EP1007831A1 - Amortisseur de vibrations pour moteurs a combustion interne - Google Patents

Amortisseur de vibrations pour moteurs a combustion interne

Info

Publication number
EP1007831A1
EP1007831A1 EP98941079A EP98941079A EP1007831A1 EP 1007831 A1 EP1007831 A1 EP 1007831A1 EP 98941079 A EP98941079 A EP 98941079A EP 98941079 A EP98941079 A EP 98941079A EP 1007831 A1 EP1007831 A1 EP 1007831A1
Authority
EP
European Patent Office
Prior art keywords
crankshaft
connecting rod
rod
disposed
journal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP98941079A
Other languages
German (de)
English (en)
Other versions
EP1007831A4 (fr
Inventor
Julian Alex Decuir
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US09/140,398 external-priority patent/US6044818A/en
Application filed by Individual filed Critical Individual
Publication of EP1007831A1 publication Critical patent/EP1007831A1/fr
Publication of EP1007831A4 publication Critical patent/EP1007831A4/fr
Withdrawn legal-status Critical Current

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
    • F02B75/06—Engines with means for equalising torque
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • 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
    • F16C7/02—Constructions of connecting-rods with constant length
    • F16C7/023—Constructions of connecting-rods with constant length for piston engines, pumps or the like
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/124—Elastomeric springs
    • F16F15/126—Elastomeric springs consisting of at least one annular element surrounding the axis of rotation
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

Definitions

  • This invention relates to the absorption/isolation of vibrations in internal combustion engines, and is more particularly directed to absorbing/isolating harmonic vibrations between a connecting rod/bearing cap assembly or crank shaft main bearing assembly and the crankshaft of an internal combustion engine.
  • U.S. Patent 5,517,957 discloses a device for damping torsional vibrations in a drive train connected to an internal combustion engine and is incorporated herein by reference.
  • the '957 reference to Wagner et al. is complicated and expensive to manufacture, is bulky and is located further away from the source of the vibrations.
  • U.S. patent 4,617,884 also discloses a torsional vibration isolator and is incorporated herein by reference.
  • the '884 reference to Allen et al. discloses a resilient coupling 12 to isolate the flywheel from the crank shaft.
  • vibrations isolation is attempted far away from the source of the vibrations, requires a custom In re: Decuir, A. crankshaft/flywheel configuration and is expensive to manufacture.
  • the isolators of the prior art suffer from the drawback that they can not be simply incorporated into conventional internal combustion engine designs, are costly, heavy, bulky and are located far from the source of the vibrations.
  • the instant invention is believed to alleviate all of the drawbacks of the prior art isolators with a simple inexpensive design.
  • a vibration absorbing member is disposed within an annular recess on the side of the connecting rod/bearing cap assembly or alternatively/additionally disposed between the crankshaft main bearing and crank shaft main bearing journal.
  • a vibration absorbing member is preferably comprised of two pieces to fit in a recessed portion of the connecting rod and a recessed portion of the bearing cap to facilitate easy installation.
  • the vibration absorbing member absorbs vibrations between the connecting rod/bearing cap assembly and the crank shaft.
  • the vibration absorbing member absorbs vibration between the crank shaft and the engine block when disposed between the crankshaft and the crankshaft main bearing.
  • the vibration absorbing member is disposed on both sides of the In re: Decuir, A.
  • one of the connecting rods has a single vibration absorbing member disposed on the side contacting the crankshaft.
  • the other connecting rod has a vibration absorbing member disposed on both sides of the connecting rod and bearing cap assembly.
  • the vibration absorbing material is preferably made of an oil resistant elastomeric rubber material.
  • Fig. 1 represents an exploded perspective view of a connecting rod incorporating the dampener of the present invention.
  • Fig. 2 is a perspective view of the assembled device of Fig. 1 according to the present invention.
  • Fig. 3 is an isolated perspective view of the bearing cap incorporating the dampener of the present invention.
  • Fig. 4 is another exploded perspective view of a bearing cap incorporating the dampener according to the present invention.
  • Fig. 5 is a perspective assembled view of the bearing cap of Fig. 4. In re: Decuir, A.
  • Fig. 6 is a cross sectional exploded view taken along line 6-6 of Fig. 7.
  • Fig. 7 is an exploded side view of a connecting rod having a recessed portion adapted to receive the dampener according to the present invention.
  • Fig. 8 is a side view of an assembled conventional connecting rod and bearing cap assembly of the prior art.
  • Fig. 9 is a cross sectional view taken long line 9-9 of Fig. 8.
  • Fig. 10 is an exploded cross sectional view taken along line 10-10 of Fig. 11.
  • Fig. 11 is an exploded side view of an alternated connecting rod and bearing cap incorporating the dampener of the present invention.
  • Fig. 12 is an exploded bottom view of two adjacent connecting rods incorporating the dampener of the present invention taken along line 12-12 of Fig. 14.
  • Fig 13 is a bottom view of two adjacent connecting rods incorporating the dampener of the present invention taken along line 13-13 of Fig. 15.
  • Fig 14 is a cross sectional exploded view of two adjacent connecting rods and bearing caps incorporating the dampener of the present invention.
  • Fig. 15 is a cross sectional view of two adjacent connecting rods and bearing caps incorporating the dampener of the present In re: Decuir, A. invention.
  • Fig. 16 is an exploded cross sectional view of two adjacent connecting rods of an alternate embodiment incorporating the dampener of the present invention.
  • Fig 17 is a cross sectional view of the two adjacent connecting rods of Fig. 16 assembled.
  • Fig 18 is an exploded bottom view of the two connecting rods of Fig. 16 taken along line 18-18.
  • Fig 19 is a bottom view of the two connecting rods of Fig. 17 taken along line 19-19.
  • Fig. 20 is a side view of two adjacent connecting rods connected to a crank shaft of a V-type internal combustion engine.
  • Fig. 21 is a cross sectional view of two adjacent connecting rods connected to a crankshaft of a v-type internal combustion engine and a main bearing journal each incorporating dampener according to the present invention.
  • Fig. 22 is an enlarged view of a connecting rod bearing cap incorporating the vibration dampener of the present invention.
  • a vibration dampener member 6a, 6b is disposed between the connecting rod and crankshaft.
  • the connecting rod which houses the rod bearings is separated from the crankshaft journal by a thin layer of lubricating oil.
  • the sides of the connecting rod are bathed in lubricating oil preventing contact with the crankshaft. Because of the relative inco pressibility of this oil layer, vibrations are easily transmitted from the connecting rod/bearing assembly to the crankshaft.
  • the arrangement of the present invention has demonstrated significant reduction in the transmission of vibrations emanating from the combustion chamber, which in turn are transmitted to the connecting rod via the piston. Thus vibrations are prevented/reduced from being transmitted to the crankshaft and consequently to the remaining portions of the drive train assembly.
  • Figure 1 represents an exploded view of the vibration dampener according to one embodiment of the invention.
  • a connecting rod 1 has a first end 2 for connection to a piston pin in a conventional manner.
  • the connecting rod 1 extends to a second end 3 which connects with a bearing cap 4.
  • the second end 3 of the connecting rod 1 and the bearing cap 4 are secured together in a conventional manner to circumscribe a journal of a crank shaft.
  • the connecting rod has a semi-annular recessed portion 5 adapted to receive a semi-annular vibration dampener member 6a.
  • the bearing cap 4 has a semi-annular recessed portion 7 adapted to receive a second semi-annular vibration dampener 6b.
  • the two vibration dampeners 6a, 6b together form an o-ring like pad.
  • This vibration dampener is preferably made of a slippery elastomeric oil resistant rubber material.
  • other vibration absorbent material may be used such as oil resistant elastomeric plastic or other synthetic materials.
  • Figure 11 represents a similar connecting rod and bearing cap assembly comprising oil passages 10 and 11 to facilitate lubrication between the connecting rod and piston and the crankshaft. Such an arrangement provides the necessary lubrication for the embodiments having a dampener disposed on both sides of the connecting rod.
  • each connecting rod/bearing cap assembly will comprise a vibration dampener.
  • each connecting rod will have two such vibration dampeners disposed on either side of the connecting rod.
  • FIG. 12-15 represent an alternative embodiment of the claimed invention.
  • two connecting rod and bearing cap assemblies are disposed juxtaposed to one another for connection to a single journal of a crankshaft in a V-type internal combustion engine.
  • one of the two connecting rod and bearing cap assemblies has vibration dampener members 6a, 6b disposed between In re: Decuir, A. the two assemblies to dampen transmission of vibrations therebetween.
  • Figures 16-19 represent a preferred V-type engine vibration dampener arrangement.
  • one of two juxtaposed connecting rod assemblies has a vibration dampener disposed on opposite sides.
  • the second of the two juxtaposed connecting rods has just one vibration dampener disposed on the longitudinally outwardly facing side of the connecting rod with respect to an attached crankshaft journal.
  • Figure 20 and 21 each depict two such juxtaposed connecting rod/bearing cap assemblies connected to a crankshaft journal 13 of a V-type internal combustion engine.
  • the three vibration dampeners effectively reduce and nearly eliminate the transmission of vibrations from the connecting rods to the crankshaft.
  • oil distributions passages 10,11 may be employed to facilitate lubrication.
  • Figure 21 also discloses an additional vibration dampener 15 disposed about the crank shaft main bearing journal 14.
  • the vibration dampener 15 is disposed within the main bearings similarly to the way the vibration dampeners 6a, 6b are disposed within the connecting rod and bearing cap assembly.
  • the vibration dampener 15 is disposed both radially between the main bearings and the crank shaft's main bearing journal and between the main bearings and the counter weight lobe 16. This embodiment reduces/eliminates vibrations transmitting through the crank shaft to the engine block and vice versa.
  • Decuir, A the vibration dampener 15 disposed about the crank shaft main bearing journal 14.
  • the vibration dampener 15 is disposed within the main bearings similarly to the way the vibration dampeners 6a, 6b are disposed within the connecting rod and bearing cap assembly.
  • the vibration dampener 15 is disposed both radially between the main bearings and the crank shaft's main bearing journal and between the main bearings and the counter weight lobe 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Vibration Prevention Devices (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Elément absorbant les vibrations (6a, 6b) situé à l'intérieur d'un évidement annulaire (5, 7) sur le côté de l'ensemble constitué par la bielle (1) et par le chapeau (4) ou, de plus, dans un autre mode de réalisation, entre le palier principal de vilebrequin et les coussinets principaux du vilebrequin. Cet élément absorbant les vibrations est composé, de préférence, de deux pièces (6a, 6b) conçues pour loger dans une partie évidée (5) de la bielle (1) et dans une partie évidée (7) du chapeau (4) afin de faciliter son montage. Cet élément (6a, 6b) absorbe les vibrations entre l'ensemble constitué par la bielle (1) et par le chapeau (4) et le vilebrequin. De même, cet élément (6a, 6b) absorbe les vibrations entre le vilebrequin et le bloc moteur quand il est placé entre le vilebrequin et le palier principal du vilebrequin. Dans des moteurs classiques comportant un ou de multiples cylindres en ligne, cet élément est placé des deux côtés de l'ensemble constitué par la bielle et par le chapeau. Dans des moteurs en V comportant deux bielles contiguës, une de ces bielles possède un élément unique absorbant les vibrations situé sur le côté de contact avec le vilebrequin.
EP98941079A 1997-08-27 1998-08-27 Amortisseur de vibrations pour moteurs a combustion interne Withdrawn EP1007831A4 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US5607897P 1997-08-27 1997-08-27
US56078P 1997-08-27
US140398 1998-08-26
US09/140,398 US6044818A (en) 1998-08-26 1998-08-26 Vibration dampener for internal combustion engines
PCT/US1998/017745 WO1999010638A1 (fr) 1997-08-27 1998-08-27 Amortisseur de vibrations pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1007831A1 true EP1007831A1 (fr) 2000-06-14
EP1007831A4 EP1007831A4 (fr) 2002-07-17

Family

ID=26734948

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98941079A Withdrawn EP1007831A4 (fr) 1997-08-27 1998-08-27 Amortisseur de vibrations pour moteurs a combustion interne

Country Status (6)

Country Link
EP (1) EP1007831A4 (fr)
JP (1) JP2003525396A (fr)
KR (1) KR20010023336A (fr)
AU (1) AU1741499A (fr)
CA (1) CA2302319C (fr)
WO (1) WO1999010638A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6745740B1 (en) * 2003-02-13 2004-06-08 Decuir Engine Technologies, Llc Vibration dampening arrangement for internal combustion engines
FR2897125B1 (fr) * 2006-02-06 2009-02-27 Peugeot Citroen Automobiles Sa Bielles pour moteur a combustion interne et moteur combustion interne equipe de telles bielles
JP2015161322A (ja) * 2014-02-26 2015-09-07 マツダ株式会社 エンジンのコンロッド構造

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB882299A (en) * 1957-09-19 1961-11-15 Auto Union Gmbh Improvements in bearing assemblies
US4362341A (en) * 1979-04-25 1982-12-07 Nissan Motor Co., Ltd. Low-noise level internal combustion engine
DE3813223A1 (de) * 1988-04-20 1989-11-02 Kloeckner Humboldt Deutz Ag Koerperschalluebertragung vermindernde lagerstelle
JPH08261233A (ja) * 1995-03-22 1996-10-08 Koyo Seiko Co Ltd 転がり軸受装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2371599A1 (fr) * 1974-05-16 1978-06-16 Rolls Royce Motors Ltd Palier de tete de bielle de moteur
US4254743A (en) * 1977-12-27 1981-03-10 Reid Allen F Combustion engine
US4617884A (en) 1984-07-27 1986-10-21 Charles A. Allen Torsional vibration isolator and method
DE9417045U1 (de) 1994-10-22 1994-12-15 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Vorrichtung zur Dämpfung von Drehschwingungen in einem Antriebsstrang

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB882299A (en) * 1957-09-19 1961-11-15 Auto Union Gmbh Improvements in bearing assemblies
US4362341A (en) * 1979-04-25 1982-12-07 Nissan Motor Co., Ltd. Low-noise level internal combustion engine
DE3813223A1 (de) * 1988-04-20 1989-11-02 Kloeckner Humboldt Deutz Ag Koerperschalluebertragung vermindernde lagerstelle
JPH08261233A (ja) * 1995-03-22 1996-10-08 Koyo Seiko Co Ltd 転がり軸受装置

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 02, 28 February 1997 (1997-02-28) & JP 08 261233 A (KOYO SEIKO CO LTD), 8 October 1996 (1996-10-08) *
See also references of WO9910638A1 *

Also Published As

Publication number Publication date
JP2003525396A (ja) 2003-08-26
WO1999010638A1 (fr) 1999-03-04
AU1741499A (en) 1999-03-16
KR20010023336A (ko) 2001-03-26
CA2302319A1 (fr) 1999-03-04
CA2302319C (fr) 2004-11-16
EP1007831A4 (fr) 2002-07-17

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