EP3126722A1 - Soupape de régulation de pression proportionnelle - Google Patents

Soupape de régulation de pression proportionnelle

Info

Publication number
EP3126722A1
EP3126722A1 EP15707880.9A EP15707880A EP3126722A1 EP 3126722 A1 EP3126722 A1 EP 3126722A1 EP 15707880 A EP15707880 A EP 15707880A EP 3126722 A1 EP3126722 A1 EP 3126722A1
Authority
EP
European Patent Office
Prior art keywords
armature
characteristic curve
consumer
pressure
control
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.)
Withdrawn
Application number
EP15707880.9A
Other languages
German (de)
English (en)
Inventor
Philipp Hilzendegen
Peter Bruck
Frank Schulz
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik 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 Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP3126722A1 publication Critical patent/EP3126722A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • F16K3/34—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor

Definitions

  • the invention relates to a proportional pressure control valve with a longitudinally movable in a valve housing controlled piston, which serves by means of an actuating system for selectively connecting existing in the valve housing connection points, such as a pressure supply port, a consumer port and a tank or return port, wherein a first characteristic curve between a control signal the actuation system and the flow volume or the control pressure, based on a connectable to the consumer terminal consumer is made.
  • proportional pressure control valves are known, for example under the order designation PDMC04S30D according to content of Fig. 1 of the attached specific description.
  • the known solution is a directly controlled 3-way proportional pressure control valve.
  • the pump or pressure supply connection In the de-energized state, the pump or pressure supply connection is closed, whereas the load connection is connected to the tank or return connection in a fluid-conducting manner.
  • a magnetic system designed as an actuating system presses the control piston with a force corresponding to the magnitude of the control current, whereby it is longitudinally moved against the force of a return spring and the fluid, in particular in the form of hydraulic oil, flows from the pump or pressure supply connection to the load connection along a linear characteristic curve. If the current signal is removed, the valve closes and, in turn, returns to its previously described, unactuated position while maintaining the predetermined characteristic curve in the reverse direction.
  • the pertinent valve actuation behavior produces a linear pressure or volumetric flow control signal characteristic which is more than suitable for most applications of proportional pressure control valves of this type.
  • the present invention seeks to further improve the known valve solution to the effect that it can be used for a wider range of applications while still functionally reliable behavior and low manufacturing cost.
  • a related object solves a proportional pressure control valve with the features of claim 1 in its entirety.
  • the first characteristic curve is further formed linear and that immediately after the end of the first characteristic curve, a ramping characteristic curve is generated by means of the control device.
  • a ramping characteristic curve is generated by means of the control device.
  • a multi-way valve connectable to the consumer port of the valve consumer is a multi-way valve with at least one valve position, which allows a kind of floating position for another hydraulic consumer, which is connectable to the multi-way valve, said valve position due to
  • a pending floating position is approached proportionally, which ultimately costs a good pilot control valve resolution goes.
  • FIG. 1 This show in principle and not to scale representation of the in the manner of a longitudinal section, a provable proportional pressure control valve in the prior art; one of the valve solution according to FIG. 1 associated linearly increasing characteristic curve, wherein in the X direction, the current signal I is plotted and above it in the Y direction of the pressure P or the volume flow Q; one of the longitudinal sectional view of FIG 1 corresponding representation of the proportional pressure control valve solution according to the invention ..; in the circle shown an enlarged section of a valve member of FIG. 3; 2 shows a graphic illustration corresponding to FIG. 2, wherein the linear characteristic curve shown in FIG.
  • FIG. 1 shows in longitudinal section a per se known proportional pressure regulating valve with a control piston 12 which can be moved longitudinally in a valve housing 10 and serves by means of an actuating system designated as a whole by 14 for selectively connecting connecting points present in the valve housing 10 such as a pressure supply port P, a consumer port A, and a tank or return port T.
  • the actuator system shown in Fig. 1 is formed like a magnet system; but it would also be possible operations by means of a pneumatic or other fluidic actuator (not shown). Also, a mechanical actuation system for the control piston 12 is not excluded in principle.
  • the magnet system 14 has a coil winding 16 in a pole tube body 18 in a customary and therefore not described in detail manner, the coil winding 16 being able to be supplied with the actuator coil via a plug part 20 with a control current.
  • the pole tube body 18 adjoins a pole plate 22, which is encompassed by its free end face of a flange plate 24 which serves to set the pressure control valve to a valve block, not shown.
  • a magnet armature 26 is guided along a longitudinal movement, which has a pressure equalization channel 28, in order to allow such a pressure balanced an obstacle-free reciprocating movement of the magnet armature 26.
  • the cylindrical magnet armature 26 has on its lower free end face an actuating rod 30 which bears permanently against the control piston 12.
  • the pole plate 22 has a conical control edge profile 38 which defines a cylindrical center recess 40, in which the magnet armature 26 can be guided in accordance with its downward movement.
  • the actual magnetic separation between pole plate 22 and magnet armature 26 is carried out in the usual way via an air gap 42.
  • the entire arrangement of pole tube body 18 with pole plate 22 au odons character of a housing 44 which seals at its two free end faces via sealing means of the interior of the magnet system 14 relative to the environment.
  • the pertinent structure is also common, so that will not be discussed in more detail here at this point. The illustrated in Fig.
  • the fluid medium in particular in the form of hydraulic oil, flows from the pressure supply connection P to the consumer port A.
  • a hydraulic consumer (not shown) connected to the consumer port A, for example in the form of a directional spool valve, a corresponding pressure then builds up on the consumer port A, which acts on the rule piston surface of the control piston 12 and generates a corresponding counterforce of the magnet system 14, which moves the control piston 12 back again.
  • the inflow from the pump or pressure supply connection P to the consumer connection A is reduced until the pressure applied to the consumer connection A corresponds to the magnetic force of the magnet system 14 and thus to the pressure value specification above the current signal I.
  • the hydraulic consumer no longer requires any hydraulic fluid, which is the case, for example, if the addressed directional spool valve is located at the stop, the regulating piston 12 moves further back and closes the inlet bore P as shown in FIG. 1. Decreases the output pressure by the discharge of the connected load below the pressure target, the armature 26 presses the control piston 12 turn down and the control process starts again.
  • the maximum achievable control pressure is determined by the magnetic force of the magnet system 14.
  • Fig. 2 of the pertinent qualitative course of a control signal pressure curve 46 is shown.
  • the characteristic curve 46 is linear in the entire working range due to the selected actuator.
  • the first characteristic curve 46 shown in FIG. 2 thus extends linearly between the control signal in the form of the control current I of the magnetic actuation system 14 and the flow volume Q or the control pressure P, always with reference to a consumer which can be connected to the consumer connection A of the valve.
  • the further characteristic curve 58 adjoining at the free end of the first characteristic curve 46 allows a steep increase in the volume Q or the pressure P in a vertical orientation until, at the end of the ramp-like jump, the vertical characteristic curve merges into a horizontal final characteristic curve 60, ie despite a further increasing control current I, along the closing characteristic curve 60, both the volume flow Q and the pressure P then remain constant.
  • an armature compression spring 64 is biased as part of a control device 65 which is arranged in a cylindrical center recess 67 within the magnet armature 26, the bias voltage exactly on the force at the break point 66 (see Fig. 5) of the there shown pressure control signal characteristic 46, 58, 60 is designed.
  • This inner armature compression spring 64 has no effect on the linear characteristic curve of the first curve 46, because the magnetic force is forwarded in spite of the thus designed control device to the pressure regulating piston 1 2 in the ratio 1: 1.
  • the magnet armature 26 moves on to a pole face 68 of the pole plate 22, which is seen in the viewing direction in FIG down the center recess 40 limited.
  • the in this In principle, the use of electromagnets for proportional pressure regulating valves has the characteristic of developing a horizontal path-force characteristic within a predefinable control range. However, this characteristic curve increases sharply, the more the armature 26 is brought to the addressed pole face 68. This increasing magnetic force is utilized to allow the pressure, respectively the volumetric flow, to suddenly rise in accordance with the characteristic curve 58, 60, starting from the mentioned break point 66 between the two characteristic curves 46, 58.
  • the armature compression spring 64 is supported with its lower end as seen in the viewing direction in FIGS. 3 and 4 on a contact part 70 which, in turn, in each displacement position of the magnet armature 26 due to the spring preload the armature compression spring 64 is in abutment with the magnet armature 26.
  • the annular abutment part 70 at its one free end face 72, which is opposed to the contact surface 74 with the armature compression spring 64 in permanent contact with an abutment shoulder 76 of a press-in sleeve 78 used in the magnet armature 26.
  • lever 76 of the press-in sleeve 78 projects radially inwardly, it relies on a further abutment shoulder 80 of the actuating rod 30 from.
  • the abutment member 70 can lift against the pressure effect of the armature compression spring 64 on the further contact shoulder 80 of the actuating rod 30 of the press-in sleeve 78, provided in the direction of FIG 4, the operating rod 30 is moved upwards.
  • the actuating rod 30 passes through the center of the armature compression spring 64, which in the de-energized state of the magnet system 14 with their respective free upper end with a predetermined distance to the magnet armature 26 toward ends, which is overlapped by the armature compression spring 64 with its upper free end.
  • the pertinent distance is required so that the magnet armature 26 can initially move freely against the action of the armature compression spring 64, resulting in the linear characteristic curve 46. Subsequently, the armature compression spring 64 moves to "block", which generates the ramp-shaped rise of the further characteristic curve 58, 60.
  • the cylindrical center recess 67 in the magnet armature 26 is provided at its upper end with a compensation bore 82 which opens into the upper end of an armature space 84, whereby the armature space 84 as well as parts of the pole plate 22 in the region of the conical control edge course 38 of one
  • Pressure sleeve 86 are enclosed as part of the Polrohr Economicss system.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention porte sur une soupape de régulation de pression proportionnelle qui comprend un piston de régulation (12) guidé en mouvement linéaire dans un carter de soupape (10) et qui, au moyen d'un système d'actionnement (14), sert à relier sélectivement des points de raccordement présents dans le carter de soupape, tels qu'un raccord d'alimentation en pression (P), un raccord d'utilisation (A) et un raccord de bâche ou de retour (T), et dans laquelle il se produit un premier parcours d'une courbe caractéristique liant un signal de commande du système d'actionnement (14) au débit volumique, ou à la pression de commande (P) prévue pour un récepteur qui peut être raccordé au raccord d'utilisation (A), et, au moyen d'un dispositif de commande (65) et après le premier parcours de la courbe caractéristique, il se produit un second parcours de la courbe caractéristique pour le récepteur pouvant être raccordé au raccord d'utilisation (A) du carter de soupape (10), qui est différent du premier parcours de la courbe caractéristique.
EP15707880.9A 2014-04-02 2015-03-05 Soupape de régulation de pression proportionnelle Withdrawn EP3126722A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014004796.2A DE102014004796A1 (de) 2014-04-02 2014-04-02 Proportional-Druckregelventil
PCT/EP2015/000499 WO2015149906A1 (fr) 2014-04-02 2015-03-05 Soupape de régulation de pression proportionnelle

Publications (1)

Publication Number Publication Date
EP3126722A1 true EP3126722A1 (fr) 2017-02-08

Family

ID=52627165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15707880.9A Withdrawn EP3126722A1 (fr) 2014-04-02 2015-03-05 Soupape de régulation de pression proportionnelle

Country Status (4)

Country Link
US (1) US20170159832A1 (fr)
EP (1) EP3126722A1 (fr)
DE (1) DE102014004796A1 (fr)
WO (1) WO2015149906A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013014558A1 (de) * 2013-08-31 2015-03-05 Hydac Fluidtechnik Gmbh Ventil nebst seiner Verwendung für eine Kupplung
DE102016007881A1 (de) 2016-06-28 2017-12-28 Hydac Fluidtechnik Gmbh Einrichtung zur Strömungskraft-Kompensation
EP3358233B1 (fr) * 2017-02-03 2020-09-30 SVM Schultz Verwaltungs-GmbH & Co. KG Soupape, en particulier soupape à tiroir
DE102017203286A1 (de) 2017-03-01 2018-09-06 Robert Bosch Gmbh Druckregelventil mit Druckübersetzungsstift
DE102017012102A1 (de) 2017-12-21 2019-06-27 Hydac Fluidtechnik Gmbh Einrichtung und Ventil zur Strömungskraft-Kompensation
DE102018220903A1 (de) * 2018-12-04 2020-06-04 Robert Bosch Gmbh Druckregelventil mit Nachsaugung
DE102018132448A1 (de) * 2018-12-17 2020-06-18 ECO Holding 1 GmbH Expansionsventil für Kältemittel und Klimaanlage, Wärmemanagementsystem und Batteriekühlsystem mit einem Expansionsventil
RU192204U1 (ru) * 2019-02-20 2019-09-06 Общество с ограниченной ответственностью "Производственная компания "Промтрактор" (ООО "ПК "Промтрактор") Клапан для управления давлением в гидравлических устройствах
DE102019130672A1 (de) * 2019-11-13 2021-06-17 Svm Schultz Verwaltungs-Gmbh & Co. Kg Elektromagnetventil und Verfahren zur Herstelllung eines Elektromagnetventils
DE102021003430A1 (de) * 2021-07-02 2023-01-05 Hydac Fluidtechnik Gmbh Ventil
US11635097B1 (en) 2022-04-20 2023-04-25 Hamilton Sundstrand Corporation Actuator with end stop valve

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DE29705635U1 (de) * 1997-04-02 1998-08-06 Voith Turbo GmbH & Co. KG, 89522 Heidenheim Ventileinrichtung, insbesondere kombinierte Proportional-Wegeventileinrichtung
DE19904901A1 (de) * 1999-02-06 2000-08-10 Zahnradfabrik Friedrichshafen Proportional-Druckregelventil

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DE19815778A1 (de) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Absperrventil mit Druckbegrenzungsfunktion, insbesondere für schlupfgeregelte hydraulische Bremsanlagen von Kraftfahrzeugen
US6737766B1 (en) * 2003-03-14 2004-05-18 Delphi Technologies, Inc. Magnetic actuator and method
US8056576B2 (en) * 2007-08-27 2011-11-15 Husco Automotive Holdings Llc Dual setpoint pressure controlled hydraulic valve
DE102012213112A1 (de) * 2012-07-26 2014-01-30 Zf Friedrichshafen Ag Ventilvorrichtung mit einer Strömungseinrichtung
DE102012215556A1 (de) * 2012-09-03 2014-03-06 Continental Teves Ag & Co. Ohg Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29705635U1 (de) * 1997-04-02 1998-08-06 Voith Turbo GmbH & Co. KG, 89522 Heidenheim Ventileinrichtung, insbesondere kombinierte Proportional-Wegeventileinrichtung
DE19904901A1 (de) * 1999-02-06 2000-08-10 Zahnradfabrik Friedrichshafen Proportional-Druckregelventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2015149906A1 *

Also Published As

Publication number Publication date
US20170159832A1 (en) 2017-06-08
WO2015149906A1 (fr) 2015-10-08
DE102014004796A1 (de) 2015-10-08

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