EP0561185A1 - Commande hydraulique de tiroir pour vérins avec des vitesses de piston inégales - Google Patents

Commande hydraulique de tiroir pour vérins avec des vitesses de piston inégales Download PDF

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Publication number
EP0561185A1
EP0561185A1 EP93102909A EP93102909A EP0561185A1 EP 0561185 A1 EP0561185 A1 EP 0561185A1 EP 93102909 A EP93102909 A EP 93102909A EP 93102909 A EP93102909 A EP 93102909A EP 0561185 A1 EP0561185 A1 EP 0561185A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
piston
pilot
hydraulic
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
EP93102909A
Other languages
German (de)
English (en)
Other versions
EP0561185B1 (fr
Inventor
Friedrich Dipl.-Ing. Schwing
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.)
Friedrich Wilhelm Schwing GmbH
Original Assignee
Friedrich Wilhelm Schwing 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 Friedrich Wilhelm Schwing GmbH filed Critical Friedrich Wilhelm Schwing GmbH
Publication of EP0561185A1 publication Critical patent/EP0561185A1/fr
Application granted granted Critical
Publication of EP0561185B1 publication Critical patent/EP0561185B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a hydraulic slide control for working cylinders according to the preamble of claim 1.
  • Hydraulic working cylinders are used primarily in mechanical engineering to supply kinetic energy in two opposite directions. This allows moving parts to be moved back and forth.
  • the kinetic energy of such a hydraulic drive depends on the volume flow of the hydraulic medium, which is fed to the respective side of the piston in the hydraulic cylinder.
  • the piston While the piston generally develops a substantially uniform speed over the back and forth in the hydraulic working cylinder, the invention provides for the piston to be driven at different speeds in at least one of its two ways. This takes into account practical requirements that place different demands on the hydraulic drive. For example, it may be important to start the movement at a slow speed, then to accelerate in the central area and to slow it down again at the end of the movement.
  • Such hydraulic working cylinders are known per se.
  • One of the known embodiments provides a quantity control of the hydraulic volume flow corresponding to the respective piston speed in the working cylinder via the hydraulic pressure generator.
  • This usually requires quantity-adjustable pumps, where z. B. in a swash plate pump, the inclination of the control mirror determines the respective volume flow.
  • Such pumps are relatively expensive.
  • it is not always possible to provide pumps controlled in this way for the working cylinder. If such pumps are necessary in a control circuit from which the control circuit of the hydraulic working cylinder is derived, it is often not possible to easily achieve different piston speeds in this way.
  • the invention is based on the above-described possibility of controlling the piston speed via the volume flow acting on the drive piston, the direction of movement being switched over with a pilot-controlled directional valve. she goes however, another way, the basic idea of which is given in claim 1. Further features of the invention are the subject of the dependent claims.
  • the pilot control valve is precontrolled with a pilot valve which directs hydraulic medium to one or the other side of the valve piston and thus brings about the respectively desired switching state, which is determined by the higher-level control.
  • the piston speed is determined by the control of a control valve, the piston of which can assume any number of positions, adapted to the individual case, with the control bores assigned to it and thereby directly influence one of the volume flows in each position.
  • This control valve is located on both sides of its valve piston on a control line of the pilot control and is therefore pilot-controlled itself. As a result, the desired control state can be brought about hydraulically and determines one of the piston speeds.
  • the invention has the advantage that it enables different working speeds with a linear drive in the form of a hydraulic working cylinder in a simple manner, namely in particular without the aid of the hydraulic pressure generator. This also includes the possibility of stopping the piston of the working cylinder.
  • the feature of claim 5, namely to provide a memory as a pressure generator for the linear drive of a hydraulic working cylinder, has the advantage over a hydraulic pump with a constant delivery volume that the difference between the amount of pressure determined by the control bore for the working cylinder and the amount available from the pressure generator do not need to be routed to the tank via a safety valve to generate heat.
  • FIG. 1 shows the slide control according to the invention in symbols, while the hydraulic working cylinder 1 and the machine part driven by its piston rod 2 are shown schematically in the form of a two-armed rocker arm 3.
  • the piston 4 runs in the hydraulic working cylinder 1.
  • a line 5 applies a volume flow of the hydraulic pressure generator (pump or accumulator) indicated at 6 (piston or side) to the piston rod side 7 of the working piston 4, while the line 8 acts on the piston side 9 of the piston 4 in the working cylinder 1 becomes.
  • the hydraulic pressure generator pump or accumulator
  • the reversing valve S3 is a 4/2-way valve of known type and enables the hydraulic pressure oil flow to be applied to each piston side, while at the same time the opposite piston side is depressurized on the oil tank 10. in the
  • the piston side 9 is connected to the oil tank 10.
  • a pilot valve A which can be acted upon by switching control pulses on both sides of its valve piston, is used to control the two pilot control paths 11, 12 of the reversing valve S3.
  • This pilot valve essentially corresponds to the reversing valve S3, but it can also be switched over electrically or electronically.
  • the tank appears twice in the drawing, in practice it can be the same tank into which the outgoing volume flow is directed from the pilot control paths 11, 12.
  • a third directional valve in the form of a pilot-controlled control valve B is installed in the pilot paths 11, 12. It is also hydraulically piloted. This takes place via throttles 14, 15 from the pilot control paths 11, 12.
  • the valve piston of the control valve B has five paths. The drain from the drive cylinder connects to the tank in two ways. Two paths in between contain throttles with the same or different throttling effect, while the middle path blocks the volume flow.
  • the arrangement is such that the volume flow displaced from the piston side 9 runs via the line 8 through the control valve B, while the piston rod side 7 is connected to the hydraulic pressure generator 6 via line 5 and a bypass 16.
  • the throttle 14 acts on the unpressurized side of the valve piston in the control valve B.
  • the throttle 15 determines the respective position of the valve piston, the valve piston running through all switching paths one after the other.
  • the drive piston 4 is driven at different speeds and stopped in the middle position.
  • the rocker arm 3 of the lever mechanism therefore executes a sequence of movements via the effective path indicated by the double arrows.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Sliding Valves (AREA)
  • Actuator (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Reciprocating Pumps (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Harvester Elements (AREA)
  • Control Of Presses (AREA)
EP93102909A 1992-03-19 1993-02-25 Commande hydraulique de tiroir pour vérins avec des vitesses de piston inégales Expired - Lifetime EP0561185B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4208755A DE4208755A1 (de) 1992-03-19 1992-03-19 Hydraulische schiebersteuerung fuer arbeitszylinder mit ungleichen kolbengeschwindigkeiten
DE4208755 1992-03-19

Publications (2)

Publication Number Publication Date
EP0561185A1 true EP0561185A1 (fr) 1993-09-22
EP0561185B1 EP0561185B1 (fr) 1997-05-02

Family

ID=6454412

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93102909A Expired - Lifetime EP0561185B1 (fr) 1992-03-19 1993-02-25 Commande hydraulique de tiroir pour vérins avec des vitesses de piston inégales

Country Status (12)

Country Link
US (1) US5353684A (fr)
EP (1) EP0561185B1 (fr)
JP (1) JPH0610904A (fr)
KR (1) KR100280255B1 (fr)
CN (1) CN1036730C (fr)
AT (1) ATE152502T1 (fr)
BR (1) BR9301230A (fr)
CA (1) CA2092657A1 (fr)
DE (2) DE4208755A1 (fr)
ES (1) ES2103390T3 (fr)
GR (1) GR3024142T3 (fr)
RU (1) RU2134363C1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4231399A1 (de) * 1992-08-20 1994-02-24 Rexroth Mannesmann Gmbh Hydraulische Steuereinrichtung
DE19623549A1 (de) * 1996-06-13 1997-12-18 I T E C Gmbh Steuerung von Bewegungen an Maschinen und Vorrichtungen
US6530564B1 (en) * 1997-06-12 2003-03-11 Nitinol Technologies, Inc. Nitinol impact absorbers
US6375432B1 (en) 2000-12-20 2002-04-23 Schwing America, Inc. Pipeline air pocket detection system
CN102865178A (zh) * 2012-09-21 2013-01-09 国网新源水电有限公司丰满培训中心 具有开度限制功能的液压锁定装置
DE102013001829B4 (de) 2013-02-04 2014-08-21 Bourns, Inc. Drehwinkel- und Torsionswinkelsensor
CN105545857B (zh) * 2016-02-02 2018-04-03 泊姆克(天津)液压有限公司 一种新型二通插装式振动控制阀
CN107587933A (zh) * 2017-11-01 2018-01-16 潍柴动力股份有限公司 一种海水流量调节机构、一种中冷器系统、一种发动机
CN109058187B (zh) * 2018-08-01 2020-07-10 福建龙马环卫装备股份有限公司 一种卸荷缓冲液压系统
WO2020102199A1 (fr) * 2018-11-16 2020-05-22 Cnh Industrial America Llc Table de coupe de moissonneuse à système de commande de segment
KR102196957B1 (ko) 2020-10-20 2020-12-30 신상열 유압포지셔너가 구비된 밸브제어시스템

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2009340A1 (de) * 1970-02-27 1971-09-02 Exnii Hydrauhkwerk zur Steuerung der Vor und Ruckbewegung eines Schleifmaschinen tisches
DE2107324A1 (de) * 1971-02-16 1972-08-24 Krupp Gmbh Einrichtung zum Abbremsen eines Körpers bei Lastwechseln
DE2262450A1 (de) * 1972-01-27 1973-08-09 Gen Signal Corp Schaltkreis fuer einen hydraulikantrieb
FR2181479A1 (fr) * 1972-04-25 1973-12-07 Poclain Sa
DE2449736A1 (de) * 1973-10-24 1975-04-30 Atlas Copco Ab Verfahren und vorrichtung zur steuerung der bewegungsgeschwindigkeit eines auslegers, insbesondere eines bohrauslegers
US4215844A (en) * 1978-08-28 1980-08-05 The Babcock & Wilcox Company Valve actuator system
EP0292457A1 (fr) * 1987-05-18 1988-11-23 Atlas Copco Aktiebolag Dispositif connecté à un moteur sous charge dans un système hydraulique de puissance
EP0505977A1 (fr) * 1991-03-25 1992-09-30 Schwing GmbH Système de contrôle de vitesse pour entraînements hydrauliques de préférence pour vérins hydrauliques

Family Cites Families (15)

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CA943040A (en) * 1970-10-06 1974-03-05 Ronald B. Walters Hydraulic actuator controls
SU393485A1 (ru) * 1970-12-22 1973-08-10 Панель реверса
US3872773A (en) * 1972-08-09 1975-03-25 Nutron Corp Position controlling
GB1452609A (en) * 1973-05-15 1976-10-13 Sperry Rand Ltd Hydraulic systems
SU830016A1 (ru) * 1979-07-26 1981-05-15 Киевский институт автоматики им.ХХУ съезда КПСС Реверсивный пневмогидропривод
JPS56109903A (en) * 1980-02-01 1981-08-31 Kanto Seiki Kogyo Kk Speed control device in oil hydraulic circuit
SU1038627A1 (ru) * 1980-09-08 1983-08-30 Всесоюзный научно-исследовательский и проектно-конструкторский институт промышленных гидроприводов и гидроавтоматики Система управлени расходом
JPS6051301U (ja) * 1983-09-16 1985-04-11 株式会社トキメック 昇降装置の液圧回路
JPH0343443Y2 (fr) * 1986-03-01 1991-09-11
JPH07107378B2 (ja) * 1986-07-23 1995-11-15 ヤマハ発動機株式会社 二段型気化器
AT389501B (de) * 1987-08-12 1989-12-27 Hoerbiger Hydraulik Servosteuerung fuer motorboote
US4919039A (en) * 1988-07-25 1990-04-24 General Electric Company Hydraulic turning gear
JPH0221303U (fr) * 1988-07-28 1990-02-13
JPH0294596A (ja) * 1988-09-30 1990-04-05 Hitachi Ltd 電子装置
JP3060317B2 (ja) * 1989-12-14 2000-07-10 株式会社ナブコ 油圧モータの制御回路

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2009340A1 (de) * 1970-02-27 1971-09-02 Exnii Hydrauhkwerk zur Steuerung der Vor und Ruckbewegung eines Schleifmaschinen tisches
DE2107324A1 (de) * 1971-02-16 1972-08-24 Krupp Gmbh Einrichtung zum Abbremsen eines Körpers bei Lastwechseln
DE2262450A1 (de) * 1972-01-27 1973-08-09 Gen Signal Corp Schaltkreis fuer einen hydraulikantrieb
FR2181479A1 (fr) * 1972-04-25 1973-12-07 Poclain Sa
DE2449736A1 (de) * 1973-10-24 1975-04-30 Atlas Copco Ab Verfahren und vorrichtung zur steuerung der bewegungsgeschwindigkeit eines auslegers, insbesondere eines bohrauslegers
US4215844A (en) * 1978-08-28 1980-08-05 The Babcock & Wilcox Company Valve actuator system
EP0292457A1 (fr) * 1987-05-18 1988-11-23 Atlas Copco Aktiebolag Dispositif connecté à un moteur sous charge dans un système hydraulique de puissance
EP0505977A1 (fr) * 1991-03-25 1992-09-30 Schwing GmbH Système de contrôle de vitesse pour entraînements hydrauliques de préférence pour vérins hydrauliques

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 014, no. 424 (M-1024)12. September 1990 & JP-A-02 168 002 ( TOYOOKI ) 28. Juni 1990 *
PATENT ABSTRACTS OF JAPAN vol. 016, no. 129 (M-1228)2. April 1992 & JP-A-03 292 401 ( HITACHI ) 24. Dezember 1991 *

Also Published As

Publication number Publication date
GR3024142T3 (en) 1997-10-31
ATE152502T1 (de) 1997-05-15
CN1078542A (zh) 1993-11-17
CA2092657A1 (fr) 1993-09-20
CN1036730C (zh) 1997-12-17
EP0561185B1 (fr) 1997-05-02
ES2103390T3 (es) 1997-09-16
KR930020037A (ko) 1993-10-19
RU2134363C1 (ru) 1999-08-10
KR100280255B1 (ko) 2001-02-01
DE59306308D1 (de) 1997-06-05
JPH0610904A (ja) 1994-01-21
DE4208755A1 (de) 1993-09-23
US5353684A (en) 1994-10-11
BR9301230A (pt) 1993-09-21

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