EP1032375A1 - Distributeur hydraulique - Google Patents

Distributeur hydraulique

Info

Publication number
EP1032375A1
EP1032375A1 EP99969674A EP99969674A EP1032375A1 EP 1032375 A1 EP1032375 A1 EP 1032375A1 EP 99969674 A EP99969674 A EP 99969674A EP 99969674 A EP99969674 A EP 99969674A EP 1032375 A1 EP1032375 A1 EP 1032375A1
Authority
EP
European Patent Office
Prior art keywords
piston
chamber
valve
consumer
magnet
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
EP99969674A
Other languages
German (de)
English (en)
Other versions
EP1032375B1 (fr
Inventor
Willy Kussel
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.)
Tiefenbach Bergbautechnik GmbH
Original Assignee
Tiefenbach Bergbautechnik 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 Tiefenbach Bergbautechnik GmbH filed Critical Tiefenbach Bergbautechnik GmbH
Publication of EP1032375A1 publication Critical patent/EP1032375A1/fr
Application granted granted Critical
Publication of EP1032375B1 publication Critical patent/EP1032375B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • 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
    • F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
    • F15B19/005—Fault detection or monitoring
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/008—Valve failure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8158—With indicator, register, recorder, alarm or inspection means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86919—Sequentially closing and opening alternately seating flow controllers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor

Definitions

  • the invention relates to a hydraulic directional control valve, the control piston (main piston 3) against the force of a spring (main spring 18) by the plunger of a magnet (12) from its first position (closed position) to its second position (open position) is adjustable according to the preamble of Claim 1.
  • the pressure chamber (7), into which the pump connection (P) opens is closed with respect to the consumer chamber, while the consumer chamber with the consumer is opened with respect to the return chamber (20) and the tank connection (R) are so that the consumer is relieved of pressure.
  • the open position the consumer is connected to the pump connection, while the pressure chamber is closed off from the return chamber and the tank.
  • This valve is particularly suitable as a pilot valve for a hydraulic valve that is actuated hydraulically.
  • the object of the invention is to design this valve so that it is suitable as a pilot valve in the smallest size and has a positive overlap with regard to the closing of the consumer chamber with respect to the return and the opening of the consumer chamber with respect to the pressure chamber.
  • the solution according to claim 1 has the advantage that the valve housing does not have to provide any connections between the return duct and the consumer duct.
  • the valve can therefore be accommodated in a valve cartridge in particular (claim 4).
  • the plunger piston is pressed into its open position by a safety spring against the force of the magnet , so that the central channel is open in the closed position of the main piston.
  • Claim 3 provides a secure, leak-free closure between the pressure chamber and the consumer chamber (8).
  • the manufacturing advantages of the training according to claim 4 combine with a good adjustment for the coverage and the opening width of the connection between the consumer and return.
  • the sealing end of the main piston which projects into the consumer chamber is preferably designed as a cone pairing according to claim 5.
  • the embodiment according to claim 6 and claim 7 has the advantage that the pressure chamber is closed leakage-free with respect to the consumer room and control connection.
  • Hydraulic directional valves which are used as pilot valves and are controlled electromagnetically, must offer a high level of safety in many areas of application (e.g. in hoists or in mining).
  • a current control device is integrated in the control device of the magnet.
  • the current control device is preferably located on or in the area of the magnet.
  • the current control device has an electronic memory. Characteristic values are stored in the memory which ideally characterize the current consumption of the magnet during the switching process when switching to one of the switching positions.
  • the actual course of the current consumed by the magnet when the valve is switched to the switch position and / or when the magnet is switched off is measured and at least prominent points of the actual course or the entire actual course are compared and signaled with the corresponding points of the desired course or with the desired course.
  • the error message is signaled on the valve itself, in particular by means of an optical signal (claim 9).
  • the advantage of the design according to claim 11 is that not every deviation is signaled, but it can be determined beforehand by experiment which deviations are within the permissible functional tolerances. It is essential for the function of a pilot valve that, on the one hand, sufficient holding forces act on the valve piston in order to securely position the piston in its approached switching position. On the other hand, power consumption should be minimized. In the case of an electrohydraulic pilot valve or directional valve, this is achieved by training or further development according to claim 12. In addition, the current profile of the magnet can be measured during the switching process and the reaching of the switching position can be detected by the current control device.
  • the current is substantially increased once again to the highest level passed during the switching process and then reduced to the level required to maintain the switching position.
  • this also happens with directional valves that have several switching stages located one behind the other in the switching path. On the one hand it is achieved that the valve piston reaches its switching position safely and with sufficient holding force. On the other hand, however, it is prevented that the magnet is subjected to current up to saturation and is thereby stressed, in particular heated, beyond what is necessary. The power consumption and especially the current peaks are limited to the necessary amount.
  • Fig.1 a hydraulically controlled directional valve, which is by an electro-hydraulic
  • Fig.2 the electro-hydraulic pilot valve
  • Fig. 3 the current consumption when switching the pilot valve
  • the main valve, electro-hydraulic control valve 15, has an electromagnetically controlled pilot valve.
  • the pilot valve has a valve housing (outer housing 1) which fits into a valve body (pilot valve 14, only visible in FIG. 1) can be installed.
  • An essentially hollow cylindrical valve housing can be screwed into the outer housing 1 and screwed in zones by means of outer seals 22 and 23.
  • the main piston, valve piston 3 is slidably guided at one end and sealed against the end space of the cartridge by a seal 16.
  • the end space forms the return chamber 20, which is connected to the return R of the valve leading to the tank.
  • a plunger piston 4 is slidably mounted and sealed to the outside by a seal 17.
  • the plunger piston 4 projects into the control chamber 8, which is formed in this area of the outer housing 1 and in the cartridge 2.
  • the control chamber 8 is closed off from the pump connection chamber 7 by an inner collar which forms a seat 5.
  • the main piston 3 has a seat collar 6 which interacts with the seat 5 of the cartridge and forms the seal between the one side of the consumer chamber, control chamber 8, and the other side of the pump connection chamber 7.
  • the pump connection chamber 7 is delimited on the other side by the seal 16, which on the other hand delimits the return chamber 20.
  • the main piston 3 has a connecting channel (central channel 21) which connects the return chamber 20 on the one hand and the control chamber 8 on the other hand.
  • the plunger piston 4 projects with its free end into the consumer chamber, control chamber 8.
  • control chamber 8 In the consumer chamber, control chamber 8, the closing end 9 of the valve piston and the plunger piston 4 interact by combining an inner and an outer cone.
  • the seat end 10 of the main piston 3 is designed as an outer cone 9 and the facing end 10 of the tappet piston 4 as an inner cone 10.
  • the control chamber 8 can thus be connected to the return chamber 20 or separated therefrom.
  • the tappet 11 of the tappet piston 4 interacts with the (not shown) tappet of the magnet 12, which is controlled by the electrical control connection 13.
  • the main piston 3 is pressed with its seat collar 6 against the seat 5 by the main spring 18, which is supported on the end face of the pump connection chamber 7 in the region of the seal 16.
  • the cross-sectional areas of the seat 5/6 and the piston end of the The main piston 3 at the other end of the pressure chamber 7 essentially correspond, so that the main piston is pressure-balanced and is pressed against the seat 5 only by the main spring 18.
  • the plunger piston can be loaded by a safety spring 19 in the sense of lifting off from the seat end 9 of the main piston 3.
  • the safety spring 19 is supported on the one hand on the inner collar 5 of the cartridge and on the other hand on a collar of the plunger piston 4.
  • the pressure chamber 7 is closed off from the control chamber 8 by the main spring 18 pressing the main piston 3 with the seat collar 6 against the seat 5. Since the tappet piston is not loaded by the magnetic tappet, the safety spring 19 presses the tappet piston 4 against the end face of the control chamber 8 or against a stop (not shown) of the magnetic tappet.
  • the control chamber 8 is connected to the return chamber 20 via the central channel 21 and is therefore relieved of pressure. The main valve thus has its starting position.
  • the control device 25 contains a memory in which one or more of the points 31-38, but in particular the peak values, limit values and limit ranges are stored. These limit values / limit ranges have been determined beforehand by experiment and establish the target values and the permissibility limits. That means: as long as the current occurring during the switching process does not exceed these limit values, it can be assumed that the valve and all of its parts perform their function properly. However, if the current exceeds maximum values or falls below minimum values, this is a sign that the valve is faulty, e.g. is stuck due to chips or has become leaky due to wear.
  • the control device detects a deviation of the actual values from the stored target values or the limit ranges are exceeded in this way, a warning signal is issued.
  • this warning signal In mining or other large systems, it can be advantageous to signal this warning signal to the central control station.
  • the warning signal For the optical monitoring of a hydraulic system, on the other hand, it can be advantageous if the warning signal also appears on the valve, for example as a red lamp.

Abstract

Le distributeur hydraulique contient un piston de commande (piston principal 3) qui se règle à l'encontre d'une force d'un ressort (ressort principal 18) par le poussoir d'un aimant (12) de sa première position (position de fermeture) à sa deuxième position (position d'ouverture). Dans la position de fermeture, la chambre de pression (7) est fermée par le raccord de pompe (P) vis-à-vis de la chambre de consommateur (8) et la chambre de consommateur est ouverte par le consommateur (A) vis-à-vis de la chambre de retour (20) et du raccord de réservoir (R). Dans la position d'ouverture, la chambre de consommateur (8) est fermée vis-à-vis de la chambre de retour (20). A cet effet, la chambre de consommateur (8) et la chambre de retour (20) sont placées aux extrémités opposées du piston principal (3), notamment la chambre de consommateur (8) est placée sur la face orientée vers l'aimant et la chambre de retour (20) sur la face opposée à l'aimant. Le piston principal est traversé par un canal central (21) qui relie la chambre de consommateur (8) et la chambre de retour (20). Le poussoir d'aimant agit sur un piston de poussoir qui se déplace dans le boîtier de soupape de façon coaxiale avec le piston principal, et il présente une extrémité de contact tournée vers le piston principal (3) par laquelle il ferme le canal central lorsqu'il arrive en butée contre le piston principal.
EP99969674A 1998-09-28 1999-09-14 Distributeur hydraulique Expired - Lifetime EP1032375B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19844184 1998-09-28
DE19844184 1998-09-28
PCT/EP1999/006807 WO2000018382A2 (fr) 1998-09-28 1999-09-14 Distributeur hydraulique

Publications (2)

Publication Number Publication Date
EP1032375A1 true EP1032375A1 (fr) 2000-09-06
EP1032375B1 EP1032375B1 (fr) 2005-07-13

Family

ID=7882331

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99969674A Expired - Lifetime EP1032375B1 (fr) 1998-09-28 1999-09-14 Distributeur hydraulique

Country Status (4)

Country Link
US (1) US6263913B1 (fr)
EP (1) EP1032375B1 (fr)
DE (2) DE19943828A1 (fr)
WO (1) WO2000018382A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110925452A (zh) * 2019-12-03 2020-03-27 中铁五局集团第一工程有限责任公司 一种基于bim的工程供水系统

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GB2391287B (en) * 2002-07-30 2004-11-03 Lotus Car Control valve for controlling flow of hydraulic fluid
JP3994871B2 (ja) * 2002-12-19 2007-10-24 いすゞ自動車株式会社 圧力比例制御弁
AU2003207057A1 (en) * 2003-02-12 2004-09-06 Isuzu Motors Limited Flow control valve
JP4406292B2 (ja) * 2004-01-20 2010-01-27 株式会社フジキン 流体通路のウォータハンマーレス開放方法及びこれを用いたウォータハンマーレス開放装置
US7225830B1 (en) 2005-02-09 2007-06-05 Kershaw Charles H Fluid control valve
EP2202387B1 (fr) * 2008-12-23 2012-08-22 Techspace Aero S.A. Vanne d'isolation du circuit d'huile sans commande dans un moteur d'avion
DE102009032374B3 (de) * 2009-07-08 2010-12-30 Pierburg Gmbh Druckregelventil
WO2011144242A1 (fr) * 2010-05-20 2011-11-24 Pierburg Pump Technology Gmbh Soupape de régulation de pression
ITMI20101516A1 (it) * 2010-08-06 2012-02-07 Dropsa Spa Dispositivo di lubrificazione minimale perfezionato
ITMI20101517A1 (it) 2010-08-06 2012-02-07 Dropsa Spa Dispositivo di lubrificazione minimale con regolazione fine del flusso di olio
FR2966507B1 (fr) * 2010-10-20 2015-03-20 Turbomeca Dispositif de lubrification avec vanne de derivation
DE102011086655A1 (de) * 2011-11-18 2013-05-23 Zf Friedrichshafen Ag Ventilvorrichtung eines Hydrauliksystems zum Betätigen wenigstens eines Schaltelementes einer Getriebeeinrichtung
DE102018111601B4 (de) * 2018-05-15 2020-09-24 Prominent Gmbh Membrananlagensteuerung mit magnetisch gehaltenem Verschlusselement
CN110567705B (zh) * 2019-07-26 2021-03-23 中国北方车辆研究所 一种基于浮动盘的配流摩擦副性能模拟试验装置

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Cited By (2)

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Publication number Priority date Publication date Assignee Title
CN110925452A (zh) * 2019-12-03 2020-03-27 中铁五局集团第一工程有限责任公司 一种基于bim的工程供水系统
CN110925452B (zh) * 2019-12-03 2021-06-04 中铁五局集团第一工程有限责任公司 一种基于bim的工程供水系统

Also Published As

Publication number Publication date
DE19943828A1 (de) 2000-04-13
WO2000018382A2 (fr) 2000-04-06
US6263913B1 (en) 2001-07-24
WO2000018382A3 (fr) 2000-08-10
EP1032375B1 (fr) 2005-07-13
DE59912263D1 (de) 2005-08-18

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