WO2004053354A1 - Twin mass flywheels - Google Patents

Twin mass flywheels Download PDF

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Publication number
WO2004053354A1
WO2004053354A1 PCT/GB2003/005284 GB0305284W WO2004053354A1 WO 2004053354 A1 WO2004053354 A1 WO 2004053354A1 GB 0305284 W GB0305284 W GB 0305284W WO 2004053354 A1 WO2004053354 A1 WO 2004053354A1
Authority
WO
WIPO (PCT)
Prior art keywords
flange
side plates
masses
mass flywheel
mass
Prior art date
Application number
PCT/GB2003/005284
Other languages
French (fr)
Inventor
Paul Andrew Gallagher
Andrea Ribichini
Original Assignee
Automotive Products Italia S.P.A.
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 Automotive Products Italia S.P.A. filed Critical Automotive Products Italia S.P.A.
Priority to EP03782592A priority Critical patent/EP1567785A1/en
Priority to GB0510335A priority patent/GB2410991B/en
Priority to AU2003290227A priority patent/AU2003290227A1/en
Publication of WO2004053354A1 publication Critical patent/WO2004053354A1/en

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
    • 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
    • F16F15/13107—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 for damping of axial or radial, i.e. non-torsional vibrations
    • 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
    • F16F15/139—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 friction-damping means
    • 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
    • F16F15/139—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 friction-damping means
    • F16F15/1395—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 friction-damping means characterised by main friction means acting radially outside the circumferential lines of action of the elastic members

Definitions

  • This invention relates to twin mass flywheels, hereinafter referred to as being of the type described, having an input mass for connection with an engine, an output mass for connection with a transmission, bearing means supporting the masses for limited relative rotation, an annular radially extending flange connected adjacent its outer or inner periphery with one of the masses, a pair of annular side plates located on either side of the flange and connected at their inner or outer peripheries with the other mass, and circumferentially extending spring means acting between the flange and the side plates to damp relative rotation between the masses.
  • Twin mass flywheels of the type described are well known and are achieving increasing acceptance in motor vehicles in order to damp torsional vibrations introduced into the vehicle drive line by the vehicle engine.
  • twin mass flywheels of the type described One problem associated with twin mass flywheels of the type described is the tendency of the input and output masses to tilt relative to each other as they rotate as a result of the flexing of the engine crankshaft caused by the firing strokes of the engine.
  • twin mass flywheel of the type described in which the other peripheries of the side plates remote from their connection with the other mass contact the flange on either side thereof to limit the tipping of the masses relative to each other during relative rotation.
  • this contact between the side plates and the flange tends to support the two flywheel masses relative to each other and thus at least partially controls any tendency for relative tipping.
  • the side plates also either contact the flange or apply axial pressure to a component rotatable with the flange at a location radially inboard of the spring means to lend further stabilise the masses against tipping.
  • a friction device is provided between the side plates adjacent the radially inner periphery of the flange.
  • the side plates only contact the flange to control tipping adjacent the radially outer periphery of the flange.
  • the friction device in which the friction device is provided between the side plates, the friction device may be of a multi-disc type with some discs keyed for rotation with the flange and other interleaved discs keyed for rotation with the output mass, the friction force being generated by a belleville spring which is also located between the side plates.
  • the above friction device may also include a low friction disc which forms part of the friction disc stack and which is keyed for rotation with either the flange or the output mass and which provides low friction damping of idle rattle etc.
  • the friction discs which are keyed for rotation with the output mass may be keyed onto rivets which also secure the side plates to the output mass.
  • the bearing between the input and output mass may be a plain bearing.
  • This plain bearing may be located between tubular projections formed on the input and output masses respectively. Typically these projections will extend in opposite axial directions and may be formed integrally with or separate from the associated flywheel mass.
  • Figure 1 is an axial cross section through a twin mass flywheel in accordance with the present invention
  • Figure 2 is a view on arrows A-A of Figure 1 with the clutch removed and a segment of the output flywheel mass cut away;
  • Figure 3 shows, on an enlarged scale, details on the section line B-B of Figure 2 of the friction device
  • Figure 4 shows an axial section through an alternative form of twin mass flywheel in accordance with the present invention
  • Figure 5 is a view on arrows C-C of Figure 4 with part of the output flywheel mass cut away and showing some internal details in section;
  • Figure 5a is an edge view on arrow X of Figure 5;
  • Figure 6 shows, on an enlarged scale, details of the friction device used in the twin mass flywheel of Figures 4 and 5, and
  • Figure 7 shows a variant of the twin mass flywheel shown in Figures 4 to 6 in which the bearing support is formed as a separate component from the input flywheel mass.
  • this shows a twin mass flywheel 10 having an input mass 11 for connection with an engine crankshaft via bolt holes 11a and an output mass 12 for connection with a vehicle transmission via a clutch 13 mounted thereon.
  • the output mass 12 is supported from the input mass 11 via a plain bearing 14 which is carried on an axially extending tubular extension 15 of the input mass 11.
  • the output mass 12 can rotate through a limited circumferential distance relative to the input mass 11 under the control of compression springs 16. These springs are housed in windows 17 in a flange 18 which is riveted at 19 to input mass 11 and in windows 20 in side plates 21 and 22 positioned on either side of the flange 18 and riveted to output mass 12 at 23.
  • Rivets 19 also secures an added mass ring 24 to input mass 11.
  • rivets 23 secure a friction retaining ring 25 (see Figure 3) to output mass 12 under which is compressed a friction disc 26 which is keyed to retaining ring 25 and hence to output mass 12, a second friction disc 27 which is keyed to tubular extension 15 and a belleville spring 28 which contacts the end 29a of a bearing support member 29 which is also riveted to output mass 12 between side plates 21 and 22 by rivet 23.
  • belleville spring 28 provides the necessary axial force between bearing support end 29a and retaining ring 25 to generate friction on the relative rotation on the input and output flywheel masses.
  • the rotational keying of the disc 26 to ring 25 and hence to output mass 12 and the keying of disc 27 to tubular extension 25 can be with or without lost circumferential motion so that the friction device can operate for all rotational movements of the input and output flywheel masses or only after a predetermined amount of relative rotational movement has taken place.
  • the side plates 21 and 22 make contact at their outer peripheries 21a and 22a with the radially outer portion 18a of flange 18 and thus stabilise the flywheel against tipping of the input mass relative to the output mass due to flexing of the engine crankshaft etc.
  • the side plates 21 and 22 also contact the radially inner portion 18b of flange 18 at locations 21 b and 22b to further stabilise the flywheel masses against relative tipping.
  • Figure 4 shows a further form of twin mass flywheel in accordance with the present invention in which components of a similar function to those described above in relation to Figures 1 to 3 have been similarly numbered.
  • the side plates 21 and 22 are riveted to output mass 12 via a rivet 30 which also includes a spacing portion 31 to hold the side plates 21 and 22 spaced apart.
  • a friction device 32 is provided (see Figure 6) which comprises a pair of friction discs 33 which are keyed at their outer peripheries within the radially inner portion of flange 18 and interleaved friction discs 34 which are keyed at their inner peripheries onto rivets 30.
  • the friction device also includes a plastics friction disc 35 of L-shaped cross section having axial projections 36 which are keyed to flange 18 radially outboard of discs 33.
  • a belleville spring 39 completes the friction device and provides the axial loading to ensure that the friction discs generate the necessary frictional force.
  • the keying of friction disc 35 to flange 18 is without any lost circumferential motion (see Figure 5) so that the low level of friction generated by friction disc 35 operates for all relative rotations of the input and output masses and provides a so-called idle rattle friction suppression of the twin mass flywheel.
  • the keying of the discs 33 and 34 to their co-operating members 18 and 30 may be with or without lost motion in the circumferential sense (see lost motion 'x' as shown in Figure 5) so that the overall friction characteristics of the friction device can be tuned to the particular vehicle on which the twin mass flywheel is to be used.
  • Inner and outer added mass rings 24a and 24b respectively are rivetted to input mass 11 by rivets 19.
  • the outer peripheral portions 21a and 22a of the side plates 21 and 22 contact the radially outer portion 18a of flange 18 to resist tipping of the input and output masses of the flywheel due to flexing of the crankshaft etc.
  • the side plate portions 21b and 22b apply axial pressure to the discs 33 which are splined for rotation with flange 18 via the interleaved plates 34, the friction disc 35 and the belleville spring 39. This again tends to resist tipping of the flywheel masses.
  • the input and output masses are supported for relative rotation on a plain bearing 40 which is of L-shaped cross section and which itself is supported between an axially extending projection 15 on input mass 11 and a parallel axially extending projection 41 formed integrally with the output mass 12.
  • the radially outwardly extending flange 42 on bearing 40 acts between the projections 15 and 41 to resist any axial movement of the masses towards each other.
  • the flywheel shown in figures 4 to 6 also includes a stop arrangement to limit the relative rotation of the flywheel masses 11 and 12.
  • This stop arrangement is provided by radially inwardly extending projections 24c on outer added mass ring 24b which move in pressed axial recesses 22c in side plate 22 (see figure 5). Rotation is limited when projections 24c strike the sides 22d of recesses 22c. Typically this rotation is limited to 24 degrees in either direction (ie 48 degrees total relative rotation).
  • the circumferential zones 22e of side plate 22 between the recesses 22c contact the flange 18 as does the entire zone 21a of side plate 21 to limit the tipping of the flywheel masses.
  • this shows a further variant of the twin mass flywheel shown in Figures 4 to 6 in which the bearing 40 is supported from a separate axially extending projection 45 which is bolted to input mass 11 by the same bolts which attach the twin mass flywheel to the vehicle crankshaft and which extend through bolt holes 11a.
  • This construction is cheaper to produce and may also save weight.

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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)
  • Pulleys (AREA)

Abstract

A twin mass flywheels having an input mass (11) for connection with an engine, an output mass (12) for connection with a transmission, bearing means (14) supporting the masses for limited relative rotation, an annular radially extending flange (18) connected adjacent its outer or inner periphery with one (11) of the masses, a pair of annular side plates (21,22) located on either side of the flange (18) and connected at their inner or outer peripheries with the other mass (12), and circumferentially extending spring means (16) acting between the flange (18) and the side plates (21,22) to damp relative rotation between the masses. The other peripheries (21a,22a) of the side plates remote from their connection with the other mass (12) contact the flange (18) on either side thereof to limit the tipping of the masses relative to each other during relative rotation. The side plates (21,22) may also either contact the flange (18b) or apply axial pressure to a component (33) rotatable with the flange at a location (21b,22b) radially inboard of the spring means (16) to lend further stabilize the masses against tipping. A friction device (32) may be provided between the side plates (21,22) adjacent the radially inner periphery of the flange (18).

Description

TWIN MASS FLYWHEELS
This invention relates to twin mass flywheels, hereinafter referred to as being of the type described, having an input mass for connection with an engine, an output mass for connection with a transmission, bearing means supporting the masses for limited relative rotation, an annular radially extending flange connected adjacent its outer or inner periphery with one of the masses, a pair of annular side plates located on either side of the flange and connected at their inner or outer peripheries with the other mass, and circumferentially extending spring means acting between the flange and the side plates to damp relative rotation between the masses.
Twin mass flywheels of the type described are well known and are achieving increasing acceptance in motor vehicles in order to damp torsional vibrations introduced into the vehicle drive line by the vehicle engine.
One problem associated with twin mass flywheels of the type described is the tendency of the input and output masses to tilt relative to each other as they rotate as a result of the flexing of the engine crankshaft caused by the firing strokes of the engine.
It is an object of the present invention to provide a twin mass flywheel of the type described which is capable of at least mitigating this tipping of the flywheel masses relative to each other.
Thus in accordance with the present invention there is provided a twin mass flywheel of the type described in which the other peripheries of the side plates remote from their connection with the other mass contact the flange on either side thereof to limit the tipping of the masses relative to each other during relative rotation. As will be appreciated this contact between the side plates and the flange tends to support the two flywheel masses relative to each other and thus at least partially controls any tendency for relative tipping.
In one form of twin mass flywheel in accordance with the present invention the side plates also either contact the flange or apply axial pressure to a component rotatable with the flange at a location radially inboard of the spring means to lend further stabilise the masses against tipping.
In another form of twin mass flywheel in accordance with the present invention a friction device is provided between the side plates adjacent the radially inner periphery of the flange. In this construction the side plates only contact the flange to control tipping adjacent the radially outer periphery of the flange.
In the twin mass flywheel described above, in which the friction device is provided between the side plates, the friction device may be of a multi-disc type with some discs keyed for rotation with the flange and other interleaved discs keyed for rotation with the output mass, the friction force being generated by a belleville spring which is also located between the side plates.
The above friction device may also include a low friction disc which forms part of the friction disc stack and which is keyed for rotation with either the flange or the output mass and which provides low friction damping of idle rattle etc.
The friction discs which are keyed for rotation with the output mass may be keyed onto rivets which also secure the side plates to the output mass.
The bearing between the input and output mass may be a plain bearing.
This plain bearing may be located between tubular projections formed on the input and output masses respectively. Typically these projections will extend in opposite axial directions and may be formed integrally with or separate from the associated flywheel mass.
Several embodiments of the present invention will now be described, by way of example only, with reference to the accompanying drawings in which:-
Figure 1 is an axial cross section through a twin mass flywheel in accordance with the present invention;
Figure 2 is a view on arrows A-A of Figure 1 with the clutch removed and a segment of the output flywheel mass cut away;
Figure 3 shows, on an enlarged scale, details on the section line B-B of Figure 2 of the friction device;
Figure 4 shows an axial section through an alternative form of twin mass flywheel in accordance with the present invention;
Figure 5 is a view on arrows C-C of Figure 4 with part of the output flywheel mass cut away and showing some internal details in section;
Figure 5a is an edge view on arrow X of Figure 5;
Figure 6 shows, on an enlarged scale, details of the friction device used in the twin mass flywheel of Figures 4 and 5, and
Figure 7 shows a variant of the twin mass flywheel shown in Figures 4 to 6 in which the bearing support is formed as a separate component from the input flywheel mass.
Referring to Figure 1 this shows a twin mass flywheel 10 having an input mass 11 for connection with an engine crankshaft via bolt holes 11a and an output mass 12 for connection with a vehicle transmission via a clutch 13 mounted thereon. The output mass 12 is supported from the input mass 11 via a plain bearing 14 which is carried on an axially extending tubular extension 15 of the input mass 11.
The output mass 12 can rotate through a limited circumferential distance relative to the input mass 11 under the control of compression springs 16. These springs are housed in windows 17 in a flange 18 which is riveted at 19 to input mass 11 and in windows 20 in side plates 21 and 22 positioned on either side of the flange 18 and riveted to output mass 12 at 23.
Rivets 19 also secures an added mass ring 24 to input mass 11. Similarly rivets 23 secure a friction retaining ring 25 (see Figure 3) to output mass 12 under which is compressed a friction disc 26 which is keyed to retaining ring 25 and hence to output mass 12, a second friction disc 27 which is keyed to tubular extension 15 and a belleville spring 28 which contacts the end 29a of a bearing support member 29 which is also riveted to output mass 12 between side plates 21 and 22 by rivet 23. Thus belleville spring 28 provides the necessary axial force between bearing support end 29a and retaining ring 25 to generate friction on the relative rotation on the input and output flywheel masses.
As will be appreciated, the rotational keying of the disc 26 to ring 25 and hence to output mass 12 and the keying of disc 27 to tubular extension 25 can be with or without lost circumferential motion so that the friction device can operate for all rotational movements of the input and output flywheel masses or only after a predetermined amount of relative rotational movement has taken place.
In accordance with the present invention the side plates 21 and 22 make contact at their outer peripheries 21a and 22a with the radially outer portion 18a of flange 18 and thus stabilise the flywheel against tipping of the input mass relative to the output mass due to flexing of the engine crankshaft etc. Similarly, in the arrangement shown in Figure 1 , the side plates 21 and 22 also contact the radially inner portion 18b of flange 18 at locations 21 b and 22b to further stabilise the flywheel masses against relative tipping.
Figure 4 shows a further form of twin mass flywheel in accordance with the present invention in which components of a similar function to those described above in relation to Figures 1 to 3 have been similarly numbered.
In Figure 4, the side plates 21 and 22 are riveted to output mass 12 via a rivet 30 which also includes a spacing portion 31 to hold the side plates 21 and 22 spaced apart. Inside the side plates a friction device 32 is provided (see Figure 6) which comprises a pair of friction discs 33 which are keyed at their outer peripheries within the radially inner portion of flange 18 and interleaved friction discs 34 which are keyed at their inner peripheries onto rivets 30. The friction device also includes a plastics friction disc 35 of L-shaped cross section having axial projections 36 which are keyed to flange 18 radially outboard of discs 33. A belleville spring 39 completes the friction device and provides the axial loading to ensure that the friction discs generate the necessary frictional force.
The keying of friction disc 35 to flange 18 is without any lost circumferential motion (see Figure 5) so that the low level of friction generated by friction disc 35 operates for all relative rotations of the input and output masses and provides a so-called idle rattle friction suppression of the twin mass flywheel. The keying of the discs 33 and 34 to their co-operating members 18 and 30 may be with or without lost motion in the circumferential sense (see lost motion 'x' as shown in Figure 5) so that the overall friction characteristics of the friction device can be tuned to the particular vehicle on which the twin mass flywheel is to be used.
Inner and outer added mass rings 24a and 24b respectively are rivetted to input mass 11 by rivets 19. In accordance with the present invention the outer peripheral portions 21a and 22a of the side plates 21 and 22 contact the radially outer portion 18a of flange 18 to resist tipping of the input and output masses of the flywheel due to flexing of the crankshaft etc. Also, at the inner periphery of the flange 18, the side plate portions 21b and 22b apply axial pressure to the discs 33 which are splined for rotation with flange 18 via the interleaved plates 34, the friction disc 35 and the belleville spring 39. This again tends to resist tipping of the flywheel masses.
The input and output masses are supported for relative rotation on a plain bearing 40 which is of L-shaped cross section and which itself is supported between an axially extending projection 15 on input mass 11 and a parallel axially extending projection 41 formed integrally with the output mass 12. The radially outwardly extending flange 42 on bearing 40 acts between the projections 15 and 41 to resist any axial movement of the masses towards each other.
The flywheel shown in figures 4 to 6 also includes a stop arrangement to limit the relative rotation of the flywheel masses 11 and 12. This stop arrangement is provided by radially inwardly extending projections 24c on outer added mass ring 24b which move in pressed axial recesses 22c in side plate 22 (see figure 5). Rotation is limited when projections 24c strike the sides 22d of recesses 22c. Typically this rotation is limited to 24 degrees in either direction (ie 48 degrees total relative rotation). The circumferential zones 22e of side plate 22 between the recesses 22c contact the flange 18 as does the entire zone 21a of side plate 21 to limit the tipping of the flywheel masses.
Referring to Figure 7, this shows a further variant of the twin mass flywheel shown in Figures 4 to 6 in which the bearing 40 is supported from a separate axially extending projection 45 which is bolted to input mass 11 by the same bolts which attach the twin mass flywheel to the vehicle crankshaft and which extend through bolt holes 11a. This construction is cheaper to produce and may also save weight.

Claims

1. A twin mass flywheel of the type described in which the other peripheries of the side plates remote from their connection with the other mass contact the flange on either side thereof to limit the tipping of the masses relative to each other during relative rotation.
2. A twin mass flywheel according to claim 1 in which the side plates also either contact the flange or apply axial pressure to a component rotatable with the flange at a location radially inboard of the spring means to lend further stabilise the masses against tipping.
3. A twin mass flywheel according to claim 1 or 2 in which a friction device acts between the masses to damp relative rotation.
4. A twin mass flywheel according to claim 3 in which the friction device is provided between the side plates adjacent the radially inner periphery of the flange.
5. A twin mass flywheel according to claim 4 in which the side plates only contact the flange to control tipping adjacent the radially outer periphery of the flange.
6. A twin mass flywheel according to claim 4 or 5 in which the friction device is of a multi-disc type with some discs keyed for rotation with the flange and other interleaved discs keyed for rotation with the output mass, the friction force being generated by a belleville spring which is also located between the side plates.
7. A twin mass flywheel according to claim 6 in which the friction device includes a low friction disc which forms part of the friction disc stack and which is keyed for rotation with either the flange or the output mass and which provides low friction damping of idle rattle.
8. A twin mass flywheel according to claim 7 in which the friction discs which are keyed for rotation with the output mass are keyed onto rivets which also secure the side plates to the output mass.
9. A twin mass flywheel according to any one of claims 3 to 8 in which the friction device includes lost motion in a circumferential sense so that the frictional damaging provided by the device varies with the relative rotation of the masses.
10. A twin mass flywheel according to any one of claims 1 to 9 in which stop means are provided to limit the relative rotation of the masses.
11. A twin mass flywheel according to claim 10 in which the stop means comprises abutment means on the input mass which operates between circumferentially spaced abutments provided on one or both side plates.
12. A twin mass flywheel according to claim 11 in which the circumferentially spaced abutments are formed in the radially outer periphery of at least one of the side plates as axial recesses into which abutment means on the flange extend, the portion of the radially outer periphery between the recesses contacts the flange to limit tipping.
13. A twin mass flywheel according to any one of claims 1 to 12 in which the masses are supported from each other for relative rotation by a plain bearing.
14. A twin mass flywheel according to claim 13 in which the plain bearing is located between tubular projections formed on the input and output masses respectively.
15. A twin mass flywheel according to claim 14 in which at least one tubular projection is formed separately from its associated mass and is secured thereto.
16. A twin mass flywheel of the type described constructed and arranged substantially as hereinbefore described with reference to and as shown in figures 1 to 3 or 4 to 6 or 7 of the accompanying drawings.
PCT/GB2003/005284 2002-12-06 2003-12-04 Twin mass flywheels WO2004053354A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP03782592A EP1567785A1 (en) 2002-12-06 2003-12-04 Twin mass flywheels
GB0510335A GB2410991B (en) 2002-12-06 2003-12-04 Twin mass flywheels
AU2003290227A AU2003290227A1 (en) 2002-12-06 2003-12-04 Twin mass flywheels

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0228462A GB0228462D0 (en) 2002-12-06 2002-12-06 Twin mass flywheels
GB0228462.8 2002-12-06

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WO2004053354A1 true WO2004053354A1 (en) 2004-06-24

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PCT/GB2003/005284 WO2004053354A1 (en) 2002-12-06 2003-12-04 Twin mass flywheels

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EP (1) EP1567785A1 (en)
AU (1) AU2003290227A1 (en)
GB (2) GB0228462D0 (en)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1707843A1 (en) * 2005-03-29 2006-10-04 Valeo Embrayages Double mass flywheel for vehicle
FR3059379A1 (en) * 2016-11-30 2018-06-01 Valeo Embrayages TORSION DAMPER HAVING FRICTION DEVICE AND TILT LIMITING DEVICE

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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US5617940A (en) * 1994-02-08 1997-04-08 Exedy Corporation Power transfer apparatus having a vibration dampening mechanism which provides structural support for the apparatus
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US6120380A (en) * 1983-11-15 2000-09-19 Luk Lamellen Und Kupplungsbau Gmbh Assembly for compensation of fluctuations of torque
WO2001011257A1 (en) * 1999-08-10 2001-02-15 Ap Tmf Limited Torsional vibration dampers
FR2823547A1 (en) * 2001-04-17 2002-10-18 Zf Sachs Ag Torsional vibration damper has driving and driven transmission components with torsion spring mounted between them, axially flexible coupling connecting components being mounted radially inside spring

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* Cited by examiner, † Cited by third party
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US4583959A (en) * 1982-09-16 1986-04-22 Kabushiki Kaisha Daikin Seisakusho Damper disc
US6120380A (en) * 1983-11-15 2000-09-19 Luk Lamellen Und Kupplungsbau Gmbh Assembly for compensation of fluctuations of torque
US5601492A (en) * 1993-10-15 1997-02-11 Fichtel & Sachs Ag Two mass flywheel for a motor vehicle transmission having a separate thrust bearing between the two masses
US5617940A (en) * 1994-02-08 1997-04-08 Exedy Corporation Power transfer apparatus having a vibration dampening mechanism which provides structural support for the apparatus
US5688177A (en) * 1994-12-07 1997-11-18 Fichtel & Sachs Ag Transmission system for a motor vehicle, the transmission system having a flywheel with two centrifugal masses
WO2001011257A1 (en) * 1999-08-10 2001-02-15 Ap Tmf Limited Torsional vibration dampers
FR2823547A1 (en) * 2001-04-17 2002-10-18 Zf Sachs Ag Torsional vibration damper has driving and driven transmission components with torsion spring mounted between them, axially flexible coupling connecting components being mounted radially inside spring

Cited By (3)

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Publication number Priority date Publication date Assignee Title
EP1707843A1 (en) * 2005-03-29 2006-10-04 Valeo Embrayages Double mass flywheel for vehicle
FR2883947A1 (en) * 2005-03-29 2006-10-06 Valeo Embrayages DOUBLE FLYWHEEL DAMPER FOR MOTOR VEHICLE
FR3059379A1 (en) * 2016-11-30 2018-06-01 Valeo Embrayages TORSION DAMPER HAVING FRICTION DEVICE AND TILT LIMITING DEVICE

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GB2410991A (en) 2005-08-17
GB0510335D0 (en) 2005-06-29
GB2410991B (en) 2006-03-29
EP1567785A1 (en) 2005-08-31
GB0228462D0 (en) 2003-01-08
AU2003290227A1 (en) 2004-06-30

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