EP1338785B1 - Steuerventil, insbesondere für eine Brennkraftmaschine, zur gesteuerten Rückführung von Abgas - Google Patents

Steuerventil, insbesondere für eine Brennkraftmaschine, zur gesteuerten Rückführung von Abgas Download PDF

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Publication number
EP1338785B1
EP1338785B1 EP20020025157 EP02025157A EP1338785B1 EP 1338785 B1 EP1338785 B1 EP 1338785B1 EP 20020025157 EP20020025157 EP 20020025157 EP 02025157 A EP02025157 A EP 02025157A EP 1338785 B1 EP1338785 B1 EP 1338785B1
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EP
European Patent Office
Prior art keywords
valve part
control valve
valve
valve according
webs
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.)
Expired - Lifetime
Application number
EP20020025157
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1338785A2 (de
EP1338785A3 (de
Inventor
Bernd Dr.-Ing. Bareis
Mathias Dipl.-Ing. Elsässer (FH)
Franz Bender
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.)
Gustav Wahler GmbH and Co KG
Original Assignee
Gustav Wahler GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gustav Wahler GmbH and Co KG filed Critical Gustav Wahler GmbH and Co KG
Publication of EP1338785A2 publication Critical patent/EP1338785A2/de
Publication of EP1338785A3 publication Critical patent/EP1338785A3/de
Application granted granted Critical
Publication of EP1338785B1 publication Critical patent/EP1338785B1/de
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
    • 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
    • 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
    • F02M26/11—Manufacture or assembly of EGR systems; Materials or coatings specially adapted for EGR systems
    • 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
    • F02M26/45—Sensors specially adapted for EGR systems
    • F02M26/48—EGR valve position sensors
    • 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
    • F02M26/50—Arrangements or methods for preventing or reducing deposits, corrosion or wear caused by impurities
    • 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
    • F02M26/54—Rotary actuators, e.g. step motors
    • 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
    • F02M26/72—Housings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/4238—With cleaner, lubrication added to fluid or liquid sealing at valve interface
    • Y10T137/4245—Cleaning or steam sterilizing
    • Y10T137/4273—Mechanical cleaning
    • Y10T137/428—Valve grinding motion of valve on seat

Definitions

  • the invention relates to a control valve, in particular for an internal combustion engine, for controlled recirculation of exhaust gas to the fresh gas of the internal combustion engine, with two valve parts, which lie on one side, wherein the valve parts each have passages and relative to each other between the passage of exhaust releasing opening position and a closing position blocking this passage are rotatable, along which the passages of a valve member, for. B. the first valve member, delimiting boundary edges to an axial side of the valve member projecting, the passages framing webs extending with their free narrow surfaces bearing surfaces for the other valve member, z.
  • the radially outwardly open recesses permit valve venting in the closed position of the valve caused by the rotational adjustment of this disc, so that in the case of gas as the controlled fluid, maintenance and repair work can be carried out safely when removing the fluid line from the supply side of the valve.
  • the webs are directed radially and extend approximately at 90 ° to each other.
  • the protruding ridges are not intended as scraping tools.
  • an exhaust valve is known with a rotatably actuable valve disc which includes an approximately semicircular opening and is rotatably disposed above a second valve disc fixedly disposed in the housing.
  • the second valve disc also has an approximately semicircular opening.
  • the rotatable valve disc is rotated by means of a drive means in such a way that its approximately semicircular opening more or less covers the corresponding opening of the non-rotatable valve disc, whereby the flow rate of the gas flowing therethrough is controlled.
  • the opening of the fixed disc is covered by a disc part of the rotatable disc.
  • the first valve part as Flat slide can be formed, which cooperates with a flat seat of an outlet opening of the exhaust pipe, wherein the flat seat of the outlet opening and the flat slide are arranged in an extension of the exhaust passage of the valve housing.
  • the flat slide is moved via a rod by an adjusting device, such as a solenoid actuator, against a spring in the opening direction, wherein the spring brings the flat slide in the closed position with unconfirmed actuator, so that then no exhaust gas recirculation takes place.
  • the flat seat and the flat slide are made of materials with low frictional properties, so that a small force is required.
  • the flat slide contains only one slide opening, which is brought in the open position in coincidence with the outlet opening, wherein the slide opening determines the flow cross-section of the outlet opening.
  • the exhaust gas recirculation to the individual cylinders of the internal combustion engine can also be effected via individual exhaust gas lines, in which case the flat slide has a slide opening for each individual exhaust gas line with an outlet opening therein.
  • the respective flat slide is moved in the direction of its surface extension and transversely to the inflowing exhaust gas by means of the rod via the adjusting device between the open position and the closed position.
  • the flat slide lies flat on the end of the transverse thereto exhaust pipe, said end containing the outlet opening.
  • the translational reciprocating flat slide can also be designed as a flat rotary valve, but no information about the arrangement and rotatable operation of such a flat slide are given.
  • This known control valve has the particular disadvantage that accumulate in operation both at the flat seat with the outlet opening and the flat slide with the slide opening and adjacent surfaces soot and the like particles that caking and thus adhere and a Trouble-free operation of the control valve impair and make it completely impossible after some time. It follows that even after a relatively short period of use of the control valve, the adjustment of the flat slide is difficult. Because of this, it requires an adjusting device that allows relatively large actuating forces. Such a setting device has a relatively large footprint, is heavy and expensive.
  • the invention has for its object to design a control valve of the type mentioned as such rotary valve, which requires a small rotational actuating force for adjusting the rotatable valve member, whereby the actuator can be made small, compact, lightweight and inexpensive, and not only a small Ensures friction between the relatively rotatable valve parts and ease of rotation adjustment but also a permanent accumulation of soot or the like particles, which could affect the operation, counteracts.
  • control valve according to the invention is small, compact, lightweight and inexpensive. Small design and few individual components used result in a low weight and low production costs. Furthermore, the control valve is reliable with a concomitant long life. A further advantage is that the control valve is not only insensitive to contamination, but allows a high positioning accuracy, has only small valve leaks and that the valve actuation necessary actuating force or the necessary adjusting torque is constant over the life of the control valve.
  • a control valve 10 in particular for an internal combustion engine, according to a first embodiment is shown, which is in the open position.
  • the control valve 10 is used for the controlled return of exhaust gas, which in the in Fig. 1 Lower area A, namely the local front side of the control valve 10, for example approximately parallel to the axis as shown by arrow 11, coming from an exhaust gas recirculation line, not shown, the control valve 10 passes and this leaves transversely to the longitudinal center axis 12 on a peripheral side according to arrow 13 and a not shown further line is added to the fresh gas of the internal combustion engine.
  • exhaust gas recirculation valves are common in internal combustion engines.
  • the control valve 10 has a first valve part 14 and a second valve part 44, which at the in Fig. 1 lower end of the housing 9 are arranged and one another with one side.
  • Both valve parts 14, 44 each have passages 15 and 45, respectively. They are relative to each other about the longitudinal center axis 12 between a passage of supplied in the direction of arrow 11 exhaust gas releasing, in Fig. 1 shown opening position and a passage blocking this, not shown, closed position rotatable.
  • Both valve parts 14, 44 are substantially plate-shaped, wherein the first valve member 14 is fixed and the second valve member 44 is arranged rotatable relative thereto. In another embodiment, not shown, the conditions may also be reversed. Due to the rotational adjustability of the second valve member 44, this represents a rotary valve.
  • the surface area extending between two circumferentially successive passages 15 is closed.
  • the first valve member 14 has a substantially planar smooth back 16, which in particular in Fig. 4 is visible.
  • the opposite, in Fig. 1 downward and to the second valve member 44 facing front 17 of the first valve member 14 is recessed in the area of the surfaces which extend between two circumferentially successive passages 15.
  • the passages 15 framing webs 21 and 22 and 23, which project beyond the lower surfaces of the front side 17.
  • the first valve part 14 is formed as a circular disk. It has an annular web 24 extending along the circular edge and a through-bore 25 in the center, which is surrounded by an annular hub 26.
  • the annular web 24 and the annular hub 26 are in the same direction and as far as the webs 21, 22 and 23 and form with their respective narrow surface also a bearing surface for the second valve member 44 which rests with its back 46 and slides on it.
  • the passages 15 of the first valve member 14 and the passages 45 of the second valve member 44 are approximately triangular segment-shaped and formed such that two triangular sides, which correspond approximately to the boundary edges 18 and 19 at the passages 15, starting from the center are directed substantially radially and the other Triangle side, which is predetermined approximately by the arcuate boundary edge 20, is formed by the corresponding arc portion of the circular edge.
  • the passages 15 of the first valve member 14 extend in the radial direction so far that the respective local web 23 coincides with the annular web 24 in this area.
  • the circumferential annular web 24 thus forms in the region of the passages 15 whose arcuate webs 23rd
  • the first valve part 14 has a total of three passages 15, which follow one another at the same circumferential angle spacings, so that the rectilinear boundary edges 18 follow one another at circumferential angular intervals of 120 °.
  • the other, approximately radial triangle side, which is predetermined by the boundary edge 19, is not straight but arcuate and is - if you look at 3 and 4 - Prevails in the direction of the rectilinear boundary edge 18 out.
  • the webs 21 and 22 with respect to both web edges be designed sharp-edged.
  • the outer edge of the annular hub 26 and the inner edge of the arcuate web 23 may be formed sharp-edged. This sharp-edged design, together with the smooth back 46 of the second valve member 44, e.g.
  • the passages 45 of the second valve member 44 correspond in terms of their shape, size and spatial arrangement of those of the first valve member 14, so that reference can be made to the relevant description.
  • the straight and in the direction of a diametrical extending boundary edge 18 corresponds to the second valve member 44, the boundary edge 48.
  • the other bulging boundary edge 19 of the first valve member 14 corresponds to the second valve member 44 to the rectilinear boundary edge 48 within the valve part plane bulging boundary edge 49.
  • the boundary edge 20, causes the radial limitation of the passages 15 in the first valve member 14, omitted in the second valve member; because this is designed as a wing disc, the successive at three in the circumferential direction at equal angular intervals Passages 45 is three leaves.
  • the passages 45 are radially outwardly open and thereby formed as about V-shaped spaces between two circumferentially successive wings 57, 58 and 59.
  • the second valve part 44 lying with its smooth back 46 on the narrow surfaces of the webs 21 to 24 and the annular hub 26 is relative to the first valve member 14 of a closed position, not shown, in which each wing 57, 58 and 59, a passage 15 of the first valve member 14th completely covered and tightly closes, in the direction of arrow 8 in an open position and in opposite directions back to the closed position rotatably adjustable.
  • the narrow surfaces of the arcuate webs 23 and 22 run over by the rectilinear boundary edge 48 and scraper-like cleaned in a similar manner.
  • the second valve member at the radially outer transition region of the arcuate boundary edge 49 in the subsequent arc-shaped edge each have a protruding in the direction of rotation nose 60, 61 and 62, which slides in the movement in the opening direction on the narrow surface of the annular web 24 and a particularly good Has cleaning effect similar to a scraping tool.
  • the boundary edges 48 and 49 may be formed sharp-edged on the back 46.
  • the first valve part 14 is at the in Fig. 1 below located end face of the housing 9 in a ring seat 63 used this, for example, pressed.
  • the fastening of the valve member 14 is preferably such that it is detachable and interchangeable with another with a different geometry of the passages 15, so that the flow rate characteristic and eg the maximum flow rate of the control valve 10 can be easily changed thereby.
  • the housing 9 has at in Fig. 1 lower end at least one protruding so far projection or edge 64, that this also beyond the voltage applied to its rear side 46 on the first valve member 14 second valve member 44 and such that both valve members 14 and 44 are protected by this projecting edge or protruding projections ,
  • the first valve member 14 is on the side facing away from the second valve member 44, secured against rotation by means of positive connection means 65, 66 with respect to the housing 9.
  • positive connection means 65, 66 at least one approximately axially parallel projection 65 and receptacles 66 of the housing 9 and the first valve member 14 are provided, which engage with each other when inserting the first valve member 14 in the ring seat 63.
  • the housing side, a projection 65 and on the back 16 of the first Valve part 14 three receptacles 66 provided in the form of blind holes, one of which cooperates with the projection 65.
  • actuating shaft 67 For adjusting the rotation of the second valve member 44 is an actuating shaft 67, which is driven by a drive means 68, such as a rotary magnet. Part of the drive device 68 is also an only schematically indicated electronic device 69 with position detection.
  • the drive device 68 is on the in Fig. 1 attached to the upper portion of the housing 9, wherein the actuating shaft 67 may consist in a non-illustrated embodiment of two interconnected by a coupling coaxial parts or in a particularly advantageous manner according to the first embodiment in Fig. 1 can be designed as a component which, starting from the drive means 68 clutch-free up to the in Fig. 1 lower end of the control valve 10 and the local second valve member 44 and may extend beyond this.
  • the second valve member 44 is approximately floating, preferably releasably and interchangeably held with respect to the housing 9 and the actuating shaft 67.
  • the adjusting shaft 67 passes through the through hole 25 in the first valve part 14 and also has a central through-bore 70 in the second valve part 44, which also serves to center the latter in relation to the control shaft 67. Outside the second valve member 44, this is connected to the end of the control shaft 67.
  • the first valve member 14 and / or the second valve member 44 is formed of ceramic, wherein in the embodiment shown both valve parts are made of ceramic in an advantageous manner. It has been recognized that ceramic material is inert, low in reaction, and does not attract soot or other particles as much as metallic material. Although soot and similar particles could adhere to the ceramic material, they are more easily removed or peeled off. Characterized in that both valve parts 14, 44 are made of ceramic, thus a possible unwanted adhesion and caking of soot or the like particles is prevented.
  • the two valve members 44 and 14 have in the design in ceramic with advantage different roughness, to a possible sticking this prevent overlapping surfaces.
  • the narrow surfaces of the first valve member 14 may have a lower roughness than the surface 46 of the second valve member 44 lying thereon.
  • the narrow surfaces of the webs 21 to 24 and the annular hub 26 are, for example ground and polished and thus smoother than the back 46 of the other valve member 44, whereby sticking is counteracted and thereby necessary for the adjusting movement of the second valve member 44, to be applied by the drive means 68 Stell product be further reduced.
  • the drive device 68 can be made even smaller and lighter and, under certain circumstances, less expensive.
  • the second valve member 44 made of ceramic this can not be welded to the actuator shaft 67 due to this material or connected by soldering.
  • a floating arrangement which nevertheless allows at least substantially play-free rotational drive between the control shaft 67 and the second valve member 44 and a large tolerance width, is achieved in that at the end of the control shaft 67.
  • the attachment can be solvable or permanent, eg by welding or soldering.
  • the connecting member 71 engages over the outer side of the second valve part 44 facing away from the first valve part 14 and is in rotational driving connection with the latter.
  • the second valve member 44 by means of axial spring force, which is directed toward the first valve member 14 toward the front 17, namely the narrow surfaces of the webs 21 to 24 and the annular hub 26, pressed.
  • This can be achieved by a spring acting axially on the control shaft 67 or a shaft part.
  • the connecting member 71 itself as a spring member, for example as a leaf spring, formed by means of which even the axial spring force the second valve member 44 is exerted.
  • This has the advantage that one of the drive means 68 up to the in Fig. 1 reaching the lower end of the control valve 10 adjusting shaft 67 can be used, which makes it possible to dispense with a split control shaft with coupling between the two parts and a special axial pressure spring.
  • the connecting element 71 in the form of a spring member has a plurality of, for example, three, radially abstrebende, approximately leaf spring-like arms 72 and a virtually non-resilient center 73. In this there is a through hole 74 through which the end of the control shaft 67 extends through, which is rotatably connected in this area with the connecting member 71.
  • the arms 72 are relatively narrow in relation to the center 73 and can therefore well with thin walls of the connecting member 71, so that the connecting member 71 can engage with a certain axial bias on the second valve member 44 in the fully assembled position.
  • the second valve member 44 receptacles 75, which are formed, for example, as radially directed, blind hole-like slots.
  • These receptacles 75 are assigned to the connecting member 71, approximately as wide driver 76 associated with which are arranged at the ends of the arms 72 and project from this approximately at right angles and engage approximately parallel to the axis and thereby positively into the receptacles 75.
  • These drivers 76 are formed, for example, from tabs which are provided approximately at the center with a slot 77 and thereby, if necessary, springs and can have a balancing effect.
  • Fig. 1 results, the housing 9 in the interior of one or more approximately axially parallel housing chambers 78 which are in communication with a transverse to the longitudinal center axis 12 outlet 79 in the housing 80.
  • the control valve 10 When the control valve 10 is open, the exhaust gas to be controlled, coming from an exhaust gas recirculation line, passes in the direction of the arrow 11 through the passages 15, 45 into the housing chambers 78, from which the exhaust gas exits via the outlet 79 transversely to the longitudinal central axis 12 in the direction of the arrow 13.
  • Above thereof contains the housing 9 an inner, for example, annular, cooling channel 81, for example, the axis is fed parallel to the axis at one point coolant, which is discharged radially elsewhere, for example.
  • a control shaft 67 surrounding the spring 82 for example in the form of a leg spring, arranged, which engages with one end on the housing 9 and with its other end to the control shaft 67.
  • the spring 82 serves as a safety spring which, in the event of any failure of the drive means 68, moves the second valve member 44 to the closed position or, should it be desired, to the open position.
  • the peculiarity of the second embodiment according to Fig. 11 is that the first valve member 14 and the second valve member 44 for supplying the exhaust gas, two separate supply channels 83, 84 are connected upstream, each associated with a cylinder bank of the internal combustion engine not shown. Both feed channels 83, 84 are separated from each other until they hit the second valve part 44, so that there is no mixing of the exhaust gas supplied per supply channel 83, 84 in the direction of the arrow and no influencing of the cylinder banks due to different pressure conditions of the exhaust gas.
  • the supply channels 83, 84 are separated by a web 85, which extends to the lower end of the control shaft 67, where a small gap is left to maintain the rotational adjustability.
  • the conditions can be kinematically reversed and selected such that not the first valve member 14 but instead the second valve member 44 along the boundaries 45 delimiting boundary edges 48, 49, in particular along the wing edges seaming edges, to an axial side of the valve member 44 projecting webs, which form bearing surfaces for the first valve member 14 with their free narrow surfaces.
  • the first valve member 14 is formed on the side facing the second valve member 44 side 17 planar, wherein the second valve member 44 substantially rests with the narrow surfaces of the webs on this flat surface 17.
  • the second valve member 44 slides with these narrow surfaces on the flat surface 17 of the first valve member 14.
  • the annular web 24 and / or the annular hub 26 and / or the webs 21, 22, 23 have a height of at least five tenths mm.
  • a distance between zero and one tenth mm may be kept constant. This happens z. B. by means of a valve between two parts 14, 44 arranged spacer element, for. B. a spacer, or by a correspondingly sized height of the ring hub 26.
  • kinematic permutation then applies analogous then for the design of the wing edges fringing, protruding ridges of the second valve member 44 and an existing in the region of the through hole 70 annular hub.
  • the second valve member 44 made of metal, for. B. steel.
  • the second valve member 44 may be connected directly to the control shaft 67, z. B. by positive engagement, which then acts on the control shaft 67, an axial force which causes the pressing of the second valve member 44 to the first valve member 14.
  • the first valve member 14 made of metal, for. B. steel be formed. Is that one or the other valve member 14 or 44 made of metal, for.
  • the annular hub 26 of the first valve member 14 it may be formed in an advantageous manner then the annular hub 26 of the first valve member 14 as a ring seal for sealing with respect to the guided-through control shaft 67.
  • this annular hub can in this case be designed as a ring seal for the corresponding sealing.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
EP20020025157 2002-02-23 2002-11-11 Steuerventil, insbesondere für eine Brennkraftmaschine, zur gesteuerten Rückführung von Abgas Expired - Lifetime EP1338785B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002107922 DE10207922A1 (de) 2002-02-23 2002-02-23 Steuerventil, insbesondere für eine Brennkraftmaschine, zur gesteuerten Rückführung von Abgas
DE10207922 2002-02-23

Publications (3)

Publication Number Publication Date
EP1338785A2 EP1338785A2 (de) 2003-08-27
EP1338785A3 EP1338785A3 (de) 2006-05-24
EP1338785B1 true EP1338785B1 (de) 2011-01-05

Family

ID=27635287

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020025157 Expired - Lifetime EP1338785B1 (de) 2002-02-23 2002-11-11 Steuerventil, insbesondere für eine Brennkraftmaschine, zur gesteuerten Rückführung von Abgas

Country Status (5)

Country Link
US (1) US6726174B2 (pt)
EP (1) EP1338785B1 (pt)
BR (1) BR0300220B1 (pt)
DE (2) DE10207922A1 (pt)
MX (1) MXPA02012952A (pt)

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MXPA02012952A (es) 2004-09-03
BR0300220A (pt) 2004-08-03
DE50214848D1 (de) 2011-02-17
DE10207922A1 (de) 2003-09-04
US6726174B2 (en) 2004-04-27
US20030160199A1 (en) 2003-08-28
EP1338785A2 (de) 2003-08-27
EP1338785A3 (de) 2006-05-24
BR0300220B1 (pt) 2012-04-03

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