value according to the prior art.
  • a valve assembly 1 for controlling a hydraulic load 2 is shown in a schematic circuit diagram.
  • the consumer 2 is designed as a double-acting hydraulic cylinder, to whose operation a pressure medium flow is provided by a constant current pump 19.
  • the constant-current pump 19 is driven by an internal combustion engine, not shown, of a working machine, such as a mini-excavator or wheel loader.
  • the hydraulic cylinder is used, for example, for raising and lowering a front working tool or an excavator arm or bucket or the like. It is understood that other fields of application of the valve arrangement 1 are possible, for example in an industrial truck or in known hydraulic hoists.
  • the consumer 2 is a continuously adjustable directional control valve 3, of which in the Fig.1 to 3 only exemplary embodiments are shown, driven.
  • the directional control valve 3 is shown in FIG Fig.1 as 4/3-way valve with two working lines 4.5 connected to the consumer 2 fluid leading. Taking the load-sensing line into consideration, it is a 5/3-way valve.
  • a brake valve 10 is knotted in the working line 5, which opens into a piston-side working space of the hydraulic cylinder.
  • the brake valve 10 is mounted directly on the hydraulic cylinder to represent a pipe rupture function can.
  • a check valve 21 secures the valve assembly 1 in case of any pipe break before loss of pressure medium.
  • the brake valve 10 thus represents one, the drain volume flow 6 of a pressure medium 7 in the consumer 2 very stable controlling throttle device 8.
  • FIG.2 is a schematic longitudinal section of a valve assembly 1 from a directional control valve 3 with an integrated therein according to the invention with a controlled dynamic pressure p 'controlled brake slide 11 shown in the brake valve 10.
  • the valve assembly 1 has a pump or pressure supply port P, a return port R, two load ports A, B and two control ports P ' A and P' B and a load signal or load sensing port LS.
  • the basic function of such a valve arrangement 1 is described in several prior applications by the applicant (for example in US Pat DE 10 2007 054 137.8 A1 ), so that will not be discussed in detail on this issue.
  • the valve assembly 1 has one in its housing in the direction of the Fig.2 seen horizontally displaceable spool 12, which is shown in its neutral position.
  • the spool 12 in turn serves as a housing for the therein also displaceable in the horizontal direction brake slide 11.
  • the spool 12 has in addition to metering 9 ( Figure 4 ) between the control terminals P ' A and P' B and the respective load ports A and B two openings 22 in an inner, longitudinal through hole 23. These openings 22 are in constant communication with throttle notches 24 of the inner brake slide 11.
  • the throttle notches 24 can only then release the drain or fluid carrying connection 13 to the return port R when the spool 12 is moved from the neutral position shown to a working position.
  • an opening 15,15 ' are each provided at the ends 16 of the spool 12, at which end faces 18 of the brake slide 11 with the back pressure p' can be connected.
  • the Figure 3 shows in a schematic circuit diagram of a valve assembly 1 according to the invention, the additional application of a hydraulic circuit 17, which superimposed the back pressure signal for the brake slide 11, a signal which maps the size and direction of a pressure medium flow for the consumer 2.
  • a hydraulic circuit 17 which superimposed the back pressure signal for the brake slide 11, a signal which maps the size and direction of a pressure medium flow for the consumer 2.
  • each of the two control lines 25,26 for the spool 1 such, also known as brake detector with pressure divider circuit to be designated hydraulic circuit 17 is knotted.
  • the hydraulic circuit 17 is the deflection of a non-biased by means of spring elements piston 27, the control pressure for the spool 12 to the brake slide 11 on.
  • Figure 4 shown in detail pressure divider circuit that a comparatively reduced pressure the brake slide 11 i drives.
  • the throttle device 8 or the brake valve 10 are closed disproportionately. This contributes to the dynamics of, for example, the in Figure 3 as a hydraulic motor 28 illustrated consumer 2 and results in a rapid deceleration of the hydraulic motor 28.
  • the circuit according to the Figure 3 further discloses a pressure compensator 29 upstream of the constant displacement pump 19, which can serve for Druckstoffmengenabschneidung to avoid overloading of the hydraulic motor 28.
  • the Figure 4 shows an embodiment of a hydraulic circuit 17 for detecting the size and direction of the pressure medium flow for each consumer, which may be performed twice, approximately at each end face of the spool 12 in the directional control valve housing.
  • the hydraulic circuit 17 is shown in a longitudinal section in a longitudinal center plane of the directional control valve 3, so that not all fluid-carrying connections according to the circuit diagram 3 are shown.
  • the Figure 5 There are linear dependencies in both operating states in the working position (a) and the braking position (b) of the spool 12.
  • In the working position (a) of the control spool 12 is a direct given proportional ratio of said pressures, while in the braking position or throttle position of the Brake valve 11 is a disproportionate connection of the pressures.
  • the Figure 6 further illustrates the change in the driving pressure for the brake slide 11 when braking (a) a load and when accelerating (b) a load or a consumer. 2

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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)

Claims (9)

  1. Système de vanne pour la commande d'un consommateur (2) comprenant un distributeur (3) à plusieurs voies, qui agit en étranglement d'accès, qui peut être réglé constamment et par lequel un raccord (P) de pompe peut être-relié à des raccords (A, B) de consommateur, le consommateur (2) étant raccordé au distributeur (3) à plusieurs voies par des conduits (4, 5) de travail et un courant (6) d'évacuation en volume d'un fluide (7) sous pression étant réglable par le consommateur (2) par un dispositif (8) d'étranglement en fonction d'un signal (LS) de charge du consommateur (2), le dispositif (8) d'étranglement étant réglable par une pression (p') dynamique déduite du signal (LS) de charge, caractérisé en ce que le dispositif (8) d'étranglement est commandé par un circuit (17) hydraulique qui détecte une grandeu-r et une direction d'un courant (7) de fluide sous pression allant au consommateur (2).
  2. Système de vanne suivant la revendication 1, caractérisé en ce que le dispositif (8) d'étranglement fait partie d'une vanne (10) de freinage ou d'un tiroir (11) de freinage d'une vanne (12) de freinage et en ce que le circuit (17) superpose, dans une position de travail d'un tiroir (10, 12) de commande du distributeur (3), la pression dynamique sur un côté (18) frontal du tiroir (11) de freinage à une pression de commande du tiroir (12) de commande.
  3. Système de vanne suivant la revendication 2, caractérisé en ce que, lors d'un déplacement du tiroir (12) de commande d'une position de travail à une position neutre, le circuit (17) achemine moins que proportionnellement au tiroir (12) de freinage la pression de commande du tiroir (12) de commande et inversement.
  4. Système de vanne suivant l'une des revendications 2 à 3, caractérisé en ce qu'un circuit (17) hydraulique est incorporé dans chacun des deux conduits (25, 26) de commande du tiroir (1) de commande.
  5. Système de vanne suivant l'une des revendications précédentes, caractérisé en ce que la pression (p') dynamique sert à déterminer le courant en volume par un diaphragme (9) de mesure d'afflux du distributeur (3).
  6. Système de vanne suivant l'une des revendications précédentes, caractérisé en ce que la pression (p') dynamique est prélevée par une balance (29) manométrique du distributeur (3).
  7. Système de vanne suivant l'une des revendications 2 à 6, caractérisé en ce que le tiroir (11) de freinage est inséré dans le tiroir (12) de commande du distributeur (3) et peut coulisser axialement par rapport à celui-ci.
  8. Système de vanne suivant l'une des revendications 2 à 7, caractérisé en ce que le tiroir (11) de freinage dégage une communication (13) fluidique allant du consommateur (2) à un réservoir (14) de fluide sous pression, lorsque le tiroir (12) de commande est dans une position de commutation qui correspond à une position de travail pour le consommateur (2).
  9. Système de vanne suivant l'une des revendications 2 à 8, caractérisé en ce que le tiroir (11) de freinage peut, par des traversées (15, 15') aux extrémités du tiroir (12) de commande, être soumis à la pression (p') dynamique sur ses deux côtés frontaux.
EP10784445.8A 2009-12-15 2010-11-09 Systeme de vanne pour commander un consommateur Not-in-force EP2513491B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009058371A DE102009058371A1 (de) 2009-12-15 2009-12-15 Ventilanordnung zur Ansteuerung eines Verbrauchers
PCT/EP2010/006814 WO2011072778A1 (fr) 2009-12-15 2010-11-09 Système de vanne pour commander un consommateur

Publications (2)

Publication Number Publication Date
EP2513491A1 EP2513491A1 (fr) 2012-10-24
EP2513491B1 true EP2513491B1 (fr) 2014-05-28

Family

ID=43500104

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10784445.8A Not-in-force EP2513491B1 (fr) 2009-12-15 2010-11-09 Systeme de vanne pour commander un consommateur

Country Status (5)

Country Link
US (1) US20120205563A1 (fr)
EP (1) EP2513491B1 (fr)
JP (1) JP2013513770A (fr)
DE (1) DE102009058371A1 (fr)
WO (1) WO2011072778A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010014071B4 (de) 2010-04-07 2012-12-06 Hydac Filtertechnik Gmbh Hydraulische Anlage
CN113107929B (zh) * 2021-04-15 2023-06-30 中国铁建重工集团股份有限公司 负载敏感液压回路
DE102022124970A1 (de) * 2022-09-28 2024-03-28 Deere & Company Anordnung zur Steuerung eines hydraulischen Dreipunkt- Krafthebers

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4067357A (en) * 1974-06-14 1978-01-10 Herion-Werke Kg Pilot-operated directional control valve
DE3104957C2 (de) * 1981-02-12 1986-12-04 Herion-Werke Kg, 7012 Fellbach Hydraulisch betätigbares Pressensicherheitsventil
US4738279A (en) * 1985-12-17 1988-04-19 Linde Aktiengesellschaft Multiway valves with load feedback
ES2004356A6 (es) * 1986-12-26 1989-01-01 Hiac Valman S A Distribuidor para cilindros hidraulicos
DE8801058U1 (de) * 1988-01-29 1988-03-10 Danfoss A/S, Nordborg Hydraulisches Steuerventil mit Druckfühleinrichtung
DE3817123A1 (de) * 1988-05-19 1989-11-30 Herion Werke Kg Sicherheitsventil
DE4021347A1 (de) * 1990-07-05 1992-01-16 Heilmeier & Weinlein Hydraulische steuervorrichtung
US5701933A (en) * 1996-06-27 1997-12-30 Caterpillar Inc. Hydraulic control system having a bypass valve
DE19735482B4 (de) * 1997-08-16 2006-08-10 Bosch Rexroth Aktiengesellschaft Hydraulisches System mit einem Differentialzylinder und einem Eilgangventil
DE102005013823A1 (de) 2004-03-25 2005-11-10 Husco International Inc., Waukesha Verfahren zum Steuern eines Hydrauliksystems unter Verwendung eines differenzdruckkompensierten Durchflusskoeffizienten
DE602004008764T2 (de) * 2004-07-22 2008-06-12 Eaton S.R.L. Verbrauchsmengesteuerventil für ein hydraulisches System mit Lastmeldung
DE102007020558A1 (de) * 2007-05-02 2008-11-06 Robert Bosch Gmbh Ventilanordnung
DE102007054137A1 (de) 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung

Also Published As

Publication number Publication date
EP2513491A1 (fr) 2012-10-24
WO2011072778A8 (fr) 2011-09-09
JP2013513770A (ja) 2013-04-22
US20120205563A1 (en) 2012-08-16
DE102009058371A1 (de) 2011-06-16
WO2011072778A1 (fr) 2011-06-23

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