WO2005003541A1 - Composant de moteur, en particulier, culasse pour moteur a combustion interne - Google Patents

Composant de moteur, en particulier, culasse pour moteur a combustion interne Download PDF

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Publication number
WO2005003541A1
WO2005003541A1 PCT/EP2004/006881 EP2004006881W WO2005003541A1 WO 2005003541 A1 WO2005003541 A1 WO 2005003541A1 EP 2004006881 W EP2004006881 W EP 2004006881W WO 2005003541 A1 WO2005003541 A1 WO 2005003541A1
Authority
WO
WIPO (PCT)
Prior art keywords
support section
wall
transition
undercut
support
Prior art date
Application number
PCT/EP2004/006881
Other languages
German (de)
English (en)
Inventor
Alexander Berndt
Wolfgang Kizler
Frank Müller
Original Assignee
Daimlerchrysler Ag
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 Daimlerchrysler Ag filed Critical Daimlerchrysler Ag
Publication of WO2005003541A1 publication Critical patent/WO2005003541A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/26—Cylinder heads having cooling means
    • F02F1/36—Cylinder heads having cooling means for liquid cooling
    • F02F1/38—Cylinder heads having cooling means for liquid cooling the cylinder heads being of overhead valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/248—Methods for avoiding thermal stress-induced cracks in the zone between valve seat openings

Definitions

  • Machine component in particular cylinder head for an internal combustion engine
  • the invention relates to a machine component, in particular a cylinder head for an internal combustion engine, with two support sections arranged at an angle to one another and abutting one another, wherein in operation in a first of the support sections essentially compressive forces directed towards the transition area and in the second, other support section essentially Forces directed away from the transition area act.
  • a cylinder head for an internal combustion engine is known from European patent application EP 1 028 247 A2, in which stiffening ribs are provided within the cylinder head in order to increase the load-bearing capacity.
  • the invention is intended to provide a machine component, in particular a cylinder head for an internal combustion engine, the load capacity of which is improved compared to conventional machine components.
  • a machine component in particular a cylinder head for an internal combustion engine, is provided with two support sections arranged at an angle to one another and abutting one another, wherein in operation in a first of the support sections pressure forces directed essentially towards the transition area and in the second, other support section in forces acting away from the transition area act, in which the transition area forms an undercut of the first support section, which extends over an imaginary extension of an outer wall of the first support section extends into the transition area.
  • the inventive design of the transition area makes it possible to superimpose and at least partially compensate for the differently directed forces in the two support components in the critical transition area.
  • tensile and compressive stresses are superimposed, for example, and the material stress is reduced to an acceptable level for the selected material.
  • a deepest point of the undercut lies within the imaginary extension of the outer wall of the first support section.
  • Such a configuration enables a particularly effective compensation of tensile and compressive stresses.
  • the transition area seen in a sectional plane, forms a parabolic or parabolic curve, and a change between the transition area and the first or second support section takes place outside of material areas that are heavily loaded during operation.
  • discontinuities or sudden changes in the curvature profile on the outer wall of the transition area can be avoided.
  • Such discontinuities in the course of the curvature usually caused by changes in geometry, for example the transition from a radius to a straight line, lead to effects similar to notch effects and thus to highly stressed material areas.
  • notch effect Similar effects can be avoided and the material load can be reduced to an acceptable level for the material.
  • a geometry change can then take place outside the highly stressed material areas, in which case even sharp-edged transitions or notches can be permitted since there is no fear of a locally high material load.
  • the transition region forms a • transition curve in a sectional plane, which has a continuous curvature or whose discontinuities in the curvature are minimized.
  • an outer wall of the transition area continues an outer wall of the first support section with small curvatures or large radii of curvature into the area of a base of the undercut
  • the outer wall of the transition area continues an outer wall of the second support section with small curvatures or large radii of curvature into the region of the base of the undercut and the outer wall of the transition region has large curvatures or small radii of curvature in the region of the base of the undercut.
  • Such a design makes it possible to guide and superimpose tensions from the first support section and tensions from the second support section into the area of the base of the undercut in order to partially compensate for the tensions on both sides.
  • the first support section has a transverse dimension b in a sectional plane and the undercut extends in the sectional plane by a distance a, which is between b / 16 to b / 3, over the imaginary extension of the outer wall of the first support section.
  • Such a configuration of the transition region is particularly advantageous for symmetrical support structures in which a first support section merges into second support sections on both sides, for example, or for rotationally symmetrical support structures, for example.
  • the first support section has a transverse dimension b in a sectional plane, a material reinforcement is provided opposite the undercut in the transition area and the undercut extends in the sectional plane by a distance a that is up to b / 2 over the imaginary one Extension of the outer wall of the first support section.
  • the undercut can extend significantly further into the first support section extend into it to achieve a particularly effective superimposition of oppositely directed forces or tensions.
  • the first support section and the transition area in the sectional plane form an S-like cross-sectional shape.
  • Such a configuration is advantageous, for example, in the edge region of a cylinder head, in that a material reinforcement can be provided on an outer wall and an intake or exhaust duct is only provided on one side of a screw pipe.
  • the first support section forms a pressure support of a cylinder head of an internal combustion engine, which in the assembled state is arranged in alignment with an engine block web, and the second support section forms a duct wall section of an intake or exhaust duct of the cylinder head that extends from the combustion chamber.
  • the design of transition areas according to the invention allows a consumption and emission-optimizing increase in the combustion chamber pressure without exceeding permissible material loads.
  • 1 is a schematic sectional view of a transition area between a pressure support and a channel wall in a cylinder head, two different embodiments being shown, 2 shows a schematic illustration of the voltage curve at a transition region in a cylinder head according to the prior art,
  • FIG. 3 shows a schematic representation of the material stresses on a cylinder head according to the invention
  • FIG. 6 shows a further embodiment of an inventive design of a transition area.
  • FIG. 1 shows on the right of a dash-dotted center line a first design according to the invention of a transition region between a pressure support 10 and a channel wall 12 of a cylinder head.
  • a first design according to the invention of a transition region between a pressure support 10 and a channel wall 12 of a cylinder head.
  • To the left of the dash-dotted center line is a further possibility of designing a transition area between the pressure support 10 and a further channel wall 14 according to the invention.
  • the pressure support 10 is arranged above an engine block web 16 and a cylinder head gasket 18 is arranged between the engine block web 16 and the cylinder head.
  • the engine block web 16, cylinder head gasket 18 and cylinder head are shown in an exploded view only for the sake of clarity.
  • the engine block web 16 separates a first combustion chamber 20 and a second combustion chamber 22 from one another. 1, combustion chambers 20, 22 are delimited by a combustion chamber plate 24 of the cylinder head. Openings for an inlet channel 26 and an outlet channel 28 are provided in the combustion chamber plate, each of which is defined by a valve seat ring 30. schematically an inlet valve 32 which either opens or closes the inlet channel is indicated.
  • the cylinder head is held against the gas force F G directed upward in the illustration in FIG. 1 by the downward screw prestressing force F s on the engine block web 16.
  • the screw prestressing force F s is indicated by means of two arrows 36.
  • a conventional design of the transition between the pressure support 10 and the channel wall 12 is indicated in dashed lines.
  • the design of the transition area according to the invention is shown in solid lines.
  • the undercut of the pressure support 10 according to the invention enables tensile stresses from the channel wall 12 to be guided into the region of a base 38 of the undercut, so that the tensile stresses are superimposed there with compressive stresses in the pressure support 10 and at least partially compensated for.
  • the base 38 of the undercut corresponding to the lowest point of the undercut, is arranged such that it lies downward within an imaginary extension of the pressure support 10.
  • Such an imaginary extension is indicated by a dashed line 40 on the left half of the illustration in FIG. 1.
  • the transition curve 42 indicated by dashed lines according to the prior art.
  • the rectilinear outer wall of the pressure support 10 merges into an edge radius, the base of the transition curve is again rectilinear and then merges into the channel wall by means of a further edge radius.
  • the transition region according to the invention defined by the transition curve 44 shown as a solid line
  • care is taken to ensure a constant curvature.
  • the transition curve is largely and in any case in the highly stressed material areas in the vicinity of the base 38 determined by a parabola that has a constant curvature.
  • care is taken to ensure that the course of the curvature is as constant as possible or gradual changes in the curvature.
  • a parabolic transition curve 46 is shown in the left half of FIG. 1, which forms the undercut of the pressure support 10. It can be seen that the parabolic shape has been retained until the transition into the straight outer wall of the pressure support 10. At the transition between the straight outer wall of the pressure support 10 and the transition curve, the outer wall of the pressure support 10 and the outer wall of the transition region meet at an angle. However, since this sharp-edged transition lies outside the highly stressed material area, no material stress is to be expected at this point that is above the level that can be tolerated by the material.
  • a transverse dimension b of the pressure support 10 is indicated.
  • the transition curve 44 extends in the region of the undercut of the pressure support 10 by a distance a beyond the imaginary extension of the pressure support 10.
  • the value a can be between b / 16 and b / 3.
  • These values for a are expedient in the case of a symmetrical design of the pressure support 10, for example for the symmetrical design of the center line shown in broken lines.
  • the height of the transition area h which is chosen to be so large that a transition between the transition curve 44 and the straight outer wall of the pressure support 10 is already outside the highly stressed material areas.
  • FIG. 2 shows the voltage curve at a conventionally designed transition between a pressure support 50 and a channel wall 52 of a cylinder head.
  • the stresses are plotted relative to the transition curve, so that tensile stresses are drawn on the side of the transition curve marked with a plus sign and compressive stresses are plotted on the side of the transition curve marked with a minus sign.
  • the material stresses caused by the screw prestressing force F s are indicated schematically by a dashed line 54.
  • the material stresses caused by a gas force F G in the combustion chamber are indicated schematically by a dotted line 56.
  • the dash-dotted lines line 58 represents the superposition of the curves 54 and 56, corresponding to a superimposed tension from the bolt preload F s and the gas force F G.
  • FIG. 3 shows, in an illustration comparable to FIG. 2, the voltage curve on a cylinder head designed according to the invention.
  • the pressure support 10 merges into the channel wall 12 by means of an undercut, the undercut extending over an imaginary extension of the outer wall of the pressure support 10.
  • material stresses are shown relative to the transition curve 64, by means of which the outer wall of the pressure support 10 merges into the outer wall of the channel wall 12.
  • a material tension caused by the screw prestressing force F s is indicated by a broken line 66.
  • a material tension caused by the gas force F G is indicated by a dotted line 68 and the superimposition of the curves 66 and 68 is indicated by a dash-dotted line 70.
  • the tensile stresses from the channel wall 12 are conducted through the design of the transition curve 64 according to the invention into the region of the base of the undercut.
  • the compressive stresses acting in the pressure support 10 also have their maximum approximately in the region of the base of the undercut, which lies clearly within the imaginary extension of the outer wall of the pressure support 10.
  • the resulting total tension, corresponding to the dash-dotted line 70 thereby shows a significantly reduced maximum compressive stress 72 compared to the illustration in FIG. 2, and a significantly reduced maximum tensile stress 74, because tensile and compressive stresses at least partially cancel each other out by the design of the transition region according to the invention.
  • the result is a reduced material load compared to the conventional design in FIG. 2.
  • FIG. 4 shows a further embodiment of an inventive design of a transition area between a pressure support 76 of a cylinder head and a channel wall 78.
  • the transition area is asymmetrical in the embodiment of FIG. 4 and opposite the undercut 80 is a material reinforcement on the pressure support 76 Material order provided.
  • the pressure support 76 thus has an approximately S-shaped appearance in the sectional view of FIG. 4. Due to the material reinforcement of the pressure support 76, the undercut 80 can be a distance a over the imaginary extension of the outer wall of the pressure support 76 in the asymmetrical design of a pressure support 76 extend into this, which is up to half the transverse dimension b of the pressure support 76.
  • the schematic sectional view of FIG. 5 shows a further design option for a transition between a pressure support 82 and a channel wall 84 of a cylinder head.
  • the pressure support 82 has a conical shape in the sectional view of FIG. 5 and tapers downward toward the undercut.
  • FIG. 6 Another possible design of a pressure support 86 and the transition to a channel wall 88 in a cylinder head is shown in the schematic sectional view in FIG. 6.
  • the pressure support 86 has a conical shape, which, in contrast to the embodiment in FIG. 5, widens downward.
  • the transverse dimension of the pressure support 86 is reduced again by an undercut 90 in the transition region, in order then - starting from the undercut 90 - to pass into the channel wall 88.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

L'invention concerne un composant de moteur, en particulier, un composant pour moteur à combustion interne, comprenant deux sections supports disposées adjacentes et inclinées entre elles ; lors du fonctionnement, des forces de pression s'exercent, dans une première section, de manière à être sensiblement dirigées vers la zone de transition et, dans l'autre section, de manière à être sensiblement dirigées en dehors de la zone de transition. Conformément à l'invention, la zone de transition forme une section arrière de la première section support, laquelle s'étend dans la zone de transition, via un prolongement imaginaire d'une paroi extérieure de la première section support. Le composant selon l'invention trouve son application, par exemple, dans une zone de transition comprise entre une tubulure de refoulement et les parois de conduits dans des culasses de moteurs.
PCT/EP2004/006881 2003-07-01 2004-06-25 Composant de moteur, en particulier, culasse pour moteur a combustion interne WO2005003541A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10329443.0 2003-07-01
DE2003129443 DE10329443B4 (de) 2003-07-01 2003-07-01 Zylinderkopf für eine Brennkraftmaschine

Publications (1)

Publication Number Publication Date
WO2005003541A1 true WO2005003541A1 (fr) 2005-01-13

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ID=33559771

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/006881 WO2005003541A1 (fr) 2003-07-01 2004-06-25 Composant de moteur, en particulier, culasse pour moteur a combustion interne

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DE (1) DE10329443B4 (fr)
WO (1) WO2005003541A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3326685C1 (de) * 1983-07-23 1984-03-01 Daimler-Benz Ag, 7000 Stuttgart Zylinderkopf für Brennkraftmaschinen
EP1028247A2 (fr) * 1999-02-09 2000-08-16 Toyota Jidosha Kabushiki Kaisha Culasse pour un moteur à combustion interne

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD200908B1 (de) * 1981-09-16 1987-09-16 Hans Standhardt Verspannungsverband von zylinderkopf, zylinderlaufbuchse und zylindergehaeuse fuer viertaktdieselmotoren
JP2870463B2 (ja) * 1996-01-19 1999-03-17 トヨタ自動車株式会社 多気筒内燃機関のシリンダヘッド構造
DE19713246C2 (de) * 1997-03-29 1999-01-21 Daimler Benz Ag Zylinderkopf einer Mehrzylinder-Brennkraftmaschine
AT2804U1 (de) * 1998-05-28 1999-04-26 Avl List Gmbh Zylinderbüchse für den zylinderblock einer brennkraftmaschine
DE19836441C1 (de) * 1998-08-12 1999-11-11 Daimler Chrysler Ag Zylinderkopf einer Mehrzylinder-Brennkraftmaschine
DE19854323A1 (de) * 1998-11-25 2000-05-31 Porsche Ag Brennraum für eine Brennkraftmaschine
DE10007151A1 (de) * 2000-02-17 2001-08-23 Bayerische Motoren Werke Ag Flüssigkeitsgekühlter Querstrom-Zylinderkopf für Brennkraftmaschinen mit in Reihe angeordneten Zylindern
AT4875U1 (de) * 2000-06-27 2001-12-27 Avl List Gmbh Zylinderbüchse für eine flüssigkeitsgekühlte brennkraftmaschine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3326685C1 (de) * 1983-07-23 1984-03-01 Daimler-Benz Ag, 7000 Stuttgart Zylinderkopf für Brennkraftmaschinen
EP1028247A2 (fr) * 1999-02-09 2000-08-16 Toyota Jidosha Kabushiki Kaisha Culasse pour un moteur à combustion interne

Also Published As

Publication number Publication date
DE10329443A1 (de) 2005-02-17
DE10329443B4 (de) 2012-04-26

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