WO2000075528A2 - Amortisseur de torsion pour embrayage a friction, en particulier pour vehicule automobile - Google Patents
Amortisseur de torsion pour embrayage a friction, en particulier pour vehicule automobile Download PDFInfo
- Publication number
- WO2000075528A2 WO2000075528A2 PCT/FR2000/001521 FR0001521W WO0075528A2 WO 2000075528 A2 WO2000075528 A2 WO 2000075528A2 FR 0001521 W FR0001521 W FR 0001521W WO 0075528 A2 WO0075528 A2 WO 0075528A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- damper
- shock absorber
- guide
- main
- washer
- Prior art date
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
-
- 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
- F16F15/123—Wound springs
- F16F15/1238—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub
-
- 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
- F16F15/123—Wound springs
- F16F15/12313—Wound springs characterised by the dimension or shape of spring-containing windows
Definitions
- the invention relates to a torsional damper for a friction clutch, in particular for a motor vehicle and in particular for an industrial vehicle.
- a torsional damper of this type comprises an input element (such as a disc carrying friction linings) connected by a main damper and by a pre-damper to an output element (such as a solidizable hub in rotation with a driven shaft, for example the input shaft of a gearbox).
- an input element such as a disc carrying friction linings
- an output element such as a solidizable hub in rotation with a driven shaft, for example the input shaft of a gearbox.
- the main damper comprises an annular web integral with the input element and rotatably mounted on a cylindrical ring which meshes with the output element with a predetermined circumferential play, two guide washers integral with the cylindrical ring and s' extending on either side of the annular web, and elastic members with circumferential action, such as helical springs, mounted in housings of the annular web and guide washers.
- Friction washers are generally arranged between the annular web and at least one guide washer for damping vibrations and oscillations.
- the pre-damper for its part, comprises another annular web integral in rotation with the outlet element, at least one guide washer which extends between the main damper and the annular web of the pre-damper, and elastic members with circumferential action such as helical springs mounted in housings of the second annular web and of the pre-damper guide washer.
- Friction washers are generally arranged between the web and the guide washer to dampen vibrations and oscillations.
- the main damper and the input element constitute a sub-assembly in which the guide washers are fixed to the aforementioned cylindrical ring by welding, and the pre-damper constitutes a another sub-assembly mounted on the output element (a cylindrical hub) by crimping the annular web on the hub, the cylindrical ring of the main damper serving as a stop for the pre-damper for its axial positioning on the hub.
- a pre-damper guide washer is applied to a straight end face of the cylindrical ring and has pins parallel to the axis of rotation engaged in blind holes in this end face of the cylindrical ring for driving in rotation of this pre-damper guide washer by the cylindrical ring of the main damper.
- the invention provides, for this purpose, a torsional damper for a friction clutch, in particular for a motor vehicle, comprising an input element connected by a main damper and a pre-damper to an output element, the main damper comprising a annular web integral with the input element and rotatably mounted on a cylindrical ring which meshes with the output element with a predetermined circumferential clearance, two guide washers integral with the cylindrical ring and extending on either side other of the annular web, elastic circumferential members mounted in housings of the annular web and guide washers, the pre-damper comprising a second annular web integral in rotation with the outlet element, at least one guide washer extending between the main shock absorber and the second annular web, circumferential elastic members mounted in housings ents of the second annular web and of the pre-damper guide washer, and means for axial positioning and rotational drive of said pre-damper guide washer by the main damper, characterized in that a guide washer of the main damper is in contact with the a
- the bosses or stampings formed on one of the adjacent guide washers of the main shock absorber and of the pre-shock absorber make it possible to offset axially certain parts of this guide washer to a sufficient extent that the means for fixing the guide washers of the 'main damper on the cylindrical ring are not a discomfort, even if they are axially projecting on these guide washers. Consequently, the guide washers of the main damper can be fixed to the cylindrical ring by rivets whose heads are not embedded and form protrusions on the guide washer located on the side of the pre-damper. Of course, these guide washers can also be fixed for welding or crimping on the cylindrical ring.
- These guide washers may extend radially more inwardly relative to the rotation drive means, which do not affect the cylindrical ring and do not interfere with it due to the presence of bosses.
- the guide ring is therefore simplified and forms a spacer between the guide washers by being narrower at this level than that of the aforementioned document US-A-5,366,057.
- the bosses are formed on the guide ring of the main shock absorber adjacent to the guide ring of the pre-shock absorber and protrude axially from the side of the pre-shock absorber, at the level of the drive means.
- rotation of the pre-damper guide washer comprise pins or fingers fixed on one of the two aforementioned guide washers and extending axially in holes or notches in the other of these two guide washers so that the solution is economical because the holes or notches are easier to make than the blind holes in the guide ring. This takes advantage of the guide washers.
- the aforementioned pins or fingers are rivets fixed to the guide ring of the pre-shock absorber and extend in notches formed in the bosses of the guide ring of the main shock absorber.
- the means for driving the pre-damper in rotation are thus offset axially with respect to the fixing rivets of the guide washers of the main damper and the abovementioned bosses participate in the axial positioning of the pre-damper and in its drive in rotation.
- the bosses are formed in the pre-damper guide washer, at the level of the means for driving the pre-damper in rotation by the guide ring of the main damper, which makes it possible to avoid any interference between the pre-damper guide washer and the heads of the fixing rivets of the main damper guide washers.
- the pre-damper comprises two guide washers which extend on either side of the above-mentioned second annular web and which are secured in rotation to one another by rivets or the like.
- the rivets which connect the pre-damper guide washers are approximately the same distance from the axis of rotation as the fixing rivets of the pre-damper washers. guide of the main shock absorber and are advantageously mounted in stamped areas of the pre-shock absorber guide washers.
- the invention makes it possible to simplify the structure and assembly of a torsion damper of the aforementioned type without increasing its axial size, and to reduce its cost price.
- FIG. 1 is a schematic front view, partially broken away, of a torsion damper according to the invention
- Figure 2 is an axial sectional view along the line II-II of Figure 1;
- Figure 3 is a half view in axial section of an alternative embodiment of the invention.
- the torsion damper shown in Figures 1 and 2 is intended to connect an input element, such as a friction disc 10 of which only the internal periphery has been shown in Figure 2, to an output element, such as 'A cylindrical hub 12 whose internal surface has longitudinal grooves 14 for securing in rotation with a driven shaft to rotate it about an axis 16 of rotation which is also the axis of the driving shaft.
- the torsion damper is here intended to equip a motor vehicle friction clutch.
- This clutch comprises a pressure and reaction plate calibrated in rotation on the shaft leading to the crankshaft of the internal combustion engine of the vehicle in this case.
- the clutch axis is axis 16.
- the disc 10 carries two friction linings intended to be disengageably clamped between the pressure and reaction plates, the driven shaft being the drive shaft. gearbox input.
- the torsional damper comprises a main damper and a pre-damper, which are designed for damping vibrations and torque oscillations for different loads between the input element 10 and the output element 12.
- the main damper comprises, in this exemplary embodiment, an annular veil 18 centered on the axis of rotation and integral with the input element 10, this annular veil 18 being rotatably mounted around a cylindrical ring 20 which surrounds the hub 12 and which has an internal peripheral surface formed with an internal toothing 22 which meshes, with a predetermined circumferential clearance, with an external toothing 24 of the hub 12.
- Two guide washers 26 are fixed on the end faces of the ring 20 and extend on either side of the annular web 18 substantially as far as the internal periphery of the input element 10.
- Housing here in the form of windows 28 and 30, are formed opposite in the guide washers 26 and in the annular web 18 respectively, to receive elastic members with circumferential action (here helical springs 32 mounted concentrically) so as to allow a relative angular movement between the annular web 18 and the guide washers 26 with an elastic return force towards an equilibrium position; friction washers 34 and 36 being mounted at the outer periphery of the cylindrical ring 20 between the annular web 18 and the guide washers 26.
- a Belleville washer (not referenced) is interposed axially between the web 18 and the washer 36 to urge the washer 36 in contact with one of the guide washers 26 and tighten the friction washer 34 between the other guide washer 26 and the web 18.
- the washer 36 has axial tabs engaged in a complementary manner in holes in the web 18 for rotationally connecting the washer 36 with the web 18.
- the housings 28, 30 may consist of stampings made in the washers 26 as in FIG. 1 of document US-A-5, 366, 057 and / or in notches open towards the outside made in the web. .
- the guide washers 26 of the main damper are fixed to the lateral end faces of the ring 20 by rivets 38, six in number in the example shown, which are angularly distributed uniformly around the axis 16 and the heads 40 of which project from the guide washers 26.
- the pre-damper is axially juxtaposed with the main damper and comprises an annular web 42 integral in rotation with the hub 12, two guide washers 44 which extend on either side of the web 42 and which are fixedly connected to one the other by rivets 46 and elastic members with circumferential action, such as helical springs 48 having a stiffness much less than that of the springs 32 of the main damper, the springs 48 being mounted, like the springs of the damper main, in housings or windows formed opposite in the guide washers 44 and in the annular web 42.
- Friction washers 50 are interposed between the annular web 42 and the guide washers 44 of the pre-damper.
- the annular web 42 of the pre-damper is secured in rotation with the hub 12 by force fitting on an axial end of the toothing 24 of the hub and is wedged in translation on the hub by split rings, by welding or by any other means.
- the main damper constitutes a sub-assembly which, by the cylindrical ring 20, is mounted in translation on the end of the hub opposite to that which receives the preamortor.
- a retaining member, such as a split ring 52 is mounted on the end of the hub which receives the main damper, and is associated with timing rings.
- the main damper is thus wedged in translation by the pre-damper in one direction and by the ring 52 in the other direction.
- an elastic washer and / or a friction washer In this position, the guide washer 26 of the main shock absorber, which is located on the side of the pre-shock absorber, is supported on a guide washer 44 of the pre-shock absorber, which makes it possible to determine an axial position of the pre-shock absorber on the hub and also a good perpendicularity of the annular veil 42 and the guide washers 44 of this pre-damper relative to the axis of rotation 16.
- the veil 42 has on its internal periphery an internal toothing meshing without play with the toothing 24 of 12 of reduced height at this location for the formation of a shoulder making it possible to axially wedge the web 42 of the pre-damper.
- the web 42 is wedged by material creep from the axial end of the toothing 24 leading to crimping.
- a circlip engaged in a groove in the hub 12, replaces the crimping.
- welding is carried out.
- Rivets 54 fixed on the guide washer 44 of the pre-damper which is supported on the guide washer 26 of the main damper, extend in a complementary manner in notches or indentations 56 of the internal periphery of this guide washer, and constitute members for rotating the guide washers 44 of the pre-damper by the guide washer 26 of the main damper.
- the notches 56 are formed in portions 58 of the guide washer 26 which are axially spaced from the cylindrical ring 20 to axially offset the pre-damper relative to the main damper, sufficiently to avoid any interference with the heads 40 of the rivets for fixing the guide washers 26 to the ring 20.
- these offset parts of the guide washer 26 are bosses 58 having an approximately semicircular general outline, which project from the side of the pre-damper.
- these bosses 58 are three in number and are distributed at 120 ° from one another around the axis 16.
- the two guide washers 26 of the main damper are identical for reasons of standardization, the bosses 58 of the guide washer 26 located on the side opposite to the pre-shock absorber having no function.
- the notches 56 are formed centrally in the bosses 58 and are open towards the inside. The notches have a semi-circular shape for engagement of the heads of the rivets 54 and this, in a complementary manner so that the guide washer 44 of the preamortor is linked in rotation by cooperation of shapes to the adjacent guide washer 26 of the main shock absorber.
- the heads of the rivets 54 are in the form of cylindrical pins engaged in a complementary manner in the notches 56. Thanks to these bosses 58, the guide washer 44 of the pre-damper which is applied to the guide washer 26 of the main damper, can extend in a plane perpendicular to the axis 16 coming close to the head 40 rivets 38, this guide washer 44, however, including stampings 60 in the fastening zones of the above-mentioned rivets 46, so that the heads of these rivets do not protrude from the plane of the guide washer 44 and come substantially flush with the plane defined by the heads 40 of the rivets 38. As can be seen in FIG. 1, the various rivets 38, 46, 54 are distributed angularly around the axis of rotation 16.
- the rivets 54 are installed circumferentially between two rivets 38 consecutive ( Figure 1) and the same is true of the rivets 46.
- the rivets 38 and 46 are implanted generally on the same median circumference, while the rivets 54 are implanted on a circumference of media diameter n neighbor here, slightly lower than that of the rivets 38, 66 ( Figure 1), so that the rivets 38 and 54 are approximately the same distance from the axis of rotation 16.
- the guide washers of the main damper extend radially below the rivets 54.
- the presence of the rivets 38 is not compulsory because the guide washers 26 can be fixed by welding or crimping on the ring 20.
- the structures can be reversed.
- the rivets 54 can be fixed to the washer 26 and penetrate into holes in the washer 44.
- the head of the rivets can be of rectangular section and thus form fingers.
- the teeth 22, 24 come into abutment and the pre-damper behaves like a rigid member, and the torque oscillations are absorbed by the springs 32 of the main damper and damped by the friction washers 34, 36 until the main damper is itself in abutment and behaves like a rigid member.
- the bosses 58 of the guide washer (s) 26 of the main shock absorber are eliminated and bosses 62 of substantially semi-spherical shape are formed on the guide washer 44 of the pre-shock absorber, at level of the rivets 54 for driving the guide washer 44 of the pre-damper by the guide washer 26 of the main damper. These bosses 62 protrude towards the main damper and come into contact with the guide washer 26, so that the heads 40 of the rivets 38 do not abut on the guide washer 44 of the pre-damper.
- the rivets 54 are fixed on the guide washer 44 and extend into notches in the guide washer 26. Thanks to the invention, the cylindrical ring 20 is not used for the rotary drive of the pre-shock absorber and use is made of the guide ring of the main shock absorber.
- the guide washers 26 are identical here for reasons of standardization. Of course the washer 26 furthest from the pre-damper can be devoid of bosses.
- the guide washers 26 of the main damper comprise an enlarged annular zone 64 projecting outwards relative to the external periphery of the washer 26, preferably substantially toric which allows the circumferential movement of the means 66 (in general of the rivets) for fixing the disc 10 to the annular web 18, and in which the windows 28 for housing the springs 32 are formed.
- Each window 28 includes an eyelet 68 stamped outwards, preferably in the form of a torus eccentric relative to the annular zone 64, making it possible to retain the spring 32 in the window 28.
- the ends of the eyelet 68 serve to guide the spring 32, and the middle part of the eyecup is moved away from the corresponding part of the spring.
- the toroidal stamping forming the eyecup 68 can end with a straight generator 70.
- a strike can be made on the eyecup as indicated in dotted lines to reduce the axial size.
- a rounded clearance 72 can advantageously be formed at each end of the eyecup 68 in its connection to the annular zone 64 to avoid blocking of the spring 32 at this location and the appearance of cracks when the stamping of the eyelet connected by folds 168 to the annular zone 64 extended towards the center by a zone 164 projecting inwards, in the direction of the web 18, to serve as support for the internal springs, knowing that the springs 32 are of the concentric type , an outer spring surrounding the inner spring as shown in Figure 2.
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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
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10081749.1T DE10081749B3 (de) | 1999-06-04 | 2000-05-31 | Torsionsdämpfer für eine Reibungskupplung, insbesondere für Kraftfahrzeuge |
BRPI0006631-1A BR0006631B1 (pt) | 1999-06-04 | 2000-05-31 | amortecedor de torção para embreagem de fricção. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9907113A FR2794505B1 (fr) | 1999-06-04 | 1999-06-04 | Amortisseur de torsion pour embrayage a friction, en particulier pour vehicule automobile |
FR99/07113 | 1999-06-04 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2000075528A2 true WO2000075528A2 (fr) | 2000-12-14 |
WO2000075528A3 WO2000075528A3 (fr) | 2003-11-13 |
Family
ID=9546422
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2000/001521 WO2000075528A2 (fr) | 1999-06-04 | 2000-05-31 | Amortisseur de torsion pour embrayage a friction, en particulier pour vehicule automobile |
Country Status (5)
Country | Link |
---|---|
KR (1) | KR100652887B1 (fr) |
BR (1) | BR0006631B1 (fr) |
DE (1) | DE10081749B3 (fr) |
FR (1) | FR2794505B1 (fr) |
WO (1) | WO2000075528A2 (fr) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3013089B1 (fr) | 2013-11-12 | 2017-04-07 | Valeo Embrayages | Support pour dispositif d'amortissement pour systeme de transmission de vehicule |
FR3023340B1 (fr) * | 2014-07-04 | 2017-11-24 | Valeo Embrayages | Amortisseur de torsion pour systeme de transmission de vehicule |
FR3072593B1 (fr) * | 2017-10-23 | 2020-11-20 | Valeo Embrayages | Amortisseur de torsion et procede associe |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3414101A (en) * | 1965-11-20 | 1968-12-03 | Fichtel & Sachs Ag | Driven clutch plate with flexible center |
US4433771A (en) * | 1980-07-15 | 1984-02-28 | Valeo S.A. | Torsion damping device for a clutch plate |
GB2183790A (en) * | 1985-11-30 | 1987-06-10 | Fichtel & Sachs Ag | Clutch assembly for a motor vehicle friction clutch |
US5000304A (en) * | 1987-12-18 | 1991-03-19 | Fichtel & Sachs Ag | Clutch disc |
EP0732525A1 (fr) * | 1995-03-14 | 1996-09-18 | Valeo | Amortisseur de torsion à préamortisseur |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2688841B1 (fr) * | 1992-03-19 | 1998-03-13 | Valeo | Amortisseur de torsion, notamment friction d'embrayage, pour vehicule automobile. |
FR2689191B1 (fr) | 1992-03-26 | 1998-04-10 | Valeo | Friction d'embrayage, notamment pour vehicule industriel. |
FR2736111B1 (fr) * | 1995-06-29 | 1997-09-05 | Valeo | Dispositif amortisseur de torsion |
-
1999
- 1999-06-04 FR FR9907113A patent/FR2794505B1/fr not_active Expired - Lifetime
-
2000
- 2000-05-31 KR KR1020017001473A patent/KR100652887B1/ko active IP Right Grant
- 2000-05-31 WO PCT/FR2000/001521 patent/WO2000075528A2/fr active IP Right Grant
- 2000-05-31 DE DE10081749.1T patent/DE10081749B3/de not_active Expired - Fee Related
- 2000-05-31 BR BRPI0006631-1A patent/BR0006631B1/pt not_active IP Right Cessation
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3414101A (en) * | 1965-11-20 | 1968-12-03 | Fichtel & Sachs Ag | Driven clutch plate with flexible center |
US4433771A (en) * | 1980-07-15 | 1984-02-28 | Valeo S.A. | Torsion damping device for a clutch plate |
GB2183790A (en) * | 1985-11-30 | 1987-06-10 | Fichtel & Sachs Ag | Clutch assembly for a motor vehicle friction clutch |
US5000304A (en) * | 1987-12-18 | 1991-03-19 | Fichtel & Sachs Ag | Clutch disc |
EP0732525A1 (fr) * | 1995-03-14 | 1996-09-18 | Valeo | Amortisseur de torsion à préamortisseur |
Also Published As
Publication number | Publication date |
---|---|
DE10081749B3 (de) | 2018-02-15 |
DE10081749T1 (de) | 2001-08-30 |
KR20010079609A (ko) | 2001-08-22 |
KR100652887B1 (ko) | 2006-12-01 |
BR0006631A (pt) | 2001-05-02 |
FR2794505A1 (fr) | 2000-12-08 |
WO2000075528A3 (fr) | 2003-11-13 |
BR0006631B1 (pt) | 2009-08-11 |
FR2794505B1 (fr) | 2001-07-13 |
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