EP1203161B1 - Soupape de securite de presse - Google Patents

Soupape de securite de presse Download PDF

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Publication number
EP1203161B1
EP1203161B1 EP00960352A EP00960352A EP1203161B1 EP 1203161 B1 EP1203161 B1 EP 1203161B1 EP 00960352 A EP00960352 A EP 00960352A EP 00960352 A EP00960352 A EP 00960352A EP 1203161 B1 EP1203161 B1 EP 1203161B1
Authority
EP
European Patent Office
Prior art keywords
valve
working
valves
minimum
connection
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
EP00960352A
Other languages
German (de)
English (en)
Other versions
EP1203161A2 (fr
Inventor
Lothar GRÖTZINGER
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.)
Herion Systemtechnik GmbH
Original Assignee
Herion Systemtechnik 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 Herion Systemtechnik GmbH filed Critical Herion Systemtechnik GmbH
Publication of EP1203161A2 publication Critical patent/EP1203161A2/fr
Application granted granted Critical
Publication of EP1203161B1 publication Critical patent/EP1203161B1/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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/14—Control arrangements for mechanically-driven presses
    • B30B15/142—Control arrangements for mechanically-driven presses controlling the brake or the clutch
    • 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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/10—Delay devices or arrangements

Definitions

  • the invention relates generally to hydraulic safety valves and in particular a safety valve unit according to the preamble of claim 1.
  • Document DE-A-3008935 discloses a safety valve unit according to the preamble of claim 1.
  • Hydraulic safety valves of the affected here Type will be e.g. for controlling the brake and / or clutch used a mechanical press. That's how it is DE 38 17 123 A1 already a hydraulic valve became known for the aforementioned application, the by two electromagnetically operated pilot valves is controlled.
  • the valve also has two opposite directions mutually movable valve body with control piston on. By means of the control piston, the connections between a pump connection, two working connections and two tank connections controlled. at If there is a malfunction, the valve bodies go into a hydraulically locked end position.
  • Safety valves are exclusively in piston slide valve technology executed, whereby their maximum Flow rate is limited.
  • these valves require due to the required during a switching operation Piston strokes long switching times when coupling and Braking the press.
  • the invention is therefore based on the object, a Hydraulic valve arrangement of the type mentioned specify the shortest possible switching times of a mechanical consumer, in particular as short as possible Clutch and brake operations on a mechanical press, provides while still a possible ensures high operational safety.
  • the invention provides for a for the operation of a mechanical Consumer's suitable safety valve unit of the type mentioned, which means at least a pressure connection with a hydraulic Pressure source, by means of at least one working port with the hydraulic consumer and by means of at least a tank connection with a hydraulic fluid connected tank, and which at least having two working valves by means of at least an electrically controllable control valve are operable, the at least two working valves are designed as seat valves, and wherein the at least two work valves operated in opposite directions be, with the first working valve in the open state the pressure connection at least with the working connection connects and that the at least second working valve in the open state with the work connection the tank connection connects, in particular before, that the at least second working valve by means of a spring force is normally open.
  • the seat valve construction used in the valves mentioned allows in particular high flow rates and at the same time very short switching times of these valves, because of this design already low piston movements almost no time delay to large valve port cross sections to lead.
  • Fig. 1 shows a hydraulic valve assembly consisting from two assemblies, namely a safety valve unit 10 and a damping valve unit 20.
  • the two units 10, 20 are connected via a pressure connection 30 with a hydraulic pump 40, via a tank connection 50 with a hydraulic fluid tank 60 and over a working connection 70 with a mechanical consumer, one for operation in the present example a (not shown here) mechanical Press provided clutch and / or brake piston 80, connected hydraulically or pressure-conducting.
  • On the hydraulic fluid it does not matter here; it may therefore be either a gas or a liquid.
  • the safety valve unit 10 has a first in Seat valve design trained 2/2-way valve 90, in which a reaching into a valve chamber 100 Piston 105 with one on the inside of the valve housing trained annular surface forms a valve seat 110.
  • This valve seat 110 connects or disconnects one from the pressure port 30 outgoing pressure line 120th with an outgoing from the work port 70 working line 130.
  • the two lines 120, 130 are in interrupted in the present operating state (closed).
  • An active movement of the piston 105 to operate the Valve 90 is also hydraulic, via a (Valve) control chamber 115.
  • the directional control valve 90 also has a designed as an inductive switch proximity switch (S3) 95, by means of which the operating state the directional control valve 90 can be sensed.
  • valves 140, 150 are also trained in poppet design 2/2-way valves 140, 150 are provided, in which on an inner annular surface 160, 170 about to concern upcoming piston 155, 165 form a valve seat, and in the currentless operating state shown by means of Spring preloads 180, 190 are open. Therefore, find the directional valves 140, 150 in particular in the case of Energy failure in the safe "open" position, in which the working line 130 is relieved. Also at These valves 140, 150, the piston 155, 165 hydraulically moved via control chambers 162, 175 (active). In addition, the directional valves 140, 150 each have one Proximity switch 145, 155 with the above Functionality on.
  • the directional control valves 90, 140, 150 by each via the control chambers 115, 162, 175 driven Movements of the pistons 105, 155, 165 connected.
  • the control chambers 115, 162, 175 are to this Purpose to a dashed line in the drawing hydraulic control line system 225 connected.
  • the safety valve unit 10 also has two as 4/2-way valves formed pilot valves 230, 240th on, connected by means of electromagnets 235, 245 become.
  • the pilot valves 230, 240 connect either (as shown here) the control chamber 115 of the first Directional valve 90 with the pressure line 120, and thus also the pump 40, and the control chambers 162, 175 of the directional control valves 140, 150 with the tank line 220, and so also the tank 60. In a (not shown here) Cross position, however, the control chamber 115 with the tank line 220 and the control chambers 162, 175 with the pressure line 227 connected.
  • the damping valve unit 20 has a proportional pressure relief valve 250 on, by means of a spring preload normally closed and that over one Control current is controlled or opened. Thereby is guaranteed that even with an electric Power failure the press via the clutch or brake piston 80 can be braked soft.
  • a proportional pressure reducing valve 260 allows a Pressure modulation during soft coupling and different Pressure levels when engaging the press by means of Clutch piston 80.
  • a pressure limiting valve 270 serves for maximum pressure protection the driven by the clutch piston 80 Clutch.
  • the pressure limiting valve 270 prevents too high actuating pressure in the coupling, for example, by a faulty control of the proportional pressure reducing valve 260 could arise.
  • the damping valve unit also has a Spring accumulator 290, which provides a permanent back pressure in the tank line, in particular during a soft braking phase, guaranteed and thus a more controlled Braking the press allows.
  • the electromagnets 235, 245 of the pilot valves 230 and 240 de-energized.
  • the directional control valves 140 and 150 switch by means of the respective spring preload 180, 190 in the open position, wherein the inductive switch 145 and 155 be damped.
  • the directional control valve 90 is in the Basic position closed and its inductive switch 95 undamped.
  • the transmitted via the pressure line 120 pump pressure acts accordingly on the annular surface of the valve piston 105th of the directional valve 90.
  • the pilot valves 230, 240, the directional control valve 90 due to the area difference the two sides of the piston in the closed Held position.
  • the proximity switch 95th the closed i. acknowledge undamped position. Accordingly, the proximity switches 145 and 155 must S2 the present opened, i. damped position Acknowledge.
  • the electromagnets 235, 245th the two pilot valves 230, 240 energized. Thereby becomes the directional control valve 90 leading part of the control line 225 relieved to the tank 60 down. In addition will be the directional valves 140 and 150 closed.
  • the Switching position is the pump connection 30 with the working connection 70 connected. The connection between the Work port 70 and the tank port 50 is, however, blocked.
  • the proximity switches are switched 145, 155 and 95 cyclically checked.
  • the hydraulic generated by the clutch / brake combination Switching volume now flows through the proportional pressure relief valve 250 in the tank 60 from. Short before the brake closes, the current at the proportional pressure relief valve 250 lowered again, so that in leading to the work terminal 70 line build up a pressure. This soft brake pressure acts in the type of backpressure and causes the Soft braked press. The height of the soft brake pressure is determined by the modulation of the proportional pressure relief valve 250 determined.
  • the damping valve unit therefore allows optimization the start and stop process of the press and thus ensures high security for the entire Production facility. In addition, it can be lower the operating noise level of the press and the reduce mechanical load on the press drive, resulting in longer service life of the production facility leads.
  • FIG. 1b shows a valve arrangement corresponding to FIG. 1a different with respect to FIG. 1a formed damping valve unit 20, however with a matching safety valve unit 10.
  • FIG. 1a shows a valve arrangement corresponding to FIG. 1a different with respect to FIG. 1a formed damping valve unit 20, however with a matching safety valve unit 10.
  • Regarding the features and function (s) of the safety valve unit is therefore completely on refer to the comments on Fig. 1a.
  • a directional valve 310 formed way valve 300 provided to the pressure relief valve 250th is connected in parallel.
  • the directional control valve 300 is over a pilot valve 330 is driven. Due to the seat valve design be, similar to the way valves 140 and 150, high flow rates and shorter switching times when braking, especially in the danger area of Press, possible.
  • the directional control valve 300 is in the de-energized Condition is opened by a spring force 320 and is located in the basic position, especially in the Fall of a power failure, in the open position.
  • the open position of the directional valve 300 allows in addition, a very fast switching and very effective EMERGENCY STOP or fast braking of the press (via the piston 80), as one in the working line 130th about existing hydraulic pressure over the lines 223, the tank line 220, and in particular on the Routing 222 are reduced almost instantaneously can.
  • Another advantage of the seat valve construction of the directional control valve 300 is that the damping valve unit 20 directly over the valve seat 310 of the directional control valve 300 can be monitored, resulting in a particularly high Ensured safety with respect to the damping behavior is.
  • valve arrangement according to the invention not only advantageous for mechanical presses can be used, but wherever large Masses by means of a hydraulically operated clutch and / or brake are moved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Control Of Presses (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (6)

  1. Unité de soupapes de sécurité pour actionner un consommateur (80) hydraulique, laquelle est reliée à une source de pression (40) hydraulique par l'intermédiaire d'au moins un raccord de pression (30), au consommateur (80) hydraulique par l'intermédiaire d'au moins un raccord de travail (70) et à un réservoir (60) contenant un fluide hydraulique à l'aide d'au moins un raccord de réservoir (50), et
    l'unité de soupapes présente au moins deux soupapes de travail (90, 140) qui peuvent être actionnées à l'aide d'au moins une soupape de distribution (230) à commande électrique, les au moins deux soupapes de travail (90, 140) étant conçues sous forme de soupapes à siège (110, 170) et les au moins deux soupapes de travail (90, 140) étant actionnées en sens contraire, la première soupape de travail (90) à l'état ouvert relie le raccord de pression (30) au moins au raccord de travail (70), et
    l'au moins deuxième soupape de travail (140) à l'état ouvert relie le raccord de travail (70) au raccord de réservoir (50),
    caractérisée en ce que
    l'au moins deuxième soupape de travail (140) est ouverte sans courant à l'aide d'une force de ressort (180).
  2. Unité de soupapes de sécurité selon la revendication 1,
    caractérisée en ce que
    les au moins deux soupapes de travail (90, 140) prennent la forme de soupapes à 2/2 voies et l'au moins une soupape de distribution (230) d'une soupape à 4/2 voies, l'au moins une soupape de distribution (230) relie alors les chambres de piston des au moins deux soupapes de travail (90, 140) dans le sens contraire au raccord de pression (30) et au raccord de réservoir (50).
  3. Unité de soupapes de sécurité selon la revendication 1 ou 2,
    caractérisée en ce que
    les au moins deux soupapes de travail (90, 140) peuvent être actionnées par la même au moins une soupape de distribution (230).
  4. Unité de soupapes de sécurité selon l'une des revendications précédentes,
    caractérisée en ce que
    on prévoit au moins deux deuxièmes soupapes de travail (140) sous forme de soupape à 2/2 voies montées en parallèle.
  5. Unité de soupapes de sécurité selon l'une des revendications précédentes,
    caractérisée en ce que
    la première soupape de travail (90) est commandée à retardement par rapport à l'au moins deuxième soupape de travail (140).
  6. Unité de soupapes de sécurité selon l'une des revendications précédentes,
    caractérisée en ce que
    les au moins deux soupapes de travail (90, 140) ont chacune une détection inductive de position commutée (95, 145).
EP00960352A 1999-08-13 2000-08-11 Soupape de securite de presse Expired - Lifetime EP1203161B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19937866 1999-08-13
DE19937866 1999-08-13
PCT/DE2000/002749 WO2001012997A2 (fr) 1999-08-13 2000-08-11 Soupape de securite de presse

Publications (2)

Publication Number Publication Date
EP1203161A2 EP1203161A2 (fr) 2002-05-08
EP1203161B1 true EP1203161B1 (fr) 2005-05-25

Family

ID=7917936

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00960352A Expired - Lifetime EP1203161B1 (fr) 1999-08-13 2000-08-11 Soupape de securite de presse

Country Status (5)

Country Link
EP (1) EP1203161B1 (fr)
JP (1) JP2003507664A (fr)
DE (1) DE50010408D1 (fr)
ES (1) ES2243299T3 (fr)
WO (1) WO2001012997A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103047207A (zh) * 2012-12-24 2013-04-17 中联重科股份有限公司 分合流阀组、液压系统、负载敏感式液压系统及工程机械
DE102021005824A1 (de) 2021-11-24 2023-05-25 Hydac International Gmbh Sicherheitsventilvorrichtung

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1275854A1 (fr) 2001-07-09 2003-01-15 Herion Systemtechnik GmbH Méthode et dispositif hydraulique de commande pour la protection contre les surcharges d'une presse mécanique actionnée par une combinaison embrayage-frein
CN102094861B (zh) * 2010-12-02 2013-04-10 徐州重型机械有限公司 一种用于起重机的多泵合流液压系统及其合流阀组
CN104154056B (zh) * 2014-07-30 2016-05-04 宁波恒力液压股份有限公司 一种具有互锁功能的大流量液压换向回路
IT201900002599A1 (it) * 2019-02-22 2020-08-22 Bosch Gmbh Robert Sistema valvola di ritegno a controllo elettronico

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
DE2033736C3 (de) * 1970-07-08 1978-03-30 Klaus 7300 Esslingen Huegler Universalsteuerblock für flüssige oder gasförmige Medien
JPS5424393Y2 (fr) * 1975-06-05 1979-08-17
DE3008935A1 (de) * 1980-03-08 1981-09-24 Aktiebolaget Arosverken, Västerås Steuereinrichtung fuer eine exzenterpresse
DE3023890A1 (de) * 1980-06-26 1982-01-14 Udo Ing.(grad.) 7148 Remseck Leikauf Ventil
JPS59172801U (ja) * 1983-05-06 1984-11-19 株式会社日立製作所 油圧回路
DE3523163A1 (de) * 1984-07-19 1986-02-13 ZF-Herion-Systemtechnik GmbH, 7990 Friedrichshafen Druckbeeinflussungseinrichtung fuer eine hydraulisch betaetigbare kupplung und/oder bremse der antriebswelle einer presse
DE3817123A1 (de) 1988-05-19 1989-11-30 Herion Werke Kg Sicherheitsventil
DE4312283A1 (de) * 1993-04-15 1994-10-20 Paals Packpressen Fabrik Gmbh Steuerung für ein hydraulisches Hochleistungsstellglied
GB9315778D0 (en) * 1993-07-30 1993-09-15 Pridham Peter W Proportional control hydraulic valves
US5494075A (en) * 1994-06-20 1996-02-27 Northrop Grumman Corporation Hydraulic time delay valve
DE19620468A1 (de) 1996-05-21 1997-11-27 Herion Technomatic Ag Aesch Verfahren und Vorrichtung zum Überwachen der Funktionsabläufe in einem Ventil

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103047207A (zh) * 2012-12-24 2013-04-17 中联重科股份有限公司 分合流阀组、液压系统、负载敏感式液压系统及工程机械
CN103047207B (zh) * 2012-12-24 2015-04-29 中联重科股份有限公司 分合流阀组、液压系统、负载敏感式液压系统及工程机械
DE102021005824A1 (de) 2021-11-24 2023-05-25 Hydac International Gmbh Sicherheitsventilvorrichtung
DE102021005824B4 (de) 2021-11-24 2023-08-10 Hydac International Gmbh Sicherheitsventilvorrichtung

Also Published As

Publication number Publication date
EP1203161A2 (fr) 2002-05-08
DE50010408D1 (de) 2005-06-30
JP2003507664A (ja) 2003-02-25
ES2243299T3 (es) 2005-12-01
WO2001012997A2 (fr) 2001-02-22
WO2001012997A3 (fr) 2001-09-27

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