EP0857252A1 - Soupape de retour de gaz d'echappement - Google Patents

Soupape de retour de gaz d'echappement

Info

Publication number
EP0857252A1
EP0857252A1 EP96934428A EP96934428A EP0857252A1 EP 0857252 A1 EP0857252 A1 EP 0857252A1 EP 96934428 A EP96934428 A EP 96934428A EP 96934428 A EP96934428 A EP 96934428A EP 0857252 A1 EP0857252 A1 EP 0857252A1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
valve
gas recirculation
armature
valve according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96934428A
Other languages
German (de)
English (en)
Other versions
EP0857252B1 (fr
Inventor
Erwin Krimmer
Bruno Hezel
Eberhard Wizgall
Tilman Miehle
Peter Jauernig
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 EP0857252A1 publication Critical patent/EP0857252A1/fr
Application granted granted Critical
Publication of EP0857252B1 publication Critical patent/EP0857252B1/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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/59—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor
    • F02M26/61—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to exhaust pressure
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/66—Lift valves, e.g. poppet valves
    • F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/66—Lift valves, e.g. poppet valves
    • F02M26/68—Closing members; Valve seats; Flow passages

Definitions

  • the invention is based on an exhaust gas recirculation valve according to the preamble of claim 1.
  • the valve seat is designed as a conical seat which points into the interior of the exhaust gas recirculation line.
  • a conical valve member comes to rest on this seat, which is brought into the closed position by the force of the spring and is lifted off the valve seat by the electromagnetic force of the electromagnet.
  • Such a valve has the disadvantage that it is acted upon by the exhaust gas pressure in the closed position in the closing direction, so that considerable forces are necessary, in particular additionally in the case of negative pressure in the tube, to bring the valve into the open position. This requires a large-sized electromagnet and high energy, which must be provided cost-effectively by appropriately expanded output stages.
  • the exhaust gas recirculation valve according to the invention with the features of the characteristic has the advantage that the exhaust gas pressures acting on the valve member can be compensated for on the valve member by providing the movable wall. Accordingly, the actuating forces which are intended to bring the valve into the open position are only slight, so that the exhaust gas recirculation valve can be switched quickly and precisely.
  • the electromagnet can be small in size and operated with low energy consumption. The effort for an electrical control stage for the winding of the electromagnet is correspondingly low.
  • the exhaust gas recirculation valve can be held in intermediate positions by analog or quasi-analog control, clocked with a variable duty cycle.
  • control chamber is connected via a channel passing through the valve stem, so that a direct connection is made without a separate line between the exhaust gas recirculation line and the control room. This is particularly small with easy assembly and low sources of error.
  • the area of the valve member acted upon by the exhaust gas pressure in the closing direction of the valve is essentially the same size as the area of the movable wall acting in the opening direction of the valve member. By dimensioning this area, the closing force when the electromagnet is not energized or the opening force of the electromagnet can be set exactly.
  • the movable wall consists of a membrane.
  • the design of the exhaust gas recirculation valve according to The preceding claims 1 to 3 have the advantage that in the event of a rupture of the membrane, the compensation of the exhaust gas pressure in the closing direction is omitted and the valve is kept securely closed by the exhaust gas pressure upstream of the valve member. A partial flow of exhaust gas then passes through the control chamber, the torn membrane and the pressure chamber into the pipe as a partial quantity of exhaust gas recirculation, which can be limited by the cross section of the channel. In particular, it is avoided that, in the event of a failure of the membrane, hot exhaust gas flows into the surroundings of the exhaust gas recirculation valve, enters the engine compartment of the associated motor vehicle and can possibly cause damage there.
  • the movable wall is designed as a piston, according to claim 5, which reliably prevents failure, as can be possible when using a membrane.
  • the mouth of the channel upstream of the valve member is provided with a shield cap, which ensures that the pressure in the control chamber is not influenced as a function of a dynamic dynamic pressure, but rather occurs as a static exhaust gas pressure.
  • the upstream wall deflects an inflow of exhaust gas towards the mouth, so that exhaust gas can only enter the channel transversely thereto at a pressure which corresponds to the static pressure in the exhaust gas recirculation line.
  • a setting result of the exhaust gas recirculation valve is thus advantageously not influenced by the flow pressure, in particular if it is to assume intermediate positions between open and closed.
  • the kind of Mouth of the nozzle in the tube according to claim 12 has the advantage that the nozzle itself is intensively washed by cooling air with air flow in the tube and the introduction of exhaust gas takes place in the region of the flow profile in the tube, which has the highest speed and thus a very fast , uniform swirling of exhaust gas with air supplied. If the mouth is moved directly adjacent to a throttle valve controlling the flow cross-section of the tube, this cooling and swirling effect can be intensified at different positions of the throttle valve.
  • FIG. 1 shows a first embodiment of the exhaust gas recirculation valve with a membrane as the movable wall
  • FIG. 2 shows a second embodiment of the exhaust gas recirculation valve with a piston as the movable wall.
  • a tube 1 is shown, which is part of an intake system of an internal combustion engine, for example.
  • a first opening 3 and diametrically opposite a second opening 4 are provided in the wall 2 of the tube 1.
  • An exhaust gas recirculation line 6 opens into the pipe 1 via the first opening 3. It is part of the
  • a connector 8 is provided, protrudes into the interior of the tube through the opening 3.
  • the nozzle 8 can be formed, for example, as a drawn part made of sheet metal and has on the outside a flange 9 which is screwed together with a flange 10 of the exhaust gas recirculation line and a corresponding flange of the pipe 1, not shown, so that the transition from
  • Exhaust gas return line and nozzle is tightly closed.
  • the connecting piece is guided through the opening 3 at a lateral distance to produce thermal insulation, in particular when the tube 1 is made of plastic.
  • a conical part 12 adjoins the cylindrical part 11 of the nozzle protruding through the opening 3 and forms a valve seat 13, the seat surface of which is directed into the interior of the nozzle or towards the exhaust gas recirculation line. Subsequent to the valve seat 13, the connecting piece merges into a tube part 14 with a reduced diameter, which has its mouth into the tube 1 just before the axis of the tube 1.
  • a valve member 15 cooperates with the valve seat 13, which has a conical sealing surface 16 and is attached to the end of a valve stem 17.
  • This valve stem is tightly guided in a bore 18 which is axially introduced into the core 19 of an electromagnet 20.
  • the core 19 is guided with a nozzle 21 in the second opening 4 and also tightly connected to the tube 1 in a manner not shown.
  • the core carries a magnetic winding 22, which is arranged inside the housing 24 receiving the electromagnet.
  • An immersion armature 25 with an essentially circular cylindrical shape cooperates with the core and, when the magnetic winding is excited, dips into an axial recess 26 in the core 19.
  • the ring wall surrounding the recess 26 27 of the core increases in cross-section with increasing immersion depth. In this way, a linear characteristic of the electromagnet is achieved.
  • a compression spring 29 acts against the magnetic force that pulls the armature into the recess 26 and is clamped between the armature 25 and the magnetic core 19 and is guided on the valve stem
  • valve stem 17 coaxially penetrates the magnetic core 19 and carries the armature 25 at its end.
  • the valve stem has an outer ring shoulder 30 which is directed away from the tube 1 and the magnetic core 25 has a bore 31. by means of which it is pushed on the part 32 of the valve stem with reduced diameter up to the shoulder 30. In this position, it is fixed on the valve stem 17 by lock nuts 33.
  • the armature can also be pressed onto the valve stem. Between the end face 34 and the lock nuts 33, a washer 35 is provided, between which and the end face 34 a membrane 36 is clamped, which is sealed on its outer circumference 37 between a flange 38 of the housing 24 and a cover 39.
  • the membrane 36 now includes a control chamber 41 towards the cover 39, into which only one channel 42 opens, which is guided coaxially through the valve stem and, on the other hand, opens in an unsealable manner inside the connector 8 upstream of the valve seat 13.
  • the membrane delimits a pressure chamber 44, which is connected to the interior of the tube 1 in a non-closable manner via a first channel 46 in the armature 25 and a second channel 47 in the core 19.
  • a throttle valve 49 is arranged in the tube 1 immediately adjacent to the nozzle 8 so that it can be brought from a fully open position, as shown, to a fully closed position of the tube.
  • the free effective diameter of the diaphragm 36 which is loaded by the pressure in the control chamber 41 on the one hand and the pressure in the pressure chamber 44 on the other hand, is essentially the same size as the diameter of the valve member 14 which is effectively acted upon in the closing direction of the valve member 15 by the pressure in the exhaust gas recirculation line on the valve member, the exhaust gas pressure in the opening direction essentially on an area of the same size as the area which is acted upon by the exhaust gas pressure in the closing direction.
  • the exhaust gas forces on the valve member cancel each other out.
  • the degree of compensation can be varied by the choice of the areas applied.
  • the closing force of the compression spring 29 then acts mainly in the closing direction of the valve member.
  • the exhaust gas recirculation valve is brought into different opening positions when the magnet winding 22 of the electromagnet 20 is excited.
  • the force required for this is measured from the required closing force of the exhaust gas recirculation valve.
  • it is also not influenced by the pressures in the exhaust gas recirculation line and in pipe 1. This is because these negative pressures act both on the surface of the valve member 15 facing the tube and on the diaphragm on the side of the pressure chamber 44. The resulting forces acting on these surfaces also cancel each other out.
  • Such a valve is very small because the relatively low actuating forces only require a small electromagnet.
  • the provision of energy for such a magnet is not very expensive, both with regard to the generation of energy and with respect to the required control output stages of an electronic control device.
  • the magnet is advantageously controlled in a clocked manner with a variable pulse duty factor, so that different intermediate positions and thus metering cross sections can be set on the exhaust gas recirculation valve between v completely open and 'completely closed'.
  • a variable pulse duty factor e.g. 1 metering cross sections
  • the mouth 50 of the channel 42 which lies centrally to the valve member 15, is protected by a shield cap 51.
  • This cap has a wall axially in front of the mouth, which serves as a baffle for the incoming exhaust gas flow. Through lateral openings 53, the exhaust gas can then enter the control chamber 41 to form pressure. This takes place from a flow-reduced zone within the cap 51 with a pressure which is equal to the static pressure of the exhaust gas in the exhaust gas recirculation line.
  • the type of introduction of the exhaust gas pressure into the control chamber 41 is particularly advantageous through the channel 42 provided here in the valve stem 17. Because of this configuration, no separate line connections between the exhaust gas recirculation line and the control chamber 41 are necessary, which in the other case require additional connection effort and sealing effort with the possibility of a would bring damage. Of course, instead of the channel that goes through the valve stem, it is also possible to provide a correspondingly different connection, for. B. in the form of a Housing of the exhaust gas recirculation valve and the pipe leading to the exhaust gas recirculation line or a separate line there.
  • the exhaust gas entering the pipe 1 when the exhaust gas recirculation valve is open is only released via the pipe part 14 approximately in the middle of the pipe 1, where the highest velocity components of a flow profile of the medium flowing through the pipe 1 occur.
  • this medium is air or an air / fuel mixture.
  • This wide hand into the tube 1 in the thin-walled design of the nozzle leads to intensive cooling of the nozzle by the cooler air flowing around it, which removes heat from the connection point of the nozzle to the tube 1, which is taken up by the exhaust gas recirculation line 6 and passed on. So that the connection point between nozzle 8 and pipe 1 is less thermally stressed.
  • the immediate vicinity of the throttle valve intensifies the air flow.
  • the introduction of the exhaust gas into the flow core of the tube 1 improves the rapid swirling and mixing of the introduced exhaust gas with the medium flowing there.
  • the valve construction described is highly damage-proof, such that in the event of a breakage Membrane 36 the force compensation by the exhaust gas pressure in the control chamber 41 is omitted, which has the consequence that the exhaust gas pressure acts on the valve member 15 in its closing direction.
  • an excessively high exhaust gas recirculation be set, which maintains the operability of an associated internal combustion engine.
  • exhaust gas recirculation occurs to a small extent via channel 42, control chamber 41, channels 46 and 47 into the pipe 1. Under no circumstances does exhaust gas escape into the environment if the membrane breaks.
  • a second embodiment of the exhaust gas recirculation valve according to the invention according to FIG. 2 essentially the same parts are provided as in the embodiment according to FIG. 1.
  • the part of the armature 125 facing away from the magnetic core is designed as a piston 136 which, in replacement of the membrane, forms a movable wall by the piston sliding tightly in a bore 61 and in turn sealingly enclosing a control chamber 141 with a housing cover 139.
  • the piston 136 separates this control chamber 141 from a pressure chamber 144, the design of which is the same as the pressure chamber 44 from the exemplary embodiment according to FIG. 1.
  • the bore 61 is provided in a housing part which consists of non-magnetizable material, preferably in the form of a Brass sleeve 65, which is firmly inserted into the housing, so that the piston is easily movable within this range, unaffected by the magnet.
  • a housing part which consists of non-magnetizable material, preferably in the form of a Brass sleeve 65, which is firmly inserted into the housing, so that the piston is easily movable within this range, unaffected by the magnet.
  • the end face 66 of the piston reaches a seal 67 which leads to the Example is used on the lid 139, such that the control chamber 141 is sealed to guide the piston when the exhaust gas recirculation valve is in its closed position.
  • the piston 136 can also be provided with an axial recess 68, into which the channel 42 opens and which is filled by a soot filter. This also avoids contamination of the guide of the piston 136 in the sleeve 65.
  • this embodiment has the essential advantage that a case of damage, such as the rupture of the membrane of FIG. 1, does not have to be expected here. The valve therefore has a much longer life expectancy.
  • a shield cap 51 is also provided on the valve member 15, which prevents dynamic exhaust gas pressure from reaching the control chamber 141.

Landscapes

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

Abstract

L'invention concerne une soupape de retour de gaz d'échappement, dont l'élément soupape (15) coopère avec un siège de soupape (13) d'une tubulure d'une conduite de retour de gaz d'échappement (6), cette tubulure (8) faisant saillie dans un tuyau (1) du système d'admission d'un moteur à combustion interne, et le siège de soupape faisant face à l'extrémité d'admission de la conduite de retour des gaz d'échappement (6). Ainsi, un élément soupape (15) de la soupape de retour de gaz d'échappement est soumis à l'action de la pression des gaz d'échappement dans le sens de fermeture, en plus d'un ressort de pression (29) à l'encontre duquel une armature (25) d'un électro-aimant (20) agit dans le sens d'ouverture. Dans le but d'égaliser les forces agissant dans le sens de fermeture, les gaz d'échappement sont guidés, par l'intermédiaire d'un conduit (42) de la tige de soupape (17), dans un espace de régulation (41) qui est scellé, par rapport à la pression dans le tuyau (1), par une paroi mobile (36) dotée d'une surface d'actionnement correspondant sensiblement à la surface d'actionnement de l'élément soupape (15). Ainsi, les forces sont égalisées de telle manière que la commande de la soupape de retour de gaz d'échappement dépend uniquement des forces électromagnétiques et de la force du ressort de pression (29).
EP96934428A 1996-03-01 1996-09-19 Soupape de retour de gaz d'echappement Expired - Lifetime EP0857252B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19607811A DE19607811A1 (de) 1996-03-01 1996-03-01 Abgasrückführventil
DE19607811 1996-03-01
PCT/DE1996/001775 WO1997032125A1 (fr) 1996-03-01 1996-09-19 Soupape de retour de gaz d'echappement

Publications (2)

Publication Number Publication Date
EP0857252A1 true EP0857252A1 (fr) 1998-08-12
EP0857252B1 EP0857252B1 (fr) 2001-03-21

Family

ID=7786869

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96934428A Expired - Lifetime EP0857252B1 (fr) 1996-03-01 1996-09-19 Soupape de retour de gaz d'echappement

Country Status (5)

Country Link
US (1) US5975064A (fr)
EP (1) EP0857252B1 (fr)
JP (1) JPH11504694A (fr)
DE (2) DE19607811A1 (fr)
WO (1) WO1997032125A1 (fr)

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US5669364A (en) * 1996-11-21 1997-09-23 Siemens Electric Limited Exhaust gas recirculation valve installation for a molded intake manifold
US6223733B1 (en) 1997-07-08 2001-05-01 Siemens Canada Limited Exhaust gas recirculation valve
US6073617A (en) * 1997-07-08 2000-06-13 Siemens Canada Ltd. Manifold-mounted emission control valve
EP0962646A4 (fr) * 1997-10-22 2000-09-20 Mitsubishi Electric Corp Dispositif a soupape de commande de recyclage des gaz d'echappement
US6293266B1 (en) * 1998-05-26 2001-09-25 A. Kayser Automotive Systems Gmbh Exhaust gas recirculation device
US6135415A (en) * 1998-07-30 2000-10-24 Siemens Canada Limited Exhaust gas recirculation assembly
US6182646B1 (en) * 1999-03-11 2001-02-06 Borgwarner Inc. Electromechanically actuated solenoid exhaust gas recirculation valve
US6422223B2 (en) 1999-03-11 2002-07-23 Borgwarner, Inc. Electromechanically actuated solenoid exhaust gas recirculation valve
DE19927186A1 (de) 1999-06-15 2000-12-28 Daimler Chrysler Ag Abgasrückführeinrichtung mit einem Tellerventil
US6217001B1 (en) * 1999-06-29 2001-04-17 Delphi Technologies, Inc. Pressure balanced gas valve
JP4667609B2 (ja) * 2000-02-29 2011-04-13 イーグル工業株式会社 ソレノイド
US6776146B1 (en) * 2003-01-27 2004-08-17 International Engine Intellectual Property Company, Llc Obstruction of flow to improve flow mix
JP4192763B2 (ja) * 2003-11-07 2008-12-10 株式会社日立製作所 電子式ｅｇｒガス制御装置
EP1701029A1 (fr) * 2003-11-28 2006-09-13 Hitachi, Ltd. Dispositif de commande rge et dispositif a papillon entraine par un moteur d'un moteur diesel
US6959700B2 (en) 2004-03-18 2005-11-01 International Engine Intellectual Property Company, Llc Flow deflector for a pipe
US7934696B1 (en) * 2006-02-21 2011-05-03 John Gruben Ether injection control valve
FR2921433B1 (fr) * 2007-09-25 2009-11-06 Mann & Hummel Gmbh Dispositif de mise en tourbillonnement et de melange de gaz d'echappement recycles dans la tubulure d'aspiration d'un moteur a combustion interne.
DE102009004803A1 (de) * 2008-01-17 2009-07-23 Eto Magnetic Gmbh Elektromagnetisch betätigbare Ventilvorrichtung
DE102010025171B4 (de) * 2010-06-25 2014-02-27 Pierburg Gmbh Fluiddruckumschaltventil
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DE102015215734A1 (de) 2015-08-18 2017-02-23 Mahle International Gmbh Ventiltrieb einer abgasführenden Einrichtung

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Also Published As

Publication number Publication date
EP0857252B1 (fr) 2001-03-21
DE59606643D1 (de) 2001-04-26
JPH11504694A (ja) 1999-04-27
DE19607811A1 (de) 1997-09-04
US5975064A (en) 1999-11-02
WO1997032125A1 (fr) 1997-09-04

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