* GB785423 (A)

Description: GB785423 (A) ? 1957-10-30

Method and apparatus for the mechanical separation of a part from a rod- ortube-like work piece

Description of GB785423 (A)

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COMPLETE SPECIFICATION Method and Apparatus for the Mechanical Separation of a Part From a Rod- or Tube-like Work Piece I, HELMUT SICKEL, a German Citizen, of Springeitwiete 9, Hamburg 1, Germany, do hereby declare this 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 invention relates to a method of and apparatus for the mechanical separation of a part from a rod- or tube-like work piece which is made of a material capable of being softened by heat. The invention is particularly, but not exclusively, concerned with the mechanical closing of ampoules or the like by the separation of the tip thereof. In the known drawing processes for rods and tubes and also in the known sealing of ampoules, the piece to be separated is removed by

drawing whilst the point of separation is being heated. Thus a softened zone produced by the heating is continuously drawn to a strand with a simultaneous reduction in diameter and, in the case of tubes and ampoules, with a continuous reduction in wall thickness, this strand being finally melted through in the zone of the hottest flame. However, in rods, tubes and ampoules, pointed ends are not desired and in tubes and ampoules the danger of fracture is increased by the thinly drawn wall. Frequently the thin wall produced by the drawing process, cannot withstand the internal pressure produced by the heat and blows out; alternatively it may be melted through when it is not removed in good time from the flame area. The resistance to pressure is further reduced since the thin wall sharply merges into a solid glass knob resulting from the melting of a piece of the glass thread produced by the drawing process whereby un- favourable stress ratios are formed. Moreover, the glass threads hanging at the drawn end are not only troublesome but, in the case of ampoules, present a serious danger as the glass particles resulting from the breakage of these threads float in the air and can fall into open ampoules. Moreover, special difficulties arise with these drawing processes, if the tube-like work pieces to be treated have different diameters or wall thicknesses, and this very frequently occurs particularly in the tips of ampoules. In such cases the glass or other material is occasionally not sufficiently softened when due for drawing as determined by the timing of the machine with the result that the pincers holding the tip slip or incomplete drawing is obtained; occasionally the material is softened to such an extent that the wall blows out or melts before drawing takes place. The result is a considerable amount of wastage. The invention has as its primary object the development of a novel process which obviates or reduces the disadvantages described and delivers uniform separated parts and, in the case of tubes and ampoules, provides reliably sealed and resistant fused closures. According to one aspect of the invention, in the mechanical separation of a part from a rod- or tube-lilre work piece made of a material capable of being softened by heat and in the closing of ampoules or the like with the separation of a tip piece, the process is such that the work piece is heated at a predetermined separating point and, at the moment of suitable softening, a force previously held inoperative is released for action on the piece to be separated, thereby suddenly to break off the piece. In the process of this invention the separation is not effected, as in the known processes, by a drawing process which extends over a measurable period and through a corresponding extended path followed

by final melting of the resulting thread of work material, but by means of a sudden breaking action so that there is no time at all for the walls to become thin by drawing. The sud den movement of separation provides, due to the action of the flame, a well-rounded fused top with an almost uniform continuous wall thickness. This uniform thickness and therefore resistance and reliable sealing of the fused closure is particularly important for ampoules and moreover the suddenness and violence of the separation of the softened tip part does not permit the formation of glass threads. Another object of the invention is to facilitate and improve this novel separating method particularly, but not exclusively, in the case of work pieces having wide diameter or thin walls. Thus the work piece or the ampoule spear or tip can, before being sufficiently heated for the sudden breaking off, be stretched by a certain amount and thereby somewhat narrowed; on the other hand, a limited compression which effects a thickening of the wall can be carried out. Another object of the invention is to take into account or compensate for the varying rapid softening of work pieces which deviate in diameter and in wall thickness, and to obtain, in spite of these deviations, equally good results. Thus, said preparatory stretching or compression may advantageously be effected, irrespectively of the timing of the machine, by a spring or weight acting on the pincers and adjusted to a predetermined tension or pressure action. Another object of the invention is to prevent said preparatory stretching or compression taking place too quickly on increasing softening and also to compensate for the minute weakening of the wall caused by the preparatory stretching. This is attainable by a suitable braking of the stretching or compression movement, which also permits the flow of softened material to the hottest part thereby effecting a strengthening of the wall. A similar effect is attainable when the stretching is followed by a short compression prior to the sudden breaking off. Another object d the invention is to ensure that said preparatory stretching or compression, in spite of the different times required by different work pieces, is followed directly by the sudden breaking off action, which means to say that the attack of the breaking means is automatically controlled by the varying rapid softening as a function af the unequalities of the work pieces. Thus, the tensioned and locked force for the breaking off action may be released, irrespectively of the timing of the machine, by the stretching or compression movement; for example, the pincers or their carrier may release the lock at a certain end position as at this point each work piece, in spite of deviations in dimensions, has a uniform degree of softening suitable for breaking.

Thus the stretching or compression is desirably effected even if it is not absolutely necessary for shaping reasons. With completely uniform work pieces, it can be dispensed with and the release of the lock can be effected mechanically at the moment of reaching a softening degree suitable for the breaking, as this moment does not vary. On the other hand with different work pieces in which the degree of softening suitable for breaking occurs at different times, the described stretching or compression treatment by means of a spring or weight has the important advantage of automatic regulation not only of this treatment but also of the subsequent breaking, it the stretching or compression also effects the release of the breaking force. The automatic operation of the actual working parts in this case limits the mechanical work in bringing the working parts back to their starting position. According to another feature of the invention said preparatory stretching or compression may be replaced by suitable other deformation, for example by a bending or a torsional deformation. Also here the extent of the deformation serves to determine the moment of softening suitable for breaking, and the deformation means may, when reaching a certain end position. release the lock of the tensioned force for breaking. A further object of the invention, in particular for the case in which the ampoules to be closed have oblique or eccentric spears or tips, is to provide that no harmful lateral pressure or pull is exerted on the spear or tip. Thus, the pincers may have a freely movable suspension instead of a rigid guide. With such a suspension, the pincers can adapt themselves to any position of the spear or tip and exercise thereupon no lateral pressure ar pull. A further important advantage of this feature is that, because of the omission of guide means, the pincers are easily movable almost without frictional resistance, which is a further aim of the invention. Thus the breaking can be effected accurately at the optimum time if the pincers are suspended by a rope or a chain on which a spring acts to provide for the limited stretching. Moreover simple working parts can be provided for the stretching and the breaking and these may be mechanically returned to the starting position by means of a single movement. The process according to the invention may be carried into effect in many different ways, and it is a further object of the invention to provide suitable means and apparatus therefor. Thus according to a further aspect of the invention, the apparatus may comprise one or more burners or other sources of heat, holding means for the work piece, pincers or like holding or gripping means for tile part to be separated easily movable in the breaking direction, means

for opening and closing the pincers, and a moving mechanism imparting the breaking movement to the pincers, such mechanism comprising a forceproducing member for example a spring or a weight, means for tensioning and locking such force-producing member, and means for releasing the lock at a time suitable for breaking the tip. Conveniently further means may be provided to impart a preparatory stretching or compression movement to the pincers, such means preferably being in the form of a spring or weight; means for braking the stretching or compression movement; and finally means to effect the release of the lock by this stretching or compression movement. The construction of the apparatus may also be effected in many different ways. As examples given without limitation, certain arrangements particularly suitable for sealing ampoules by the separation of a tip piece will now be described and illustrated with reference to the accompanying drawings, from which it may be seen how the invention may be applied to slightly irregular work pieces and from which further details and advantages of the process will be apparent. In the drawings: Fig. 1 shows, in vertical central section, sealing apparatus for ampoule tips employing weights, in six working postions I to VI: Fig. 2 is a plan view, partly in section, of the same apparatus in position I; Fig. 3 is a side elevation of a portion of the same apparatus showing a removal device for the broken off tips in the two positions IV and V; Fig. 4 is a rear elevation of the removal device of Fig. 3 in position V; Fig. 5 shows, in part vertical central section, alternative sealing apparatus for ampoule tips employing springs; Fig. 6 is a section on the line 55 of Fig. 5; Fig. 7 shows, in side elevation, further sealing apparatus for ampoule tips employing a parallelogram linkage and weights at the commencement of the stretching procedure; Fig. 8 shows the apparatus of Fig. 7 in side elevation after carrying out the breaking movement; Fig. 9 shows, in side elevation, means adapted for use with the apparatus of Figs. 7 and 8 which provides for compression between the stretching and breaking; and Fig. 10 shows a modification of the apparatus of Figs. 7 and 8 so that the apparatus can be used alternatively for stretching or compression prior to breaking.

The separating and closing apparatus for ampoule tips illustrated in Figs. 1 to 4 uses a freely movable suspended pincers which fits clip-fashion onto the ampoule tip and is therefore hereinafter called a "clip". The position of this clip and of weights and control means operating it is illustrated in six working positions I to VI. Of these, position III is a full vertical central section show- ing also the lower parts. A hollow column 2 is mounted on a base plate 1 next to an ampoule transport arrangement and carries at its upper end a sleeve 3 supporting a plate 4 through which pass guide rods 5 and 6 (only illustrated in Fig. 2) and a cable pulley 8 is mounted in ball races in bearing blocks 7 on the plate 4. A cap 9 covers the cable pulley 8. The sleeve 3 carries a locking lever 10 having a pawl and an arcuate feeler 11 (Fig. 2) which penetrate into the hollow column through a slot therein. A ring or clamp 12 with four bearings located thereon (see also Fig. 2) surrounds the hollow column 2. Two of these bearings are located on upwardly extending projections of the ring 12 and form bearings 13 for a catch 14 which includes a pawl 15 projecting through a slot in the hollow column 2 and which is operated by a roller 17 mounted on an upper lever arm 16 of the catch. The third bearing 18 (Figs. 2, 3, 4) located on the ring 12 carries a pivotal sector plate 19 which includes a delivery tube 20. The fourth bearing 21 serves to guide a brake and con trol rod 22 (Figs. 2, 3, 4) which is pressed upwards by a spring 23 (Fig. 1, Position III) and carries, at its top, a stop 24 (Figs. 2-4) for a pin 25 located on the sector plate 19 and, at its bottom, an arm 26 (Figs. 1 and 2) which penetrates through a slot 27 (Fig. 1, Positions III) into the interior of the hollow column and is there provided with a brake plate 28. A guide arm 30 carries a stop member 31. and is moved by a lifting rod 29 (illustrated only in Fig. 1, Position III), sliding over the guide rods 5 and 6 (Fig. 2), the stop member 31 operating the roller 17 of the pawl 15. A further operating member 32 is carried by a guide arm 30 and engages a roller 33 (Figs. 2-4) on the sector plate 19. Furthermore the guide arm 30 carries a guide head A for the clip C which is suspended on a cable B. The guide head A consists of the guide ring 34 connected to the guide arm 30 and a guide core 36 slidable therein and pressed upwards by a spring 35. The clip C consists of a cone 37 which fits into a conical bore in the guide core 36, an intermediate joint 38 and pincer arms 40 pivoted at 39 and having fingers 41.

Closing of the pincers 40 is effected by an annular spiral spring 42, and opening by engaging upper pincer arm extensions 43 against the guide ring 34. The clip C is connected to a preferably hollow control cone D and thence to a weight E by means of the cable B, which consists advantageously of a chain 44 (Fig. 1, Position b passing over the pulley 8. The weight E consists of a control of a conical tip 45 and a rod 46 over which, after release of a knurled-head screw 47, the necessary number of ring weights 48 are placed. The weight is se calculated that the total weight of D and E exceeds the weight of the clip C by such an amount that the desired pulling action for stretching the tip is effected. For the purpose of changing the ring weights the whole head of the hollow column 2, with the parts 3, 4, 7-11, and the parts D, E, F hanging on the cable B are withdrawn upwards. For this purpose, the hollow column 2 is slit in the area of the lever 10 up to its upper end. A loose sliding weight F, having a continuous bore widened conically at the top and bottom, is provided in the hollow column 2. An annular groove 49 for receiving the pawl of the lever 10 is provided immediately below the upper end of the weight F. An upper lever arm of the locking lever 10 may be provided with a movable weight 50 (Fig. 1, Position I). The transport of the ampoules may be effected on the straight path X or a curved path Y, as desired. The type of ampoule transport arrangement is a matter of secondary importance. It is advisable to provide a tip support 51 just below the future melting point and an ampoule body support 52 adjustable for different ampoule thicknesses just above a base support 53. The support 51 need not be adjustable in height but supports 52 and 53 are adjustable for the different sizes of ampoule (Fig. 1, Position III). To prevent the ampoules falling out during transport, it is sufficient to provide a wire line (not shown) surrounding the path. At the working points, the ampoules are pressed against their supports 51 and 52 by means of a pad in order to bring them into the position required for the separation and at the -same time to secure them against translatory movement. In order to make a control movement for this padding unnecessary, a pressure roller 54 with thick moss or foamed rubber covering is provided and is mounted on an arm 55 (Fig. 1, Position III) to press resiliently against the arriving ampoule, rotating in a bearing 56. By means of a drive not shown, the roller 54 can be rotated for the purpose of rotating the ampoule to be closed. A burner carrier 58 provided with gas andlor air conduits carries one

or more burners 57. The manner of operation of the apparatus is as follows:- Position I shows how, by means of the guide head A with which it is rigidly con nected by the interlocking of the cone 37 and core 36, the clip C is opened and guided over an ampoule as it arrives between the burners. On the downward movement of the clip C, the weights D and E and the weight F (carried by the weight E) reach their highest positions in the hollow column 2 and are locked in this position by the automatically operating locking lever 10 and pawl 15. Position II shows how, immediately after the lowering of the head A, it rises immediately. This movement frees the upper pincer arm extensions 43 to close the pincer arms 40 through the action of the spring 4 and, as the cone 37 is released from its rigid connection to the guide core 36 and the clip C hangs freely on the cable B, the clip C grips the ampoule tip and adapts itself to any position of the ampoule spear. The two pivots 38 and 39 of the clip C permit engagement with a slightly displaced ampoule spear without causing a disadvantageous lateral pressure or pull. On lifting the guide arm 30, the stop member 31 approaches the roller 17 of the locking lever 15 which holds the weight E until the clip C has seized the tip of the ampoule. As soon as that has happened, as shown in Position III. the stop member 31 displaces the roller 17 and the pawl 15 so that the weight E (aided by the slight weight of the hollow control cone D) can cause a pulling action on the clip C. However, this pulling action only leads to a stretching of the tip when the appropriate degree of softness of the glass is reached. With increasing softening. an acceleration in the movement of the weights and thereby a thinning of the wall would occur. In order to prevent this and on the contrary obtain a thickening of the glass at and below the hottest zone, the pull of the weight is braked shortly after the commencement of its action. This braking is effected by friction of the control cone D on the arcuate feeler 11 of the locking lever 10 increased by the friction on a projection 3' of the sleeve 3 against which the control cone D is pressed by the feeler 11. The amount of the pressure (and the friction and braking resulting therefrom) may be varied as desired by the adjustable weight 50 (only shown in Fig. 1, Position I) on the locking lever 10. Fig. 1. Position III shows the locking lever 10 as just ready to free the weight F held by it.

In Position IV. the released weight F has moved down and. on striking the cone 45 of the weight E, has moved this also. This achieves a sudden breaking off of the tip at the hottest part, i.e., just above the accumulation of glass caused by the original slight stretching. The downward movement of the weights D, E, F is then so resisted by the resiliently mounted brake plate 28 that the clip C with its cone 37 gently enters the bore of the guide core 36 of the head A as shown in Position V. It should be noted that, on the upward movement of the guide arm 30 effected by the rod 29, the head A engages the plate 4 to cause displacement of the core 36 relative to the guide ring 34 (Fig. 1, Positions IV and V). In Position V the guide arm 30 with its associated parts is in its highest position. The stop member 31 engages the upper arm of the locking lever 10 and lifts it after it has fallen back into its locking position on the passage of the control cone D. This step is in itself superfluous, but it provides securing means for the cases in which for any reasons (for example, flame failure due to a sudden strong draught in the chamber) the melting process is disturbed and accordingy the stretching or breaking off step is delayed. Should this occur the weight F would be released automatically at the last moment of the timing prescribed by the machine, so that the breaking off occurs with force or if the material of the work piece should not have been sufficiently softened the clip would be drawn off the spear so that the clip is available for the next working step. In the highest position of the guide arm 30, the guide head A is completely compressed and the lower surface of the guide core 36 is flush with the guide ring 34. This step is necessary in order to prevent, on penetration of the cone 37 into the core 36, engagement of the upper pincer arm extensions 43 with the guide ring 34 and a premature opening of the pincers. On descent of the weights E, F onto the brake plate 28, the resiliently mounted brake and control rod 22 is lowered by the arm 26 connected to it (Fig. 1, Position III). Hence the stop 24 carried by the rod 22, which has up till now locked the pin 25 (Fig. 3, Position IV), frees this pin so that the sector plate 19 with the delivery tube 20 can spring into the position shown in Fig. 3, Position V and in Fig. 4. This is effected by a spring 59 which, for example, is connected to an extension of the plate 4. By means of this automatic control of the raising of the delivery tube 20, the top thereof reaches its working position virtually at the same time as the clip A, with the drawn off end of the tip, reaches Nts uppermost position.

Thus the last phase can begin immediately and in this phase the guide arm 30 with its suspended parts carries out a rapid and uninterrupted downward movement to the final position which is the same as Fig. 1, Position I. Fig. 1 Position VI shows the commencement of this movement, namely the position in which the guide ring 34 of the head A has moved far enough to open the pincers 40 of the clip C, the cone 37 remaining in the guide core 36 in consequence of the pull of the weights D, E, F. The freed tip falls through the delivery tube 20 into a container (not shown). The downward movement of the guide arm 30 and the head A guiding the opened clip C continues without any further interruption, since the operating member 32, at the moment of opening of the clip and the beginning of its downward movement, strikes the roller 33 (Fig. 3, Position V and Fig. 4) and accelerates the delivery tube 20 in front of the clip, forcing it to the side until the pin 25 snaps behind the stop 24 (Fig. 3, Position IV). This stop 24 is displaced downwards somewhat by the circular path of the pin 25 due to the resilient mounting of the control rod 22. The downward movement of the lifting rod 29 (Fig. 1, Position lIll) moving the guide arm 30 with the head A etc. can therefore (including the opening of the clip resulting at Position VI) be effected as quickly as the downward movement of a filling needle at a filling station. The ampoule transport is thus so determined that a fresh ampoule arrives just when the lower end of the clip is directly over its tip. For the mechanical operation of the whole separating and closing apparatus only the rod 29 (Fig. 1, Position III and Fig. 2) is actuated. It carries out a rapid downward movement and a somewhat slower but immediate upward movement. All other movements are derived from or automatically controlled by, this up-and-down movement. The same apparatus can also employ rigidly guided pincers instead of the freely movable clip. It is sufficient to connect the pincers to a sliding rod which is mounted slidably in the guide core 36 and connected by means of the cable to the weights D and E which are correspondingly to be dimensioned. To reduce friction, it is advisable to effect the bearing on a guide between two sliding ball bearings. If rigidly guided pincers are also to be rotatable, whereby, because of the necessary ball bearings, a sleeve of greater diameter is needed, two opposed sliding ball bearings are sufficient for the axial movement However three balls distributed around the sleeve are better and still better is a closed slide ball bearing with three rows

of balls and a common cage as illustrated in Figs. 5 and 6.jarating 6. Figs. 5 and 6 show a separating and cles- ing apparatus for ampoule 4 tips which is similar to that of Figs. 1 to 4 (after substi- tution of the freely movable pincers by rigidly guided pincers) and likewise the mechanical operation is effected by means of a single lifting rod in which springs pro vide for the stretching and the breaking off movement instead of weights. A sliding body 63 is movable on guide rods 61 an,d 62 and carries a carrying sleeve 64. A sliding sleeve 66 is axially movable in the carrying sleeve 64 through a sliding ball bearing 65. A sleeve 68 is rotatably mounted in the sliding sleeve 66 in a ball bearing-67-and carries at its lower end a head 69 for bearings 70 of two L-shaped pincer members 71. The short arms of the two pincer members 71 are toothed and engage one another and carry pins 72 which are laterally slidable in a stop73 at the lower end of an operating rod 74 which is guided in the sleeve 68. The operating rod 74 also carries a plate 75 just below its upper end. A spring 76 urges the plate 75 and therefore the operating rod 74 upwardly and in this manner causes the pincers 71 to be closed. The foot of a carrying arm 78 is mounted in the sliding body 63 and is adjustable in height by an adjusting screw 77, this carrying arm 78 passing through openings 79 in the carrying sleeve 64, in the bearing cage, and in the sliding sleeve 66 to the inside of the latter and there carries an annular plate SO. A spiral compression spring 81, carrying the sliding sleeve 66 with its contents, is supported on the annular plate 80. A lifting rod 82, which forms a single mechanical operating means for the apparatus, runs through an opening in the sliding body 63 and carries on its upper end a pincer opening arm 83 having a pressure piece 85 and bushes 84 sliding over the guide rods 61 and 62. On lowering, this pressure piece 85 presses onto the operating rod 74 and opens the pincers 71. At a certain distance below the pincer opening arm 83 a control slide 86 having bushes 87 slides with slight friction on the guide rod 61 and 62. An adjusting ring 88 is located on the lifting rod 82 in the space between the control slide 86 and the sliding body 63. A powerful compression spring 89 is arranged around the lifting rod 82 to urge the sliding body 63 upwards. A locking lever 90, mounted on the sliding body 63, snaps into a notch 91 in the guide rod 62 and holds the sliding body 63 locked against the pressure of the spring 89. A control stop 92 on the sliding sleeve 66 releases the locking lever 90 on upward movement of the sliding sleeve. The manner of operation of the apparatus is as follows : - On lowering the lifting rod 82, the pressure piece 85 presses onto the operating rod 74, which, due to the angled shape of the parts engaging

one another, causes the pincers 71 to be turned to the position illustrated in the drawing. On further lowering, the pincers open and, as soon as the plate 75 engages a cap on the sliding sleeve 66, are moved downwards in the open state until the lowest position illustrated in the drawing is reached and the locking lever 90 falls into the notch 91. During this downward movement, the control slide 86 is pushed downwards by the bush 84, carrying with it the sliding sleeve 66 and, through its bush 87, the sliding body 63. Thus the spring 89 is compressed. This is the starting position for t the pincers. The sliding weight 111 is so adjusted as to cause the pincers 104 to develop the necessary pulling action for the stretching treatment. The tilting weight 110 rests on a sliding surface 112 which is adjustable by means of an adjusting screw 113. A plunger 114, mounted on a lifting and lowering control rod 115, is positioned under the roller 106. A lifting rod 116 with an angle attachment 117 for raising the weight 110 is located under this weight. The ampoules are guided by means of a carrier 119 along a mounting 118 under the pincers 104 and are held and rotated by a roller 120. A burner 121 and a receiving dish 122 for the broken-off tip pieces are provided on the mounting 118. The method of operating the apparatus is as follows: In the position illustrated in Fig. 7 the pincers 104 have already taken hold of the ampoule tip. In consequence of the excess weight of the weight arm 109 adjusted by the sliding weight 111, the pincers 104 exercise a slight pull on the ampoule tip which causes, after initial softening, a slight stretching of the tip. This causes a lowering of the weight arm 1Q9 and the tilting weight 110 which slides along the upper edge of the sliding surface 112 and, since the weight 110 is of upwardly widened form and the surface 1-12 is not completely parallel thereto, causes slight tilting of the weight 110. On further lowering, the side of the tilting weight 110 becomes parallel to the sliding surface 112 and the increased friction provides greater resistance than with the previous sliding along the upper edge to cause the desired delay in the stretching of the ampoule tip. Finally a slight further lowering of the tilting weight 110 over the sliding surface 112 moves it over the dead center and it tilts over. The weight 110, striking on the weight arm 109, effects a sudden breaking off of the tip piece to be separated. The roller 106 of the rocker arm 107 of the raised parallel linkage strikes on the plunger 114 (see Fig. 8) and presses down the head 105 of the operating rod of the pincers to open the pincers Thus, as can be seen from Fig. 8 and because of

the movement of the pincers on a circular path, the tip piece which is thrown from the pincers before reaching the position shown moves in an arc into the receiving dish 122. The pincers remain open whilst the weight arm 109 (which has become heavier due to the larger leverage of the tilted weight 110) holds the head 105 pressed against the rocker arm 107. The control rod 115 with the plunger 114 is raised to return the apparatus to the starting position. The pressure against the roller 106 of the rocker arm 107 returns the pincers 104 (in the opened state) back to the starting position. Lifting of the lifting rod 116 and the angle attachment 117 raises the tilting weight 110 into its tensioned and locked position. Whilst the weight 110 is still supported by the angle attachment 117 the control rod 115 is lowered and on released ing the rocker arm 107 the pincers 104 close around a new ampoule tip. After they have found a grip, the whole movable system can be released by lowering the lifting rod 116, which state is illustrated in Fig. 7 and is taken as the starting point of the description of the manner of working. Fig. 9 shows the weight arm 109 of the apparatus illustrated in Figs. 7 and 8 in which the tilting weight 110 carries on its front or rear side a lever arm 123 (the outer continuation of the weight arm 109 being cut off in the drawings). On a fixed point of the apparatus below this lever arm is mounted a flexible stop 124, for example a leaf spring. With the aid of these two additional members a short compression of the softened zone is effected after stretching the ampoule tip but before the breaking off. This comes about in the following manner. After the commencement of the tilting of the weight 110, the lever arm 123 strikes against the resistance of the stop 124. The excess weight of the longer and heavier lever arm formed by the weight 110 cannot prevent a further downward movement of these parts. But due to the resistance of the stop 124 a reaction force is produced and due to this reaction force the weight arm 109 makes a short upward movement while the heavy weight 110 continues its downward tilting movement. Thus the lever arm 109 and the weight 110 act as a sot of toggle-link. Due to this movement the point 125 moves towards the end of the leaf spring 124 until finally the lever arm 123 slides from the spring 124. The weight 110 continues its tilting movement until it strikes a stop of the arm 109 (compare Fig 8) whereby the breaking of the work piece is effected. The cooperation of these parts may be adjusted depending upon the displacement of the striking point 125 and the degree of flexibility of the leaf spring 124. By varying the dimensions of the lever arm 123 and the leaf spring 124, their positions relatively to one another, the degree of flexibility of the leaf spring or other

stop as well as the form of the upper surface of the stop on which the striking point moves, short, elastic, soft or hard compressions of shorter or longer duration according to requirements can be obtained. Conversely the lever arm 123 may be flexible and the stop 124 rigid or both parts may be flexible or rigid. Ill the example shown, an adjusting screw 127 is provided by means of which the leaf spring 124 can be brought into different angular positions. Such a short compression accompanied by a limited stretching has the two advantages that thinning of the wall occurring during the stretching is compensated and the reinforced part under the hottest flame zone (at which the breaking off takes place) is compressed so that a particularly resistant fused end results. This compression can be carried out with suitable modifications also in connection with other constructions of the apparatus according to the invention. Alternatively, to provide limited compression without previous stretching, all forms of apparatus with rigidly guided pincers can be used, if these forms of apparatus according to the invention effect stretching by means of a spring or weight force and the direction of effect of the force is reversed and the locking members or control members are suitably adapted. Fig. 10 illustrates how in a simple manner the apparatus shown in Figs. 7 an;i 8 can be so arranged that it can be used as desired for stretching or for compression. Instead of the tilting weight 110 a suitable diamondshaped tilting weight 128 is used and a second sliding surface 129 is provided in addition to the sliding surface 112, this sliding surface 129 being regulatable by means of an adjusting screw 130. To use the compression process, the slide weight 111 is moved to the right so that the parallel linkage with the pincers is the heavier to effect the compression. At the commencement of the softening of the heated point, the pincers lower and lift the tilting weight 128, the side surface of which now slides along on the upper sliding surface 122 in a manner similar to the description already given in Figs. 7 and 8, making contact first on the upper edge and then on its whole surface until finally it is. forced over the dead centre and tilts. The breaking off point obtained in this manner has a greater wall thickness than one obtained after stretching. However there is no direct thickening, as might be assumed from the term "compression", as no sudden compression is effected, but it is rather a matter of a contraction of the heated point yielding to the slight excess pressure, this contraction being adjustable in its extent as desired by the excess weight applied and by the thickness and form of the flame. It may therefore be an advantage in the separation and fusing of thick walled pieces to use the stretching process and, with thin walled

pieces, to use the compression process according to the invention or as described with reference to Fig. 9, a combination of both processes. The drawings relate to the separation and fusing of ampoules as it is known that in such cases, in particular. there are many possibilities of disturbances and faults which have had to be considered when making the invention and are taken into consideration by suitable means. For the separation of one part of other rod- or tube-like heat soften able work pieces, the arrangements described are either unaltered or are usable with the variations required by special circumstances but without departing from the invention. The same applies also to other modifications of the process or apparatus according to the invention. The possibilities of the combination of the different individual elements within suitable apparatus are numerous. Thus for example, brake members and a drop weight similar to the weight loaded lever illustrated in Fig. 1 may be combined with other arrangements similar to those illustrated in Figs. 7 to 10 or, for example, the spring 81 may be replaced by a weight loaded lever and the release of the locking pawl 90 may be effected by a tilting weight located on such lever. Further the release of the lock of the tensioned breaking means may, for example, be effected by an electro-magnetic relav. Finally the invention may be extended in its use in that instead of the spring or weight forces mentioned heretofore for the breaking off and the stretching and compression any other suitable force within the scope of the invention may be used for the sudden breaking off and any uniform and flexible force suitable for stretching or compression and acting independently of the machine stroke is applicable; for example, pneumatic, hydraulic, electrical or magnetic forces. What I claim is : - 1. Process for the mechanical separation of a part from a rod- or tube-like work piece made of heat soften able material, comprising heating said work piece at the separation point, potentially loading a force and holding same inactive, and releasing said force to act on said work piece at the moment of suitable softening to cause sudden breaking off. 2. Process according to Claim 1, wherein the heated part, before being sufficiently softened for the sudden breaking off, is stretched and/or compressed by a certain limited amount. 3. Process according to Claim 2, wherein the limited stretching or compression movement is effected by means of a spring, weight or other force which is adjusted to a certain stretching or compression action. 4. Process according to Claim 2 or 3, wherein the limited stretching or compression movement is retarded, for example by braking. 5. Process according to Claim 2, 3 or 4, wherein said limited

stretching or compression movement effects, when reaching its limit, the release of the' tensioned force for the sudden breaking off. 6. Process according to any of the preceding claims, wherein the best moment for the

* GB785424 (A)

Description: GB785424 (A) ? 1957-10-30

Improvements in or relating to couplings for rail vehicles

Description of GB785424 (A)

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The EPO does not accept any responsibility for the accuracy of data and information originating from other authorities than the EPO; in particular, the EPO does not guarantee that they are complete, up-to-date or fit for specific purposes.

", #i ^a 5,t' -e,- -H; 1 l ' 11 ' ' c 1 PTF m, E-C Z a -I PATENT SPECIFICATION Date of Application and filing Complete l 't "l Specification: May 18, 1956 Nc A H a Application made in Switzerland on May 25, 1955. Complete Specification Published: Oct 30, 1957. index at acceptance:-Class 103 ( 5), B 2 81. International Classification:-B 61 g. COMPLETE SPECIFICATION Improvements in or relating to Couplings for Rail Vehicles ERRATA

SPECIFICATION NO 785,424 Page 1, line 19, for 'lit is' read "is it". page 3, line 49, for nvody" read "bod Yl". THE PAIENT OFFICE, 3rd December, 1957 couplings, it is already icnown to provide spring-operated locking pins having releasing draw chains, i e, transverse bolts, for securing the coupling after the coupling heads have been brought together. According to the present invention there is provided an automatic coupling for a rail vehicle, wherein a coupling part for one vehicle is adapted to engage and lock with a similar coupling part for a second vehicle, the body of each coupling part being formed with a recess for accommodating a projecting head of each other coupling part, and wherein a spring-loaded locking bolt is slidably carried in the body of each coupling part, and carries a securing latch, the bolt and the latch of each coupling part each having a projection adapted to fit into a recess formed therefor in the head of each other coupling part, the arrangement being such that, when the two parts of the coupling are engaged, the projections of each latch and bolt fit in said recess in the head of a respective other coupling part and lock the two parts of the coupling together. lPrice 3/ 61 DB O 0889/2 ( 1 S)13612 150 11/317 R showing the couplings when unlocked; and Fig 7 is a detail view taken along the line VII-VII of Fig 1. Referring now to the drawings, there is shown a coupling for a railway vehicle, the 70 coupling having a main body l, an inserting lug 2, and a coupling head 3 A locking bolt 4 is located in a sleeve 17 which is secured in a transversely extending recess formed in the body 1, by means of a locking screw 18 75 A two-armed securing latch 5 is pivotally mounted in the bolt 4 on a pin 6 The locking bolt 4 is formed with a recess 7, one face 7 a of which acts as a cam controlling face and as an abutment for a cam 8, the cam 8 80 being located in the recess 7, and being integral with its cam pin 9 which is vertically mounted in the body 1 Fixedly arranged on the lower end of the cam pin 9 is a double pulley 10, wound about which in opposite 85 directions respectively are two rope lines 11 and 12, there being handles 13 and 14 provided on the ends of the rope lines 11 and 12 respectively A draw spring 46 is arranged on the rope line 12, for influencing the posi 90 85,424 l 15638/56. PATENT SPECIFICATION Date of Application and filing Complete Specification: May 18, 1956. 785,424 No 15638/56. ty M/ D Application made in Switzerland on May 25, 1955. Complete Specification Published: Oct 30, 1957. Index at acceptance:-Class 103 ( 5), B 2 B 1.

International Classification:-B 161 g. COMPLETE SPECIFICATION Improvements in or relating to Couplings for Rail Vehicles We, GEORG FISCHER AKTIENGESELLSCHAFT, a Company organised under the laws of Switzerland, of Schaffhausen, Switzerland, 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 an automatic coupling for rail vehicles. Couplings with coupling pins are already known, such couplings consisting of two similar coupling heads with a projecting coupling arm for the pin and cone-shaped elements The connection between the heads is a double one, and the two halves of the coupling form a rigid unit, handles being used for uncoupling. Nor it is novel to use inserting lugs for centering purposes In connection with such couplings, it is already known to provide spring-operated locking pins having releasing draw chains, i e, transverse bolts, for securing the coupling after the coupling heads have been brought together. According to the present invention there is provided an automatic coupling for a rail vehicle, wherein a coupling part for one vehicle is adapted to engage and lock with a similar coupling part for a second vehicle, the body of each coupling part being formed with a recess for accommodating a projecting head of each other coupling part, and wherein a spring-loaded locking bolt is slidably carried in the body of each coupling part and carries a securing latch, the bolt and the latch of each coupling part each having a projection adapted to fit into a recess formed therefor in the head of each other coupling part, the arrangement being such that, when the two parts of the coupling are engaged, the projections of each latch and bolt fit in said recess in the head of a respective other coupling part and lock the two parts of the coupling together. lPrice 3/6 l For a better understanding of the invention, and to, show how the same may be carried into effect, reference will now be made to the accompanying drawings in which:Fig 1 is a side view, partly in section, of 50 one half of a coupling for railway vehicles; Fig 2 is a plan view, partly in section, of the coupling shown in Fig 3; Figs 3, 4 and 6 are sectional views illustrating the method of operation; 55 Fig 3 is a sectional plan view of the coupling showing a first stage in the joining of two couplings; Fig 4 is a view similar to Fig 3, showing two couplings locked together, 60 Fig 5 is a side view of the coupling shown in Fig 1, when in an inoperative position, the operative position being shown in chain-dotted lines; Fig 6 is a view

similar to Figs 3 and 4, 65 showing the couplings when unlocked, and Fig 7 is a detail view taken along the line VII-VII of Fig 1. Referring now to the drawings, there is shown a coupling for a railway vehicle, the 70 coupling having a main body 1, an inserting lug 2, and a coupling head 3 A locking bolt 4 is located in a sleeve 17 which is secured in a transversely extending recess formed in the body 1, by means of a locking screw 18 75 A two-armed securing latch 5 is pivotally mounted in the bolt 4 on a pin 6 The locking bolt 4 is formed with a recess 7, one face 7 a of which acts as a cam controlling face and as an abutment for a cam 8, the cam 8 80 being located in the recess 7, and being integral with its cam pin 9 which is vertically mounted in the body 1 Fixedly arranged on the lower end of the cam pin 9 is a double pulley 10, wound about which in opposite 85 directions respectively are two rope lines 11 and 12, there being handles 13 and 14 provided on the ends of the rope lines 11 and 12 respectively A draw spring 46 is arranged on the rope line 12, for influencing the posi 90 785,424 tion of the cam 8 in such a way as to tend to return the cam 8 into an initial position. As shown in Fig 1, the coupling body 1 is fitted with an air brake connection 15, on which is mounted an adjusting lever 16 which is actuated by a cam (not shown) on the pin 9, and which serves, in a known manner, for opening or closing the air passage. The locking bolt 4 is slidable in the recess formed in the body 1, and is spring-loaded by means of a cup-shaped spring holder 19, in which one end of a spring 20 is mounted, the holder 19 bearing against one arm 5 a of the two-armed securing latch 5, and the said arm 5 a in turn bearing against an abutment 4 a (Fig 4) formed on the locking bolt 4. The other end of the spring 20 is wound about a supporting bush 21 which is screwed into the coupling head 3 of the body 1 Also formed in the body I (Fig 3, left-hand side) is a recess -22 into which the coupling head of the other half of the coupling can penetrate, the coupling head 3 of one half of the coupling corresponding to the coupling head of the other half. The head 30 is formed with a recess 31 having bearing surfaces 32 and 33 for a projection 4 b formed on the end of the locking bolt 4 and for the outer end Sb of the other arm of the securing latch 5 This other arm of the two-armed securing latch 5 has a pawl-like projection 5 c recesses 17 a and 17 b being formed in the sleeve 17 for receiving or arresting the projection 5 c. A recess 310 is formed in the coupling head 3, the recess 310 corresponding to the recess 31 formed in the coupling head 30, and being adapted to receive those parts of the other half of the coupling which correspond to the parts 4 b and 5 b, and the coupling head 3 has

the shape of a hemisphere, mounted on a short cylindrical portion. The body 1 is constructed with buffers at the side, and comprises (see Fig 2) two rearwardly directed tubular arms 23 and 24. Carried in the arms 23 and 24 are buffer arms 27 and 28, a spring 26 arranged about a pin 25 being provided in each composite arm 23, 27 or 24, 28 of the buffer The arms 27 and 28 are connected together by a stirrup 29, which supports a draw-bar hook cap 35 which is pivotable about a pin 34, the cap 35 being formed with a hole 35 a for a pin 34, and stops 35 b for the reception of the head 36, which is rounded, of the pin 34 A centering boss 37 which is triangular in cross-section is arranged with a sliding fit on the pin 34 and below the stirrup 29, the boss 37 being subjected to the pressure of a spring 38 arranged on the pin 34 and supported on the flange of a flanged sleeve which is held in position by locknuts 39 and 40 on the other end of the pin. The buffer parts 27, 28 and 29 are pivotable about a pin 41 (Fig 2) which in turn is mounted with some play in the draw-bar hook 42, the pin 41 being secured in position by a locking pin 43 70 In the operation of the coupling just described the coupling head 30 of the coupling half of a first wagon comes into engagement with the coupling half of a second wagon which is to be connected to the first 75 wagon, the head 30 coming into engagement with the recess 22 in the body 1 of the second wagon (see Fig 3). Provided on the body 1 of the second half of the coupling is a lug 44 which guides the 80 lower edge of the joint face 45 (Fig 4) of the first half of the coupling An abutment surface 32 a on the head 30 engages, and pushes backwards the projection 4 b of the locking bolt 4 and the projection 5 b formed on the 85 end of the other arm of the securing latch 5, so that the locking bolt 4 and with the latch are removed, in opposition to the action of the spring 20, from the path of the head 30 and the latter, i e, the first ha'f of the coup 90 ling, enters the recess 22 of the body 1 of the second half of the coupling, and thereat the recess 31 in the head 30 is situated adjacent to the projections 4 b and 5 b As a result, the way is open for the locking bolt 4 and the 95 latch 5 to advance so that the projections 4 b and 5 b can enter the recess 31 and bear against the abutment surfaces 32 and 33 respectively Thus the coupling is engaged ( 4 b and 32) and secured ( 5 b and 33) The 100locking bolt 4 and latch 5 are automatically advanced by the spring 20, which had previously been compressed to the fullest extent permitted by the parts 19 and 21 In this operation, the arm 5 a of the latch 5 is 105 engaged by the spring holder 19 and is swung about the pin 6 until the arm 5 a abuts against the abutment 4 a of the locking bolt 4 During this advance, the cam 8 is simultaneously swung by the action of the spring 110 46 (Fig 2), into the position illustrated in Fig 4, thus

also preventing any undesirable movement of the parts 4 and 5 The cam 8 abuts against an edge 7 b of the recess 7, and engages in a recess 5 d formed in the 115 other arm of the securing latch 5, the recess d being complementary in shape to part of the contour of the cam 8. It will be appreciated that all the parts of one half of the coupling have their counter 120 parts in the other half of the coupling, and therefore these counterparts have not been described in detail. When it is desired to release the coupling, the operator must grasp and Dull the handles 125 13 or 14 depending on whether he is standing at the left-hand or right-hand side of the wagons to be uncoupled i e two handles at each end of the rope lines 11 or 12 The cam 8 is thereby swung into the recess 7 in 130 785,424 a counter-clockwise direction (Fig 6), so that it withdraws the bolt 4 and the latch 5, the cam 8 abutting against the face 7 a, whereby the projections 4 b and 5 b are swung out from the recess 33, i e, from the position shown in Fig 4 to that shown in Fig 6. At the end of the movement, after the rope lines have been released, the cam 8 is caused to move into the position shown in Fig 6 by the spring 46 and the spring 20 presses on the arm 5 a, thus swinging the pawl-like projection 5 c of the latch 5 into the recess 17 b of the sleeve 17, so that further advance of the bolt 4 and the latch 5 is prevented by the locking engagement of the projection 5 c in the recess 17 b Thus the bolt 4 is held fast, together with the latch 5, in the position shown in Fig 6, and the coupling is ready to be uncoupled. The pin 41 (Figs 5 and 2) serves to allow the half of the coupling, hereinbefore described, to be swung downwardly about the pin, into the position shown in full lines in Fig 5, when the other wagon is not equipped with a similar coupling half for automatic coupling In this case, the draw-bar hook 42 is itself used as a coupling hook in the conventional manner The cap 35, controlled by the spring 38 and the centering boss 37 allows the coupling to be swung into the operative position and held there The springs 26 (Fig 2) in the arms 27 and 28 take up the shock of coupling-up, and when the two halves of the coupling are introduced into one another, the rigid inserting lug 2 (Figs 1 and 2) is used for aligning the parts in the vertical and lateral directions In the constructional form which has been described and illustrated, the coupling is constructed as a coupling with buffers at the side, but it is also possible for the coupling to be constructed as a centre-buffer coupling, i.e, without side buffers.

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* GB785425 (A)

Description: GB785425 (A) ? 1957-10-30

An electric two-part connector for coaxial cables

Description of GB785425 (A)

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FR1153870 (A) FR1153870 (A) less Translate this text into Tooltip

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The EPO does not accept any responsibility for the accuracy of data and information originating from other authorities than the EPO; in particular, the EPO does not guarantee that they are complete, up-to-date or fit for specific purposes.

PATENT SPECIFICATION Date of Application and filing Complete Specification: May 23, 1956. Application made in France on March 2, 1956. 785,425 No 15911/56. Complete Specification Published: Oct 30, 1957. Index at acceptance:-Class 38 ( 1), E 3 (A 4 D: A 6 H A 11 B:A 15:B 2 C:C 6 C:C 6 D 2:G 9), E( 10 B 15:18:21:22 C:29:30). International Classification:-HO 2 f. COMPLETE SPECIFICATION An Electric Two-Part Connector for Coaxial Cables We, SOCIETE OTTAWA, of 37, Bis rue Gauthey, Paris 17, France, a company of limited liability and organised under the laws of France, 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 an electric twopart connector for coaxial cables, of a type more and more widely used in present-day electrical equipment at the higher frequencies A coaxial cable usually comprises one or more central or core conductors and an annular outer conductor surrounding and insulated from the core conductor (s), and the annular conductor being generally surrounded in turn by a sheath or coating of insulating material. The connexion of a section of such coaxial cable with another section of coaxial cable or with a pluggable unit of equipment involves certain difficulties which this invention sets out to overcome The object of the invention is to provide an improved electric two-part connector for coaxial cables, which will render the connexion more reliable, the electrical contacts more efficient, and at the same time to reduce the size and facilitate the assembly of the connector. According to the invention, there is provided an electric two-part connector for connecting a coaxial cable having at least one inner, and an outer conductor to a further unit such as a further coaxial cable or a plugging unit of apparatus, which further unit includes further inner and outer conductors to be electrically connected with said first mentioned inner and outer conductors resoectively, which connector comprises a tubular element projecting from one of said inner conductors and engageable with a stiffener element projecting from the other inner conductor, and conductive members lPrice 3/6 l respectively connected with said outer conductors and insulated from the inner conductors, said members having mating frustoconical surfaces, and means for securing said members to each other with said mating 50 surfaces in engagement and with said elements in engaged condition. The accompanying drawings illustrate by way of example one form of embodiment of the invention which is specifically designed 55 for connecting a single-core coaxial cable with a fixed plug in a unit of apparatus It should however be distinctly understood that the invention is applicable with only minor modifications to the connexion of two cable 60 sections. In the drawings, Fig 1 shows, in axial section and at an enlarged scale, the two parts of the connector prior to assembly; Fig 2 shows the parts in assembled and 65 in plugged-in condition, and Fig 3 is a view, included for convenience, showing the coaxial cable alone. A conventional cable as illustrated in Fig. 3 usually comprises a core conductor 1 sur 70 rounded by an insulating layer 2 surrounded by the annular conductor 3 surrounded in turn by an

outer insulating sheath or cover 4. Referring to the right-hand portions of Figs 1 and 2, the reference 5 designates part 75 of a conductive casing wall of a unit of equipment which is grounded and which is to be connected with the annular conductor 3 and 1 ' designates an inner conductor which is to be connected with the core con 80 ductor 1 of the coaxial cable shown at the left of Figs 1 and 2. Associated with the coaxial cable is a connector part comprising a body 6 adapted to be assembled around the annular conduc 85 tor 3 while beinig insulated from the core 1, and said body 6 being further adapted for connexion with the grounded plate or wall 5. The body 6 includes a rear part 6 a slightly larger in diameter than the diameter of the 90 l-J '175 p 785,425 outermost insulating sheath 4 of the cable, and formed with cutouts allowing said body to be tightly clamped around the cable in a way to be described further below Beyond part 6 a is a part 61; which is externally threaded and which receives inside it an insulating core 7 adapted to surround the insulating cover of the cable as well as an electrically conductive fitting 8 engaged around the core conductor I in a manner presently described. Beyond part 6 b is an end part 6 c having a frustoconical enlargement 6 e at its end and formed with an internal annular shoulder adapted to abut against a shoulder 6 d formed on the insulating core member 7. The part 6 a is adapted to be tightly clamped about the cable by means of a nut 9 screwed over the threaded part 6 f of the member 6, the nut having a smooth rearward extension with a taper bore adapted to -co-operate with the periphery of part 6 a. Near the forward end of part 6 is a flatted or polygonal portion 6 adapted for engagement with a key or wrench to hold said part stationary during the screwing of nut 9. The body 6 is assembled around the cable in the following way: The outer sheath or cover 4 of the cable is first removed over a suitable distance such as a and the inner insulation 2 is removed over a smaller distance such as b The projecting length of the annular conductor 3 designated by c, is arranged to be substantially equal to the length of the part 6 a of the body 6. The free section b of the core conductor I is preferably stiffened by any appropriate means, as by welding or soldering thereto a thin-walled tube 8 of corresponding diameter. The annular conductor 3 is then combed, spun and turned over as at 3 a over the insulating outer cover 4 The body 6 is engaged around the cable end thus prepared by forcing the portion 6 a on to the folded-over section 3 a of the covering The resulting assembly is then locked tight by screwing the nut 9 over the portion 6 b of body 6

while locking the latter with a wrench engaged around the part 6 g as already indicated The resulting locking of the lapped-over cover portion 3 a by the taper section 6 a simultaneously binds the cable to the part 6 as a whole. It will be noticed that a thoroughly efficient contact is obtained in this way between the annular conductor 3 and the body 6 over a comparatively great length The core conductor 1 projects a distance d beyond the front end of the body 6. The complementary part of the connector, shown on the right of the drawing, and more especially intended in the example being described for connexion with a unit of electronic equipment, is constructed as follows: It includes a main body 11 having a reduceddiameter part 1 la for insertion into an opening provided therefor in the casing 5 of the apparatus, with a shoulder 1 lb engaging the front face of said wall The part 11 is fur 70 ther formed with a frustoconical entrance aperture or recess le for co-operating with the complementary frustoconical flanged portion 6 g of the first described member 6. upon the two connector parts being clamped 75 into assembly by means of a nut 12 which is screwed over a screw threaded part I 1 c of the body 11, said nut having an internal flange or shoulder 12 adapted to engage with the rear end face of the flange 6 c So The conductor section 1 ' which is to be connected with the core conductor I of the cable has soldered around it a t'lin-wailled tube 13 having a slightly widened portion 13 a which is slotted for resiliency so as to 85 be tightly applicable about the stiffener tube 8 surrounding the core conductor 1. Inserted between tube 13 and part 11 is an insulating bushing 14-14 a which conforms accurately with the dimensions of tube 13 90 and its widened extension 13 a The part I Ia is threaded and a nut 15 is screwed around it after the part 1 Ia has been inserted into an aperture in the casing wall 5. It will be seen that the cable having the 95 body 6 assembled to it in the manner aforedescribed is readily and quickly connectible with the casing wall 5 The part 11 is positioned on the casing wall by inserting the former rightwards into the aperture in the 100 latter and screwing the nut 15 over the projecting right end of the part i 1 The conductor I' is inserted through the insulating bushings 14 and 14 a with the front end of the tube 13 a lying within the bushing 14 a 105 The core conductor 1 with the tube 8 surrounding it, forming part of the cable assembled with the connector member previously described, is then pushed into the insulating bush 14 a and the conductor tube 110 13 a until the frustoconical surfaces 6 c and 1 lc are in contact The nut 12 is then screwed home on the threads 11 ( of part 11 so as

to maintain firm contact simultaneously between the taper surfaces 6 c and 1 lc and 115 the core conductors 1 and I'. A rubber or other flexible washer 16 is preferably inserted between the surface of casing wall 5 and the end of nut 12 to prevent disassembly under vibrational stress 120 and to provide a tight seal against the entry of moisture and the like. Variations may be made in the illustrated embodiment especially in cases where a cable is to be coupled to another coaxial 125 cable rather than to a unit of apparatus In such cases the further coaxial cable would be fitted with a connector part similar to that described above for the coaxial cable (i e the part on the left side of Figs 1 and 2) 130 elements in engaged condition 30

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* GB785426 (A)

Description: GB785426 (A) ? 1957-10-30

Improved vehicle brake

Description of GB785426 (A)

PATENT SPECIFICATION Date of Application and filing Complete Specification: May 28, 1956. 785,426 No 16408/56. Application made in United States of America on June 17, 1955. Application made in United States of America on Nov 21, 1955. \\\X N/> Complete Specification Published: Oct 30, 1957. Index at acceptance:-Classes 79 ( 3), A 2 F; and 103 ( 1), E 1 E, E 2 N 2 (A 2 A:B 1 82:D 6 A:D 12. E 5:K 2). International Classification:-B 62 d, F 06 d.

COMPLETE SPECIFICATION Improved Vehicle Brake We, GENERAL MOTORS CORPORATION, a Company incorporated under the laws of the State of Delaware in the United States of America, of Grand Boulevard in the City of Detroit, State of Michigan in the United States of America (Assignees of OLIVER KENNETH KELLEY, GILBERT KENNETH HAUSE, BURNETTE HECK, JAMES ORAN HELVERN and WILLIAM FREDERICK ERICKSON) 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: - 1.5 This invention relates to liquid cooled friction brakes such as include engageable stationary and rotatable friction brake members, the latter being connected to an axle and the former to a housing The engageable members are disposed in a chamber for circulation of cooling liquid under pressure by a pump between the engageable members. By the invention, the chamber has a first seal between the housing and axle to restrict cooling liquid flow from the chamber and a second seal, beyond the first seal, to prevent loss of cooling liquid and a vent passage from between the first and second seals. Preferably the passage leads to the inlet of the pump and includes a relief valve to maintain positive pressure between the seals. Alternatively, the passage lead to the lower pressure outlet of cooling liquid from between the engageable members This prevents leakage of cooling liquid and the seals are held under pressure to prevent leakage of air into the cooling liquid which would cause frothing of the liquid during circulation. The scope of the present invention is defined by the appended claims; and how it can be carried into effect is hereinafter particularly described with reference to the accompanying drawings, wherein:Fig 1 is a transverse cross section of a liquid cooled friction brake according to the lPrice< invention for the rear wheel of a vehicle; Fig 2 is a cross section on the line 2-2 of Fig 1; Fig 3 is a cross section on the line 3-3 of Fig 1; 50 Fig 4 is a half cross section at right angles to that of Fig 1; Fig 5 is a cross section of a friction brake according to the invention for the front wheel of a vehicle; 55 Fig 6 is a cross section on the line 6-6 of Fig 5; Fig 7 is an elevation in the direction of the arrow 7 in Fig 5; Fig 8 is a diagram of a brake system in 60 corporating the brakes shown in Figs 1 and 5; Fitg 9 is an enlarged cross section of part of Fig 1: and Fig 10 is a transverse cross section of a 65 modified form of brake according to the invention for the rear wheel of a vehicle. A vehicle has a pair of front wheels 11 (Fig 8) and a pair of rear wheels, to which are applied brake assemblies 10 and 20, re 70

spectively Each rear wheel 12 is mounted on a flange 65 at the end of a rear axle 26 which is encased in an axle housing 66 connected to a differential casing A radial flange plate 67 is welded to the axle hous 75 ing 66 and supports a housing 27 for the rear wheel brake assembly 20-by bolts 68. The housing 27 encloses a chamber 69 within which is a multi-plate friction brake 80 The multi-plate brake 25 comprises a plurality of alternately disposed stationary annular friction plates 70 and rotatable annular friction plates 90 A stationary carrier 71 is secured to the housing 27 by screws 85 79 and consists of a radial wall 72 and an annular wall 73 which has axial slots 73 to receive ears 75 on the outer peripheries of the friction plates 70. A rotatable carrier 82 has a hub 80 sup 90 Price 785,426 ported upon the axle shaft 26 by splines 81. The carrier 82 also has a plurality of outwardly projecting teeth 83 engaged by inwardly projecting teeth 84 on the brake plates 90. At opposite ends of the stack of brake plates are wear plates 91 and 92 which bear, respectively, against the radial wall 72 and against an annular pressure plate 95. The pressure plate 95 has notches into which fit the ends 96 of the annular wall 73. A wavy retraction spring 97 between the pressure plate 95 and a retaining ring 98 in the housing 27 normally maintains the pressure plate in the released position. The pressure plate 95 has an annular projection 100 which extends into an annular groove 101 in a closure plate 102 supported on the flange plate 67 by bolts 103 The annular groove 101 also contains an annular piston 105 "T" shape in cross section, the stem 106 of the piston 105 extending into an annular slot 107 in the end of the annular projection 100 An annular ring seal 108 is located between the piston 105 and the projection 100 on one side of the stem 106 of the piston and a similar ring seal 109 is located on the opposite side of the stem 106 between the piston 105 and the projection 100. The annular space 110 between the head of the piston 105 and the bottom of the recess 101 forms an annular wheel cylinder 28 connected through a connector 111 to receive hydraulic fluid under pressure from a master cylinder 22 (Fig 8) through hydraulic lines 21 19, 29 and 31 The master cylinder is operable by a pedal 23 The ring seals 108 and 109 seal against leakage of fluid between the chamber 69 and the annular space 110. The seals 108 and 109 have a square transverse cross section (Fig 9) that is substantially the same as the transverse cross section of the spaces between the head 105 of the annular piston and the projection 100 on the pressure plate 95, so that upon application of fluid under

pressure to the space 110, there is substantially no movement of the annular piston 105 relative to the pressure plate 95. Due to manufacturing tolerances it is not practically possible to make the seal rings 108 and 109 of exactly the same dimension, and the axial dimension of the seal ring 108 is made slightly greater than the axial dimension of the seal member 109 so that the seal ring 108 determines the position of the pressure plate 100 relative to the annular piston 105. A plurality of adjustment screws 115 permit adjustment of the clearance between the brake plates 70 and 90 Each screw 115 comprises a screw portion 116 threaded into a boss 117 extending from the closure plate 102 through an aperture in the flange plate 67 The forward end of the adjustment screw has an annular groove 118 for an " O " ring seal 119 to prevent leakage of fluid from the space 110 The forward end 121 of the adjustment screw engages the piston 105 to 70 limit its rightward axial movement under the force of the retraction spring 97. The closure plate 102 has an inner annular wall 120 positioned between which and the hub 80 is a thrust bearing 122 At the 75 opposite end of the hub 80 is a thrust bearing 123 between the hub and a ring 124 press fitted on a shaft portion 125 of the axle 26 to retain the inner race 127 of an antifriction bearing 128 against the flange 65 80 The anti-friction bearing 128 has an outer race 129 retained in a recess 130 in the forward wall 27 a of the housing 27 by a retainer plate 131 fastened by bolts 132 An "O" ring seal 133 between the outer race 12985 and the wall 27 a prevents leakage loss of fluid. The hub 80 has external ring seals 135 and 136 at opposite ends thereof the ring seal 136 engaging an inner surface 137 on 90 the annular wall 120 and the ring seal 135 engaging an inner surface 138 on an annular extension 139 of the forward wall 27 a. The ring seals 135 and 136 restrict loss of fluid from the chamber 69 95 To circulate cooling fluid through the brake assembly, an eccentric vane pump 30 is mounted within a pump recess 140 in the housing 27 the radial wall 72 of the carrier 71 forming one wall of the pump housing 100 The pump 30 (Figs 1 and 3) comprises an annular ring 141, of "T" shape in cross section keyed to the hub 80 by means of a ball key 142 The ring 141 carries a plurality of vanes 143 that are held out 105 wardly in engagement with the internal surface 144 of the recess 140 by a ring 145 An inlet passage 145 leads into the recess 140 and is connected to a line 48 of the fluid system (Fig 8) Fluid under pressure is 110 discharged from the recess 140 through discharge ports 147 in the radial wall 72 through the internal space 156 within the plate 91 into the chamber 69 internally of the brake plates 70 and 90 Between adja 115 cent brake plates are friction faces 150 which have a

plurality of grooves 151 (Fig 2) to permit fluid flow in the chamber 69 from within to without the brake plates The chamber 69 externally of the brake plates 120 has a discharge port 152 connected to a line 36 of the fluid system (Fig 8). The carrier 82 (Fig 2) has every third tooth 83 removed to leave spaces 155 which permit distribution of cooling fluid from the 125 space 156 to within the multi-plate brake assembly for circulation through the passages 151 in the friction facings 150. A seal 160 comprising two seal members 162 and 163 is disposed between the axle 26 130 785,426 and the internal surface 161 of the annular wall 120, the seal member 162 sealing against leakage of fluid from chamber 69 and the seal member 163 preventing grease leakage along the rear axle 26 from the differential. A chamber 185 is formed between the seals 162 and 136. A seal member 170 is disposed between the inner and outer races of the anti-friction bearing 128 to seal against leakage of fluid through the bearing The bearing chamber containing the anti-friction bearing 128 is vented by means of a vent passage 176 which is in the wall 27 a and is connected to an annular groove 177 in the body of a check valve comprising a ball 178 urged against its seat by a spring 179 and having an inlet passage 180 from the groove 177 to the ball seat and an outlet passage 181 to the passage 146. A pin 190 is slidable in an opening 191 in the housing 27 and radial wall 72 and engages the wear plate 91 A manually operable lever 192 is pivoted to a boss 193 on the housing 27 by a pivot pin 194 A strut 195 is disposed between the lever 192 and the pin 190 to effect reciprocation of the pin 190 upon rotation of the lever 192 about its pivot pin 194. The lever 192 is connected by a cable to the hand brake of the vehicle so that upon actuation thereof the plates 70 and 90 are brought into engagement by the pin 190. The pin 190 is substantially coaxially aligned with one of the adjustment screws 115 so that the latter takes the thrust. Each brake assembly 10 (Fig 5) has a cap 202 and a closure plate 200 with an axial bore for a kingpin 201 The closure plate 40200 and cap 202 are secured together by bolts 203 with an "O" ring seal 204 therebetween The plate 200 and cap 202 form a housing 17 and enclose a chamber 205 within which is a multi-plate brake 15 cornprising alternately disposed stationary annular friction plates 206 and rotatable annular friction plates 207. The outer peripheries of the stationary plates 206 have external projections which extend into axial slots in an annular wall integral with a radial wall 208 which is secured to the cap 202 At the other end of the stack of plates to the wall 208 is a pressure plate 209

having an annular projection 55210 which supports an annular piston 211 disposed in a groove 212 which forms a wheel cylinder 18 connected by hydraulic lines 19 and 21 (Fig 8) to the master cylinder 22. The inner peripheries of the rotatable plates 207 are splined to a carrier 214, which has a hub 213 carried on an axle spindle 215 by splines 216 The axle spindle 215 has a flange 16, in which a front wheel 11 is mounted, and is journaled in anti-friction bearings 218 and 219 The axle spindle 215 carries the inner races 260 and 221 of the anti-friction bearings 218 and 219, the outer race 261 being supported in a recess 260 in the housing part 202 and the outer 70 race 222 being supported in an annular recess 223 in the housing part 200 and held by a snap-ring 225. The axle spindle 215 is bored to receive a stud bolt 226 which has a radial flange 227 75 at one end engaging the inner race 221 and a threaded portion at the other end engaged by a nut 228 which bears against the end of the axle spindle 215 The flange 227 has slots 235 to receive tongues 236 projecting 80 from the spindle 215 to prevent relative rotation The anti-friction bearings 218 and 219 are taper roller bearings and are adjustable by rotation of the nut 228. Brake cooling fluid can be delivered into 85 the chamber 205 internally of the multiplate brake assembly through a fluid inlet port 230 connected to a line 53 of the fluid system (Fig 8) From the chamber internally of the brake assembly, cooling fluid 90 passes between the plates and is discharged through an outlet port 231 to a line 54 of the fluid system (Fig 8). A ring seal 240 is located between the hub 213 and the annular wall 241 of the 95 housing 202 to provide a resistance seal against leakage of fluid under pressure from the chamber 205 An "O" ring seal 242 is located between the stud bolt 226 and the spindle 215 to prevent leakage of fluid from 100 the chamber 205 through the bore in the spindle A seal 245 is located between an end closure plate 246 on the cap 202 and the spindle 215 to prevent loss of fluid through the anti-friction bearing 218 105 Between the seals 240 and 245 is a bearing chamber 250 connected by a vent passage 251 to the port 231. The discharge lines 36 from the rear wheels are connected by a line 37 (Fig 8) to 110 a temperature responsive valve 40 The valve 40 has a by-pass passage 41 controlled by a valve member 42 actuated by a thermally responsive device 43 and leading into the interior 44 of the valve 40 which is con 115 nected by a return line 46 to the suction lines 48 of the pumps 30. The line 37 is also connected to an outlet passage 49 leading to a delivery line 51 connected through a heat exchanger 50 and a 120 line 52 to the lines 53. The return lines 54 are connected to a line 56 and through a heat

exchanger 55 to a line 57 connected to a reservoir 60, from which a line 58 is connected to the suction lines 48 125 When the rear wheels 12 of the vehicle rotate, cooling fluid is circulated from the pump 30 through the rear wheel brake assemblies 25 to the valve 40 So long as the cooling fluid is below a predetermined 130 785,426 temperature the fluid is returned to the suction lines 48 through the open valve When the temperature of the fluid rises above a predetermined value the thermally responsive device 43 expands and moves the valve member 42 to close the valve Fluid passes through the lines 49 and 51 to the heat exchanger 50 and thence to the front wheel brake assemblies 15 and the fluid heated in the rear wheel brake assemblies is cooled by flow through the heat exchanger 50 before reaching the front wheel brake assemblies. Fluid from the front wheel brake assemblies passes through the heat exchanger 55 and is again cooled before returning to the reservoir from which it is drawn by the pumps 30. Fluid under pressure delivered from the pump 30 into the space 156 and thence into the chamber 69 of the housing 27 has a tendency to leak along the thrust bearing 122 and through the ball key 142 until it is restricted by the seal rings 135 and 136 which prevent higi pressure leakage Some fluid leaks past the seal rings 135 and 136 and enters the spaces 175 and 185 Fluid in the space 185 is vented through the spline 81 and the thrust bearing 123 into the chamber The pressure in the chamber 185 tends to maintain the seal 162 on the shaft 26. The ball check valve permits pressure to build up in the vent line 176 and in the bearing chamber 175 to counterbalance the effect of the spring 179 This pressure is held just at or slightly above atmospheric pressure so that the fluid pressure in the chamber 175 acts on the seal 170 to maintain it under pressure at all times irrespective of the pressure in the line 146, which at times drops below atmospheric This prevents leak ae of air past the seal 170 which air would enter the fluid system and produce frothing of the cooling fluid. Cooling fluid from the chamber 205 can seep through the splines 216 into the chain45-ber 250 to increase the pressure on the seal 245 This pressure is relieved through the vent passage 251 to the low pressure port 231 so that only a minimum pressure will stand against the seal 245 This minimum ( pressure is substantially above atmospheric pressure due to the resistance to flow of fluid from the front wheel brake assemblies in the lines 54 56 the heat exchanger 55 and the line 57 to the reservoir 60 With a positive pressure in the vent line 251 and the chamber 250 leakage of air past the seal 245 into the low 7 r pressure lines of the fluid system is effectively prevented. The liquid cooled friction brake assem613 blies shown in Figs 1 and 5 need not be applied to the rear end front wheels of a vehicle

respectively and the brake assemblies could be reversed as to their wheel positions. In the second embodiment of this invention the friction brake includes a housing 310 carried on an axle housing 311 extending from the differential housing of a motor vehicle The axle housing 311 carries a radial flange 312 to which the housing 31070 and a cover plate 318 are attached by through bolts 313 and nuts 314. The axle housing 311 encloses a drive axle 315 which has a radial flange 316 to which a wheel disc can be secured by studs 75 317. The cover plate 318 has a recess for the outer race 321 of an anti-friction bearing 320 whose inner race 322 is secured on the drive axle 315 A retainer plate 324 holds the 80 outer race 321 in place in the cover plate 318 and a seal 325 between the inner and outer races 322 and 321 prevents loss of fluid from the brake housing 310 through the antifriction bearing 320 85 The housing 310 has a hollow boss 326 which fits into the axle housing 311 and supports a double seal 327 between the housing 310 and the drive axle 315 to prevent loss of fluid from the housing 310 along the shaft 9 ( 315 and entry of fluid into the housing along the shaft. The brake housing 310 encloses a multiplate friction brake assembly 330 including a plurality of alternately disposed annular 95 stationary plates 331 and rotatable plates 332 The stationary Plates 331 are prevented from rotation by engagement with the throuah bolts 313 and the rotatable plates 332 have their internal perinheries splined 100 to fit upon a spline 333 on a carrier 334 secured by splines 335 to the drive axle 315. The plates of the brake assembly 330 can be engaged by an annular piston 340 which has an annular extension 341 slidable in an 105 annular groove 342 in the housing 310 The groove 342 forms a chamber 343 connected to receive hydraulic fluid from a master cylinder (not shown) of the motor vehicle which is operated by a brake pedal Delivery 110 of fluid into the chamber 343 from the master cylinder effects axial movement of annular piston 340 to apply pressure to the plates 331 and 332. Compression springs 345 carried upon 115 studs 346 a release the brake when hydraulic pressure is removed from the space 343. The brake assembly 330 divides the chamber of the brake housing 310 into an internal chamber 346 and an external chamber 347 120 Fluid under pressure is delivered into the internal chamber 346 from a fluid pump 350 for passage between the plates of the assemblv 330 and discharge through an outlet port 351 The outlet port 351 is connected 125 through a heat exchanger 352 to an inlet passage 353 to a suction chamber 390 of the fluid pump 350 The pump 350 when driven by the drive axle 315 circulates fluid under pressure into the chamber 346

and through 130 785 $ 26 the brake assembly 330 and through the heat exchanger 352. The fluid pump 350 is an eccentric vane pump and has a plurality of vanes 360 carried in a rotor 361 which rotates in a pump chamber 362 in the brake housing 310 The pump vanes 360 are held against the internal periphery of the pump chamber 362 by annular rings 364 the rotor 361 is keyed to the hub, 334 by one or more lugs 365 so that the pump vanes 360 rotate within the pump chamber 362 whenever the drive axle 315 is rotated to cause the pump 350 to circulate fluid when the axle 315 rotates. The pump chamber 362 has a radial closure wall 370 which is disposed between the pump chamber 362 and the chamber 346 and is retained in position in a recess 371 by a snap ring 372. To reduce flow of pressure fluid from the chamber 346, a metal ring seal 373 is disposed between the hub of the carrier 334 and the cover plate 318 and a metal ring seal 374 is disposed between the hub of the carrier 334 and the wall 370 There is some leakage of fluid past the ring seals 373 and 374 into an internal cavity 375 of the pump 350 and into a cavity 376 adjacent the antifriction bearing 320 The cavities 376 and 30375 are interconnected through the clearances in the spline 335 so that there is the same fluid pressure in the cavity 376 as in the cavity 375. To prevent the fluid pressure in the cavities 376 and 375 rising to a high value and thereby impressing a high fluid pressure on the seals 325 and 327, a pressure operated valve 380 is adapted to open when pressure in the cavity 375 reaches a predetermined value. The valve 380 comprises a valve member 381 which engages a valve seat 382 formed on the periphery of an opening 383 in the wall 370 A compression spring 384 between the valve member 381 and the housing 310 normally retains the valve member 381 on the valve seat 382 to close the opening 383. The valve 380 is disposed in the suction inlet chamber 390 of the pump 350, with which the passage 353 communicates. The port 383 in the wall 370 communicates with a passage 385 formed by a plate 386 secured to the wall 370 by brazing or welding and communicating through an opening 387 in the wall 370 with the cavity 375 internally of the pump 350. When fluid seeping past the seals 373 and 374 creates a pressure in the cavities 376 and 375 above a predetermined value, the valve element 381 is lifted off its seat 382 to allow fluid to escape from the cavities 376 and 375 through the opening 387, the passage 385 and the port 383 into the suction inlet chamber 390 of the pump 350 Thus the fluid pressure in the cavities 375 and 376 is maintained below a maximum predetermined positive fluid pressure so that the seals 327

and 325 are not subject to a fluid pressure of more than a fixed value At the same time, a minimum pressure at or above atmospheric 70 is maintained in the cavities 375 and 376 to prevent the entry of air even when the pressure in the inlet chamber 390 is below atmospheric.

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* GB785427 (A)

Description: GB785427 (A) ? 1957-10-30

Improvements in screens and sieves

Description of GB785427 (A)

PATENT SPECIFICATION Invenito: ROBERT ALAN 'MUSGROVE 7 Date of Application and filing Complete Specification: June 15, 1956. No 18695/56. -4 (Patent of Addition to No784,995 dated Dec19, 1955). Complete Specification Published: Oct 30,1957. Index at acceptance:-Classes 46, D 3 C; and 117, B 4. International Classification:-B Old B 02 f. C Oi M Pi LETTE SPECIFICATION Improvements in Screens and Sieves We, THOMAS DE LA RUE & COMPANY LIMITED, a company organised under the laws of Great Britain, of Imperial House, 84/8,6 Regent Street, London, W 1, 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 screens and sieves, and particularly to jigger screens which are used in coal washing plant to remove water from coal slurry tailings from the main plant.

Such jigger screens are described, in the specification of our co-pending application No. 27315/54 (Serial No 784 J 995), and this invention, is an improvement in or modification of the invention therein described and claimed. In, the said specification the screen or sieve comprises a plurality of individual longitudinal slats mounted on edge in parallel relationship to each other, each slat having its top and bottom edge parallel and one side at right angles thereto, the other side being tapered downwardly for at least part of its depth, and a number of spacing elements on said other side at regular intervals therealong, each spacing element having an outer face at right angles' to the top and bottom edges and increasing fractionally the width of said top edge of each slat for the length of each spacing element, so that there is provided, between adjacent slats a number of longitudinal slots each of whose length is determined by the;distance between the spacing elements on each slat, and the width of each slot being a minimum at the top and increasing downwardly in accordance with the tapered side of each slat. According to the present invention the top surface of each slat is of constant width and one side is formed with a taper from the top to adjacent the bottom edge, said side having formed integrally therewith a number of spaced locating means having a reverse taper on their inner faces and, vertical outer faces, whilst the spacing elements are adapted to be detachably secured to said locating means. The spacing elements may be rectangular and may be of the same dimensions as that lPrice-dt of a locating means, or may be of less width than that of a locating means in order to increase the open area of the screen. The invention is illustrated in the accompanying drawing in which Figure 1 shows the slat with its locating means in front elevation, Figure 2 is a section on the line I-I Figure 1, and Figure 3 ' a detail of a spacing element. Referring to the drawing there is shown a slat 1 which has top and bottom parallel edges 2., 3, and one side 4 at right angles to said edges The other side of the slat has a portion adjacent the base, which is parallel to the side 4, and, then' diverges in' taper form' as shown at '6 up to the top, edge 2, It will be appreciated that the slat at the bottom edge is of reduced thickness compared to the top edge. At regular intervals along the length of the slat there are formed integrally with the slat locating means 7 which are formed with a reverse taper to that of the slat 1, so that the slat at the said locating means has the same thickness at the top and bottom edges, so that the slat throughout its' length has a constant thickness along

its top edge 2. A spacing element 8 is adapted to be detachably secured to each locating means 7, for example by means; of cross ties such as 10, as illustrated in the said specification No 27315/ 54 (Serial No, 784,9915)' The spacing element as shown has the same length along its base as that of a locating means 7, but its top edge is of reduced width as compared with that of the locating means, although as previously stated, the dimension at the top may be the same as that of the locating means; The method of assembly of a screen is exactly the same as that described in the said co-pending specification No 27315/54 (Serial No 784,99,5). It will be appreciated that with a screen or sieve constructed in accordance with this invention it is possible to produce a light weight, strong and durable screen which can, be easily assembled or disassembled, so as to facilitate cleaning and, the replacement of those parts which are subject to considerable wear and tear 859427 785,427

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