4756 4760.output

* GB785163 (A)

Description: GB785163 (A) ? 1957-10-23

Improvements in and relating to a vessel closing device and apparatus forassemblingthis device with the vessel

Description of GB785163 (A)

KI 1 1 i: i 1 'a '2 -' I_ __ 9 ' _1 '1r - PATENT SPECIFICATION 785,163 Date of Application and filing Complete Specification: Nov 22, 1955. No 33339155. Application made in France on Nov 23, 1954. Application made in France on March 29, 1955. Complete Specification Published: Oct 23, 1957. Index at acceptance:-Classes 125 ( 2), E( 2 F: 3 B 2 D); and 125 ( 3), T 7 D 2 A. International Classification:-B 67 b. COMPLETE SPECIFICATION Improvements in and relating to a Vessel Closing Device and Apparatus for Assembling this Device with the Vessel I, BE Rw ARD N Ico L As LAEAR Gu, a Citizen of the French Republic, of 38, Avenue Eiffel, Sevres (Seine et Oise), France, 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:- The present invention relates to closing devices for glass jars and the like for condiments, mustard and other products and for any other vessels with or without a neck, the vessel comprising around its entrance a conical or ribbed outer circular cylindrical face. The problem of closing or sealing such vessels is generally greatly complicated, since the diameter of these vessels, and especially glass vessels, varies considerably, owing to wear in the machine in which they are made For example, in the case of glass vessels in current production, the diameter of the edge of the vessel entrance varies by

as much as one to several millimetres. The object of the invention is to provide a closing device which is simple in construction, adapts itself to these variations, has excellent sealing qualities and permits the vessel to be successively opened or closed any number of times. This closing device is of the known type comprising a metal-lid or cap, whose transverse wall is lined, at least in the region of its periphery, with a sealing member, and whose lateral wall comprises, starting from said transverse wall, a cylindrical portion extended by a flared portion which terminates in a formed-over edge or rim This closing device is characterized in that the cap com-prises in its cylindrical portion, at a level below the inner face of the sealing element, a number of peripheral slits each one of which extends in the peripheral direction in such manner as to subtend at the centre of the cap an angle of at least 45 , the lower lPrice 3 s 6 d l edges of these slits being pushed inwardly of the cap in such manner as to form in the upward extension of the flared portion an arcuate projection facing toward the transverse wall of the lid and extending inwardly 50 relative to the adjacent cylindrical portion of the cap, this projection being capable of bearing resiliently against the side wall of the vessel to be closed. The arcuate projections thus formed are 55 both stiff and perfectly resilient owing to their large peripheral extent, which would not be the case if the projection had a small peripheral extent, since the latter would form merely small bosses which would readily 60 yield when applying the cap. With such a cap provided with these arcuate projections, it is possible to engage the closing device on a vessel of the abovementioned type, whose outer face decreases 65 in size after an entrance rib or rim ofmaximum diameter, and resiliently to lock the closing device on this vessel, on the sole condition that in the free unstressed state the closing device has such dimensions that the inner 70 upper edge of each arcuate projection has a diameter less than said maximum diameter of the vessel and that, moreover, the inner diameter at the base of this projection is greater thadn said maximum diameter of the 75 vessel. If these conditions are satisfied, when the vessel is inserted in the cap the projections yield resiliently and then, after having passed by the portion of the vessel having the large 80 diameter, close inwardly resiliently under this portion and ensure a secure closing, so that there is no risk of the cap detaching itself under the effect of vibration or blows. Whether the vessel is cylindrical or has an 85 outer face comprising an entrance having the maximum diameter, the closing device may always

be readily removed by the user since the flared portion of the cap constitutes a ready means for_ engaging the fingers of the 90 hand cupped over the cap and thereafter raising it. In a preferred arrangement, the lower edge of each slit and the adjoining portion of the cap are pushed inwardly of the latter over a height which is zero at each end of the slit and gradually increases up to midway of the ends of the latter, whereas in the radial direction, said edge is progressively inwardly offset from the inner face of said cylindrical portion over, a short length starting from the two ends of the slit, the rest of this edge being arcuate and concentric with the longitudinal axis of the cap. When closing the vessel with the cap, these projections are urged outwardly to an extent which is the greater as the diameter of the outer edge of the entrance of the vessel is greater, and, on account of the great stiffness of these projections due to the abovementioned manner of forming them, these projections, when the cap is pressed by hand onto the vessel, result in deformation of the adjacent unslit portions of the cap, and in particular its flared portion Thus in the course of closing the vessel it is necessary to maintain this flared portion inside a cylindrical face which, in so preventing its deformation, causes ipso facto a permanent tilting or deformation of the projections despite their stiffness and thus adapts them to the outer face of the vessel and reduces their gripping force, even if this outer face has a diameter distinctly greater than the minimum diameter of the allowed tolerance in the dimensions of the vessel. Another object of the invention is to provide a closing head for a vessel closing machine which permits obtaining this result. This head is characterized in that it comprises in combination: a block provided at its upper end with means for fixing this block to the moving part of the vessel closing machine, an axial skirt which extends downwardly of this block and has an inner face comprising a cylindrical portion extended by a lower flared portion, the diameter of the cylindrical portion being substantially equal to the maximum or base diameter of the flared portion of the caps to be assembled with the vessel, a plunger axially movable in the skirt, a resilient device for urging the plunger to a lower operative position, and locking devices resiliently retractable for maintaining this plunger in the operative position in opposition to a force equal to at least the force exerted on the plunger when forcing the cap on a vessel whose entrance has an outer diameter which is the maximum permissible diameter in accordance with the allowed tolerance for the dimensions of the vessel. When the closing head is lowered on to the vessel to be closed, on which the cap has been previously positioned, the cap is forced to the

full extent on to the vessel before the lower edge of the flared portion of the cap finally engages the cylindrical portion of the skirt, which has for result to constrain the inner projections of the cap to tilt and 70 adapt themselves to the dimensions of the vessel. Experiments have shown that by using this closing head, after closing the vessel, irrespective of the extent to which the dia 75 meter of the vessel exceeds that of the minimum diameter of the allowed tolerance which is considerable, being of the order of several millimeters, the cap conserves its strictly circular shape and the projections are de 80 formed in such manner that they continue to apply themselves resiliently against the vessel with a force just sufficient to ensure that the cap continues to close the latter notwithstanding handling and accidental 85 blows while permitting an easy opening of the vessel by engagement of the fingers of the hand under the flared portion of the cap. By contrast, closing the vessel by hand would result in deformation of the cap and 90 not the projections, and the vessel would be practically impossible to open for entrance diameters in the neighbourhood of the maximum diameter of the allowed tolerance for the dimensions of the vessel 95 Further features and advantages of the invention will appear from the ensuing description. In the accompanying drawings, to which the invention is in no way restricted: 100 Fig 1 is an elevational view with a part cut away of a cap embodying the invention; Fig 2 is a plan view of the under side of this cap; Fig 3 is a sectional view of the cap taken 105 along line 3-3 of Fig 1; Fig 4 is a partial elevational and a partial diametral sectional view of the head of a vessel closing machine adapted to force the cap on to the vessel; 110 Fig 5 is a similar partial view showing the head and the cap at the end of the closing operation on a conventional glass pot of conical shape having an entrance whose outer diameter is the minimum permissible 115 diameter of the tolerance; Fig 6 is a sectional view taken along line 6-6 of Fig 5 of this pot and closing device; Fig 7 shows the shape the cap assumes if it is forced on to the pot by hand, when its 120 flared portion is unrestrained, the pot having a diameter which is the maximum permissible diameter; Fig 8 shows the shape obtained, with the same glass pot having said maximum per 125 missible diameter, when the cap has been applied by means of the closing head shown in Fig 4; Fig 9 shows side by side at 1, II and III sectional views on an enlarged scale taken 130 785,163 of this edge is therefore arcuate and has its centre situated on the axis XX. It will be noticed, furthermore, that the inner projection 10 formed by each offset portion (Fig 1), when viewed from the side, 70 has a substantially crescent shape, has an upper portion which is curved

upwardly so that the inner face 11 (Fig 9) adjacent the inner edge 9 is substantially parallel to the longitudinal axis XX of the cap, or in any 75 case slightly inclined relative to this axis, the maximum angle c being of the order of 250 (see Fig 9 diagram 1) The constant offset x of the arcuate portion rs of each projection is such that the diameter 80 D (Figs 3 and 6) between the edges 9 of two diametrally opposed projections is less than the diameter D 1 (see Figs 5 and 6 and the diagram I of Fig 9) of the outer edge of the entrance of the vessel R 1 85 Thus this closing device could even be placed in position by hand on the vessel R 1, the projections 10 separating resiliently so as to permit entry of the vessel However, irrespective of whether it concerns a vessel 90 having a diameter D 1 or a larger diameter, the allowed tolerance in the diameter obviously increasing with the diameter of the vessel and being of the order of one or some millimetres in the case of conventional 95 jars or pots for mustard or other condiments, an automatic machine would be used for closing the vessel, this machine being provided with a special closing head embodying a feature of the invention 100 Fig 4 shows such a head It comprises a block 12, provided with a screw-threaded' portion 13 at its upper end which permits fixing this block to the moving part of the vessel closing machine (not shown in the draw 105 ing) Thus this head is subjected by the machine to an operative movement in the direction of arrow fl and a return movement in the opposite direction Provided at the lower part of the block 12 and concentric 110 with the longitudinal axis YY of the latter is a skirt portion having a peripheral edge 13 a. This skirt comprises in succession in the upward direction a first conical portion 14 followed by a cylindrical portion 15 whose 115 diameter D 3 is exactly equal to the outer diameter of the base of the flared portion 4 of the cap A. The cylindrical portion 15 of the skirt is connected by a peripheral shoulder 16 to 120 another cylindrical portion 17 of smaller diameter, this latter portion being axially extended by a circular recess 18 of still smaller diameter Slidable in the portion 17 is a pressure-applying cylindrical plunger 125 19 which is urged downwardly by a relative weak spring 20 engaged in the recess 18. The plunger 19 is held in its lower operative position shown in Fig 4, in which it is urged by the spring 20, by several locking devices 130 along lines I-I, II-II, and III-III of Figs. 6 to 8; Fig 10 shows an application of the invention to the closing of a metal vessel having a flanged-over upper outer rim or lip; Fig 11 is a horizontal sectional view taken along line 11-11 of Fig 10; Fig 12 is a vertical sectional view taken along line 12-12 of Fig 10 on an enlarged scale; Fig 13 is a longitudinal sectional view of a

modification of the closing head just before it enters into operation, the cap being shown in position on the vessel but not forced thereon, and Fig 14 is a similar view after the cap has been forced on to the vessel. In the embodiment shown in Figs 1 to 3, the closing device comprises the combination of a cap or lid A and a sealing disc B housed inside the cap A. The cap A is formed of a metal pressing comprising, starting from a transverse wall 1, which is preferably provided with a recessed peripheral portion 2, a cylindrical wall 3 from which extends a flared conical or like portion 4 which terminates in a rim 5 formed over inwardly. The sealing disc B may be of any type composed of impermeable cardboard or any other material, it may also be annular or even replaced by a coating or layer of plastic material poured directly on the transverse wall of the cap, over the entire surface of the latter or merely in the region of the peripheral portion 2. According to the invention, the cylindrical portion 3 of the cap comprises, evenly distributed on its circumference, very narrow slits 6 parallel to the wall 1 The angle a subtended at the centre of each slit (Fig 3) is equal to at least 450 and preferably to around 50 -70 , the angle b subtended by each unslit portion between each slit being equal to at the most 45 and preferably to around 40 -20 ' The lower side or edge 8 of each slit is pushed or offset inwardly of the cap in the following manner: Firstly, the cylindrical portion 3 and the start of the flared or conical portion 4 of the part of the cap situated below each slit 6 is offset in a region whose dimension in the direction parallel to the axis XX of the cap (see Fig 1) increases from zero at the two ends m and p of the slit 6 to a maximum at n midway of these ends. Secondly, in the radial direction of the cap (see Fig 3), the offset increases progressively at qr and ts over a short peripheral length starting from the two ends of the slit, the offset remaining constant between r and S so that between these two points the inner edge 9 of the offset side 8 is at a constant distance from the axis XX; the portion rs 785,163 which are retractable in opposition to resilient means, each locking device comprising a ball 21 which is capable of engaging an annular recess 22 formed in the plunger 19 under the action of the pressure exerted by a spring 23 disposed with the ball in a radial hole 24 formed in the block 12 This spring bears at one end against an adjusting screw 25, screwed in a tapped portion of the hole 24, and applies pressure at its other end against the ball through the medium of a washer or disc 26 rigid with a rod 27 slidably mounted in an axial bore formed in the screw 25 This rod extends

beyond the end of the screw and permits ascertaining, by the amount it protrudes from the screw, whether the ball 21 is in its retracted position. The pressure applied by the spring 23 is so adjusted by means of the screw 25 that the sum of the radial forces exerted by the springs 23 is such that the force required to urge back the balls of the locking devices and displace the plunger 19 upwardly is equal to at least the force required to force the cap on to a vessel whose entrance has the maximum permissible diameter within the tolerance. The setting of the closing head is carried by a trial closing operation on a vessel, the head being so set that the observed projection of the rods 27 from the screws 25 occurs after the cap has been forced on to the vessel. The closing operation is carried out in the following manner; The cap A, provided with its sealing member B, is placed on the upper edge of the vessel, such as the vessel BR shown in Fig 5 This vessel is then placed on a support (not shown in the drawing), the head a is lowered, the plunger 19 bears against the cap and forces it over the end of the vessel, this plunger remaining stationary relative to the block 12 due to the combined and simultaneous actions of the spring 20 and the springs 23 Thereafter, as soon as the closing device bears through the medium of its sealing member B against the upper edge of the vessel, the head C continuingto descend, the plunger 19 is urged upwardly relative to the block 12, the balls 21 being shifted out of the annular groove 22 The block 12 continues to descend relative to the plunger 19 and the vessel B' until it reaches the position shown in Fig 5, in which the whole of the cap B, including the flared position 4, is engaged in the cylindrical portion 15 of the head skirt (see Fig 5 and diagram I of Fig 9)If the vessel is similar to vessel R 1, that is has an outer diameter D' corresponding to the diameter D between the edges 9 of the cap, the latter merely enters the portion and the inner projections 10 undergo practically no deformation apart from a very slight flexion for making the diameter D between inner edges 9 equal to the outer entrance diameter D' of the vessel. If, on the other hand, the vessel is larger, such as the vessel R 2, i e if it has a larger entrance diameter D 2 as shown in Figs 7 and 8, the various elements behave in a 70 different manner. As has been explained above, if the cap A were forced on to the vessel R 2 by hand, the diameter D of the inner edges 9 increases to the value D 2 and, owing to the stiffness of 75 the projections 10 there results, as shown in Fig 7 and in diagram II in Fig 9, an outward displacement of the projections 10 and a consequent deformation of the cap, the flared portion 4 tending to adopt a square 80 shape (see Fig 7) However, owing to the action of the closing head C, explained above

with reference to Fig 5, at the end of the closing operation the whole of the cap is engaged in the cylindrical portion 15 of the 85 skirt of the block 12 and this causes the flared portion 4 of the cap to resume the strictly circular shape shown in plan in Fig 8 The rim of the cap resumes the maximum outer diameter D 3 This brings 90 about a tilting of the projections 10 each of which assumes the shape shown in diagram III of Fig 9 Each projection is straightened (see the position of the upper edge 8 which has moved to substantially the level of the 95 upper side of the slit 6 and the angle formed by the inner face 11, which has decreased). Each projection 10 therefore assumes a final position in which it now exerts on the vessel R 2 only a limited pressure sufficient to 100 maintain the cap exactly in the same manner as the cap on the vessel R', whose extrance diameter is the minimum diameter allowed by the tolerance. Figs 10 to 12 show an application of the 105 invention in the case of a vessel R 3 consisting of a metal box which is cylindrical and provided at its upper end with a peripheral rim or lip 28 formed outwardly The cap A with its sealing member B is of the type 110 described above having a cylindrical portion 3, a flared portion 4, and projections i Oa which differ from the above-described projections in that their arcuate upper portions form a supporting face 29 for the rim 28 of the 115 box (see Figs 11 and 12). The cap behaves exactly in the same way as those described above when it is forced on to the box R 3 and the closing operation is effected with the closing head C in the 120 manner described above. Figs 13 and 14 show a modification of the closing head. This head comprises a support block consisting of a plate 30 on which is fixed by 125 screws 31 a ring 32, the latter and the plate having a common axis YY. The inner cylindrical face 33 of the ring is connected by a conical portion 34 to a peripheral inner flange 35 surrounding a 130 785,163 the flared portion 4 of the cap A However, the member 45 is detachable and, if desired, a member 45 may be used having a cylindrical portion 50 o whose diameter is slightly less than the diameter of the base of the cap A 70 for the reason explained hereinafter, the diameter of the cylindrical portion 50 being in this case slightly greater than that of the portion 50 a. Vertically movable in this skirt is a plunger 75 comprising two parts transversely movable relative to one another, the upper part being guided in the skirt and the lower part, which forms the pressure applying part, being therefore transversely movable relative to 80 the skirt. The upper part comprises a piston 53 and a ring 54 attached to the

under side of this piston by screws 55 The ring 54, like the ring 32 of the upper support block, has an 85inner cylindrical portion 56 connected by an inner conical portion 57 to a flange 58 which surrounds a circular aperture 59 The outer face of the ring 54 is recessed at 54 a so as to permit the use of a member 45 whose 90 cylindrical portion 50 a is slightly smaller than that of the portion 50, if this is desired. It will be observed that an ejecting spring is disposed between the piston 53 and the plate 38 The lower part forming the 95 pressure-applying part of the plunger comprises the combination of a circular member 61 and a base 62 which is attached to this circular member and is adapted to bear against the upper face of the transverse wall 100 of the cap A. The member 61 comprises an upper flange whose diameter corresponds substantially to that of the minimum diameter of the conical portion 57, so that as this member 105 61 rises within the ring 54 there is an increasing radial clearance between its periphery and the inner face of this ring, this radial clearance reaching a value equal to at least the aforementioned radial clearance v between 110 the skirt ( 44-45) and the aperture 36 when the flange of the member 61 is raised above the level of the maximum diameter of the conical portion 57. The portion of the member 61 depending 115 from the flange is cylindrical and its diameter is less than the diameter of the aperture 59 of the ring 54 by the amount 2 v. The member 61 is normally held applied against the flange 58 of the ring 54 in the 120 same manner as the skirt is held, applied against the flange 35, i e by means of springs 63 interposed between the piston 53 and a disc 64, itself bearing against the member 61 through the medium of balls 65 freely disposed 125 in a cage 66. The plunger unit ( 53-54, 61-62) is held e in its lower position shown in Fig 13 by a number of locking devices or pins 67 which f slidably mounted in radial holes 68 formed 130 circular aperture 36 The faces 33, 34 and aperture 36 are coaxial and the flange 35 is perpendicular to the axis YY. Provided on the axis of this plate is a screw-threaded rod 37 for fixing the block ( 30-32) to the moving part of the vessel closing machine (not shown in the drawings) so that the closing head is subjected to a forward operative stroke in the direction of arrow fl and a return stroke in the opposite direction, the support S for the vessel R 4 being in this case stationary. It will be observed that the reverse arrangement may be adopted, the head being fixed and the support S upwardly movable Alternatively, these two arrangements may be combined. Disposed inside the chamber formed in the ring 32 under the plate 30

is a circular plate 38 whose diameter corresponds substantially to that of the small diameter of the conical portion 34, so that in moving this plate 38 upwardly relative to the ring 32 there is obtained between the cylindrical portion 33 and the periphery of the plate 38 a radial clearance which gradually increases from zero to a value u obtained when the plate 38 reaches the portion 33. The plate 38 is held applied against the flange 35 by the action of springs 39 which are housed in holes 40 in the plate 30 and bear against a back plate 41 Disposed between the latter and the plate 38 is a thrust ball bearing comprising balls 42 freely disposed in a cage 43 from either side of which they protrude. The plate 38 serves as a support for the skirt adapted to act on the flared portion 4 of the cap A This skirt comprises two annular members 44 and 45 connected together by screws 46, the unit 44-45 being fixed to the plate 38 by further screws 47. The annular members 44 and 45 are cylindrical and their outer diameter is smaller than the diameter of the aperture 36 of the ring 32 by an amount v The latter is less than u (radial clearance between the plate 38 and the cylindrical face 33) but greater than the maximum offset the axis XX of the vessel to be closed may assume relative to the axis YY of the support block 31-32. This skirt comprises an inner recess which is ordinarily concentric with the axis YY and has a conical portion 48, a second conical portion 49 having less conicity, and three cylindrical portions, that is a portion 50 o pertaining to the member 45, and portions and 51 pertaining to the member 44, the portion 51 having a diameter greater than the portion 50 so as to provide between these portions a shoulder 52. It will be observed that in the presently described embodiments the diameter of the cylindrical portions 50 and 501 exactly -65 corresponds to the diamneter of the base oi 785,163 785,163 in the ring 44 and are capable of engaging by a spherical portion 69 formed thereon in an annular recess 70 formed in the piston 53 (one locking device only is shown in the drawings) Each locking pin 67 is urged toward the axis YY by a spring 71 disposed in a tube 72 screwed in a tapped portion of a radial hole 68 The spring 71 bears against the locking pin 67 and against an adjusting nut 73 screwed on the tube 72, which is screwthreaded for this purpose An axial rod 74 screwed in the locking pin 67 extends beyond the end of the nut 73 through an axial hole formed in the latter This rod 74 permits, by observation of the amount by which it extends from the nut, ascertaining whether the locking pin 67 has been pushed back The tension of the spring 71 is adjusted by means of the nut 73 as in the arrangement described above. The vessel closing operation is carried out in the following manner:

The vessel R' is placed on the support S, the cap A, provided with its sealing member B, is placed more or less horizontally (no particular care being required in so positioning the cap) on the upper edge of the vessel on which the inneredges of the projections 10 rest. It could occur that the longitudinal axis XX of the cap and vessel does not exactly coincide with the axis YY of the support block 30, for example it may be offset from this axis an amount W which is less than or at the most equal to the value v (in constructing the closing head, v is chosen equal to at least the greatest possible offset w) The axes of the skirt and plunger can coincide with the axis YY owing to the fact that the plate 38 and the flange of the member 61 rest respectively on the flanges 35 and 58 and are in consequence held in this position by the conical portions 34 and 57. After slightly lowering the closing head, the base 62 of the plunger bears against the transverse wall 1 of the cap in a position offset an amount W from this cap Thereafter, the base 62 of the plunger is held in position in the transverse direction owing to frictional contact with the wall 1 of the cap A and it retains this offset position until the end of the closing operation The head continues to descend, compresses the springs 39 and 63 and presses the cap against the vessel until the flared portion 4 of the cap bearsagainst the conical portion 48 of the skirt ( 44-45) At this moment, owing to the offset position of the vessel R' and its cap relative to the axis YY, the unit comprising the skirt ( 44-45), the plate 38 and the piston 53, is subjected to a lateral force from the cap A and this unit is displaced transversely, substantially without friction or effort owing to provision of the two thrust ball bearings including balls 42 and 65, both relative to 655 the support block ( 30-32) and relative to the member 61 until its longitudinal axis coincides with the axis XX of the vessel Ro and cap A (Fig 14) and thus becomes offset an amount w relative to the axis YY of the support block 30 70 Thereafter the skirt ( 44-45) continues to descend in perfect axial alignment with the cap A, the back plate 41 eventually bears against the inner face of the plate 30 and the base 62 bears against the ring 54 (Fig 14), 75 and the cap A is forced fully onto the vessel without the plunger unit ( 53-60) moving upwardly relative to the skirt owing to the resistance of the spring 60 and the springs 71 of the locking pins 67 80 As soon as the cap A bears through its sealing member B against the upper edge of the vessel, the head continuing to descend, the piston 53 is urged upwardly relative to the skirt The locking pins 37 are then shifted 85 out of the annular recess 70 The unit comprising the members 30, 32, 44 and 45 continues to descend relative to the plunger ( 53-61) until it reaches the position shown in Fig 14, so that the whole of the cap A, 90 including its flared portion 4, is engaged in the cylindrical

portion 50 a of the skirt. If the vessel Ro is a vessel whose outer diameter is equal to that of the arcuate edges 9 of the projections of the cap, the latter 95 merely enters the cylindrical portion 504 and the inner projections 10 undergo hardly any deformation, apart from a very slight flexion adapted to give said diameter of the inner edges 9 a value equal to the outer diameter 100 of the vessel. If, on the other hand, the vessel is larger, that is has a greater entrance diameter, when the cap engages, at the end of the -closing operation, the cylindrical portion 50 a, the 105 flared portion 4, which would become deformed if it were not supported, is held strictly circular Hence the projections 10 are tilted and slightly flattened and assume such position that they exert on the vessel only 110 a limited pressure sufficient to hold the cap in position exactly as in the case of a vessel having the minimum diameter permitted by the tolerance for this dimension. If it is desired to decrease the pressure 115 applied by the projections on the vessel, the member 45 of the skirt may be replaced by another member having a cylindrical portion 50 ' whose diameter is slightly smaller, which would result in an increased 120 tilting of the projections. Although specific embodiments of the invention have been described hereinbefore, it must be understood that many modifications and changes may be made therein 125 without departing from the scope of the invention defined in the appended claims.

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* GB785164 (A)

Description: GB785164 (A) ? 1957-10-23

Manufacture of polyvinyl acetal sulpho-acids


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r- ' t& - A-_ 1 PATENT SPECIVICATION Date of Application and filing Complete Specification: Nov 22, 1955. l No33486155. Application made in Germany on Nov 24, 1954. Complete Specification Published: Oct 23, 1957. Index at acceptance:-Class 2 ( 6), PLA, P 1 D( 1 B: XC: 1 X: 3: 5: 6), P 1 (P: T 2). 55.164 International Classification:-CO 8 f. COMPLETE SPECIFICATION Manufacture of Polyvinyl Acetal Sulpho-Acids We, -FARBWERKE HOECHST Ax TIENGESELLSCHAFT vormals Meister Lucius & Br Unning, a body corporate recognised -under German Law, of Frankfurt (M)-Hoechst, 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: - Polymerisation products -containing sulphoacid groups have recently acquired an intcreasing importance in industry -Thus, wate-rCE 2 , _I -CH 01-O Hf H # I OH 2 CH:-OHsubstances of-this kind have been proor example, as adhesives, as auxiliary or the textile industry, for the photo 15 1 industry and as tanning agents, while e high polymers containing sulpho-atid ire used, among other purposes, as ion ers. way of preparing such substances con 20 reacting polyvinyl alcohol with aide:ontaining S,-groups In the icourse of action polymeric acetals are obtained ig to the following reaction: CH 2 CH-O CH 2 C-R-503 m ct-O (R =-bivalent organic hydrocarbon radical) The present invention is based on the obserThe reaction cang

for example, -be carried vation that polyvinyl acetal sulpho-acids can -out by condensing polyvinyl alcohol in aqueous -be prepared by reacting in aqueous media solution with aldehyde suipho-acids in the polyvinyl alcohol or polymers containing the presence of acid condensing agents, -such as vinyl alcohol group with unsaturated aldehydes mineral acids, in the presence of sulphurous acid. When employing this process, -it is there One can, for example, proceed in such a fore necessary to start frdm aldehyde sulpho manner that the calculated quantity of an acids The preparation-of the latter may entail unsaturated aldehyde is introduced into an difficulties and leads to by-products -which aqueous solution whiclh may, for exaiple connecessitate -an -additional purification Thus, taim up to 25 per cent of the polymer,-aand for example, butyraldehyde sulpho-acid is, then at about room temperature gaseous suladcording to "Monatshafte fiir -Chemie", Vol phur dioxide is conducted into the solution 12, page 546 ( 1891), accessible by the reac while under reflux and while stirring The tion, of crotonaldehyde -with sulphurous acid reaction mixture is then heated -to tempera-in water The compound formed during this tures of about 800 C During the reaction it is reaction by the addition of 2 mols of H 1 SO, not necessary to add an additional acid con'(addition to the double bond and addition to denwsing agent In most cases the viscosity the aldehyde group) is then converted into the increases strongly in the beginning, while it -aldehyde sulplho-acid by treatment at an decreases again after the reaction mixture -has -elevated temperature In the course of this been heated for a prolonged period When the treatment there easily occurs a discolouration reaction has terminated, which is shown by which has unfavourable effects when this the disappearance of the free aldehyde, the aldehyde is used -for the alcetalisation of poly aqueous solution is heated in -an open vessel vinyl alcohol in order to remove the excess SOY If desired, , viy lchl rib 2 5,16 a knowr, anti-foaming agent, such as a silicone, may be added in orbiter to avoid the formation of foam The analysis of the polymer obtained shows that a quantity of sulpho-acid groups equivalent to the quantity of combined aldehyde is chemically combined. It was surprising and not to be expected that the two reactions, acetalisation and aidition of sulphurous acid, follow a simultaneous, quantitative course, all the more so since it was known that, when acetalizing polyvinyl alcohol with unsaturated aldehydes, it is easily possible that products may be obtained which are completely insoluble owing to cross-Jink-7 ing The present process has, moreover, the advantage that the solutions do not contain. an additional condensing agent and are thusi absolutely free from low molecular constituents As examples, acrolein, crotonaldehyde,

a-methacrolein, chiloro-crotonaldehyde, sorbaldehyde and ethyl-hexenal are suitable-as unsaturated aldehydes As compounds of high molecular weight containing hydroxyl groups, which are suited for thisreaction, there may be mentioned: polyvinyl alcohols of various molecular -weights, for example between 10,00 and 500,000, -in which case 2 to 98 per cent of the originally existing acyl groups of the polyvinyl ester may still' be present in the-macromolelcule, also copolymners of vinyl esters, for example vinyl acetate, vinyl propionate and vinyl benzoate, together with other copolymerizable compounds such as acrylic eaters, methacrylic esters, vinyl chloride, crotonic acid, maleic acid ester or fumaric acidester, after corresponding hydrolysis of the acyl groups The reaction as described can be carried out in an aqueous phase containing varying quantities (up to 50 per cent) of water-soluble organic compounds, such as, for examiple, aliaohols=(methanol, ethanol), acetone, dioxane, tetrahydrofurane The introduction of the& sulphur dioxane into the reaction mixture takls place at tenmperatures of about 00 C to room -temperature. The reaction -is started and cairied on by heating the reaction mixture to temperatures upto 800 C. By selecting the required quantity of the aldehytde used, it is possible to introduce the desired number of sulpho-acid acetal groups. It is, of course, also possible to react at the same -time, in addition to the unsaturated aldehydes, also with saturated aldehydes, for example acetaldehyde, proipionaldehyde, butyraldehyde, isobutyraldehyde, {heptylaldehyde, octylaldehyde, benzaldehyde and naphthylaldehyde By varying -the different possibilities described, products of different properties are accessible in a very easy technical manner. According-to the quantity of the sulpho-acidacetal groups in proportion to the residual molecule, high -polymers soluble in water -(large content ouf silpho-acid-acetal gr ups, for example, when ccetalizin, between 50 and 100 per cent of the -OH groups present), or high polymers which can be emulsified or which are capable of swelling only (low content of sulpho-acid-acetal groups, for example, when acetalizing -from 0 F to 50 per cent of the 70 -OH groups present), can be prepared. Such products find manifold applications in industry -In the textile industry they are used in acid or neutralised form as anti-static preparation agents, as sizing agents and also 75 generally as-ithickening agents and adhesives, as auxiliary agents for dye-stuff pastes, as antistatic preparations for photographic films and, as protective colloids, for use for example during the emulsion polymerisation of un 80 saturated compounds Those products are especially advantageous which are prepared from a polyvinyl alcohol

(which still contains 2 per cent of the acetyl groups originally present in the polyvinyl acetate) and equl 85 molecular quantities of crotonaldehyde. The following Examples illustrate the invention, the parts being by weight: EXAMPLE 1 - 4.5 Parts of polyvinyl alcohol (K value 70), 90 obtained by complete alkaline hydrolysis of polyvinyl acetate, are dissolved in 45 5 parts of water 3 5 Parts of crotonaldehyde are added 3 5 Parts of sulphur dioxide are introduced at room temperature While stirring, 95 the solution is gradually heated to 650 C to TC The batch is at first highly viscous. After having been stirred for some time, it becomes thinner It is stirred for another three hours at 65 'C to 70 C Under a pressure 100 of about 100 mm Hg, the excess sulphur dioxide is removed and about 5 parts of water are distilled off After cooling, the reaction mixture is neutralised with about -7 5 parts of sodiuin hydroxide solution (of 25 per cent 105 strength) and filtered through a pressure filter. Approximately 60 parts ot an aqueous solution of about 20 per Icent strength of the sodium salt of the polyvinylbutyral sulphonate are obtained 110 EXAMPLE 2- 7.5 Parts of polyvinyl alcohol (K value 30), still containing 12 % of acyl groups, are dissolved in 42 5 parts of water 5 7 Parts of crotonaldehyde are added 5 7 Parts; of sul 115 phur dioxide are introduced at room temperature. The operation is continued as indicated in Examnple 1 48 Parts of solution of about 30 per cent strength of polyvinylbutyral sulpho 120 acid are obtained. EXAMPLE 3. 3.0 Parts of polyvinyl alcohol (K-value 30), obtained by complete alkaline hydrolysis of polyvinyl acetate, are dissolved in 47 O parts 125 of water 1 8 Parts of acrolein are added: 2 4 -Parts of sulphur dioxide are introduced at room temperature The operation is continued as indicated in Example 1 After neutralisation wih about 2 5 13 g 185,164 195,i 64 parts of ammonia of 25 per cent strength, 50 parts of an aqueous solution of about 16 per cent strength of the ammoniumr salt of polyvinylpropional sulphonate are obtained. EXAMPLE 4. 4.5 Parts of polyvinyl alcohol which is free from acyl groups (K value 70) are dissolved in 45 5 parts of water 6 0 Parts of ethylhexenal and 2 parts of acetaldehyde are added. 3 5 Parts of sulphur dioxide are introduced at a temperature of 00 C-10 C. The operation is continued as described in Example 4 1 No increase in

the viscosity is observed During the distillation, part of the uis changed ethyl hexenal distils over After neutralisation with about 10 parts of sodium hydroxide solution of 25 per cent strength, about 40 parts of an aqueous mixed acetal solution of about 19 per cent strength of the sodium salt of' the polyvinylacetaldehvde-ethylhexenal sulphonate are obtained.


* GB785165 (A)

Description: GB785165 (A) ? 1957-10-23

Improved apparatus for indicating fatigue in a structure


COMPLETE SPECIFICATION Improved Apparatus for Indicating Fatigue in a Structure I, Bo KLAS OSCAR LUNDBERG, a Subject of the King of Sweden, of 16, Blverviigen, Bromma, Sweden, 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: The provision of apparatus has been suggested, which in structures actuated by loads of varying magnitudes render possible counting of the number of times elongations reach or exceed certain threshold values in a structure for the purpose of facilitating, with the guidance of the indications of the counting apparatus, a computation of the extent to which the structure has become fatigued. This method suffers from the drawback that said computation is relatively complicated and time-wasting. A considerable difficulty in elongation

counters of this kind also resides in that an alteration of the average load about which the fluctuating loads change may considerably upset the indication in so far that with an increase of the average load, for example, a greater number of positive elongations will be counted than corresponds to the damage of fatigue. The present invention has for its object to obviate these disadvantages, above all by the fact that the apparatus renders possible a direct reading or indication of the degree of fatigue imparted to a structure through a certain arbitrary number of elongations of varying magnitudes. An advantage of the invention resides in that if facilitates an automatic compensation for that upsetting effect for an indication of the damage of fatigue which may be caused by an alteration of the average load. The invention refers to such apparatus of the type indicated hereinabove that renders possible an indication of the fatigue in a structure and that may be applied to a building element comprised in the structure. The invention is principally distinguished by the feature that the apparatus comprises members adapted to be actuated by the elongation in the structural element, while being so devised as to integrate elongation changes of varying magnitudes in the structural element, in a manner such that the contribution to the integration of any elongation change of a certain magnitude is in a certain relation to the number of load changes up to breakdown at the magnitude of the elongation change in consideration for the fatigue curve which is topical for a part of the structure sensitive to fatigue. On the condition that the so-called part damage theory (breakdown occurs at n 2--=1 wherein 8 is the summation symbol, N n represents a number of load changes the amplitudes of which fall within certain marked intervals and N represents the number of load changes up to breakdown) may be taken to hold true with sufficient accuracy, the apparatus may be so constructed that said contribution to the integration is inversely proportional to the number of load changes up to breakdown. The members of the apparatus may comprise a transmission gearing so devised that a primary movement brought about by the elongation is transformed through the gearing into a secondary movement, the ratio of gear of which relatively to the primary movement increases with an increase of the primary movement, the increase of the ratio of gear then corresponding to the progress of the fatigue curve. The basic theory of the invention and a few examples of applying the same are elucidated in the accompanying drawings. Figure 1 shows diagrams illustrating schematically the relation of the load change in the fatigue curve of the structure, Figures 2-3 show two projections at right angles to each other of an

apparatus according to the invention with a continuous gear ratio, which is suitable in cases of a comparatively small difference between the possibly occurring different amplitude levels. Figures 4, 5 and 6 show three projections at right angles to each other of a further embodiment, where the transmission gearing is- arranged in steps, in which the difference between the amplitude levels may in principle be of any magnitude. Figure 7 is a perspective view of a detail of the last-mentioned embodiment. Figure 8 is a diagram elucidating the effect of the changes of the average load. Figure 1 shows on the right hand side thereof a fatigue curve or SN-curve, where the ordinate S represents the load amplitude and N represents the number of load changes up to breakdown for a structural element. As is well known, the curve refers to Ioading at con stant amplitude levels Actually, it frequently occurs, for-nstance in connection with a wing of an airplane, that a structure is subjected to mixed ladings, the rule bering then that in a certain period of the service life the number of load changes of a small magnitude -is far greater than the number of load changes of a greater magnitude. Farthest to the left in Fig. 1, a number of such load changes of different amplitudes are indicated. The middle portion of the figure illustrates a soalled histogram indicating a number of load changes n,, n and rut,, the amplitudes of which fall within the marked intervals I, II,- m. The limits of these interyals are marled by the letters e, b, c and d. In applying the part damage theory to this simplified example, it holds true that a break down occurs when ni n, n, + + =1 N1 N2 N2 Here, N1,-N2 and N, refer to the numbers of load changes up to failure at an SN-fatigue atamplitude levels S1, S2, S,, which are repre sentative of the part damage within the res pective intervals. With small intervals, these levels may be taken to be at the middle of the

interval. The load change numbers N1, N2, N2 as indicated may correspond, for example, to 105, 105 and 104 load changes. Even a reasonable increase of the load amplitude thus involves a very great reduction of the number of load changes up to breakdown. This means that the part-damage brought abbut by a cer tain load;level, such as S2, which is only slightly greater (for instance 25 % greater) than another load level S1 may be 10 times greater or even greater than the damage caused by a load change at the lower level S1. To make it possible bring about an integration -of a cumulative damage effect caused by load changes of a varying magnitude, it is thus necessary to provide for a variable transmis sion ratio involving that the contribution to the integration of large load amplitudes will be much greater than the contribution from only inconsiderably less load amplitudes. Finally, it might be mentioned that in Fig. 1 the average load has been taken to be equal to zero in the left hand portion of the figure for all fulldrawn liners. The conditions with an increase of the average load corresponding to a positive elongation are indicated by dotted lines. In Figs. 2 and 3 on the drawings, 10 designates the structural element, the fatigue of which is to be indicated, while 12 denotes a plate carrying the members comprised in the apparatus. The plate 12 is non-displaceably connected to the element 10 at one point, that is to say by means of a rigid bolt 14, said plate being retained in a suitable position in front of the element 10 at a second point by means of connecting members, which at this point render possible elongations or displacements being transmitted to the plate. Said connecting members consist of a bolt 16 screwed into the element 10, a distance sleeve 18 and a bushing 20 of resilient material, such as rubber, fitted into the plate, said sleeve and bushing having the bolt 16 extending tnere- through. A rod 22 is connected to the element 10 at one point, the point of attachment, by means of a bolt 24 having one end of the rod mounted thereon. In the example shown, the rod 22- extends in the proximity of and in parallel to the lower edge of the element 10 and has its other end connected to a movable member in a transmission gearing. Said member consists of wheel 26 in the example illustrated in Fig. 2, which wheel is rotatable on the bolt 14 extending through the plate 12, and the end of the bolt is mounted on a pin 28 on said wheel. When the element 10 is elongated or shortened at the lower edge thereof by reason of a varying loading of the

element-positive or negative elongation-the rod 22 will move to- and fro, to the right in Fig. 2 at a positive elongation, and to the left at a negative elongation. The movements corresponding to a positive elongation are accu- raulated and indicated in the apparatus by means of members to be set forth in the following. If desired, the apparatus may instead be devised to record only negative elongations. The wheel 26 forms the one pulley in a belt transmission, the other pulley 30 of which has a considerably small diameter than the pulley 26 and is mounted by means of a bolt 32 on the plate 12. By means of the belt 34, the movement of the wheel. 26 is transmitted to the pulley 30 and is changed to a greater rotary movement of a further pulley 36 having the small pulley 30 secured thereto. The pulley 36 is comprised in a transmission gearing having a continuously varying gear ratio, said transmission gearing comprising otherwise a cam disk 38 with a preferably spiralshaped outline 40 and a belt 42 with a member incorporated into the same and shown in the form of a helical spring 44. The cam disk 38 is mounted on a bolt 46 on the plate 12, and the cam disk has in turn one end of a rod 48 mounted thereon. The other end of said rod is provided with a hook 50, which is kept by a spring 52 in resilient engagement with the periphery of a toothed wheel 54. A pawl 55 prevents the toothed wheel 54 from being turned backwardly. The input rotary movement of the pulley 36 is augmented at a continuous increase of the transmission ratio to a many times greater rotary movement of the cam disk 38 about the bolt 46. The oscillations of the cam disk 38 are accumulated by means of the stepping mechanism consisting of the rod 48 and the toothed wheel 54, into a unidirectional rotary movement, which is transmitted to an indicating member by a changedown transmission contrivance. This transmission contrivance is shown as a small pulley 56 secured on the toothed wheel 54, a belt 58 and a larger pulley 60 mounted on a bolt 62 on the plate 12. The rotary movement of the pulley 60 is changed down further in a transmission contrivance 64, the output shaft of which has arranged thereon an indicating disk 66 provided with an index 68 adapted to be read off against a scale 70 on a fixed annular disk 72. When a structural element was mentioned hereinabove, such element referred to the part having the apparatus secured thereto. It is evidently possible to make arrangements so that the structure comprises another element, which is more sensitive to fatigue than the element to which the plate is secured, provided that the member which is sensitive to fatigue will be subjected to elongations that are proportional to the elongations of the structural element Positive elongations in the lower part of the structural element 10 manifest themselves as greater or smaller displacements of the rod 22

to the right in the drawing and as a corresponding rotary movement of the pulley 26. In Fig. 2, the three different positions 0, 1, 2 are marked of the attaching bolt 24 of the rod, the pin 28, the pulley 36, the pulley 38, the pawl 50 and the indicating disk 60 with fullArawn lines with respect to the position 0 and with chain-dotted lines with respect to the positions 1 and 2, corresponding positions then having the same designation. The inconsiderable rotary movement of the pulley 26 indicated by the radii at 0, 1 and 2 brings about a greater but proportional rotary movement of the pulley 36. On the other hand, the rotary movement of the cam disk 38 from the initial position 0 to the final position 2 is increased further, according as the cam disk swings in the direction of the arrow, inasmuch as the belt 42 successively loses its contact with the periphery of the cam disk, so that the active radius is diminished with an increase of the transmission ratio in consequence thereto. The angle of the rotary movement during the movement from the position 1 to the position 2 is consequently many times greater than the movement between the positions 0 and 1, in spite of the fact that the corresponding angles of the rotary movement of the input pulley 36 are of equal magnitude. The rotary movement of the toothed wheel 54 transmitted by means of the rod 48 and the pawl 50 will be of the same character. The primary movement caused by the elongations and transmitted into the transmission gearing has been changed into a secondary movement, the increase of the transmission ratio then corresponding to the shape of the fatigue curve. The rotary movementis changed down a much greater number of times, so that the output rotary movement of the indicating disk 66 is only called upon to comprise a rotary movement of a single revolution during the whole life of the structural element. By reading off the position of the index 68 on the scale 70 one may obtain direct information as to the continued fatigue of the structural element. The scale has an index 70b thereon, which marks the limit that must not be surpassed by the fatigue life of the element. When the apparatus is mounted on another element, for instance on one with bettter fatigue properties, a further index 70" may indicate a corresponding limit. By reading off the scale one may readily peroeive when the structure in question is fatigued to such an extent that the same should be taken out of service. It is obvious that the apparatus shown in Figs. 2 and 3 here only indicates the one kind of elongations, namely the positive ones. In connection with the other kind of elongations, it is understood that the pawl 50 will drag along the teeth of the toothed wheel 54, which is prevented by the pawl 55 from turning in a

counterclockwise direction in Fig. 2. In the embodiment shown in Figs. 5-8, positive as well as negative elongations will be integrated and indicated. As in the preceding form of embodiment the apparatus is here provided with a mounting plate 12, which is secured to the structural element 10 at a mounting point, determined by a fixed bolt 14, and with a bolt bond 16 permitting displacements in parallel to the plane of the plate, besides which the rod 22, which is sensitive to elongations of the element 10, is secured with one end thereof at a point of attachment on the element 10 determined by the bolt 24. The other end of the rod 22 is mounted on a pin 78 secured to a single-armed lever 80 comparatively near the mounting bolt 14 thereof. At a greater distance from the pin 78, the lever 80 is pivotally connected to a frame 84 by means of a link 82, said frame being displaceably guided between rollers 85 mounted on the plate 12 so as to permit of being readily displaced rectilinearly in parallel to the plate. The frame is broadly rectagular, and provided at the lower portion thereof are members capable of transmitting movements of the frame caused by positive elongations, while at the upper portion thereof there are members to transmit movements caused by negative elongations. The members provided at the lower as well as at the upper portion are arranged behind one another and adapted to transmit movements of the arm 84 caused by load amplitudes of varying magnitudes. Three members are arranged behind each other, the first one of which transmits small, the next one somewhat larger, and the third one still larger movements, and it should be observed that further members may be arranged in an analogous manner. The members broadly consist of stepping mechanisms, namely of step ping pawls 86, 88, 90 and of stepping wheels 92, 94, 96, which are advanced by the stepping pawls. The first stepping pawl 86 is mounted on a - pin 98 on the frame 84, and the second stepping pawl 88 is mounted on a pin 100 on a double-armed lever 102, which is mounted on a pin 104 rigidly secured to the plate 12; the third stepping pawl 90 is pivotally mounted on a- pin 108 on the upper end of a single-armed lever 110, the lower end of which is mounted on a pin 112 rigidly secured to the plate 12. The stepping pawls are kept in intial positions determined by abutments 114, against which they are held set by means of springs 116. The stepping pawl 86 is formed as a double-armed bell crank lever, one arm of which cooperates with the abutment 114. The lever 102 and the single-armed lever 110 carrying the stepping pawls 88 and 90 are kept in their- initial positions by means of springs 118, 120 and abutments 122 and 124, respectively. The angular stepping pawl 86 is adapted upon the displacement of the frame 84 for a certain

distance to be brought into engagement with an abutment 126 rigidly secured to the plate .12, whereby it is, on having turned the stepping wheel 92 forwardly through a certain angle, brought out of engagement therewith. Secured to a projection 128 of the frame 84 is a preferably adjustable carrier in the form of a set screw 130 adapted to actuate the lower arm of the double-armed lever 102, in order thus to swing it in a counter-clockwise direction, so that the stepping pawl 88 is moved to the left in Fig. 4 so as to turn the stepping wheel 94 in a clockwise direction. This movement takes place against the action of the spring 118 tending to return the lever 102 into its initial position. Arranged in a second projection 132 is a carrier in the form! of a set screw 134 > which is intended to be moved in an analogous manner by the frame 84 into engagement with the single-armed lever 110 so as to swing the latter in a clockwise direction about its pivot 112 against the action of the spring 120, so that the stepping pawl 90 is moved to the right so as to turn the stepping wheel in a counterclockwise direction. The stepping wheels 92, 94, 96 are each splined to an axle 136, 138 and 140, respeclively, and these axles are pivotally mounted in the plate 12 and in a bearing bracket 142 secured thereto and extending in the longitudinal direction of the plate 12 in front of the stepping wheels. The axles 136, 138 and 140 have gear wheels 144, 145, -146, 148, 150, 152 secured thereto, by means of which the movements of the stepping wheels are transmitted at a drastic change-down onto a large gear wheel 154, which is splined onto an output shaft 156. The small gear wheel 146 is rigidly connected to the large gear wheel 148, and the large gear wheel 150 is rigidly connected to the small gear wheel 152. The shaft 156 is mounted in the plate 12 and the bearing bracket 142 and carries a pointer 158 on the end thereof projecting through the strap, said pointer pointing at a scale on an annular dial-plate, which is secured to the front side of the bearing bracket. The pointer 158 and the dial-plate 160 form the indicating contrivance, on which the degree of fatigue of the structure may be read off, and th dial-plate is provided with a corresponding scale (0--9). To the wheel 145 only rotary movements in one direction may be transmitted from the stepping wheel. For this purpose some arbitrary suitable free wheel mechanism may be made use of In the example shown, said mechanism consists of the gear wheel 144 secured to the stepping wheel 92, the teeth of which gear wheel are formed as ratchet teeth, and of a carrier 162 made in the form of a pawl, said carrier being secured to a part of the peripheral portion of the gear wheel 145, said part being devoid of teeth (see Fig. 7). The carrier 162 is resilient and in engagement with the teeth of the

wheel 144, in a manner such as to be able to entrain the gear wheel 145, when the stepping wheel 92 and thus the wheel 144 are turned in a counter-clockwise direction, but not when they are turned in a clockwise direction. Similar free wheels may also be incorporated between the stepping wheels 94, 96 and the respective gear wheels arranged on their corresponding axles. Arranged in the upper portion of the frame are dogs, such as stepping pawls 164, 166, 168 to transmit movement to the stepping wheels 92, 94 and 96, respectively, at movements of the frame 12 caused by negative elongations of the element 10, that is to say, at a displacement to the left in Fig. 4 from the initial position shown by fulldrawn lines. These stepping pawls are formed so as to be operative to turn the stepping wheels 92, 94, 96 in the same direction at a negative elongation in which they are operative to turn the stepping pawls 86, 88, 90 at a positive elongation. The effects of the positive and negative elongations will thus be added. The pawl 164 is formed by one arm of a three-armed lever rotatable on the frame, the opposite arm of which has an obliquely bevelled end surface 170 to cooperate with a pin 172 secured to the plate 12. A spring 176 secured to a fixed abutment 178 tends to rotate the three-armed lever clockwise to engage its third upwardly directed arm 174 with said abutment 178 whereby the pawl 164 takes the initial position shown by full-drawn lines. The pawl 166 is arranged on a doublearmed lever 180 actuated by a spring 182 in complete agreement with the pawl 88 of the lever 102 described hereinbefore, and may be actuated by a carrier in the form of a set screw 184 which is screwed into a projection 186 of the frame. The initial position of the lever is determined by a fixed abutment 188 on the plate 12. The pawl 168 forms one arm of a bell-crank lever mounted on the frame, the other arm 190 of which is retained by a spring 192 in the initial position against an abutment 194 secured to the frame 12. The mode of operation of the embodiment shown in Figs. W7 is broadly as follows: As stated, an initial position 0 for the various parts is designated by fullwdrawn lines. Furthermore, a number of positions at positive elongations of the ement 10 are marked in the drawing, Fig. 4, by dash lines , b, c and d, while a number of positions at negative elongations are marked by lines - a, - b, - c and - d. These lines correspond to the limits of the intervals I, II and 111 within which the amplitudes of the load changes fall according to the histogram in Fig. 1, and in Fig. 4 these intervals are also marked between the limit lines. With a positive elongation, the rod 22 is moved to the right in Fig. 4, and at a negative elongation it is moved to the left, as indicated

by the arrows 196 and 198, respectively. A movement of the rod 22 and thus a swinging movement of the lever 80 from the position 0 to the position a shall not have any effect on the stepping mechanism, and consequently shall not be transmitted to the indicating contrivance, since said movements correspond to elongations so small as to cor;es- pond only to an inconsiderable fatigue damage or do not even reach the fatigue limit B in Fig. 1 for the material of the element. To render possible this free stroke of the frame 84, the stepping pawl 86, which at a positive elongation shall first come into engagement with its stepping wheel 92, is arranged with the point thereof at a distance from the nearest tooth of the stepping wheel 92, cor responding to a movement between the positions O--cn. Said point is thus brought into engagement with this tooth only when the arm 80 and the frame 84 have reached the position a. With amplitudes, which are greater than the movement between 0 and a but not greater than the movement between 0 and b, the stepping pawl 86 will turn the stepping wheel 92 by one or a few steps, depending on the magnitude of the movement within this interval. At this rotary movement the gear wheel 144 is entrained, which is also the caseover the resilient carrier 162-with the gear wheel 145 to which the carrier is secured. This rotary movement is changed down by means of the gear wheels 148, 146, 152, 150 to a little rotary movement of the output gear wheel 154 and the shaft 156, so that the pointer 158 is turned through a small angle in a clockwise direction. When the frame has reached the position b, the carrier 130 arranged on the projection 128 of the frame, which carrier is in the initial position at a distance equal to the difference between the limits b and 0, has just been brought into contact with the lower alm of the double-armed lever 102 carrying the other stepping pawl 88. At the same time the downwardly directed arm of the stepping pawl 86 has just been brought into touch with the fixed abutment 126. Now, if the amplitude of the movement of the frame 84 is so great that the position b is transgressed and the position c is reached, the following will take place: The stepping pawl 86 is swung in a clockwise direction through oooperation with the abutment 126 so as to be brought out of engagement with the stepping wheel 92, and consequently has no longer any entraining effect on the latter. The carrier 130 swings the double-armed lever 102 in a counter-dockwise direction about its pivot 104, so that the stepping pawl 88, which is in engagement with the stepping wheel 94 in the initial position, will be moved to the left in Fig. 4 so as to turn this stepping wheel in a clockwise direction. This rotary movement is transmitted through the shaft 138 to the gear wheel 146 non-rotatably arranged thereon, and

further, at a change-down through the gear wheels 150, 152 and 154, to the shaft 156, so that the pointer 158 is further advanced into a new position. Simultaneously with the rotary movement of the gear wheel 146 caused by the stepping wheel 194 the large gear wheel 148 will also be rotated, so that the gear wheel 145 is caused to rotate, that is to say, in a counter-clockwise direction in Fig. 4. However, this rotary movement is not transmitted to the gear wheel 144 and the stepping wheel 92, inasmuch as the resilient carrier pawl 162 then drags rearwardly along the periphery of the gear wheel 144. If the movement of the frame 84 is so great that the position c is transgressed and the frame reaches the position d, the following will take place: The stepping pawl 86 is still held out of engagement with the stepping wheel 92 by the fact that its lower arm is still in contact with the abutment 126. Immediately at the transgression of the position c, the stepping pawl 88 releases the tooth of the stepping wheel 94 with which it had been in engagement, inasmuch as this tooth is now moved upwardly so far that the pawl is unable to retain the same. Thus the stepping wheel 94 is no longer actuated by the stepping pawl 88 and consequently also not by the move ment of the frame 84.- - In the position C, On the other hand, the carrier 134 on the pro jection 132 of the framo has just been brought into contact with the-single-armed lever 110, and at a continued movement of the frame 84 the lever 110 is therefore swung in a clock wise direction about the fixed pivot 112, whereby the stepping pawl 90 is moved to the right in Fig. 4 so as to- turn-the stepping wheel 96 in a counter-clockwise direction. The movement is transmitted through the- shaft 140 and the gear wheels 150, 152 to the gear wheel 154 and tion to the damage integration will be substantially underrepresented on the negative side to the same extent in which it is overrepresented on the positive side. This is elucidated in Fig. 8, where the pointer 158 of the indicating device is conceived as advanced from the position 0 to the position A through positive elongations, and further advanced by an equal angle, that is to say, to the position B, through negative elongations, when the average load is equal to zero. At an increase of the average load the pointer will have turned through a greater angle than previously on account of the positive elongations that is to say, to the position A1, whereas the negative

elongations give birth to a smaller turning movement, namely, only from the position A1 to the position B1. The position B1 coindudes with or is in the propinquity of the position B, that is to say, the resulting advancement of the pointer will be approximately the same as previously. The denomination " stmctiral.element" in the foregoing refers to that part of the structure to which the apparatus is secured. However, the apparatus need not be secured to the part of the structure which is sensitive to fatigue, but may be mounted on another part, provided the part which is sensitive to fatigue is subjected to elongations that are proportional to the elongations in this part. The invention is not limited to the embodiments shown but are only to be regarded as illustrative examples. Instead of arranging the stepping pawl 86 at a distance from its stepping wheel in the initial position, it will be possible to transmit a play in the lever system formed by the rods 22, 80 and 82 for instance by arranging a few of the connecting bolts in an elongated aperture. What I claim is: - 1. An apparatus for indicating the fatigue in a structure, said apparatus being intended to be secured to an element contained in said structure, characterized in that the apparatus comprises members actuated by the elongation in the element and so devised as to integrate the effect of elongation changes of varying magnitudes in the element, in a manner such that the contribution to the integration of any elongation change of a certain magnitude is in a certain relation to the number of load changes up to breakdown, at the magnitude of the elongation change in consideration, for the fatigue curve which is topical for a part contained in the structure and sensitive to fatigue. 2. An apparatus according to Claim 1, characterized by the same being so devised that the contribution to the integration is inversely proportional to the number of load changes up to breakdown. 3. An apparatus according to Claim 1, characterized in that the members comprise a transmission gearing which is so devised that a primary movement effected by the elongation is transformed through the trans mission gearing into a secondary movement, the ratio of gear of which relatively to the primary movement increases with an increase of the primary movement, the increase of the ratio of gear then corresponding to the shape of the fatigue curve. 4. An apparatus according to Claim 1, 2

or 3, characterized in that the members com prise an integrating device consisting of one or more wheels, such as gear wheels, which are driven in the same direction through the effect of a positive and/or a negative elonga tion. 5. An apparatus according to Claim 1., 2 or 3, characterized in that the transmission gear ing comprises a curve of such configuration as to transform the primary movement into the secondary movement at a continuous increase of the ratio of gear. 6. An apparatus according to Claim 5, characterized in that the transmission gearing comprises a first part, such as a belt trans mission, into which the movements caused by the elongations are introduced and trans mitted proportionally, a second part compris ing the curve, and a third part, in which the secondary movement brought about by the curve is changed down for being transmitted to an indicating device. 7. An apparatus according to Claim 4, characterized in that the integrating device consists of a number of stepping mechanisms with stepping pawls for an integration of posi tive elongations and with stepping pawls for an integration of negative elongations and with corresponding stepping wheels the various stepping pawls for each kind of elongations being arranged per se to actuate the stepping wheels successively, in a manner such that one stepping pawl is operative at elongations of certain amplitudes, a second stepping pawl is operative at elongations of greater amplitudes, and, optionally, one or more further stepping pawls are operative at elongations of still greater amplitudes. 8. An apparatus according to Claims 4 and 7, characterized in that a member adapted to introduce the elongation movements into the integrating device is devised with a free stroke in such manner as to become inoperative for integration of small elongations, preferably elongations below the fatigue limit for the

material of the structural element in consider ation. 9. An apparatus according to Claim 7 or 8, characterized in that a gear wheel transmis sion common to the stepping mechanism is arranged between the stepping mechanism and an indicating device, free wheels being incorporated at one or more points between the gear wheels of the various stepping mech anisms, said free wheels being so devised that when a stepping wheel intended for greater

* GB785166 (A)

Description: GB785166 (A) ? 1957-10-23

Salts of oxyalkylated fatty amines

Description of GB785166 (A) Translate this text into Tooltip



PATENT SPECIFICATION. 1 N Inventor: ALLAN EDWARD CHESTER 7 (@ Date of Application and filing Complete Specification: Nov 29, 1955. No 34176/55. Complete Specification Published: Oct 23, 1957. Index at acceptance:-Classes 2 ( 3), C 2 B 3 (A 1: B: E: G 1: G 5); and 82 ( 2), E 3. International Classification:-CO 7 c C 23 g. COMPLETE SPECIFICATION Salts of Oxyalkylated Fatty Amines 855166 We, POOR & COMPANY, a

corporation of the State of Delaware, United States of America, of Railway Exchange, Chicago 4, State of Illinois, 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 new and useful organic compounds and more particularly to reaction products of aldonic acids and oxyalkylated fatty amines and to a method for the preparation thereof. One of the objects of the invention is to produce complex organic compounds which are soluble in acid solutions. Another object of the invention is to produce new and useful reaction products of oxyalkylated fatty arnines and aldonic acids. A more specific object of the invention is the preparation of new and useful salts of oxyalkylated fatty amines and gluconic acid. Another specific object of the invention is the preparation of new and useful acid stable water soluble oxyalkylated fatty amine gluconates. A further object of the invention is the provision of a new and improved method for preparing compounds of the type referred to above Other objects will appear hereinafter. In accordance with the invention it has been found that new and useful products are obtained by reacting aldonic acids with oxyalkylated fatty amines The preferred products are acid soluble and are especially suitable for use in acidic aqueous liquids, for example, acid pickling solutions It will be understood, however, that the products may be employed for many other purposes. The invention will be further illustrated but is not limited by the following Example in which the quantities are stated in parts by weight unless otherwise indicated. EXAMPLE. A product was prepared by mixing together Parts A soybean amine oxyethylated with approximately 10 moles of ethylene oxide, containing 20 carbon atoms in its alkyl chain and having an average molecular weight of 714 % gluconic acid The reaction between the amine and the aldonic acid to form the salt takes place at ordinary temperatures or may be effected by refluxing at elevated temperatures The resultant product is a cationic wetting agent which is usually stable in acid solutions, for example, 6 to 20 % sulfuric acid solutions or 101 to 15 % hydrochloric acid solutions. The addition of -,I to 1 part of this product to 1000 gallons of a 6 to 20 % sulfuric acid solution or a 10 to 15 % hydrochloric acid solution increases the penetrating properties of such solutions in acid pickling, reduces the rusting tendency during the transfer of the pickled object from the pickling solution to a rinsing bath and assists in removing carbonaceous deposits.

Other reaction products of oxyalkylated fatty amines with aldonic acids may be prepared by substituting equivalent quantities of other oxyalkylated; fatty amines for the oxyethylated soybean amine and by substituting other aldonic acids for the gluconic acid in the foregoing Example. The fatty amines are amines derived from fatty acids and contain 8 to 60 carbon atoms, but preferably 8 to 36 carbon atoms They differ from each other in the number of carbon atoms in their alkyl groups, in the degree of saturation of the alkyl groups and in the number of alkyl groups attached; to the amino nitrogen. Examples of fatty amines are those derived from soya beans, those derived from coconut oil and those derived from tallow The oxyalkylation of these amines to produce oxyalkylated amines is effected by reacting the amines with ethylene oxide, 1,2-propylene so 86.5 13.5 oxide, or mixtures of ethylene oxide and 1,2 that the oxyalkylation of the fatty amine repropylene oxide The number of moles of the suits in the formation of 2 oxyalkylene chains alkylene oxide is at least 4 moles per mole of on the primary nitrogen atoms of the fatty primary fatty amine, and for the purpose of amine thereby producing a tertiary amine The the present invention the preferred products products of the present invention are therecontain around 10 to 20 oxyethylene or oxy fore reaction products of aldonic acids and propylene groups per molecule of primary tertiary oxyalkylated fatty amines.


* GB785167 (A)

Description: GB785167 (A) ? 1957-10-23

Improvements in or relating to packing devices for pistons


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CH336705 (A) FR1137988 (A) NL92415 (C) CH336705 (A) FR1137988 (A) NL92415 (C) less Translate this text into Tooltip



; -,1 N PATENT SPECIFICATION 7859167 Date of Application and filing Complete Specification: Dec 16, 1955. / No 36183/55. Application made in Germany on Feb 19, 1955. Complete Specification Published: Oct 23, 1957. Index at acceptance:-Class 122 ( 1), B 7 E( 2 A: 2 B). International Classification:-FO 6 j. COMPLETE SPECIFICATION Improvements in or relating to Packing Devices for Pistons We, HEINZ TEVES and ERNST AUGUST T Ev Es, both German citizens, trading as A FRFD TEVES M As Oe NEN-und A Rm ATUHENFABRI KG., 41-53, Rebstbcker Strasse, Frankfurt/ Main, 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:- The idea of providing pistons, particularly those for use in master cylinders for hydraulic brakes, with an annular chamber intermediate their length is known, this chamber being filled with pressure fluid. The idea of connecting this annular chamber to the piston via an aperture or a pipe to the fluid reservoir -of the braking system is known, the reservoir being subjected to atmospheric pressure The annular chamber is provided on its rearward side with a packing sleeve, adapted to seat in a groove in the piston, which preferably has two oppositely directed sealing lips bearing against the cylinder wall. While the fluid in the annular space is normally subjected to

atmospheric pressure, pressure in excess of atmospheric may build up inside the annular space in certain cases, for example when replenishing the system from a source of fluid under pressure In this connection there is the danger of the packing sleeve being pushed out of its groove under the action of the pressure, so that the sleeve is displaced, and no longer has a sealing action It is then possible for fluid to penetrate along the inside of the sleeve on the piston, even at atmospheric pressure,. and to be lost, which makes the brake unusable. In order to prevent this disadvantage, the sleeve according to the invention is provided with an inner annular body portion from which the lips extend, said body portion being adapted to seat upon the piston lPrice. and to be axially confined between radial shoulders thereon, and having a lip adapted to co-operate with one of said shoulders to prevent radial displacement of the sleeve When the pressure in the annular chamber 50 increases this additional lip is acted on by the fluid pressure, and secures the inner body of the sleeve against radial displacement; at the same time, fluid is prevented from passing via the sleeve along the 55 piston. In order further to secure the inner body of the sleeve between the radial shoulders, the internal diameter of the packing sleeve is, according to a further feature of the 60 invention, made smaller in the free condition at its seating surface on the piston than the external diameter of the piston at this point, and on the other hand the external diameter of the rearwardly directed lip 65 which is adapted to seal against the external air is so dimensioned as to be somewhat larger than the internal diameter of the cylinder when the sleeve is fitted on the piston According to a further feature of 70 the invention, the lip sealing against the external air ends short of the rearmost of the radial shoulders between which the inner body portion of the sleeve is confined. A constructional example of the subject 75 of the invention is illustrated in the accompanying drawing. Fig 1 shows the sleeve according to the invention as incorporated in a master cylinder of a hydraulic braking system, and 80 Fig 2 shows a cross-section of the same sleeve in the free condition. The piston 2 is displaceably arranged in the master cylinder 1 (Fig 1) The annular chamber 3 is closed at the front by the 85 piston head, not shown, with the associated seal, while the packing sleeve 4 provides sealing on the rear side of the piston. The sleeve 4 has an inner body 5, which is snapped into a corresponding piston 90 .' 1 t 1 ' _' 1 groove 6 The lip 7 provides security against the entry of air from behind, while the lip 8 seals

against the annular chamber. A space 9 is provided between the sleeve intermediate the two lips 7 and 8 and the cylinder wall. The sleeve also has a third lip 10, which lies against the annular shoulder 11 of the piston. If the sleeve is put under pressure in the chamber 3, the lip 10 is pressed against the shoulder 11, and holds the inner body 5 firmly in position, even if fluid pressure tries to push the sleeve into the space 9, in order simultaneously to lift the inner body out of the groove 6 The internal diameter of the inner body 5 is smaller in the free condition than the internal diameter of the piston groove 6; in addition, the external diameter of the lip 7 in the free condition is greater than the internal diameter of the cylinder 1.
