EP3181874B1 - Boîtier de papillon pour un système de boîtier de papillon pour un moteur à combustion interne - Google Patents

Boîtier de papillon pour un système de boîtier de papillon pour un moteur à combustion interne Download PDF

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Publication number
EP3181874B1
EP3181874B1 EP16204900.1A EP16204900A EP3181874B1 EP 3181874 B1 EP3181874 B1 EP 3181874B1 EP 16204900 A EP16204900 A EP 16204900A EP 3181874 B1 EP3181874 B1 EP 3181874B1
Authority
EP
European Patent Office
Prior art keywords
throttle valve
valve housing
sealing
edge
sealing piece
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.)
Not-in-force
Application number
EP16204900.1A
Other languages
German (de)
English (en)
Other versions
EP3181874A1 (fr
Inventor
Oberacker Dieter
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.)
Fischer Rohrtechnik GmbH
Original Assignee
Fischer Rohrtechnik 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
Priority claimed from DE102015122036.9A external-priority patent/DE102015122036A1/de
Priority claimed from DE102016110998.3A external-priority patent/DE102016110998A1/de
Priority to RS20190213A priority Critical patent/RS58698B1/sr
Application filed by Fischer Rohrtechnik GmbH filed Critical Fischer Rohrtechnik GmbH
Priority to PL16204900T priority patent/PL3181874T3/pl
Priority to PCT/EP2017/064585 priority patent/WO2017216246A1/fr
Priority to US16/310,018 priority patent/US10753288B2/en
Priority to CN201780050184.4A priority patent/CN109642504A/zh
Publication of EP3181874A1 publication Critical patent/EP3181874A1/fr
Publication of EP3181874B1 publication Critical patent/EP3181874B1/fr
Application granted granted Critical
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1035—Details of the valve housing
    • F02D9/104—Shaping of the flow path in the vicinity of the flap, e.g. having inserts in the housing
    • F02D9/1045—Shaping of the flow path in the vicinity of the flap, e.g. having inserts in the housing for sealing of the flow in closed flap position, e.g. the housing forming a valve seat

Definitions

  • the present invention relates to a throttle body according to the subject-matter of independent claim 1.
  • Throttle valve assemblies for internal combustion engines have long been known.
  • such throttle valve arrangements are provided in order to be able to control the amount of air flowing into the engine in a targeted manner, so that it is possible to influence the output power of gasoline engines by adjusting the air-fuel ratio.
  • throttle valve arrangements in the incoming air stream have a different meaning, namely with regard to adjusting the recirculation rate of exhaust gases.
  • throttle valve arrangements are frequently used for influencing noise emissions and for influencing the back pressure in the exhaust gas system. Due to the thermal load throttle body are usually made of metal.
  • the throttle valve assemblies that is influenced by pivoting the throttle valve in the throttle body, the flow cross-section and thus the flow resistance between the inlet and the discharge opening.
  • the inflow opening is used to hold a fluid - usually of fresh air, exhaust gas or a mixture of both - in the throttle body. Accordingly, the fluid escapes via the discharge opening from the throttle body.
  • the flow path between the inflow port and the outflow port is influenced by the throttle valve. It is readily apparent that a quality feature for throttle assemblies is the degree of tightness achieved in the throttle closed position. Of course, in the production of throttle valve assemblies, this degree of tightness must be reproducible with high accuracy to achieve consistent quality.
  • Throttle valve arrangements are frequently known from the prior art in which the throttle body is completely uncontoured even in the area of movement of the throttle valve, so that the throttle valve forms a sealing gap in the closed position with the throttle body which, viewed in the direction of flow, thus flows from the inlet opening the flap housing looking to the outflow opening, can be seen.
  • the throttle is then practically perpendicular to the wall of the throttle body.
  • additional material for example, in the form of an integrally formed on the wall of the throttle body plate - to install, so that a stop for the throttle valve is formed in its closed position.
  • DE4408909A1 discloses a throttle body, wherein the sealing ridge is formed spanok in the wall of the throttle body.
  • DE4329526A1 discloses a method of manufacturing a throttle body wherein the seal bar is made in the throttle body by forming.
  • the object of the present invention is to provide a throttle body with improved sealing properties, and a corresponding method for producing such a throttle body.
  • a throttle body according to the subject of independent claim 1. Due to the chip-free design of the sealing web in the wall of the throttle body is made clear that the sealing web is made with the material of the wall and no additional elements for the realization of the sealing web are introduced into the throttle body.
  • a throttle body can be prepared by machining the chip-free forming, so for example by applying the high pressure forming or by pressing the wall material of the throttle body into a correspondingly contoured counter-mold with a rigid die (female-male forming).
  • Such a throttle body is therefore particularly advantageous because not only simple geometries of the movement space of the throttle and simple throttle body geometries can be realized, but virtually any contours can be realized.
  • the throttle body and the sealing web of the throttle body are made of a one-piece pipe part by chip-free forming is particularly advantageous.
  • Circular tubes can also be used to produce non-circular throttle bodies, especially in the area of the movement space of the throttle valve.
  • the sealing web is formed in the movement space everywhere where the throttle valve terminates only in the closed position with the throttle body.
  • the sealing web does not have to be a completely and closed circumferential sealing contour, but instead the sealing web is only formed where it can also unfold a corresponding sealing and stopping action with respect to the throttle valve.
  • the throttle valve is attached to a shaft which extends centrally through the flow cross-section of the movement space of the throttle body. When pivoting the throttle valve with such a shaft inevitably moves a part of the throttle valve against the flow direction and the other part of the throttle valve in the flow direction.
  • the throttle valve is practically not moved, at least not moved in the sense of a release and a closing of a flow cross-section. Accordingly, in the area of the shaft, the sealing web must not be executed. It can be seen from this example that the sealing web can be formed by a plurality of sealing web segments, which are formed along the sealing contour in and with the throttle body.
  • the sealing web has a triangular profile with a flow flank, with a sealing flank and with a dome, wherein the flow flank and the sealing flank originate from a respective base level of the throttle body with a foot point and converge in the dome.
  • the dome protrudes furthest into the flow cross section.
  • the sealing flank is formed on the side of the sealing web on which the throttle valve strikes in the closed position.
  • the flow flank is consequently arranged on the other side, ie opposite the sealing flank.
  • Such a geometry of the sealing bar is particularly easy to produce and also gentle to the material. Due to the non-cutting shaping of the wall of the throttle body, a material flow is practically always to effect, which can significantly burden the formed material.
  • the stress is greatest where the largest internal material displacement is effected, since the structure of the material is changed the most there.
  • the triangular profile also has fluidic advantages, since the guided through the throttle body fluid flow is performed continuously and without offset through the edges of the sealing land, so that the influence of the sealing land is fluidically relatively low. It is particularly preferably provided that in the sealing flank between its base and the dome a flat sealing area is formed. In a tubular throttle body so practically a circumferential sealing surface is realized, which - looking in or opposite to the flow direction of the sealing edge - forms a sealing ring. This is advantageous because it is particularly easy to also just form the parts of the throttle, in the closed position of the throttle valve face the flat sealing region of the sealing edge.
  • the triangular profile of the sealing web is formed asymmetrically, wherein the sealing edge is steeper than the flow edge. It has proven to be advantageous to let the sealing edge run relatively steep, so with a very large slope in the flow cross section.
  • the sealing flank is then inclined only very slightly with respect to the flow cross-section and thus with respect to the throttle valve located in the closed position, which is then usually positioned in the flow cross-section, ie perpendicular to the flow direction.
  • the throttle valve should rest not only with a narrow edge on its outer boundary on the sealing edge of the sealing strip circumferentially, but a better sealing effect is to be achieved, then the throttle should lie flat in the closed position on the sealing edge of the sealing web, so that realizes a circumferential sealing surface becomes. In this area, the throttle must thus form a correspondingly molded counterpart to the sealing edge. The steeper the sealing flank protrudes into the flow cross-section, the less must the throttle flap be bevelled in its sealing edge region, deviating from the pure shape of a flat disk.
  • a disadvantage of the steep profile of the sealing flank in the flow cross-section is that the material load by non-cutting forming, for example by hydroforming, in this area is very high, since with little material, a relatively large deformation must be realized.
  • the flow flank extends flatter than the sealing flank, so that significantly more material of the wall of the throttle body is available compared to the sealing flank to form the flow flank from its base to the crest.
  • the asymmetrical design of the triangular sealing bar profile results in a comparatively small proportion of the area of the sealing bar - namely that in the region of the flow flank - being subjected to a comparatively small amount is and that a better stiffness than in a symmetrical design is achieved.
  • the chip-free design of the sealing web in the wall of the throttle body allows a precise realization of the angle of attack of the sealing flank and also a precise realization of a flat sealing area, in which case a slightly larger material load is accepted than at the flow flank.
  • the realization of a provided on the outer periphery of the throttle aperture with a slope corresponding to the slope of the sealing edge is also advantageous because in this way also causes a stiffening of the throttle itself.
  • the inclination of the sealing flank additionally leads to the fact that the sealing surface is increased, in any case with respect to a vertically extending sealing flank, which therefore runs perpendicular to the flow direction.
  • the plane sealing area of the sealing flank is inclined more than 70 °, more preferably more than 75 ° and most preferably about 80 ° with respect to the flow axis of the throttle body.
  • the flow flank is inclined less than 50 °, more preferably less than 40 ° and most preferably about 35 ° relative to the flow axis of the throttle body.
  • the invention also relates to a method for producing a throttle body for a throttle assembly for an internal combustion engine according to the subject-matter of independent claim 10.
  • the initially derived object is achieved in this method in that a one-piece pipe part is reshaped so that the sealing web is produced in the throttle body by chip-free forming.
  • the tube part is deformed by pressure effect from the inside to the outside, so that a material flow is brought to the outside in a shaping outer tool, in particular by hydroforming or by moving a rigid inner tool into a rigid outer tool.
  • Fig. 1 to 5 are shown in varying degrees of detail and with different focuses throttle body 1. Throttle body forms together with the throttle valves installed in them throttle valve assemblies; the throttle valves are not shown here themselves, of particular interest are the throttle body 1.
  • Throttle body 1 serve to accommodate a pivotally mounted throttle and therefore form the space for movement of the throttle.
  • the throttle body 1 has on a first side an inflow port 2 for receiving a fluid, and the throttle body 1 has on a second side an exhaust port 3 for discharging the throttle body 1 by flowing fluid; characterized the flow direction D is defined.
  • the throttle body 1 and the sealing web 4 of the throttle body 1 are made of a one-piece pipe part by chip-free forming.
  • the throttle body 1 shown in the figures has been made by hydroforming using a solid but flexible forming medium. As a molding medium, a polyurethane elastomer has been used.
  • the medium is introduced into the blank of the throttle body 1, axially, thus compressed in the flow direction D, whereby the material escapes radially and presses the wall of the blank in an unillustrated outer tool, whereby the end-formed Throttle body 1 is formed, which is shown in the figures.
  • Fluide forming media can also be used.
  • the sealing web 4 is formed in the movement space where the throttle valve terminates only in the closed position with the throttle body 1; in the region of the shaft opening 5 or around the shaft opening 5, the sealing web 4 is not formed. This results in two nearly semicircular sealing bar segments, which are incoherent and together form the sealing bar 4.
  • the sealing ridge 4 has a triangular profile with a flow edge 6, with a sealing edge 7 and a dome 8, wherein the flow edge 6 and the sealing edge 7 each originate from a base level G of the throttle body 1 with a base FP and in the dome 8 converge.
  • the base level is formed by the straight course of the wall of the throttle body, starting from which the contouring of the wall by the sealing web 4 begins.
  • the dome 8 is the element which projects furthest into the flow cross section.
  • the sealing flank 7 is formed on the side of the sealing web 4, against which the throttle valve strikes in the closed position.
  • a flat sealing region 9 is formed between its base FP and the dome 8. This is particularly advantageous because a correspondingly flat counter surface can be formed without much effort on the throttle, for example in the form of an applied aperture. As a result, a significantly better sealing effect is achieved than if the sealing web 4 and the throttle valve would only seal against one another in a line-shaped contact contour.
  • the triangular profile of the sealing web 4 is formed asymmetrically, wherein the sealing edge 7 is steeper than the flow edge 6.
  • the planar sealing region 9 is inclined at about 80 ° with respect to the flow axis or the flow direction D, respectively, relative to the base level G of the throttle body 1.
  • Fig. 3 is good to see that the sealing edge 7 fuß Vietnamese medicinal substance reaches below the base level of the throttle body 1, namely the base level by the distance h below.
  • the reshaped contour runs arcuately in the base level G of the throttle body 1. This "undershooting" of the contour profile causes larger Umformradien can be realized with a smaller material load.
  • a larger, even sealing area 9 can be realized in this way since the sealing area 9 is widely spaced from the outlet area of the arcuate section at the root FP of the sealing flank 7.
  • Fig. 3 indicates that the flow edge 6 is inclined about 35 ° relative to the flow axis D of the throttle body 1 and thus with respect to the base level G of the throttle body 1.
  • Fig. 1 . 2 and 4 to 6 in each case at least one circular opening region 5 is shown as a passage point for a drive shaft 10; the shaft 10 is only in the Fig. 5 and 6 shown schematically.
  • the throttle body 1 is formed by hydroforming, the only defined opening area 5 is still closed; he will be opened afterwards, here by laser cutting.
  • the sealing web 4 eccentrically to the opening portion 5, wherein the height of the sealing ridge 4 ramps down to the level of the boundary of the defined opening portion 5.
  • the height of the sealing web 4 is thus already switched off on reaching the border of the opening area 5 to zero.
  • Fig. 4 perspective situation is shown in Fig. 5 shown again simplified, wherein the shaft 10 has entered the place of the defined opening area 5. This is necessary in order to be able to recognize the advantageousness of the construction described.
  • the height of the sealing web 4 drops in a ramp shape, that is to say along the ramp 11, to the level of the boundary of the defined opening region, it is considered in the flow direction (FIG. Fig. 5 below) realized over the full circumference almost closed sealing ring, also directly on the shaft 10th
  • FIG. 6 An alternative realization is in Fig. 6 shown. Again, the sealing ridge 4 off-center on the circular opening portion 5 as a passage point for the drive shaft 10, the in Fig. 6 has taken the place of the opening area 5. The height of the sealing web 4 remains unchanged up to the boundary of the defined opening area 5 or up to the shaft 10. In Fig. 6 above is indicated that the ramp 11 only in the region of the potential opening 5, here replaced by the shaft 10, drops. Even so, as seen in the flow direction, a closed sealing contour can be realized, but then the boundary of the opening 5 is no longer circular.

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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)

Claims (11)

  1. Boîtier de vanne papillon (1) pour un système de vanne papillon pour un moteur à combustion interne, dans lequel le boîtier de vanne papillon (1) est destiné à contenir une vanne papillon montée de façon pivotante et forme la chambre de mouvement pour la vanne papillon, dans lequel le boîtier de vanne papillon (1) présente sur un premier côté une ouverture d'entrée (2) pour l'admission d'un fluide et le boîtier de vanne papillon (1) présente sur un deuxième côté une ouverture de sortie (3) pour l'évacuation d'un fluide et dans lequel au moins une nervure d'étanchéité (4) s'engageant dans la section transversale d'écoulement, qui sert de butée pour la vanne papillon en position fermée, est disposée dans la chambre de mouvement du boîtier de vanne papillon (1), dans lequel la nervure d'étanchéité (4) est formée sans enlèvement de copeaux dans la paroi du boîtier de vanne papillon (1), dans lequel la nervure d'étanchéité (4) présente un profil de forme triangulaire avec un flanc d'écoulement (6), avec un flanc d'étanchéité (7) et avec un sommet arrondi (8), dans lequel le flanc d'écoulement (6) et le flanc d'étanchéité (7) partent respectivement d'un niveau de base G du boîtier de vanne papillon (1) avec un point de pied FP et se rejoignent au sommet arrondi (8), dans lequel le sommet arrondi (8) pénètre le plus profondément dans la section transversale d'écoulement et dans lequel le flanc d'étanchéité (7) est formé sur le côté de la nervure d'étanchéité (4), sur lequel la vanne papillon vient buter en position fermée, dans lequel le profil de forme triangulaire de la nervure d'étanchéité (4) est de forme asymétrique, caractérisé en ce que le flanc d'étanchéité (7) arrive du côté du point de pied en dessous du niveau de base (8) du boîtier de vanne papillon (1).
  2. Boîtier de vanne papillon (1) selon la revendication 1, caractérisé en ce que le boîtier de vanne papillon (1) et la nervure d'étanchéité (4) du boîtier de vanne papillon (1) sont fabriqués à partir d'une pièce tubulaire d'un seul tenant par déformation sans enlèvement de copeaux.
  3. Boîtier de vanne paillon (1) selon la revendication 1 ou 2, caractérisé en ce que la nervure d'étanchéité (4) est formée dans la chambre de mouvement partout là où la vanne papillon ne ferme avec le boîtier de vanne papillon (1) que dans la position fermée.
  4. Boîtier de vanne papillon (1) selon l'une quelconque des revendications 1 à 3, caractérisé en ce qu'une zone d'étanchéité plane (9) est formée dans le flanc d'étanchéité (7) entre le point de pied FP et le sommet arrondi (8).
  5. Boîtier de vanne papillon (1) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le flanc d'étanchéité (7) est plus abrupt que le flanc d'écoulement (6), dans lequel la zone d'étanchéité plane (9) est inclinée de préférence de plus de 70°, en particulier de préférence de plus de 75°, et tout particulièrement de préférence d'environ 80° par rapport à l'axe d'écoulement D ou à la ligne de niveau de base G du boîtier de vanne papillon (1).
  6. Boîtier de vanne papillon (1) selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le flanc d'étanchéité (7) se termine sous forme d'arc dans la ligne de niveau de base G du boîtier de vanne papillon (1).
  7. Boîtier de vanne papillon (1) selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le flanc d'écoulement (6) est incliné de préférence de moins de 50°, en particulier de préférence de moins de 40°, et tout particulièrement de préférence d'environ 35° par rapport à l'axe d'écoulement D ou à la ligne de niveau de base G du boîtier de vanne papillon (1).
  8. Boîtier de vanne papillon (1) selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'au moins une zone d'ouverture ronde (5) est définie en tant que point de passage pour un arbre d'entraînement (10) de la vanne papillon, dans lequel la nervure d'étanchéité (4) arrive de façon décentrée sur la zone d'ouverture (5), dans lequel la hauteur de la nervure d'étanchéité (4) diminue en forme de rampe jusqu'au niveau du bord de la zone d'ouverture définie (5).
  9. Boîtier de vanne papillon (1) selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'au moins une zone d'ouverture ronde est définie en tant que point de passage pour un arbre d'entraînement (10) de la vanne papillon, dans lequel la nervure d'étanchéité (4) arrive de façon décentrée dans la zone d'ouverture (5), dans lequel la hauteur de la nervure d'étanchéité (4) reste inchangée jusqu'au bord de la zone d'ouverture définie (5) et la hauteur de la nervure d'étanchéité (4) ne diminue qu'ensuite en forme de rampe.
  10. Procédé de fabrication d'un boîtier de vanne papillon (1) pour un système de vanne papillon pour un moteur à combustion interne, dans lequel le boîtier de vanne papillon (1) est destiné à contenir une vanne papillon montée de façon pivotante et forme la chambre de mouvement pour la vanne papillon, dans lequel le boîtier de vanne papillon (1) présente sur un premier côté une ouverture d'entrée (2) pour l'admission d'un fluide et le boîtier de vanne papillon (1) présente sur un deuxième côté une ouverture de sortie (3) pour l'évacuation d'un fluide et dans lequel au moins une nervure d'étanchéité (4) s'engageant dans la section transversale d'écoulement, qui sert de butée pour la vanne papillon en position fermée, est disposée dans la chambre de mouvement du boîtier de vanne papillon (1), caractérisé en ce que la nervure d'étanchéité (4) est formée sans enlèvement de copeaux dans la paroi du boîtier de vanne papillon (1), dans lequel la nervure d'étanchéité (4) présente un profil de forme triangulaire avec un flanc d'écoulement (6), avec un flanc d'étanchéité (7) et avec un sommet arrondi (8), dans lequel le flanc d'écoulement (6) et le flanc d'étanchéité (7) partent respectivement d'un niveau de base G du boîtier de vanne papillon (1) avec un point de pied FP et se rejoignent au sommet arrondi (8), dans lequel le sommet arrondi (8) pénètre le plus profondément dans la section transversale d'écoulement, dans lequel le flanc d'étanchéité (7) est formé sur le côté de la nervure d'étanchéité (4), sur lequel la vanne papillon vient buter en position fermée, le profil de forme triangulaire de la nervure d'étanchéité (4) est de forme asymétrique et dans lequel le flanc d'étanchéité (7) arrive du côté du point de pied en dessous du niveau de base (8) du boîtier de vanne papillon (1), dans lequel on déforme une pièce tubulaire d'un seul tenant de telle manière que la nervure d'étanchéité (4) soit produite dans le boîtier de vanne papillon (1) par déformation sans enlèvement de copeaux, à savoir par déformation de la pièce tubulaire par action de la pression de l'intérieur vers l'extérieur par déformation sous haute pression intérieure, de façon à créer un flux de matière vers l'extérieur dans un outil extérieur de formage.
  11. Procédé selon la revendication 10, caractérisé en ce que l'on déforme la pièce tubulaire en un boîtier de vanne papillon (1) avec nervure d'étanchéité (4) selon les caractéristiques d'au moins une partie caractérisante d'une des revendications 3 à 9.
EP16204900.1A 2015-12-16 2016-12-16 Boîtier de papillon pour un système de boîtier de papillon pour un moteur à combustion interne Not-in-force EP3181874B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PL16204900T PL3181874T3 (pl) 2015-12-16 2016-12-16 Obudowa przepustnicy do układu przepustnic do silnika spalinowego
RS20190213A RS58698B1 (sr) 2015-12-16 2016-12-16 Kućište prigušnog ventila za sklop prigušnog ventila kod motora sa unutrašnjim sagorevanjem
PCT/EP2017/064585 WO2017216246A1 (fr) 2016-06-15 2017-06-14 Boîtier de papillon des gaz pour un ensemble papillon des gaz pour un moteur à combustion interne
US16/310,018 US10753288B2 (en) 2016-06-15 2017-06-14 Throttle valve housing for a throttle valve arrangement for an internal combustion engine
CN201780050184.4A CN109642504A (zh) 2016-06-15 2017-06-14 用于燃烧马达用的节流阀装置的节流阀壳体

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015122036.9A DE102015122036A1 (de) 2015-12-16 2015-12-16 Drosselklappenanordnung für einen Abgasstrang oder einen Zuluftstrang eines Verbrennungsmotors
DE102016110998.3A DE102016110998A1 (de) 2016-06-15 2016-06-15 Drosselklappenanordnung und Verfahren zur Herstellung einer Drosselklappenanordnung

Publications (2)

Publication Number Publication Date
EP3181874A1 EP3181874A1 (fr) 2017-06-21
EP3181874B1 true EP3181874B1 (fr) 2018-11-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16204900.1A Not-in-force EP3181874B1 (fr) 2015-12-16 2016-12-16 Boîtier de papillon pour un système de boîtier de papillon pour un moteur à combustion interne

Country Status (6)

Country Link
EP (1) EP3181874B1 (fr)
ES (1) ES2711752T3 (fr)
HU (1) HUE042579T2 (fr)
PL (1) PL3181874T3 (fr)
PT (1) PT3181874T (fr)
RS (1) RS58698B1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2487034B1 (fr) * 1980-07-18 1985-09-27 Pont A Mousson Robinet a papillon
DE8120908U1 (de) * 1981-07-16 1981-10-08 Bowa GmbH, Apparate- und Behälterbau, 8261 Aschau Rohrstutzen mit einer schwenkbaren abgasklappe
DE4329526A1 (de) * 1993-09-02 1995-03-09 Mann & Hummel Filter Drosseleinrichtung
DE4408909A1 (de) * 1994-03-16 1995-09-21 Bosch Gmbh Robert Verfahren zum Herstellen einer Drosselvorrichtung
DE102005028397A1 (de) * 2005-06-20 2006-12-28 Arvinmeritor Emissions Technologies Gmbh Ventil, insbesondere für eine Kraftfahrzeug-Abgasanlage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
PL3181874T3 (pl) 2019-05-31
RS58698B1 (sr) 2019-06-28
PT3181874T (pt) 2019-02-25
HUE042579T2 (hu) 2019-07-29
ES2711752T3 (es) 2019-05-07
EP3181874A1 (fr) 2017-06-21

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