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WO2001011257A1 - Amortisseurs de vibrations de torsion - Google Patents

Amortisseurs de vibrations de torsion Download PDF

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Publication number
WO2001011257A1
WO2001011257A1 PCT/GB2000/003018 GB0003018W WO0111257A1 WO 2001011257 A1 WO2001011257 A1 WO 2001011257A1 GB 0003018 W GB0003018 W GB 0003018W WO 0111257 A1 WO0111257 A1 WO 0111257A1
Authority
WO
WIPO (PCT)
Prior art keywords
members
bearing
mould
sleeve
carriers
Prior art date
Application number
PCT/GB2000/003018
Other languages
English (en)
Inventor
Alastair John Young
Bharat Bushan Sood
Original Assignee
Ap Tmf Limited
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 Ap Tmf Limited filed Critical Ap Tmf Limited
Priority to AU64560/00A priority Critical patent/AU6456000A/en
Priority to EP00951702A priority patent/EP1119715A1/fr
Priority to GB0107341A priority patent/GB2359869B/en
Publication of WO2001011257A1 publication Critical patent/WO2001011257A1/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
    • 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/13164—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 the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • F16F15/13171—Bearing arrangements
    • F16F15/13178—Bearing arrangements comprising slide bearings

Definitions

  • This invention relates to torsional vibration dampers for use in vehicles, hereinafter referred to as of the kind specified, comprising an input member for connection with an associated engine and an output member for connection with an associated vehicle driveline, said members being relatively rotatable via a support bearing acting therebetween against the action of a torsional damping means to damp torsional vibrations in the associated vehicle driveline
  • Such torsional vibration dampers may be in the form of twin mass flywheels in which the input and output members are each of significant mass or may have relatively light input and output members which possess relatively little flywheel mass Such dampers may be positioned at any convenient point in the drive line
  • the support bearing for such torsional dampers conventionally comprises a ball or roller bearing and, although the use of a plain bearing has been suggested in the patent literature for many years, plain bearings have not had any significant usage in practice due mainly to the high level of accuracy required in their manufacture in order to achieve satisfactory operation
  • a torsional vibration damper of the kind specified in which the support bearing comprises a plain bearing formed in situ between the input and output members
  • the plain bearing may be formed in situ directly on the input and output members or between a first bearing carrier connected with one member and a second bearing carrier connected with the other member
  • the carriers may be made from sheet metal by any suitable technique or can be made by casting, forging or sintering.
  • the carriers preferably have generally axially extending regions between which the low friction plain bearing means is located to support the members radially and may also include generally radially extending regions which are used to secure each of the carriers to its respective member
  • An axially acting spring means such as a belleville spring, may act between confronting generally radially extending regions of the carriers to generate friction damping on said relative rotation
  • This axially acting spring may also bias other surfaces which rotate with the respective masses into frictional contact to generate further friction damping
  • One of the members may include circumferential spaced axially facing support pads which contact a co-operating support surface on the other member to control relative axial movement of the members These pads may also help to control relative tipping of the members during use of the damper
  • the plain bearing may be moulded with a generally axially extending portion and a generally radially extending portion, the generally radially extending portion controlling axial movement and tipping of the members
  • the invention also provides a method of manufacturing a support bearing for a torsional vibration damper the kind specified, said method comprising the steps of - placing a pair of concentric annular members into a mould,
  • the method may include the additional step of moving said members relative to each other to crack the sleeve from one or both members to provide a functioning support bearing in which said members are relatively rotatable via the sleeve
  • concentric annular members may be the flywheel masses themselves or may be separate first and second bearing carriers for subsequent connection with the input and output masses respectively Similarly in a non-flywheel torsional damper the concentric annular members may also be the input and output members themselves or may be separate first and second bearing carriers for subsequent connection with the input and output members respectively
  • Portions of the mould adjacent one or both members may be cooled or heated to discourage bonding of the bearing sleeve to the cooler mould portion(s) This differential cooling or heating may be controlled to cause slight shrinkage of the moulded bearing sleeve away from the cooler mould portion to provide a working clearance between the sleeve and members
  • one or both members may be coated in a release agent prior to injection of the bearing material to remove the need for, or at least facilitate, cracking of the members from the moulded bearing sleeve
  • each carrier may comprise a generally axially extending region between which the void is defined and a generally radially extending portion, these radially extending portions being held in contact with each other during the moulding process to close-off one end of the void, the other end of the void being closed by the mould
  • the carriers can be displaced axially and/or rotated relative to each other to crack the moulded sleeve from one or both carriers
  • FIGS. 2 and 3 show sections on lines B-Bl and B2-B3 of figure 1 respectively
  • Figures 4 shows part of figure 2 on a larger scale
  • Figure 5 shows a further part of figure 1 on a larger scale
  • Figure 6 shows part of a casting mould for an in situ moulded plain bearing
  • Figure 7 shows an alternative in situ moulded plain bearing
  • Figure 8 shows an alternative tapering form of in situ moulded plain bearing
  • a twin mass flywheel 10 comprises an input flywheel mass 1 1 [carrying a starter ring 11a] and an output flywheel mass 12 which are mounted for limited relative rotation about a common axis A-A via a plain bearing arrangement 13 described in detail below carried on a bearing support block 1 Id Relative rotation of the input and output flywheel members is opposed by a damping means in the form of bob-weight linkages 14, compression spring assemblies 15, elastomeric springs 16, and a radially inner multi-plate friction damper 17 All these damping means act in parallel between the input and output flywheel masses
  • Input flywheel mass 1 1 is of a composite construction having pressed metal central disc portion 1 lb and a forged outer annular portion 1 lc which are welded together by a weld bead 1 If and are centred relative to each other by contact between the outer periphery of disc portion 1 lb and annular surface 1 le on outer portion l ie
  • the output flywheel mass 12 is of a cast metal construction
  • the two flywheel masses are held in an assembled state, prior to attachment to the associated engine crankshaft by screws 18 see Figure 1 , on the same pitch circle diameter as bolt holes 1
  • the twin mass flywheel is bolted to the crankshaft by attachment bolts 19a which extend through circumferentially spaced bolt holes 1 in bearing support block 1 Id and input flywheel mass disc portion 1 lb
  • Each compression spring assembly may comprise an outer compression spring 15a and an inner compression spring 15b with the operation of the inner compression spring 15b being timed to be delayed by several degrees from the commencement of the operation of the outer compression spring 15a
  • one pair of diametrically opposite compression springs 15 may be arranged to operate before the other pair of diametrically opposite compression springs during the relative rotation of the two flywheel masses
  • the springs 15a and 15b have a natural shape in which their longitudinal axes are straight When mounted between abutments 20 and 21 the springs are deflected to an acute shape by a sheet metal support member 40 which will be described further below
  • Figure 1 shows the flywheel in its central or neutral position and, with the flywheel rotating in the direction of arrow D, in the normal drive condition a relative rotation of P (see Figure 5) occurs before abutments 21 are contacted by spring chairs 15c which fit around the end of the springs 15 Springs 15 are non-operational in the overrun condition when abutments 21 tend to move away from springs 15
  • the elastomeric compression springs or blocks 16 are each supported on the input mass 11 between end plates 16a in a window 22 pressed out of input flywheel mass 1 1 by a sheet metal casing member 41 Member 41 has end portions 41a and 41b which are respectively curved around a radially outer abutment 24 which is pressed out of input flywheel mass 1 1 and around the bottom edge 22a of window 22
  • the end plates 16a are acted upon by abutments 23 on a ring 23a which is secured to output flywheel mass 12 by rivets 23b
  • the end plates 16a have wings 16b which extend between abutments 23 and output mass 12 and tabs 16c which hook under the radially inner edge of block 16
  • Each elastomeric spring block 16 is also located against radially outwards movement to mass 1 1 by radially outer abutment 24
  • the elastomeric sp ⁇ ngs 16 are therefore confined within windows 22 between the two flywheel masses 1 1 and 12
  • the blocks 16 operate to damp relative rotation of the flywheel masses in the end zones of the relative rotation both in the drive and overrun conditions
  • Blocks 16 operate in the drive condition after a relative rotation of Q and in the overrun condition after a relative rotation of R Further details of blocks 16 are set out in the Applicant's co-pending UK patent application No 98 28399 7
  • Each bob-weight linkage 14 comprises a bob-weight 25 which is pivotally mounted on output flywheel mass 12 via a cantilevered pivot pin 26 and a bush 27 which is press fit into the bob- weight
  • the linkage is completed by a flexible link 28 which is connected at one end with the input flywheel mass 11 via a rivet 29 and at its other end with a bob- weight 25 via a rivet 30
  • Each rivet 29 extends through a mounting tab 40a of support member 40
  • the other end 40b of spring support member 40 rests on outer radially abutment 24.
  • pivotal connections 28 and 29 are again described in greater detail in the previously referred to co-pending application no. 98 28399.7.
  • pivots 29 are located radially within compression spring assemblies 15 This allows a longer length for links 28 so that the total permitted relative rotation between the input and output flywheel masses can be increased
  • Bob-weights 25 are also shaped having a cut-out portions 25a, to concentrate their mass as radially far outwards as possible
  • Output mass 12 is provided with radially outwardly projecting lugs 45 which move in circumferentially extending slots 46 between radially inwardly extending lugs 47 on input mass 1 1 Relative rotation between mass 1 1 and 12 in the drive condition is limited by contact between surfaces 47a and 45a on lugs 47 and 45 and in the overrun condition by contact between surfaces 47b and 45b
  • the multi-plate friction damper 17 is best seen in Figure 4
  • This damper comprises discs 50 and 51 which are splined onto output mass 12 at 50a and 51 a respectively, the disc 52 which is splined at 52a onto a first bearing carrier 60 which has a radially inwardly extending portion 60d which is bolted to input flywheel mass disc portion 1 lb by bolts 19a and further discs 53 and 54 which are splined at 53a and 54a to an annular band 55 which is itself splined at 55a onto spines 52a of disc 52
  • the friction damper is completed by a pair of belleville springs 56 which act between disc 50 and a second bearing carrier 61 which is secured via rivets 23b to output flywheel mass 12
  • bearing carriers 60 and 61 have concentric generally axially extending portions 61a and 60a respectively between which a plain bearing sleeve 80 which is formed in situ is located
  • the bearing is completed by a belleville spring 62 which acts between radially extending regions 60c and 61c of the bearing carriers to bias the regions 60c and 61c apart and hence axially load the output flywheel mass 12 to the left, as viewed in figure 4, relative to the input mass 11
  • effect disc 52 which is sandwiched between the input and output flywheel masses acts as an axial thrust bearing/support member
  • axially facing support pads 66 are provided at circumferentially spaced locations around the input mass 1 1 These pads contact the confronting surface 12a of the output mass 12 to control any tendency of the two flywheel masses to move axially or tilt relative to each other during relative rotation
  • Pads 66 could replace disc 52 to take axial loading or could supplement disc 52 to control tilt to a given level
  • the input flywheel mass 1 1 is provided with additional mass 70 at circumferentially spaced positions around the input mass to increase the inertia of the flywheel
  • This additional mass is located generally in the annular zone within which the bob weight linkages 14 operate but is located to the side of the linkages in a non swept volume of this annular zone
  • This extra mass is forged into the outer annular portion 1 lc of the input mass and includes the spring abutments 20
  • the bearing support block 1 Id is preferably manufactured from cast metal and, in order to avoid problems due to local radial distortion of the support block when attachment bolts 19a are fully tightened the radially outer surface 1 lg of block l id may be sized to be positioned with a slight clearance from the bearing carrier 60 and the carrier 60 may be supported against radially inward movements by annular washer 65 through which the attachment bolts 19a extend This washer is also provided to prevent the attachment bolt
  • the plain bearing sleeve 80 is formed in situ between the carriers 60 and 61 using a mould arrangement part of which is shown diagrammatically in Figure 6 Essentially the mould comprises two platens 81 and 82 which support the bearing carriers 60 and 61 with their radially extending portions 60c and 61c in contact with each other to seal off one end of a void between the bearing supports within which the bearing sleeve 80 will be moulded The other end of the void is sealed by the platen 82 Platen 82 includes injection nossles 83 through which polymeric bearing material is injected When the bearing material is solidified the supports 60 and 61 together with the in situ moulded sleeve 80 are removed from the mould and the supports 60 and 61 are moved axially and/or rotated relative to each other to crack the bond between the sleeve 80 and one or both of the supports 60 and 61 to provide a functioning bearing The bearing is then subsequently mounted in its operational position in the flywheel with the two radially extending portions 60c
  • carrier 60 may, for example, be formed with a series of holes, cut-outs, grooves or other recesses into which the sleeve 80 may flow during the moulding process to provide a positive key If no carriers 60,61 are used and the sleeve is directly moulded onto the flywheel masses 1 1 and 12 one of these masses may be provided with the above keying recesses
  • the moulding process may be modified by providing differential temperature control to the platens This can be achieved by providing one or both of the platens with a cooling water gallery which cools one or both carriers 60 or 61 so that the in situ moulded bearing sleeve does not attach itself to the or each cooled carrier This obviates the need to crack the carriers from the moulded sleeve 80. If the or each platen is cooled sufficiently the bearing sleeve may shrink back slightly from the cooled carrier(s) to give a working clearance
  • differential temperature of the platens can be achieved by applying heat rather than cooling
  • one or both of the carriers may be coated in a release agent prior to insertion into the mould to remove the need to, or at least facilitate, cracking of the carriers from sleeve 80
  • the material from which the bearing sleeve is moulded may, for example, comprise modified or unmodified thermoplastic or thermosetting polymers
  • PEEK polyetherether ketone
  • fillers such as glass fibre, carbon fibre and/or friction modifiers such as molybdenum disulphide
  • PES polyethersulphone
  • the bearing construction shown in Figure 4 may be modified, for example, by moving belleville spring 62 to the position occupied by disc 52 and forming bearing sleeve 80 with an integral radially extending portion 80a (see Figure 7) which replaces disc 52 and acts as an axial thrust bearing Bearing sleeve 80 with the radially extending portion 80a may be cast in situ by a suitable modification of the mould platens shown in Figure 6
  • the bearing sleeve 80 may be directly moulded or otherwise formed into portions of flywheel mass 12 and support 1 Id or an axially extended portion of flywheel mass 11
  • This arrangement requires appropriate modification of the mould platens shown in Figure 6
  • the supports 60 and 61 and the sleeve 80 may be of a slightly tapering form, as shown in Figure 8, so that any slight shrinkage can be counteracted by slight migration of the sleeve 80 down the taper as indicated by arrow M in Figure 8
  • any shrinkage of sleeve 80 will have no effect on the ability of sleeve 80 to rotate relative to support 61
  • the invention is not only applicable to twin mass flywheels but can also be used in relation to torsional vibration dampers of the kind specified in general and is not limited to dampers which use bob-weight torsional damping but can be used with any type of torsional damping between the input and output members

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un amortisseur de vibrations de torsion pour véhicules, qui comporte un élément d'entrée (11) destiné à être connecté à un moteur associé, et un élément de sortie (12) destiné à être connecté à une transmission de véhicule associée. Les éléments d'entrée et de sortie peuvent tourner l'un par rapport à l'autre par l'intermédiaire d'un palier d'appui situé entre ceux-ci, qui s'oppose à l'action d'un moyen d'amortissement de torsion afin d'amortir les vibrations de torsion de la transmission de véhicule associée. Le palier d'appui est un palier lisse (80) moulé in situ entre les éléments d'entrée et de sortie (11, 12), ou entre des porte-coussinets (60, 61) destinés à être connectés à un élément d'entrée ou de sortie respectif. Un procédé de fabrication du palier lisse (80) par moulage in situ est également décrit.
PCT/GB2000/003018 1999-08-10 2000-08-04 Amortisseurs de vibrations de torsion WO2001011257A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU64560/00A AU6456000A (en) 1999-08-10 2000-08-04 Torsional vibration dampers
EP00951702A EP1119715A1 (fr) 1999-08-10 2000-08-04 Amortisseurs de vibrations de torsion
GB0107341A GB2359869B (en) 1999-08-10 2000-08-04 Torsional vibration dampers

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9918716.3 1999-08-10
GBGB9918716.3A GB9918716D0 (en) 1999-08-10 1999-08-10 Torsional vibration dampers

Publications (1)

Publication Number Publication Date
WO2001011257A1 true WO2001011257A1 (fr) 2001-02-15

Family

ID=10858819

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2000/003018 WO2001011257A1 (fr) 1999-08-10 2000-08-04 Amortisseurs de vibrations de torsion

Country Status (4)

Country Link
EP (1) EP1119715A1 (fr)
AU (1) AU6456000A (fr)
GB (2) GB9918716D0 (fr)
WO (1) WO2001011257A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004053354A1 (fr) * 2002-12-06 2004-06-24 Automotive Products Italia S.P.A. Volant a deux masses
EP1865221A1 (fr) * 2006-06-07 2007-12-12 LuK Lamellen und Kupplungsbau Beteiligungs KG Dispositif d'amortissement d'oscillations de rotation
WO2007140741A1 (fr) * 2006-06-02 2007-12-13 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Volant d'inertie divisé

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2387881B (en) * 2002-04-23 2005-11-09 Metaldyne Internat Method of bearing construction

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0232922A1 (fr) * 1986-01-21 1987-08-19 KOLBENSCHMIDT Aktiengesellschaft Matériau composite pour palier à glissement
US5673598A (en) * 1993-11-15 1997-10-07 Valeo Damped flywheel, especially for a motor vehicle, wherein a friction means is mounted in a cavity bounded by the reaction plate and the damper plate
DE29715250U1 (de) * 1996-09-26 1997-12-11 Mannesmann Sachs AG, 97424 Schweinfurt Schwungmassenvorrichtung mit einem axialen Gleitlager
EP0826899A2 (fr) * 1996-08-30 1998-03-04 Aisin Seiki Kabushiki Kaisha Support à palier lisse dans un mécanisme à double masse pour transmission de force

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09103975A (ja) * 1995-10-04 1997-04-22 Fujicopian Co Ltd カルコ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0232922A1 (fr) * 1986-01-21 1987-08-19 KOLBENSCHMIDT Aktiengesellschaft Matériau composite pour palier à glissement
US5673598A (en) * 1993-11-15 1997-10-07 Valeo Damped flywheel, especially for a motor vehicle, wherein a friction means is mounted in a cavity bounded by the reaction plate and the damper plate
EP0826899A2 (fr) * 1996-08-30 1998-03-04 Aisin Seiki Kabushiki Kaisha Support à palier lisse dans un mécanisme à double masse pour transmission de force
DE29715250U1 (de) * 1996-09-26 1997-12-11 Mannesmann Sachs AG, 97424 Schweinfurt Schwungmassenvorrichtung mit einem axialen Gleitlager

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004053354A1 (fr) * 2002-12-06 2004-06-24 Automotive Products Italia S.P.A. Volant a deux masses
WO2007140741A1 (fr) * 2006-06-02 2007-12-13 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Volant d'inertie divisé
EP1865221A1 (fr) * 2006-06-07 2007-12-12 LuK Lamellen und Kupplungsbau Beteiligungs KG Dispositif d'amortissement d'oscillations de rotation

Also Published As

Publication number Publication date
GB0107341D0 (en) 2001-05-16
GB2359869B (en) 2004-01-21
AU6456000A (en) 2001-03-05
EP1119715A1 (fr) 2001-08-01
GB9918716D0 (en) 1999-10-13
GB2359869A (en) 2001-09-05

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