GB2151334A

GB2151334A - Clutch disc with torsional vibration damper

Info

Publication number: GB2151334A
Application number: GB08431346A
Authority: GB
Inventors: Hulmuth Weissenberger
Original assignee: Fichtel and Sachs AG
Current assignee: ZF Sachs AG
Priority date: 1983-12-13
Filing date: 1984-12-12
Publication date: 1985-07-17
Also published as: DE3344954A1; GB8431346D0; GB2151334B; FR2558226B1; FR2558226A1; DE3344954C2

Abstract

A clutch disc includes a torsional vibration damper with under-load 2 and idling 3 dampers in which a prefabricated unit consisting of hub and hub disc 23 of the idling damper is provided. Between the output part of the under-load damper 2 and the hub 20 there is provided a toothing 6 18, 19 with play in the circumferential direction. The internally situated cover plate 7 of the under-load damper is made with the appropriate larger toothing 22 so that it can be fitted over the toothing 19 of the hub. After the introduction of this cover plate 7 it is rotated through a specific amount in the circumferential direction and riveted 17. Thus this cover plate 7 can be utilised in relation to the toothing in the hub as axial guide. The other components which must be fitted from the same side are also correspondingly formed. Due to the separate formation of the 16 internally situated cover plate of the under-load damper and of the transmission component of the torque to the idling damper 3 it is possible to achieve a higher operational reliability and simpler fitting, compared with the prior art. <IMAGE>

Description

SPECIFICATION Clutch disc with torsional vibration damper The invention relates to a clutch disc with device for torsional vibration damping.

In a clutch disc known for example from Fed. German Patent Specification No.

1,680,049 the entraining of the cover plates of the idling damper takes place through axially protruding noses formed by cutting on the output part of the idling damper. For axial fixing between the under-load damper and the hub a divided, annular component is necessary which is secured with rivets. This divided component is necessary since hub and hub disc of the idling damper are produced as a pre-fabricated construction unit. This pre-fabricated construction unit. This pre-fabricated construction unit is distinguished especially by a specially operationally reliable connection between hub and hub disc. Thus the use of such a clutch disc becomes possible even for higher powers and greater diameters.

Now it is in the problem of the present invention, in clutch discs of the construction type according to classification, to achieve a facilitation of assembly-with simultaneous simplification of the individual parts. As many already existing individual parts as possible are here to be usable again.

In accordance with the invention this problem is solved by the feature of the Main Claim. Due to the configuration of the side disc, axially adjacent to the idling damper, of the second under-load damper, in accordance with the invention this disc can be installed over the hub toothing, with the hub disc for the idling damper previously fitted, and secured after turning through about half of the tooth pitch. Thus the axial guidance of the under-load damper in relation to the hub is ensured and additionally a stable securing of both side discs on the coupling or output part of the under-load damper is possible. The complicated introduction of a divided ring according to the prior art can thus be omitted and this two-part ring can thus be eliminated.

The rotation-fast connection between the under-load damper and the side discs of the idling damper takes place preferably by way of a sheet metal part of annular disc form having axially protruding noses which serve for engagement in corresponding apertures in the side discs. In this case this sheet metal part is rivetted together with the output part and the side discs of the under-load damper.

This separately produced sheet metal part is considerably simpler to produce than the output part according to the prior art.

The sheet metal part is preferably formed so that-like the internally toothed side disc of the under-load damper-it is installed over the hub toothing. Moreover the correspondingly formed internal circumference of this sheet metal part forms an axial abutment for the internally situated side disc of the idling damper.

The invention will next be explained in greater detail by reference to an example of embodiment. Individually: Figure 1 shows the longitudinal section through a clutch disc with under-load and idling dampers, for a motor vehicle friction disc clutch, Figure 2 shows the section ll-ll according to Fig. 1, Figure 3 shows the partial view of one of the two cover plates of the idling damper and of the sheet metal part, Figure 4 shows the view of the pre-fabricated hub with hub disc of the idling damper, seen in the direction "X".

Fig. 1 shows the longitudinal section through a clutch disc 1 with an under-load damper 2 and an idling damper 3. The hub 20 is mounted with its toothing 21 fast in rotation but axially displaceably on a gear shaft (not shown). The under-load damper 2 is mounted on the hub 20. This damper---consi- dered from radially outside--consists of the lining carrier 1 5 with the friction linings 4, of intermediate discs 1 6 connected fast with the lining carrier 15, of friction rings 9 arranged to both sides of the intermediate discs 1 6 and of side discs or cover plates 6 and 7 arranged to both sides of the friction rings 9, windows for the reception of torsion springs 5 being arranged in the cover plates 6 and 7, in the lining carrier 15, in the intermediate discs 1 6 and in the friction rings 9. Furthermore a coupling or output part 8 of the underload damper 2 is arranged which is connected by through-passing rivets 1 7 firmly with the two cover plates 6 and 7. The output part 8 has an internal toothing 1 8 which is arranged with play in the circumferential direction on an external toothing 1 9 of the hub 20. This play between the two toothings 1 8 and 1 9 constitutes the range of effect of the idling damper 3. The idling damper 3 is arranged laterally beside the under-load damper 2. Its hub disc 23 is arranged fast on the hub 20.

To both sides of the hub disc 23 there are arranged side discs or cover plates 25 and 26 which accommodate torsion springs 24 for the idling range in appropriate windows in combination with windows 28 in the hub disc 23. The rotation-fast connection of the underload damper 2 takes place by way of a sheet metal part 33 which is arranged between the idling damper 3 and the cover plate 7 of the under-load damper 2. It is held together with the cover plate 7 by the through-passing rivets 1 7. It comprises axially bent-over noses 34 which engage in corresponding apertures 32 of the cover plates 25 and 26. To the exterior the idling damper 3 is closed off by a cover 27.Furthermore the rivets 1 7 hold friction springs 11 which extend substantially radially, are angled off axially at their outer ends and extend through openings 1 2 in the cover plate 7 in the direction towards the intermediate discs 16. They rest under initial spring stress upon a pressure plate 10 which is axially displaceably arranged between the cover plate 7 and the one of the friction rings 9. This pressure plate 10 is here connected fast in rotation with the cover plate 7, namely by radially externally arranged noses 1 3 which engage in apertures 14 of the cover plate 7.

At this point the function of this clutch disc is to be discussed, merely briefly, since it does not differ from the function of the prior art. On introduction of a torque by way of the friction linings 4 firstly a twisting of the under-load damper 2, to be regarded as a rigid component, takes place. The entraining of the cover plates 25 and 26 of the idling damper 3 takes place through the cover plates 6 and 7 and the sheet metal part 33. Thus these cover plates 25 and 26 load the torsion springs 24 in relation to the stationary hub 20 and thus the stationary hub disc 23.After the play between the hub toothing 1 9 and the internal toothing 1 8 of the output part 8 of the under-load damper 2 has been taken up, a bridging-over of the idling damper 3 takes place, while at the same time a relative rotation takes place between the input parts 4, 15, 1 6 of the under-load damper 2 and its output parts 6, 7, 8, 10. This rotation takes place against the force of the torsion springs 5 and against the friction force of the friction rings 9.

The formation of the individual parts of the clutch disc 1 renders simple assembly possible. The basis will be adopted that for various reasons the hub 20 and the hub disc 23 are present as a prefabricated construction unit. Thus from the direction X only the torsion springs 24, the externally situated cover plate 26 and the lid 27 can be fitted.

All other components must be fitted from the opposite side over the external toothing 1 9 of the hub 20. This is possible because according to Fig. 2-Section Il-li--the cover plate 7 of the under-load damper 2 is provided with a toothing 22 which is made slightly larger than the external toothing 1 9 of the hub 20, while the internal diameter 29 of the cover plate 7 is also made larger than the groove bottom diameter 30 of the external toothing 1 9. Thus the cover plate 7 can be introduced over the toothing 19. Then a rotation takes place by about half of the pitch T of the toothing 18, 19, that is by the amount t, whereby the cover plate 7 functions as axial guide in the direction of the arrow X, in relation to the toothing 1 9 of the hub 20.

However the components 33 and 25 must previously be fitted-likewise over the toothing 1 9. In this connection reference should be made to Fig. 1 in combination with Fig. 3.

The sheet metal part 33, which is only partially represented in Fig. 3, has an internal diameter 35 which is made larger than the crown circle diameter 37 of the toothing 1 9.

On the other hand however the internal diameter 35 is made smaller than the external diameter 36 of the two cover plates 25 and 26. Thus while the sheet metal part 33 can be fitted from the side of the under-load damper 2, in the fitted condition it constitutes an axial fixing for the inwardly situated cover plate 25 of the idling damper 3. From Fig. 3 there may further be seen the arrangement of the noses 34 of the sheet metal part 33 which engage in apertures 32 of the cover plates 25 and 26. Furthermore the windows 31 are represented in which the torsion springs 24 are accommodated.

After the introduction of the parts 25, 33 and 7 over the toothing 1 9 these can be connected together with the parts 11, 10, 9, 16, 6 by the through-passing rivets 1 7. The insertion of the torsion springs 24 and the application of the cover plate 26 and the lid 27 take place as final assembly step.

Finally in Fig. 4 the view X of the hub 20 with the hub disc 23 is reproduced. It can be seen there that the windows 28 of the hub disc 23 for the torsion springs 24 are arranged exactly between the teeth of the external toothing 1 9. Both the windows 28 and the teeth of the toothing 1 9 have the same pitch T.

As shown best by Fig. 1, the torsion springs 24 of the idling damper 3 are arranged radially within a circle on which the rivets 1 7 are arranged. In this way no additional axial space is required for the heads of the rivets 1 7. The noses 34 of the sheet metal part 33 of annular disc form are arranged inthe region of its internal circumference and guide the cover plates 25, 26 of the idling damper on their external circumference.

The windows 31 in the cover plates 25, 26 and the windows 28 in the hub disc 23 are arranged in the same angle pattern as the toothing 19 of the hub 20. The windows 31 of the cover plate 25 axially arranged between the hub disc 23 and the cover plate 7 are open towards the internal circumference of the cover plate 25 and form a toothing complementary to the toothing 1 9 of the hub.

Thus the cover plate 25 can be pushed, in the assembly of the clutch disc, over the toothing 1 9 of the hub. In the assembled condition the windows 31 of the cover plate 25 are radially inwardly limited by the outer surface of the hub 20 for the guidance of the torsion springs 24.

In the example of embodiment as illustrated the two cover plates 6, 7 of the under-load damper 2 rest on the axial ends of the toothing 1 9 of the hub 20. The cover plate 6 axially remote from the idling damper 3 can alternatively be fixed axially to an axial shoul der formed elsewhere on the hub 20. Furthermore friction damper devices of the idling damper 3 are not represented in the Figures.

Such friction damper devices can however be present.

Claims

1. Clutch disc for a friction disc clutch, comprising: a) a hub (20) having two axial stop shoulders facing away axially from one another and an axially accessible external toothing (19), the axial end faces of which form at least one of the two stop shoulders, b) a friction lining carrier (15) of annular disc form enclosing the hub (20), c) an under-load vibration damper (2) having a coupling part (8) which has a countertoothing (18) engaging with rotational play in the external toothing (19) of the hub (20), with two first side discs (6, 7) arranged on axially opposite sides of the friction lining carrier (1 5) and of the coupling part (8), secured on the coupling part (8) and rotatable therewith in relation to the friction lining carrier (15), which side discs are axially fixed to the stop shoulders, and with a plurality of under-load damping springs (5) held in windows of the friction lining carrier (15) and of the first side discs (6, 7) and stressable in the relative rotation of the friction lining carrier (15) and of the first side discs (6, 7), d) an idling vibration damper (3) having a hub disc (23) secured on the hub (20) on the axial side of the end face of the external toothing (1 9) which forms the stop shoulder with second side discs (25, 26) of annular disc form arranged on axially opposite sides of the hub disc (23) and rotatable in relation to the hub disc (23), which side discs are connected fast in rotation with the axially adjacent first side disc (7), and with at least one idling damping spring (24) held in windows (28, 31) of the hub disc (23) and of the second side discs (25, 26) and stressable in the relative rotation of the hub disc (23) and of the second side discs (25, 26), characterised in that the first side disc (7) axially adjacent to the hub disc (23) comprises on its internal circumference a complementary toothing (22) suitable for engagement in the external toothing (19) of the hub (20) and is secured to the coupling part (8) in such a way that the complementary toothing (22) is axially fixed to the axial end face, forming the stop shoulder, of the external toothing (19), with angular offsetting in relation to the external toothing of the hub.

2. Clutch disc according to Claim 1, characterised in that the windows (28, 31) of the hub flange (23) and of the second side discs (25, 26) are arranged in the angle pattern of the external toothing (19) of the hub (20) and in that the second side disc (25) axially adjacent to the under-load vibration damper (2) has on its internal circumference a complementary toothing suitable for engagement in the external toothing (19), and forming the windows (31).

3. Clutch disc according to Claim 1 or 2, characterised in that the coupling part (8), the two first side discs (6, 7) and an annular disc (33) arranged axially between the first side disc (7), which comprises the toothing (22), and the idling vibration damper (3) are secured to one another by common rivets (17) and in that from the annular disc (33) noses (34) protrude axially to the idling vibration damper (3), which noses engage in apertures (32) of the two second side discs (25, 26) and connect the second side discs (25, 26) fast in rotation with the first side discs (6, 7) and the coupling part (8).

4. Clutch disc according to Claim 3, characterised in that the noses (34) are formed in the region of the internal circumference of the annular disc (33) and in that the rivets (17) are arranged radially outside the region limited by the noses (34).

5. Clutch disc according to Claim 3 or 4, characterised in that the idling damping springs (24) are arranged radially within the region limited by the noses (34).

6. Clutch disc according to one of Claims 3 to 5, characterised in that the noses (34) engage in apertures (32), which are open to the external circumference, of the second side discs (25, 26).

7. Clutch disc according to one of Claims 3 to 6, characterised in that the internal diameter of the annular disc (33) is smaller than the external diameter of the second side disc (25) axially adjacent to the under-load vibration damper (2), but larger than the crown circle diameter of the external toothing (19) of the hub (20).

8. Clutch disc for a friction disc clutch, substantially as herein described with reference to the accompanying drawings.