EP0837275A1 - Electrovanne d'évacuation de levage électrohydraulique - Google Patents

Electrovanne d'évacuation de levage électrohydraulique Download PDF

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Publication number
EP0837275A1
EP0837275A1 EP97117260A EP97117260A EP0837275A1 EP 0837275 A1 EP0837275 A1 EP 0837275A1 EP 97117260 A EP97117260 A EP 97117260A EP 97117260 A EP97117260 A EP 97117260A EP 0837275 A1 EP0837275 A1 EP 0837275A1
Authority
EP
European Patent Office
Prior art keywords
valve
magnet
spring
closing element
passage
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
EP97117260A
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German (de)
English (en)
Other versions
EP0837275B1 (fr
Inventor
Martin Dipl.-Ing. Heusser
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
Publication of EP0837275A1 publication Critical patent/EP0837275A1/fr
Application granted granted Critical
Publication of EP0837275B1 publication Critical patent/EP0837275B1/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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • F15B2013/008—Throttling member profiles

Definitions

  • the invention relates to a solenoid-operated drain valve according to the preamble of Patent claim 1.
  • the pilot valve is fully opened, so that the Load pressure with unloaded control chamber via a differential surface on the closing element lifts the closing element in the opening direction over the entire opening stroke.
  • the drain valve is at zero-current magnet on passage position.
  • the lifting and lowering movements are by means of controlled both valves.
  • the drain valve When lifting is at befindlichem in the load holding position Two-position switching valve, the drain valve by current loading of the magnet in set the closed position and the lifting speed controlled by the pump. To lower the drain valve to the closed position and the two-position switching valve placed in the deflation position, before the drain valve in the passage position is switched.
  • the interconnection principle can be with the Black / white drain valve when lowering no ramp function control as for Lift truck is desired.
  • the in the first case as a closing spring and in the second case as Opening spring for the pilot valve provided spring is soft in both cases, i.e. she has a spring characteristic without significant increase.
  • the nozzle and the passage of the pilot valve in view of a rapid response of the Drain valve as large as possible and, for example, designed with regard to the minimum discharge amount.
  • the closing element works exclusively with a seat function with the Main valve seat together to absolute in the closed position of the drain valve To ensure tightness. This tightness is required to ensure that the load pressure is maintained for a long time.
  • the invention is based on the object, a drain valve of the type mentioned to create that in a structurally simple and cost-effective way a ramp function allows for the control of lowering movements. It is aimed, despite the ramp function the proven and simple construction principle of the previous To maintain largely black / white drain valves. Furthermore, one, a clean Ramp function when lowering permitting drain valve are created, also is useful for larger and more expensive forklifts, which so far, for example, with a lifting module according to DE-C2-42 39 321 were equipped.
  • the manufacturing cost is low, so that the drain valve especially for Small and inexpensive forklift trucks are usefull which puts enormous pressure on prices subject.
  • the necessary stacker tightness or absolute tightness for holding the Load pressure remains.
  • the previously for the black and white drain valve concept used Magnet can be easily modified so that its force characteristic to the curve the hard spring fits.
  • the throttle and the passage can be the same size and should not be greater than 0.6 mm in practice. Conveniently, the throttle but smaller than the passage. In practice, for example, a throttle with a diameter of 0.4 mm a passage preceded by about 0.5 mm. Thereby a starting pressure and a hitching when lowering can be largely avoided.
  • the hard spring acts on the closing member in the closing direction the pilot valve, in the opening direction by the movable armature of the magnet is adjustable.
  • the closing member by the hard spring in the opening direction biased the pilot valve.
  • the closing member by the hard spring in the opening direction biased the pilot valve.
  • the gap is in the range of conventional slide fits.
  • a manufacturing technology favorable embodiment is apparent from claim 7.
  • Manufacturing technology is simpler embodiment according to claim 8, wherein a desirable low coverage for barely noticeable starting or hitching is achieved.
  • the ramp function using as many Components of the black / white drain valve achieved what the manufacturing cost the discharge valve for the ramp function favorably influenced. It is possible at the Black / white drain valve to replace only the spring and the closing member, and the Slightly modify the magnet to achieve the ramp function.
  • a rigid or hard spring with a steep characteristic used according to the invention is for example, a spring characterized by a force of 13N or more per mm Spring travel, while a soft spring with a flat characteristic, for example characterized by a force of 8N or less per mm travel.
  • a lifting module H of FIG. 1 for a forklift in the lifting movements of a Load by means of a cylinder Z in speed and extent by means of a pump P to be controlled, one of the driven by a motor M P to the cylinder Z running work line 1 on.
  • the pump P sucks from a tank T, in the one of the working line 1 branching drain line 5 with two sections 5a and 5b opens.
  • Another drain line 3 contains a system pressure relief valve 4. Between the discharge lines 3 and 5 is in the working line 1 in the direction to the pump P blocking check valve 2 classified. Between the sections 5a, 5b of the discharge line 5, a solenoid-operated discharge valve V is provided, and - as indicated by the parallel lines - a regulating discharge valve V.
  • FIG. 1 In the symbolic representation of FIG. 1 is a closing element of Discharge valve V indicated by 7, which by a spring 8 in the direction of the shown Closed position and adjustable by a magnet 6 in a passage position is.
  • the magnet 6 is excitable according to an arrow 9 with variable current, with the a ramp function is controlled.
  • the drain valve V is at de-energized magnet 6 in the closed position.
  • the ramp function can be sensitive when lowering from a standstill To control the load a gradual increase in speed and a gradual Deceleration to a standstill, essentially without noticeable Starting or hitchhiking.
  • a two-position switching valve V2 is provided in contrast to the embodiment of FIG. 1 between a branch 10 of the drain line 5 and the cylinder Z, which is switchable by a solenoid 11 from the shut-off position into the passage position (black / white).
  • Valve V2 The solenoid-operated shut-off valve V ', which is also a control valve, automatically holds the passage position (shown in FIG. 7) when the magnet 6 is de-energized and is actuated upon application of the magnet 6 with a variable current (arrow 9) while controlling the amount of pressure medium to be discharged into several positions or steplessly adjusted to the closed position.
  • a stepped bore 12 is provided, the the sections 5a and 5b of the discharge line 5 intersects.
  • A is the load pressure side indicated while B represents the discharge side to the tank T.
  • a sleeve-like insert 13 In the stepped bore 12 is positioned between the sections 5a and 5b, a sleeve-like insert 13, the a main valve seat S with a sharp (or possibly beveled) seat edge 14 contains.
  • To drain side B is followed by the seat edge, a cylindrical slide bore portion 15 on.
  • To the load pressure side A lead several unthrottled passages 17.
  • the insert 13 is by means of a screw-18 in the stepped bore 12 fixed, which carries the magnet 6.
  • the magnet 6 contains a coil 19, for adjusting a movable armature 20 (in Fig. 3 up) with variable Electricity can be applied.
  • the armature 20 has a bore 21 into which a hard spring 22 is engaged, which is supported in a stationary core of the magnet 6 is (spring abutment 23), and a plunger 24 in the bore 21 with bias applied to the bottom.
  • the plunger 24 has a head portion 25, on which the spring 22 rests, and in the in Fig. 3 shown closed position of the drain valve V on a shoulder 39 of the movable Ankers 20 sits.
  • the lower end of the plunger 24 is approximately conical designed and forms a closing member 26 of a pilot valve C.
  • the pilot valve C monitors the connection between a control chamber 27 at the top of a Closing element G and the drain side B and has a passage 29 in the closing element E on, which is designed as a cylindrical throttle bore. If necessary in the control chamber 27, a weak closing spring 40 for the closing element G. contain. At the passage 29, a larger axial bore 30 connects.
  • a throttle 28 is provided, for example in the form of a radial bore.
  • the throttle 28 is for example about 0.4 mm in size, while the passage 29 is about 0.5 mm in size.
  • the closing element G operates as a seat valve by means of a conical surface 31 with the seat edge 14 of the main valve seat S together.
  • a dilemmaneinstellvorraum E provided from the slide bore portion 15 in Extension of the main valve seat S in use 13 and a cylindrical Slider extension 32 in extension of the conical surface 31 of the closing element G consists and will be explained with reference to FIG. 6.
  • the spring 22 is a hard spring, i. you has a characteristic (Fig. 7, 36b) with considerable drop in the spring force F over the Deformation path s.
  • the spring provided at this point is a soft spring with a spring Characteristic curve 37b with a flat course (indicated by dot-dash lines).
  • the magnet 6 is in its force characteristic is matched to the spring characteristic curve 36b of the hard spring 22 in FIG. 3, to set exactly reproducible different positions of the plunger 24 to be able to.
  • the hard spring 22 keeps the pilot valve C closed.
  • the load pressure of the load pressure side A prevails on a Area of the closing element G that is larger than the area of the main valve seat S.
  • the load pressure holds the closing element G in the closed position shown, in the absolute Tightness is given, as well as the pilot valve C. Is used to initiate a Lowering the magnet 6 applied to a certain current, then the plunger 24 is raised to an intermediate position in which the closing member 26th from the passage 29 occurs.
  • the pressure in the control chamber 27 is reduced, so that the load pressure lifts the closing member G from the main valve seat S.
  • the slide approach 32 initially cooperates with the slide bore portion 15 to initially a small amount of pressure medium to flow out, in addition to the Pressure medium amount, which flows through the open pilot valve C.
  • the closing element G executes a game movement in which an equilibrium state occurs, in which, depending on any load pressure fluctuations, the pilot valve C just so far throttles that a certain opening position or Game movement of the closing element G results in the case of a predetermined amount of pressure medium flows to the tank T.
  • By amplifying the current for the magnet 6 of the plunger 24 positioned further up then follows the closing element G accordingly, until finally the overlap between the slide portion 32 and the slide bore portion 15 is released, and pressure fluid flows more strongly. With further increase of the current for the magnet, the closing element can be G finally adjust to the full passage position.
  • the armature 20 of the magnet 6 pushes the plunger 24 when it is excited downward.
  • the hard spring 22 is supported on a stationary abutment 23 'in one stationary anchor portion 20 'from and acts on the head portion 25 of the plunger 24 in Upward direction with a biasing force to open the pilot valve C.
  • the Magnet 6 is modified with respect to FIG. 3, so that it is energized the plunger 24 down in the closing direction of the pilot valve C, although optionally by means of an auxiliary tappet 24.
  • the further construction of the drain valve V ' corresponds to that described in Fig. 3, i. also the size and characteristic of the Magnet 6 is about the same.
  • the magnet 6 or the hard spring 23 is designed to that he or she in the closed position resulting from the surface of the passage 29 Force on the plunger 24 without noticeable jump to overcome. These Closing force results from the fact that the plunger 24 in the magnet 6 on all sides with the Pressure in the control chamber 27 is acted upon.
  • the closing element G takes its passage position a, since the hard spring 22 has placed the plunger 24 in the upper end position. Will the Magnet 6 is acted upon by a preselected current, then the plunger 24 against the force of the hard spring 22 with the closing member 26 in the passage 29 of the Closing element G adjusted. The control pressure in the control chamber 27 increases. The Closing element G is in the direction of its closed position on the main valve seat S adjusted. The flowing over the main valve seat S pressure medium quantity is throttled. In this case, the closing element G perform game movements to the Pilot valve C more or less open or close. When increasing the Current for the magnet 6, the plunger 24 is adjusted even further down.
  • the closing element G takes the final Closed position, in which the conical surface 31 on the seat edge 14 sealing seated. If then the current applied to the magnet is reduced again, then is on the initial opening stroke of the closing element G, the outflowing Pressure medium through the cooperation between the spool portion 32 and the spool bore portion 15 (FIG. 3). It settles on this How to control the lowering of the load with a ramp function.
  • the conical surface 31 of the closing element G is directly through the Spool piston extension 32 extended.
  • the spool bore portion 15 starts in a distance from the seat edge 14, which is predetermined by an extension 33.
  • a cover Ü which expediently may be less than 10% of the total opening stroke of the closing element G.
  • the overlap Ü is defined, for example, by the stepped transition between the widening 33 and the spool bore portion 15 and a lower one End edge 34 of the spool portion 32. It lies in this area Gap 35 sized in the manner of conventional slide fits, e.g. with 0.1 mm. Since the conical surface 31 in a lying outside of the spool piston portion 32 Area cooperates with the seat edge 14, the conical surface can be 31 and the spool portion 32 simply finished.
  • the conical surface 31 of the closing element G is for manufacturing reasons transferred over a groove-like constriction 38 in the spool portion 32, the with the a direct axial extension of the seat edge 14 forming Slider bore portion 15 cooperates.
  • the overlap Ü can be something to be taller.
  • the gap 35 is sized as specified.
  • the characteristic curve 36a for the hard spring 22 of the embodiment of FIG. 4 indicated, in comparison to the spring characteristic 37a of a usually in a black / white drain valve of this design used soft spring.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Magnetically Actuated Valves (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Fluid-Driven Valves (AREA)
EP97117260A 1996-10-15 1997-10-06 Electrovanne d'évacuation de levage électrohydraulique Expired - Lifetime EP0837275B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE29617922U DE29617922U1 (de) 1996-10-15 1996-10-15 Magnetbetätigtes Ablaßventil eines elektrohydraulischen Hubmoduls
DE29617922U 1996-10-15
US08/948,203 US6017015A (en) 1996-10-15 1997-10-09 Magnetically operated drain valve of an electrohydraulic lifting module

Publications (2)

Publication Number Publication Date
EP0837275A1 true EP0837275A1 (fr) 1998-04-22
EP0837275B1 EP0837275B1 (fr) 2002-04-17

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EP97117260A Expired - Lifetime EP0837275B1 (fr) 1996-10-15 1997-10-06 Electrovanne d'évacuation de levage électrohydraulique

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US (1) US6017015A (fr)
EP (1) EP0837275B1 (fr)
DE (1) DE29617922U1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19849877A1 (de) * 1998-02-28 1999-09-02 Continental Teves Ag & Co Ohg Elektromagnetventil
EP2270340A1 (fr) 2009-07-02 2011-01-05 HAWE Hydraulik SE Soupape hydraulique pilotée à siège
EP2392819A1 (fr) 2010-05-31 2011-12-07 HAWE Hydraulik SE Dispositif de réglage rotatif hydroélectrique des pales de rotor sur le rotor d'une éolienne
EP2466152A1 (fr) 2010-12-17 2012-06-20 HAWE Hydraulik SE Dispositif de commande hydroélectrique
DE102012002189B3 (de) * 2012-02-07 2013-05-16 Hydac Fluidtechnik Gmbh Ventil

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29706717U1 (de) * 1997-04-14 1997-07-17 Bürkert Werke GmbH & Co., 74653 Ingelfingen Breitbandventil
DE29713293U1 (de) 1997-07-25 1997-10-23 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Magnetbetätigtes Ablaßventil
JP3662159B2 (ja) * 2000-02-16 2005-06-22 株式会社テージーケー ソレノイド駆動パイロット弁
US6398182B1 (en) * 2000-08-31 2002-06-04 Husco International, Inc. Pilot solenoid control valve with an emergency operator
DE10343608B4 (de) * 2003-09-20 2015-01-08 Buchholz Hydraulik Gmbh Magnetbetätigtes Ventil
US7080817B2 (en) * 2004-02-17 2006-07-25 Y. Stern Engineering (1989) Ltd. Electromagnetic valve
DE102004039848A1 (de) * 2004-08-17 2006-03-09 Jungheinrich Ag Fluidschaltung und Flurförderzeug mit Fluidschaltung
US20070157980A1 (en) * 2006-01-11 2007-07-12 Husco International, Inc. Pilot operated control valve having a two stage poppet
DE102006027859B4 (de) * 2006-04-28 2015-05-21 Continental Teves Ag & Co. Ohg Elektromagnetventil
CN103429910B (zh) 2011-03-21 2016-10-26 丹佛斯公司 阀
CN103747887A (zh) * 2011-04-28 2014-04-23 丰永正一 轧制用的轧辊冷却剂阀
CN102213245B (zh) * 2011-07-15 2013-10-30 朱国胜 螺纹插装式电控双向压力补偿流量阀
CN102213242B (zh) * 2011-07-19 2013-12-11 宁波克泰液压有限公司 螺纹插装式电控液压锁
US9926178B2 (en) 2014-08-20 2018-03-27 Crown Equipment Corporation Actuator in a lift truck
US11788644B2 (en) * 2014-12-03 2023-10-17 Hydralectric Group Ltd Proportional valve, electric shower incorporating the proportional valve and tap incorporating same
ITUB20160518A1 (it) * 2016-01-28 2017-07-28 Bosch Rexroth Oil Control S P A Boccola di centraggio per valvole
CN107701534B (zh) * 2017-08-29 2019-12-06 潍柴动力股份有限公司 负荷传感压力补偿阀
US10781937B2 (en) * 2017-10-17 2020-09-22 Sun Hydraulics, Llc Actuator assembly and method of securing an actuator to a valve body
US11891928B2 (en) 2019-06-19 2024-02-06 The Oilgear Company Hydraulic valve with linear adjustable throttling gate and a hydraulic velocity fuse throttling gate

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1110895A (fr) * 1954-07-19 1956-02-17 Vannes électromagnétiques
US3977649A (en) * 1973-09-24 1976-08-31 Control Concepts, Inc. Normally closed solenoid operated valve assembly with relief function
GB2041169A (en) * 1979-01-30 1980-09-03 Automatic Switch Co Pilot-operated valve having varying bleed flow area
US5205531A (en) * 1992-04-09 1993-04-27 Sterling Hydraulics, Inc. Solenoid operated cartridge valve
DE4239321A1 (de) * 1992-11-23 1994-05-26 Heilmeier & Weinlein Elektrohydraulisches Hubmodul

Family Cites Families (2)

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Publication number Priority date Publication date Assignee Title
US5048790A (en) * 1990-07-18 1991-09-17 Target Rock Corporation Self-modulating control valve for high-pressure fluid flow
DE4330073A1 (de) * 1993-09-06 1995-03-09 Frutigen Hydrotechnik Ag Vorgesteuertes Hydraulikventil

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
FR1110895A (fr) * 1954-07-19 1956-02-17 Vannes électromagnétiques
US3977649A (en) * 1973-09-24 1976-08-31 Control Concepts, Inc. Normally closed solenoid operated valve assembly with relief function
GB2041169A (en) * 1979-01-30 1980-09-03 Automatic Switch Co Pilot-operated valve having varying bleed flow area
US5205531A (en) * 1992-04-09 1993-04-27 Sterling Hydraulics, Inc. Solenoid operated cartridge valve
DE4239321A1 (de) * 1992-11-23 1994-05-26 Heilmeier & Weinlein Elektrohydraulisches Hubmodul

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
HEILMEIER & WEINLEIN: "2/2-Wege-Magnet-sitzventile typ EM11 ... 31 zum einschrauben.", DATENBLATT D 7490/1, March 1996 (1996-03-01), MÜNCHEN, pages 1 - 4, XP002030878 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19849877A1 (de) * 1998-02-28 1999-09-02 Continental Teves Ag & Co Ohg Elektromagnetventil
EP2270340A1 (fr) 2009-07-02 2011-01-05 HAWE Hydraulik SE Soupape hydraulique pilotée à siège
EP2392819A1 (fr) 2010-05-31 2011-12-07 HAWE Hydraulik SE Dispositif de réglage rotatif hydroélectrique des pales de rotor sur le rotor d'une éolienne
EP2466152A1 (fr) 2010-12-17 2012-06-20 HAWE Hydraulik SE Dispositif de commande hydroélectrique
DE102012002189B3 (de) * 2012-02-07 2013-05-16 Hydac Fluidtechnik Gmbh Ventil

Also Published As

Publication number Publication date
US6017015A (en) 2000-01-25
DE29617922U1 (de) 1996-11-28
EP0837275B1 (fr) 2002-04-17

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