WO2017202777A1 - Bielle pour moteur à combustion interne à taux de compression réglable - Google Patents

Bielle pour moteur à combustion interne à taux de compression réglable Download PDF

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Publication number
WO2017202777A1
WO2017202777A1 PCT/EP2017/062284 EP2017062284W WO2017202777A1 WO 2017202777 A1 WO2017202777 A1 WO 2017202777A1 EP 2017062284 W EP2017062284 W EP 2017062284W WO 2017202777 A1 WO2017202777 A1 WO 2017202777A1
Authority
WO
WIPO (PCT)
Prior art keywords
connecting rod
eccentrical element
internal combustion
combustion engine
crank pin
Prior art date
Application number
PCT/EP2017/062284
Other languages
English (en)
Inventor
Alexander Becker
Original Assignee
ThyssenKrupp Metalúrgica Campo Limpo Ltda.
Thyssenkrupp 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 ThyssenKrupp Metalúrgica Campo Limpo Ltda., Thyssenkrupp Ag filed Critical ThyssenKrupp Metalúrgica Campo Limpo Ltda.
Publication of WO2017202777A1 publication Critical patent/WO2017202777A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/041—Sliding-contact bearings self-adjusting with edge relief
    • 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
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods
    • 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
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other

Definitions

  • prior art documents DE 10 2012 020 999 A1 , DE 10 2013 014 090 A1 and DE 10 2005 055 199 A1 disclose internal combustion engines with a cylinder piston and a crank shaft coupled with each other by means of a connecting rod having an adjustable effective length e.g. in order to increase fuel efficiency of the internal combustion engines under varying loads.
  • the connecting rod comprises a crank pin bearing eye for connecting the connecting rod to the crank shaft on the one hand and a connecting rod bearing eye for connecting the connecting rod to a cylinder piston on the other hand.
  • the connecting rod comprises an eccentrical element adjustment device for adjusting the effective length of the connecting rod.
  • the eccentrical element adjustment device comprises an eccentrical element including a bore hole for receiving a piston pin, an eccentrical element lever non-rotatably connected to the eccentrical element and two eccentrical element rods engaging the eccentrical element lever.
  • the eccentrical element rods are operatively connected to hydraulic cavities in the body of the connecting rod in order to generate a force onto the eccentrical element rods generated by hydraulic pressure.
  • the eccentrical element lever is thereby actuated by the eccentrical element rods.
  • the hydraulic cavities are loadable with hydraulic oil through hydraulic oil conduits from the crank pin bearing eye.
  • the crank pin bearing eye and the crank shaft pin both have a cylindrical shape.
  • the axial flow leads to a reduction of oil pressure in the hydraulic cavities of the connecting rod. Thereby, the fuel efficiency of the internal combustion engine is restricted.
  • a connecting rod for an internal combustion engine with an adjustable compression ratio comprising a crank pin bearing eye for connecting the connecting rod to a crank shaft of the internal combustion engine, a connecting rod bearing eye for connecting said connecting rod to a cylinder piston of said internal combustion engine and an eccentrical element adjustment device for adjusting the distance between said crank pin bearing eye and said connecting rod bearing eye
  • said eccentrical element adjustment device comprises an eccentrical element including said connecting rod bearing eye, an eccentrical element lever and eccentrical element rods engaging the eccentrical element lever, wherein said eccentrical element rods are actuated with a force generated by hydraulic pressure in hydraulic cavities
  • the crank pin bearing eye comprises a first bearing surface designed to contact a second load bearing surface of said crank shaft in a load-bearing area that bears the forces acting between the crank pin bearing eye and the crank shaft when the internal combustion engine is operated, wherein the first bearing surface of the crank pin bearing eye has a convex profile.
  • an internal combustion engine with an adjustable compression ratio comprising a crank shaft and at least one connecting rod comprising a crank pin bearing eye for connecting the connecting rod to the crank shaft, a connecting rod bearing eye for connecting said connecting rod to a cylinder piston of said internal combustion engine and an eccentrical element adjustment device for adjusting an effective connecting rod length
  • said eccentrical element adjustment device comprises an eccentrical element including a bore hole for receiving a piston pin, an eccentrical element lever and eccentrical element rods engaging the eccentrical element lever, wherein said eccentrical element rods are actuated with a force generated by hydraulic pressure in hydraulic cavities, wherein a first bearing surface of the crank pin bearing eye and a second bearing surface of the crank shaft and are in close contact to one another in a load-bearing area that bears the forces acting between the crank pin bearing eye and the crank shaft when the internal combustion engine is operated, wherein the second bearing surface of the crank shaft in its load-bearing area features a concavely curved profile in the longitudinal shaft section and that the bearing
  • crank pin bearing eye During operation of the internal combustion machine the crank pin bearing eye and the crank pin of the crank shaft are subject to tensile forces and compression forces that elastically deform the crank pin bearing eye as well as the crank pin. Alternately, small gaps are opening and closing between the bearing surfaces of the crank pin bearing eye and the crank pin which result in a sucking effect that pumps hydraulic oil inside the gap between the respective bearing surfaces.
  • the convex profile of the crank pin bearing eye and the concave profile of the crank pin of the crank shaft create an oil pocket at the bearing surface.
  • the present invention it is thereby advantageously possible to reduce outflow of hydraulic oil from the crank pin bearing eye by changing the profile configuration, i.e. convergence and / or divergence levels between connecting rod and crankshaft surfaces.
  • the curved profiles of the bearing surfaces allow an effective lubrication of the bearing surfaces because operating displacements and / or elastic deformations of the crank drive result in an oil pump effect between the cooperating convex and concave bearing surfaces.
  • the concave curvature of the second bearing surface of the crank shaft is also advantageous for oil lubrication between the second bearing surface of the crankshaft and the adjoining first bearing surface of the crank pin bearing eye.
  • crankshaft When the crank drive is operated the crankshaft works under tensile and compression strength due to the inertia and gas load effects. Under tensile and compression forces the crank pin and the crank pin bearing eye mounted thereon are deformed elastically such that small gaps of a few micrometers are opened and closed in the load-bearing area.
  • the throw of the connecting rod When the throw of the connecting rod is under tensile load oil that drips from the piston after the jet oil flow has cooled and lubricated the piston pin region is captured in a first region of the crank pin which is facing towards the small end of the connecting rod.
  • a second region of the crank pin located opposite of the first region and therefore facing away from the small end of the connecting rod works as a guiding for the connecting rod and also to pump the captured oil to the center of the crank pin.
  • the first region works as a guide for the connecting rod and also to pump oil to the center of the crank pin.
  • the first bearing surface of the crank pin bearing eye may have a convex profile in the longitudinal crank shaft section.
  • the convex profile of the first bearing surface may be a curve arranged in a plane, wherein the plane includes the longitudinal axis of the connecting rod and the plane is perpendicular to an opening area of the crank pin bearing eye.
  • the clearance between the first bearing surface of the crank pin bearing eye and the second bearing surface of the crank shaft varies in a direction parallel to a longitudinal crank shaft axis.
  • the curvature of the first bearing surface of the crank pin bearing eye and the curvature of the second bearing surface of the crank shaft do not match.
  • the bearing surfaces are either converging or diverging in longitudinal shaft section thereby adjusting axial oil outflow.
  • a hydraulic oil conduit extends from one of said hydraulic cavities to an aperture in the first bearing surface of the crank pin bearing eye. Oil may be supplied to the hydraulic oil conduit from the crank pin bearing eye through the aperture. Thus the oil pocket created at the bearing surfaces may supply a hydraulic cavity with oil via the hydraulic oil conduit.
  • the aperture is arranged close to, in particular on, a vertex of the convex profile of the first bearing surface.
  • the oil pocket created at the first bearing surface has its maximum close to, in particular at, the vertex of the convex profile.
  • the first bearing surface features a curved profile that is symmetrical to the longitudinal axis of the connecting rod extending between the center of the crank pin bearing eye and the center of the connecting rod bearing eye.
  • Figure 2 illustrates schematically part of a crank shaft and part of a connecting rod for an internal combustion engine with an adjustable compression ratio according to another exemplary embodiment of the present invention in a sectional view onto a plane including the crank shaft axis.
  • Figure 3 illustrates schematically part of a crank shaft and part of a connecting rod for an internal combustion engine with an adjustable compression ratio according to yet another exemplary embodiment of the present invention in a sectional view onto a plane including the crank shaft axis.
  • FIG 1 an exemplary connecting rod for an internal combustion engine having an adjustable compression ratio is shown.
  • the connecting rod 1 is provided for connecting a crank shaft (not shown) of the internal combustion engine with a cylinder piston (not shown) of the internal combustion engine.
  • the connecting rod 1 comprises a crank pin bearing eye 2 for connecting the connecting rod 1 to the crank shaft and a connecting rod bearing eye 3 for connecting the connecting rod 1 to the cylinder piston.
  • the connecting rod 1 has a shank portion 14 and a cap portion 15 which are connected by connection elements 16, e.g. screws.
  • the internal combustion engine has an adjustment mechanism to adjust the compression ratio inside the cylinder. This is achieved by adjusting the effective length l eff of the connecting rod 1 .
  • the connecting rod 1 comprises an eccentrical element adjustment device 4 for adjusting the distance l eff between the center of the crank pin bearing eye 2 and the center of a bore hole 7 of the eccentrical element 5 which is suited for receiving a piston rod.
  • the eccentrical element adjustment device 4 comprises the eccentrical element 5 with the bore hole 7.
  • the eccentrical element 5 is non-rotatably connected to an eccentrical element lever 6.
  • the eccentrical element lever 6 comprises a through bore in which the eccentrical element 5 is mounted.
  • the bore hole 7 is located outside the rotational center of the eccentri- cal element 5, so that rotating the eccentrical element 5 varies the distance between the center of the bore hole 7 and the center of the crank pin bearing eye 2.
  • the eccentrical element lever 6 is torque-proof and non-rotatably connected to the eccentrical element 5, so that a rotation the eccentrical element 5 can be initiated by rotating the eccentrical element lever 6.
  • the eccentrical element lever 6 comprises two fixation points provided on opposite sides of the eccentrical element lever 6.
  • each fixation point one end of an eccentrical element rod 8 is mounted by means of a bolt.
  • the other end of the eccentrical element rod 8 is linked to a supporting piston that is operatively connected to a hydraulic cavity 9 provided in the body of the connecting rod 1 .
  • the hydraulic cavity 9 is filled with oil in order to generate a force onto the eccentrical element rods 8 generated by hydraulic pressure.
  • the function of the hydraulic system and the eccentrical element rods 8 rotating the eccentrical element lever 6 is explained e.g. in prior art document DE 10 2013 014 090 A1 .
  • the torque-proof and non-rotatably connection between the eccentrical element 5 and the eccentrical element lever 6 is realized by a form-fit connection:
  • the outer circumferential surface of the eccentrical element 5 is provided with a plurality of teeth extending outwardly from the eccentrical element 5 and engaging a corresponding teeth and groove structure at the inner border of the through bore 7 in the eccentrical element lever 6.
  • a welded connection between the eccentrical element 5 and the eccentrical element lever 6 may be applied.
  • crank shaft 20 and a connecting rod 1 of an internal combustion engine with an adjustable compression ratio is illustrated in a sectional view onto a plane including the crank shaft axis C.
  • the crank pin bearing eye 2 comprises a first bearing surface 10 designed to contact a second load bearing surface 21 of said crank shaft 20 in a load-bearing area that bears the forces acting between the crank pin bearing eye 2 and the crank shaft 20 when the internal combustion engine is operated, wherein the first bearing surface 10 of the crank pin bearing eye 2 has a convex profile.
  • the first bearing surface 10 of the crank pin bearing eye 2 and a second bearing surface 12 of the crank shaft 20 are in close contact to one another in a load- bearing area that bears the forces acting between the crank pin bearing eye 2 and the crank shaft 20 when the internal combustion engine is operated, wherein the second bearing surface 12 of the crank shaft 20 in its load-bearing area features a concavely curved profile in the longitudinal shaft section and that the bearing surface 10 of the crank pin bearing eye 2 features a convex profile being in close contact with the concave profile of the crank shaft 20.
  • a hydraulic oil conduit 1 1 extends from one of the hydraulic cavities (not shown) to an aperture 12 in the first bearing surface 10 of the crank pin bearing eye 2.
  • the hydraulic oil conduit 1 1 is arranged in a shank portion 14 of the connecting rod 1.
  • the aperture 12 is arranged close to, in particular on, a vertex V of the convex profile of the first bearing surface 10.
  • the convex profile of the first bearing surface is a curved profile that is symmetrical to the longitudinal axis L of the connecting rod 1 extending between the center of the crank pin bearing eye 2 and the center of the connecting rod bearing eye 3.
  • the convex curvature of the first bearing surface 10 is also advantageous for oil lubrication between the first bearing surface 10 of the connecting rod 1 and the second bearing surface 21 of the crank shaft 20.
  • the crank shaft 20 works under tensile and compression forces due to the inertia and gas load effects. Under the tensile and compression forces the crank pins of the crank shaft 20 and the crank pin bearing eye 2 mounted thereon are deformed elastically such that small gaps of few micrometers are opened and closed in the edge region of the convex profile of the crank pin bearing eye 2. Those gaps restrict axial oil flow and lead the oil in the direction of the vertex V of the convex profile, thus, towards the aperture 12 of the hydraulic oil conduit 1 1 . Thus an oil pump effect is achieved which increases the oil flow into the hydraulic cavities 9.
  • crank shaft 20 and another embodiment of a connecting rod 1 of an internal combustion engine with an adjustable compression ratio is illustrated in a sectional view onto a plane including the crank shaft axis C.
  • a hydraulic oil conduit 1 1 is arranged in a cap portion 15 of the connecting rod 1 .
  • the oil conduit 1 1 connects to an oil cavity (not shown).
  • the cap portion 15 is connected to the shank portion 14 of the connecting rod 1 by screws 16.
  • the hydraulic oil conduit 1 1 ends in an aperture 12 in the first bearing surface 10 of the crank pin bearing eye 2.
  • the aperture 12 is arranged in the cap portion 14 of the connecting rod 1.
  • the aperture 12 is arranged close to, in particular on, a vertex V of the convex profile of the first bearing surface 10.
  • the convex profile of the first bearing surface is a curved profile that is symmetrical to the longitudinal axis L of the connecting rod 1 extending between the center of the crank pin bearing eye 2 and the center of the connecting rod bearing eye 3. Similar to the embodiment depicted in figure 2, an oil pump effect is achieved that increases the oil flow into the hydraulic cavities 9 via the conduit 1 1 .
  • the connecting rod 1 features oil conduits 1 1 in both the shank portion 14 and the cap portion 15. Apertures at the crank pin bearing eye 2 may be arranged both in the shank portion 14 and the cap portion 15.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

La présente invention concerne une bielle pour un moteur à combustion interne à taux de compression réglable comprenant un œillet de palier de maneton pour raccorder la bielle à un vilebrequin du moteur à combustion interne, un œillet de support de bielle pour raccorder ladite bielle à un piston de cylindre dudit moteur à combustion interne et un dispositif de réglage d'élément excentrique pour régler une longueur de bielle effective, ledit dispositif de réglage d'élément excentrique comprenant un élément excentrique comportant un trou de forage destiné à recevoir un axe de piston, un levier à éléments excentriques et des tiges à éléments excentriques mettant en prise le levier à éléments excentriques, lesdites tiges à éléments excentriques étant actionnées par une force générée par la pression hydraulique dans les cavités hydrauliques, l'œillet de palier de maneton comportant une première surface d'appui destinée à venir en contact avec une seconde surface d'appui dudit arbre de manivelle dans une zone porteuse qui porte les forces agissant entre l'œillet de palier de maneton et l'arbre de manivelle lorsque le moteur à combustion interne est actionné, la première surface d'appui de l'œillet de palier de maneton présentant un profil convexe.
PCT/EP2017/062284 2016-05-25 2017-05-22 Bielle pour moteur à combustion interne à taux de compression réglable WO2017202777A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16171431 2016-05-25
EP16171431.6 2016-05-25

Publications (1)

Publication Number Publication Date
WO2017202777A1 true WO2017202777A1 (fr) 2017-11-30

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PCT/EP2017/062284 WO2017202777A1 (fr) 2016-05-25 2017-05-22 Bielle pour moteur à combustion interne à taux de compression réglable

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WO (1) WO2017202777A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110067646A (zh) * 2018-01-23 2019-07-30 伊希欧1控股有限公司 用于可变压缩内燃机的连杆
EP3521644A1 (fr) * 2018-01-31 2019-08-07 ThyssenKrupp Metalúrgica Campo Limpo Ltda. Vilebrequin avec manetons courbés concaves

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1931231A (en) * 1930-07-01 1933-10-17 Robert B Luker Self-adjusting angular crank shaft and bearing
JPH02109009U (fr) * 1989-02-17 1990-08-30
EP1983200A2 (fr) * 2007-04-19 2008-10-22 ThyssenKrupp Metalúrgica Campo Limpo Ltda. Entrainement par manivelle
DE102012020999A1 (de) * 2012-07-30 2014-01-30 Fev Gmbh Hydraulischer Freilauf für variable Triebwerksteile
DE102013206512A1 (de) * 2013-04-12 2014-10-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verbrennungsmotor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1931231A (en) * 1930-07-01 1933-10-17 Robert B Luker Self-adjusting angular crank shaft and bearing
JPH02109009U (fr) * 1989-02-17 1990-08-30
EP1983200A2 (fr) * 2007-04-19 2008-10-22 ThyssenKrupp Metalúrgica Campo Limpo Ltda. Entrainement par manivelle
DE102012020999A1 (de) * 2012-07-30 2014-01-30 Fev Gmbh Hydraulischer Freilauf für variable Triebwerksteile
DE102013206512A1 (de) * 2013-04-12 2014-10-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verbrennungsmotor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110067646A (zh) * 2018-01-23 2019-07-30 伊希欧1控股有限公司 用于可变压缩内燃机的连杆
EP3521644A1 (fr) * 2018-01-31 2019-08-07 ThyssenKrupp Metalúrgica Campo Limpo Ltda. Vilebrequin avec manetons courbés concaves

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