EP3203048B1 - Système de fixation d'un tuyau coudé de sortie sur une culasse de cylindre d'un moteur à combustion interne - Google Patents

Système de fixation d'un tuyau coudé de sortie sur une culasse de cylindre d'un moteur à combustion interne Download PDF

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Publication number
EP3203048B1
EP3203048B1 EP17153043.9A EP17153043A EP3203048B1 EP 3203048 B1 EP3203048 B1 EP 3203048B1 EP 17153043 A EP17153043 A EP 17153043A EP 3203048 B1 EP3203048 B1 EP 3203048B1
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European Patent Office
Prior art keywords
fastening
fastening bolt
cylinder head
exhaust manifold
longitudinal axis
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EP17153043.9A
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German (de)
English (en)
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EP3203048A1 (fr
Inventor
Ralf Mohr
Arnulf Spieth
Jürgen Häberle
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Eberspaecher Exhaust Technology GmbH and Co KG
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Eberspaecher Exhaust Technology GmbH and Co KG
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Priority claimed from DE102016102844.4A external-priority patent/DE102016102844A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1838—Construction facilitating manufacture, assembly, or disassembly characterised by the type of connection between parts of exhaust or silencing apparatus, e.g. between housing and tubes, between tubes and baffles
    • F01N13/1844—Mechanical joints
    • F01N13/1855—Mechanical joints the connection being realised by using bolts, screws, rivets or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N2340/00—Dimensional characteristics of the exhaust system, e.g. length, diameter or volume of the exhaust apparatus; Spatial arrangements of exhaust apparatuses

Definitions

  • the present invention relates to a fastening arrangement for fixing an exhaust manifold to a cylinder head of an internal combustion engine.
  • an exhaust manifold of an elongated cylinder along the row of cylinders and thus the exhaust gases exiting therefrom is generally located on an exhaust side of the cylinder head also referred to as exhaust manifold defined.
  • the exhaust manifold has a substantially planar bearing surface, which is supported with the intermediate storage of a sealing element with respect to a likewise substantially planar bearing surface of the cylinder head.
  • the exhaust manifold has on its longitudinal sides respective fastening edge regions.
  • the exhaust manifold like the cylinder head, is subject to high thermal and mechanical stress. Due to the thermally induced expansions or contractions occurring at the beginning of an internal combustion operation and after the end of a combustion operation, forces repeatedly occur in the region of the attachment of the exhaust manifold to the cylinder head, which also heavily load the fastening bolt units used to fix the exhaust manifold on the cylinder head and, as well supported by the vibrations occurring in the combustion operation, can lead to the loosening of fastening bolt units and a deviating from a desired mounting position of the exhaust manifold with respect to the cylinder head installation position.
  • FIG DE 10 2010 025 657 A1 A mounting arrangement for fixing an exhaust manifold to a cylinder head of an internal combustion engine according to the preamble of claim 1 is shown in FIG DE 10 2010 025 657 A1 known.
  • a Befest Trentselementabstütz a mounting flange of the exhaust manifold and provided for abutment against a contact surface of a cylinder head bearing surface of the mounting flange portion is formed a wedge angle in the range of 15 ° to 30 ° to produce a force acting parallel to the contact surface of the cylinder head force, which is another mounting flange of the Exhaust manifold to press against this supporting and acting as an abutment fastener.
  • a first mounting bolt longitudinal axis of the at least one first mounting bolt unit is inclined with a first longitudinal axis angle with respect to the second contact surface from the cylinder head towards a free end of the first mounting flange portion.
  • the first wedge angle in the aforementioned range, it is ensured that the forces oriented essentially parallel to the mutually prestressed support surfaces of the exhaust manifold on the one hand and of the cylinder head on the other hand, due to the wedge-like configuration of the first mounting flange region, result in a transverse load or transverse displacement the exhaust manifold with respect to the cylinder head could occur only in a friction cone not significantly exceeding extent.
  • This limitation of the displacement forces acting on the exhaust manifold ensures that undesired displacement of the exhaust manifold or unwanted loosening of the fastening bolt units will not occur even if the thermal and mechanical loads repeatedly occur.
  • the following applies for the first wedge angle and the static friction coefficient: 0 ⁇ W 1 ⁇ 2 tan - 1 ⁇ . preferably W 1 tan - 1 ⁇ ,
  • the first fastening element to a first fastening bolt longitudinal axis of the at least one first fastening bolt unit substantially orthogonal first Befest Trentsbolzenöabstschreib description for supporting the at least one first fastening bolt unit with respect to the first Has fastening element.
  • the first fastening bolt longitudinal axis of the at least one first fastening bolt unit preferably lies in a plane substantially orthogonal to the second contact surface, which ultimately means that this first fastening bolt longitudinal axis essentially only outwards, ie in the direction away from the exhaust manifold and in the direction of the free end of the first Mounting flange portion is inclined to, but not in the direction of the longitudinal extent of the exhaust manifold, in which it extends along the row of cylinders in a cylinder block, is inclined.
  • a fastening bolt of the at least one first fastening bolt unit be Mounting bolt through opening in the first fastener substantially transversely to the first mounting bolt longitudinal axis passes through without play.
  • the exhaust manifold in a second fastening edge region have a second fastening flange region oriented substantially opposite the first fastening flange region and having a second inclined with respect to the first contact surface with a second wedge angle Fastening element support surface, wherein a second fastening element by means of at least one with respect to the cylinder head is supported or supportable second fastening bolt unit pressed against the cylinder head or pressable and identifies a relative to the second bearing surface with the second wedge angle inclined second Befest
  • the second fastening element can be fixed to the cylinder head prior to attachment of the exhaust manifold so that the exhaust manifold with its likewise wedge-like second fastening flange region is pushed under the second fastening element can be and subsequently carried out at the first attachment edge portion a determination by means of the first fastener.
  • a second fastening bolt longitudinal axis of the at least one second fastening bolt unit is arranged with respect to the second contact surface with a second longitudinal axis angle, wherein the second longitudinal axis angle is in the range of 90 °.
  • the second wedge angle is preferably greater than the first wedge angle
  • the second fastening element may comprise a second fastening bolt unit supporting surface substantially orthogonal to the second fastening bolt longitudinal axis of the at least one second fastening bolt unit for supporting the at least one second fastening bolt unit with respect to the second fastening element.
  • the exhaust manifold may be made of steel, preferably ST52.
  • the first fastening element which comes into frictional interaction with the exhaust manifold can also be made of steel, preferably also ST52.
  • the coefficient of static friction acting between the exhaust manifold and the cylinder head is, for example, in the range from 0.10 to 0.14, preferably in the range from 0.11 to 0.13, in particular when steel material is used to build up these assemblies.
  • the invention further relates to an internal combustion engine, in particular for a vehicle, comprising a cylinder head fixed to a cylinder block and an exhaust manifold fixed to the cylinder head by means of a fastening arrangement according to the invention.
  • the Fig. 1 and 2 show in simplified representation a generally designated 10 mounting arrangement, by means of which an exhaust manifold 12 can be fixed to a cylinder head 14 of an internal combustion engine. It shows the Fig. 1 the determination of the exhaust manifold 12 on the cylinder head 14 in a first fastening edge region 16 of the exhaust manifold 12, while the Fig. 2 the determination of the exhaust manifold 12 on the cylinder head 14 in a second fastening edge region 18 of the exhaust manifold 12 shows.
  • the exhaust manifold 12 is basically orthogonal to the planes of the drawing Fig. 1 and 2 may be elongate and extend with its longitudinal direction along the cylinder provided in a cylinder block.
  • the exhaust manifold 12 has a planar first contact surface 20, which faces a second abutment surface 22 of the cylinder head 14. As described below, the exhaust manifold 12 is urged toward the second abutment surface 22, wherein between the first abutment surface 20 and the second abutment surface 22 to obtain a gas-tight termination, a sealing element, not shown in the figures, is positioned.
  • the outlet manifold 12 has a wedge-like first fastening flange region 24. This is limited in the direction of the cylinder head 14 through the first contact surface 20 and is limited in the direction away from the cylinder head 14 by a Befest Nathans institutenabstütz Structure 26. Between the first contact surface 20 and the first Befestauers institutenabstschreibamide 26, a first wedge angle W 1 is formed, so that the first mounting flange portion 24 is tapered toward a free end 28 thereof.
  • first fastening bolt units 30 For fixing the exhaust manifold 12 in its first fastening edge region 16 on the cylinder head 14, it is preferable to have a plurality of in the longitudinal extension direction of the exhaust manifold 12, that is to say orthogonal to the plane of the drawing Fig. 1 successive first fastening bolt units 30 are provided.
  • Each of these first fastening bolt units 30 comprises a fastening bolt 32, also generally referred to as stud bolt, which is inserted into an associated opening 34 in the cylinder head 14, preferably screwed.
  • the fastening bolt 32 is therefore preferably designed as an external thread bolt, and the receiving opening 34 in the cylinder head 14 is designed as an internal thread opening.
  • a fastening bolt through opening 36 which is open towards the free end 28 of the same is formed.
  • the fastening bolt 32 extends outward from the cylinder head 14 with its first fastening bolt longitudinal axis A 1 at a first longitudinal axis angle L 1 with respect to the second contact surface 22, ie in the direction away from the exhaust manifold 12 or in the direction of the free end 28 of FIG first mounting flange portion 24 to inclined.
  • the first fastening bolt longitudinal axis A 1 preferably lies in a position orthogonal to the second contact surface 22, and thus substantially also the plane of the drawing Fig. 1 appropriate level.
  • the fastening bolt 32 thus has no inclination angle component in the direction of the longitudinal extent of the exhaust manifold 12.
  • the fastener assembly 10 also includes a first fastener 38 associated with the first fastener flange portion 24.
  • the first fastener 38 preferably extends across the entire first fastener rim portion 16 in the direction of the longitudinal extent of the exhaust manifold 12 and thus acts with those therein Longitudinal direction of the exhaust manifold 12 successive first fastening bolt units 30 together.
  • the first attachment element 38 has a first attachment flange support surface 40, with which this rests against the first attachment element support surface 26 of the first attachment flange region 24.
  • the first fastening element 38 has a fastening bolt through-opening 42, in which a respective fastening bolt 32 is received transversely to its first fastening bolt longitudinal axis A 1 substantially without play.
  • the first fastening element 38 has a fastening bolt unit support surface 44.
  • a fastening nut 46 standing or engageable in threaded engagement with the fastening bolt 32 can be supported either directly or via an insert disk element.
  • the exhaust manifold 12 has a substantially wedge-like second mounting flange 48.
  • the second mounting flange 48 has a at a second wedge angle W 2 with respect to the first contact surface 20 and thus also the second contact surface 22 inclined second Befest Trents institutenabstütz construction 50 on.
  • the second mounting flange portion 48 is tapered toward its free end 52 and is thus oriented substantially opposite to the first mounting flange portion 24.
  • the mounting assembly 10 Associated with the second mounting flange portion 48, the mounting assembly 10 includes a second fastener 54. This is defined by a plurality of in the direction of the longitudinal extent of the exhaust manifold 12 successive second mounting bolt units 56 on the cylinder head 14. Each second mounting bolt unit 56 includes a mounting bolt 58 which is inserted into an associated opening of the cylinder head 14, preferably held therein by threaded engagement.
  • the fastening bolts 58 of the second fastening bolt units 56 are thus preferably designed as external thread bolts, while the openings receiving these are formed in the cylinder head 14 as internal threaded openings. It can be seen in Fig.
  • fastening bolts 58 with their second fastening bolt longitudinal axes A 2 are arranged with respect to the second contact surface 22 with a second longitudinal axis angle L 2 of 90 °.
  • the fastening bolts 58 thus extend substantially orthogonally with respect to the second contact surface 22 and also have no inclination angle components in the direction of the longitudinal direction of the exhaust manifold 12.
  • the fastening element 54 On a side remote from the second contact surface 22 of the cylinder head 14 side, the fastening element 54 has a second Befest Trentsbolzenöabstütz derivative 60, the respective second mounting bolt longitudinal axis A 2 of the mounting bolt 58 in Substantially orthogonal and at which a threaded engagement with the fastening bolt 58 of a respective second fastening bolt unit 56 standing or bringable fastening nut 62 either directly or with intermediate storage of a Shim is supported or supportable.
  • the fastening nuts 62 of the second fastening bolt units 56 the second fastening element 54 is pressed with a Zylinderkopfabstütz construction 64 against the second bearing surface 22 of the cylinder head 14.
  • the second fastening element 54 is thus held in a defined position relative to the cylinder head 14 by means of the second fastening bolt units 56.
  • the fastening bolt through openings for the fastening bolts 58 of the second fastening bolt units 56 formed in the second fastening element 54 have a dimensioning such that the fastening bolts 58 are in turn received without movement play transversely to their second fastening bolt longitudinal axes A 2 , so that the second fastening element 54 is held substantially immovable not only in the direction orthogonal back to the receiving surface 22, but also in the direction parallel to the second bearing surface 22 in a defined position.
  • a second mounting flange support surface 66 is provided on the second fastener 54. This is inclined with respect to the second contact surface 22 and thus also the first contact surface 20 with the second wedge angle W 2 , with which also the second Befest Whileselementabstütz phenomenon 50 of the second mounting flange 48 is inclined with respect to these surfaces.
  • a wedge-like undercut is formed, in which the second mounting flange 48 can be positioned engaging.
  • the fastening bolts 58 of the second fastening bolt units 56 extend out of the cylinder head 14
  • open recesses may be formed in the second mounting flange region 48 towards the free end 52, into which the fastening bolts 58 are partially formed engage or through which the fastening bolts 58 may extend therethrough.
  • the exhaust manifold 12 and the two fastening elements 38, 54 are preferably made of steel material, for example ST52.
  • the cylinder head 14 is constructed, for example, of aluminum material.
  • the fastening bolt units 30, 56, in particular the fastening bolts 32, 58 of the same, are preferably also constructed of steel material, which also in the Abstützcic GREAT with the cylinder head 14 on the one hand and the fastener 38, 54 on the other hand, the required connection strength and load capacity of the fastening bolts 32, 58 also guaranteed transversely to their mounting bolt longitudinal axes A 1 , A 2 .
  • the sealing element is placed on the second contact surface 22, so that it lies substantially between the two rows of fastening bolts 32, 58 at the intended position for installation.
  • the exhaust manifold 12 is moved towards the cylinder head 14 such that the second mounting flange portion 18 engages with its second fastener support surface 50 below the second mounting flange support surface 66 of the second fastener 54.
  • the exhaust manifold 12 may be pivoted such that its first abutment surface 20 approximates the second abutment surface 22 and the seal member positioned thereon.
  • the first mounting flange portion 24 with the fastener bolt through holes 36 formed thereon moves over the mounting bolts 32 of the first mounting bolt units 30 until the exhaust manifold 12 is supported flatly with respect to the cylinder head 14, ie, the two abutment surfaces 20, 22 are substantially interposed therebetween are positioned parallel to each other.
  • the first fastener 38 is pushed with its Befest onlysbolzen micratsö réelleen 42 on the mounting bolts 32 of the first mounting bolt units 30 and thus the first fastener 38 with its first Befest onlysflanschabstütz phenomenon 40 on the first Befest onlys institutenabstschreib construction 26 fitting.
  • the fastening nuts 46 of the first fastening bolt units 30 By applying and tightening the fastening nuts 46 of the first fastening bolt units 30, the first fastening element 38 is pressed against the first fastening flange region 24. Due to the inclination of the fastening bolts 32 and due to the wedge-like configuration of the second mounting flange portion 24, forces can thereby arise, which the exhaust manifold 12 in the two representations of Fig. 1 and 2 each to the left, so in the direction of the cylinder head 14 fixed second fastener 24 to apply or move.
  • the first wedge angle W 1 is selected such that it fulfills the following condition: 0 ⁇ W 1 ⁇ 2 tan - 1 ⁇ ,
  • ⁇ is in the region of the abutting first Befest onlys institutenabstütz structure 26 and first Befest onlyschabstschreib Structure 40 occurring static friction coefficient, also called coefficient of friction.
  • This is essentially determined by the construction materials of the two abutting with these surfaces 26, 40 components Auslasskrümmer 12 and first fastener 38. As indicated above, these two components are preferably constructed of steel material, such as ST52, so that in this area Mutual investment will result in a static coefficient of friction in the range of 0.11 to 0.13.
  • the first wedge angle W 1 according to the principles of the present invention, it is not greater than twice the inverse tangent of this static friction coefficient.
  • this first wedge angle W 1 in the range of approximately 14.81 ° thus results for a static friction coefficient of, for example, 0.13.
  • this first wedge angle W 1 should not be greater than the simple inverse tangent of the coefficient of static friction, that is should not be greater than 7.41 °.
  • the various fastening bolt units, in particular the first fastening bolt units 30, due to a displacement of the first mounting flange portion 24 relative to the first fastening element 38 in the illustration of Fig. 1 be loosened to the left or a required tightening torque is not maintained even over a longer period of operation.
  • the wedge-like configuration in particular of the first attachment flange portion 24, enables the thermally induced expansions or contractions of the various components unavoidably occurring during operation of an internal combustion engine, without an undefined, excessive relative movement between the exhaust manifold 12 and the cylinder head 14 or a loosening of the fastening bolt units.
  • the first wedge angle W 1 essentially corresponds to the inverse tangent of the static friction coefficient ⁇ . In this case, therefore, the first wedge angle W 1 essentially corresponds to the friction angle or friction cone angle. Thus, it can be ensured that significant lateral forces, which lead to a displacement of the cylinder head 14, do not occur. If the first wedge angle W 1 is chosen so that it is slightly larger than the inverse tangent of the coefficient of static friction ⁇ , although limited transverse forces can occur, excessive loading of the cylinder head 14 in the transverse direction is avoided.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)

Claims (13)

  1. Arrangement de fixation pour fixer un tuyau d'échappement (12) à une tête de cylindre (14) d'un moteur à combustion interne, le tuyau d'échappement (12) ayant une première surface de contact (20) essentiellement plane pour un support en relation à une deuxième surface de contact (22) essentiellement plane de la tête de cylindre (14), où le tuyau d'échappement (12) comprend dans une première périphérie de fixation (16), une première région de bride de fixation (24) en cône avec une première surface de support de membre de fixation (26) inclinée par rapport à la première surface d'appui (20) par un premier angle d'attaque (W1); où un premier membre de fixation (38) est poussé ou peut être poussé contre la première surface de support de membre de fixation (26) avec une première surface de support de bride de fixation (40) au moyen d'au moins d'une unité de boulon de fixation (30) qui est supportée ou peut être supportée par rapport à la tête de cylindre (14) ;
    où un premier axe longitudinal de boulon de fixation (A1) de ladite au moins une unité de boulon de fixation (30) est incliné par un premier angle d'axe longitudinal (L1) par rapport à la deuxième surface d'appui (22) partant de la tête de cylindre (14) dans le sens d'une extrémité libre (28) de la première région de bride de fixation (24),
    caractérisé en ce que
    le premier angle d'attaque (W1) et un coefficient de friction statique (µ) de l'interaction de friction du premier membre de fixation (38) par rapport au tuyau d'échappement (12) est défini par 0 < W 1 ≤ 2 tan − 1 μ ,
    Figure imgb0014
     où
    W1 est le premier angle d'attaque, et
    µ est le coefficient de friction statique.
  2. Arrangement de fixation selon la revendication 1, caractérisé en ce que le premier angle d'attaque (W1) et le coefficient de friction statique (µ) sont définis par : 0 < W 1 ≤ tan − 1 μ ,
    Figure imgb0015
     de préférence W 1 = tan − 1 μ .
    Figure imgb0016
  3. Arrangement de fixation selon la revendication 1, caractérisé en ce que le premier angle d'attaque (W1) et le coefficient de friction statique (µ) sont définis par : tan − 1 μ < W 1 ≤ 2 tan − 1 − μ .
    Figure imgb0017
  4. Arrangement de fixation selon une des revendications 1-3, caractérisé en ce que le premier membre de fixation (38) comprend une première surface de support d'unité de boulon de fixation (44) qui est essentiellement orthogonal à un premier axe longitudinal de boulon de fixation (A1) de ladite au moins une unité de boulon de fixation (30) pour supporter ladite au moins une première unité de boulon de fixation (30) par rapport au premier membre de fixation (38).
  5. Arrangement de fixation selon une des revendications 1-4, caractérisé en ce que le premier axe longitudinal de boulon de fixation (A1) de ladite au moins une unité de boulon de fixation (30) est incliné par un premier angle d'axe longitudinal (L1) par rapport à la deuxième surface de contact (22) à partir de la tête de cylindre (14) dans le sens d'une extrémité libre (28) de la première région de bride de fixation (24) dans une gamme comprise entre 50º et 70º, de préférence d'environ 60º.
  6. Arrangement de fixation selon une des revendications 1-5, caractérisé en ce que le tuyau d'échappement (12) comprend dans une deuxième région de bord de fixation (18) une deuxième région de bride de fixation (48) orientée essentiellement dans un sens opposé à la première région de bride de fixation (24) avec une deuxième surface de support de membre de fixation (50) inclinée par rapport à la première surface de contact (20) par un deuxième angle d'attaque (W2), où un deuxième membre de fixation (54) est poussé ou peut être poussé contre la tête de cylindre (14) au moyen d'au moins une deuxième unité de boulon de fixation (56) qui est supporté ou peut être supporté par rapport à la tête de cylindre (14) et comprend une deuxième surface de support de bride de fixation (66) inclinée par rapport à la deuxième surface de contact (22) par le deuxième angle d'attaque (W2).
  7. Arrangement de fixation selon la revendication 6, caractérisé en ce qu'un deuxième axe longitudinal de boulon de fixation (A2) de ladite au moins une deuxième unité de boulon de fixation (56) est arrangé avec un deuxième angle d'axe longitudinal (L2) par rapport à la deuxième surface de contact (22), le deuxième angle d'axe longitudinal (L2) étant d'environ 90º.
  8. Arrangement de fixation selon la revendication 6 ou 7, caractérisé en ce que le deuxième angle d'attaque (W2) est plus grand que le premier angle d'attaque (W1).
  9. Arrangement de fixation selon une des revendications 6-8, caractérisé en ce que le deuxième membre de fixation (54) comprend une deuxième surface de support d'unité de boulon de fixation (60) s'étendant essentiellement à angle droit au deuxième axe longitudinal de boulon de fixation (A2) de ladite au moins une deuxième unité de boulon de fixation (56) pour supporter ladite au moins une deuxième unité de boulon de fixation (56) par rapport au deuxième membre de fixation (54).
  10. Arrangement de fixation selon une des revendications 1-9, caractérisé en ce que le tuyau d'échappement (12) est fait d'acier, de préférence de ST52, ou/et en ce que le premier membre de fixation (38) est fait d'acier, de préférence de ST52, ou/et en ce que le coefficient de friction statique (µ) est compris dans la gamme de 0,10 à 0,14, de préférence dans la gamme de 0,11 à 0,13.
  11. Arrangement de fixation selon une des revendications 1-10, caractérisé en ce qu'un premier axe longitudinal de boulon de fixation (A1) de ladite au moins une unité de boulon de fixation (30) est situé dans un plan qui est essentiellement perpendiculaire à la deuxième surface de contact (22).
  12. Arrangement de fixation selon une des revendications 1-11, caractérisé en ce que le boulon de fixation (32) de ladite au moins une unité de boulon de fixation (30) passe à travers d'une ouverture de passage de boulon de fixation (42) dans le premier membre de fixation (38) essentiellement sans jeu de mouvement transversalement au premier axe longitudinal de boulon de fixation (A1).
  13. Moteur à combustion interne, en particulier pour un véhicule, comprenant une tête de cylindre (14) fixé à un bloc-cylindre, et un tuyau d'échappement (12) fixé à la tête de cylindre (14) au moyen d'un arrangement de fixation (10) selon une des revendications précédentes.
EP17153043.9A 2016-02-04 2017-01-25 Système de fixation d'un tuyau coudé de sortie sur une culasse de cylindre d'un moteur à combustion interne Active EP3203048B1 (fr)

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DE102016101980 2016-02-04
DE102016102844.4A DE102016102844A1 (de) 2016-02-04 2016-02-18 Befestigungsanordnung zur Festlegung eines Auslasskrümmers an einem Zylinderkopf einer Brennkraftmaschine

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EP3203048B1 true EP3203048B1 (fr) 2019-01-23

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