EP0914552A1 - Valve for proportioned supply of volatilized fuel - Google Patents

Valve for proportioned supply of volatilized fuel

Info

Publication number
EP0914552A1
EP0914552A1 EP98912262A EP98912262A EP0914552A1 EP 0914552 A1 EP0914552 A1 EP 0914552A1 EP 98912262 A EP98912262 A EP 98912262A EP 98912262 A EP98912262 A EP 98912262A EP 0914552 A1 EP0914552 A1 EP 0914552A1
Authority
EP
European Patent Office
Prior art keywords
valve
section
nozzle
cross
valve seat
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
EP98912262A
Other languages
German (de)
French (fr)
Other versions
EP0914552B1 (en
Inventor
Erwin Krimmer
Wolfgang Schulz
Tilman Miehle
Manfred Zimmermann
Maria Esperilla
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0914552A1 publication Critical patent/EP0914552A1/en
Application granted granted Critical
Publication of EP0914552B1 publication Critical patent/EP0914552B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/08—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding fuel vapours drawn from engine fuel reservoir
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/08—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding fuel vapours drawn from engine fuel reservoir
    • F02M25/0836—Arrangement of valves controlling the admission of fuel vapour to an engine, e.g. valve being disposed between fuel tank or absorption canister and intake manifold

Definitions

  • the invention relates to a valve for the metered introduction of fuel volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine according to the preamble of claim 1.
  • a valve is already known (DE-PS 42 29 110) which has a valve seat , which is formed on an edge of an inlet cross-section of a Laval nozzle, against which a cylindrical valve member which can be actuated by an electromagnet bears in the closed position.
  • the valve seat thus also represents an axial delimitation of the Laval nozzle.
  • the design of the nozzle as a Laval nozzle enables a comparatively high flow rate to be achieved, so as to bring about only a relatively low flow resistance with a planned throughput of the valve.
  • valve according to the invention with the characterizing features of claim 1 has the advantage that even at high flow rates, only relatively low differential pressures are required at the valve. It is particularly advantageous that only a small valve lift is required to control the flow, so that a particularly fast-switching valve can be realized, in which only little scatter in the flow rate occurs.
  • a valve characteristic can advantageously be realized in which, depending on the differential pressure, there is a rapid increase in the flow characteristic for small differential pressures and a constant flow for larger differential pressures.
  • valve characteristic of the valve according to the invention can be changed in a simple manner.
  • FIG. 1 shows a Longitudinal section through the valve according to the invention
  • Figure 2 is a perspective view of a valve seat body of the valve according to a first embodiment
  • Figure 3 is a bottom view of a valve seat body of the valve according to a second embodiment.
  • the valve 1, shown schematically in longitudinal section in FIG. 1, serves for the metered introduction of fuel volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine and is part of a fuel evaporation retention system, not shown in more detail, of a mixture-compressing, externally ignited internal combustion engine.
  • a fuel evaporation retention system not shown in more detail, of a mixture-compressing, externally ignited internal combustion engine.
  • the structure and function of such fuel evaporation restraint systems can be found, for example, on pages 48 and 49 of Bosch Technical Instruction, Motor Management Motronic, Second Edition, August 1993.
  • the structure and the mode of operation of such a valve 1, also referred to as a regeneration valve or tank ventilation valve are further known to the person skilled in the art from DE-OS 40 23 044, the disclosure of which is to be part of the present patent application.
  • the valve 1 has, coaxially to a longitudinal valve axis 2, a two-part valve housing with a cylindrically stepped, sleeve-shaped lower housing part 4 and a cover-shaped upper housing part 5.
  • the upper housing part 5 is, for example, placed on the lower housing part 4 and thereby encompasses the lower housing part 4 on its outer surface.
  • Both housing parts 4, 5 are preferably made of plastic and are, for example, inseparable, for example by means of ultrasonic welding or also separably connected, for example by means of a snap connection.
  • the lower housing part 4 carries an inlet connection 8 for connection to a ventilation connection, not shown, of a fuel tank of the internal combustion engine or to a downstream connection thereof
  • Adsorption filter The adsorption filter is used in a known manner for the intermediate storage of fuel vapor volatilized from the fuel tank and is filled with activated carbon, for example.
  • the upper housing part 5 has an outflow connection 9 for connection to an intake pipe of the internal combustion engine.
  • the inflow nozzle 8 and the outflow nozzle 9 are each arranged axially in the housing parts 4 and 5, approximately in alignment with one another.
  • An electromagnet 12 is arranged in the interior of the lower housing part 4. It has a pot-shaped magnet housing 14 with a coaxial, hollow-cylindrical magnet core 15 penetrating a bottom 25 of the magnet housing 14 and a cylindrical excitation coil 16, which is on a coil carrier
  • the magnetic core 15 has an axial through opening 21 which is delimited by the hollow magnetic core 15, so that fuel vapor can flow in the through opening 21 from the inflow nozzle 8 to the outflow nozzle 9.
  • the magnet housing 14 with the magnetic core 15 is inserted into the lower housing part 4 in such a way that 4 axial channels 24 remain between an outer jacket 22 of the magnet housing 14 and an inner wall 23 of the lower housing part 4, for example in the circumferential direction at the same angle are offset from one another, so that, as shown in FIG. 1, only two axial channels 24 can be seen, for example.
  • the axial channels 24 are located on the one hand in the lower housing part 4 between the bottom 25 of the magnet housing 14 and the inflow connector 8 annular space 27 on the one hand with the inflow connector 8 and on the other hand via bores 28 which are introduced into the magnet housing 14 near the open end of the magnet housing 14, in communication with the inside of the magnet housing 14 downstream of the excitation coil 16. Through these axial channels 24 can in the
  • Incoming fuel nozzle 8 also flow around the magnet housing 14 and thus dissipate the heat generated here.
  • the magnet housing 14 has a bent edge 29, which serves as a support flange for a bow-shaped valve seat body 31.
  • the valve seat body 31 forms the yoke of the electromagnet 12.
  • the valve seat body 31 partially covers the magnet housing 14 and is fastened to the lower housing part 4 by means of at least two fitting holes 47 shown in FIGS. 2 and 3.
  • the valve seat body 31 resting on the edge 29 is accommodated in an elastic, annular bearing receptacle 32 which has a U-shaped cross section and which in turn is clamped between the two housing parts 4 and 5.
  • a valve member 36 made of magnetic material also forms the armature of the electromagnet 12 and is fastened to a leaf spring 33 which is clamped on the edge side between the valve seat body 31 and the edge 29.
  • the valve seat body 31 has at least one valve opening 34.
  • two slit-shaped valve openings 34 are provided which, as shown in FIG. 2, have, for example, a semicircular shape and are provided opposite one another, so that they complement one another to form a fictitious circular shape.
  • FIG. 3 a top view of the valve seat body 31 designed according to a second embodiment, shows the valve openings 34 in a U-shape, which can be supplemented to form a fictitious rectangle.
  • the two valve openings 34 can be closed by the valve member 36, so that a double valve seat 37 results. As shown in FIG.
  • a through opening 38 running coaxially to the hollow cylindrical magnetic core 15 is provided in the valve member 36, through which fuel flowing from the inflow nozzle 8 via the through opening 21 of the magnetic core 15 can flow into the outflow nozzle 9 when the valve openings 34 are open.
  • the valve member 36 is acted upon by a valve closing spring 43 in the valve closing direction in the direction of the outflow connector 9, which is supported on the one hand on the valve member 36 and on the other hand on a sleeve-shaped end 41 of the magnetic core 15.
  • the valve member 36 carries on its side facing the valve double seat 37 a sealing rubber 42 made of elastic
  • the sealing rubber 42 also lines the through opening 38 and projects somewhat beyond a side of the valve member 36 facing away from the valve double seat 37.
  • the valve closing spring 43 presses the valve member 36 with the sealing rubber 42 onto the valve double seat 37 and thus closes the valve openings 34.
  • the valve member 36 with its sealing rubber 42 protruding from the through opening 38 becomes against the end 41 of the magnetic core 15 pressed, which forms a stop 44 for the attractive movement of the valve member 36.
  • the stop 44 can be axially displaced and thereby the flow rate with the valve member 36 lifted from the valve double seat 37 at the maximum.
  • the valve closing spring 43 is weakly dimensioned since, in the event of a pressure drop between the outlet connection 9 and the inlet connection 8, a suction effect is exerted on the valve member 36 in the direction of valve closing and the closing effect of the valve closing spring 43 is supported.
  • the electromagnet 12 is actuated in a clocked manner by the control electronics of a control device (not shown in more detail), for which purpose a connector connection 50 is provided on the upper housing part 5.
  • the cycle rate is predetermined by the operating state of the internal combustion engine, so that the flow rate of volatilized fuel vapor passing through valve openings 34 from the inflow nozzle 8 into the outflow nozzle 9 can be dosed accordingly.
  • the channel penetrating the outflow nozzle 9 is designed in the form of a Laval nozzle 55, which is composed in a known manner from a convergent part 56 and a divergent part 57.
  • the Laval nozzle 55 tapers from a first inlet cross section 60 downstream in the vicinity of the valve seat body 31 to a narrowest cross section 61, in order to then widen from the narrowest cross section 61 to an end cross section 62 at the downstream end.
  • the cross sections 60, 61, 62 are designed in such a way that the inlet cross section 60 is at least equal to or larger than the end cross section 62.
  • the inlet cross section 60 is preferably 1.1 to 2 times larger than the end cross section 62.
  • the narrowest cross section 61 is preferably 2 up to 4 times smaller than that Entry cross section 60.
  • the length of the Laval nozzle 55 measured is, for example, 3 to 5 times larger than a diameter at the inlet cross-section 60.
  • the side 49 of the valve seat body 31 is at a distance from the inlet side of the outflow connector 9 having the inlet cross-section 60 in the direction of the valve longitudinal axis 2, so that an intermediate space 63 is formed between the side 49, the inlet side of the outflow connector 9 and the sealing ring 51, which has at least one lateral extension perpendicular to the longitudinal axis 2 of the valve, which is as large as the diameter of the inlet cross-section 60, and into which the valve openings 34 flow out. Since only the two valve openings 34 of the valve seat body 31 have to be covered by the valve member 36 for actuation, it is possible to optimally adjust the valve cross section of the valve member 36 by simply changing the valve lift
  • Valve openings 34 are made substantially smaller from an inlet cross-section 60 of the Laval nozzle 55. Both cross-sections together are preferably only about 10 to 20 percent of the inlet cross-section 60. Due to the relatively no cross-section of both valve openings 34, the interruption of the fuel flow by means of valve member 36 can be high Speed are carried out so that a particularly fast switching valve 1 can be realized.
  • the adaptation to the desired flow rates of the valve 1 is possible by simply changing the valve stroke or by rotating the magnetic core 15 in the magnet housing 14.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

The known types of fuel tank ventilation valve that are provided with a Laval nozzle pose a problem concerning the fine flow rate control since the inlet section of the nozzle is directy covered by a valve portion. The present invention relates to a valve whose seat (37) is part of the valve support (31) having at least one opening (34) which can be closed by said support (36). The cross section of said opening is substantially smaller than that of the Laval nozzle inlet (60), which is mounted to the opening at a distance thereof. The inventive valve is designed so as to enable a proportioned supply of fuel from an internal combustion engine with compressed mixture and spark ignition into an admission pipe in said engine.

Description

Ventil zum dosierten Einleiten von verflüchtigtem BrennstoffValve for the metered introduction of volatilized fuel
Stand der TechnikState of the art
Die Erfindung geht aus von einem Ventil zum dosierten Einleiten von aus einem Brennstofftank einer Brennkraftmaschine verflüchtigtem Brennstoff in ein Ansaugrohr der Brennkraftmaschine nach der Gattung des Anspruchs 1. Es ist schon ein derartiges Ventil bekannt (DE-PS 42 29 110) , das einen Ventilsitz aufweist, der an einem Rand eines Eintrittsquerschnittes einer Laval-Düse gebildet wird, an welchem ein von einem Elektromagneten betätigbares, zylinderförmiges Ventilglied in Schließstellung anliegt. Der Ventilsitz stellt somit auch eine axiale Begrenzung der Laval-Düse dar. Die Ausbildung der Düse als Laval-Düse ermöglicht, daß eine vergleichsweise hohe Durchströmgeschwindigkeit verwirklicht werden kann, um so bei einem vorgesehenen Durchsatz des Ventils nur einen relativ geringen Strömungswiderstand zu bewirken. Es ergibt sich dabei das Problem einer feinfühligen Regelung der Durchflußmenge, da stets der relativ große Eintrittsquerschnitt der Laval-Düse unmittelbar von dem Ventilglied bedeckt werden muß. Außerdem ist für eine bestimmte Durchflußmenge ein bestimmter Ventilhub des Ventilgliedes erforderlich, der aber von der konstruktiven Auslegung der Laval-Düse, insbesondere der Dimensionierung ihres engsten Querschnitts, abhängt, so daß eine Anpassung der Kennlinie des Ventils nur durch eine konstruktive Änderung der Laval-Düsenform erfolgen kann, was jedoch aufwendig ist .The invention relates to a valve for the metered introduction of fuel volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine according to the preamble of claim 1. Such a valve is already known (DE-PS 42 29 110) which has a valve seat , which is formed on an edge of an inlet cross-section of a Laval nozzle, against which a cylindrical valve member which can be actuated by an electromagnet bears in the closed position. The valve seat thus also represents an axial delimitation of the Laval nozzle. The design of the nozzle as a Laval nozzle enables a comparatively high flow rate to be achieved, so as to bring about only a relatively low flow resistance with a planned throughput of the valve. The problem arises of a sensitive control of the flow rate, since the relatively large inlet cross section of the Laval nozzle must always be covered directly by the valve member. In addition, a certain valve lift of the valve member is required for a certain flow rate, but that of the constructive The design of the Laval nozzle, in particular the dimensioning of its narrowest cross section, depends on it, so that the characteristic curve of the valve can only be adjusted by constructively changing the Laval nozzle shape, which is, however, complex.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Ventil mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß selbst bei hohen Durchflüssen nur relativ geringe Differenzdrücke am Ventil erforderlich sind. Besonders vorteilhaft ist dabei, daß nur ein kleiner Ventilhub zur Steuerung des Durchflusses benötigt wird, so daß sich ein besonders schnell schaltendes Ventil verwirklichen läßt, bei dem außerdem nur geringe Streuungen der Durchflußmenge auftreten. Vorteilhafterweise läßt sich eine Ventilcharakteristik verwirklichen, bei der abhängig vom Differenzdruck ein schneller Anstieg der Durchflußkennlinie bei kleinen Differenzdrücken und ein gleichbleibender Durchfluß bei größeren Differenzdrücken vorhanden ist.The valve according to the invention with the characterizing features of claim 1 has the advantage that even at high flow rates, only relatively low differential pressures are required at the valve. It is particularly advantageous that only a small valve lift is required to control the flow, so that a particularly fast-switching valve can be realized, in which only little scatter in the flow rate occurs. A valve characteristic can advantageously be realized in which, depending on the differential pressure, there is a rapid increase in the flow characteristic for small differential pressures and a constant flow for larger differential pressures.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Ventils möglich.Advantageous further developments and improvements of the valve specified in claim 1 are possible through the measures listed in the subclaims.
Von besonderem Vorteil ist, daß sich die Ventilcharakteristik des erfindungsgemäßen Ventils in einfacher Art und Weise verändern läßt.It is particularly advantageous that the valve characteristic of the valve according to the invention can be changed in a simple manner.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch das erfindungsgemäße Ventil, Figur 2 eine perspektivische Darstellung eines Ventilsitzkörpers des Ventils gemäß einer ersten Ausführungsart, Figur 3 eine Unteransicht auf einen Ventilsitzkörper des Ventils gemäß einer zweiten Ausführungsart .An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. 1 shows a Longitudinal section through the valve according to the invention, Figure 2 is a perspective view of a valve seat body of the valve according to a first embodiment, Figure 3 is a bottom view of a valve seat body of the valve according to a second embodiment.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Das in Figur 1 im Längsschnitt schematisch dargestellte Ventil 1 dient zum dosierten Einleiten von aus einem Brennstofftank einer Brennkraftmaschine verflüchtigtem Brennstoff in ein Ansaugrohr der Brennkraftmaschine und ist Teil eines nicht näher dargestellten Brennstoffverdunstungs- Rückhaltesystems einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine. Der Aufbau und die Funktion derartiger Brennstoffverdunstungs-Rückhaltesysteme ist beispielsweise der Bosch Technischen Unterrichtung, Motormanagement Motronic, zweite Ausgabe, August 1993, auf Seiten 48 und 49 entnehmbar. Der Aufbau und die Wirkungsweise eines derartigen, auch als Regenerierventil oder Tankentlüftungsventil bezeichneten Ventils 1 ist dem Fachmann weiter aus der DE-OS 40 23 044 bekannt, deren Offenbarung Bestandteil der hier vorliegenden Patentanmeldung sein soll.The valve 1, shown schematically in longitudinal section in FIG. 1, serves for the metered introduction of fuel volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine and is part of a fuel evaporation retention system, not shown in more detail, of a mixture-compressing, externally ignited internal combustion engine. The structure and function of such fuel evaporation restraint systems can be found, for example, on pages 48 and 49 of Bosch Technical Instruction, Motor Management Motronic, Second Edition, August 1993. The structure and the mode of operation of such a valve 1, also referred to as a regeneration valve or tank ventilation valve, are further known to the person skilled in the art from DE-OS 40 23 044, the disclosure of which is to be part of the present patent application.
Das Ventil 1 weist koaxial zu einer Ventillängsachse 2 ein zweiteiliges Ventilgehäuse mit einem zylindrisch abgestuften, hülsenförmigen unteren Gehäuseteil 4 und einem deckeiförmigen oberen Gehäuseteil 5 auf. Der obere Gehäuseteil 5 ist auf den unteren Gehäuseteil 4 beispielsweise aufgesetzt und umgreift dabei den unteren Gehäuseteil 4 an seiner Außenfläche. Beide Gehäuseteile 4, 5 bestehen vorzugsweise aus Kunststoff und sind beispielsweise untrennbar zum Beispiel mittels Ultraschallverschweißung oder auch trennbar zum Beispiel mittels einer Rastverbindung verbunden. Der untere Gehäuseteil 4 trägt einen Zuströmstutzen 8 zum Anschließen an einen nicht näher dargestellten Entlüftungsstutzen eines Brennstofftanks der Brennkraftmaschine oder an einen diesem nachgeschaltetenThe valve 1 has, coaxially to a longitudinal valve axis 2, a two-part valve housing with a cylindrically stepped, sleeve-shaped lower housing part 4 and a cover-shaped upper housing part 5. The upper housing part 5 is, for example, placed on the lower housing part 4 and thereby encompasses the lower housing part 4 on its outer surface. Both housing parts 4, 5 are preferably made of plastic and are, for example, inseparable, for example by means of ultrasonic welding or also separably connected, for example by means of a snap connection. The lower housing part 4 carries an inlet connection 8 for connection to a ventilation connection, not shown, of a fuel tank of the internal combustion engine or to a downstream connection thereof
Adsorptionsfilter. Der Adsorptionsfilter dient in bekannter Weise zur Zwischenspeicherung von aus dem Brennstofftank verflüchtigtem Brennstoffdampf und ist zum Beispiel mit Aktivkohle gefüllt. Der obere Gehäuseteil 5 besitzt einen Abströmstutzen 9 zum Anschließen an ein Ansaugrohr der Brennkraftmaschine. Der Zuströmstutzen 8 und der Abströmstutzen 9 sind jeweils axial in den Gehäuseteilen 4 beziehungsweise 5 etwa fluchtend zueinander angeordnet. Im Innern des unteren Gehäuseteils 4 ist ein Elektromagnet 12 angeordne . Er weist ein topfförmiges Magnetgehäuse 14 mit einem einen Boden 25 des Magnetgehäuses 14 durchdringenden, koaxialen, hohlzylindrischen Magnetkern 15 und eine zylindrische Erregerspule 16 auf, die auf einem SpulenträgerAdsorption filter. The adsorption filter is used in a known manner for the intermediate storage of fuel vapor volatilized from the fuel tank and is filled with activated carbon, for example. The upper housing part 5 has an outflow connection 9 for connection to an intake pipe of the internal combustion engine. The inflow nozzle 8 and the outflow nozzle 9 are each arranged axially in the housing parts 4 and 5, approximately in alignment with one another. An electromagnet 12 is arranged in the interior of the lower housing part 4. It has a pot-shaped magnet housing 14 with a coaxial, hollow-cylindrical magnet core 15 penetrating a bottom 25 of the magnet housing 14 and a cylindrical excitation coil 16, which is on a coil carrier
17 sitzt und im Magnetgehäuse 14 den Magnetkern 15 umschließend einliegt. An dem Boden 25 des Magnetgehäuses 14 ist einstückig ein nach außen vorspringender Gewindestutzen17 sits and in the magnet housing 14, the magnetic core 15 surrounds. On the bottom 25 of the magnet housing 14 there is in one piece an outwardly projecting threaded connector
18 mit einem Innengewinde 19 ausgebildet, in welchem ein Außengewindeabschnitt 20 auf dem hohlzylindrischen Magnetkern 15 verschraubt ist . Durch Drehen des Magnetkerns 15 kann dieser im Magnetgehäuse 14 zu Justierzwecken axial verschoben werden. Der Magnetkern 15 hat eine vom hohlen Magnetkern 15 begrenzte, axiale Durchgangsöffnung 21, so daß Brennstoffdampf in der Durchgangsöffnung 21 vom Zuströmstutzen 8 zum Abströmstutzen 9 strömen kann.18 formed with an internal thread 19, in which an external thread section 20 is screwed onto the hollow cylindrical magnetic core 15. By rotating the magnetic core 15, it can be axially displaced in the magnet housing 14 for adjustment purposes. The magnetic core 15 has an axial through opening 21 which is delimited by the hollow magnetic core 15, so that fuel vapor can flow in the through opening 21 from the inflow nozzle 8 to the outflow nozzle 9.
Das Magnetgehäuse 14 mit dem Magnetkern 15 ist dabei so in den unteren Gehäuseteil 4 eingesetzt, daß zwischen einem Außenmantel 22 des Magnetgehäuses 14 und einer Innenwandung 23 des unteren Gehäuseteils 4 Axialkanäle 24 verbleiben, die beispielsweise in Umfangsrichtung um gleiche Winkel gegeneinander versetzt sind, so daß wie in Figur 1 dargestellt ist, zum Beispiel nur zwei Axialkanäle 24 zu sehen sind. Die Axialkanäle 24 stehen über einen im unteren Gehäuseteil 4 zwischen dem Boden 25 des Magnetgehäuses 14 und dem Zuströmstutzen 8 gelegenen Ringraum 27 einerseits mit dem Zuströmstutzen 8 und andererseits über Bohrungen 28, die nahe des offenen Endes des Magnetgehäuses 14 in das Magnetgehäuse 14 eingebracht sind, mit dem Innern des Magnetgehäuses 14 stromabwärts der Erregerspule 16 in Verbindung. Durch diese Axialkanäle 24 kann der in denThe magnet housing 14 with the magnetic core 15 is inserted into the lower housing part 4 in such a way that 4 axial channels 24 remain between an outer jacket 22 of the magnet housing 14 and an inner wall 23 of the lower housing part 4, for example in the circumferential direction at the same angle are offset from one another, so that, as shown in FIG. 1, only two axial channels 24 can be seen, for example. The axial channels 24 are located on the one hand in the lower housing part 4 between the bottom 25 of the magnet housing 14 and the inflow connector 8 annular space 27 on the one hand with the inflow connector 8 and on the other hand via bores 28 which are introduced into the magnet housing 14 near the open end of the magnet housing 14, in communication with the inside of the magnet housing 14 downstream of the excitation coil 16. Through these axial channels 24 can in the
Zuströmstutzen 8 eintretende Brennstoffdampf auch um das Magnetgehäuse 14 herumströmen und so hier entstehende Wärme abführen.Incoming fuel nozzle 8 also flow around the magnet housing 14 and thus dissipate the heat generated here.
Das Magnetgehäuse 14 hat einen abgebogenen Rand 29, der als Auflägeflansch für einen bügeiförmigen Ventilsitzkörper 31 dient. Der Ventilsitzkörper 31 bildet das Rückschlußjoch des Elektromagneten 12. Der Ventilsitzkörper 31 überdeckt das Magnetgehäuse 14 teilweise und ist mittels wenigstens zwei, in Figuren 2 und 3 dargestellten Paßlöchern 47 am unteren Gehäuseteil 4 befestigt. Der an dem Rand 29 aufliegende Ventilsitzkörper 31 ist dabei in einer einen U-förmigen Querschnitt aufweisenden, elastischen, ringförmigen Lageraufnahme 32 aufgenommen, die ihrerseits zwischen den beiden Gehäuseteilen 4 und 5 eingeklemmt ist. Ein aus magnetischem Material bestehendes Ventilglied 36 bildet zugleich den Anker des Elektromagneten 12 und ist an einer Blattfeder 33 befestigt, die randseitig zwischen dem Ventilsitzkörper 31 und dem Rand 29 eingespannt ist. Der Ventilsitzkörper 31 hat zumindest eine Ventilöffnung 34. Im Ausführungsbeispiel sind zwei spaltförmige Ventilöffnungen 34 vorgesehen, die, wie in Figur 2 dargestellt ist, beispielsweise eine halbkreisringförmige Form aufweisen und gegenüberliegend vorgesehen sind, so daß sie sich zu einer fiktiven Kreisform ergänzen. Es ist aber auch möglich, wie in Figur 3, einer Draufsicht auf den gemäß einer zweiten Ausführungsart ausgebildeten Ventilsitzkörper 31, dargestellt ist, die Ventilöffnungen 34 in einer U-Form auszubilden, die sich zu einem fiktiven Rechteck ergänzen lassen. Die beiden Ventilöffnungen 34 sind vom Ventilglied 36 verschließbar, so daß sich ein Ventildoppelsitz 37 ergibt. Wie in Figur 1 dargestellt ist, ist im Ventilglied 36 eine koaxial zum hohlzylindrischen Magnetkern 15 verlaufende Durchgangsöffnung 38 vorgesehen, durch die vom Zuströmstutzen 8 über die Durchgangsöffnung 21 des Magnetkerns 15 strömender Brennstoff bei geöffneten Ventilöffnungen 34 in den Abströmstutzen 9 strömen kann. Das Ventilglied 36 ist von einer Ventilschließfeder 43 in Ventilschließrichtung in Richtung des Abströmstutzens 9 beaufschlagt, die sich einerseits am Ventilglied 36 und anderseits an einem hülsenförmigen Ende 41 des Magnetkerns 15 abstützt.The magnet housing 14 has a bent edge 29, which serves as a support flange for a bow-shaped valve seat body 31. The valve seat body 31 forms the yoke of the electromagnet 12. The valve seat body 31 partially covers the magnet housing 14 and is fastened to the lower housing part 4 by means of at least two fitting holes 47 shown in FIGS. 2 and 3. The valve seat body 31 resting on the edge 29 is accommodated in an elastic, annular bearing receptacle 32 which has a U-shaped cross section and which in turn is clamped between the two housing parts 4 and 5. A valve member 36 made of magnetic material also forms the armature of the electromagnet 12 and is fastened to a leaf spring 33 which is clamped on the edge side between the valve seat body 31 and the edge 29. The valve seat body 31 has at least one valve opening 34. In the exemplary embodiment, two slit-shaped valve openings 34 are provided which, as shown in FIG. 2, have, for example, a semicircular shape and are provided opposite one another, so that they complement one another to form a fictitious circular shape. But it is also possible how FIG. 3, a top view of the valve seat body 31 designed according to a second embodiment, shows the valve openings 34 in a U-shape, which can be supplemented to form a fictitious rectangle. The two valve openings 34 can be closed by the valve member 36, so that a double valve seat 37 results. As shown in FIG. 1, a through opening 38 running coaxially to the hollow cylindrical magnetic core 15 is provided in the valve member 36, through which fuel flowing from the inflow nozzle 8 via the through opening 21 of the magnetic core 15 can flow into the outflow nozzle 9 when the valve openings 34 are open. The valve member 36 is acted upon by a valve closing spring 43 in the valve closing direction in the direction of the outflow connector 9, which is supported on the one hand on the valve member 36 and on the other hand on a sleeve-shaped end 41 of the magnetic core 15.
Das Ventilglied 36 trägt auf seiner dem Ventildoppelsitz 37 zugewandten Seite einen Dichtgummi 42 aus elastischemThe valve member 36 carries on its side facing the valve double seat 37 a sealing rubber 42 made of elastic
Material, zum Beispiel Elastomer. Der Dichtgummi 42 kleidet auch die Durchgangsöffnung 38 aus und steht etwas über eine dem Ventildoppelsitz 37 abgewandte Seite des Ventilgliedes 36 hinaus. Im stromlosen Zustand des Elektromagneten 12 drückt die Ventilschließfeder 43 das Ventilglied 36 mit dem Dichtgummi 42 auf den Ventildoppelsitz 37 und verschließt so die Ventilöffnungen 34. Im bestromten Zustand des Elektromagneten 12 wird das Ventilglied 36 mit seinem aus der Durchgangsöffnung 38 herausragenden Dichtgummi 42 gegen das Ende 41 des Magnetkerns 15 gedrückt, das einen Anschlag 44 für die Hübbewegung des Ventilgliedes 36 bildet. Mittels des vom Innengewinde 19 des Gewindestutzens 18 des Magnetgehäuses 14 und vom Außengewindeabschnitt 20 des Magnetkerns 15 gebildeten Einstellgewindes läßt sich der Anschlag 44 axial verschieben und dadurch die Durchflußmenge bei maximal vom Ventildoppelsitz 37 abgehobenen Ventilglied 36 festlegen. Die Ventilschließfeder 43 ist schwach dimensioniert, da bei einem Druckgefälle zwischen Abströmstutzen 9 und Zuströmstutzen 8 eine Saugwirkung auf das Ventilglied 36 in Richtung Ventilschließen ausgeübt und die Schließwirkung der Ventilschließfeder 43 unterstützt wird. Beim Betrieb der Brennkraftmaschine wird der Elektromagnet 12 von der Steuerelektronik eines nicht näher dargestellten Steuergeräts getaktet angesteuert, wofür am oberen Gehäuseteil 5 ein Steckeranschluß 50 vorgesehen ist. Die Taktfolgefrequenz wird durch den Betriebszustand der Brennkraftmaschine vorgegeben, so daß die über VentilÖffnungen 34 vom Zuströmstutzen 8 in den Abströmstutzen 9 übertretende Durchflußmenge an verflüchtigtem Brennstoffdampf entsprechend dosierbar ist.Material, for example elastomer. The sealing rubber 42 also lines the through opening 38 and projects somewhat beyond a side of the valve member 36 facing away from the valve double seat 37. In the de-energized state of the electromagnet 12, the valve closing spring 43 presses the valve member 36 with the sealing rubber 42 onto the valve double seat 37 and thus closes the valve openings 34. In the energized state of the electromagnet 12, the valve member 36 with its sealing rubber 42 protruding from the through opening 38 becomes against the end 41 of the magnetic core 15 pressed, which forms a stop 44 for the attractive movement of the valve member 36. By means of the adjusting thread formed by the internal thread 19 of the threaded connector 18 of the magnet housing 14 and by the external thread section 20 of the magnet core 15, the stop 44 can be axially displaced and thereby the flow rate with the valve member 36 lifted from the valve double seat 37 at the maximum. The valve closing spring 43 is weakly dimensioned since, in the event of a pressure drop between the outlet connection 9 and the inlet connection 8, a suction effect is exerted on the valve member 36 in the direction of valve closing and the closing effect of the valve closing spring 43 is supported. When the internal combustion engine is operating, the electromagnet 12 is actuated in a clocked manner by the control electronics of a control device (not shown in more detail), for which purpose a connector connection 50 is provided on the upper housing part 5. The cycle rate is predetermined by the operating state of the internal combustion engine, so that the flow rate of volatilized fuel vapor passing through valve openings 34 from the inflow nozzle 8 into the outflow nozzle 9 can be dosed accordingly.
An der dem Abströmstutzen 9 zugewandten Seite 49 des Ventilsitzkörpers 31 liegt ein Dichtring 51 an, der einen äußeren Ringraum 52 zwischen dem Ventilsitzkörper 31 und dem oberen Gehäuseteil 5 von einem mit den VentilÖffnungen 34 in Verbindung stehenden Innenraum 53 im Abströmstutzen 9 abdichtet. Der den Abströmstutzen 9 durchdringende Kanal ist in Form einer Laval-Düse 55 ausgebildet, die sich in bekannter Weise aus einem konvergenten Teil 56 und einem divergenten Teil 57 zusammensetzt. Die Laval-Düse 55 verjüngt sich dabei von einem ersten Eintrittsquerschnitt 60 stromabwärts in der Nähe des Ventilsitzkörpers 31 auf einen engsten Querschnitt 61, um sich dann vom engsten Querschnitt 61 auf einen Endquerschnitt 62 am stromabwärtigen Ende zu erweitern. Die Ausbildung der Querschnitte 60, 61, 62 erfolgt derart, daß der Eintrittsquerschnitt 60 zumindest gleich oder größer ist als der Endquerschnitt 62. Vorzugsweise ist der Eintrittsquerschnitt 60 1,1 bis 2 mal größer als der Endquerschnitt 62. Der engste Querschnitt 61 ist vorzugsweise 2 bis 4 mal kleiner ausgebildet als der Eintrittsquerschnitt 60. Die zwischen EintrittsquerschnittOn the side 49 of the valve seat body 31 facing the outflow connector 9 there is a sealing ring 51 which seals an outer annular space 52 between the valve seat body 31 and the upper housing part 5 of an interior 53 in the outflow connector 9 which is connected to the valve openings 34. The channel penetrating the outflow nozzle 9 is designed in the form of a Laval nozzle 55, which is composed in a known manner from a convergent part 56 and a divergent part 57. The Laval nozzle 55 tapers from a first inlet cross section 60 downstream in the vicinity of the valve seat body 31 to a narrowest cross section 61, in order to then widen from the narrowest cross section 61 to an end cross section 62 at the downstream end. The cross sections 60, 61, 62 are designed in such a way that the inlet cross section 60 is at least equal to or larger than the end cross section 62. The inlet cross section 60 is preferably 1.1 to 2 times larger than the end cross section 62. The narrowest cross section 61 is preferably 2 up to 4 times smaller than that Entry cross section 60. The between entry cross section
60 und Endquerschnitt 62 gemessene Länge der Laval-Düse 55 ist beispielsweise 3 bis 5 mal größer als ein Durchmesser am Eintrittsquerschnitt 60. Die Seite 49 des Ventilsitzkörpers 31 hat gegenüber der den Eintrittsquerschnitt 60 aufweisenden Eintrittsseite des Abströmstutzens 9 in Richtung der Ventillängsachse 2 einen Abstand, so daß zwischen der Seite 49, der Eintrittsseite des Abströmstutzens 9 und dem Dichtring 51 ein Zwischenraum 63 gebildet wird, der senkrecht zur Ventillängsachse 2 mindestens eine seitliche Erstreckung hat, die so groß wie der Durchmesser des Eintrittsquerschnitts 60 ist, und in den die Ventilöffnungen 34 münden. Da vom Ventilglied 36 zum Absteuern nur die beiden Ventilöffnungen 34 des Ventilsitzkörpers 31 abgedeckt werden müssen, ist es möglich, durch einfaches Ändern des Ventilhubes des Ventilgliedes 36 diesen optimal an den engsten Querschnitt60 and the final cross-section 62, the length of the Laval nozzle 55 measured is, for example, 3 to 5 times larger than a diameter at the inlet cross-section 60. The side 49 of the valve seat body 31 is at a distance from the inlet side of the outflow connector 9 having the inlet cross-section 60 in the direction of the valve longitudinal axis 2, so that an intermediate space 63 is formed between the side 49, the inlet side of the outflow connector 9 and the sealing ring 51, which has at least one lateral extension perpendicular to the longitudinal axis 2 of the valve, which is as large as the diameter of the inlet cross-section 60, and into which the valve openings 34 flow out. Since only the two valve openings 34 of the valve seat body 31 have to be covered by the valve member 36 for actuation, it is possible to optimally adjust the valve cross section of the valve member 36 by simply changing the valve lift
61 der Laval-Düse 55 anzupassen, ohne daß es hierzu einer Veränderung der Größenverhältnisse der Querschnitte der Laval-Düse 55 bedarf. Die beiden Querschnitte der61 to adapt the Laval nozzle 55 without this requiring a change in the size ratios of the cross sections of the Laval nozzle 55. The two cross sections of the
Ventilöffnungen 34 sind wesentlich kleiner ausgebildet aus ein Eintrittsquerschnitt 60 der Laval-Düse 55. Vorzugsweise betragen beide Querschnitte zusammen etwa nur 10 bis 20 Prozent des Eintrittsquerschnitts 60. Aufgrund des relativ keinen Querschnittes beider VentilÖffnungen 34 kann die Unterbrechung der BrennstoffStrömung mittels des Ventilgliedes 36 mit hoher Geschwindigkeit durchgeführt werden, so daß sich ein besonders schnell schaltendes Ventil 1 verwirklichen läßt. Die Anpassung an gewünschte Durchflußmengen des Ventils 1 ist dabei durch einfaches Ändern des Ventilhubs beziehungsweise durch Drehen des Magnetkerns 15 im Magnetgehäuse 14 möglich. Valve openings 34 are made substantially smaller from an inlet cross-section 60 of the Laval nozzle 55. Both cross-sections together are preferably only about 10 to 20 percent of the inlet cross-section 60. Due to the relatively no cross-section of both valve openings 34, the interruption of the fuel flow by means of valve member 36 can be high Speed are carried out so that a particularly fast switching valve 1 can be realized. The adaptation to the desired flow rates of the valve 1 is possible by simply changing the valve stroke or by rotating the magnetic core 15 in the magnet housing 14.

Claims

Patentansprüche claims
1. Ventil zum dosierten Einleiten von aus einem Brennstofftank einer Brennkraftmaschine verflüchtigtem Brennstoffdampf in ein Ansaugrohr der Brennkraftmaschine, mit einer Ventillängsachse, mit einem Ventilgehäuse, das einen Zuströmstutzen zum Anschließen an einen Brennstofftank oder an einen diesem nachgeschalteten Adsorptionsfilter für den verflüchtigten Brennstoff hat, und mit einem Abströmstutzen zum Anschließen an das Ansaugrohr, mit einem zwischen Zuströmstutzen und Abströmstutzen im Innern des Ventilgehäuses untergebrachten Ventilglied, das von einem einen Magnetkern aufweisenden Elektromagneten betätigbar ist und mit einem an einem Ventilsitzkörper ausgebildeten Ventilsitz zusammenwirkt, und mit einer im Abströmstutzen ausgebildeten Düse, die einen konvergent und einen divergent gestalteten Teil aufweist, dadurch gekennzeichnet, daß der Ventilsitz (37) und ein Eintrittsquerschnitt (60) der Düse (55) in Richtung der Ventillängsachse (2) einen Abstand zueinander aufweisen.1.Valve for metered introduction of fuel vapor volatilized from a fuel tank of an internal combustion engine into an intake pipe of the internal combustion engine, with a longitudinal valve axis, with a valve housing which has an inflow connection piece for connection to a fuel tank or to an adsorption filter for the volatilized fuel connected downstream thereof, and with an outflow connection for connection to the intake pipe, with a valve member accommodated between the inflow connection and outflow connection inside the valve housing, which can be actuated by an electromagnet having a magnetic core and cooperates with a valve seat formed on a valve seat body, and with a nozzle formed in the outflow connection, the one has a convergent part and a divergent part, characterized in that the valve seat (37) and an inlet cross-section (60) of the nozzle (55) are at a distance from one another in the direction of the valve longitudinal axis (2) exhibit.
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der der Ventilsitzkörper (31) und der Abströmstutzen (9) als eigenständige Teile ausgebildet sind. 2. Valve according to claim 1, characterized in that the valve seat body (31) and the outflow nozzle (9) are designed as independent parts.
3. Ventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Ventilsitzkörper (31) ein Rückschlußjoch des Elektromagneten (12) bildet und mit Abstand von dem Eintrittsquerschnitt (60) der Düse (55) im Ventil (l) untergebracht ist.3. Valve according to claim 1 or 2, characterized in that the valve seat body (31) forms a yoke of the electromagnet (12) and is housed at a distance from the inlet cross-section (60) of the nozzle (55) in the valve (l).
4. Ventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß zwischen Ventilsitzkörper (31) und Abströmstutzen (9) ein Dichtring (51) vorgesehen ist.4. Valve according to claim 2 or 3, characterized in that a sealing ring (51) is provided between the valve seat body (31) and outflow nozzle (9).
5. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Querschnitt einer zumindest einen vom Ventilsitz (37) umgebenen Öffnung (34) im Ventilsitzkörper (31) wesentlich kleiner ausgebildet ist als der Eintrittsquerschnitt (60) der Düse (55) .5. Valve according to claim 1, characterized in that the cross section of at least one of the valve seat (37) surrounded opening (34) in the valve seat body (31) is formed substantially smaller than the inlet cross section (60) of the nozzle (55).
6. Ventil nach Anspruch 5, dadurch gekennzeichnet, daß der Querschnitt der zumindest einen Öffnung (34) etwa 10 bis 20 Prozent des Eintrittsquerschnitts (60) der Düse (55) beträgt.6. Valve according to claim 5, characterized in that the cross section of the at least one opening (34) is about 10 to 20 percent of the inlet cross section (60) of the nozzle (55).
7. Ventil nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß zwei Öffnungen (34) im Ventilsitzkörper (31) vorgesehen sind, die eine halbkreisringförmige Form oder eine U-Form aufweisen.7. Valve according to claim 5 or 6, characterized in that two openings (34) in the valve seat body (31) are provided which have a semi-circular shape or a U-shape.
8. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Eintrittsquerschnitt (60) der Düse (55) zumindest 1,1 bis 2 mal größer ist als ein Endquerschnitt (62) der Düse (55) .8. Valve according to claim 1, characterized in that the inlet cross-section (60) of the nozzle (55) is at least 1.1 to 2 times larger than an end cross-section (62) of the nozzle (55).
9. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß die zwischen dem Eintrittsquerschnitt (60) und einem Endquerschnitt (62) gemessene Länge der Düse (55) 3 bis 5 mal größer ist als ein Durchmesser am Eintrittsquerschnitt (60) . 9. Valve according to claim 1, characterized in that the length of the nozzle (55) measured between the inlet cross section (60) and an end cross section (62) is 3 to 5 times larger than a diameter at the inlet cross section (60).
10. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß die Querschnittsübergänge der Düse (55) kontinuierlich ineinander übergehend ausgebildet sind.10. Valve according to claim 1, characterized in that the cross-sectional transitions of the nozzle (55) are continuously merged.
11. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der zwischen einer Anlage des Ventilgliedes (36) an dem Ventilsitzkörper (31) und einer Anlage an dem Magnetkern11. Valve according to claim 1, characterized in that between an abutment of the valve member (36) on the valve seat body (31) and an abutment on the magnetic core
(15) sich ergebende Ventilhub des Ventilgliedes (36) in Abhängigkeit von einem engsten Querschnitt (61) der Düse (55) gewählt ist.(15) resulting valve stroke of the valve member (36) is selected as a function of a narrowest cross section (61) of the nozzle (55).
12. Ventil nach Anspruch 11, dadurch gekennzeichnet, daß der Ventilhub des Ventilgliedes (36) mittels des Magnetkerns (15) einstellbar ist. 12. Valve according to claim 11, characterized in that the valve stroke of the valve member (36) by means of the magnetic core (15) is adjustable.
EP98912262A 1997-05-23 1998-02-18 Valve for proportioned supply of volatilized fuel Expired - Lifetime EP0914552B1 (en)

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DE19721562 1997-05-23
DE19721562A DE19721562A1 (en) 1997-05-23 1997-05-23 Valve for the metered introduction of volatilized fuel
PCT/DE1998/000472 WO1998053195A1 (en) 1997-05-23 1998-02-18 Valve for proportioned supply of volatilized fuel

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US6149126A (en) 2000-11-21
DE19721562A1 (en) 1998-11-26
RU2195571C2 (en) 2002-12-27
KR20000029436A (en) 2000-05-25
JP2000515606A (en) 2000-11-21
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EP0914552B1 (en) 2003-05-07
BR9804944A (en) 1999-08-24

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