EP0239848A2 - Régulation de commande pour cylindre hydraulique servant d'entraînement pour pompes à piston - Google Patents

Régulation de commande pour cylindre hydraulique servant d'entraînement pour pompes à piston Download PDF

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Publication number
EP0239848A2
EP0239848A2 EP87103653A EP87103653A EP0239848A2 EP 0239848 A2 EP0239848 A2 EP 0239848A2 EP 87103653 A EP87103653 A EP 87103653A EP 87103653 A EP87103653 A EP 87103653A EP 0239848 A2 EP0239848 A2 EP 0239848A2
Authority
EP
European Patent Office
Prior art keywords
control
piston
longitudinal
throttle
pressure
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
EP87103653A
Other languages
German (de)
English (en)
Other versions
EP0239848B1 (fr
EP0239848A3 (en
Inventor
Ernst Korthaus
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT87103653T priority Critical patent/ATE68564T1/de
Publication of EP0239848A2 publication Critical patent/EP0239848A2/fr
Publication of EP0239848A3 publication Critical patent/EP0239848A3/de
Application granted granted Critical
Publication of EP0239848B1 publication Critical patent/EP0239848B1/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
    • 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
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F04B9/1053—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor one side of the double-acting liquid motor being always under the influence of the liquid under pressure

Definitions

  • the invention relates to a control according to the preamble of claim 1.
  • Piston pumps for which the control is suitable are described, for example, in DE-OS 34 10 911.
  • Piston pumps of this type are used, for example, as construction pumps for conveying dirty water from construction pits and the like.
  • Such construction pumps must be self-priming, ie they must first be able to carry out a pure air pump.
  • gas-free liquids must also be pumped.
  • such construction pumps can further become one Vacuum in the suction line, which acts as a pulling load on this piston after reversing the direction of movement of the pump piston.
  • a pressure-side load on the pump piston due to the water column present here can lead to tearing off, if the deceleration and acceleration of the piston are not adapted accordingly.
  • the object of the invention is to design a control system of the type mentioned at the outset in such a way that precisely predetermined movement sequences are ensured under all the load cases mentioned above.
  • a differential hydraulic cylinder 2 is shown in rapid traverse as a thrust piston drive.
  • the piston of a piston pump is connected to the piston rod 3 of the cylinder 2.
  • the pressure oil is supplied via a hydraulic pump 4 with a constant flow rate.
  • the pump 4 is protected on the pressure side in the usual way via a pressure relief valve 6.
  • the pressure line 8 of the hydraulic pump 4 leads to the rod chamber 10 of the cylinder 2.
  • a branch line 12 leads via the controller 14 to be described below to the connecting line 16 of the piston chamber 18 of the cylinder 2.
  • a tank line 20 leads into the Oil tank 22.
  • An auxiliary pump 24 is directly coupled to the hydraulic pump 4. which is secured by a pressure relief valve 25.
  • This pump supplies the pressure oil for switching the control valve 26, which can be switched over via a remotely operated reversing valve 28.
  • an adjustable throttle 32 is arranged in the tank line 20 of this hydraulic circuit, by means of which the speed of the movement of the control piston 34 of the control valve 26 can be adjusted when reversing.
  • the housing of the control valve 26 is indicated here by dashed lines. Four annular spaces 36, 38, 40, 42 are formed in it, of which the right annular space 36 is connected to line 12.
  • the controller 14 has two pressure compensators 44, 46.
  • the pressure compensator 44 lies in a line 48 which leads from the annular space 38 of the control valve 24 to the connecting line 16 of the cylinder 2.
  • the annular space 42 is also connected to the line 16 via a line 50.
  • the tank line is connected to the annular space 40 via the pressure compensator 46.
  • the control piston 34 is designed as a hollow piston with two cavities 52, 54, which are provided with inflow bores 56, 58 in the area of the annular spaces 36 and 42 and at the mutually facing ends with throttle slots 60, 62 in the area of the annular spaces 38 and 40, respectively are, which are designed here as radially flowed throttle slots.
  • the two pressure compensators 44, 46 are connected with their control lines 64, 66 and 68, 70 in parallel to the throttles 60, 62, in the present case connected to the annular spaces 36, 42 and 38, 40.
  • the ratio of the two areas of the piston 19 acted upon by hydraulic oil is 2: 1.
  • area ratios deviating therefrom can also be selected.
  • control piston 24 of the control valve 28 is in its right end position and the piston 19 is in a central position. In this position of the control piston, the connection between the annular spaces 36 and 38 is blocked.
  • the pump 4 thus conveys exclusively into the rod chamber 10 of the cylinder 2. Oil flows from the piston side 18 of the cylinder L via the lines 16, 50 via the throttle slots 52 and the pressure compensator 46 into the tank. The piston 19 thus moves to the left in the direction of the arrow 5.
  • Fixed sensors 72, 74 are provided in the range of motion of the piston rod 3, which are indicated schematically here and with which, for example, certain markings on the piston rod are scanned. These markings are arranged so that the sensors 72, 74 each respond at a predetermined distance from the piston 19 before its end position. After such a sensor has responded, the deceleration of the piston is initiated. This is done by reversing the changeover valve 28, pressure oil flowing into the actuating chamber in front of the right end of the control piston, while the oil flows out of the left actuating chamber via the throttle 32 into the tank. With the speed dependent on the set passage of the throttle 32, the control piston 34 is shifted to the left.
  • two pairs of longitudinal throttles 74, 76 and 78, 80 are provided in the control piston 72 at a distance from one another in the axial direction which are connected via the bores or cavities 82 and 84 to centrally arranged radial connection bores 83 and 85, respectively.
  • the left longitudinal throttle pair 78, 80 is connected to the feed line 12 via the connection bores 86, while the throttle pair 74, 76 are connected to the tank connection 20 via the connection bore 83.
  • the ports 12 and 20 are in turn associated with annular spaces 86, 88, while the throttles 74, 76 and 78, 80, respectively Annular spaces 90, 92 and 94, 96 cooperate.
  • the annular spaces 90, 92 are connected to the rod spaces 102 and 1 04 of the drive cylinders 106 and 108, respectively, via pressure compensators 98, 100.
  • the two piston chambers 110, 112 of the drive cylinders are connected to one another via a line 114 in the manner of a hydraulic linkage.
  • the control lines of the pressure compensators 98, 100 shown in dashed lines, are in turn connected here via the chokes 78 and 80, respectively.
  • Two further pressure compensators 116 and 118 are connected upstream of the inlets of the annular spaces 94, 96 and thus in the flow direction to the restrictors 74, 76 of the other pair of restrictors , while the inlet of the pressure compensator 116 is connected to the line 124 to the rod chamber 104 of the drive cylinder 108.
  • the function of this embodiment of the control is readily apparent from the description of FIG. 1. Also in this arrangement with two cylinders, the pistons and the associated pressure compensators are used to clamp the pistons during all operating states.
  • the drive cylinder is a single differential cylinder 126, as in the embodiment according to FIG. 1.
  • the speed of movement of the piston 128 with the piston rod 130 is different in both directions and depends on the area ratio.
  • 128 different speeds can also be specified by the area ratio of the piston by selecting different throttle cross sections on the inlet and outlet sides.
  • the throttle cross sections on the outlet side can be made larger in relation to the effective piston areas in order to achieve the same piston speeds in both directions.
EP87103653A 1986-04-04 1987-03-13 Régulation de commande pour cylindre hydraulique servant d'entraînement pour pompes à piston Expired - Lifetime EP0239848B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87103653T ATE68564T1 (de) 1986-04-04 1987-03-13 Antriebe ''steuerung fuer hydraulikzylinder als antriebe fuer kolbenpumpen''.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3611212A DE3611212C1 (de) 1986-04-04 1986-04-04 Steuerung fuer Hydraulikzylinder als Antriebe fuer Kolbenpumpen
DE3611212 1986-04-04

Publications (3)

Publication Number Publication Date
EP0239848A2 true EP0239848A2 (fr) 1987-10-07
EP0239848A3 EP0239848A3 (en) 1989-12-13
EP0239848B1 EP0239848B1 (fr) 1991-10-16

Family

ID=6297859

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87103653A Expired - Lifetime EP0239848B1 (fr) 1986-04-04 1987-03-13 Régulation de commande pour cylindre hydraulique servant d'entraînement pour pompes à piston

Country Status (7)

Country Link
US (1) US4768420A (fr)
EP (1) EP0239848B1 (fr)
JP (1) JPH06100205B2 (fr)
AT (1) ATE68564T1 (fr)
CA (1) CA1268098A (fr)
DE (2) DE3611212C1 (fr)
IN (1) IN169287B (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4919039A (en) * 1988-07-25 1990-04-24 General Electric Company Hydraulic turning gear
US5145332A (en) * 1991-03-01 1992-09-08 Atlantic Richfield Company Well pumping
US5615648A (en) * 1992-07-25 1997-04-01 Robert Bosch Gmbh Electro-hydraulic adjusting device
DE4414779C1 (de) * 1994-04-25 1995-11-02 Mannesmann Ag Multifunktionsventil
CN108253082B (zh) * 2018-04-11 2024-01-09 宜春市鼎鑫高能科技有限公司 一种气流输送碳酸锂用空气平衡器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1299922B (de) * 1967-01-17 1969-07-24 Koeppern & Co Kg Maschf Hydraulischer Vibrationsantrieb mit einem Schubkolbentrieb
DE1904778A1 (de) * 1969-01-31 1970-08-20 Koeppern & Co Kg Maschf Hydraulischer Vibrationsantrieb
US3945206A (en) * 1973-11-22 1976-03-23 Ruthner Industrieanlagen-Aktiengesellschaft Control system for hydraulic presses comprising a plurality of press rams

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1042504B (de) * 1953-01-09 1958-11-06 Hans Doern Einrichtung zum Fernbetaetigen von umsteuerbaren Druckluftarbeits-zylindern im Bergbaubetrieb, insbesondere im Untertagebetrieb
US3882896A (en) * 1971-09-30 1975-05-13 Tadeusz Budzich Load responsive control valve
JPS5517241B2 (fr) * 1972-07-28 1980-05-10
US4401009A (en) * 1972-11-08 1983-08-30 Control Concepts, Inc. Closed center programmed valve system with load sense
US3908515A (en) * 1973-09-10 1975-09-30 Caterpillar Tractor Co Hydraulic circuit with selectively actuatable float control
SU607061A1 (ru) * 1974-12-04 1978-05-15 Предприятие П/Я В-2302 Гидравлический след щий привод
DE2461021A1 (de) * 1974-12-21 1976-06-24 Bosch Gmbh Robert Vorrichtung zur steuerung wenigstens einer hydraulischen stelleinrichtung
DE2609434C2 (de) * 1976-03-06 1985-03-07 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur Steuerung eines hydraulischen Motors
SU739260A1 (ru) * 1977-10-10 1980-06-05 Горьковский Автомобильный Завод (Производственное Объединение Газ) Гидропривод
SU916787A1 (ru) * 1977-10-25 1982-03-30 Od Sp K B Sp Stankov Oskbss Гидропривод рабочего органа станка 1
SU840518A2 (ru) * 1979-09-12 1981-06-23 Государственный Проектный Институт Ме-Занизации И Автоматизации Предприятийпищевой Промышленности "Роспищепромавто-Матика" Гидросистема управлени исполнительнымМЕХАНизМОМ
US4282898A (en) * 1979-11-29 1981-08-11 Caterpillar Tractor Co. Flow metering valve with operator selectable boosted flow
US4418612A (en) * 1981-05-28 1983-12-06 Vickers, Incorporated Power transmission
US4569272A (en) * 1982-03-22 1986-02-11 Vickers, Incorporated Power transmission
DE3410911A1 (de) * 1983-04-06 1984-10-11 Ernst Dipl.-Ing. 4600 Dortmund Korthaus Kolbenpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1299922B (de) * 1967-01-17 1969-07-24 Koeppern & Co Kg Maschf Hydraulischer Vibrationsantrieb mit einem Schubkolbentrieb
DE1904778A1 (de) * 1969-01-31 1970-08-20 Koeppern & Co Kg Maschf Hydraulischer Vibrationsantrieb
US3945206A (en) * 1973-11-22 1976-03-23 Ruthner Industrieanlagen-Aktiengesellschaft Control system for hydraulic presses comprising a plurality of press rams

Also Published As

Publication number Publication date
CA1268098A (fr) 1990-04-24
US4768420A (en) 1988-09-06
ATE68564T1 (de) 1991-11-15
DE3611212C1 (de) 1987-06-11
JPH06100205B2 (ja) 1994-12-12
DE3773720D1 (de) 1991-11-21
EP0239848B1 (fr) 1991-10-16
IN169287B (fr) 1991-09-21
JPS631803A (ja) 1988-01-06
EP0239848A3 (en) 1989-12-13

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