EP0645343B1 - Pilot controlled valve for petrol stations - Google Patents

Pilot controlled valve for petrol stations Download PDF

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Publication number
EP0645343B1
EP0645343B1 EP94114516A EP94114516A EP0645343B1 EP 0645343 B1 EP0645343 B1 EP 0645343B1 EP 94114516 A EP94114516 A EP 94114516A EP 94114516 A EP94114516 A EP 94114516A EP 0645343 B1 EP0645343 B1 EP 0645343B1
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EP
European Patent Office
Prior art keywords
valve
duct
pressure equalizing
pilot
pressure
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EP94114516A
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German (de)
French (fr)
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EP0645343A1 (en
Inventor
Harald Böke
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Buerkert Werke GmbH and Co KG
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Buerkert Werke GmbH and Co KG
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    • 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 according to the preamble of claim 1.
  • Such a valve is known from DE-B-12 08 960.
  • the closure body is subjected to the same liquid pressure on both sides and is held against the valve seat only by the force of the compression spring supported on it.
  • a check valve is arranged in the pressure equalization channel, which connects the pressure equalization chamber to the inflow channel in terms of flow, which closes the pressure equalization channel in the flow direction from the pressure equalization chamber to the inflow channel.
  • a backflow of the metered fuel can be done in particular by expanding the fuel, for example by heating the sun.
  • the valve becomes back pressure-tight and further check valves in the motor vehicle tank system to prevent the metered fuel from flowing back can be dispensed with.
  • fuel is included in the known pilot-controlled valve when it is in the closed state, it can expand when heated, which can lead to dangerous uncontrolled leakage flows.
  • the object of the invention is to prevent uncontrolled leakage flows by an expansion of enclosed fuel due to heating.
  • a pressure relief valve is integrated in the valve body, which opens a flow connection to the inflow channel when a pressure prevails on the outflow side of the valve delimited by the closure body, which pressure corresponds to that on the Inflow side exceeds a predetermined value. This allows the enclosed fuel to expand without any risk.
  • the pressure compensation channel passes through the closure body and thus the check valve can also be arranged on the closure body.
  • a further 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 region 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, which 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 additionally on the side of the pressure compensation chamber 22 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 off 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 drain 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 chamber, 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 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 conclude.
  • 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 middle part 24A, on which the compression spring 26 is supported, and an annular membrane 24B connected to it, the outer periphery of which between the housing parts 10 and 12 is clamped.
  • pilot valve 30 is preferably designed as a stepless 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 similar manner 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 manner similar 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 compensation 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 channel 78 branches off, which is connected to the inflow channel 14 by a relief channel 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.

Description

Die Erfindung betrifft ein pilotgesteuertes Ventil nach dem Oberbegriff des Anspruchs 1.The invention relates to a pilot-controlled valve according to the preamble of claim 1.

Ein derartiges Ventil ist aus der DE-B-12 08 960 bekannt. Bei diesem Ventil wird der Verschlußkörper auf beiden Seiten mit demselben Flüssigkeitsdruck beaufschlagt und nur durch die Kraft der sich auf ihm abstützenden Druckfeder gegen den Ventilsitz gehalten. Zudem ist in dem Druckausgleichskanal, der den Druckausgleichsraum mit dem Zuflußkanal strömungsmäßig verbindet, ein Rückschlagventil angeordnet, das den Druckausgleichskanal in Strömungsrichtung vom Druckausgleichsraum zum Zuflußkanal schließt. Durch diese Maßnahme wird verhindert, daß, falls aus irgendeinem Grund der Flüssigkeitsdruck auf der Seite des Abflußkanals den Druck im Druckausgleichsraum deutlich überschreitet, so daß die Kraft der Feder überwunden wird, der Verschlußkörper vom Ventilsitz abhebt und Kraftstoff in Richtung des Zuflußkanals zurückfließen kann. Dies ist deshalb wichtig, da aufgrund der für Kraftfahrzeug-Tankanlagen geltenden Bestimmungen eine genaue Dosierung erfolgen muß. Ein Zurückfließen des dosierten Kraftstoffs kann insbesondere durch Ausdehnen des Kraftstoffs z.B. durch Sonnenerwärmung erfolgen. Durch das Vorsehen des Rückschlagventils im Druckausgleichskanal wird das Ventil gegendruckdicht und es können weitere Rückschlagventile in der Kraftfahrzeug-Tankanlage zum Verhindern des Zurückfließens des dosierten Kraftstoffs entfallen. Da jedoch bei dem bekannten pilotgesteuerten Ventil, wenn sich dieses im geschlossenen Zustand befindet, Kraftstoff eingeschlossen ist, kann sich dieser bei Erwärmung ausdehnen, was zu gefährlichen unkontrollierten Leckageströmungen führen kann.Such a valve is known from DE-B-12 08 960. In this valve, the closure body is subjected to the same liquid pressure on both sides and is held against the valve seat only by the force of the compression spring supported on it. In addition, a check valve is arranged in the pressure equalization channel, which connects the pressure equalization chamber to the inflow channel in terms of flow, which closes the pressure equalization channel in the flow direction from the pressure equalization chamber to the inflow channel. This measure prevents that, 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 and fuel can flow back in the direction of the inlet channel. This is important because, due to the regulations applicable to motor vehicle fueling systems, precise dosing must be carried out. A backflow of the metered fuel can be done in particular by expanding the fuel, for example by heating the sun. By providing the check valve in the pressure equalization channel, the valve becomes back pressure-tight and further check valves in the motor vehicle tank system to prevent the metered fuel from flowing back can be dispensed with. However, since fuel is included in the known pilot-controlled valve when it is in the closed state, it can expand when heated, which can lead to dangerous uncontrolled leakage flows.

Aufgabe der Erfindung ist es, unkontrollierte Leckageströmungen durch eine erwärmungsbedingte Ausdehnung von eingeschlossenem Kraftstoff zu verhindern.The object of the invention is to prevent uncontrolled leakage flows by an expansion of enclosed fuel due to heating.

Diese Aufgabe wird bei einem pilotgesteuerten Ventil der eingangs angegebenen Art erfindungsgemäß dadurch gelöst, daß in dem Ventilkörper ein Überdruckventil integriert ist, das eine Strömungsverbindung zum Zuflußkanal hin öffnet, wenn auf der durch den Verschlußkörper abgegrenzten Abflußseite des Ventils ein Druck herrscht, der den auf der Zuflußseite um einen vorbestimmten Wert überschreitet. Dadurch kann sich der eingeschlossene Kraftstoff ohne Gefährdung ausdehnen.This object is achieved according to the invention in a pilot-controlled valve of the type specified in the introduction in that a pressure relief valve is integrated in the valve body, which opens a flow connection to the inflow channel when a pressure prevails on the outflow side of the valve delimited by the closure body, which pressure corresponds to that on the Inflow side exceeds a predetermined value. This allows the enclosed fuel to expand without any risk.

Eine besonders einfache Bauform wird erreicht, wenn gemäß einer voneilhaften Ausführungsform der Druckausgleichskanal den Verschlußkörper durchsetzt und somit auch das Rückschlagventil am Verschlußkörper angeordnet werden kann.A particularly simple design is achieved if, according to an advantageous embodiment, the pressure compensation channel passes through the closure body and thus the check valve can also be arranged on the closure body.

Eine weitere einfache Anordnung des Überdruckventils wird erreicht, wenn dieses in einem Entlastungskanal angeordnet wird, der von dem durch das Pilotventil gesteuerten Strömungsweg abzweigt und zu dem Zuflußkanal führt.A further 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.

Bei dem erfindungsgemäßen Ventil kann der Verschlußkörper als Ventilteller oder Membran ausgebildet werden. Es sind Bauformen mit Anströmung gegen den Ventilsitz oder über den Ventilsitz möglich. Ferner können Ausführungen mit zweistufiger Dosierung (Grob- und Feindosierung) oder auch stufenloser Dosierung verwirklicht werden. Gemäß einer besonders vorteilhaften Ausführungsform wird eine stufenlose Dosierung mit nur einem Pilotventil erreicht, welches als stufenloses Proportional-Magnetventil ausgebildet ist.In the valve according to the invention, 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.

Besonders hervorzuheben sind ferner Ausführungsformen, bei denen die Anströmung gegen den Ventilsitz erfolgt, die Ringkammer also mit dem Abflußkanal verbunden ist, da bei solchen Bauformen alle erforderlichen Steuerbohrungen und -kanäle mit dem Druckausgleichsraum in einem von zwei Gehäuseteilen angeordnet werden können, aus denen der Ventilkörper zusammengesetzt ist.Emphasis should also be placed on embodiments in which the flow flows against the valve seat, i.e. the annular chamber is connected to the drainage channel, since in such designs all the necessary control bores and channels with the pressure compensation chamber can be arranged in one of two housing parts from which the valve body is made is composed.

Weitere Merkmale und Vorteile der Erfindung ergeben sich aus der folgenden Beschreibung mehrerer Ausführungsformen und aus der Zeichnung, auf die Bezug die genommen wird. In der Zeichnung zeigen:

Fig. 1
eine Schnittansicht einer ersten Ausführungsform des Ventils;
Fig. 2
eine vergrößerte Detailansicht eines als Ventilteller ausgebildeten Verschlußkörpers;
Fig. 3
eine Detailansicht eines durch den Verschlußkörper führenden Druckausgleichskanals mit zugeordnetem Rückschlagventil; und
Figuren 4 bis 7
schematische Darstellungen mehrerer Ausführungsvarianten des Ventils.
Further features and advantages of the invention will become apparent from the following description of several embodiments and from the drawing, to which reference is made. The drawing shows:
Fig. 1
a sectional view of a first embodiment of the valve;
Fig. 2
an enlarged detail view of a closure body designed as a valve plate;
Fig. 3
a detailed view of a pressure compensation channel leading through the closure body with an associated check valve; and
Figures 4 to 7
schematic representations of several design variants of the valve.

Bei der in Fig. 1 gezeigten Ausführungsform des pilotgesteuerten Ventils für Kraftfahrzeug-Tankanlagen bilden zwei zusammengesetzte Gehäuseteile 10 und 12 einen Ventilkörper. In dem Gehäuseteil 10 sind ein Zuflußkanal 14, ein Abflußkanal 16 und ein mit diesen in Verbindung stehender Ringkanal 18 ausgebildet. Der Ringkanal 18 umgibt einen ringförmigen Ventilsitz 20, an dem der Zuflußkanal 14 ausmündet.In the embodiment of the pilot-controlled valve for motor vehicle tank systems shown in FIG. 1, two assembled housing parts 10 and 12 form a valve body. 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.

In dem Gehäuseteil 12 ist ein zylindrischer Druckausgleichsraum 22 gebildet. In diesem Druckausgleichsraum 22 ist ein als Ventilteller ausgebildeter Verschlußkörper 24 nach Art eines an seinem Umfang abgedichteten Kolbens axial verschiebbar aufgenommen. Eine Druckfeder 26 ist zwischen dem Verschlußkörper 24 und der diesem gegenüberliegenden Begrenzungswandung des Druckausgleichsraums 22 abgestützt. Durch diese Druckfeder 26 wird der Verschlußkörper 24 gegen den Ventilsitz 20 beaufschlagt.A cylindrical pressure compensation chamber 22 is formed in the housing part 12. In this pressure compensation chamber 22, 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.

Das Ventil ist für eine zweifstufige Dosierung ausgelegt und mit zwei Pilotventilen 30, 32 versehen. Der Ventilraum 34 des Pilotventils 30 ist durch eine Bohrung 36 mit dem Druckausgleichsraum 22 verbunden. Der Ventilraum 38 des Pilotventils 32 ist durch eine Bohrung 40 mit dem Druckausgleichsraum 22 verbunden. Ferner ist der Ventilraum 34 des Pilotventils 30 durch eine von einem Ventilsitz umgebene Steuerbohrung 41 mit einem ersten Abschnitt eines Steuerkanals 42 verbunden, der sich in dem den Pilotventilen 30, 32 benachbarten Bereich des Gehäuseteils 12 erstreckt und zur Außenseite des Gehäuseteils 12 hin durch eine eingepreßte Kugel 44 verschlossen ist sowie mit zwei weiteren, zum ersten Abschnitt dieses Steuerkanals 42 rechtwinkligen Kanalabschnitten 43, 45 in Verbindung steht, die in den Ringkanal 18 einmünden. Mit dem Steuerkanal 42 ist ferner über eine Steuerbohrung 46 der Ventilraum 38 des Pilotventils 32 verbunden. Die Steuerbohrung 46 hat einen geringeren Querschnitt als die Steuerbohrung 41. Auch die Steuerbohrung 46 bildet auf ihrer von dem Steuerkanal 42 abgewandten Seite einen Ventilsitz. Jedes Pilotventil 30, 32 weist zum Zusammenwirken mit dem zugehörigen Ventilsitz ein Ventilglied 48 bzw. 50 auf, das durch einen in der Zeichnung nicht dargestellten Elektromagnet betätigt wird.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. Furthermore, 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 region 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. To interact with the associated valve seat, each pilot valve 30, 32 has a valve member 48 or 50, which is actuated by an electromagnet (not shown in the drawing).

Durch den Verschlußkörper 20 führt ein Druckausgleichskanal 52 koaxial hindurch und verbindet den Zuflußkanal 14 mit dem Druckausgleichsraum 22. Der Druckausgleichskanal 52 ist auf seiner dem Druckausgleichsraum 22 zugewandten Seite von einem ringförmigen Ventilsitz 54 umgeben, gegen den eine Ventilkugel 56 durch eine Druckfeder 58 in Anlage gehalten wird. Auf diese Weise ist ein Rückschlagventil gebildet, das eine Strömung durch den Druckausgleichskanal 52 nur in der Strömungsrichtung vom Zuflußkanal 14 in den Druckausgleichsraum 22 zuläßt.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.

Von dem Steuerkanal 42 ist ein Entlastungskanal 60 abgezweigt, der aus zwei zueinander rechtwinkligen Kanalabschnitten besteht, wovon der eine, auf der Seite des Steuerkanals 42 gelegene mit einem Überdruckventil ausgestattet ist und der andere, mit 62 bezeichnete Kanalabschnitt mit einer Bohrung 64 in der benachbarten Wandung des Gehäuseteils 10 fluchtet und in den Zuflußkanal 14 ausmündet. Das Überdruckventil ist durch eine Ventilkugel 66 gebildet, die durch eine Druckfeder 68 gegen einen Ventilsitz im Entlastungskanal 60 beaufschlagt wird. Die Druckfeder 68 stützt sich mit ihrem von der Ventilkugel 66 abgewandten Ende auf einer Kugel 70 ab, die in den Entlastungskanal 60 eingepreßt ist und diesen nach außen hin verschließt.A relief duct 60 is branched off from the control duct 42, which 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.

Der durch eine (nicht gezeigte) Pumpe der Kraftfahrzeug-Tankanlage geförderte flüssige Kraftstoff strömt durch den Zuflußkanal 14 in den Ventilkörper und überwindet die Kraft der Druckfeder 58, so daß die Ventilkugel 56 von dem Ventilsitz 54 abhebt und der Kraftstoff durch den Druckausgleichskanal 52 in den Druckausgleichsraum 22 gelangt. Der Verschlußkörper 24 wird daher auf beiden Seiten durch den Flüssigkeitsdruck beaufschlagt, auf der Seite des Druckausgleichsraums 22 jedoch zusätzlich durch die Druckfeder 26. Folglich wird der Verschlußkörper 24 in Anlage an den Ventilsitz 20 gehalten. Das Ventil ist geschlossen.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 additionally on the side of the pressure compensation chamber 22 by the compression spring 26. Consequently, the closure body 24 is held in contact with the valve seat 20. The valve is closed.

Durch einen Schalter in der (nicht gezeigten) Zapfpistole der Tankanlage wird der Elektromagnet des Pilotventils 30 betätigt. Das Ventilglied 48 wird von dem zugeordneten Ventilsitz abgehoben, so daß nunmehr ein Strömungsweg aus der Druckausgleichskammer 22 über den Kanal 36, den Ventilraum 34, die Steuerbohrung 41 und den Steuerkanal 42 zum Abflußkanal 16 hin hergestellt ist. Das Pilotventil 30 steuert diesen Strömungsweg. Da der Kraftstoff nunmehr aus der Druckausgleichskammer 42 zum Abflußkanal 16 abfließen kann, ist der Verschlußkörper 24 auf seiner dem Druckausgleichsraum zugewandten Seite entlastet, so daß nunmehr der Flüssigkeitsdruck auf seiner gegenüberliegenden Seite überwiegt und den Verschlußkörper 24 vom Ventilsitz 20 abhebt. Der Kraftstoff fließt nun durch den Zuflußkanal 14 über den Ventilsitz 20 und in den Ringraum 18, woraus er zum Abflußkanal 16 abströmt.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 off 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 drain 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 chamber, 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.

Das Pilotventil 32 arbeitet mit feinerer Dosierung als das Pilotventil 30, jedoch prinzipiell in gleicher Weise, so daß sich eine erneute Funktionsbeschreibung erübrigt.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.

Falls der Flüssigkeitsdruck aus irgendeinem Grund im Abflußkanal 16 größer wird als im Zuflußkanal 14, nimmt auch der Flüssigkeitsdruck im Druckausgleichsraum 22 diesen höheren Wert an, und die Ventilkugel 56 wird mit Unterstützung durch die Druckfeder 58 gegen ihren Ventilsitz 54 bewegt, um den Druckausgleichskanal 52 zu schließen. Der Verschlußkörper 24 wird daher in Anlage an seinem Ventilsitz 20 gehalten. Das Ventil ist also gegendruckdicht.If, for any reason, the fluid pressure in the drain channel 16 becomes greater than 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 conclude. The closure body 24 is therefore held in contact with its valve seat 20. The valve is therefore pressure-tight.

Wenn sich durch Erwärmung des im Ventilkörper eingeschlossenen Kraftstoffes, beispielsweise bei Sonneneinstrahlung, ein hoher Überdruck einstellt, so wirkt dieser auf die Ventilkugel 66, bis die Druckfeder 68 bei einem vorbestimmten Überdruck nachgibt und den Entlastungskanal 60 zum Zuflußkanal 14 hin öffnet.If a high overpressure arises due to heating of the fuel enclosed in the valve body, for example in the event of sunshine, then this acts on the valve ball 66 until the compression spring 68 yields at a predetermined overpressure and opens the relief channel 60 to the inflow channel 14.

Bei der in Fig. 2 gezeigten Ausführungsvariante ist der Ringraum 18 mit dem Zuflußkanal 14 verbunden und der Abflußkanal 16 von dem Ventilsitz 20 umgeben. Durch den Verschlußkörper 24 führen zwei Druckausgleichskanäle 52A, 52B, die jeweils auf ihrer dem Druckausgleichsraum 22 zugewandten Seite durch eine elastische Ventilklappe 53A bzw. 53B verschließbar sind.In the embodiment variant shown in FIG. 2, the 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.

Wie in Fig. 3 gezeigt ist, kann auch bei der Bauform nach Fig. 2 jedes der beiden Rückschlagventile als Kugelventil ausgebildet sein, in ähnlicher Weise wie bei der Ausführungsform nach Fig. 1.As shown in FIG. 3, 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.

Die Figur 4 zeigt schematisch eine Variante der Ausführungsform nach Figur 1. Bei dieser Variante besteht der Verschlußkörper aus einem starren Mittelteil 24A, auf dem sich die Druckfeder 26 abstützt, und einer daran angeschlossenen, ringförmigen Membran 24B, deren Außenumfang zwischen den Gehäuseteilen 10 und 12 eingespannt ist.FIG. 4 schematically shows a variant of the embodiment according to FIG. 1. In this variant, the closure body consists of a rigid middle part 24A, on which the compression spring 26 is supported, and an annular membrane 24B connected to it, the outer periphery of which between the housing parts 10 and 12 is clamped.

Bei den Ausführungsformen nach den Figuren 5 bis 7 ist jeweils nur ein Pilotventil 30 vorgesehen. Dieses Pilotventil 30 wird vorzugsweise als stufenloses Proportional-Magnetventil ausgebildet, so daß auch mit nur einem Pilotventil eine feine Dosierung des Kraftstoffs realisierbar ist.In the embodiments according to FIGS. 5 to 7, only one pilot valve 30 is provided in each case. This pilot valve 30 is preferably designed as a stepless proportional solenoid valve, so that fine metering of the fuel can be achieved even with only one pilot valve.

Wie aus Fig. 5 ersichtlich ist, besteht der Verschlußkörper 24 aus einer starren Ventilplatte. Wie bei der Ausführungsform nach Fig. 1 ist der Ringkanal 18 mit dem Abflußkanal 16 verbunden. Von dem Steuerkanal 42 zweigt unmittelbar der Entlastungskanal 60 ab, der unter Zwischenfügung des Überdruckventils mit der Ventilkugel 66 in einen Verbindungskanal im Gehäuseteil 10 übergeht, welcher in den Zuflußkanal 14 mündet Der Ventilraum 34 des Pilotventils 30 ist über den Verbindungskanal 36 mit dem Druckausgleichsraum 22 verbunden und umgibt einen Ventilsitz, an dem eine mit dem Steuerkanal 42 verbundene Steuerbohrung 40 ausmündet. Bei dieser Ausführungsform wird die Dosierung des Kraftstoffs durch Pulsbreitenmodulation des dem Elektromagnet des Pilotventils 30 zugeführten Erregungsstromes gesteuert.As can be seen from Fig. 5, the closure body 24 consists of a rigid valve plate. As in the embodiment according to FIG. 1, 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. In this embodiment, the metering of the fuel is controlled by pulse width modulation of the excitation current supplied to the solenoid of the pilot valve 30.

Bei den Ausführungsformen nach den Figuren 6 und 7 ist jeweils der Ringkanal 18 mit dem Zuflußkanal 14 verbunden. Ferner ist der Verschlußkörper 24 als Membran ausgebildet, die in ihrem mittleren Bereich durch eine starre Platte versteift ist. Die Rückschlagventile sind wie bei Fig. 2 durch elastische Ventilklappen 53a, 53b gebildet. Die verschiedenen Kanäle und Bohrungen sind in ähnlicher Weise wie in Fig. 5 angeordnet und ausgebildet, jedoch ist die Lage des Überdruckventils verändert, da der Entlastungskanal 60 stets in den Zuflußkanal 14 führen muß.In the embodiments according to FIGS. 6 and 7, 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 similar manner 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.

Bei der Ausführungsform nach Fig. 7 ist wiederum der Verschlußkörper 24 als starrer Ventilteller ausgebildet, in ähnlicher Weise wie bei der Ausführungsvariante nach Fig. 2. Eine Besonderheit dieser Ausführungsform besteht darin, daß der durch das Pilotventil 30 gesteuerte Strömungsweg einen koaxial durch den Verschlußkörper 24 hindurchführenden Steuerkanal 70 aufweist, der an seinem in den Druckausgleichsraum 22 mündenden Ende von einem ringförmigen Ventilsitz 72 umgeben ist, mit dem das Ventilglied 74 des Pilotventils 30 unmittelbar zusammenwirkt. Das Ventilglied 74 ist von einem ringförmigen Ventilraum 76 umgeben, von dem ein Steuerkanal 78 abzweigt, der durch einen dazu senkrechten Entlastungskanal 60, der durch ein Überdruckventil mit einer Ventilkugel 66 gesteuert wird, mit dem Zuflußkanal 14 verbunden ist. Bei dieser besonders einfachen Ausführungsform sind alle Steuerbohrungen- und -kanäle in dem Gehäuseteil 12 angeordnet, wodurch die Herstellung vereinfacht wird.In the embodiment according to FIG. 7, the closure body 24 is again designed as a rigid valve disk, in a manner similar 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 compensation 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 channel 78 branches off, which is connected to the inflow channel 14 by a relief channel 60 perpendicular thereto, which is controlled by a pressure relief valve with a valve ball 66. In this particularly simple embodiment, all control bores and channels are arranged in the housing part 12, which simplifies production.

Claims (15)

  1. A pilot controlled valve for tank systems for motor vehicles, comprising a valve body, in which an inlet duct (14), an outlet duct (16), an annular valve seat (20) and an annular duct (18) surrounding the same are formed, a valve closure member (24), which is urged by a compression spring (26) toward engagement with the valve seat (20) and on a side thereof turned away from the valve seat defines a pressure equalizing space (22) connected by at least one pressure equalizing duct (52) with the inlet duct (14) to provide a flow connection, and at least one pilot valve (30, 32), by which a flow path (42) between the pressure equalizing space (22) and the outlet duct (16) may be controlled, a check valve (54, 56) being arranged in the pressure equalizing duct (52) and closing the same in the flow direction from the pressure equalizing space (22) to the inlet duct (14), characterized by an excess pressure valve (66, 68) integrated in the valve body (10, 12) and opening a flow connection to the inlet duct (14) when at the outlet side, defined by the valve closure member (24), of the valve a pressure is present which exceeds the pressure on the inlet side by a predetermined amount.
  2. The valve as claimed in claim 1, characterized in that the pressure equalizing duct (52) extends through the valve closure member (24).
  3. The valve as claimed in claim 1 or claim 2, characterized in that the excess pressure valve (66, 68) is arranged in a relief duct (60) leading to the inlet duct (14) and branching from the flow path (42) which is under the control of the pilot valve (30, 32).
  4. The valve as claimed in any one of the preceding claims, characterized in that the check valve (54, 56) is constituted by an annular sealing seat (54) surrounding the aperture opening of the pressure equalizing duct (52) on the pressure equalizing space (22) side and by a valve ball (56) urged by a compression spring (58) into engagement with the sealing seat (54).
  5. The valve as claimed in any one of the claims 1 through 3, characterized in that the check valve is constituted by an annular sealing seat surrounding the aperture opening of the pressure equalizing duct (52) on the pressure equalizing space (22) side and by a valve flap (53A, 53B) held elastically against the sealing seat.
  6. The valve as claimed in any one of the preceding claims, characterized by a plurality of pressure equalizing ducts (52A, 52B), each having an associated check valve (53A, 53B), extending through the valve closure member (24).
  7. The valve as claimed in any one of the preceding claims, characterized in that the valve closure member (24) is constituted by a valve plate.
  8. The valve as claimed in any one of the claims 1 through 6, characterized in that the valve closure member (24) is constituted by a diaphragm (24B) held at an outer edge thereof in the valve body (10, 12) and having a rigid middle part (24A), against which the compression spring (26) bears.
  9. The valve as claimed in any one of the preceding claims, characterized by two pilot valves (30, 32) controlling the flow connections (40, 46) of different inside diameter between the pressure equalizing space (22) and the outlet duct (16).
  10. The valve as claimed in any one of the preceding claims, characterized in that the valve body is constituted by two housing parts (10, 12), the first (10) of which is provided with the inlet duct (14), the outlet duct (16) and the annular duct (18), and the second (12) of which comprises the pressure equalizing chamber (22) and the flow path (42) controlled by the pilot valve (30, 32).
  11. The valve as claimed in claim 10, characterized in that the second housing part (12) contains the excess pressure valve (66, 68).
  12. The valve as claimed in claim 11, characterized in that the annular duct (18) is connected with the outlet duct (16), in that the flow path (42) under the control of the pilot valve (30, 32) is at least nearly completely formed in the second housing part (12), and in that the relief duct (60) branching from this flow path extends from the second housing part (12) through the first housing part (10) and as far as the inlet duct (14).
  13. The valve as claimed in claim 11, characterized in that the annular duct (18) is connected with the inlet duct (14), in that the relief duct (60) branching from the flow path (42) under the control of the pilot valve (30, 32) is at least nearly completely formed in the second housing part (12), and in that this flow path extends from the second housing part (12) through the first housing part (10) and as far as the outlet duct (16).
  14. The valve as claimed in any one of the claims 1 through 12, characterized in that the annular duct (18) is connected with the inlet duct (14), in that the flow path (70) under the control of the pilot valve (30) extends through the middle part of the valve closure member (24), and in that the aperture opening, arranged on the pressure equalizing space (22) side of this flow path (70), is surrounded by an annular sealing seat (72) of the pilot valve (30), with which its valve member (74) directly cooperates.
  15. The valve as claimed in any one of the preceding claims, characterized in that the pilot valve is designed in the form of a stepless proportional solenoid valve.
EP94114516A 1993-09-16 1994-09-15 Pilot controlled valve for petrol stations Expired - Lifetime EP0645343B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4331568A DE4331568C2 (en) 1993-09-16 1993-09-16 Pilot operated valve for motor vehicle fuel systems
DE4331568 1993-09-16

Publications (2)

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

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP94114516A Expired - Lifetime EP0645343B1 (en) 1993-09-16 1994-09-15 Pilot controlled valve for petrol stations

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US (1) US5551664A (en)
EP (1) EP0645343B1 (en)
JP (1) JP3633969B2 (en)
DE (2) DE4331568C2 (en)

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Also Published As

Publication number Publication date
DE4331568C2 (en) 2001-10-18
EP0645343A1 (en) 1995-03-29
JP3633969B2 (en) 2005-03-30
DE59401907D1 (en) 1997-04-10
JPH07205862A (en) 1995-08-08
US5551664A (en) 1996-09-03
DE4331568A1 (en) 1995-03-23

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