EP0800621A1 - Soupape pour doser l'injection d'une vapeur de carburant provenant du reservoir de carburant d'un moteur a combustion interne - Google Patents

Soupape pour doser l'injection d'une vapeur de carburant provenant du reservoir de carburant d'un moteur a combustion interne

Info

Publication number
EP0800621A1
EP0800621A1 EP96918613A EP96918613A EP0800621A1 EP 0800621 A1 EP0800621 A1 EP 0800621A1 EP 96918613 A EP96918613 A EP 96918613A EP 96918613 A EP96918613 A EP 96918613A EP 0800621 A1 EP0800621 A1 EP 0800621A1
Authority
EP
European Patent Office
Prior art keywords
valve
armature
electromagnet
valve according
fuel
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
EP96918613A
Other languages
German (de)
English (en)
Other versions
EP0800621B1 (fr
Inventor
Wolfgang Schulz
Georg Mallebrein
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 EP0800621A1 publication Critical patent/EP0800621A1/fr
Application granted granted Critical
Publication of EP0800621B1 publication Critical patent/EP0800621B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M2025/0845—Electromagnetic valves

Definitions

  • the invention is based on a valve for the metered introduction of fuel vapor 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 for the metered introduction of fuel vapor 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 (EP-PS 0 528 849)
  • the fuel vapor via a Inlet nozzle is supplied in order to discharge it in a metered manner into the intake pipe via an outlet nozzle provided on the valve.
  • the inflow nozzle of the valve is connected, for example, via a hose line to an adsorption filter, which temporarily stores the fuel vapor evaporated from the fuel tank.
  • the valve is designed to be electromagnetically actuated and for this purpose has a magnetic armature which can be axially displaced by the magnetic forces of an electromagnet against the force of a valve spring.
  • a magnetic armature which can be axially displaced by the magnetic forces of an electromagnet against the force of a valve spring.
  • an end region of the armature designed as a valve closing member is pressed against a valve seat by means of the valve spring in order to interrupt a flow connection from the inlet connection to the outlet connection.
  • the armature moves against the force of the valve spring and lifts off with its end region designed as a valve closing member from the valve seat, one
  • the metering opening on the outflow nozzle is opened so that a certain fuel vapor volume can flow from the inflow pipe via the outflow pipe into the intake pipe.
  • the solenoid of the valve is controlled by means of a so-called pulse-width modulated signal, which is composed of a pulse train of an electric current which flows through the excitation coil of the electromagnet at a constant frequency.
  • the pulse duration of the individual current pulses is increased or decreased by means of control electronics in order to obtain a continuously variable attraction force of the electromagnet on the armature.
  • a certain axial position of the armature is set, in which it remains, in order to be replaced by one of the axial position of the
  • Valve closing member of the armature-dependent throttling of the flow at the metering opening to deliver a certain volume of fuel vapor via the metering opening into the outflow nozzle depends on the pulse duration of the individual current pulses and is determined by the so-called duty cycle.
  • the duty cycle indicates the quotient of the pulse duration to the pulse interval (period) of the individual pulses. Due to frictional effects and spring forces, it only takes place after a certain one
  • Duty cycle which is also referred to as an opening duty cycle, a lifting of the armature from its valve seat.
  • Hysteresis effects have the consequence that the opening duty cycle can change with each renewed activation, so that an exact metering is the smallest
  • the described, continuously operating valve emits an essentially linearly increasing fuel vapor flow with increasing pulse duty factor.
  • the linear nature of the valve described makes it difficult to meter the smallest fuel vapor volume with a relatively small duty cycle.
  • attempts are therefore made to compensate for this disadvantage by means of a second, vacuum-actuated valve.
  • the second vacuum-actuated valve is arranged parallel to the first electromagnetically actuable valve, which opens when a certain vacuum is reached in the intake pipe in order to introduce more fuel vapor into the intake pipe.
  • such a system consisting of two valves is complex.
  • the specified valve combination requires a long switch-off time to interrupt the fuel supply, so that a sensitive
  • valve according to the invention with the characterizing features of claim 1 has the advantage, an excellent small amount metering and a simple structure.
  • the measures listed in the subclaims allow advantageous developments of the valve specified in claim 1.
  • a pressure compensation connection formed in the valve which makes it possible to measure the fuel vapor flow emitted by the valve independently of the negative pressure prevailing in the intake pipe.
  • an intended compensation of the temperature dependency of the excitation coil of the electromagnet which makes it possible to dispense with a complex current-controlled output stage and to replace it with a control in which voltage pulses with a preferably relatively high frequency are supplied to the excitation coil in order to make a particularly sensitive metering of the fuel vapor volume.
  • Another special advantage is the special design of the metering opening in the valve, which gives the valve an exponential opening characteristic in order to minimize the absolute error in the small quantity range. The exponential opening characteristic also counteracts errors due to hysteresis effects, so that a further improvement in the small-quantity meterability of the valve is possible.
  • FIG. 1 shows a longitudinal section of a valve designed according to the invention
  • FIG. 2 shows a first section along a line II-II in FIG. 1 according to a first according to the invention
  • Figure 3 shows a second section along a line III-III in Figure 1 according to a second embodiment of the invention
  • Figure 4 is a diagram showing the opening characteristics of the valve designed according to the invention (course B) compared to known valves (course A).
  • valve 1 shown in longitudinal section in FIG. 1 is used for the metered introduction of a fuel tank 3, not shown, in particular mixture-compressing, spark-ignited internal combustion engine evaporated fuel vapor into an intake pipe 4 of the internal combustion engine.
  • Valve 1 is part of a fuel evaporation retention system of the internal combustion engine, the mode of operation of which can be found, for example, on the pages Bosch and Technical Documentation, Motor Management Motronic, Second Edition, August 1993, on pages 48 and 49.
  • the valve 1 has, for example, a valve housing consisting of three parts, which is composed of a cylindrical basic housing 6, a housing cover 7 which can be placed on the basic housing 6 and a lower housing part 8.
  • the cylindrical basic housing 6, the housing cover 7 and the lower housing part 8 are preferably made of plastic, for example using plastic injection molding technology.
  • the lower housing part 8 has an inlet connection 10 and an outlet connection 11.
  • the inflow nozzle 10 serves to connect the valve 1, for example via a first hose line 14, to the fuel tank 3 or, as shown in FIG. 1, to an adsorption filter 15 connected to the fuel tank 3.
  • the adsorption filter 15 is provided with a storage medium for fuel vapor , in particular filled with activated carbon, and is used for the intermediate storage of fuel vapor volatilized from the fuel tank 3.
  • the outflow connector 11 extends, for example, in the axial direction from the lower housing part 8 along a longitudinal axis 17 of the valve 1 and is provided for connecting a second hose line 18.
  • the second hose line 18 opens, for example, downstream of a throttle valve 19 rotatably accommodated in the intake pipe 4 into the intake pipe 4.
  • the inflow nozzle 10 extends, for example, transversely to the longitudinal axis 17 of the valve 1 and projects radially from the lower housing part 8.
  • an electromagnet 22 is accommodated in a magnet housing 26, which has a cylindrical excitation coil 23 and a magnetic core 37.
  • the magnet housing 26 is sleeve-shaped and carries in its interior the excitation coil 23, which is wound on a coil carrier 27 made, for example, of plastic.
  • the excitation coil 23 surrounds a preferably metallic armature 25 of the valve 1 which can be attracted by magnetic forces in order to move it in the energized state of the excitation coil 23 against the force of a valve spring 50.
  • the armature 25 is axially displaceably mounted in a guide sleeve 24 accommodated in the basic housing 6.
  • the coil carrier 27 is accommodated at a radial distance from an outer surface 39 of the smaller-diameter guide sleeve 24 in the interior of the basic housing 6 and extends radially to an inner wall 29 of the magnet housing 26.
  • the radial distance from the coil carrier 27 to the outer surface 39 of the guide sleeve 24 prevents jamming of the armature 25 due to thermal expansion, for example the excitation coil 23.
  • the coil carrier 27 lies axially against an annular extension 28 of the guide sleeve 24.
  • the shoulder 28 of the guide sleeve 24 also extends radially as far as the inner wall 29 of the magnet housing 26.
  • a contact disk 31 is also accommodated, which is at a radial distance from an outer surface 33 of the armature 25 is arranged.
  • the armature 25 has a recess 36 on its end 32 facing the housing cover 7, said recess being cylindrical, for example, and at least partially surrounding the sleeve-shaped magnetic core 37.
  • the magnetic core 37 can be designed to be axially displaceable.
  • the magnetic core 37 has, for example, an external thread section 38 which engages in an internal thread 40 which is provided in a magnetic base 35 covering the sleeve-shaped magnetic housing 26 in order to correspondingly axially shift the magnetic core 37 by rotating the magnetic core 37, so that an adjustable armature stop for the anchor 25 is present.
  • the armature 25 is hollow-cylindrical and has a through-opening 42 which extends in the axial direction from the recess 36 at the end 32 of the armature 25 shown at the top in FIG. 1 to its end 34 located in the lower housing part 8.
  • a circumferential one that radially enlarges the passage opening 42
  • Heel 45 designed to receive the valve spring 50 between the heel 45 and a recess 46 provided in the sleeve-shaped magnetic core 37.
  • the valve spring 50 is supported on the one hand in the recess 45 on the magnetic core 37 and on the other hand on the shoulder 45 in the through opening
  • valve spring 50 By means of the valve spring 50, the armature 25 in the de-energized state of the excitation coil 23 is pressed tightly with its end 34 against an annular valve seat 54 covered by an annular sealing ring 53, so that a flow connection 74 between the inflow connection piece 10 and
  • Outflow nozzle 11 is closed.
  • the valve seat 54 is provided on an end 55 of the outflow connector 11 located in the interior of the lower housing part 8 and, as is shown in the half of the valve 1 lying on the left of the longitudinal axis 17, can be tightly closed by the armature 25.
  • the sealing ring 53 consists of an elastic material, for example rubber.
  • the magnetic armature 25 is affected by the magnetic forces of the
  • Electromagnets 22 are attracted to the magnetic core 37 differently and occupies each axial intermediate position and as End position, as shown in the right half of the longitudinal axis 17 of the valve 1, its maximum open position, in which the annular bottom surface 48 of the recess 36 of the armature 25 bears against the annular surface 49 of the magnetic core 37.
  • the outer surface 33 of the armature opens at the circumference of a metering opening 56 which runs parallel to the longitudinal axis 17 at an end 51 of the inflow nozzle 10 located in the basic housing 6, so that, as shown in FIG 1 marked arrow 57, fuel vapor passes from the inflow nozzle 10 through the metering opening 56 into a space 79 delimited between the valve seat 54 and an end face 73 of the armature 25, in order to then continue to flow into the outflow nozzle 11 via the valve seat 54.
  • a smaller part of the fuel vapor passes into the passage opening 42 of the armature 25, from there into the recess 46 of the magnetic core 37 and from the recess 46 via an opening 60 in the magnetic core 37 to get into a space 62 which is sealed off from the surroundings by an inner wall 64 of the housing cover 7, the magnetic core 37 and the magnetic base 35 of the magnet housing 26.
  • a pressure compensation connection 70 which is provided in the basic housing 6 and in the lower housing part 8, for example in the form of a bore, and which opens into the outflow connection 11 downstream of the valve seat 54.
  • the partial flow of the fuel vapor identified by the arrows 58, 59 and 61 in FIG. 1 flows around the valve seat 54.
  • the main stream of the fuel vapor flowing in the direction of arrow 57 from the inflow neck 10 to the outflow neck 11 mixes with the partial stream flowing in the direction of the arrows 58, 59 and 61 downstream of the valve seat 54 and then from the outflow neck 11 to Example to get into the intake pipe 4 via the second hose line 18.
  • Dosing opening 56 is more or less released from its outer surface 33, so that the fuel vapor flow passing from the inlet nozzle 10 into the outlet nozzle 11 is appropriately metered.
  • the stroke of the armature 25 working against the valve spring 50 is determined by the strength of the magnetic field of the electromagnet 22.
  • an electronic control unit 80 is provided which is electrically connected to the electromagnet 22 via an electrical line 81 and via a plug connection 82 integrally molded on the housing cover 7.
  • the electronic control device 80 transmits to the electromagnet 22 a drive pulse sequence of an electrical voltage with a relatively high frequency of, for example, 100 Hertz.
  • the control pulse sequence is emitted by the electronic control unit 80 with a duty cycle that can be changed by the control unit 80.
  • the pulse duty factor indicates, for example, the quotient of the pulse duration to the pulse interval (period duration) of the successive pulses.
  • Such control is known to the person skilled in the art as so-called pulse-width modulation.
  • the excitation coil 23 preferably has an excitation winding which has an almost constant resistance value regardless of the temperature influences of the
  • Has valve 1 Such a temperature-compensated excitation winding can be constructed, for example, from two windings which are made of different materials, the resistance values of which are chosen such that the temperature dependence of the resistance value of both is compensated
  • a winding of the excitation coil 23 can consist of a material which has a positive temperature coefficient (PTC thermistor) and the other winding consists of a material that has a negative temperature coefficient (NTC thermistor).
  • PTC thermistor positive temperature coefficient
  • NTC thermistor negative temperature coefficient
  • an output stage can therefore be used which supplies the electromagnet 22 with a voltage pulse sequence, preferably at a relatively high frequency.
  • a voltage pulse sequence can be implemented technically in a particularly simple manner, for example in the form of a transistor circuit which the
  • DC voltage source of a motor vehicle for example that of a starter battery, is used in order to switch back and forth between two predetermined values, for example 12 volts and 0 volts.
  • a voltage pulse sequence causes an average current in the excitation coil 23, which induces a magnetic field of a certain strength in order to move the armature 25 away from the valve seat 54 against the force of the valve spring 50 and to bring it into a specific axial position.
  • the axial end position of the armature 25 depends on the applied duty cycle of the voltage pulse train. If no voltage is applied to the excitation coil 23 or no current flows in the excitation coil 23, the armature 25 is removed from the
  • Valve spring 50 pressed against the valve seat 54.
  • the armature 25 rests with its outer surface 33 on the sealing ring 53 and covers the metering opening 56 of the inflow connector 10, so that a flow connection from the inflow connector 10 to the outflow connector 11 is interrupted.
  • the metering opening 56 is designed in the form of an aperture, the opening cross section of which is designed such that the valve 1 is given an exponential opening characteristic.
  • Figure 2 a sectional view along a line II-II in Figure 1, a first embodiment of the invention.
  • the metering opening 56 has a V-shape with a cross-sectional area which is delimited by two cross-sectional borders 75, 76 which converge towards one another in the direction of the valve seat 54 and a circular arc section 77.
  • a small gap can also remain between the cross-sectional borders 75, 76 in the region of their smallest distance from one another.
  • the funnel-shaped design of the cross-sectional borders 75, 76 of the metering opening 56 results in that with increasing piston stroke H of the armature 25 an increasingly larger cross-sectional area of the metering opening 56, limited by the cross-sectional borders 75, 76 and the end face 73 of the anchor 25, is released, so that the volume of the fuel vapor flowing through the metering opening 56 can increase accordingly.
  • Range of larger duty cycles causes a slight change in the duty cycle T compared to a valve with a linear opening characteristic (curve A), a relatively large change in the volume flow, so that rapid control of high volume flows is possible.
  • the metering opening 56 can also be designed in such a way that the cross-sectional boundaries 75, 76 have a curve which, based on that in FIG 3 drawn in coordinate axes x, y of a Cartesian coordinate system with an x axis parallel to the longitudinal axis 17, of an exponential function, in particular a natural exponential function, can be described. They have
  • the maximum stroke H of the armature 25 can be set such that the armature 25 with its end face 73 at maximum stroke, at most end points 85, 86 of the
  • Cross-sectional borders 75 and 76 are reached so that the armature 25 only exposes a cross-sectional area of the metering opening 56 with exponential cross-sectional borders 75, 76.
  • the pressure compensation connection 70 provided in the valve housing 6, 7, 8 also enables the underpressure of the intake pipe 4 in the raised state of the armature 25 both on the end face 73 of the armature 25 and on the opposite bottom surface 48 of the
  • Recess 36 on armature 25 prevails.
  • the end face 73 and the bottom face 48 of the armature 25 preferably have approximately an equal area of attack, whereby a pressure equalization or force equalization on the armature 25 is effected at different intake manifold pressures, so that the metering of the fuel vapor volume is independent of the negative pressure prevailing in the intake manifold 4.
  • the flow paths 10, 11, 42, 62, 66, 70 of the fuel vapor in the valve 1 from the environment, in particular with respect to an interior space 89 of the electromagnet 22 that is subjected to atmospheric pressure.
  • Sealing is carried out, for example, by means of a seal 88 which is designed in the form of a sealing sleeve which, for example, lies tightly against the inside of the outer surface 33 of the armature 25 in the lower housing part 8 and is clamped radially on the outside between the base housing 6 and the lower housing part 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Les soupapes d'aération de réservoirs connues qui dosent en continu le flux de la vapeur de carburant, possèdent des caractéristiques linéaires d'ouverture qui ne permettent pas le dosage précis de petites quantités de vapeur de carburant. L'invention concerne une soupape (1) servant à doser l'injection dans un tuyau (4) d'admission du moteur à combustion interne d'une vapeur de carburant, laquelle provient du réservoir (3) de carburant d'un moteur à combustion. Ladite soupape comporte un carter (8) possédant une tubulure (10) d'entrée, destinée au raccordement à une tubulure d'aération du réservoir (3) de carburant ou à un filtre (15) d'absorption monté en aval de cette dernière, et une tubulure (11) de sortie, destinée au raccordement à un tuyau (4) d'admission, ainsi qu'un induit (25) logé à l'intérieur du logement (6) de soupape et commandé par un électroaimant (22). Ledit induit ferme l'orifice de dosage (56) d'un dispositf (74) de connexion de flux entre la tubulure (10) d'entrée et la tubulure (11) de sortie en étant pressé contre un siège (54) de soupape par un ressort (50) lorsque l'électroaimant (22) n'est pas alimenté en courant ou bien ouvre plus ou moins ledit orifice de dosage (56) lorsque l'électroaimant (22) est parcouru par du courant. L'orifice de dosage (56) présente une surface transversale en forme de V pour un meilleur dosage. La soupape selon l'invention est particulièrement adaptée à l'introduction dans le tuyau d'admission du moteur à combustion d'une vapeur de carburant qui provient d'un réservoir de carburant d'un moteur à combustion interne à compression du mélange et à allumage commandé.
EP96918613A 1995-10-27 1996-06-26 Soupape pour doser l'injection d'une vapeur de carburant provenant du reservoir de carburant d'un moteur a combustion interne Expired - Lifetime EP0800621B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19540021A DE19540021A1 (de) 1995-10-27 1995-10-27 Ventil zum dosierten Einleiten von aus einem Brennstofftank einer Brennkraftmaschine verflüchtigtem Brennstoffdampf
DE19540021 1995-10-27
PCT/DE1996/001120 WO1997016640A1 (fr) 1995-10-27 1996-06-26 Soupape pour doser l'injection d'une vapeur de carburant provenant du reservoir de carburant d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0800621A1 true EP0800621A1 (fr) 1997-10-15
EP0800621B1 EP0800621B1 (fr) 1998-12-02

Family

ID=7775927

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96918613A Expired - Lifetime EP0800621B1 (fr) 1995-10-27 1996-06-26 Soupape pour doser l'injection d'une vapeur de carburant provenant du reservoir de carburant d'un moteur a combustion interne

Country Status (8)

Country Link
US (1) US5791318A (fr)
EP (1) EP0800621B1 (fr)
JP (1) JPH10512346A (fr)
KR (1) KR980700514A (fr)
CN (1) CN1166195A (fr)
DE (2) DE19540021A1 (fr)
ES (1) ES2126404T3 (fr)
WO (1) WO1997016640A1 (fr)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6000677A (en) * 1997-08-25 1999-12-14 Siemens Canada Limited Automotive emission control valve with a counter-force mechanism
DE29717078U1 (de) * 1997-09-24 1997-11-13 Bosch Gmbh Robert Ventileinrichtung
JPH11202947A (ja) * 1998-01-09 1999-07-30 Sumitomo Electric Ind Ltd 電磁比例圧力制御弁の駆動制御方法
DE19807503A1 (de) 1998-02-21 1999-08-26 Bosch Gmbh Robert Ventileinrichtung
DE19810212A1 (de) * 1998-03-10 1999-09-16 Bosch Gmbh Robert Ventileinrichtung
US6205982B1 (en) * 1998-05-15 2001-03-27 Chrysler Corporation Proportional purge solenoid control system
DE19853103A1 (de) * 1998-11-18 2000-05-25 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
US6412335B1 (en) * 2000-11-08 2002-07-02 Eaton Corporation Low current solenoid valve
DE10242219A1 (de) * 2002-09-12 2004-03-25 Robert Bosch Gmbh Kraftstoffzumesseinheit für eine Kraftstoffeinspritzanlage
DE10310109B4 (de) 2003-03-06 2009-08-20 Carl Freudenberg Kg Anordnung zum dosierten Einspeisen von flüchtigen Kraftstoffbestandteilen, insbesondere in das Ansaugrohr einer Verbrennungskraftmaschine eines Kraftfahrzeugs
US7044111B2 (en) * 2003-08-07 2006-05-16 Siemens Vdo Automotive Inc. Purge valve having permanent magnet armature
KR100577561B1 (ko) * 2004-01-12 2006-05-08 삼성전자주식회사 반도체 제조 설비의 배기압력 제어장치
DE102008040870A1 (de) * 2008-07-30 2010-02-04 Robert Bosch Gmbh Vorrichtung zum dosierten Zumessen strömender Medien
US9759424B2 (en) * 2008-10-29 2017-09-12 United Technologies Corporation Systems and methods involving reduced thermo-acoustic coupling of gas turbine engine augmentors
DE102010005046B4 (de) * 2010-01-20 2016-05-04 Audi Ag Vorrichtung zum Be- und Entlüften einer Kraftstoffanlage
DE102011003924B4 (de) * 2011-02-10 2015-01-08 Zf Friedrichshafen Ag Verstellbares Dämpfventil für einen Schwingungsdämpfer
DE102012005996A1 (de) * 2012-03-24 2013-10-10 Audi Ag Verfahren zum Betreiben einer Tankeinrichtung sowie entsprechende Tankeinrichtung
WO2013143675A1 (fr) 2012-03-24 2013-10-03 Audi Ag Procédé pour faire fonctionner un système de réservoir, et système de réservoir correspondant
US9194291B2 (en) * 2012-08-24 2015-11-24 Hamilton Sundstrand Corporation Turbomachine windmill bypass valve
WO2016035654A1 (fr) * 2014-09-01 2016-03-10 愛三工業株式会社 Dispositif de traitement de carburant evapore
US10060378B2 (en) * 2016-05-20 2018-08-28 Denso International America, Inc. Inductive positive crankcase ventilation valve position sensor
CN106195375A (zh) * 2016-07-20 2016-12-07 郦强 压力油箱用保压阀装置
KR102463193B1 (ko) * 2017-12-19 2022-11-03 현대자동차 주식회사 퍼지 제어 솔레노이드 밸브

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2764995A (en) * 1952-08-18 1956-10-02 Gerber Prod Sliding plug valve
US3080885A (en) * 1960-04-25 1963-03-12 Parker Hannifin Corp Variable area valve
JPS5412464U (fr) * 1977-06-28 1979-01-26
US4326489A (en) * 1979-12-27 1982-04-27 Ford Motor Company Proportional flow fuel vapor purge control device
US4395991A (en) * 1981-01-23 1983-08-02 Yamaha Hatsudoki Kabushiki Kaisha Emission preventing system of evaporated fuel for internal combustion engine
US4471942A (en) * 1982-09-23 1984-09-18 Whitman Medical Corporation In-line valve for administering parenteral liquids
US5205537A (en) * 1984-01-12 1993-04-27 Pfeiffer Robert W Valve with enhanced rangeability and logarithmic flow characteristic
DE3411333C2 (de) * 1984-03-28 1986-07-24 Daimler-Benz Ag, 7000 Stuttgart Zumeßeinrichtung für eine Kraftstoffeinspritzanlage für eine gemischverdichtende, fremdgezündete Brennkraftmaschine
DE8612504U1 (fr) * 1986-05-07 1992-05-14 Luetzke, Klaus, Dr.-Ing., 4100 Duisburg, De
DE3639817C1 (en) * 1986-11-21 1987-10-22 Pierburg Gmbh & Co Kg Process and apparatus for the adsorptive removal of hydrocarbon vapours from internal combustion systems and regeneration of the adsorbent
DE3732553A1 (de) * 1987-09-26 1989-04-13 Bosch Gmbh Robert Magnetventil
US5199404A (en) * 1990-03-08 1993-04-06 Siemens Automotive Limited Regulated flow canister purge system
US5115785A (en) * 1990-05-01 1992-05-26 Siemens Automotive Limited Carbon canister purge system
DE4244113A1 (de) * 1992-12-24 1994-06-30 Bosch Gmbh Robert Ventil zum dosierten Einleiten von verflüchtigtem Brennstoff in einen Ansaugkanal einer Brennkraftmaschine
DE4329396A1 (de) * 1993-09-01 1995-03-02 Pierburg Gmbh Elektropneumatisches Steuerventil
US5462253A (en) * 1994-07-22 1995-10-31 General Motors Corporation Dual slope flow control valve
ES2114252T3 (es) * 1994-08-30 1998-05-16 Pierburg Ag Valvula electromagnetica de maniobra.
US5535725A (en) * 1994-09-19 1996-07-16 Hi-Stat Manufacturing Co., Inc. Flow control solenoid means

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9716640A1 *

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KR980700514A (ko) 1998-03-30
WO1997016640A1 (fr) 1997-05-09
DE59600906D1 (de) 1999-01-14
EP0800621B1 (fr) 1998-12-02
US5791318A (en) 1998-08-11
JPH10512346A (ja) 1998-11-24
DE19540021A1 (de) 1997-04-30
ES2126404T3 (es) 1999-03-16
CN1166195A (zh) 1997-11-26

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