4696 4700.output

* GB785103 (A)

Description: GB785103 (A)

No title available

Description of GB785103 (A)

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J: a PATENT SPECIFICATION Date of Application and filing Complete Specification: January 19, 1956. Application made in Austria on January 20, 1955 78,103 No 1894/56 Application made in Austria on November 11, 1955 Complete Specification Published: October 23, 1957 Index at acceptance:-Class 59, A 5 (G:H). International Classification:-BO 2 c. COMPLETE SPECIFICATION Improvements in and relating to Disc Mills I, FRANZ ZWINZ, of Austrian Nationality, of 4, Beethovengasse, Neunkirchen, Austria, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention relates to disc mills for material of all kinds,

particularly for use on farms where fibrous material is to be ground. Such mills comprise a pair of discs in the form of hollow truncated cones rotating relatively to each other Conveniently the disc which is adjacent to the feed pipe for the mill is stationary and has a central inlet opening for the material to be ground. For such mills, grinding discs have been disclosed of the type in which the grinding means cooperating with those of the associated disc are arranged on the base surface of the disc in three successive zones from the iriner periphery of the disc to the outer rim thereof In a manner known per se these grinding means may comprise, for example, chopping teeth as comminuating members, then tearing teeth, which are disposed in the central portion of the disc and consist of rib members which control the feed of the material to be ground and have also a comminuting action, and finally discharge grooves formed as fine grinding means in the outer rim portion of the disc A feature common to all known grinding discs resides in that the grinding means are regularly spaced and of uniform shape In the known grind. ing discs the material is comminuated by the chopping teeth and is cut and crushed by the tearing teeth, whereafter is passes through the fine grinding zone and is delivered in ground form at the outer periphery of the disc These grinding discs have proved satisfactory for fruit, bulbs, maize, cereals and the like, but not for fibrous material such as straw, hay, green food and the like, particularly when it is wet; such material will not be lPrice 3 s 6 d 1 comminuted at all in the mill or will leave it in an unevenly comminuted condition and with many long-fibrous parts. According to the invention there is provided a disc mill for material of all kinds, 50 particularly for fibrous material, with a stationary disc and a rotary disc each in the form of a hollow truncated cone and having grinding means disposed on the base surface of the disc in three zones succeeding each 55 other from the central portion of the disc to the outer rim thereof, the grinding means in each zone being irregularly spaced and differing from each other and from those in another zone in depth, width and/or configura 60 tion. Extensive tests have shown that the irregularity and unevenjness of the grinding means of each grinding disc is the prime cause of the observed advantages of a mill equipped 65 with discs according to the invention. An explanation of the surprising effect achievable according to the invention may be based on the fact that the irregularity and unevenness of the grinding means imparts a cer 70 tain turbulent motion to the material between the two discs, that is the material may also be moved from any point of the disc towards its centre instead of only from the centre outwards For that reason the grinding cycle is 75

irregular and the actual grinding operation is interrupted by longer or shorter intervals. Moreover, a large number of grooves and depressions extending substantially transversely to the discharge direction of the material will 80 produce a multiplied cutting action on the material, which moves continuously along the cutting edges thus formed to render the grinding disc eminently suitable particularly for long-fibrous material Hay, maize, with cobs 85 and leaves, clover, green food, straw and green leaves whether wet or dry, can be ground to controllable particle sizes in a single pass through the mill owing to the repeated passage over the uneven cutting edges 90 785,103 so that they can be fully digested and utilized by the digestive systems of animals. Specific embodiments of the invention will now be described, by way of example with reference to the accompanying drawings, in which:Figures 1 and 2 are plan views of the stationary and rotary grinding discs, respectively. Figure 3 is a sectional view of the discs taken on the lines 1-II in Figures 1 and 2, and showing the discs in working engagement. The broken lines indicate the cross-section on lines IIJ-HT' in Figures 1 and 2. J 5 Figure 4 is an enlarged plan view of the inner surface of a disc, and Figures 5 and 6 respectively are sectional views taken on lines V-V and VI-VI of Figure 4. Figure 7 is a partly sectional elevation of a modification of the grinding discs. Figure 8 is a top plan view of the central portion of the rotary disc shown in Figure 7, and Figure 9 is a sectional view taken along line IX-IX of Figure 8 showing a detail. The inner grinding zone of the grinding discs, which are arranged in most cases vertically in a mill, comprises so-called chopping 3 () teeth distributed over the inner periphery of the disc The stationary disc 1, which is disposed adjacent to the feed pipe and has a central inlet opening for the material to be ground, may have three such chopping teeth 2, each of which has a bead 3 protruding over the plane in which the outermost parts of the base surfaces of the discs meet The associated rotary disc 4, driven in a known manner, carries chopping teeth 5 of lower height than the chopping teeth 2 Each chopping tooth 5-has next to the inner periphery of the disc an extension 6 overlapping the bead 3 of a chopping tooth 2 of the stationary disc 1 (Figures 1-3). -.5 As is apparent from the drawings these chopping teeth of the two discs are not identical in form In a manner known per se one chopping tooth of the stationary disc 1 is : formed with a nose 7 (shown with

dash-anddot lines in Figure 3) extending into the disc cavity and below the extension 6 of the rotary disc whereas at least one of the chopping teeth of the rotary disc 4 has a crushing face 8 (shown in dash lines in Figure 3) which extends substantially parallel and spaced from the inner surface of the disc. Due to this shape of the chopping teeth, bulb material will drop farther down if the chopping tooth having the crushing face 8 is at its lowermost position in the mill, whereas the chopping tooth of the stationary disc formed with the nose 7 will prevent the material from rotating with the rotary disc; thus an effective action of the chopping teeth on the material is ensured. The intermediate grinding zone of each grinding disc is formed by tearing teeth 9, which are inclined relative to the periphery of the disc and are arranged to cooperate like shears during the operation of the mill The 70 inner parts -10 of the tearing teeth lie in the plane in which the outermost parts of the base surfaces of the discs meet and extend in the form of cutting edges 11 approximately -from the middle of the base surface of the disc 75 towards the inner periphery of the disc Before reaching that inner periphery they merge at 12 into the base surface of the disc (Figures 4-6). The tearing teeth 9 have groove like re 80 cesses 13 formed in their surface by casting or grinding These recesses are also of irregular arrangement, different width and depth and irregularly spaced The teeth control the feed of the material to the grinding 85 faces at the outer portion of the disc During the passage through that zone the material is further torn and comminuted It is suitable to form also the inner surfaces of the chopping teeth 2 with such groove-like recesses 13 90 (Figure 3). The outermost zone of the grinding discs comprises irregularly disposed discharge grooves 14, which extend substantially in the direction of the tearing teeth and have dif 95 ferent depth, width and inclination The lands of the annular grinding zone which lie between these grooves 14 in the plane in which the outermost parts of the base surfaces of the discs meet are again interrupted by trans 10 verse grooves 15, which are also irregularly arranged, for example extend outwardly as at 16 or inwardly as at 17 or parallel to the rim of the disc as at 18 (Figure 4) Thus the material is moved from one groove to another 105 in a repeatedly changing course and in being thus moved is crushed and ground. The material can be ground to a higher degree of fineness if the annular grinding zone is provided, over at least part of the 110 grinding discs, with an arrangement of transverse grooves 19 (Figure 1) each of which conforms to at least part of a spiral continuously approaching the periphery of the disc and whole walls are preferably

recessed 115 i in the form of half screw threads. In another embodiment of the invention at least one row of substantially radially spaced catching teeth is provided in the central portion of the rotary disc inside the chopping 12 oteeth These catching teeth cooperate with the nose of the chopping tooth of the stationary disc and consist suitably of boltlike projections which each terminate in an inclined end face' 125 This feature provides a further improvement of the method of operation and an increase in the capacity of such mills because the catching teeth arranged in the space cavity between the two grinding discs hook 130 785,103 into greater chunks of the material to be ground, carry them along and force them during the further rotation of the grinding disc against the nose of the stationary chopping tooth Thus the material is held fast, clamped and is milled off by the catching teeth during the continued operation of the mill The chunk is still held to that nose of the chopping tooth until it has been divided then it is fed to the chopping teeth for the further grinding operation. As is apparent from Figures 7-9, the stationary disc 1 which is adjacent to the feed pipe 20 with its inlet opening for as the material to be ground has the same grinding members as have been described in detail hereinbefore The tearing teeth and discharge grooves are not shown in detail in the drawing Figure 7 shows one of the chopping :20 teeth 2 with the bead 3; this is the chopping tooth also formed with the nose 7 extending inwardly into the disc cavity. Driven by a shaft 21 the rotary disc 4 is also of the type described hereinbefore. t S Figure 7 shows one of its chopping teeth 5 having an extension 6 extending below the bead 3 of the chopping teeth In this embodiment the central portion 22 of the rotary disc 4 is additionally provided with a number of substantially radially spaced catching teeth 23 as is apparent from Figure 8. These catching teeth 23 consists of boltlike projections located in the central portion of the disc and each terminating in an end face 3 S 24 which is inclined relative to the tooth axis (Figure 9) Before 25 provided in the central portion 22 serve for connecting the rotary disc 4 by means of fixing bolts 26. The mill according to the invention is -40 equally suitable for groats, fruit, green food, hay, cereals, bulbs, sugar, coal and the like. The material to be ground may be dry or moist Thus the mill is suitable for operations for which beating mills were required so far.

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* GB785104 (A)

Description: GB785104 (A) ? 1957-10-23

Powdered synthetic tanning agents

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11 ',-' PATENT SPECIFICATION 785,104 Date of Application and filing Conmplete Specification: January 19, 1956. No 1899/56. Application made in Germany on January 19, 1955. Coniplete Specification Published: October 23, 1957. Index at acceptance:-Ciass 76, C 21 ( 1: 6: 8), C 2 X. International Classification:-C 14 c. COMPLETE SPECIFICATION Powdered Synthetic Tanning Agents x"" ls A^TINFABRIKEN BAYER AKTIENGES which should produce at a sufficient acid 9 onntent solutions having a p H value of not SPECIFICATION NO 75, 104 The Inventors of this invention in the sense of being the actual devisers thereof within the meaning of Section 16 of the Patents Act, 1949, are erard Jun, of C a rlc h Rn d po f t ra S e 1 L e Ave re r W e r ks G eem an N d e lsr d J o f Ca N 1-Rumpff-Strasse, 75,

Leverkusen-Bayerwerk, Germany, and Rudolf Fingado, of Elehendorffstrasse, 1, Leverkusen, Germany, both Cerman citizens. THE PATENT OFFICE, ith N Aovember, 1957 ous solid organic acids or t Lurn,,, such as oxalic acid, adipic acid, phthalic acid anhydride or aromatic polycarboxylic acids have been used hitherto as additives for synthetic tanning agents Either their solubility is not sufficient, as for example with adipic acid or phthalic acid anhydride, or the p H value of the aqueous solution is too low, as for instance with oxalic acid In other cases the p H value is too high, as with adipic acid or phthalic acid anhydride. In accordance with the present invention a mixture of solid acids, such as obtained as a by-product in the oxidation of cyclohexane, cyclohexanol, cyolohexanone or mixtures of these substances to adipic acid, and whose main constituent is glutaric acid, is used for the adjustment of the acidity and p H value of powdered synthetic tanning ayents This acid mixture excels in respect of a good solubility, a p H value which is favourable for adjustment of powdered synthetic tanning agents, and in its productivity in application due to the low equivalent weight This acid mixture also activates tanning agents particularly well. The acid mixture is chiefly suitable for adjustment of exchange tanning agents (Price 3 s 6 d) DB 00 o 30/1 ( 7)/3597 100 11/57 R 20 per cent, y,, of acid mixture referred to the powdered neutral tanning agent (The acid value here 65 referred to is the number of milligrammes of potassium hydroxide equivalent to I gramme of tanning agent as used in the actual tanning process). Because of the low volatility, the acid 70 mixture can also be directly dissolved in the neutral tanning solution and then dried in order to obtain a powdered tanning agent having the desired acid value. The following Examples are given for the 75 purpose of illustrating the invention, the parts beinv, by weight. Example 1 A synthetic tanning agent prepared according to Example 11 of German Patent No 80 870,268, i e by reacting benzene derivatives with two adjacent hydroxyl groups with aromatic compounds containing sulphonic acid groups and aldehydes, is neutralised after condensation with formaldehyde with 85 aqueous ammonia to a p H value of 7, and the neutral solution is dried on a drying roller 890 Parts of the powdered tanning agent are homogeneously mixed in a mixing apparatus with 100 parts of the acid mixture 90 rt N g% X,1,4-e A,J 4,4 it 7 ' {J: ' ' PATENT SPECIFICATION T r,, i j '<, 785,104 " Date of Application and filing Complete Specification

January 19, 1956. No 1899/56. Application made in Germany on January 19, 1955. Complete Specification Published: October 23, 1957. Index at acceptace:-C Iass 76, C 21 ( 1: 6: 8), C 2 X. Internalional Classification:-C 14 c. COMPLETE SPECIFICATION Powdered Synthetic Tanning Agents We, FARBENFABRIKEN BAYER AKTIENGESELLSCHAFT, a body corporate organised under the laws of Germany, of Leverkusen, Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention relates to powdered synthetic tanning agents, and more particularly to a process of adjusting the acidity and p H value of the powdered synthetic tanning agents. In the manufacture of powdered synthetic tanning agents it is desirable to produce tanning agents which are wealdy acid Various solid organic acids or their anhydrides such as oxalic acid, adipic acid, phthalic acid anhydride or aromatic polycarboxylic acids have been used hitherto as additives for synthetic tanning agents Either their solubility is not sufficient, as for example with adipic acid or phthalic acid anhydride, or the p H value of the aqueous solution is too low, as for instance with oxalic acid In other cases the p H value is too high, as with adipic acid or phthalic acid anhydride. In accordance with the present invention a mixture of solid acids, such as obtained as a by-product in the oxidation of cyclohexane, cyclohexanol, cyolohexanone or mixtures of these substances to adipic acid, and whose main constituent is glutaric acid, is used for the adjustment of the acidity and p H value of powdered synthetic tanning agents This acid mixture excels in respect of a good solubility, a p H value which is favourable for adjustment of powdered synthetic tanning agents, and in its productivity in application due to the low equivalent weight This acid mixture also activates tanning agents particularly well. The acid mixture is chiefly suitable for adjustment of exchange tanning agents (Price 3 s 6 d) which should produce at a sufficient acid content solutions having a p H value of not less than 3 0. The preparation of the powdered tanning agents is carried out in known manner by 50 neutralising the synthetic tanning agents if necessary, and drying them in a suitable apparatus, for example on a drying roller or in a spray drier, after the condensation is completed The acid mixture is 55 then homogeneously mixed with the neutral powdered tanning agent in a mixer The amount of acid mixture to be added

depends solely on the desired acid value of the final powdered tanning agent In order 60 to obtain an acid value of 100 200 there must be added, on a weight basis, about 20 per cent, preferably 8 15 per cent, of acid mixture referred to the powdered neutral tanning agent (The acid value here 65 referred to is the number of milligrammes of potassium hydroxide equivalent to 1 gramme of tanning agent as used in the actual tanning process). Because of the low volatility, the acid 70 mixture can also be directly dissolved in the neutral tanning solution and then dried in order to obtain a powdered tanning agent having the desired acid value. The following Examples are given for the 75 purpose of illustrating the invention, the parts beil by weight. Example 1 A synthetic tanning agent prepared according to Example 11 of German Patent No 80 870,268, i e by reacting benzene derivatives with two adjacent hydroxyl groups with aromatic compounds containing sulphonic acid groups and aldehydes, is neutralised after condensation with formaldehyde with 85 aqueous ammonia to a p H value of 7, and the neutral solution is dried on a drying roller 890 Parts of the powdered tanning agent are homogeneously mixed in a mixing apparatus with 100 parts of the acid mixture 90 785,104 obtained as a by-product in the preparation of adipic acid by the oxidation of cyclohexane, cyclohexanol, cyclohexanone or mixtures of these compounds The resultant acid mixture has approximately the following composition: 70 % glutaric acid, % succinic acid, 15 % adipic acid and % oxalic acid The adjusted powdered tanning agent contains 96 per cent of solids having an acid value of 116 at a p H value of the solution 3 3 Leathers tanned with this product do not differ from leathers tanned with the corresponding liquid tanning agents adjusted with acetic acid. Example 2 A condensed tanning agent prepared according to Example 1 of German Patent No 611,671, i e by condensing dihydroxy diphenyl sulphones without sulphonic acid groups with 'formaldehyde in the presence of aromatic sulphonic acids or their formaldehyde or sulphuryl chloride condensation products in an acid medium, is neutralised with aqueous ammonia and 135 parts of the aforesaid acid mixture are added per 1000 parts of syrup After complete dissolution, the tanning agent is transferred in a spray drier into a powder having an acid value of at a p H value of the solution of 3 4. The tannage yields a plump white leather of good fastness to light which in respect of its properties is comparable with a leather prepared from the normal liquid tanning agent adjusted with acetic

acid.

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* GB785105 (A)

Description: GB785105 (A) ? 1957-10-23

An improved hydraulically operated scraper device for roller mills


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BE544538 (A) FR1140220 (A) BE544538 (A) FR1140220 (A) less Translate this text into Tooltip



-:,'_; 7;,z,-J%C ':-m PATENT SPECIFICATION 785, 105 Date of Application and filing Complete Specification: Jan 24, 1956. No 2311 i/56. Application made in Switzerland on Jan 28, 1955. Complete Specification Published: Oct 23, 1957.

ance:-Class 59, Al IG: lassification:-B 02 d. l COMPLETE 'SPECIFICATION An improved Hydraulically Operated Scraper Device for Roller Mills We, GEBRUDER 'BUHLER, of 'Uzwiil, I Switzerland, a Body Corporate organisedr according to the laws of Switzerland, do hereby declare the invention, for which we pray hat a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: - This invention relates to an improved hydraulically operated scraper device for the rolls of roller mfils In roller mills, especially those used for finely grinding pasty materials it is usual to scrape the material' from the roll by means of a scraper blade which leads the fnateriald ta collecting container, The scrapers usually employed, are pressed against the rolls by mechanical means including Threaded spindles and levers whereby the scrapers-may easily be pressed too heavily against the rolls and thus be submitted to inadmissible wear. Due to tfie blade wearing away, the scraping angle changes in the course of operation It has been proposed to press the scraper blades by hydraulic means against the rolls of roller mills. The object of the present invention is: an improved scraper device for roller mills, and it is characterised in that there is provided a pump for building up and maintaining constant the pressure of t he hydraulic fluid, and a reducing valve in the hydraulic line for controlling and setting the pressure applied to a scraper-blade holder, In a preferred embodiment of the invention the blade-holder is, sli'd ably mounted in guides disposed in, support blocks mounted on the roller mill frame in such a manner that they may be turned about an axis parallel with, the axis of the roll The invention is, particularly advantageous in that it allows for a temporary release and, removal of the scraper blade-holder and blade for cleaning, the pre-aet pressure always being maintained at the same value if desired upon return of the scraper blade-holder The chosen pressure is independent of temperature changes. In order that the invention may be clearly Price 3 s 6 d l understood and readily carried into effect reference is, directed to, the accompanying drawings which represent three particularly advantageous embodiments: of the invention and wherein: Figure 1 is a side view, in section,, along the line B-B of figure 2 Figure 2 is-a section of one side of a scraping device along the line A-A of figure 1. Figure 3 is a plan view of a scraping device according tothe invention Figure 4 showsl a second and Figures 5 and 6, a third embodiment of _the invention Referring more particularly to Figures 1, 2 i and 3, a is,the blade-holder provided with a scraper blade b, and adapted to

slide in' guide slots of two support blocks e The blteh'der is pressed against the roll h of a rolling mil, biy pistons c, movable in cylinders d which receive hydraulic fluid drawn out of a tank y through a' suction conduct z, and forced into the _cylinders d by means of a pump k driven by a motor 1, the pressure being maintained constarnt by the pump k which is, driven at constant speed The pressure may be set to a selected value by mnoans of a reducing valve i. The support blocks e are turnable about trunnions f, fastened to the frame m of a roller mill, their selected position being set and fixed by means of screws g so that the support blocks e are secured against rotation On the other hand the angle of attack of the blade b against the roll h may be changed within wide limits, the screws g being temporarily loosened when it is' desired to set the angle. Fon cleaning the machine and for changing the blade b, a reversing valve t is brought to' a vening position so that the pressure in the cy1 inders d faills to zero, the screws g are loosened and the blade-holder a is turned back with its two support blocks e far enough, to enable it o be withdrawn vertically upwards out of the guide slots in the support blocks. As the setting of the reducing valve i does not change during the removal' of the bladeIndex at accept International C 90. holder a and as the speed' of the pump k re applied to a scraper bladte-holder. n Mains constant, the pressure is,exactly the 2 A hydraulic scraping device according same after replacementof the blade-holder and to claim 1 wherein the blade-holder for the 45 closing the venting valve t as it was before re scraper blade is adapted to slide in guides dismoval Such pressure maintenance is parrticu posed in support blocks turamable about tunlarly advantageous in roller mills for grind& nions fastened to the frame of a roller mill. ing pasty goods = = ' ' 3 'A hydraulic scraping device according to The hydraulic fluid is distributed in the t Wo claim 2 wherein the support blocks are fastened 50 cylinders d by means of a pipe N and flexible in position by means of screws. tubes o The blade-holder a automaticali-sa 4 A'ydraulic scraping device according to sumes a position that its axis p is parallel any one of the preceding claims wherein to the axis q of the roil k I Tensioned springs single acting hydraulic cylinders are used for s are placed in the cylinders d to withdraw pressing the scraper blade against the roll of 55 the blade-holder when th venting valve t is -the roller mill, a tensionedc spring within each opened, that is when the pressre in -the hy byliiicder rbeing used for withdrawing the scraper draulic system is recuired to fall ' blade when the hydraulic

pressure is released. In the enmbodiment according to, figue 4, - A hydraulic scraping device; according the cylinders d are double acting, the hydran to claims 1: or 2 or 3 ', characterised in that 60 lic -fluid, being -fed under a suitable controlg to double acting cylinders are used for pressing bothisides,of eadh piston r, insuch a manner the scraper blade against the roll of the roller that the bla&de-holdler cau be hydraulically mill, the hydraulic fluid being fed to one side withdrawn'froiitheroll of each -piston for withdrawing the scraper In the fuirtherembodiment shown in figures Pladefrom the roll 65 and,6 -pressure cylinders, are cnmbined 6 A hydraulic scraping device, according to with the support trumnnions f in, such a manner claims 4 or 5, characterised in that the hydrauthat the piping used, for the hydraulic fluid lic-cylinders are connected to the hydraulic may be rigida The pressure cylinders v may be pre'ssure source by means of rigid pipes and turned into whatever positioni is chosen and flexible tubes 70 are each made fast by means oef a nut w 7, 'A hydraulic scraping device according to Plaes x in which guides for the blade-holder claim 1 or 2, or 3 characterised in that hydraua are disposed mawy ibe tumned about the pres li cyli nders are formed in the trunnions and sure cylinders: v andl be displaced& within, wide are connected' to the hydraulic pressure source limits to adjust the angle of attack of the bladebyrmeans of:tubes 75 and fasteed, to the frame by means of screws 8 The improved hydraulically operated g - = scraper device for the rolls of roller mills sub-


* GB785106 (A)

Description: GB785106 (A) ? 1957-10-23

Improvements in method and apparatus for assembling a vibration damper


PATENT SPECIFICATION 785,106 Date of Application and filing Complete Specification: January 30, 1956. No 2891/56 Application made in United States of America on April 19, 1955 Complete Specification Published: October 23, 1957 Index at acceptance:-Class 108 ( 3), R. International Classification:-FO 6 f. COMPLETE SPECIFICATION Improvements in Method and Apparatus for Assembling a Vibration Damper We, UNITED STATES RUBBER COMPANY, of Rockefeller Center, 1230 Avenue of the Americas, New York, State of New York, United States of America, a corporation S organized and existing under the laws of the State of New Jersey, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:This invention relates to the manufacture of vibration dampers and more particularly to an improved method and a simplified apparatus for assembling a vibration damper. The type of vibration damper with which this invention is primarily concerned is that which is mounted on a crankshaft of an 2.0 internal combustion engine The primary purpose of such a device is to dampen out or reduce torsional vibrations set up in the crankshaft by the explosive forces in the engine and the reciprocating masses therein, although it may be adapted to any other shaft subject to vibrational impulses. Generally speaking, a vibration damper comprises a resilient annulus interposed between an outer rigid member known as an inertia ring and an inner rigid member known as a central hub, the latter being secured to the crankshaft The annulus holds the hub and ring in assembled relationship but permits limited relative rotation therebetween to provide the desired damping action. In the prior art, the assembly of vibration dampers involves numerous time consuming operations as well as various types of complex apparatus As a consequence, production is limited and equipment expensive, both contributing to increased assembly costs For example, in patent 1,976,789 the resilient annulus must first be accurately located between the central hub and inertia lPrice 3 s 6 d) ring, and this position must be maintained while the damper assembly is placed in a vulcanizing chamber to -bond the annulus to the inner and outer rigid members.

Although the necessity of vulcanizing the 50 annulus to the hub and ring has been avoided by patent 2,556,999, the annulus must nevertheless be initially located within the outer rigid member and both held in proper position by some means while the 55 two plates forming the inner rigid member are forced together by suitable pressure applying means Moreover, these plates must be held together by the pressure applying means or some other means while a suitable 60 riveting device is used to secure them permanently. Therefore, the primary object of this invention is to provide an improved method and simplified apparatus for assembling a 65 vibration damper quickly, easily and economically To this -end, many of the numerous assembly operations and devices formerly required have been eliminated by locating the unassembled annulus, hub and ring in 70 proper relationship with each other in a single apparatus incorporating in itself all the simplified apparatus and necessary supports for facilitating the performance of the locating operation, by applying pressure 75 with rigid means also incorporated in said apparatus to telescopically force the annulus, hub and ring into assembled relationship in one rapid stroke. Other advantages of the invention will 80 become apparent upon consideration of the following specification and claims when read in connection with the accompanying drawing wherein: Fig 1 is a top plan view, partially in 85 section, of a vibration damper produced in accordance with the teachings of the invention; Fig 2 is a vertical sectional view illustrating the apparatus employed in assembling 90 785,106 the damper of Fig 1, part of the upper portion of the apparatus being shown in phantom outline to indicate its position prior to the pressure applying stroke; the outline being partially broken away to illustrate in section the undeformed annulus supported therein, and the upper and lower portions of the apparatus being shown in solid lines to indicate their structure and position, as J 0 well as those of the damper parts, at the completion of the stroke; and Fig 3 is an enlargement of a portion of Fig 2 illustrating in detail the special structural features of the pressure applying member, hub and ring, as well as their relationship to each other at the completion of the pressure applying stroke. Referring now to Figs I and 2, the vibra-tion damper 10 comprises a resilient annulus :20 11 which is preferably made of natural or synthetic rubber, although any other suitable elastic material may be employed The annulus 11 is interposed between the adjacent peripheral surfaces 14 and 15 of a central hub 12 and an outer inertia ring 13 respectively The central hub 12 is preferably made of a stamped sheet metal such as steel and has a bore 16 for mounting the hub on a crankshaft (not shown), while the o inertia ring 13 is preferably

fabricated of cast iron or some other relatively dense and heavy material For the particular embodiment illustrated, it was required that the annulus 11 be capable of being compressed 25-40 % to allow for a minimum of 200 foot-pounds slip torque between the annulus 11 and the adjacent peripheral surfaces 14 and 15 It has been found that a 67 durometer rubber is suitable for this purpose and also has a sufficient deflection range to permit the desired limited relative rotation between the hub and ring. Referring briefly to Fig 3, the adjacent peripheral surfaces 14 of the hub 12 and 15 of ring 13 have annular tapered portions 17 and 18 extending therefrom to form a converging entrance thereto The tapered portion 17 on the hub 12 is arcuate in crosssection while -the tapered portion 18 on -ring 13 is a chamfer The hub 12 and ring 13 are so constructed that the tapered portion 18 makes an angle of 500 with the horizontal plane H-H while a line T which intersects plane H-H and vertical line V at point O and which makes an angle of 100 with line V, is tangent to arcuate tapered portions 17 As stated above, these tapered portions 17 and 18 form a converging entrance to the spaced peripheral surfaces 14 and 15, the purpose of which is to prevent the annulus 11 from being sheared or torn as it is forced in between these surfaces. Although the convex bottom radial face 19 of annulus 11 may bulge outwardly beyond bottom surface 20 of ring 13, and the flattened top radial face 21 may do likewise beyond plane I 2-H 2 when permitted to take its normal convex shape, it will be apparent that the annulus 11 lies substantially between planes HI-HI and IF-H 2 It will also be 70 observed that the arcuate portion 17 of hub 12 merges into peripheral surface 14 at point 03 in plane H 2-HI, while flange 22 of the hub begins at point 01 in plane IT-I 41 Between planes IF'-1 and H 2-H 2,peripheral 75 surfaces 14 and 15 are concentric dnldequidistant, thus the substantially coextensive annulus 11 will exert a uniform radial pressure throughout its length against peripheral surfaces 14 and 15 to keep the 80 hub 12 and ring 13 in axial alignment with each other As the damper 10 is rotated in service, this precise positioning of the annu lus 11 will prevent any wobbling between hub 12 and inertia ring 13 during its rota 85 tion Were the full radial thickness of the annulus 11 to extend any substantial distance beyond plane HI-HI' or IT-I-P, it would tend to force hub 12 and inertia ring 13 out of alignment, thereby inducing undesirable 9 o vibrations in the damper 10 itself, and reducing its effectiveness in damping the vibrations of the crankshaft The device employed for obtaining such accurate positioning of annulus 11 will be described 95 below in connection with the apparatus of which it is a part. Referring now to Fig 2, the apparatus comprises a lower platen 23 and

an upper platen 24 which may be mounted in a con 100 ventional press (not shown) by any suitable means (not shown) The press may be actuated by hydraulic or other means (not shown) in order to move platens 23 and 24 relatively to one another Either platen may 105 remain stationary while the other is reciprocated, or both may be moved toward and away from each other, depending upon the type of press employed It is preferable however, that the platens 23 and 24 be 110 mounted in axial alignment with each other along line A-A in order to properly assemble damper 10, as will become more apparent below. The lower platen 23 has a pair of con 115 centrically spaced members 25 and 26 mounted thereon for supporting the hub 12 and inertia ring 13 in spaced concentric relationship Member 25 is ring-shaped and is centered on axis A-A in shallow cylin 120 drical recess 27 cut in platen 23, the outer periphery 28 of ring 23 fittting snugly against the inner periphery 30 of annular flange 29 Ring 25 has a recess 31 and flange 32 similar to those on platen 23 for 125 centering and supporting inertia ring 13. Member 26 is a relatively thick cylindrical block centrally positioned in recess 27 in platen 23 and is rounded off at 33 to accommodate the arcuate portion 17 of hub 130 785,106 12 Members 25 and 26 are preferably rigidly secured to platen 23 by any suitable fastening means (not shown). Block 26 is also provided with a central bore 34 in which the reduced end 36 -of a cylindrical plug 35 is held by means of a press fit Plug 35 has an enlarged head 37, the bottom of which forms a shoulder 38 resting on the upper surface 39 of block 26, and the top of which is rounded off at The enlarged head 37 of plug 35 slidably projects into a central cylindrical recess 41 cut into upper platen 24 for guiding platen 24 and maintaining its alignment A 5 with axis A-A as it moves relatively to lower platen 23. Upper platen 24 is provided with eight or more circumferentially and radially spaced inner and outer bores 42, only four of which -20 are shown The upper and lower ends of bores 42 are provided with enlarged recesses 43 and 44 respectively Passing through bores 42 are rods 45, the upper ends of which have heads 46 disposed in recesses 43 and the opposite ends of which are externally threaded as at 47 Attached to rods are a pair of concentrically spaced annular plates 48 and 49, the threaded ends 47 of rods 45 being screwed into internally threaded bores 50 in plate 48 and 51 in plate 49 Inner plate 49 is also provided with a central bore 52 for the passage of plug 35 which maintains plate 49 in alignment with axis A-A, and lower surface 53 of plate 49 is concave to closely fit hub 12. A plurality of coiled springs 54 surround rods 45, the upper ends of the springs 54 seating in recesses 44 in platen 24 and the lower ends

thereof seating in recesses 55 and -40 56 in plates 48 and 49 respectively Springs 54 are of the compression type and there. fore urge the resiliently mounted plates 48 and 49 outwardly from upper platen 24 this outer movement being limited by en. gagement between heads 46 of bolts 45 anc recesses 43 in platen 24. Rigidly mounted in the lower portion o: platen 24 is an annular steel die 57 The upper end of the die 57 fits snugly into ai annular recess 58 in platen 24 and may b secured therein by welding or any othe suitable means As will be apparent, the di 57 extends between the adjacent peripherie 59 and 60 of plates 48 and 49 respectivelj and is movable relatively thereto Referrin to Fig 3, the lower end of die 57 is provide with downwardly converging annular tapere portions 61 and 62 and a reduced annuk portion 63 The portion 61 extends ou wardly from the inner peripheral surfac -64 of die 57 while portion 62 extends ih wardly from the outer peripheral surface 6. each of these portions intersecting the r duced portion 63 at the horizontal plai H-H Obviously, the angularity of portioi 61 and 62 are the same as line T tangent to arcuate portion 17, and chamfered surface 18 respectively Thus, the tapered portions 61 and 62 on die 57 which fit snugly against the corresponding tapered portions 70 17 and 18 on hub 12 and inertia ring 13, and the reduced portion 63 which projects between the hub and ring, cooperate to properly position annulus 11 therein. Referring to Fig 2, the method of 75 assembling the damper 10, together with the operation of the apparatus will now be described The platens 23 and 24 are first moved apart from each other by the press (not shown) until plates 48 and 49 are in 80 the position shown in phantom outline. Next, the hub 12 and inertia ring 13 are located in substantially spaced concentric relationship on members 26 and 25 respectively The undeformed annulus 11 is now 85 positioned in substantially axial alignment -with hub 12 and ring 13 by inserting the annulus between the adjacent peripheries 59 and 60 of plates 48 and 49 respectively,. as shown in the partial section broken out 90 of the phantom outline As will be apparent, the adjacent peripheries 59 and 60 of plates 48 and 49 are considerably farther apart than the corresponding peripheral surfaces 14 and 15 of 95 hub 12 and inertia ring 13, in order to accommodate and support the annulus 11 in undeformed condition The lower portion of die 57 also serves as a stop to assist the operator in determining how far the annulus 100 is to be inserted between plates 48 and 49. Moreover, even though the outer periphery of inner plate 49 is not completely coextensive with inner periphery 59 of outer plate 48, the

die 57 is recessed far enough 105 when plates 48 and 49 are fully extended by springs 54 so that the entire inner and outer peripheries of the undeformed annulus 11 are supported by the adjacent peripheries d 59 and 60 of the plates This is important 110 in order to maintain the annulus 11 in true f alignment with hub 12 and ring 13 prior to e the assembly stroke. a The platens 23 and 24 are now moved e toward each other; the head 37 of plug 35 115 r -first passes through bore 52 in plate 49, and e then into recess 41 in upper platen 24 to zs ensure alignment of the various press parts r, with each other along axis A-A As the g platens 23 and 24 continue to approach 120 d each other, the plates 48 and 49 simuld taneously engage ring 13 and hub 12 to ir maintain the -latter in spaced concentric t relationship In case it is necessary for the ce hub 12 to be shifted laterally somewhat to 125 i closely engage the concave surface 53 on 5, plate 49, the rounded portion 33 and the diameter of block 26 are made slightly ie smaller than arcuate portion 17 and the as diameter of hub 12 to permit such move 130 ment It is also important to note that the relative position of plates 48 and 49 does not change as the plates move from their upper position (in phantom outline) into engagement with hub 12 and inertia ring 13 (solid line position) Thus, the annulus 11 is continuously supported by the adjacent peripheries 59 and 60 of plates 48 and 49 respectively, until it is squeezed by tapered portions 17 and 18 of hub 12 and inertia ring 13 As the platens 23 and 24 move closer together, the springs 54 are compressed and annular die 57 moves downward relatively to and between them The die 57 applies axial pressure to the upper radial face 21 of annulus 11 to telescopically force the annulus into assembled relationship with hub 12 and inertia ring 13 in one rapid stroke For the particular embodiment illustrated this pressure is of the order of 6,000 pounds per square inch to obtain the -desired compression of annulus 11 During the pressure applying stroke of die 57, the annulus 11 first passes through the converging entrance formed by tapered portions 17 and 18 extending from the adjacent peripheral surfaces 14 and 15 of hub 12 and inertia ring 13 respectively, and then in between peripheral surfaces 14 and 15 themselves As this occurs, the annulus 11 is simultaneously radially compressed and axially elongated to be properly positioned between and securely engage the aforementioned peripheral surfaces. As stated previously, tapered portions 17 and 18 provide a smooth converging entrance to peripheral surfaces 14 and 15 to prevent the annulus 11 from shearing or tearing as it is forced in between the hub 12 and ring 13 The tapered portions 17 and 18 have another equally important function, and that is to provide a close fitting seat for the tapered portions 61 and 62 on the lower end of die 57, at the

completion of the pressure applying stroke As seen in Fig 3, the reduced portion 63 and tapered portions 61 and 62 of die 57 ensure that the annulus 11 is properly positioned between hub 12 and ring 13 The primary purpose of reduced portion 63 is to force the deformed annulus 11 far enough between hub 12 and -inertia ring 13 so that the full radial thickness of the annulus 11 lies between planes -H'-W and if-H 2 Naturally, the undeformed annulus 11 is so proportioned that it will be elongated under compression to be substantially coextensive with the distance between these planes Thus, the uniformly deformed annulus 11 will maintain the hub 12 and inertia ring 13 in axial alignment when damper 10 is rotated on its crankshaft (not shown) Referring back to Fig 2, it will be noted that the reduced portion 63 of die 57 does not engage the full radial face 21 of undeformed annulus 11 As may be expected, the unsupported portion of face 21 may have a tendency to extrude backwardly around the-reduced portion 63 and against tapered 7 GT portions 61 and 62 of die 57 because of the friction developed between annulus 11 and plates 48 and 49, during the pressure applying stroke However, as the tapered portions 61 and 62 approach the corresponding 75 tapered portions 17 and 18 on hub 12 and inertia ring 13, this backwardly extruding rubber will become compressed more and more between the aforementioned tapered portions until all or practically all of it 8 () extrudes forwardly with the rest of the annulus 11 into the space formed between hub 12 and ring 13 Any amount of rubber which might possibly be sheared or scraped off in the process would be too small to have any 815 more than a negligible effect on the proper positioning of annulus 11 between the hub 12 and ring 13. Thus, it will be apparent that no lubricant of any kind is necessary to make the 90 ' assembly operation successful If desired, however, the peripheries of annulus 11 may be coated with a suitable lubricant such as a mixture of 20 % petrolatum and 80 % light mineral oil This will completely eliminate 95 any tendency of the annulus 11 to extrude backwardly during the pressure applying stroke However, care should be taken to keep the lubricant coating thin so that substantially all of it will be wiped off the annu l Ot G lus 11 as the latter is squeezed between hub 12 and inertia ring 13, in order to prevent any undesirable slippage between these damper parts. Upon completion of the pressure apply 105 ' ing stroke, the platens 23 and 24 are again moved apart until the plates 48 and 49 assume the position shown in phantom outline The damper 10 may now be removed from members 23 and 24 by any suitable 110 means forming no part of the present invention For the sake of clarity and completeness, however, there is shown a plurality of ejector pins 66, which may be simultaneously reciprocated t h r o u g h circumferentially 115spaced

bores 67 extending through platen 23 and member 25, by a convenient actuating means (not shown) As is apparent, the ejector pins 66 may be actuated to engage inertia ring 13 and lift damper 10 high 120enough so that the operator can easily grasp the ring to completely remove damper 10 and prepare for the next assembly operation. The space between block 26 and hub 12 will facilitate the removal of damper 10 125 because only the flat upper surface 39 of the block is in direct contact with the hub, while the compressed annulus 11 will keep inertia ring 13 in alignment with hub 12 so that ring 13 will slide out of recess 31 in 13078 J 91, 10 785,106 member 25 without difficulty. While the invention has been shown and described in a certain preferred form, it is to be understood that various changes and modifications may be made therein by one skilled in the art without departing from the principle of the invention, the scope of which is to be determined by the appended claims.


* GB785107 (A)

Description: GB785107 (A) ? 1957-10-23

Rubber insert with lubricant channel


COMPLETE SPECIFICATION Rubber Insert with Lubricant Channel We, THE GENERAL TIRE & RUBBER COM- PANY, of No. 1708 Englewood Avenue, Akron, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be

performed, to be particularly described in and by the following statement: The present invention relates to resilient mounting and more particularly to an elastic tubular rubber insert which is positioned between an outer rigid sleeve and an inner rigid tubular core of a resilient bushing under sufficient radial compression to provide a firm frictional bond between the elastic rubber and the sleeve. It is common practice to assemble resilient bushings by employing a tapered core pilot to expand the rubber insert prior to the entry of the core, for example as disclosed in British Patent No. 660,625. Where such a core pilot must be removed and replaced after the assembly of each bushing, it is difficult to assemble the bushings rapidly. The present invention eliminates the need for a, core pilot with an external diameter greater than the internal diameter of the rigid tubular core and facilitates high speed assembly of the resilient bushings. According to the present invention there is provided a tubular elastic member adapted for use as an insert for a resilient mounting having a central opening therein with an internal annular lubricant groove formed in the opening spaced from one end thereof, and a flexible lip projecting radially inwardly and forming one side of the groove, said tubular member having an annular shoulder spaced from the lip and facing the lip to form the other side of the groove, the opening in said member being enlarged outwardly from said lip toward said end, said lip being located between said groove and said end. An object of the invention is to provide a simple elastic and deformable insert for a resilient mounting which may be assembled easily and rapidly. A further object of the invention is to provide an elastic rubber insert having means to facilitate entry of a rigid core. Another object of the invention is to provide a rubber insert for a resilient mounting which may be assembled at high speed in an automatic or semi-automatic machine. Other objects, uses and advantages of the present invention will become apparent to one skilled in the art from the following description and from the drawings in which: Figure 1 is a fragmentary longitudinal sectional view on a reduced scale of a machine for assembling the bushings of the present invention showing the work positioning members in work receiving position, the work pressing members in their separated positions, and the core inserting plunger in retracted position; Figure 2 is a longitudinal vertical sectional view of the rubber insert of the present invention; Figure 3 is a fragmentary longitudinal sectional view of the machine

illustrated in Fig. 1 showing the alining pin in engagement with the tubular insert to guide it into engagement with the outer sleeve; Figure 4 is a fragmentary longitudinal section through the work gripping portions of the work pressing members showing said members in closed position in clamping the sleeve and insert between them; and Figure 5 is a fragmentary longitudinal section similar to Fig. 4 but showing the coreinserting plunger advanced to a position where the tubular core is in place within the rubber insert. In the drawings like parts are identified with the same numerals throughout the several views. Each figure of the drawings is drawn substantially to scale so that the relative sizes and shapes of the various parts of the resilient bushings and of the machine for assembling such bushings will be apparent to the eye, but it will be understood that the rubber insert of the present invention and the machine for assembling the insert in a resilient mounting may have various forms quite different from those shown in the drawings. The machine for assembling resilient mountings incorporating the elastic rubber insert of the present invention may be identical with the machine disclosed in-copending- British application No. 21,772/54 :iled July 26, 1954, serial number 758295 entitled MACHINE FOR ASSEMBLING RE SILIENT BUSHINGS". However, it is unnecessary to employ fluid udder pressure in such machine to facilitate assembly of a rigid tubular core within the rubber insert of the present invention or otherwise to expand the radially inner portion of the rubber insert before the tubular core is inserted therein. The machine shown herein is identical with the machine shown in said cop enduing application except that the core inserting plunger and the means associated therewith for supplying fluid under pressure through the plunger are replaced by a simplified plunger which does not expand the portion of the rubber insert immediately in advance of the end edge of the tubular core as the core is advanced through the insert. The machine shown in the drawings is designed to assemble a resilient bushing or mounting which, as shown in Fig. 5, has a tubular insert A of elastic rubber which is disposed= between an outer sleeve B and an inner tubular core C under radial compression sufficient to firmly bind both the inner rigid core and outer rigid sleeve to the rubber. The bushing herein shown is well suited for use on vertically disposed pivots, the sleeve B being provided with a circumferential supporting flange b at its upper end and the insert A being provided -with - an -enlarcred upper end portion a that projects above the sleeve and bears upon the flange b. As herein illustrated the machine is mounted on-a suitable horizontal

bed 1 which is provided with a longitudinal way 2 and includes a sleeve and insert-assembling press that comprises a pair of work pressing membars 3 and 4 mounted on the bed 1 for relative linear movement, one toward and away from the other. As herein shown, the member 3~ is mounted in fixed position on the bed adjacent one end thereof and the member 4 is slidable an the bed and is guided for longitudinal movement along the way 2. The work pressing member 4 may be moved toward and away -from the work pressing member 3 by means of a suitable motor such as a reciprocating piston operated by a fluid pressure cylinder. As best shown in Figs. 1 and 4, the work pressing members 3 and 4 are provided with axially alined bores 7 and -8 that are parallel to the way 2. At their opposed faces the work pressing members 3 and 4 have counter bores 9- and 10, the counterbore 9 forming a socket to receive a sleeve B and the counter bore 10 providing a socket in which an end of the insert A fits. The countebore 9 is of a depth to receive substantially the entire sleeve B and may be provided with a removable stop sleeve 11 for engagement with the sleeve B, the sleeve 11 being readily removable and replaceable with other sleeves of different lengths to accommodate longer or shorter sleeves. The work pressing members 3 and 4 serve to force thttrubber insert A into the sleeve B and, in order to enable this to be done while the moveable member 4 moves into engage ment with the stationary member 3, means is provided for supporting an insert A and a sleeve B in axial alinement between the mem bers 3 and 4. The insert and sleeve support ing means comprises retractable supporting elements-that are movable into positions be tween the work pressing members 3 and 4 when the work pressing members are separated. As most clearly shown in Fig. 1, the stationary work pressing member 3 carries a supporting- element 12 that forms part of its clamping face, the part 12 having a top face in the plane of the axis of the counterbore 9 and being mounted on a pair of pistons 13

disposed parallel to the bed 1 and to the axis of the counterbore 9, the pistons 13 being slid able in cylinder 14 to a position inwardly of the clamping face of the member 3. Since the top of the supporting element 12 conforms to the lower half of the counterbore 9, it pro vides a sleeve-receiving seat 12a on which a sleeve B may be supported in axial alinement with the counterbore 9. The movable work pressing member 4 carries a retractable supporting element I5 that forms the lower part of its clamping face and that has a top face in the plane of the axis of the counterbore 10. The supporting elements 15 is mounted on a pair of pistons 16 that are parallel to the bore 8 and that slide in cylinder 17 formed in the member 4. Since the top of the element 15 conforms to the lower half of the counterbore 10, it provides a concave insert-receiving seat 15a. During operation of the machine, air under pressure is supplied to the cylinders 14 and 17 for yieldably pressing the supporting elements 12 and 15 toward one another so that the supporting elements 12 and 15 automatically move to sleeve and insert-receiving positions when the member 4 is moved away from the stationary member 3. The bore 8 of the work pressing member 4 is of a diameter but slightly greater than the external diameter of the core C and the mem ber 4 is provided with an opening 18 through which a core C may be entered into the bore 8. A plunger 19 is slidable in the bore 8 toward and away from the stationary work pressing member 3, the plunger 19 when in its retracted position as shown in Fig. 1 being positioned beyond the core-receiving opening 18 so that it may engage with the core C in the bore 8 when it is moved toward the stationary member 3. The plunger 19 slidable fits in the bore 8 and has a core-receiving end portion 20 of reduced diameter which enters the core as shown in Fig. 4 during movement of the plunger toward core'inserting position. At its inner end the plunger has a tapered pilot portion 21 that is integral with a portion 20. The plunger 19 may be reciprocated once during each cycle of operation

of the machine by any suitable mechanism, such for example as a reciprocating slide and a crank that is rotated by a crankshaft through a onerevolution clutch. Adjacent the stationary work-pressing member 3, the bed 1 is provided with alined transverse ways 23 disposed at right angles to the path of travel of the work-pressing member 4, and these ways carry identical oppositely-movable work-positioning slides 24 that are movable into the space between the work pressing members 3 and 4 when the work pressing member 4 is in its retracted position. The slides 24 are mounted for reciprocation parallel to the ways 23 and may be reciprocated by a fluid motor or any other suitable motor means. Such motor holds the slides 24 in their retracted positions and thereafter moves the slides 24 inwardly toward the supporting members 12 and 15 with which the slides 24 engage when in their innermost positions. Each slide 24 has an insert-positioning portion 25 provided with recesses 26 that conform to the large end a of the insert A and that overlie the seat 15a on the supporting member 15. The insert-positioning portions 25 also have projections 27 that extend into the space between the retractable supporting members 12 and 15 closely adjacent the face of the supporting members 15, the projections 27 being shaped to receive the body portion of an insert A to support the insert in axial alinement with the socket 9. The slides 24 also have sleeve-positioning portions 28 that are brought into position overlying the retractable sleeve-supporting member 12 and that are provided with recesses 29 that conform to the flanged ends b of the sleeve B. When the slides 24 are in their innermost positions, the positioning members 25 and the retractable supporting member 15 provide a receiving pocket for a rubber insert A in which the insert will be supported in axial alinement with the bores 7 and 8 of the work pressing members. The sleeve positioning portions 28 of the slides together with the reretractable supporting member 12, form a receiving pocket for a sleeve 8 in which a sleeve B will be supported in axial alinement with the bores 7 and 8 of the work-pressing members and also in axial alinement with an insert A in the pocket formed by the portions 25 of the slide 24 and the retractable supporting member i5. In order to permit the work pressing member 4 to move into engagement with the stationary member 3, it is necessary to retract the slides 24 prior to movement of the member 4 toward the member 3. The supporting member 12 provides a seat in which the cylindrical body of the sleeve B fits and serves to support the sleeve B and to guide it into the socket 9 when the member '4 exerts pressure on the supporting member 12 to move it inwardly against the pressure of the air in the

cylinders 14. The - supporting member 15, however, engages only the enlarged portion a of the insert A; and, in order to more adequately support the insert in proper position during the closing movement of the work pressing member 4, an alining pin 30 is - provided which is movable through the bore 7, - which is in axial alinement with the bores 7 and 8 and which is of a size to fit within an insert A. The alining pin 30 is advanced into tracting movement of the work-positioning engagement with the insert A prior to the reslides 24 and serves to guide the insert into engagement with the sleeves B during the closing movement of the movable work pressing member 4. The alining pin 30 may be connected to a suitable reciprocating motor such as a fluid motor having a piston mounted in a cylinder that is axially alined with the bores 7 and 8 of the work pressing members and that is secured to the bed 1. At the beginning of each cycle of operation of the machine, the work pressing member 4 and the slides 24 are in their retracted positions and the plunger 19 is in its fully retracted position where its core-receiving end 20 is clear of the core-receiving opening 18 in the member 4. The alini3Zg pin 30 is also in retracted position. The slides 24 are first moved inwardly to their sleeve and insertreceiving position; and, after a sleeve and insert have been positioned on the seats 12a and 15a and a core inserted into the bore 8 through.1he opening 18, the alining pin 30 is advanced into engagement with an insert on the seat 15a, the slides 24 are retracted and the motor is energized to move the work pressing member 4 toward the stationary member 3. During this movement of the work pressing member, the insert A is slid along the alining pin 30 into engagement with the sleeve B on the seat 12a and the sleeve B is pushed into the socket 9 and the insert A is simultaneously pushed into the sleeve B as shown in Fig. 4, after which the pin 30 is retracted and the plunger 19 is advanced to force a core C into the insert A as shown in Fig. 5. During the final closing movement of the movable work pressing member 4, the plunger 19 is moved toward the stationary work pressing member 3, past the opening 18 where it picks up a core C and positions it on the reduced end portion 20 so that upon continued movement.the core will be forced into the insert as shown in Fig. 5. The leading end of the core C forms a shoulder that would normally engage with the insert A and greatly increase the resistance to the passage of the core into the rubber insert. Toeliminate this difficulty means may be provided for delivering a fluid, such as a liquid under pressure, radially against the interior of the rubber insert A immediately in advance of the leading end of the core C as for example in said copending application or other suitable means may be provided for expanding

portions of the insert radially in advance of said leading end to facilitate entry of the core. However, such means are unnecessary with the insert A of the present invention. Since a - fluid supply means for the plunger 19 is unnecessary where the machine is assembling bushings with the rubber insert A of the present invention, the plunger 19 and the tapered pilot 21 thereof shown in the drawings is slightly different from the plunger 49. and pilot 21 shown in the aforesaid application Serial No. 758295, As herein shown, the large end of the tapered pilot 21 is of substantially the same diameter as the externally cylindrical core-receiving portion 20 of the plunger 19 and said pilot 21 and said portion 20 are substantially the same size and shape as the pilot 21 and the portion 20 of the plunger 19 shown in the aforesaid copending application, but unlike the latter plunger the pilot 21 is integral with the cylindrical portion 21 and does not contain fluid passages. The core C may be entered into the rubber insert A of the present invention without damage to the insert. Since the large end of the tapered pilot 21 is of the same diameter as the corereceiving portion 20 of . the plunger, the plunger and pilot will pass freely through the core C when the plunger 19 is retracted. During the retracted movement of the work pressing member 4, an assembled bushing is discharged from the socket 9 by means of an ejector latch 39 that has tooth 40 that engages with the flange b of the sleeve B to pull the assembled bushing out of the socket 9 during the movement of the member 4 away from the member 3 as will be apparent from the drawings. The latch 39 is held by a spring 41 in a position in which the tooth 40 is slightly above the bottom edge of the flange B, and during the closing movement of the movable member 4 the forward - end- of the latch 39 is moved downwardly by engagement with the flange of the sleeve B as it moves past the flange b and into a recess 42 formed in the supporting member 12. After the tooth 40 has passed the flange b, it is lifted by the spring 41 to a position where it will engage with the flange b upon retracting movement of the member 4. While the insert A, sleeve B and Core C could be fed to the machine by hand, it is preferable that they be fed automatically, and to this end three chutes 43, 44 and 45 are provided. The chute 43 is shaped to receive a row of sleeves B and is positioned with its discharge end directly over the seat 12a of the retractable supporting member 12. The -chute 44 is shaped to receive a row of inserts A and is positioned directly over the seat 15a of the retractable supporting member 15, and the chute 45 is positioned directly over the

opening 18. The positioning portions 28 of the slides 24 are directly beneath the chute 43 and provide an extension of the chute when they are positioned over the block 12. Like wise, the positioning portions 25 of the slides 24 form extensions of the chute 44 when they are positioned over the supporting block 15. A sleeve, an insert and a core are delivered one at a time from each of the chutes 43, 44 and 45; and, in the machine shown herein, the discharge of the three parts to be assembled from the three chutes is simultaneous. The discharge from each of the three chutes may be controlled by suitable means such as solenoid-controlled stop pins or the like to release the lowermost article in each chute while simultaneously arresting movement of the article immediately above the lowermost article so as to prevent the delivery of more than one article at a time. The discharge from the chutes may be timed so as to deliver one sleeve, one insert and one core during each cycle of operation of the machine. At the end of each cycle of operation of the machine, the member 4, the slides 24, the alining pin 30, and the plunger 19 are all in their fully retracted positions. During the cycle of operation the sequence of operations is as follows: (a) a motor is energized to move the slides 24 to work-receiving position; (b) the feed control members for the three chutes 43, A4 and 45 are simultaneously acutated to discharge a sleve, an insert and a core simultaneously, the sleeve B being delivered to the seat 12a, the insert A being delivered through the opening 18 into the bore 8; (c) immediately after delivery of the sleeve, insert and core to the machine, the positioning pin 30 is advanced into engagement with the insert A supported by the positioning portions 25 of the work positioning slides 24 and the slides 24 are immediately moved to their retracted positions; (d) after the slides 24 have been moved out of the path of the member 4, a motor is energized to move the member 4 toward the mem ber 3 to move the insert into engagement with the sleeve. and to press the sleeve into the socket and the insert into the sleeve as shown in Figs. 3 and 4. (e) before completion of the closing movement of the member 4, the alining pin 30 is withdrawn and a reciprocating stroke is imparted to the plunger 19 to move the plunger and core into engagement with the

insert and to force the core into the insert as shown in Fig. 5 of the drawings; (f) immediately after the insertion of the core, the work pressing member 4 is moved to its retracted position; and (g) when the plunger 19 and work pressing member 4 reach their retracted positions, the cycle of operations is completed, the assmbled bushing having been ejected from the machine by at latch 39 during the retracting movement of the member 4. The sequence of operations may be controlled by any suitable timing mechanism, such for example as a series of control cams driven by a common drive shaft and a timer motor far initiating the operation of the various parts of the machine in the proper sequence during each revolution of the drive shaft. Such series of cams may, for example, control a series of switches to energize and denergize solenoids which effect operation of the slides 24, cause a discharge of a sleeve A, an insert B and a core C from the chutes 43, 44 and 45, cause advancing of the alining pin 30 into engagement with an insert on the seat 15a, cause movement of the work pressing member 4 toward the stationary work pressing member 3, and cause reciprocation of the core inserting plunger 19. Such timer mechanism may be designed normally to operate continuously and to cause a complete cycle of operations to be performed to assemble a bushing during each revolution of the timer shaft. The tubular elastic and deformable insert of the present invention is designed to facilitate entry of the core C into the insert and to eliminate the necessity of a tapered core pilot or other means to expand the portions of the insert in advance of the leading end of the core during assembly of the resilient bushing. The resilient bushing shown herein is specifically designed for use on vertically disposed pivots or the like but it will be understood that the insert A of the present invention may, in the normal unstressed condition, be externally cylindrical throughout its length or may have various other shapes in a bushing or joint designed for such use. It will also be understood that the present invention also applies to various other types of resilient mountings wherein the tubular rubber member is mounted on an inner core with its axis horizontal or otherwise disposed. Figure 2 is drawn to scale and shows the tubular rubber insert A in the normal unstressed condition prior to assembly in the resilient joint. The insert has a central opening 5 that extends the length of the insert and has an internal cylindrical surface 6 that extends the major portion of said length. The normal diameter of the surface 6 is not substantially different from that of the alining pin 30 but is substantially less than the external diameter of the cylindrical core

C. The surface 6 may, for example, have a normal diameter from about ten to twenty percent less than the external diameter of the core so that the insert A must be expanded substantialy to receive the core. In order to facilitate entry of the core during assembly without the use of fluid pressure means or other special means to expand the insert radially in advance of the leading edge of the core, a narrow internal peripheral groove 46 and a thin flexible peripheral lip 47 are provided at the end of the surface 6 first engaged by the core during assembly of the bushing. The groove is located substantially in the plane of juncture of the enlarged portion a and the body portion 56 of the insert A. The lip forms one side of the groove and is pressed toward the groove during entry of the core. The lip 47 is preferably tapered to facilitate entry of the leading end of the core and the groove 46 is filled with a solid or plastic tubricant 22, preferably throughout its circumference, to lubricate the exterior cylindrical surface of the Core C. Any suitable rubber-to-metal lubricant may be used in the groove 46, but the lubricant is preferably non-liquid at normal temperatures and preferably is sufficiently viscous so that it holds its shape and stays in and substantially fills the groove when the axis of the insert is in horizontal position. The lubricant may, for example, be mutton tallow or other solid lubricant which does not swell or otherwise damage the rubber substantially. The groove 46 controls the position of the lubricant and the amount thereof and acts as a lubricant reservoir. The lubricant in the groove 46 may be sufficient to permit entry of the core C into the insert A, but it is usually preferable to apply a light weight lubricant to the insert A, the sleeve B and the core C in the conventional manner by fogging or spraying the same as they pass into the assemblying machine. As herein shown, the insert A is annular and has a uniform cross-sectional shape throughout its circumference whereby the groove 46 and the lip 47 are annular. The opening 5 is enlarged from the lip to the end of the insert A to provide a counterbore with an inner surface of revolution 48 for guiding the core C into the insert. The surface 48 in cludes a cylin,drical portion 49 with a diameter greater than that of the surface 6 and substantially equal to the external diameter of the core C and a tapered outwardly-flaring frusto-conical portion 50 at the mouth of .the opening 5. As herein shown, the lip 47 is tapered to provide a frusto-conical shoulder 51 extending from the surface 48 to the radially inner surface 52 of the lip which has the same radious as the surface of revolution 6. The external surface of the insert A may be generally cylindrical or may have any other suitable shape; but, as~herein shown, the insert

has an annular enlarged portion a with an annular shoulder 53 which engages the radial flange b or the sleeve B in the assemble bushing. The insert also has a reduced end portion 54 that is tapered to provide a frusto-conical-surface 55 with a diameter normally less than the internal diameter of the sleeve B. The insert has a body portion 56 between the end portions a and 54 with a radial thickness, in the normal unstressed condition as shown in Fig. 2, substantially the same as that of the end portion a. However, the radial thickness of the body :portion is reduced more than about half when it is compressed between the sleeve and the core so that its thickness in the assembled bushing is not substantially greater than the normal thickness of the end portion 54. A rubber insert embodying the present invention may, for example, increase in length more than 50 percent and even asmuch as 150 percent or so when it is placed under radial compression between a rigid sleeve and a rigid core. As herein shown, the body portion 56 has an external cylindrical surface 57 substantially throughout its length and- an annular shoulder 58 extending radially from the frusto-conical surface 55. The diameter of the surface 57 is not substantially different from the internal diameter of the sleeve B so that the rubber insert A may easily be inserted into the sleeve without compressing the rubber substantially. However, the sleeve is preferably tapered or enlarged slightly at its flanged end to facilitate entry of the rubber insert. As herein shown, the internal surface of the sleeve is in the form of a surface of revolution 59 having a cylindrical portion 60 extending the major portion of the length of the sleeve and having a cylindrical portion 61 of a slightly greater diameter adjacent the flange b. The surface of revolution 59 extends the length of the sleeve and, in the assembled bushing has a length substantially equal to that of the radially compressed body portion 56 as shown in Fig. 5. The inner surface 6 of the insert is of substantially smaller diameter than the outer diameter of the inner sleeve or core C. Since the diameter of the outer surface 57 of the insert A is not greatly different from the dia meter of the inner surface 60 of t

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