EP2187032A2 - Dispositif de soupape destiné à la commande d'un flux de gaz d'échappement transporté ou recyclé à partir d'un moteur à combustion interne - Google Patents

Dispositif de soupape destiné à la commande d'un flux de gaz d'échappement transporté ou recyclé à partir d'un moteur à combustion interne Download PDF

Info

Publication number
EP2187032A2
EP2187032A2 EP09008700A EP09008700A EP2187032A2 EP 2187032 A2 EP2187032 A2 EP 2187032A2 EP 09008700 A EP09008700 A EP 09008700A EP 09008700 A EP09008700 A EP 09008700A EP 2187032 A2 EP2187032 A2 EP 2187032A2
Authority
EP
European Patent Office
Prior art keywords
valve
shaft
housing
flap
valve device
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.)
Withdrawn
Application number
EP09008700A
Other languages
German (de)
English (en)
Other versions
EP2187032A3 (fr
Inventor
Bernd Bareis
Martin Hofmann
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 EP2187032A2 publication Critical patent/EP2187032A2/fr
Publication of EP2187032A3 publication Critical patent/EP2187032A3/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F02M26/71—Multi-way valves
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • F02M26/26—Layout, e.g. schematics with coolers having bypasses characterised by details of the bypass valve
    • 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
    • F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves

Definitions

  • the invention relates to a valve device for controlling a recirculated from an internal combustion engine and supplied exhaust stream, having the features in the preamble of claim 1.
  • EP 1 707 790 A1 It is a valve device of this type known ( EP 1 707 790 A1 ), wherein the housing has an inlet connectable to the outlet of an exhaust gas cooler and a second inlet for the exhaust gas, through which exhaust gas can be introduced into the housing via a bypass bypassing the radiator.
  • the housing further has an outlet for the exhaust gas.
  • a changeover valve with a changeover flap is arranged, to which a separate drive is assigned. By pivoting the flap of the change-over valve, either the inlet connectable to the radiator or the inlet connectable to the bypass line can be shut off with respect to the housing-side outlet.
  • a return valve In the region of the housing-side outlet, a return valve is further arranged, the actuating shaft is arranged coaxially with the shaft of the flap of the switching valve.
  • the return valve has its own drive, through which the Return valve and via this the exhaust gas leaving the outlet of the housing is controllable.
  • Such a valve device is very expensive in terms of the drive device for the return valve and the switching valve. It therefore has a lot of space.
  • the invention is based on the object to provide a valve device of the type mentioned, which is simple, reliable and inexpensive, consists of only a few components and has only a small footprint.
  • the valve device according to the invention is simple, reliable, consists of only a small number of components and is compact, which therefore requires only a small space. It also requires a relatively low cost.
  • the drive for switching the switching valve is derived by the operation of the return valve between an open position and a closed position causing drive means such that before or when the closed position of the return valve, the switching valve is actuated and to switch from one to the other Position is driven, the number of necessary components is significantly reduced. It is only a drive device with appropriate gear means necessary. As a result, the control of the drive device is simplified.
  • the invention also provides the conditions for realizing a large gear ratio in the opening area by appropriate design of the drive device with compact gearbox construction, but decreases more with further opening of the valve and allows a short positioning time between the closed position and the fully open valve position , Also, the realization is a big one Transmission efficiency through reduced friction possible.
  • the return valve may be designed as a flap valve with a valve designed as a rotary flap, pivoting flap, hinged lid.
  • Valve member also with a valve designed as a rotary valve member which is inclined and substantially upright with respect to their operating shaft at an acute angle and within a tubular valve seat surface is rotatable about the axis of the actuating shaft.
  • Such a so-called butterfly valve is particularly space-saving, simple and reliable.
  • the return valve may also include a hinged lid disposed adjacent to and connected to the actuating shaft via a transverse arm and along an arcuate path about the axis of the actuating shaft between the closed position in which a valve opening is covered, and Open position in which the hinged lid is moved away from the valve opening is movable.
  • such a drive device may be of particular advantage, comprising a cam gear with at least one cam element with at least one cam curve, with which a roller is engaged, which is rotatably supported on a lever, which rotatably connected to the actuating shaft of the return valve.
  • the cam element can advantageously be designed with regard to the cam curve so that a large force is exerted on the lever at the beginning of the movement and only a small force at the end.
  • a first embodiment of a valve device 10 for controlling an exhaust gas flow shown, which is to be branched off and returned by an internal combustion engine, not shown.
  • the valve device has a housing 15, which is closed at the top by means of a cover 16 and contains a housing channel 40 with an inlet 14 and an outlet 13 for the exhaust gas.
  • the valve device 10 has a return valve 17 which can be actuated by means of a drive device 18 for controlling the amount of exhaust gas through the housing channel 40.
  • the drive device 18 has a reversible in its drive direction rotary drive 19, in particular an electric drive motor, for. As a DC motor, servo motor, stepper motor, rotary magnet od.
  • the housing 15 may be provided with an inner housing cooling, which is realized by inner channels 21, 22 and connecting lines and through which, for example, the cooling water of the cooling circuit of the internal combustion engine is passed.
  • Part of the valve device 10 is also a switching valve 23 in the housing channel 40, which is driven to switch between a first and a second position, in particular for a bypass flow or radiator flow in the housing channel 40.
  • the switching valve 23 has a means of a rotatable shaft 24 pivotable valve member 25, the z. B. consists of a flap 26 which is pivotable by means of the shaft 24 within the housing channel 40 between two positions.
  • the drive for switching the changeover valve 23 is derived by the actuation of the return valve 17 between an open position and a closed position causing drive means 18 such that before or upon reaching the closed position of the return valve 17, the changeover valve 23 is actuated and to switch from one to the other position is driven.
  • a radially projecting fork lever 27 is rotatably connected to the shaft 24 in particular at its upper end, which has an approximately U-shaped fork opening 28 into which the rotary drive of the shaft 24, a pin 29 of the drive means 18 can engage positively on a circular path is moved by means of the drive means 18, such as. B. off Fig. 4a to Fig. 4f and from Fig. 10 is apparent.
  • the fork lever 27 is in Fig. 3 shown in simplified form.
  • the pin 29 extends approximately parallel to the shaft 24 and at a transverse distance from this. It is driven by the drive device 18 on a circular arc path and over a circumferential angle z. B.
  • the return valve 17 has an actuating shaft 31 and a valve member 32 actuated by means of the actuating shaft 31.
  • the actuating shaft 31 and the shaft 24 of the switching valve 23 extend transversely from each other and parallel to each other.
  • this Switching valve 23 in front of the outlet 13 and the return valve 17, are arranged behind the inlet 14. In this case, the return valve 17, seen in the flow direction of the exhaust gas through the housing channel 40, the switching valve 23 upstream.
  • the shaft 24 of the switching valve 23 is rotatably mounted in the housing 15 with both sides of the flap 26 to this adjacent shaft portions 33, 34 by means of bearings 35 and 36, for example, sliding bearings.
  • the shaft 24 is sealed with respect to the housing channel 40 carrying the exhaust gas.
  • Upper bearing 35 a seal 37 is arranged.
  • Fig. 1 . 2 and Fig. 4a to 4f contains the housing channel 40 on the portion extending between the flap 26 and the outlet 13 for the exhaust gas, a partition wall 41, by means of a subdivision into a first channel part 42, for example for the first stream, in particular bypass stream, and in a second channel part 43, for example for the second stream, in particular cooler stream, takes place. It can be seen that further the section of the housing channel 40, which adjoins the flap 26, widens approximately funnel-shaped towards the outlet 13. The shaft 24 of the flap 26 extends approximately at right angles to the portion of the housing channel 40 containing this flap 26 ( Fig. 2 ).
  • This section has inside stop lines 44 and 45, at which the flap 26 abuts in a switched position and in a contrast pivoted other switching position. In each switching position of the flap 26 is for this a stable end position.
  • the approximately funnel-shaped extension of the housing channel 40 terminates in an approximately rectangular opening 46 which divided by the partition 41 into two juxtaposed, preferably different sized, opening halves 47, 48, of which an opening half 47, preferably the smaller, for the first Stream, in particular bypass stream, and the other, preferably the larger Opening half 48, for the second stream, in particular cooler stream, is provided which emerges from the opening 46.
  • an opening half 47 preferably the smaller, for the first Stream, in particular bypass stream
  • the other preferably the larger Opening half 48, for the second stream, in particular cooler stream
  • the housing channel 40 has a tubular portion 49 with an inlet 14 forming the opening, in which the return valve 17 is included.
  • This portion 49 of the housing channel 40 extends at least approximately in alignment with the approximately funnel-shaped extended portion or inclined at an obtuse angle.
  • the valve member 32 of the return valve 17 and the flap 26 of the switching valve 23 are juxtaposed and spaced from each other.
  • the actuating shaft 31 of the return valve 17 extends through the housing 15 and passes through the tubular portion 49 completely, wherein both shaft ends 50, 51 are rotatably supported in the housing 15 by respective bearings 52 and 53, in particular plain bearing sleeves, preferably substantially.
  • actuating shaft 31 protrudes freely into the tubular portion 49 and extending in this section 49 extending shaft end free and unsupported.
  • the actuating shaft 31 is provided in the region of one shaft end 51 with a radially projecting annular part 54, eg shaft collar or ring, on which the adjacent bearing 53, in particular the local plain bearing sleeve, with its ring part 54 facing the end is axially supported.
  • the ring member 54 and / or at least that shaft end 51 which is mounted by means of the bearing 53, in particular the plain bearing sleeve, are hardened on the surface, eg hard chrome plated, kolsterinstrument od.
  • the bearing 53 in particular the plain bearing sleeve
  • the actuating shaft 31 of the return valve 17 and / or the shaft 24th the switching valve 23 are made of stainless steel.
  • the actuating shaft 31 is sealed with respect to the exhaust duct housing channel 40 by means of a lower seal 55 and an upper seal 56.
  • the actuation shaft 31 has a soot entry on the shaft portion extending axially between the annular member 54 and the valve member 32 preventing sleeve 57 on.
  • a corresponding sleeve 58 is further provided on the axial portion of the actuating shaft 31, which extends between the Valve member 32 and the in Fig. 2 lower bearing 52 extends. Through these sleeves 57, 58 is reliably counteracted the penetration of soot or the like impurities.
  • the ring member 54 serves for the axial securing of the actuating shaft 31.
  • the rotary drive 19 is connected to the transmission 20 in drive connection, which is designed as a spur gear.
  • the transmission 20 has a drive wheel 59, which operates directly on the actuating shaft 31 of the return valve 17 in the first embodiment.
  • the drive wheel 59 is on in Fig. 2 arranged upper end of the actuating shaft 31 and rotatably connected thereto.
  • Part of the transmission 20 is also a driven gear 60, z.
  • As pinion the rotary drive 19 and an adjacent intermediate gear 61, preferably with stepped wheel.
  • the intermediate gear 61 meshes with the driven gear 60, wherein the in Fig. 1 non-visible stage wheel of the intermediate gear 61 is in drive connection with the drive wheel 59. All wheels are circumferentially toothed.
  • the output gear 60 may be directly in drive connection with the drive wheel 59.
  • the actuating shaft 31 of the return valve 17 is associated with a rotary encoder 62, which has a donor element 63 z. B. in the form of a magnet on the actuating shaft 31 and a sensor element 63 associated with the sensor 64 which is connected to the housing 15, in particular the cover 16.
  • the rotary drive 19, z. B. the actuating shaft 31 or the drive wheel 59 of the return valve 17, is a respective spring element 65 and 66 in the form of z. B. associated with a torsion spring.
  • the spring element 65 is provided for the cooler operation and the other spring element 66 for the bypass operation.
  • an approximately cup-shaped spring holder 67 is provided, which is inserted into the housing 15 in this everted orientation. How out Fig. 5 it can be seen, the spring elements 65, 66 are arranged concentrically and coaxially with each other and in associated Annular spaces, which are formed by the spring holder 67 and the housing 15, added.
  • the spring elements 65, 66 are fixed at one end to the housing 15 and with its other end 68 and 69 in Fig. 6 directed upward, wherein the spring elements 65, 66 engage with these ends 68, 69 in a respective associated arcuate slot 70 and 71 of the drive wheel 59 and are supported there at the end of the slot.
  • the spring elements 65, 66 are fixed with a spring end on the housing 15 and on the other hand, connected to the other end 68, 69, with the actuating shaft 31 and the drive wheel 59 of the return valve 17, such that the respective spring element 65, 66 in the rotary drive in the one or the other direction of rotation, which corresponds to the respective opening operation of the return valve 17, is set under spring tension and 19 drops the actuator shaft 31 with its valve member 32 under spring relaxation in the closed position with waste of the rotary drive. If the return valve 17 via the drive wheel 59 z. B. in the direction of arrow 72 and thus clockwise from the closed position according to Fig. 4e in the open position according to Fig.
  • the spring element 65 is placed under spring tension over the end 68, while the other spring element 66 remains without function. If in this position the rotary drive 19 fails, it is necessary that the valve member 32 by means of the relaxing spring element 65 from the open position according to Fig. 4f in the opposite direction to the arrow 72 in the closed position according to Fig. 4e is pivoted. This is done in this case by the fact that the tensioned spring element 65 relaxes, being over the end 68, which abuts the slot end of the curved slot 70, the drive wheel 59 and with this the actuating shaft 31 are rotated in opposite directions to the arrow 72.
  • Fig. 2 shows, cooperating with the fork lever 27 pin 29 is fixedly connected to the drive wheel 59, wherein the pin 29 is located on an axial side of the drive wheel 59 of the return valve 17 and the fork lever 27 of the shaft 24 of the switching valve 23 is disposed at the level of the pin 29 ,
  • the pin 29 has according to Fig. 4 down, while the spring element 30 is disposed above the drive wheel 59.
  • the return valve 17 and the switching valve 23 are coupled via the fork lever 27 and the pin 29 for switching the flap 26 in one or the other switching position with each other, wherein the switching valve 23 is actuated by the return valve 17 by the rotational actuation in one direction and in the other direction ,
  • FIG. 4a a position is shown which corresponds to the bypass operation.
  • the flap 26 is in Fig. 4a pivoted so far with the shaft 24 in the clockwise direction that the flap strikes in the one end position on the housing-side stop line 44.
  • the valve member 32 of the return valve 17 is located in a more or less completely open position. Exhaust gas introduced via the inlet 14 thus passes through the opened recirculation valve 17 in the form of a relatively large volume flow and flows out of the opening half 47 out of the first passage part 42 provided for the bypass operation. Should be based on the Valve device 10 are switched to the cooler operation, so by means of the rotary drive 19, the drive wheel 59, starting from Fig.
  • the switching valve 23 is switched to cooler operation, the return valve 17, however, still in the closed position. If now a regulation of the volume flow of the flowing exhaust gas in this cooler operating position is desired, the drive wheel 59 is clockwise from Fig. 4e in the position according to Fig. 4f and thus turned into the full open position until z. B. the pin 29 abuts a housing-side end stop.
  • the mass flow can be controlled by rotational actuation of the return valve 17 between the closed position Fig. 4e and the open position according to Fig. 4f be controlled, both clockwise and in opposite directions. Based on this, the changeover valve 23 back into the bypass operation according to Fig.
  • the drive wheel 59 is rotated in opposite directions to the arrow 72 via the rotary drive 19.
  • the pin 29 engages with the fork lever 27, so that a continued rotation of the drive wheel 59 in a counterclockwise direction to a pivoting operation of the shaft 24 and flap 26 via Fig. 4c up to Fig. 4b and there leads to the other end position of the flap 26.
  • the first channel part 42 is connected to the inlet 14, while the second channel part 43 is blocked by the flap 26 with respect to the inlet 14.
  • the volume flow of the exhaust gas passed through the first channel part 42 can be controlled in this bypass operating position by corresponding rotary actuation of the exhaust gas Return valve 17 are controlled by the drive wheel 59.
  • Fig. 1 and 2 results in the course of inner channels 21, 22 which form a cooling channel in the housing interior, which is connectable with its openings to an outer coolant supply, not shown.
  • This cooling channel through the channels 21, 22 is preferably provided in the region of the housing 15, which contains the bearings 52, 53, in particular sliding bearing, the actuating shaft 31 of the return valve 17.
  • the cooling channel can be approximately arcuate, z. B. about 180 ° circumferential angle to which these bearing 52 and / or 53 containing area of the housing 15 extend around.
  • good cooling is achieved along the area of the actuating shaft 31, which prevents the Kolstermaschine of the areas of the actuating shaft 31 is nullified by high heat exposure.
  • the formation of chromium-nickel carbides is prevented when formed from stainless steel actuating shaft 31.
  • the return valve 17 may be designed in various ways, for.
  • the return valve 17 as a flapper valve with respect to the actuating shaft 31 at an acute angle obliquely and substantially upright rotary valve as a valve member 32 is formed, which is rotatable within an approximately tubular valve seat surface 74 in the tubular portion 49 of the housing channel 40 by means of the actuating shaft 31 about its axis.
  • the actuating shaft 31 is arranged thereon with a rotatably mounted valve member 32 centrally with respect to the non-rotatably associated drive wheel 59.
  • the axis of rotation of the drive wheel 59 extends approximately parallel to the shaft 24 of the changeover valve 23.
  • the drive device 18 is particularly simple. Only a few components are needed.
  • the two spring elements 65, 66 and their arrangement a fail-safe function in both positions of the changeover valve 23, so both in bypass operation and in cooler operation, realized in a simple manner.
  • Fig. 12 the same reference numerals are used for the parts that correspond to the first embodiment, so that reference is made to avoid repetition of the description of the first embodiment.
  • the spring element 30, which in the first embodiment z. B. is designed as a cylindrical coil spring in the form of a tension spring, instead designed as a leaf spring 75.
  • This leaf spring 75 engages with a spring end on the shaft 24 and / or on the fork lever 27, while the other end of the spring is fixed at a transverse distance from the housing 15.
  • the leaf spring 75 is when the flap 26 of the switching valve 23 is brought into a switching position, curved approximately arcuate, as in Fig. 12 left and right positions, each of which may be assigned to a switching position show.
  • the rotary or rotary actuator of the return valve 17 is carried out directly via the drive wheel 59 and the actuating shaft 31 on the thus non-rotatable valve member 32nd
  • the drive wheel 59 does not work directly but by means of the following described transformer on the actuating shaft 31 of the return valve 17.
  • the same reference numerals are used for the parts that correspond to the first embodiment, thereby thereby avoiding repetition is made to the description of the first embodiment reference.
  • the transmission 20 has a spur gear in the form of driven by the rotary drive 19 output gear 60, in particular of the pinion, and with the latter engaged drive wheel 59, the z. B. rotatably supported on an axis 76 and guided.
  • the drive wheel 59 may be rotatably connected to the axis 76, which in turn is then rotatably received in the housing 15 and stored.
  • the return valve 17 is formed as a flapper valve, wherein the valve member 32 is designed as a hinged lid 77 which is disposed adjacent to the actuating shaft 31 and connected thereto via a transverse arm 78 and along an arcuate path around the axis of the actuating shaft 31 around between the z ,
  • the valve member 32 is designed as a hinged lid 77 which is disposed adjacent to the actuating shaft 31 and connected thereto via a transverse arm 78 and along an arcuate path around the axis of the actuating shaft 31 around between the z ,
  • Fig. 17 and Fig. 18 shown closed position and in Fig. 16 and Fig. 19 Open position is movable.
  • a valve opening 79 In the closed position according to Fig. 17 and 18 is covered by the hinged lid 77, a valve opening 79, while in the open position according to Fig. 16 and 19 in which the hinged lid 77 is moved away from the valve opening 59 is released.
  • the drive wheel 59 carries in the region of the outer periphery an upwardly directed pin 29 which cooperates in the same manner as in the first embodiment with the fork lever 27 for switching movement of the shaft 24 of the switching valve 23.
  • an upwardly directed pin 29 which cooperates in the same manner as in the first embodiment with the fork lever 27 for switching movement of the shaft 24 of the switching valve 23.
  • the drive wheel 59 acts here via a cam gear 80 on the actuating shaft 31 of the return valve 17.
  • This cam gear 80 has below the drive wheel 59, a cam member 81 with a cam 82, with a roller 83 is engaged and held in engagement.
  • the roller 83 is rotatably held on a lever 84 which is rotatably connected to the actuating shaft 31 of the return valve 17.
  • the cam member 81 is driven by the drive wheel 59 of the drive device 18.
  • the cam member 81 may, for. B. be integral with the drive wheel 59 ( Fig. 14 ) and be rotatably mounted together with this on the axis 76.
  • the cam member 81 is formed as a cam.
  • the Camming cam 82 is eccentric with respect to axis 76, which axis 76 is approximately parallel to actuating shaft 31.
  • the cam curve 82 is provided on the outer peripheral surface of the cam member 81, wherein the roller 83 abuts against this outer surface and is resiliently pressed by means of a spring 85 to this outer surface.
  • the spring 85 is fixed at one end to the housing 15 and works with the other end on the lever 84 or the actuating shaft 31. This ensures that the roller 83 is resiliently pressed against the outer surface of the cam member 81, wherein any deposits between the Valve seat in the region of the valve opening 79 and the hinged lid 77, the functionality of the valve device 10 is maintained.
  • This valve device 10 is particularly suitable for use in high-pressure exhaust gas recirculation devices.
  • the valve member 32 can be opened with the flow of the exhaust gas or in particular against the flow, wherein the valve member 32 is pressed with the differential pressure against the valve seat of the valve opening 79. Due to the cam gear 80, it is possible to apply for transferring the return valve 17 from the closed position to the open position when opening against the exhaust flow, the large required driving torques, which in the wide open position of the valve member 32 then only small actuating torques are required.
  • the valve device according to the third embodiment has a simple actuator for the return valve 17 with a highly variable transmission ratio between the closed position and the open position, which is also tolerant of a changing over the operation angle of rotation of the closed position.
  • the cam gear 80 With the cam gear 80, a design is realized which has a compact gear, which has a large gear ratio in the opening area, but greatly decreases with further opening, thus allowing a short positioning time between the closed position and the fully open position.
  • the transmission efficiency is high due to low friction.
  • the cam member 81 is designed with respect to the configuration of the cam curve 82 so that Beginning of the movement a large force is exerted on the lever 84 and at the end only a small force is exerted on it. If soiled between the valve seat of the valve opening 79 and the hinged lid 77, the hinged lid 77 is held by the deposits at a distance from the valve seat.
  • roller 83 can lift off the cam curve 82 via the corresponding pivoting of the actuating shaft 31 with lever 84. A possible jamming in the region of the cam gear 80 and the actuation of the valve member 32 is avoided in a simple manner.
  • the cam member 81 on three different curves I, II, and III on its outer peripheral surface. If the changeover valve 23 is transferred in the manner described in the end position, which corresponds to the bypass operation, the curve I of the cam member 81 during rotation of this counterclockwise in accordance with FIGS. 16 and 17 provided for the corresponding volume control of the exhaust gas, starting from the in Fig. 17 shown closed position of the return valve 17 to the in Fig. 16 shown opening position. This is achieved by rotation of the cam member 81 about the axis 76 in the counterclockwise direction as indicated by arrow 86.
  • the cam curve 82 with the curves I, II and III is thus designed such that at the beginning of an opening against the flow direction opening operation of the return valve 17, a large force and at the end of the opening operation, only a small force on the lever 84 is exercised.
  • the cam gear 80 achieves an extremely compact design with a low space requirement.
  • the cam member 81 can easily realize a variety of different characteristics for the valve opening and closing operation.
  • cam gear 80 is formed of the described cam member 81 and the roller 83 in the third embodiment, however, any other types of cam gear are also conceivable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Exhaust Silencers (AREA)
EP09008700A 2008-11-13 2009-07-03 Dispositif de soupape destiné à la commande d'un flux de gaz d'échappement transporté ou recyclé à partir d'un moteur à combustion interne Withdrawn EP2187032A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008057128A DE102008057128A1 (de) 2008-11-13 2008-11-13 Ventileinrichtung zur Steuerung eines von einer Brennkraftmaschine zurückgeführten und zugeführten Abgasstromes

Publications (2)

Publication Number Publication Date
EP2187032A2 true EP2187032A2 (fr) 2010-05-19
EP2187032A3 EP2187032A3 (fr) 2012-03-28

Family

ID=41727394

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09008700A Withdrawn EP2187032A3 (fr) 2008-11-13 2009-07-03 Dispositif de soupape destiné à la commande d'un flux de gaz d'échappement transporté ou recyclé à partir d'un moteur à combustion interne

Country Status (2)

Country Link
EP (1) EP2187032A3 (fr)
DE (1) DE102008057128A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014140447A1 (fr) * 2013-03-13 2014-09-18 Valeo Systemes De Controle Moteur Dispositif d'aiguillage d'un fluide pour une vanne ayant au moins trois voies
WO2014167266A1 (fr) * 2013-04-12 2014-10-16 Valeo Systemes De Controle Moteur Vanne, notamment de controle moteur, dotee d'un volet de dosage et d'un volet d'aiguillage
WO2014167264A1 (fr) * 2013-04-12 2014-10-16 Valeo Systemes De Controle Moteur Vanne, notamment de controle moteur, dotee d'un volet de dosage et d'un volet d'aiguillage
WO2014167265A1 (fr) * 2013-04-12 2014-10-16 Valeo Systemes De Controle Moteur Vanne, notamment de controle moteur, dotee d'un volet de dosage et d'un volet d'aiguillage
FR3022968A1 (fr) * 2014-06-30 2016-01-01 Valeo Sys Controle Moteur Sas Ensemble de regulation fluidique d'une vanne

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015100546A1 (de) 2014-02-13 2015-08-13 BorgWarner Esslingen GmbH Heißgasventil, insbesondere AGR-Ventil

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1707790A1 (fr) 2005-03-31 2006-10-04 Cooper-Standard Automotive (Deutschland) GmbH Système de recyclage des gaz d'échappement

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5740785A (en) * 1997-06-09 1998-04-21 Southwest Research Institute Two way-high pressure loop, exhaust gas recirculation valve
US6089019A (en) * 1999-01-15 2000-07-18 Borgwarner Inc. Turbocharger and EGR system
LU90480B1 (en) * 1999-11-29 2001-05-30 Delphi Tech Inc Exhaust gas re-circulation device for an internal combustion engine
US6390079B1 (en) * 2000-08-21 2002-05-21 Siemens Canada Limited Exhaust gas recirculation valve including cam linkage for converting constant angular motion to non-linear motion
EP1270924A3 (fr) * 2001-06-28 2004-01-07 Delphi Technologies, Inc. Ensemble intégré de collecteur d'admission pour un moteur à combustion interne
US7461642B2 (en) * 2006-01-13 2008-12-09 Delphi Technologies, Inc. Rotary-actuated exhaust gas recirculation valve having a seating force attenuator
DE102008005591A1 (de) * 2008-01-22 2009-07-23 Bayerische Motoren Werke Aktiengesellschaft Ventileinrichtung für eine Abgasrückführungseinrichtung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1707790A1 (fr) 2005-03-31 2006-10-04 Cooper-Standard Automotive (Deutschland) GmbH Système de recyclage des gaz d'échappement

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014140447A1 (fr) * 2013-03-13 2014-09-18 Valeo Systemes De Controle Moteur Dispositif d'aiguillage d'un fluide pour une vanne ayant au moins trois voies
FR3003326A1 (fr) * 2013-03-13 2014-09-19 Valeo Sys Controle Moteur Sas Dispositif d'aiguillage d'un fluide pour une vanne ayant au moins trois voies
WO2014167266A1 (fr) * 2013-04-12 2014-10-16 Valeo Systemes De Controle Moteur Vanne, notamment de controle moteur, dotee d'un volet de dosage et d'un volet d'aiguillage
WO2014167264A1 (fr) * 2013-04-12 2014-10-16 Valeo Systemes De Controle Moteur Vanne, notamment de controle moteur, dotee d'un volet de dosage et d'un volet d'aiguillage
WO2014167265A1 (fr) * 2013-04-12 2014-10-16 Valeo Systemes De Controle Moteur Vanne, notamment de controle moteur, dotee d'un volet de dosage et d'un volet d'aiguillage
FR3004502A1 (fr) * 2013-04-12 2014-10-17 Valeo Sys Controle Moteur Sas Vanne, notamment de controle moteur, dotee d’un volet de dosage et d’un volet d’aiguillage
FR3004504A1 (fr) * 2013-04-12 2014-10-17 Valeo Sys Controle Moteur Sas Vanne, notamment de controle moteur, dotee d’un volet de dosage et d’un volet d’aiguillage
FR3004503A1 (fr) * 2013-04-12 2014-10-17 Valeo Sys Controle Moteur Sas Vanne, notamment de controle moteur, dotee d’un volet de dosage et d’un volet d’aiguillage
US20160138533A1 (en) * 2013-04-12 2016-05-19 Valeo Systemes De Controle Moteur Valve, in particular an engine control valve, equipped with a metering gate and a diverter gate
US20160161020A1 (en) * 2013-04-12 2016-06-09 Valeo Systemes De Controle Moteur Valve, in particular an engine control valve, equipped with a metering gate and a diverter gate
FR3022968A1 (fr) * 2014-06-30 2016-01-01 Valeo Sys Controle Moteur Sas Ensemble de regulation fluidique d'une vanne
WO2016001526A1 (fr) * 2014-06-30 2016-01-07 Valeo Systemes De Controle Moteur Ensemble de regulation fluidique d'une vanne

Also Published As

Publication number Publication date
DE102008057128A1 (de) 2010-05-20
EP2187032A3 (fr) 2012-03-28

Similar Documents

Publication Publication Date Title
WO2007051332A2 (fr) Activateur comprenant un mecanisme de reduction pour un element d'activation permettant de reguler le debit d'un gaz ou d'un fluide
EP2084439A2 (fr) Tiroir rotatif, notamment pour un circuit de réfrigérant d'un moteur à combustion interne présentant plusieurs branches ; sous-ensemble électromécanique
EP2187032A2 (fr) Dispositif de soupape destiné à la commande d'un flux de gaz d'échappement transporté ou recyclé à partir d'un moteur à combustion interne
DE102006031028A1 (de) Betätigungseinrichtung eines Ventils, insbesondere eines Abasrückführventil
DE4339393A1 (de) Flacher Drehschieber
EP2017456A1 (fr) Système de recirculation de gaz d'échappement
WO2008110192A1 (fr) Dispositif d'actionnement pour un capot d'une ouverture de carrosserie d'une automobile
EP2067977B1 (fr) Soupape double pour un dispositif de recirculation des gaz d'échappement
DE102016210979A1 (de) Ventiltrieb für eine Brennkraftmaschine
EP0620386A1 (fr) Système d'actionneurs pour boîte de vitesses de véhicule
EP1332306B1 (fr) Dispositif de reglage a rotation
EP3008313A1 (fr) Dispositif d'actionnement et dispositif à clapet pourvu d'un dispositif d'actionnement de ce type
EP1526272B2 (fr) Soupape de recirculation de gaz d'échappement
EP0620387A2 (fr) Actionneur pour boîte de vitesses de véhicule
WO2002023032A1 (fr) Verin de commande electromoteur a deux etapes, destine a une soupape
DE102010006037B4 (de) Ventilvorrichtung für eine Verbrennungskraftmaschine
DE102007036286A1 (de) Ventil, insbesondere Abgasrückführventil
EP2172638B1 (fr) Dispositif de ventilation pour la commande d'un flux de gaz d'échappement
DE2334571A1 (de) Ventilbetaetigungsvorrichtung
EP2478204B1 (fr) Dispositif de réglage et dispositif d'accouplement
DE4113019A1 (de) Klappenventil
EP1637783B1 (fr) Combinaison de soupape pour turbine à vapeur avec une soupape à fermeture rapide et une soupape de régulation
DE102004003208A1 (de) Verdichter im Ansaugtrakt einer Brennkraftmaschine
WO2014191203A1 (fr) Moteur à combustion interne équipé d'un arbre à cames réglable
EP2689112B1 (fr) Entraînement de soupapes à commande mécanique et système d'entraînement de soupapes à commande mécanique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

RIC1 Information provided on ipc code assigned before grant

Ipc: F02M 25/07 20060101AFI20120223BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20120929