From the Rolls-Royce experimental archive: a quarter of a million communications from Rolls-Royce, 1906 to 1960's. Documents from the Sir Henry Royce Memorial Foundation (SHRMF).
Patent specification for improvements in pivotal bearings, such as those used for the spring shackles of automobile vehicles.
| Identifier | ExFiles\Box 154\2\ scan0058 | |
| Date | 7th February 1931 | |
| Note.—The application for a Patent has become void. This print shows the Specification as it became open to public inspection under Section 91 (3) (a) of the Acts. Handwritten: 19454/37 Compressed Elastic Bearing PATENT SPECIFICATION Convention Date (Germany): Feb. 8, 1930. Application Date (in United Kingdom): Feb. 7, 1931. No. 3932/31. Complete not Accepted. COMPLETE SPECIFICATION. 383,274 COMPLETE SPECIFICATION 1 SHEET Improvements in Pivotal Bearings such as Used for the Spring Shackles of Automobile Vehicles. We, SOCIETE ANONYME DES ETABTS. REPUSSEAU & CIE., a French Company of 15 & 77, Rue Danton, Levallois-Perret, France, (Assignees of ROBERT BOSCH 5 AKTIENGESELLSCHAFT, a German Company of, 4, Militarstrasse, Stuttgart, Germany, do hereby declare the nature of this invention and in what manner the same is to be performed, to be particu- 10 larly described and ascertained in and by the following statement:— The present invention relates to improvements in pivotal bearings such as used for the spring shackles of auto- 15 mobile vehicles and more generally known as "silentbloc" bearings. It is known to use the molecular displacement of a resilient material, pressed between two double conically joined 20 sleeves to impose on it a considerable distortion of shape, for damping reciprocating motion, as for example the movements that occur in the spring suspension of motor vehicles. In this known construc- 25 tion the two cones serve the purpose of offering a resistance to axial displacement of the resilient buffer. Certain known constructions of pivotal joints including buffers of this type have 30 the disadvantage that the resilient intermediate member is of uniform thickness throughout or again is weakest at the place where the displacements arising from the reciprocating motions of the 35 sleeves are the greatest. On that account the resilient material is either overstressed at this place or the material of the intermediate buffer member is not efficiently utilized at the other places, if 40 it is so dimensioned that it is not too highly stressed at the place of greatest displacement. According to the present invention the double cones of a pivotal connection are 45 so inclined to each other that after being pressed in, the greatest wall strength of the resilient intermediate buffer member is at the place where the two double cones have their greatest diameter. The invention is more particularly de- 50 scribed with reference to the accompanying drawings which show two forms of construction, by way of example, and in which:— Figure 1 is a longitudinal section 55 through one form of construction. Figure 2 is an end diagrammatic view showing the angle deviations between the two sleeves in the construction according to Figure 1. 60 Figure 3 is a longitudinal section through a modified form of construction. The inner sleeve a of the pivotal bearing is conical in longitudinal section, its greatest external diameter being at the 65 centre. A rubber or the like resilient ring b is forced over this sleeve and internally tapered sleeves c and d which are held together by a casing e rolled over at its ends about such sleeves c, d.{John DeLooze - Company Secretary} 70 The external surface of the sleeve a and the internal surfaces of the sleeves c, d are so inclined towards each other that the wall strength of the resilient element b is greatest at f.{Mr Friese} 75 The smallest and greatest diameters g, and h respectively of the sleeve a or the smallest and greatest diameters i, k respectively of the sleeves c, d are repre- 80 sented in Figure 2 as circles g¹, h¹, i¹, k¹ respectively. When the inner sleeve a is firmly held and the outer sleeves c, d, are rotated through an angle α relatively to the inner sleeve a, the inner surface of the 85 rubber element remains stationary as a result of the high pressure exerted on this rubber element, whilst the outer surface is displaced with the cones c, d.{John DeLooze - Company Secretary} If the thickness of the rubber ring were uniform 90 (as was hitherto usual) the displacement between h¹ and k¹ would be considerably greater than the displacement between g¹ and i¹ and the rubber would accordingly be more highly stressed between h¹ and k¹. [Price 1/-] Fig. 1. Fig. 2. Fig. 3. Malby & Sons, Photo-Litho | ||