EP0241870A2 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0241870A2
EP0241870A2 EP87105284A EP87105284A EP0241870A2 EP 0241870 A2 EP0241870 A2 EP 0241870A2 EP 87105284 A EP87105284 A EP 87105284A EP 87105284 A EP87105284 A EP 87105284A EP 0241870 A2 EP0241870 A2 EP 0241870A2
Authority
EP
European Patent Office
Prior art keywords
pressure
pilot valve
outlet
line
control device
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
EP87105284A
Other languages
German (de)
English (en)
Other versions
EP0241870A3 (en
EP0241870B1 (fr
Inventor
Martin Dipl.-Ing. Heusser (eth.Zürich)
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority to AT87105284T priority Critical patent/ATE71191T1/de
Publication of EP0241870A2 publication Critical patent/EP0241870A2/fr
Publication of EP0241870A3 publication Critical patent/EP0241870A3/de
Application granted granted Critical
Publication of EP0241870B1 publication Critical patent/EP0241870B1/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

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • control valves which are particularly suitable for speed and position control of movements in one direction against load.
  • a hydraulic control device is provided in the control circuit of which the orifice and the three-way pilot valve and the external actuator are contained.
  • the three-way pilot valve Depending on the actuating force of the actuator, the three-way pilot valve generates a pressure at its control connection which acts on the orifice element against the force of the spring and the pressure in the drain line in order to maintain a certain preselected orifice size.
  • the second outlet of the three-way pilot valve is connected to the tank so that pressure medium can be released to lower the pressure at the control connection.
  • a displacement pickup device for position control of the orifice element is required, with which the respective position of the orifice element is sensed and communicated to the actuator, which retroactively changes the actuating force to hold the previously selected aperture size hydraulically via the pilot valve.
  • the displacement device is structurally complex and expensive. Furthermore, the three-way pilot valve complex and expensive to manufacture because it has to process the full working pressure compared to the discharge pressure to the tank. Furthermore, a complex electrical control circuit is necessary.
  • the invention has for its object to provide a control device of the type mentioned, with which a selected aperture size is maintained in a structurally simple manner and with a simple and inexpensive pilot valve in the event of pressure changes in the inlet and / or in the outlet line.
  • the pressure in the drain line in the pilot valve linearly overlaps the pressure at the control connection of the pilot valve, so that the pressure difference between the pressure in the control connection of the pilot valve and the discharge pressure is always proportional to the force of the actuator.
  • the pilot valve only needs to cope with the relatively small pressure difference between the pressure in its control connection and the discharge pressure, which has the advantage that the pilot valve can be simple and inexpensive and still forms an extremely effective reinforcement for the external adjusting member. This results in the particular advantage of the control device, because an actuator with a relatively weak actuating force is sufficient to easily process even high pressures and large delivery rates. If the actuator is, for example, a proportional magnet, it can be weak and therefore small and inexpensive.
  • the high forces which may be present at a high working pressure, are generated by the pilot valve with the help of the pressure in the control connection built up from the pressure in the supply line, which pressure can be relatively high, but is nevertheless compensated by the pressure in the discharge line to such an extent that the actuator despite the high processed pressures, only a small actuating force needs to be applied and the pilot valve only has to cope with the aforementioned relatively small pressure difference.
  • the only basic requirement for the correct operation of the hydraulic control device is that the pressure prevailing in the inlet line is always greater than the pressure in the outlet line, so that the pressure required at the control connection of the pilot valve, which must be greater than the pressure in the outlet line, is generated and that the pressure in the drain line also loads the orifice element against the pressure from the control connection of the pilot valve.
  • the aperture size in the blend selected with the adjusted actuating force of the actuator is thus automatically held without a separate displacement pick-up device in the event of pressure changes in the inlet and / or outlet line. Because the pilot valve only the low Has to process pressure difference, it can work practically with zero coverage and regulate the pressure fluctuations very sensitively and still respond quickly when switching the control device on and off.
  • the most fundamental advantages of this training are the possibility of using a relatively weak actuator even at high pressures and large delivery rates, and the possibility of using a simple and therefore inexpensive pilot valve without an expensive displacement device.
  • a useful embodiment is further evident from claim 2.
  • a commercially available pressure reducing valve can be used in a particularly useful and cost-saving manner; it only needs to be connected to the tank line with the drain line.
  • the embodiment of claim 3 is also expedient because the zero position spring ensures that the pilot valve automatically assumes its zero position when the device is switched off and its valve element does not get caught in an intermediate position.
  • the features of claim 6 are important since the orifice then automatically assumes its full open position when the pilot valve is in the zero position.
  • control device creates a load-compensated flow control valve device with the pressure compensator, which is characterized by compact external dimensions and only a few individual parts.
  • the diaphragm with the control device forms the regulating diaphragm of the pressure compensator in this embodiment.
  • the pressure compensator also ensures that the pressure in the supply line is always higher.
  • an aperture 1 is shown schematically, which is housed in a housing, not shown.
  • An annular channel 2 is provided in the housing as part of an orifice chamber 6, from which an outlet channel 3 is led downward.
  • An inlet line 4 leads to the ring channel 2.
  • An outlet line 5 leads away from the outlet channel 3.
  • a diaphragm element 7 in the form of an diaphragm piston is slidably guided, which has radially distributed passages 8.
  • the diaphragm element 7 is urged upwards by a spring 9 in FIG. 1.
  • the diaphragm element 7 divides the diaphragm chamber 6 into an upper chamber 10 and a lower chamber 11.
  • the passages 8 define with their edges, together with boundary edges 13 of the ring channel 2, an diaphragm opening 14, the size of which can be changed depending on the stroke position of the diaphragm element 7.
  • a channel 15 opens into the chamber 10.
  • a control line 16 is connected to the inlet line 4, which leads into a hydraulic control device 17, indicated by dashed lines, which is connected via a line 18 to the channel 15 and via a line 19 to the outlet line 5.
  • a separate and externally supplied control line could also be provided.
  • the size of the diaphragm opening 14 is reduced. In the lower end position of the panel element 7, the panel opening 14 is closed. In the upper end position of the panel element 7, however, the full size of the panel opening is open.
  • the hydraulic control device 17 includes a three-way pilot valve 20, which can be a conventional pressure reducing valve of simple design.
  • a valve element of the three-way pilot valve 20, designated 23, is acted upon in the upward direction by a weak zero-setting spring 21 and by pressure derived from the line 18 by means of a pilot line 22. This action is counteracted by the pressure derived from line 19 via a control line 25 at the upper end of valve element 23.
  • an actuator 24 acts on the valve element 23, which can be actuated externally to adjust its actuating force, which is directed downward, for example.
  • the actuator 24 is expediently a proportional magnet, the magnetic force of which changes in proportion to the current applied.
  • a pressure compensator 26 which ensures that the pressure in the inlet line 4 is always higher than in the outlet line 5. In this way, a total load-compensated flow control valve device created.
  • the hydraulic control device works as follows:
  • the spring 9 Before starting operation, the spring 9 has moved the diaphragm element 7 into the upper end position; the aperture 14 has its full size.
  • the actuator 24 has no actuating force.
  • the zero position spring 21 has shifted the valve element 23 into its upper end position (corresponding to the symbolic representation in FIG. 2); the connection from line 18 to line 19 is open.
  • the actuator 24 also sets a predetermined actuating force which corresponds to a certain size of the aperture 14.
  • the valve element 23 of the pilot valve 20 has moved downward, so that a pressure P X is built up from the line 16 with its pressure P A in the control connection of the pilot valve 20, which loads the orifice element 7 via the line 18 and moves it downward, so that the aperture 14 is gradually closed.
  • the pressure B building up until then in the discharge line 5 generates in the line 19 the pressure P B which , via the control line 25 together with the actuating force of the actuator 24, loads the valve element 23 downward, so that there is between the pressure P X and the Pressure P B sets a pressure difference that is exactly proportional to the actuating force of the actuator 24.
  • the diaphragm element 7 Under the force of the spring 9 and with the pressure B in the line L, the diaphragm element 7 is held in a predetermined lifting position in which the predetermined diaphragm opening size is set. There is an equilibrium state.
  • valve element 23 is also moved slightly downward via the control line 25, so that the pressure P X in the pressure P A Line 18 is increased accordingly until the set size of the aperture 14 is held again.
  • control device 17 determines whether the amount of pressure medium flowing through the orifice 14 is kept constant or the pressure drop. This is also irrelevant for many applications, but what is crucial is maintaining a certain size Diaphragm opening 14. If the quantity should also be kept constant, the pressure compensator 26 can be used in the usual way.
  • FIG. 3 and 4 show two ways of forming the aperture.
  • Fig. 3 shows the aperture shown in Fig. 1 in a symbolic representation, wherein the spring 9 ensures that the aperture 1 assumes its full open position in the zero position.
  • the orifice assumes its full closed position in the zero position, in which the connection from the inlet line to the outlet line is interrupted.
  • the basic prerequisite for the proper functioning of the control device is that the pressure P A and thus the pressure in the inlet line 4 is greater than or equal to the sum of the pressure P B corresponding to the pressure B in the outlet line 5 plus the maximum pressure difference that the three-way Pilot valve 20 can process.
  • the pressure P X prevailing in the line 18 results from the sum of the pressure P B in the line 19 (corresponding to the pressure B in the discharge line 5) and the respective pressure difference of the three-way pilot valve 20, ie the pressure difference between the pressure P. X and the pressure P B.
  • the three-way pilot valve works practically without leakage losses in the zero position, so that it e.g. can easily be used with forklifts or forklifts.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Fluid Pressure (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Valve Device For Special Equipments (AREA)
EP87105284A 1986-04-15 1987-04-09 Dispositif de commande hydraulique Expired - Lifetime EP0241870B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87105284T ATE71191T1 (de) 1986-04-15 1987-04-09 Hydraulische steuervorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863612684 DE3612684A1 (de) 1986-04-15 1986-04-15 Hydraulische steuervorrichtung
DE3612684 1986-04-15

Publications (3)

Publication Number Publication Date
EP0241870A2 true EP0241870A2 (fr) 1987-10-21
EP0241870A3 EP0241870A3 (en) 1989-10-25
EP0241870B1 EP0241870B1 (fr) 1992-01-02

Family

ID=6298724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87105284A Expired - Lifetime EP0241870B1 (fr) 1986-04-15 1987-04-09 Dispositif de commande hydraulique

Country Status (7)

Country Link
US (1) US4744542A (fr)
EP (1) EP0241870B1 (fr)
JP (1) JP2667827B2 (fr)
AT (1) ATE71191T1 (fr)
DE (2) DE3612684A1 (fr)
ES (1) ES2029234T3 (fr)
GR (1) GR3003832T3 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709012A1 (de) * 1987-03-19 1988-09-29 Kuke Kg Fritz Schaltungsanordnung zur signalisierung eines anrufes fuer ein in ein digitales fernsprechnetz geschaltetes endgeraet
US5097857A (en) * 1991-08-02 1992-03-24 John Mayhew Electro-hydraulic valve-actuator system
GB9420394D0 (en) * 1994-10-10 1994-11-23 Trinova Ltd An hydraulic circuit controlling an actuator
US5654885A (en) * 1995-03-28 1997-08-05 Virginia Valve Company Corporation Valve position controller
US6354327B1 (en) 2000-07-31 2002-03-12 Virginia Valve Company Automatic position-control valve assembly
US8235163B2 (en) * 2004-09-28 2012-08-07 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Steering boost system
DE102014008648A1 (de) * 2014-06-13 2015-12-17 Hydac Technology Gmbh Anschlussvorrichtung
DE102016206092A1 (de) * 2016-04-12 2017-10-12 Robert Bosch Gmbh 3-Wege-Ventil
CN110725823B (zh) * 2019-10-11 2021-07-16 太原理工大学 一种基于压力飞升速率检测器的插装式两级比例调速阀

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2914196A1 (de) * 1979-04-07 1980-10-23 Rexroth Gmbh G L Ventil zum steuern von druckmittel
DE3047144A1 (de) * 1980-02-25 1981-09-10 Veb Kombinat Orsta-Hydraulik, Ddr 7010 Leipzig Hydraulisch gesteuerter einzelwiderstand in hydraulischen anlagen
DE3124904A1 (de) * 1980-07-04 1982-05-06 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid "stromventil mit einem hydraulisch verstellbaren drosselventil"

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD137615A1 (de) * 1978-07-06 1979-09-12 Ludwig Denk Einrichtung zur beruehrungslosen schaltstellungsueberwachung an hydraulischen oder pneumatischen ventilen
US4476893A (en) * 1980-07-04 1984-10-16 Barmag Barmer Maschinenfabrik Ag Hydraulic flow control valve
EP0073268B1 (fr) * 1981-09-02 1985-09-04 Vickers Systems GmbH Commande electro-hydraulique pour un piston d'actionnement

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2914196A1 (de) * 1979-04-07 1980-10-23 Rexroth Gmbh G L Ventil zum steuern von druckmittel
DE3047144A1 (de) * 1980-02-25 1981-09-10 Veb Kombinat Orsta-Hydraulik, Ddr 7010 Leipzig Hydraulisch gesteuerter einzelwiderstand in hydraulischen anlagen
DE3124904A1 (de) * 1980-07-04 1982-05-06 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid "stromventil mit einem hydraulisch verstellbaren drosselventil"

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
OELHYDRAULIK UND PNEUMATIK *
PATENT ABSTRACTS OF JAPAN *

Also Published As

Publication number Publication date
ES2029234T3 (es) 1992-08-01
DE3612684C2 (fr) 1988-09-29
JPS62269211A (ja) 1987-11-21
EP0241870A3 (en) 1989-10-25
JP2667827B2 (ja) 1997-10-27
EP0241870B1 (fr) 1992-01-02
DE3775594D1 (de) 1992-02-13
DE3612684A1 (de) 1987-10-22
US4744542A (en) 1988-05-17
ATE71191T1 (de) 1992-01-15
GR3003832T3 (fr) 1993-03-16

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