EP0362206A1 - Transmission hydraulique. - Google Patents

Transmission hydraulique.

Info

Publication number
EP0362206A1
EP0362206A1 EP88902481A EP88902481A EP0362206A1 EP 0362206 A1 EP0362206 A1 EP 0362206A1 EP 88902481 A EP88902481 A EP 88902481A EP 88902481 A EP88902481 A EP 88902481A EP 0362206 A1 EP0362206 A1 EP 0362206A1
Authority
EP
European Patent Office
Prior art keywords
working
valve
reversing valve
drive device
working cylinder
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
EP88902481A
Other languages
German (de)
English (en)
Other versions
EP0362206B1 (fr
Inventor
Magnus Mauch
Achim Kehrberger
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.)
Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co
Original Assignee
Delmag Maschinenfabrik Reinhold Dornfeld GmbH 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 Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co filed Critical Delmag Maschinenfabrik Reinhold Dornfeld GmbH and Co
Priority to AT88902481T priority Critical patent/ATE73907T1/de
Publication of EP0362206A1 publication Critical patent/EP0362206A1/fr
Application granted granted Critical
Publication of EP0362206B1 publication Critical patent/EP0362206B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature

Definitions

  • the invention relates to a pressure medium-operated drive device according to the preamble of claim 1.
  • Such drive devices find e.g. in hydraulic bears used for driving concrete piles, sheet piling and the like into the ground.
  • the hydraulic working cylinders used to lift a drop weight are arranged at a large distance from the hydraulic center; the length of the connecting lines between the hydraulic center and the working cylinder can be 20 to 70 or 100 m. With such long connecting lines, the line volume is larger than that of the cylinder work rooms. This means that with alternating pressurization of the two cylinder working spaces, the hydraulic working fluid is oscillated between the working lines running between the reversing valve and the working cylinder and the working spaces, but never gets into the sump. The same partial volumes of the working fluid are thus always heated in the working cylinder, which adversely affects the efficiency of the working cylinder and the service life of the working fluid in long-term operation.
  • a cooling device can be assigned to the pressure line and / or the return line and / or the pressure medium sump, as indicated in the preamble of claim 1.
  • the present invention is intended to further develop a pressure medium-operated drive device according to the preamble of claim 1 such that even with long connecting lines between the reversing valve and the Working cylinders, the volume of which is comparable to or larger than the volume of a cylinder working space, cooling of the working fluid is obtained.
  • a drive device In a drive device according to claim 1, one has a controllable bypass line connecting the cylinder-side ends of the working lines, and by opening this working line one can press the entire volume of working fluid in the working lines through the cooling device and replace it with newly drawn working fluid from the pressure sump. Since such an exchange of heated working fluid for cooled working fluid only needs to be carried out at larger time intervals and since the pushing of the working fluid takes place without any appreciable resistance and thus quickly, the proposed manner of flushing the working lines does not result in any noteworthy reduction in the work performed by the user Receive device equipped drive device according to the invention.
  • the proposal according to the invention also requires only little additional construction effort. Retrofitting to drive devices already in use is easily possible.
  • bypass line can be opened manually at intervals.
  • the solution specified in claim 6 can be used as an alternative to the solution conveyed by claim 1. Outside it is ensured that the cooling device, which contains mechanically sensitive parts such as cooling fins or cooling coils, can be arranged at the location of the hydraulic center, i.e. far away from the working cylinder, where it is not exposed to the strong impacts and vibrations generated at the cylinder working location.
  • the cooling device which contains mechanically sensitive parts such as cooling fins or cooling coils
  • the reversing valve is arranged close to the working cylinder, it is ensured that the working fluid is kept in constant circulation, thus constantly flowing through the cooling device.
  • the reversing valve is arranged on a vibration-independent, independent frame part in the vicinity of the working cylinder, the reversing valve itself can be a relatively complicated control block which contains pressure limiting valves, pilot valves and other sensitive auxiliary valves.
  • FIG. 1 shows a block diagram of a hydraulic drive device which has a working cylinder which is far away from a hydraulic center, with a cooling device for the hydraulic oil;
  • FIGS 2 and 3 each a schematic representation of a modified hydraulic drive device with cooling of the hydraulic oil.
  • a double twinking hydraulic working cylinder is designated by 10 in total.
  • a piston 12 is slidable, which together with a cylinder housing 14 two working spaces 16 and 18 limited.
  • the latter are connected via working lines 20, 22 to a reversing valve, designated overall by 24.
  • the working lines 20, 22 have a large length (in practice, for example, 70 m up to 100 m), as indicated by the broken lines in these lines.
  • the reversing valve 24 is a 4/3 valve, which is biased by springs into the middle rest position and is moved into one or the other of its working positions by energizing actuating magnets.
  • the reversing valve 24 On the input side, the reversing valve 24 is connected to the delivery opening of a hydraulic pump 26, which draws in from a sump 28.
  • the pressure line running between the hydraulic pump 26 and the reversing valve 24 is designated by 30 in FIG.
  • a return line 32 also connected to the reversing valve 24 contains a cooler 34 for the hydraulic oil.
  • a bypass line 36 which contains a normally closed bypass valve 38, is connected to the ends of the long working lines 20, 22 adjacent to the working cylinder.
  • the latter is a magnetic valve and, like the reversing valve 24, is excited by a control unit 40.
  • the control unit 40 receives as input signals the output signal of an end position sensor 42 which cooperates with end position marks 46, 48 carried by the piston rod 44 of the working cylinder 10.
  • the control unit 40 receives further input signals from a keypad 50 connected to it and from the output DO of a digital comparator 52.
  • the comparator 52 receives a reference signal from a read-only memory 54, which is continuously connected to the output signal of an analog / digital converter 56. Its input is connected to the outputs of two temperature sensors 60, 62, which is inserted into the working lines 20, 22 in the immediate vicinity of the working cylinder 10, via a schematically indicated changeover switch 58, which is actuated synchronously with the reversing valve 24.
  • the synchronization of the changeover switch 58 is selected such that that one of the temperature sensors 60, 62 is connected to the digital / analog converter which is acted upon by the hydraulic oil flowing out of the working cylinder 10.
  • the switch 58 can also freely switch with compared to the switching frequency of the reversing valve 24 high frequency, so that the Digi tal / analog converter is rapidly acted upon successively with analog temperature signals for the outflowing or the inflowing hydraulic oil.
  • control unit 40 closes the bypass valve 38 and the old one Nating excitation of the solenoids of the reversing valve 24 is resumed.
  • the length of a rinsing cycle described in detail above is specified by a timer which forms part of the control unit 40.
  • the rinsing time specified by this timer can e.g. can be set on a setting button 64 of the control unit 40 according to the respective length of the working lines 20, 22.
  • the reversing valve 24 is arranged on a frame part 66 which is closely adjacent to a frame part 68 which carries the working cylinder 10, but is at least largely decoupled from it in terms of vibration.
  • the frame part 66 is also decoupled in terms of vibration from other parts of the working device comprising the working cylinder 10.
  • the reversing valve 24 is now connected to the working cylinder 10 via short working lines 20 ', 22' which have flexible sections 70, 72.
  • the working lines 20 'and 22' now have a volume which is small compared to the volumes of the working spaces 16 and 18.
  • the major part of the hydraulic oil in the working spaces 16 and 18 is thus not exchanged in an oscillating manner with the working lines 20 'and 22', but rather reaches the device circuit from the pressure line 30 to the return line 32.
  • the hydraulic oil thus also continuously passes through the cooler 34 u, rolled and sufficiently cooled.
  • the working cycles of the working cylinder 10 and the flushing of the working lines 20, 22 after a predetermined number of working cycles can also be counted in accordance with FIG. 3 instead of the temperature measurement in the working lines 20, 22 described with reference to FIG initiate .
  • control unit 40 to the counter terminal C of a counter 56 ', the data output DO of which is connected to the one data input DI 1 of a comparator 52', which receives its reference signal again from a read-only memory 54 '.
  • the counter 56 ' is reset as well as the triggering of a rinsing cycle by the output signal of the comparator 52'.
  • the exemplary embodiment according to FIG. 3 otherwise works similarly to that according to FIG. 1.
  • control terminal of the control unit 40 intended to initiate a flushing process can simply be connected to the output of a very low-frequency free-running clock generator 74, which then replaces the circuits 52'-54 'of FIG. 3, as indicated by the dashed lines there.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)

Abstract

Dans une transmission hydraulique, dans laquelle un vérin hydraulique (10) à double effet est relié à la source centrale de puissance hydraulique par l'intermédiaire de très longues conduites de travail (20, 22), une conduite de dérivation (36) comportant une vanne de dérivation (38) normalement fermée est reliée aux extrémités des conduites de travail (20, 22) côté vérin. La vanne de dérivation (38) est périodiquement ouverte pour permettre le renouvellement complet du fluide contenu dans les conduites de travail (20, 22).
EP88902481A 1987-03-27 1988-03-22 Transmission hydraulique Expired - Lifetime EP0362206B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88902481T ATE73907T1 (de) 1987-03-27 1988-03-22 Druckmittelbetriebene antriebseinrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3710028 1987-03-27
DE19873710028 DE3710028A1 (de) 1987-03-27 1987-03-27 Druckmittelbetriebene antriebseinrichtung

Publications (2)

Publication Number Publication Date
EP0362206A1 true EP0362206A1 (fr) 1990-04-11
EP0362206B1 EP0362206B1 (fr) 1992-03-18

Family

ID=6324072

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88902481A Expired - Lifetime EP0362206B1 (fr) 1987-03-27 1988-03-22 Transmission hydraulique

Country Status (6)

Country Link
US (1) US5072584A (fr)
EP (1) EP0362206B1 (fr)
JP (1) JPH02502842A (fr)
AT (1) ATE73907T1 (fr)
DE (2) DE3710028A1 (fr)
WO (1) WO1988007633A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2666787B1 (fr) * 1990-09-19 1992-12-18 Aerospatiale Actionneur hydraulique a mode hydrostatique de fonctionnement de preference en secours, et systeme de commande de vol le comportant.
US5456078A (en) * 1994-08-12 1995-10-10 Caterpillar Inc. Method of purging a hydraulic system
GB2296046B (en) * 1994-10-18 1998-07-15 Automotive Products Plc Actuation systems
DE19627974C2 (de) * 1996-07-11 2003-02-06 Getrag Getriebe Zahnrad Hydraulische Stelleinheit und Verfahren zum Entlüften einer hydraulischen Stelleinheit
JPH11245831A (ja) * 1998-03-05 1999-09-14 Toyoda Mach Works Ltd 油圧式動力舵取装置
US6178871B1 (en) * 1998-06-25 2001-01-30 Tom Sutherland Actuator and method of operating same
CA2290117C (fr) * 1999-11-15 2005-05-10 Wheeltronic Ltd. Egalisateur de pression
JP2001180508A (ja) * 1999-12-27 2001-07-03 Toyota Autom Loom Works Ltd パワーステアリングバルブ
ITMI20040197A1 (it) * 2004-02-09 2004-05-09 Astra Veicoli Ind S P A Procedimento e circuito per la regolazione della portata di olio idraulico di raffreddamwento freni di un veicolo
US7421840B2 (en) * 2004-03-08 2008-09-09 Bosch Rexroth Corporation Energy conversion and dissipation system
US7191593B1 (en) * 2005-11-28 2007-03-20 Northrop Grumman Corporation Electro-hydraulic actuator system
SE531309C2 (sv) * 2006-01-16 2009-02-17 Volvo Constr Equip Ab Styrsystem för en arbetsmaskin och förfarande för styrning av en hydraulcylinder hos en arbetsmaskin
JP4802852B2 (ja) * 2006-05-16 2011-10-26 コベルコ建機株式会社 作業機械の油圧回路
US8042333B2 (en) * 2007-03-14 2011-10-25 Hampton Hydraulics Oil cooling circuit for continuously reciprocating hydraulic cylinders
CN104204547A (zh) * 2012-03-22 2014-12-10 优铁工有限公司 液压缸驱动回路用的冲洗回路
JP7523259B2 (ja) * 2020-06-19 2024-07-26 川崎重工業株式会社 液圧駆動システム
JP2025156819A (ja) * 2024-04-02 2025-10-15 キャタピラー エス エー アール エル 建設機械の油圧回路

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2688313A (en) * 1950-03-21 1954-09-07 Us Navy Fluid pressure reciprocating motor and control valve apparatus
US2929212A (en) * 1957-03-28 1960-03-22 Gen Electric Cooling means for fluid actuators
CH477630A (de) * 1968-09-10 1969-08-31 Hydrel Ag Maschf Mindestens angenähert lastunabhängige Genauigkeitsumsteuerung an einem hydraulischen Leistungsantrieb für Wechselbewegungen eines Arbeitsorganes, beispielsweise bei Werkzeugmaschinen und Aufzügen
US3699847A (en) * 1971-02-04 1972-10-24 Mc Donnell Douglas Corp Cooled hydraulic system
US4059042A (en) * 1976-10-04 1977-11-22 Caterpillar Tractor Co. Hydraulic system for extremely cold environments
JPS57501440A (fr) * 1980-09-29 1982-08-12
US4779418A (en) * 1987-02-17 1988-10-25 M-B-W Inc. Remote control system for a soil compactor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8807633A1 *

Also Published As

Publication number Publication date
JPH02502842A (ja) 1990-09-06
ATE73907T1 (de) 1992-04-15
DE3869412D1 (de) 1992-04-23
EP0362206B1 (fr) 1992-03-18
DE3710028A1 (de) 1988-10-06
WO1988007633A1 (fr) 1988-10-06
US5072584A (en) 1991-12-17

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