WO2011018142A1 - Profil de trou pour un montage d'axe de piston - Google Patents

Profil de trou pour un montage d'axe de piston Download PDF

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Publication number
WO2011018142A1
WO2011018142A1 PCT/EP2010/004227 EP2010004227W WO2011018142A1 WO 2011018142 A1 WO2011018142 A1 WO 2011018142A1 EP 2010004227 W EP2010004227 W EP 2010004227W WO 2011018142 A1 WO2011018142 A1 WO 2011018142A1
Authority
WO
WIPO (PCT)
Prior art keywords
bore
piston pin
piston
bearing
axis
Prior art date
Application number
PCT/EP2010/004227
Other languages
German (de)
English (en)
Inventor
Volker Gniesmer
Original Assignee
Ks Kolbenschmidt 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
Application filed by Ks Kolbenschmidt Gmbh filed Critical Ks Kolbenschmidt Gmbh
Priority to EP10737766A priority Critical patent/EP2464900A1/fr
Publication of WO2011018142A1 publication Critical patent/WO2011018142A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/10—Connection to driving members
    • F16J1/14—Connection to driving members with connecting-rods, i.e. pivotal connections
    • F16J1/16—Connection to driving members with connecting-rods, i.e. pivotal connections with gudgeon-pin; Gudgeon-pins
    • 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
    • F02F3/00—Pistons 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof

Definitions

  • the invention relates to the mounting of a piston pin in a piston, via which a connecting rod is pivotally connected to the piston.
  • Each bore includes in at least a portion of a deviating from a cylindrical shape bore profile.
  • the connecting rod connects the piston with the crankshaft.
  • a piston pin is mounted on the outside, which is further guided by a connecting rod eye of the connecting rod, while the connecting rod with another large connecting rod eye encloses a crank pin of the crankshaft.
  • the hub bores and the bore in the connecting rod eye are subjected to tensile, compressive and bending stress both horizontally and in the vertical plane, in particular in the zenith and nadir.
  • the crank rocking plane is loaded by gas forces acting on the piston head, whereby changing, directed in the pressure side and the counter-pressure side different lateral forces on the piston and on the connecting rod.
  • a transfer of the gas forces takes place from the piston via the piston pin bosses on the piston pin and then into the connecting rod. This results in a periodic elastic deformation of the piston pin. Due to increased combustion pressures, the surface pressure increases in the area intended for receiving the piston pin Holes. Exceeding limit values causes consequential damage, such as material cracks or pin gap fractures, which lead to a limited service life or premature failure of the piston.
  • the greatest stress of the piston pin is established in the region of a Boio crown, a combustion chamber-side main load zone of the piston. It is known, due to the adjusting in the operating state tensile and compressive forces and the resulting deformations of the piston pin to make geometric changes to relieve the piston pin bearing and to do the holes in the piston pin bosses not exactly cylindrical.
  • a piston In order to avoid inadmissible deformation in the bores of the piston pin bosses due to mechanical and thermal loads, a piston is known from DE 44 31 990 A, in which the hub bores are designed as a form of holes.
  • an oval hub bore is proposed according to DE 16 50 206 A1, in which the large axis of the oval is transverse to the longitudinal axis of the piston. This should be achieved at the same time the improved seizure safety between the piston pin and the holes in the piston pin bosses.
  • the invention is based on the object to provide a load of the piston pin corresponding load and deformation-oriented bore profile for the hub bores of the piston and the connecting rod bore.
  • the holes in the piston pin bosses and / or the bore in the connecting rod in the circumferential direction is at least a double ovality superimposed to form a bore profile with an asymmetric fine geometry.
  • the asymmetrical fine geometry according to the invention which is designed as a mold bore, forms a bore profile which has areas in a bore entry and / or in a bore exit that are deviated between an X-axis and a Y-axis.
  • Another inventive design criterion provides that at least one of the X-axis and / or the Y-axis adjacent portion of the bore profile to the associated opposite portion in the bore inlet and / or in the hole outlet is designed differently.
  • the bore profile according to the invention comprises an inner cylindrically shaped or deviating from a cylindrical portion, which differs from the profiling of the bore entry and / or the bore exit.
  • the inventive measures advantageous for the piston pin specific bore profiling can be realized in the piston pin bosses and / or the connecting rod, which is adapted to any temperature-induced and load-dependent deformation of the piston and the piston pin.
  • a preferred design provides that the superposed ovality, in particular the bolt deformation is adjusted taking into account the lateral forces.
  • the asymmetric bore profile according to the invention offers the possibility to Achieving an advantageous higher component load capacity of the piston to optimize a distribution of forces in the direction of the pressure side (DS) and the counter-pressure side (GDS).
  • a preferred embodiment of the invention provides that at least one bore has an asymmetrical bore profile to which a multiple, i. more than double ovality is superimposed in the circumferential direction.
  • the ovality or the ovality of the bore profile are aligned in the respective bore of the piston hub and / or the connecting rod, in particular at an angle of 45 ° to the X and Y axis.
  • the asymmetry of the bore profile of at least one bore preferably in the direction of a pressure side (DS) of the piston in order to optimize a pressure distribution in the pressure-loaded zone targeted.
  • the asymmetric fine geometry in the direction of the pressure side (DS) and / or in the direction of the counterpressure side (GDS) can be arranged in the bores of the piston hubs and / or in the bore of the connecting rod eye.
  • the staggered ovalities of the asymmetrical bore profile between the pressure side (DS) and the counter-pressure side (GDS) are formed according to the invention geometrically deviating.
  • a preferred embodiment of the invention provides a stepped ovality, in which an outer region increases in several sections, each section adjoining the preceding section in a continuous manner.
  • the asymmetrical fine geometry according to the invention includes, at least in the bores of the piston hubs, a radial widening designed as an oblique trumpet shape in end zones of the bores.
  • This aligned in particular to the piston crown and / or crankshaft inner contour advantageously forms a uniformly radially expanded trumpet-shaped course, which is adapted to a deflection or elastic deformation of the piston pin in the operating state, the trumpet-shaped course both circumferentially and between the bore inlet and the bore outlet deviating can be executed.
  • the invention also includes trumpet-shaped flared end zones of the bore in the connecting rod eye.
  • the asymmetrical fine geometry including bore profile according to the invention is further designed so that a setting from a center of the bore to a bore inner wall dimension X1 of the X-axis coincides or differs from a dimension Y1 of the Y-axis.
  • the geometric design of the bore profile according to the invention also provides that the first as well as the second ovality is defined by a deviating from a cylindrical shape radial inner dimension and a radial outer dimension.
  • the inner dimensions and the outer dimensions of each ovality are according to the invention designed to coincide or deviate from each other.
  • the dimensions of the first ovality differ from the dimensions of the second ovality.
  • FIG. 1 shows a sectional view of a piston according to the invention
  • FIG. 2 shows a front view of a hub bore designed according to the invention
  • FIG. 3 shows the hub bore according to FIG. 2 in a sectional view 3-3
  • FIG. 4 shows the hub bore according to FIG. 2 in a sectional view 4-4.
  • FIG. 1 shows a piston 1 in connection with a connecting rod 2 in a sectional view.
  • a piston upper part 3 of the piston 1 comprises a piston head 4 with integrated combustion chamber trough 5 and forms on the outside a flank 6 adjoining the piston head 4, to which a piston ring field 7 adjoins.
  • a piston lower part forming a piston skirt 8 two diametrically opposed piston pin bosses 9 are arranged, in each of which a hub bore 10 is introduced.
  • the hub bores 10 are intended for receiving a piston pin 11, via which the piston 1 is pivotally connected to the connecting rod 2.
  • the piston pin 11 is further guided by a bore 12 of a connecting rod 13.
  • the piston 1 In the operating state of the internal combustion engine, the piston 1 is periodically acted upon by a gas force in the arrow direction, which is transmitted via the piston pin 11 to the connecting rod 2. This results in an elastic deformation or deflection of the piston pin 11.
  • the hub bores 10 and the bore 12 in the connecting rod 13 are profiled accordingly, especially in a bore inlet and a bore outlet locally expanded radially.
  • the hub bores 10 form a bore profile 14 for this purpose.
  • FIG. 2 shows the hub bore 10 shaped as a shaped bore on an enlarged scale, as a result of which the asymmetric fine geometry of the hub bore 10 is shown Hole profile 14 is illustrated, which is superimposed in the circumferential direction of a double ovality.
  • the bore profile 14 is designed circumferentially in several areas deviating from a cylindrical shape and includes largely by 90 ° staggered ovalities 15, 16 which at an angle ⁇ 1, ⁇ 2 in each case by 45 ° to an X-axis or Y- Axis are arranged.
  • the first ovality 15 oriented at an angle ⁇ 2 to the X axis includes a radial inner dimension OV1 deviating from a cylindrical shape and a radial outer dimension OV3.
  • the second ovality 16 oriented at an angle ⁇ i to the X axis includes a radial inner dimension OV2 deviating from a cylindrical contour and a radial outer dimension OV4.
  • the ovalities 15, 16 are arranged such that the radial inner dimensions OV1, OV2 of a pressure side (DS) and the radial dimensions OV3, OV4 of a counter-pressure side (GDS) of the piston 1 are assigned.
  • the asymmetric fine geometry of the bore profile 14 comprises different dimensions OV1 and OV3 of the ovality 15 and different dimensions OV2 and OV4 of the ovality 16.
  • the ovalities 15, 16 also differ in their design.
  • the bore profile 14 includes stepless, rounded transitions between the ovalities 15, 16 so that each section joins steplessly to the next section or degree of ovality.
  • the bore profile 14 also comprises an X-axis dimension X1, which adjusts itself between a bore inner wall 17 and a bore center 18 and which differs from the Y-axis distance measure Y1 offset by 90 °.
  • FIG. 3 shows the bore profile 14 of the hub bore 10 in a view according to the section line 3-3 of FIG. 2.
  • the hub bore 10 is radially widened both on a bore inlet 19 assigned to the piston skirt 8 and on the bore outlet 20 directed to the connecting rod eye 13, correspondingly an adjusting elastic deformation of the piston pin 11 in the operating state of the internal combustion engine.
  • the dimensions of all radial extensions A1, A2, B1, B2 are designed to differ from each other.
  • the widenings A1, B1 facing the pressure side (DS) exceed the opposite widenings A2, B2 associated with the counterpressure side (GDS).
  • the widenings A1, A2 of the bore exit 20 exceed the widenings B1, B2 of the bore entry 19.
  • all radial widenings A1, A2, B1, B2 each form a stepless rounded contour or transition to a largely centered setting cylindrical section 21 of the hub bore 10.
  • FIG. 4 shows the bore profile 14 of the hub bore 10 in a view according to a section line 4-4 according to FIG. 2.
  • the dimensions of all the radial extensions A1, A3; B1, B3 designed differently from each other.
  • the widenings A1, B1 aligned in the direction of the piston crown 4 exceed the opposite widenings A3, B3 assigned to the connecting rod 2.
  • the expansions A1, A3 facing the bore outlet 20 are designed to be larger than the widenings B1, B3 of the bore inlet 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

L'invention concerne un montage d'un axe (11) dans un piston (1) d'un moteur à combustion interne par l'intermédiaire duquel une bielle (2) est reliée de manière articulée au piston (1). À cet effet, une tige (8) de piston présente deux moyeux (9) d'axe de piston espacés l'un de l'autre ayant chacun un trou (10) destiné à recevoir l'axe (11) de piston qui est guidé en même temps à travers un trou (12) d'une tête (13) de bielle. Chaque trou (10, 12) présente au moins dans une zone partielle un profil de trou s'écartant de la forme cylindrique et ayant une géométrie fine asymétrique. Le profil de trou (14) forme en outre dans la direction périphérique au moins une ovalité (15, 16) superposée qui est profilée de manière divergente entre un axe X et un axe Y dans une entrée de trou (19) et/ou dans une sortie de trou (20). De même, le profil de trou (14) est conçu différemment dans au moins une section voisine de l'axe X et/ou de l'axe Y par rapport à une section opposée associée. De plus, le profil de trou (14) est profilé de manière divergente par rapport à l'entrée de trou (19) et/ou la sortie de trou (20) dans une zone partielle intérieure.
PCT/EP2010/004227 2009-08-11 2010-07-12 Profil de trou pour un montage d'axe de piston WO2011018142A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10737766A EP2464900A1 (fr) 2009-08-11 2010-07-12 Profil de trou pour un montage d'axe de piston

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009036784.5 2009-08-11
DE102009036784A DE102009036784A1 (de) 2009-08-11 2009-08-11 Bohrungsprofil für eine Kolbenbolzenlagerung

Publications (1)

Publication Number Publication Date
WO2011018142A1 true WO2011018142A1 (fr) 2011-02-17

Family

ID=42937060

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/004227 WO2011018142A1 (fr) 2009-08-11 2010-07-12 Profil de trou pour un montage d'axe de piston

Country Status (3)

Country Link
EP (1) EP2464900A1 (fr)
DE (1) DE102009036784A1 (fr)
WO (1) WO2011018142A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015018712A1 (fr) * 2013-08-07 2015-02-12 Federal-Mogul Nürnberg GmbH Piston pour moteur à combustion interne

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018218373A1 (de) 2018-10-26 2020-04-30 Federal-Mogul Nürnberg GmbH Kolben für Verbrennungsmotoren und Herstellungsverfahren dafür

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1300937A (fr) * 1961-06-30 1962-08-10 Axe élastique pour piston
DE1650206A1 (de) 1967-08-18 1970-08-20 Schmidt Gmbh Karl Kolbenbolzenlagerung
DE2152462A1 (de) * 1971-10-21 1973-04-26 Schmidt Gmbh Karl Kolben fuer verbrennungskraftmaschinen
DE3036062A1 (de) * 1980-09-25 1982-04-08 Karl Schmidt Gmbh, 7107 Neckarsulm Kolben fuer verbrennungskraftmaschinen
DE4431990A1 (de) 1993-08-18 1996-03-14 Mahle Gmbh Leichtmetallkolben für hochbelastete Verbrennungsmotoren
DE10222463A1 (de) 2002-05-22 2003-12-04 Mahle Gmbh Kolbenbolzenlager für Verbrennungsmotoren
DE102005041907A1 (de) * 2005-09-03 2007-03-08 Ks Kolbenschmidt Gmbh Verlaufende Bolzenbohrungsgeometrie für einen Kolben einer Brennkraftmaschine
US20070095200A1 (en) * 2005-10-31 2007-05-03 Schroeder Kenneth E Piston having asymmetrical pin bore slot placement
WO2008107041A1 (fr) * 2007-03-07 2008-09-12 Ks Kolbenschmidt Gmbh Géométrie d'un alésage d'une bielle d'un moteur à combustion interne

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4141279C5 (de) * 1991-12-14 2006-07-27 Mahle Gmbh Leichtmetallkolben für Verbrennungsmotoren mit speziell geformten Nabenbohrungen
DE4441450B4 (de) * 1994-11-22 2006-03-09 Ks Kolbenschmidt Gmbh Leichtmetallkolben für Brennkraftmaschinen
DE10029950A1 (de) * 2000-06-26 2002-01-03 Volkswagen Ag Pleuelstange
DE10231233A1 (de) * 2002-07-11 2004-02-05 Mahle Gmbh Kolben für einen Verbrennungsmotor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1300937A (fr) * 1961-06-30 1962-08-10 Axe élastique pour piston
DE1650206A1 (de) 1967-08-18 1970-08-20 Schmidt Gmbh Karl Kolbenbolzenlagerung
DE2152462A1 (de) * 1971-10-21 1973-04-26 Schmidt Gmbh Karl Kolben fuer verbrennungskraftmaschinen
DE3036062A1 (de) * 1980-09-25 1982-04-08 Karl Schmidt Gmbh, 7107 Neckarsulm Kolben fuer verbrennungskraftmaschinen
DE4431990A1 (de) 1993-08-18 1996-03-14 Mahle Gmbh Leichtmetallkolben für hochbelastete Verbrennungsmotoren
DE10222463A1 (de) 2002-05-22 2003-12-04 Mahle Gmbh Kolbenbolzenlager für Verbrennungsmotoren
DE102005041907A1 (de) * 2005-09-03 2007-03-08 Ks Kolbenschmidt Gmbh Verlaufende Bolzenbohrungsgeometrie für einen Kolben einer Brennkraftmaschine
US20070095200A1 (en) * 2005-10-31 2007-05-03 Schroeder Kenneth E Piston having asymmetrical pin bore slot placement
WO2008107041A1 (fr) * 2007-03-07 2008-09-12 Ks Kolbenschmidt Gmbh Géométrie d'un alésage d'une bielle d'un moteur à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2464900A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015018712A1 (fr) * 2013-08-07 2015-02-12 Federal-Mogul Nürnberg GmbH Piston pour moteur à combustion interne
US9945320B2 (en) 2013-08-07 2018-04-17 Federal-Mogul Nurnberg Gmbh Piston for an internal combustioin engine

Also Published As

Publication number Publication date
EP2464900A1 (fr) 2012-06-20
DE102009036784A1 (de) 2011-02-24

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