EP2184495A1 - Procédé de limitation de la puissance maximale requise par le système hydraulique d'un engin de terrassement et vanne de contrôle directionnelle permettant de faire fonctionner ce procédé - Google Patents

Procédé de limitation de la puissance maximale requise par le système hydraulique d'un engin de terrassement et vanne de contrôle directionnelle permettant de faire fonctionner ce procédé Download PDF

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Publication number
EP2184495A1
EP2184495A1 EP09174983A EP09174983A EP2184495A1 EP 2184495 A1 EP2184495 A1 EP 2184495A1 EP 09174983 A EP09174983 A EP 09174983A EP 09174983 A EP09174983 A EP 09174983A EP 2184495 A1 EP2184495 A1 EP 2184495A1
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EP
European Patent Office
Prior art keywords
section
flow
passage
compensator
sections
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Granted
Application number
EP09174983A
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German (de)
English (en)
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EP2184495B1 (fr
Inventor
Ulderico Busani
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Walvoil SpA
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Walvoil SpA
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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve

Definitions

  • the present finding is directed to the earth-moving machines field, in particular of the excavators controlled by a hydraulic system comprising at least one sectional flow-sharing directional control valve having multiple elements or sections (each element or section being provided with a spool and a compensator), at least one relief valve, at least one pump, and at least one motor capable of providing the power required.
  • the present finding finds application in a well-specified and particular functioning configuration of the machine, i.e., that involving the complete and simultaneous actuation of at least one section of the directional control valve requiring all the flow that can be delivered by the pump and of at least another high pressure section.
  • the current LS pumps are often provided with a torque limiter that is calibrated so that, if the required power, that is nothing else than the product of the flow and the pressure, exceeds that that required can be delivered by the motor, it intervenes by reducing the power.
  • the torque limiter has to reduce at least one of the involved parameters (pressure and/or flow), and particular it intervenes on the flow by automatically reducing, as a function of the pressure, the maximum inclination possible of the pump plate and then the maximum flow.
  • the required power falls back in the limits of the one that can be delivered by the motor, and the behaviour of the directional control valve, that continues to be consistent with the flow-sharing functional concepts, is at the maximum pressure (coincident to that of the relief valve added to the flow losses); and the maximum flow that is delivered continues to go to the travel sections, however, it being reduced because of the torque limiter intervention on the pump, the travel sections slow down.
  • the present invention reduces the maximum pressure to a value such that, when multiplied by the maximum flow, the required power is always lower than that can be delivered by the motor, so that the section at the maximum flow (for example, the two travel sections previously mentioned) is not slowed down in case of the actuation of a third section at the end of the stroke of the cylinder.
  • the pressure increase upon the actuation of a third high pressure section is generated, as better illustrated in the detailed descriptive part, by the local compensators of the sections that require the maximum flow (for example, the two travel sections), which throttle the passage (and so the flow) towards the travels because they are subjected to the Load Sensing signal coming from the actuated third member.
  • the operations requiring high pressures would result to be thereby penalised, such as, for example, the excavating operation of the excavator; therefore, the optimum would be to reduce such maximum pressure only when the two travel sections are completely and concurrently actuate, to then make it to return to the relief valve value when the two travel sections are no more completely actuated.
  • the present invention in the three implementation solutions thereof, looks for a functioning compromise, always in a flow-sharing logic, to achieve the best functionality of the machine.
  • Said pressure limitation on the local compensators ends as the complete actuation of the sections, such as, for example, the travel sections, at the maximum flow stops, thus allowing the system to reach the calibration maximum pressure of the valve.
  • the pressure limitation is also active in the case of an only partial requirement of flow and not only at the maximum flow requirement, with the consequence that partial negative effects could possibly occur, consisting in possible flow increases to the use compared to the desired one, that are anyway compensated by a considerable constructive simplification of the directional control valve, as described below.
  • the system illustrated in Fig. 1 comprises a sectional flow-sharing directional control valve having 3 sections (A, B, and C), a relief valve D, a load sensing pump PP, and a motor M; each of the sections A, B, or C of the system flow-sharing valve comprises a spool 2 and a compensator 1.
  • the two A and B sections of the valve control the excavator travels that is, the actuation of the feeding means, and that the third section C controls a cylinder;
  • the sections A and B are conventionally sized so that, when the two travels are completely and concurrently actuated, they require the maximum flow Q that can be delivered by the pump PP, and in particular each of the sections A and B requires half of the maximum flow Q, i.e., Q/2.
  • the pressure increase is not due to the signal LS increase to the pump PP, but to the fact that this signal arrives to the local compensators 1 of the sections A and B.
  • the local compensators 1 of the sections A and B then intervene, according to the known flow-sharing logic, throttling the flow to the travels, and in doing so, it is they that increase the delivery pressure until arriving to the end situation, in which all the flow continues to go to the travels, which therefore do not slow down, but with a delivery pressure that is equal to the relief valve D calibration pressure plus the pump PP limit, according to the flows and pressures distribution highlighted in the simplified diagram of Fig. 10 .
  • the relief valve is calibrated at 250 bars, therefore there are, in the sections A and B, 270 bars from the pump PP to the spools 2 (delivery pressure), 250 bars downstream the spools 2, and 250 bars in the LS line.
  • first motors M (generally endothermic) capable of meeting the requirement of maximum power P max that there is in the case of the requirement of the maximum flow Q max at the maximum pressure p max , that is the relief valve D calibration one, it results that the motor M would turn off.
  • the present finding solves the above-mentioned slowdown/acceleration problem of the machine translation by intervening on the other power factor, i.e., on the pressure p; such result is obtained by bypassing the local compensators of the section(s) that require the maximum flow (for example, of the travel sections) in the instant in which it/they is/are completely and concurrently actuated relative to a third section with cylinder at the end of its stroke; said bypassing occurs by imparting a delivery pressure lower than that imparted by the relief valve D calibration.
  • the present finding can be applied both to hydraulic systems in which the LS pump is provided with a torque limiter, and to systems in which the pump is not provided with it.
  • the avobe-mentioned delivery pressure is calculated so that the power required is:
  • the local compensators intervention should have to be calibrated so that they create a delivery pressure not higher than 180 bars.
  • a first method for limiting the maximum pressure in the case of completely actuated travels A and B together with a third section C is to make so that the spools 2 of the sections A and B, at the end of their stroke, open a passage 3 between the two areas upstream 4 and downstream 5 the compensator 1 thereof, so as to bypass the same.
  • Said passage 3 is a recess that is obtained on the spool 2 of section A, B, as illustrated in detail in Fig. 2A .
  • Said passage 3 has to be such that, at the delivery pressure of 180 bars calculated before, all the maximum flow Q (Q/2 per travel) passes through it, and not through the compensator 1, that is practically shut out.
  • the flows and pressures distribution is as follows: 180 bars from the pump PP to the spools 2 (delivery pressure), 160 bars downstream the spools 2, and 180 bars in the LS line.
  • a second method for limiting the maximum pressure consists in opening a passage 2E, practically, a hole, between the two areas upstream 4 and downstream 5 the compensator 1 directly in the section A and B.
  • Said passage 2E is calculated so that, at the delivery pressure of 180 bars calculated before, all the flow Q (Q/2 per travel) passes through it, thus bypassing the compensator 1.
  • the flows and pressures distribution is as follows: 180 bars from the pump PP to the spools 2 (delivery pressure), 160 bars downstream the spools 2, and 180 bars in the LS line.
  • the pressure limiting is, however, active also in the case of only partial requirement of the flow, and not only at the maximum requirement, with the consequence that, when the travels sections A, B are partially actuated, flow increases to the use compared to that desired can occur, which translate in acceleration phenomena.
  • a third method for limiting the maximum pressure consists in using a compensator 1A that is designed so that, at the end of the stroke, it leaves a passage 2G open, through which all the flow Q passes (Q/2 per travel) at the previously calculated pressure of 180 bars.
  • Said passage 2G is obtained by limiting the compensator stroke so as not to let it completely close, or through a recess obtained on the same compensator.
  • the limitation of the maximum pressure is active also in the case of only partial requirement of flow, and not only at the maximum requirement, therefore in intermediate positions of the spool 2 of the travels A and B, acceleration phenomena can occur; however, such disadvantages are compensated by the simplicity of the solution.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
EP20090174983 2008-11-06 2009-11-04 Procédé de limitation de la puissance maximale requise par le système hydraulique d'un engin de terrassement et vanne de contrôle directionnelle permettant de faire fonctionner ce procédé Active EP2184495B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITPR2008A000071A IT1391608B1 (it) 2008-11-06 2008-11-06 Metodo per limitare la potenza massima richiesta dall impianto idraulico di una macchina per movimento terra e distributore operante detto metodo

Publications (2)

Publication Number Publication Date
EP2184495A1 true EP2184495A1 (fr) 2010-05-12
EP2184495B1 EP2184495B1 (fr) 2014-01-08

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EP20090174983 Active EP2184495B1 (fr) 2008-11-06 2009-11-04 Procédé de limitation de la puissance maximale requise par le système hydraulique d'un engin de terrassement et vanne de contrôle directionnelle permettant de faire fonctionner ce procédé

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EP (1) EP2184495B1 (fr)
IT (1) IT1391608B1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011150010A2 (fr) * 2010-05-28 2011-12-01 Caterpillar Inc. Système hydraulique à partage d'équipement et de flux de direction
EP2522860A1 (fr) 2011-05-13 2012-11-14 Walvoil S.p.A. Distributeur hydraulique ayant une connexion parallèle aux fentes pour régler la vitesse d'écoulement et compensateur local
WO2014121081A1 (fr) * 2013-01-31 2014-08-07 Parker-Hannifin Corporation Suralimentation à écoulement prioritaire et pression limitée
GB2522542A (en) * 2014-01-02 2015-07-29 Caterpillar Paving Prod Torque limit control
WO2018137014A1 (fr) * 2017-01-27 2018-08-02 Caramona Empreendimentos E Participações Ltda Système hydraulique ou pneumatique

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030200747A1 (en) * 2002-04-30 2003-10-30 Toshiba Kikai Kabushiki Kaisha Hydraulic control system
EP1375927A2 (fr) * 2002-06-19 2004-01-02 Kabushiki Kaisha Toyota Jidoshokki Dispositif de commande hydraulique et engin à travaux avec un dispositif de commande hydraulique
EP1610002A1 (fr) * 2004-06-24 2005-12-28 Walvoil S.p.A. Système hydraulique à détection de charge avec plusieures sections
WO2007116035A1 (fr) * 2006-04-12 2007-10-18 Walvoil S.P.A. Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030200747A1 (en) * 2002-04-30 2003-10-30 Toshiba Kikai Kabushiki Kaisha Hydraulic control system
EP1375927A2 (fr) * 2002-06-19 2004-01-02 Kabushiki Kaisha Toyota Jidoshokki Dispositif de commande hydraulique et engin à travaux avec un dispositif de commande hydraulique
EP1610002A1 (fr) * 2004-06-24 2005-12-28 Walvoil S.p.A. Système hydraulique à détection de charge avec plusieures sections
WO2007116035A1 (fr) * 2006-04-12 2007-10-18 Walvoil S.P.A. Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011150010A2 (fr) * 2010-05-28 2011-12-01 Caterpillar Inc. Système hydraulique à partage d'équipement et de flux de direction
WO2011150010A3 (fr) * 2010-05-28 2012-03-15 Caterpillar Inc. Système hydraulique à partage d'équipement et de flux de direction
CN102985703A (zh) * 2010-05-28 2013-03-20 卡特彼勒公司 具有执行机构以及转向流量共享的液压系统
US8756930B2 (en) 2010-05-28 2014-06-24 Caterpillar Inc. Hydraulic system having implement and steering flow sharing
CN102985703B (zh) * 2010-05-28 2015-06-17 卡特彼勒公司 具有执行机构以及转向流量共享的液压系统
EP2522860A1 (fr) 2011-05-13 2012-11-14 Walvoil S.p.A. Distributeur hydraulique ayant une connexion parallèle aux fentes pour régler la vitesse d'écoulement et compensateur local
WO2014121081A1 (fr) * 2013-01-31 2014-08-07 Parker-Hannifin Corporation Suralimentation à écoulement prioritaire et pression limitée
US9810334B2 (en) 2013-01-31 2017-11-07 Parker-Hannifin Corporation Pressure limited flow priority boost
GB2522542A (en) * 2014-01-02 2015-07-29 Caterpillar Paving Prod Torque limit control
US9464580B2 (en) 2014-01-02 2016-10-11 Caterpillar Paving Products Inc. Torque limit control
WO2018137014A1 (fr) * 2017-01-27 2018-08-02 Caramona Empreendimentos E Participações Ltda Système hydraulique ou pneumatique

Also Published As

Publication number Publication date
ITPR20080071A1 (it) 2010-05-07
IT1391608B1 (it) 2012-01-11
EP2184495B1 (fr) 2014-01-08

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