EP0561185B1 - 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
EP0561185B1
EP0561185B1 EP93102909A EP93102909A EP0561185B1 EP 0561185 B1 EP0561185 B1 EP 0561185B1 EP 93102909 A EP93102909 A EP 93102909A EP 93102909 A EP93102909 A EP 93102909A EP 0561185 B1 EP0561185 B1 EP 0561185B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
piston
hydraulic
superposed
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.)
Expired - Lifetime
Application number
EP93102909A
Other languages
German (de)
English (en)
Other versions
EP0561185A1 (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.
  • a slide control is known from US-A-4 125 844.
  • 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 supplied 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 relates to hydraulic working cylinders, the pistons of which are 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 volume-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.
  • a third of the known possibilities (US-A-4 215 844), which, however, only allows two different piston speeds, uses a pneumatic-hydraulic slide control for this.
  • a pneumatic-hydraulic slide control for this.
  • the pneumatic pilot control of both directional control valves is carried out by a setpoint-actual value comparator, which is acted upon by control pulses for the working cylinder.
  • the directional valve located in the by-pass is linked via the pneumatic pilot control to the reversing valve in such a way that in the event of large control deviations, the piston is driven at high speed via the by-pass, while the lower piston speed is achieved via the reduced volume of the throttle arrangement, which is at small control deviations is switched through.
  • 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 desired switching state, which is determined by the higher-level control.
  • the piston speed is determined by the control of a directional 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 directional valve is in contact with both sides of its valve piston a control line of the pilot control and is itself piloted by the pressure difference between the two control lines. With the built-in throttles, 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 chokes required for this purpose and built into the pilot control paths of the control valve represent simple means which can easily be implemented in hydraulic circuits.
  • the feature of claim 4, 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 action 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 acts on the piston rod side 7 of the working piston 4 with a volume flow of the hydraulic pressure generator (pump or accumulator) indicated at 6, while the piston side 9 of the piston 4 acts on the working cylinder 1 via the line 8 becomes.
  • the hydraulic pressure generator pump or accumulator
  • the reversing valve S3 is a 4/2-way valve of a 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 connected to the oil tank 10 without pressure.
  • 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 is located in the pilot control paths 11, 12 between the pilot control valve A and the reversing valve S3 built in the form of a pilot-operated control valve B. 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. Two ways switch the drain from the drive cylinder to the tank. Two intermediate paths 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 in succession.
  • 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)
  • Actuator (AREA)
  • Sliding Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Harvester Elements (AREA)
  • Control Of Presses (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Reciprocating Pumps (AREA)

Claims (4)

  1. Commande hydraulique de tiroir pour vérins (1) avec des vitesses de piston inégales pour laquelle un distributeur d'inversion (B) à travers lequel passe l'un des deux courants volumétriques du fluide moteur hydraulique adapte le courant volumétrique du fluide moteur hydraulique, courant alimentant le piston, à la vitesse du piston et pour laquelle le sens de mouvement du piston (4) est réglé avec un distributeur (S3) pilote qui est commandé avec les impulsions de commande pour le vérin (4), le distributeur d'inversion (B) étant monté devant le distributeur pilote (S3), caractérisée en ce qu'une soupape pilote (A) est réglable avec les impulsions de commande pour le vérin (4) et en ce que les parcours pilote (11, 12) conduisant au distributeur pilote (S3) commandent le distributeur d'inversion (B) qui présente une série de longueurs de course de couplage qui déterminent à chaque fois une vitesse de piston et qui traversent les unes après les autres le distributeur d'inversion (B) à l'aide de papillons (14, 15) montés dans les parcours pilote du distributeur d'inversion.
  2. Commande hydraulique de tiroir selon la revendication 1, caractérisée en ce que, dans au moins une position du distributeur d'inversion (B), un arrêt est monté dans le parcours affecté à cette position.
  3. Commande hydraulique de tiroir selon l'une des revendications 1 ou 2, caractérisée en ce que le piston du distributeur d'inversion (B) présente une série de creux de passage, d'orifices d'étranglement et d'arrêts.
  4. Commande hydraulique de tiroir selon l'une des revendications 1 à 3, caractérisée en ce qu'un réservoir est prévu en tant que générateur de pression pour la commande linéaire d'un vérin hydraulique.
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
DE4208755 1992-03-19
DE4208755A DE4208755A1 (de) 1992-03-19 1992-03-19 Hydraulische schiebersteuerung fuer arbeitszylinder mit ungleichen kolbengeschwindigkeiten

Publications (2)

Publication Number Publication Date
EP0561185A1 EP0561185A1 (fr) 1993-09-22
EP0561185B1 true 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***、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***
US20220007576A1 (en) * 2018-11-16 2022-01-13 Cnh Industrial America Llc Harvester header having a segment control system
KR102196957B1 (ko) 2020-10-20 2020-12-30 신상열 유압포지셔너가 구비된 밸브제어시스템

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DE2009340C3 (de) * 1970-02-27 1975-10-16 Experimentalnij Nautschno-Issledowatel'skij Institut Metalloreschuschtschich Stankow, Moskau Hydraulikwerk zur Steuerung der Vor- und Rückbewegung eines Schleifmaschinentisches
CA943040A (en) * 1970-10-06 1974-03-05 Ronald B. Walters Hydraulic actuator controls
SU393485A1 (ru) * 1970-12-22 1973-08-10 Панель реверса
DE2107324A1 (de) * 1971-02-16 1972-08-24 Krupp Gmbh Einrichtung zum Abbremsen eines Körpers bei Lastwechseln
US3835647A (en) * 1972-01-27 1974-09-17 Gen Signal Corp Multiple speed hydraulic drive circuit
FR2181479B1 (fr) * 1972-04-25 1974-12-20 Poclain Sa
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GB1452609A (en) * 1973-05-15 1976-10-13 Sperry Rand Ltd Hydraulic systems
SE381919B (sv) * 1973-10-24 1975-12-22 Atlas Copco Ab Sett att reglera en hydraulbroms rorelser och anordning for genomforande av settet
US4215844A (en) * 1978-08-28 1980-08-05 The Babcock & Wilcox Company Valve actuator system
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JPS56109903A (en) * 1980-02-01 1981-08-31 Kanto Seiki Kogyo Kk Speed control device in oil hydraulic circuit
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Also Published As

Publication number Publication date
KR100280255B1 (ko) 2001-02-01
EP0561185A1 (fr) 1993-09-22
US5353684A (en) 1994-10-11
GR3024142T3 (en) 1997-10-31
ATE152502T1 (de) 1997-05-15
CN1078542A (zh) 1993-11-17
KR930020037A (ko) 1993-10-19
DE59306308D1 (de) 1997-06-05
RU2134363C1 (ru) 1999-08-10
CN1036730C (zh) 1997-12-17
DE4208755A1 (de) 1993-09-23
CA2092657A1 (fr) 1993-09-20
JPH0610904A (ja) 1994-01-21
BR9301230A (pt) 1993-09-21
ES2103390T3 (es) 1997-09-16

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