EP2508763A2 - Soupape - Google Patents

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Publication number
EP2508763A2
EP2508763A2 EP12001536A EP12001536A EP2508763A2 EP 2508763 A2 EP2508763 A2 EP 2508763A2 EP 12001536 A EP12001536 A EP 12001536A EP 12001536 A EP12001536 A EP 12001536A EP 2508763 A2 EP2508763 A2 EP 2508763A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
connection
chamber
valve according
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Withdrawn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
EP12001536A
Other languages
German (de)
English (en)
Other versions
EP2508763A3 (fr
Inventor
Wolfgang Schneider
Dominik Sommer
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.)
Bieri Hydraulik AG
Original Assignee
Bieri Hydraulik AG
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 Bieri Hydraulik AG filed Critical Bieri Hydraulik AG
Publication of EP2508763A2 publication Critical patent/EP2508763A2/fr
Publication of EP2508763A3 publication Critical patent/EP2508763A3/fr
Withdrawn legal-status Critical Current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
    • 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

Definitions

  • the invention relates to a valve, in particular a power-operated directional control valve, with a movable in a valve chamber of a valve housing arranged valve element for guiding fluid pressures under a medium pressure and for selectively enabling or blocking a connection between a supply port and at least one Nutzan gleich, wherein the valve element can be acted upon on the front and rear cross-sectional areas with the respective supply pressure.
  • Valves, and in particular power-operated directional seat valves are preferably used in hydraulic systems when fluid flows, such as hydraulic oil flows, are to be controlled under high media pressure, for example under a media pressure of more than 500 bar, without media loss.
  • the DE 38 03 988 C2 describes, for example, a hydraulically switchable directional control valve, in particular for expansion systems, with a guided in the valve housing valve stem and disposed thereon, in opposite directions lifted from their valve seats valve cones.
  • a valve spring acting against the valve stem is arranged in a spring housing.
  • a control piston which can be acted upon by a hydraulic control pressure is arranged, wherein on the valve housing, a load port which leads to a valve chamber between the two valve cones, a pressure line connection is arranged, which leads to a pressure chamber which receives the valve cone loaded by the valve spring in the closing direction.
  • a return port is also provided which leads to the side located on the side of the control piston outlet chamber which receives the connection to the return controlling poppet.
  • the DE 41 01 117 A1 describes a generic power-operated, in particular electrically or magnetically actuated directional control valve, with a displaceable in a valve housing bore actuator which protrudes with an actuating extension out of the housing and is in contact with an opposite end portion for acting on a valve closing body with this, wherein the Stellfortsatz through a pressure equalization chamber in fluid communication with the system pressure port.
  • the pressure compensation chamber communicates with a consumer port via a fluid branch line. In the fluid branch line, a check valve opening to the pressure compensation chamber is arranged.
  • the DE 10 2007 001 005 A1 describes a spool valve having a valve housing with a cavity, a first passage extending from one end of the cavity, a plurality of ports connected to the cavity and having one or more components blocking the first passage, and the a spool valve element at least partially disposed in the cavity in a first position, the spool valve element being movable to one or more other positions, and the spool valve element exposing the first passage.
  • the known valves can still be improved in this regard.
  • the present invention seeks to provide a valve that allows extremely precise operation with minimal power requirement.
  • a valve which has a valve element which can be guided independently of the respective prevailing fluid pressure in the valve housing, in which the projecting into the valve chamber portion of the valve element has a further cross-sectional area, the surface facing away from the valve chamber, another corresponds to an effective cross-sectional area and the fact that these two other cross-sectional areas are regularly exposed to a different pressure from the media and / or supply pressure, in particular formed by the ambient pressure, a constructional measure is specified, the valve element of the valve during operation pressure balanced and thus free of forces in the To lead valve housing.
  • unwanted media pressures which inhibit the movement of movement of the valve element can build up in the valve housing during a displacement movement of the valve element.
  • an actuating device for the valve element For example, an electromagnet, in particular of the power consumption forth are dimensioned much smaller than is known from the prior art. Overall, this makes the valve lighter and more compact and minimizes energy consumption when operating the valve.
  • the first and second cross-sectional area respectively exposed to the supply pressure corresponds to the diameter area of a valve seat in the valve housing, on which parts of the piston-like valve element can be supported or the outer diameter area of a control bar widened on the valve element minus a piston area of the valve element, which opens outside the valve chamber into a connection with the ambient pressure.
  • a further particularly preferred embodiment corresponds to the ambient pressure respectively exposed, further, third and further effective, fourth cross-sectional area of the outer diameter surface of the valve element widened arranged wider control bar minus another piston surface of the valve element, which faces the valve seat, or the piston surface of the valve element , which opens into the connection with the ambient pressure outside the valve chamber.
  • Force equilibrium therefore prevails at the further third and further fourth cross-sectional area, at which ambient pressure acts, in that the valve element is guided without differential pressures acting on it.
  • pairs associated with each other, the first and the second, and the third and the fourth cross-sectional area are the same size and are equally exposed to the supply pressure or the ambient pressure.
  • the one valve seat establishes the connection between the supply connection and the respective utility connection and another valve seat establishes the connection between the respective utility connection and a tank connection, so that the valve according to the invention can be designed, for example, as a 3/2-way seat valve.
  • the invention is based on existing solutions in particular by the fact that by the complete pressure equalization also a tank pressure up to the level of the supply pressure only to a very limited extent to the required switching forces.
  • the first control bridge limits within the valve chamber at least partially a first chamber of variable volume, wherein the first chamber is permanently connected to the fluid supply leading to the supply port.
  • the second control ridge delimits within the valve space at least partially a second chamber of variable volume, which is permanently exposed to the ambient pressure. It is thus a compact design of the valve, in particular seen in the axial direction of its valve element allows.
  • valve ball With the fixed connection of the valve ball with a part of the valve element, an automatic guidance of the valve ball is achieved by the guided valve element, so that no further possible guidance measures for the valve ball must be taken.
  • the valve can also be operated with inverse pressure conditions (supply pressure and net pressure are reversed) as well as with any desired pressure conditions changing during operation.
  • Another advantage of the fixed connection of the closing element with a part of the valve element is that the closing element can also be designed as a cone or double cone or with a special flow-guiding contour, which can bring manufacturing advantages or minimizing flow-induced force effects (flow forces) allows the closing element.
  • valve element may also be formed in several parts and in addition to a valve piston which has the two control webs and engages through the valve chamber within the valve housing, having a arranged on its free end closure element, in particular in the form of a closing ball, in its opposite end positions on one or the other valve seat rests.
  • the closing element is preferably supported on a restoring device, which seeks to move the closing element in the direction of the second valve seat under the influence of an energy store. Furthermore, in a particularly preferred embodiment of the valve, the closing element is supported on its side facing away from the return device on the piston-like valve element.
  • the piston-like valve element may in this case preferably at least partially pass through the tank connection of the valve and, in the actuated state, seek to move the closing element counter to the action of the return device in the direction of the first valve seat.
  • a lever-like trained foreign force part is provided in the valve, which is arranged in a further valve chamber of the valve housing, which has the ambient pressure.
  • the valve element is moved in the direction of the first valve seat.
  • valve 1 is shown in the manner of a power-operated way-seat valve in a longitudinal sectional view.
  • a block-like, in its longitudinal sectional shape rectangular valve housing 5 has an overall cylindrical valve chamber 3, in which a valve element 7 is arranged axially movable.
  • the valve element 7 serves to guide fluid flows that are under a presettable medium pressure, wherein, inter alia, optionally a connection 9 between a supply connection 11 to the valve housing 5 and a utility connection 13 to the valve housing 5 is released or blocked by the cylindrical and thus piston-like constructed valve element 7 can.
  • To the utility 13 may be connected in a conventional manner, not shown in detail hydraulic consumer.
  • the valve element 7 is in the embodiment shown at its respective axial ends on front and rear cross-sectional areas 15 and 17 with a supply pressure p, which is present at the supply terminal 11, acted upon. At the front and rear cross-sectional surfaces 15, 17 thus result oppositely directed pressure or effective forces.
  • the pressure in the supply port 11 is regularly formed by the pump pressure of a supply pump or hydraulic pump, not shown.
  • the valve element 7 also has a further cross-sectional area 21 (see Fig. 2 ), whose effective area corresponds to a further effective cross-sectional area 23 on the valve element 7.
  • the different pressure po can preferably be formed by an ambient pressure of the valve 1.
  • the pressure can be exerted po by another fluid which is used at this point for corrosion protection or blocking purposes.
  • the valve is under ambient pressure po, for example, a tank pressure or a prevailing at the valve 1 air pressure understood.
  • the cross-sectional surfaces 15 and 23 are formed as circular surfaces and 17 and 21 as annular surfaces in a mutually concentric arrangement. The mentioned pressures p and po may differ in magnitude, but in certain operating states they may also assume the same values.
  • the first cross-sectional area 15 exposed to the supply pressure p corresponds to the diameter area d of a first valve seat 25 within the valve housing 5. Parts of the predominantly piston-like valve element 7 can be supported on the valve seat 25.
  • the second cross-sectional area 17 exposed to the supply pressure p also corresponds to the outer diameter area d a1 (see FIG Fig.2 ) of a widened to the valve element 7, the first control land 27 minus a piston surface d a2 of the valve element 7, which opens outside the valve chamber 3 in a port 31 with the ambient pressure po.
  • the two effective cross-sectional areas 15 and 17 are the same size.
  • the third cross-sectional area 21, which is exposed to the ambient pressure po, corresponds to the outer diameter surface d a3 of a further control web 33 widened on the valve element 7 minus a further piston surface d a4 of the valve element 7.
  • the further piston surface d a4 of the valve element 7 faces the first valve seat 25 and faces the first valve seat 25
  • the first and the second effective cross-sectional area 15, 17 and the third and the fourth effective cross-sectional area 21, 23 are of equal size in pairs.
  • connection 9 can be established between the supply connection 11 and the respective utility connection 13, and a further, second valve seat 35 allows a connection 36 between the respective utility connection 13 and a tank connection 37.
  • first control ridge 27 limited within the valve chamber 3 at least partially a first chamber 39 of variable volume, which is permanently connected via a guided in the valve housing 5, but not shown for simplicity connecting line to the supply port 11 and thus supplied with the supply pressure p.
  • the one in the viewing direction on the FIGS. 1 and 2 Seen on the left next to the first control ridge 27 arranged second control ridge 33 bounded within the valve chamber 3 at least partially a second chamber 41 of variable volume, which is permanently acted upon by the ambient pressure po.
  • the valve element 7 is designed in several parts and has, in addition to a valve piston 43, which has the two said control webs 27, 33 and the valve chamber 3 passes through within the valve housing 5, a arranged on its one free end 45 closing element 47, which is formed in the embodiment shown as a closing ball 49, but also from a valve plug (not shown) could be formed.
  • the closing ball 49 can occupy two end positions during operation of the valve 1 and thus come into abutment with the first valve seat 25 or with the second valve seat 35 and shut off the fluid-carrying connections 9 and 36 with a corresponding system.
  • the closing element 47 is supported on a reset device designated as a whole by 51, which seeks to move the closing element 47 in the direction of the second valve seat 35 under the influence of an energy store 53.
  • the energy storage 53 is formed as a cylindrical compression spring 54.
  • the closing ball 49 or the closing element 47 is supported on its side 55 facing away from the restoring device 51 again on the piston-like valve element 7, so that the closing element 47 is constantly “clamped” between the restoring device 51 and the valve piston 43 during operation of the valve 1 ,
  • the piston-like valve member 7 passes through the tank port 37 and is moved in the actuated state of the valve 1 against the action of the return device 51 in the direction of the first valve seat 25.
  • valve 1 as part of a non-illustrated and preferably designed as an electromagnetic coil means actuator a lever-like trained foreign force part 57 which is arranged in a further, longitudinally S-shaped valve chamber 59 of the valve housing 5.
  • valve chamber 59 prevails, as well as in the region of the terminal 31, ambient pressure po.
  • the foreign force part 57 is as in its planform L-shaped lever formed with a longer, horizontal part 61 and a contrast shorter approximately vertically directed part 63 formed.
  • the parts 61 and 63 together form integrally the foreign force part 57.
  • a blind hole-like receptacle 65 is arranged, which offers an engagement possibility for a free end of an actuating tappet, not shown, of an electromagnetic coil assembly.
  • the end of the actuating plunger may be loosely guided in the receptacle 65, in particular with a radial play.
  • the foreign force part 57 is penetrated by a pin 71, wherein the pin 71 has a bearing pin for pivotally mounting the foreign force part 57 to a, in viewing direction of the Fig.1 vertical, arranged bearing axis 73 forms.
  • a joint ball 77 is arranged at a free end 75 of the valve piston 43.
  • the ball joint 77 engages with radial play in a further receptacle 79 in the vertical part 63 of the foreign force part 57 a.
  • the actuating magnet not shown, which closes in the direction of the Fig.1 Seen above the valve housing 5 sits, the valve chamber 59 from the environment.
  • the valve 1 is thus designed as a 3/2-way seat valve (three connections and two switch positions). By omitting either seat 25 or seat 23 are also 2/2-way valve seat designs with equally advantageous pressure compensation achievable.
  • the valve 1 has a sleeve-like valve element housing 81 with a plurality of housing segments for receiving and axially guiding the valve piston 43 and the closing element 47.
  • a first housing segment 81 ' serves for receiving and radial and axially limited guidance of the closing element 47 and forms the first and second valve seats 25 and 35 of the valve 1.
  • the connection 9 and the connection 36 are partially made between said connections.
  • the first housing segment 81 ' is in the viewing direction of Fig. 1 seen from a return ram 83 of the return device 51 axially partially penetrated.
  • Another, second housing segment 81 "with approximately 11 ⁇ 2 times the axial extent as the first housing segment 81 'is in contact with the first housing segment 81' in the viewing direction of Fig.1 . 2 seen to the right of this subsequently arranged.
  • the second housing segment 81 "serves to receive the valve piston 43 and to guide it axially. It may also be advantageous to integrally form the first and the second housing segment 81 ', 81" as a contiguous component.
  • the closing ball 49 is guided in a simpler representation because not shown cage retainer, to whose inclusion the cup-shaped first housing segment 81 'is divided into two shell parts, which then receive the closing ball 49 between them.
  • the housing segment 81 may also be subdivided into a plurality of further ring segments The spacing of the valve seats is produced with a spacer as shown in the figures, which is not absolutely necessary since the seats can also be pressed to size.
  • the valve piston 43 has on the outer peripheral side a first sealing device 87 and a second sealing device 89.
  • Both sealing devices 87, 89 are each formed by an outer, rectangular in cross-section shape sealing ring 91 and 93, respectively.
  • the molded sealing rings 91, 93 are radially biased by, applied to each of the inner circumference further sealing rings 95 and 97 radially.
  • the first sealing device 87 is viewed in the axial direction of the valve piston 43 at a distance from the second control bar 33 left between this and the tank port 37.
  • the second sealing means 89 is axially centrally between the first control bar 27 and the second control bar 33 and seals the two Fluid chambers 39 and 41 from each other.
  • the housing segment 81 ' which has the tank connection 37, is provided with correspondingly designed flow guide surfaces 90.
  • Both sealing devices 87, 89 lie in circumferential grooves with a rectangular cross-section in the valve piston 43 and slide in operation on the inner peripheral side on the second housing segment 81 ".
  • a third housing segment 81" 'in the manner of a screw-in part forms a sealing closure of the valve chamber 3 with respect to the connection 31 with the ambient pressure.
  • Disposed in the housing segment 81 "' is a third sealing device 101, which opens in the direction of the first chamber 39.
  • the third sealing device 101 is constructed in the same way as the two sealing devices 87, 89 and has a molded sealing ring 103 and a further sealing ring 105 ,
  • a channel 117 is guided radially as far as the second chamber 41.
  • the channel 117 which extends from the valve chamber 59 through the valve housing 5 and the second housing segment 81" approximately perpendicular to the longitudinal axis 107 of the valve 1, serves the constant admission of the second chamber 41 with the ambient pressure po, independently from the respective position of the second control bar 33 and thus of the movement position of the valve element 7.
  • the third housing segment 81 '" is pressed and so far outside the outer circumference tightly received in the valve housing 5.
  • the designated 51 reset device is integrated in a screw-121, which is screwed into the valve housing 5 on the opposite side of the valve element 7.
  • the compression spring 54 is supported with its one free end on the Einschraubhülse 121 and with its other end on a Verfahrkolben 129, which at its one free end side, which is adjacent to the closing ball 49, the aforementioned return ram 83 carries.
  • the Verfahrkolben 129 is guided in a cylindrical center guide 127 in the screw 121.
  • valve according to the invention can be very high pressures, for example, in the range of a working pressure of 700 bar dominate.
  • the pressure force compensated valve element 7 can be the required switching currents for the actuating magnet, not shown significantly reduce, in particular can be achieved over a wide supply pressure range as well as tank pressure range, for example, 50 to 700 bar, a nearly complete pressure independence, which was not possible in this connection with the known comparable power-operated directional seat valves.
  • the tank connection can also be used as a utility connection.
  • the valve may be coupled to force-applying actuators located outside the fluid paths and sealed thereto.
  • the separation of the actuator from the fluid to be controlled makes the desired pressure equalization so difficult and where the double-pair pressure equalization brings the advantage.
  • it is desirable to use the opportunity to connect po with the tank connection for example, for corrosion protection reasons.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Lift Valve (AREA)
EP12001536.7A 2011-04-04 2012-03-07 Soupape Withdrawn EP2508763A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011015976A DE102011015976A1 (de) 2011-04-04 2011-04-04 Ventil

Publications (2)

Publication Number Publication Date
EP2508763A2 true EP2508763A2 (fr) 2012-10-10
EP2508763A3 EP2508763A3 (fr) 2016-07-06

Family

ID=45887859

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12001536.7A Withdrawn EP2508763A3 (fr) 2011-04-04 2012-03-07 Soupape

Country Status (2)

Country Link
EP (1) EP2508763A3 (fr)
DE (1) DE102011015976A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4101117A1 (de) 1991-01-16 1992-07-23 Rexroth Mannesmann Gmbh Fremdkraftbetaetigtes, insbesondere elektrisch- bzw. magnetbetaetigtes wege-sitzventil
DE3803988C2 (de) 1988-02-10 1995-04-13 Westfalia Becorit Ind Tech Hydraulisch schaltbares Wegeventil, vorzugsweise für hydraulische Ausbausysteme u. dgl.
DE102007001005A1 (de) 2006-01-06 2007-09-20 Caterpillar, Inc., Peoria Strömungsmittelsteuersystem

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH416252A (de) * 1963-11-27 1966-06-30 Teves Kg Alfred Aufschlagventil
DE2648145A1 (de) * 1976-10-23 1978-04-27 Frieseke & Hoepfner Gmbh Zuschaltventil
DE3220963A1 (de) * 1982-06-03 1983-12-08 Richter Chemie-Technik GmbH, 4152 Kempen Absperrklappe zum einflanschen in eine rohrleitung
DE3348219C2 (en) * 1983-10-24 1992-03-12 Mannesmann Rexroth Gmbh, 8770 Lohr, De Control motor for servo-valve
JPS6474363A (en) * 1987-09-14 1989-03-20 Smc Corp Valve body of poppet valve
DE3732445C2 (de) * 1987-09-25 1993-12-23 Rexroth Mannesmann Gmbh Druckregelventil
DE58909504D1 (de) * 1989-01-28 1995-12-21 Kuhnke Gmbh Kg H Kraftausgeglichenes Hubventil.
EP1876380B1 (fr) * 2005-04-27 2013-01-02 Eagle Industry Co., Ltd. Clapet à sélecteur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3803988C2 (de) 1988-02-10 1995-04-13 Westfalia Becorit Ind Tech Hydraulisch schaltbares Wegeventil, vorzugsweise für hydraulische Ausbausysteme u. dgl.
DE4101117A1 (de) 1991-01-16 1992-07-23 Rexroth Mannesmann Gmbh Fremdkraftbetaetigtes, insbesondere elektrisch- bzw. magnetbetaetigtes wege-sitzventil
DE102007001005A1 (de) 2006-01-06 2007-09-20 Caterpillar, Inc., Peoria Strömungsmittelsteuersystem

Also Published As

Publication number Publication date
DE102011015976A1 (de) 2012-10-04
EP2508763A3 (fr) 2016-07-06
DE102011015976A8 (de) 2012-12-20

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