EP0645343A1 - Vanne à clapet pilote pour stations d'essence - Google Patents

Vanne à clapet pilote pour stations d'essence Download PDF

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Publication number
EP0645343A1
EP0645343A1 EP94114516A EP94114516A EP0645343A1 EP 0645343 A1 EP0645343 A1 EP 0645343A1 EP 94114516 A EP94114516 A EP 94114516A EP 94114516 A EP94114516 A EP 94114516A EP 0645343 A1 EP0645343 A1 EP 0645343A1
Authority
EP
European Patent Office
Prior art keywords
valve
channel
pressure compensation
pilot
flow path
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
EP94114516A
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German (de)
English (en)
Other versions
EP0645343B1 (fr
Inventor
Harald Böke
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.)
Buerkert Werke GmbH and Co KG
Original Assignee
Buerkert Werke 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 Buerkert Werke GmbH and Co KG filed Critical Buerkert Werke GmbH and Co KG
Publication of EP0645343A1 publication Critical patent/EP0645343A1/fr
Application granted granted Critical
Publication of EP0645343B1 publication Critical patent/EP0645343B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B67—OPENING, CLOSING OR CLEANING BOTTLES, JARS OR SIMILAR CONTAINERS; LIQUID HANDLING
    • B67D—DISPENSING, DELIVERING OR TRANSFERRING LIQUIDS, NOT OTHERWISE PROVIDED FOR
    • B67D7/00—Apparatus or devices for transferring liquids from bulk storage containers or reservoirs into vehicles or into portable containers, e.g. for retail sale purposes
    • B67D7/06—Details or accessories
    • B67D7/36—Arrangements of flow- or pressure-control valves

Definitions

  • the invention relates to a pilot-controlled valve for motor vehicle tank systems, with a valve body in which an inflow channel, an outflow channel, an annular valve seat and an annular channel surrounding it are formed, with a closure body which is acted upon by a compression spring in contact with the valve seat and delimits on its side facing away from the valve seat a pressure compensation chamber which is in flow connection with the inflow channel through at least one pressure compensation channel, and with at least one pilot valve through which a flow path between the pressure compensation chamber and the outflow channel can be controlled.
  • the closure body In such a valve, the closure body, generally a valve plate, is acted upon on both sides with the same liquid pressure and is held against the valve seat only by the force of the compression spring supported on it.
  • the valve is therefore not back pressure-tight: If for any reason the liquid pressure on the side of the drain channel significantly exceeds the pressure in the pressure equalization chamber so that the force of the spring is overcome, the closure body lifts off the valve seat so that fuel is directed in the direction of the inflow channel can flow back.
  • Motor vehicle fueling systems are therefore additionally provided with a check valve which prevents the metered fuel from flowing back.
  • an overpressure valve is integrated into the check valve, which opens towards the metering valve as soon as a predetermined liquid pressure is exceeded.
  • the object of the invention is to prevent the metered fuel from flowing back via the pilot-controlled valve even without a check valve lying in the flow path of the metered fuel.
  • This object is achieved according to the invention in a pilot-controlled valve of the type specified at the outset in that a check valve is arranged in the pressure compensation channel and closes it in the flow direction from the pressure compensation chamber to the inflow channel.
  • the liquid pressure is only balanced between the two sides of the closure body in the flow direction from the inflow channel to the outflow channel.
  • the pressure equalization channel through which the pressure equalization takes place, is closed by the check valve.
  • the pressure compensation channel passes through the closure body and thus the check valve can also be arranged on the closure body.
  • a pressure relief valve is integrated into the valve body so that a heating-related expansion of the enclosed fuel can take place without any danger, which opens a flow connection to the inflow channel when the one delimited by the closure body A pressure prevails on the outflow side of the valve which exceeds that on the inflow side by a predetermined value.
  • a particularly simple arrangement of the pressure relief valve is achieved if it is arranged in a relief channel which branches off from the flow path controlled by the pilot valve and leads to the inflow channel.
  • the closure body can be designed as a valve plate or membrane. Designs with an inflow against the valve seat or via the valve seat are possible. Furthermore, versions with two-stage dosing (coarse and fine dosing) or stepless dosing can be realized. According to a particularly advantageous embodiment, continuous metering is achieved with only one pilot valve, which is designed as a continuously variable proportional solenoid valve.
  • two assembled housing parts 10 and 12 form a valve body.
  • an inflow channel 14 In the housing part 10, an inflow channel 14, an outflow channel 16 and an annular channel 18 connected to them are formed.
  • the annular channel 18 surrounds an annular valve seat 20, on which the inflow channel 14 opens.
  • a cylindrical pressure compensation chamber 22 is formed in the housing part 12.
  • a closure body 24 designed as a valve disk is accommodated in an axially displaceable manner in the manner of a piston sealed on its circumference.
  • a compression spring 26 is supported between the closure body 24 and the boundary wall of the pressure compensation chamber 22 opposite this. By this compression spring 26, the closure body 24 is urged against the valve seat 20.
  • the valve is designed for a two-stage metering and is provided with two pilot valves 30, 32.
  • the valve chamber 34 of the pilot valve 30 is connected to the pressure compensation chamber 22 through a bore 36.
  • the valve chamber 38 of the pilot valve 32 is connected to the pressure compensation chamber 22 through a bore 40.
  • the valve chamber 34 of the pilot valve 30 is connected by a control bore 41 surrounded by a valve seat to a first section of a control channel 42, which extends in the area of the housing part 12 adjacent to the pilot valves 30, 32 and is pressed in towards the outside of the housing part 12
  • Ball 44 is closed and communicates with two further channel sections 43, 45 which are perpendicular to the first section of this control channel 42 and which open into the annular channel 18.
  • the valve chamber 38 of the pilot valve 32 is also connected to the control channel 42 via a control bore 46.
  • the control bore 46 has a smaller cross section than the control bore 41.
  • the control bore 46 also forms a valve seat on its side facing away from the control channel 42.
  • each pilot valve 30, 32 has a valve member 48 or 50, which is actuated by an electromagnet (not shown in the drawing).
  • a pressure equalization channel 52 passes through the closure body 20 coaxially and connects the inflow channel 14 to the pressure equalizing space 22.
  • the pressure equalizing channel 52 is surrounded on its side facing the pressure equalizing space 22 by an annular valve seat 54, against which a valve ball 56 is held in contact by a compression spring 58 becomes. In this way, a check valve is formed, which allows a flow through the pressure equalization channel 52 only in the flow direction from the inflow channel 14 into the pressure compensation chamber 22.
  • a relief duct 60 is branched off from the control duct 42 and consists of two mutually perpendicular duct sections, one of which, on the side of the control duct 42, is equipped with a pressure relief valve and the other, designated 62 with a bore 64 in the adjacent wall of the housing part 10 is aligned and opens into the inflow channel 14.
  • the pressure relief valve is formed by a valve ball 66, which is acted upon by a compression spring 68 against a valve seat in the relief channel 60.
  • the compression spring 68 is supported with its end facing away from the valve ball 66 on a ball 70, which is pressed into the relief channel 60 and closes it to the outside.
  • the liquid fuel delivered by a pump (not shown) of the motor vehicle tank system flows through the inflow channel 14 into the valve body and overcomes the force of the compression spring 58, so that the valve ball 56 lifts off the valve seat 54 and the fuel through the pressure compensation channel 52 into the Pressure equalization chamber 22 arrives.
  • the closure body 24 is therefore acted upon on both sides by the liquid pressure, but on the side of the pressure compensation space 22 additionally by the compression spring 26. Consequently, the closure body 24 is held in contact with the valve seat 20. The valve is closed.
  • the solenoid of the pilot valve 30 is actuated by a switch in the fuel nozzle of the tank system (not shown).
  • the valve member 48 is lifted from the associated valve seat, so that a flow path from the pressure compensation chamber 22 via the channel 36, the valve chamber 34, the control bore 41 and the control channel 42 to the discharge channel 16 is now established.
  • the pilot valve 30 controls this flow path. Since the fuel can now flow out of the pressure compensation chamber 42 to the drainage channel 16, the closure body 24 is relieved on its side facing the pressure compensation space, so that the liquid pressure now predominates on its opposite side and the closure body 24 lifts off the valve seat 20. The fuel now flows through the inlet channel 14 via the valve seat 20 and into the annular space 18, from which it flows out to the outlet channel 16.
  • the pilot valve 32 works with a finer dosage than the pilot valve 30, however, in principle in the same way, so that a new description of the function is unnecessary.
  • the fluid pressure in the drain channel 16 becomes greater than that in the inflow channel 14
  • the fluid pressure in the pressure compensation chamber 22 also takes on this higher value, and the valve ball 56 is moved with the aid of the compression spring 58 against its valve seat 54 in order to increase the pressure compensation channel 52 shut down.
  • the closure body 24 is therefore held in contact with its valve seat 20. The valve is therefore pressure-tight.
  • annular space 18 is connected to the inflow channel 14 and the outflow channel 16 is surrounded by the valve seat 20.
  • Two pressure equalization channels 52A, 52B lead through the closure body 24, each of which can be closed by an elastic valve flap 53A or 53B on their side facing the pressure equalization space 22.
  • each of the two check valves can also be designed as a ball valve in the design according to FIG. 2, in a similar manner to the embodiment according to FIG. 1.
  • FIG. 4 schematically shows a variant of the embodiment according to FIG. 1.
  • the closure body consists of a rigid central part 24A, on which the compression spring 26 is supported, and an annular membrane 24B connected to it, the outer circumference of which between the housing parts 10 and 12 is clamped.
  • pilot valve 30 is preferably designed as a continuously variable proportional solenoid valve, so that fine metering of the fuel can be achieved even with only one pilot valve.
  • the closure body 24 consists of a rigid valve plate.
  • the ring channel is 18th connected to the drain channel 16.
  • the relief channel 60 branches off from the control channel 42, which, with the interposition of the pressure relief valve and the valve ball 66, merges into a connecting channel in the housing part 10, which opens into the inflow channel 14 and surrounds a valve seat at which a control bore 40 connected to the control channel 42 opens.
  • the metering of the fuel is controlled by pulse width modulation of the excitation current supplied to the solenoid of the pilot valve 30.
  • the ring channel 18 is connected to the inflow channel 14. Furthermore, the closure body 24 is designed as a membrane, which is stiffened in its central region by a rigid plate. As in FIG. 2, the check valves are formed by elastic valve flaps 53a, 53b. The various channels and bores are arranged and designed in a manner similar to that in FIG. 5, but the position of the pressure relief valve is changed since the relief channel 60 must always lead into the inflow channel 14.
  • the closure body 24 is again designed as a rigid valve disk, in a similar manner to the embodiment variant according to FIG. 2.
  • a special feature of this embodiment is that the flow path controlled by the pilot valve 30 coaxially through the closure body 24 Passing control channel 70, which is surrounded at its end in the pressure equalization chamber 22 by an annular valve seat 72 with which the valve member 74 of the pilot valve 30 interacts directly.
  • the valve member 74 is surrounded by an annular valve chamber 76, from which a control duct 78 branches off, which is connected to the inflow duct 14 by a relief duct 60 perpendicular thereto, which is controlled by a pressure relief valve with a valve ball 66.
  • all control bores and channels are arranged in the housing part 12, which simplifies production.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Safety Valves (AREA)
  • Automatic Cycles, And Cycles In General (AREA)
  • Fluid-Driven Valves (AREA)
EP94114516A 1993-09-16 1994-09-15 Vanne à clapet pilote pour stations d'essence Expired - Lifetime EP0645343B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4331568 1993-09-16
DE4331568A DE4331568C2 (de) 1993-09-16 1993-09-16 Pilotgesteuertes Ventil für Kraftfahrzeug-Tankanlagen

Publications (2)

Publication Number Publication Date
EP0645343A1 true EP0645343A1 (fr) 1995-03-29
EP0645343B1 EP0645343B1 (fr) 1997-03-05

Family

ID=6497908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94114516A Expired - Lifetime EP0645343B1 (fr) 1993-09-16 1994-09-15 Vanne à clapet pilote pour stations d'essence

Country Status (4)

Country Link
US (1) US5551664A (fr)
EP (1) EP0645343B1 (fr)
JP (1) JP3633969B2 (fr)
DE (2) DE4331568C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3098492A1 (fr) * 2015-05-26 2016-11-30 CKD Corporation Soupape actionnée par solénoïde

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0931231A4 (fr) * 1996-10-08 1999-12-15 Trevor Thomas Esplin Vannes anti-belier telecommandees de type pilote destinees aux applications de ravitaillement en combustible, d'adduction d'eau de ville et de refrigeration
US5960809A (en) * 1997-08-13 1999-10-05 R.D.K. Corporation Fuel equalizing system for plurality of fuel tanks
US6244561B1 (en) * 1998-01-09 2001-06-12 Hansen Technologies Corporation Modulating expansion valve
JP2002509839A (ja) * 1998-03-31 2002-04-02 コンチネンタル・テベス・アーゲー・ウント・コンパニー・オーハーゲー 電磁バルブ
NL1010077C2 (nl) * 1998-09-14 2000-03-15 Koppens Automatic Fabrieken Bv Afscherming voor een brandstofklep.
US6174136B1 (en) 1998-10-13 2001-01-16 Liquid Metronics Incorporated Pump control and method of operating same
US6280147B1 (en) 1998-10-13 2001-08-28 Liquid Metronics Incorporated Apparatus for adjusting the stroke length of a pump element
SE512971C2 (sv) * 1998-10-19 2000-06-12 Dresser Wayne Ab Bränslepumpenhet samt sätt att framställa densamma
DE29912814U1 (de) 1999-07-22 1999-12-02 Buerkert Werke Gmbh & Co Zapfsystem für Tanksäulen
US6264432B1 (en) 1999-09-01 2001-07-24 Liquid Metronics Incorporated Method and apparatus for controlling a pump
JP3533348B2 (ja) * 1999-09-16 2004-05-31 Ｓｍｃ株式会社 集塵機用バルブ
US6328275B1 (en) * 2000-02-04 2001-12-11 Husco International, Inc. Bidirectional pilot operated control valve
JP2002168365A (ja) * 2000-12-01 2002-06-14 Aisan Ind Co Ltd 逆流防止機能付きパイロット式流路開閉弁
US20090121171A1 (en) * 2001-12-04 2009-05-14 Parsons Natan E Automatic bathroom flushers
DE20219358U1 (de) * 2002-12-13 2004-04-22 A. u. K. Müller GmbH & Co KG Eigenmediumbetätigtes Servo-Magnetventil für Flüssigkeiten, insbesondere für sanitäre Armaturen
FI116415B (fi) * 2002-06-20 2005-11-15 Oras Oy Virtausta säätävä magneettiventtiili
ITTO20030761A1 (it) * 2003-09-30 2005-04-01 Fiat Ricerche Sistema per il controllo del riempimento di un serbatoio
CA2883044C (fr) * 2004-10-08 2017-08-15 Sdb Ip Holdings, Llc Robinet a diaphragme a detecteur de pression electronique
US9493936B2 (en) 2004-10-08 2016-11-15 Sdb Ip Holdings, Llc System, method, and apparatus for monitoring wear in a flush valve using pressure detection
US7735513B2 (en) 2004-10-08 2010-06-15 I-Con Systems, Inc. Diaphragm valve with electronic pressure detection
US7168415B2 (en) * 2004-10-27 2007-01-30 International Truck Intellectual Property Company, Llc Electronically controlled selective valve system for fuel level balancing and isolation of dual tank systems for motor vehicles
WO2007045241A1 (fr) * 2005-10-17 2007-04-26 Danfoss A/S Robinet
DE102005058526B4 (de) 2005-12-08 2019-06-19 Robert Bosch Gmbh Zweistufiges Ventil zum Steuern von Fluiden
DE102006038360A1 (de) * 2006-08-09 2008-02-14 Danfoss GmbH Geschäftsbereich Industrieautomatik Ventileinrichtung, insbesondere Betankungsventileinrichtung
US20090321667A1 (en) * 2008-06-25 2009-12-31 Honeywell International Inc. Servo valve modules and torque motor assemblies
US8528590B2 (en) * 2009-02-09 2013-09-10 Parker-Hannifin Corporation Combination solenoid check valve
US8333177B2 (en) * 2010-02-26 2012-12-18 International Truck Intellectual Property Company, Llc Motor vehicle fuel system having multiple fuel tanks
US8733729B2 (en) * 2011-10-10 2014-05-27 Liebert Corporation Back pressure capable solenoid operated diaphragm pilot valve
JP5817536B2 (ja) * 2012-01-10 2015-11-18 トヨタ自動車株式会社 燃料タンクシステム
CN106461096A (zh) * 2014-01-07 2017-02-22 桑杜科技有限公司 流量控制阀
US10378676B2 (en) 2015-12-15 2019-08-13 Sdb Ip Holdings, Llc System, method, and apparatus for optimizing a timing of a flush valve
JP7424322B2 (ja) * 2021-01-19 2024-01-30 Smc株式会社 流体圧力制御装置

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DE1208960B (de) * 1962-11-09 1966-01-13 Fr Buschjost O H G Absperrventil mit Antrieb durch das abzusperrende Druckmittel, einem Hilfsventil und einem Rueckschlagventil
DE1271477B (de) * 1965-01-05 1968-06-27 Heinz Herbertz Membranabsperrventil
FR2250059A1 (fr) * 1973-10-31 1975-05-30 Sefa Sa
DE2438590A1 (de) * 1974-08-10 1976-02-26 Herion Werke Kg Vorgesteuertes wegeventil

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US2958503A (en) * 1955-05-04 1960-11-01 Bendix Corp Bellows compensation for servo valve
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GB1322107A (en) * 1971-02-26 1973-07-04 Fiat Spa Two-way two-position electrically controlled valve
US3860073A (en) * 1974-01-25 1975-01-14 Norris Industries Fire extinguisher discharge valve
US4332368A (en) * 1978-08-21 1982-06-01 Crown Systems Company Valve
US4450863A (en) * 1981-05-13 1984-05-29 Eaton Corporation Series connected solenoid appliance control valve assembly
DE3209689A1 (de) * 1982-03-17 1983-09-29 GOK Regler- und Armaturen GmbH & Co KG, 5200 Siegburg Behaelterentnahmeventil
FR2527195A1 (fr) * 1982-05-21 1983-11-25 Satam Ind Perfectionnements aux dispositifs de distribution de carburant
DE3412545A1 (de) * 1984-04-04 1985-10-17 Gardena Kress + Kastner Gmbh, 7900 Ulm Automatisch steuerbare ventileinrichtung
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US4930665A (en) * 1988-09-19 1990-06-05 Gilbarco Inc. Liquid dispensing system with electronically controlled valve remote from nozzle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1208960B (de) * 1962-11-09 1966-01-13 Fr Buschjost O H G Absperrventil mit Antrieb durch das abzusperrende Druckmittel, einem Hilfsventil und einem Rueckschlagventil
DE1271477B (de) * 1965-01-05 1968-06-27 Heinz Herbertz Membranabsperrventil
FR2250059A1 (fr) * 1973-10-31 1975-05-30 Sefa Sa
DE2438590A1 (de) * 1974-08-10 1976-02-26 Herion Werke Kg Vorgesteuertes wegeventil

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3098492A1 (fr) * 2015-05-26 2016-11-30 CKD Corporation Soupape actionnée par solénoïde

Also Published As

Publication number Publication date
EP0645343B1 (fr) 1997-03-05
JPH07205862A (ja) 1995-08-08
US5551664A (en) 1996-09-03
DE4331568A1 (de) 1995-03-23
JP3633969B2 (ja) 2005-03-30
DE59401907D1 (de) 1997-04-10
DE4331568C2 (de) 2001-10-18

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