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* GB785478 (A) Description: GB785478 (A) ? 1957-10-30 Improvements in or relating to control systems for electric winder motors Description of GB785478 (A) PATENT SPEIFICATION 7 Inventor:-ERICH SIEGFRIED FRIEDLANDER. Date of filing Complete Specification: April 27, 1956. Application Date: April 28, 1955 No 12316155. Complete Specification Published: Oct 30, 1957. Index at Acceptance: -Class 38 ( 3), J 1 (B: H 2 A: N 1: N 2: U), J( 2 B 2 B 2 B 2 X: 5: 12 H 2), M( 22 B: 22 D 3: 23 B 2: 27 X: 28 A: 2 SB: 43 A: 43 D: 48: 56). International Classification:-H 02 p. COMPLETE SPECIFICATION. Improvements in or relating to Control Systems for Electric Winder Motors. We, THE GENERAL ELECTRIC COMPANY LIMITED, of Magnet House, Kingsway, London, W C 2, a British Company, 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

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* GB785478 (A)

Description: GB785478 (A) ? 1957-10-30

Improvements in or relating to control systems for electric winder motors

Description of GB785478 (A)

PATENT SPEIFICATION 7 Inventor:-ERICH SIEGFRIED FRIEDLANDER. Date of filing Complete Specification: April 27, 1956. Application Date: April 28, 1955 No 12316155. Complete Specification Published: Oct 30, 1957. Index at Acceptance: -Class 38 ( 3), J 1 (B: H 2 A: N 1: N 2: U), J( 2 B 2 B 2 B 2 X: 5: 12 H 2), M( 22 B: 22 D 3: 23 B 2: 27 X: 28 A: 2 SB: 43 A: 43 D: 48: 56). International Classification:-H 02 p. COMPLETE SPECIFICATION. Improvements in or relating to Control Systems for Electric Winder Motors. We, THE GENERAL ELECTRIC COMPANY LIMITED, of Magnet House, Kingsway, London, W C 2, a British Company, 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 control systems for electric winder motors. An object of the present invention is the provision of a control system which takes full advantage of the maximum feasible deceleration of the winder motor during normal operation. According to the present invention, in a control system for an electric winder motor and having a decelerating cam arranged to be driven by said motor for controlling the deceleration of said motor as a winder cage or the like approaches a stopping point, means is provided for delaying the initiation of electric braking of said motor under the control of said cam in dependence upon the load on the motor, and the rate of deceleration of said motor also under the control of said cam is arranged to be varied in dependence upon the load on the motor.

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The said means may be arranged to vary in effect the shape of the decelerating cam and one such means comprises a first member displaceable by the decelerating cam and a second member, for actuating electric braking means, displaceable by displacement of the first member, the ratio of the magnitudes of the displacements of the two members being arranged to be varied in dependence upon the load on the winder motor. The said first and second members may comprise a pair of pivoted lever arms interlPrice 3 s 6 d l connected by a pivoted link member having a variable pivot point whose position relative to the link member is arranged to be varied in dependence upon the load on the motor. Alternatively the said means may be arranged to vary in effect the shape of the decelerating cam by producing a displacement of the cam relatively to the position of the winder cage or the like and by altering, the speed ratio between the winder motor and the decelerating cam The said means may therefore comprise a gear system having two differential gear mechanisms, one, a differential mechanism, for effecting the displacement of the cam and the other mechanism for effecting the alteration in the speed ratio. Further, in a control system particularly suited to alternating current winder motors, the said means may comprise a tachometer generator driven by the winder motor and whose field excitation is arranged to be varied in dependence upon the load on the winder motor, the output voltage of the generator being arranged in opposition to a second voltage dependent on the position of the winder cage or the like, electric braking of the winder motor being arranged to be prohibited until said second voltage is less than said output voltage. Four control systems for a winder motor and in accordance with the present invention will now be described by way of example with reference to the five figures of the diagrammatic drawings accompanying the Provisional Specification and the single figure of the accompanying drawing In the drawings accompanying the Provisional Specification:0,478 - I_;' l ' ' 785,478 Figure 1 shows the essential parts for enabling the working of the first system to be understood; Figure 2 is an explanatory diagram to be read in conjunction with Figure 1, Figure 3 shows the essential parts for enabling the working of the second control system to be understood; Figure 4 is an explanatory diagram to be read in conjunction with Figure 3; and Figure 5 shows the essential parts for enabling the working of the third system to be understood. In the single figure of the accompanying drawing is shown the essential parts for enabling the working of the fourth system to be understood. Referring now to Figure 1 of the drawings the control system for the

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winder motor (not shown) comprises a load sensitive device which measures the load on the winder motor and a decelerating control which controls the deceleration of the winder motor as a winder cage approaches a stopping point, the load sensitive device being interconnected with and thus varying the decelerating control of the winder motor in dependence upon the load of the winder motor. The load sensitive device comprises two torque motors, having their windings connected to a three phase a c supply having supply leads R, Y, B which supply the winder motor The first torque motor 1 is a 3,5 power torque motor having a winding 2 connected to a current transformer 3 which is in circuit with one of the leads, say R, of the a c supply and a second winding 44 connected across the leads Y and B of the a c supply A second torque motor 4 is a brake motor and has a winding 5 connected across the leads Y and B of the a c supply and a second winding 6 connected across the leads R and B of the a c supply through an induction regulator 7 The induction regulator is connected across the a c supply and has its armature 8 connected in series with the winding 6 of the torque motor 4. The two motors 1 and 4 have their rotors connected on a common shaft 9 and are so connected to the a c supply lines that they oppose one another The shaft 9 has a worm 10 which drives a worm wheel 11, the worm wheel 11 in turn driving a shaft 12 which rotates the armature 8 of the induction regulator 7 and a cam 13 through a torque amplifier 131 Since the motor 1 derives its torque from the supply voltage and the winder motor current and the motor i> 4 derives its torque from the supply voltage through the induction regulator 7, then for each different load on the winder motor, the shaft 12 is rotated thus setting the cam 13 and the armature 8 of the induction regulator M 7) 7 in a different position for each different load The cam 13 has a feeler 14 in the form of a wheel which follows the surface of the cam 13 when the cam 13 is rotated. The feeler 14 is fitted to one end of a lever which is pivoted at a fixed pivot 16, the 70 other end of the lever 15 being provided with a pin 17 which is connected into the decelerating control. The decelerating control comprises basic. ally a decelerating cam 18 which is driven 75 by the winder motor, a pattern speed potentiometer 19 and interconnecting mechanism which transmits movement of the cam 18 to the potentiometer 19 and thus decelerates the winder motor according to 80 a certain pattern of speed The interconnecting mechanism has a feeler 20 in the form of a wheel which, when the cam 18 is rotated about its axis, follows the surface of the cam 18 The feeler 20 is fitted to a lever 85 arm 21 which is pivoted at a fixed pivot point 22 A second lever arm 23 is pivoted at a fixed pivot point 24, near the pivot point 22 and has a

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contact 25 which moves over potentiometer 90 19 The two lever arms 21 and 23 are interconnected by a link member 26 which is pivoted at one end to the lever 21 and is provided at its other end with a pin 27 fitted in a slot 28 in the lever 23 The pin 17 95 on the lever arm 15 is fitted in a circular slot 29 in the link member 26, the centre of curvature of the slot being at the pivot 16. The deceleration of the winder motor is 100 effected by moving the contact 25 on the arm 23 over the segments of the potentiometer between points "y" and "z" the pattern voltage derived from the potentiometer being fed to the speed control circuit of the 105 motor This movement of the contact 25 is derived from the rotation of the cam 18 through the levers 21 and 23 and the line member 26 For different loads on the winder motor the pin 17 is at different posi 110 tions in the slot 29 and since the link member 26 rotates about the pin 17 on movement of the lever arm 21, the ratio of the distance moved by the feeler 20 to the distance moved by the contact 25 is varied for different loads 115 on the winder motor. If, for example, a winder cage is ascending a mine shaft at its maximum speed and carrying a load, the cam 13 is rotated to a position dependent on the load When the 120 cage is at a predetermined position in the mine shaft, which position is the same for all loads, the cam 18 which is driven by the winder motor rotates the lever arm 21 about the pivot 22 and thus, moves the contact 25 125 over the potentiometer 19 At the initiation of movement of the arm 21 the contact 25 is arranged to be somewhere between points "." and "y" on the potentiometer, however until the contact 25 reaches the point "y" on 130 the change of speed with distance for minimum load, the curve "g" representing the change of speed for maximum load and A d representing the change in decelerating distance 70 Referring now to Figure 5, which shows the third control system which is particularly suitable for an alternating current winder motor, the load sensitive device is again the same as that described with reference to 75 Figure 1 In this system the load sensitive device varies the position of a contact arm 44 of a potentiometer having segments 45. The potentiometer is connected across a direct current supply D C and the field 80 winding 56 of a tachometer generator 47 is connected in series with the potentiometer segments 45 A pattern speed potentiometer 48 is also connected across the supply D C. and has a fixed tapping point 49 and a vari 85 able tapping point 50, the position of which is governed by the decelerating cam (not shown) The two tapping points 49 and 50 are connected across the output terminals of the tachometer generator 47, a torque con go trol winding 51 for the winder motor being connected between one output terminal of the tachometer generator 47 and the variable tapping point 50.

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The tachometer generator 47 is driven by 95 the winder motor at a speed proportional to the speed of the winder motor and during the deceleration period the variable tapping point 50 is arranged to be at a position on the potentiometer 48 relative to the position 100 of the winder cage in the mine shaft, the farther the winder cage is from the stopping point, the greater the voltage across the tapping points 49 and 50 When the winder motor is running at full speed the tacho 105 meter generator voltage is arranged to be slightly less than the maximum voltage derived from the potentiometer 48 so that the residual current serves to keep the a c. winder motor at full speed with its rotor re 110 sistance short circuited. If the tachometer generator output voltage corresponding to a certain load is E 1, then as long as the voltage Ep between the tapping points 49 and 50 on the potentio 115 meter is greater than E, deceleration cannot begin However when E, is greater than Ep the current between the tapping points 49 and 50 reverses and deceleration can begin. By varying the position of the potentiometer 120 arm 44 with change in load the excitation of the field winding 46 and thus the output voltage of the tachometer generator 47 is varied and thus the initiation of electric braking or deceleration is varied 125 If for instance, with increasing load the excitation of the winding 46 is correspondingly reduced, the output voltage of the generator 47 is reduced and the position of the winder cage when the potentiomneter volt 130 Llie potentiometer, deceleration of the winder motor cannot commence since between the points "x" and "y" there are no potentiometer segments. In Figure 1 of the drawings the lever arm is shown in the position for minimum load, the position for maximum load being indicated by the dotted line 30 Therefore the greater the load, the nearer the contact to O is to the point "x" on the potentiometer at the initiation of rotation of the lever arm 21 and the greater the speed of movement of the contact 25 over the potentiometer 19. Thus as can be seen from the graph of Figure 2 the greater the load, the nearer the lift cage is to the stopping point before deceleration and the greater the deceleration. In Figure 2 the speed of the winder motor is plotted against distance travelled, the point "b" indicating maximum speed, the curve "c" indicating change of speed with distance for minimum load and the curve "d" indicating the change of speed with distance for maximum load By varying the position of the pin 17 with a change in load what in effect has taken place is a change in the shape of the cam with a change in load on the winder motor. Referring now to Figure 3, which shows 330 the second control system,

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a load sensitive device (not shown) which is the same as that described with reference to Figure 1 is provided but instead of varying the position of a cam it rotates a gear wheel 31 which drives a shaft and a second gear wheel 33 The shaft 32 has a worm 34 which drives a worm wheel 35, the wheel 35 in turn driving a worm 36 to alter the gear ratio between a pair of conical gears 37 and 38 which form a differential gear mechanism The gear wheel 3-3 drives a gear wheel 39 of a differential mechanism which has three further gear wheels 40, 41 and 42 The drive from the winder motor shaft is transmitted to the decelerator cam 43 through the differential gear mechanism and conical gears 37 and 38. For each load on the winder motor the gear wheel 31 is rotated through an angle thus altering the speed ratio between the conical gears 37 and 38 and thus between the winder motor shaft and the cam 43 and also producing rotation of the gear wheel 39 thus producing rotation of the cam 43 relatively to the winder motor shaft As in the first a arrangement we have therefore changed the effective shape of the cam 43 so that the greater the load, the nearer the lift cage is to the stopping point before deceleration and the greater the deceleration. fi O The result of changing the effective shape of the cam is illustrated in the graph of Figure 4 which shows speed of the winder motor against distance travelled by the winder cage, the point "e" representing maximum speed, the curve "f" representing 785,478 age is equal to the tachometer generator voltage which is now, say E 2, will be nearer to the stopping point Therefore the deceleration must take place in a shorter period and the decelerating current is automatically increased to satisfy the new condition At the same time the minimum speed known as the creep speed at which the cage approaches the stopping point will be slightly greater the greater the load and this is favourable since it helps to compensate for the greater deceleration available when a mechanical brake is applied. If this system were used for a D C winder it would be necessary to have an additional overriding speed limitation incorporated so as to render the general characteristics of the D.C control comparable to that of an induction motor operating near synchronous speed Without this feature the reduction of excitation on the tachometer generator would merely lead to increased speed of the winder motor. In the three systems so far described the load sensitive device for measuring the load on the motor has been that illustrated in Figure 1 of the drawings accompanying the Provisional Specification, and this load sensitive device has been connected into the decelerating control by various methods such as the pivoted lever 15, the gear mechanisms 31 to 42 and the potentiometer 44, 45 A further load sensitive device is shown in the drawing accompanying this Specification.

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As before current transformers 60 and 61 are connected in the supply leads to the winder motor The current transformers 60 and 61 thus serve to measure the load on the winder motor and are connected to coils of a bi-phase wattmeter torque system 63 as shown which controls a constant speed regulating motor 64 depending on the contact operation of the relay controlled by the wattmeter torque system 63; depending on whether the load is above or below a certain datum value, either relay contacts 65 or relay contacts 66 are bridged by contact 67. If relay contacts 65 are bridged a circuit from the supply 68 is completed through rectifier 69 to operate relay 70 and open its normally closed contacts 71 and 72 and close its normally open contacts 73 and 74 This contact operation connects the supply 75 to the motor 64 to rotate it in one direction If the relay contacts 66 are bridged a circuit from the supply 68 is completed through rectifier 76 to operate relay 77 to open contacts 78 and 79 and close contacts 80 and 81 and thus connect the supply 75 to the motor 64 to rotate it in the reverse direction. Rotation of the motor 64 rotates the contact arms of two face plate controllers 82 and 83 to vary the deceleration control of the winder motor as will be described. Rotation of the motor 64 also rotates the rotor of an induction regulator 84 through the gearing 85 The induction regulator 84 is so connected to the supply 68 that two A.C voltages are produced, one of which increases from zero to a maximum while the other decreases from a maximum to zero. Both these A C voltages are rectified by rectifiers 86 and 87 and effect a control on the position of bridging contact 67 by being connected to two equal but opposed wind j ing S 88 and 89 of the D C polarised relay 90. From the description above it will be seen that for any load producing a torque by the bi-phase wattmeter system 63, either con So tacts 65 or 66 will be bridged to rotate the motor 64 in one direction or the other Rotation of the motor will continue until the torque produced by the coils 88 and 89 of the polarised relay 90 balances the torque of S; the wattmeter system 63 so that neither of contacts 65 or 66 are bridged When neither of the contacts 65 or 66 are bridged the motor is brought to a quick standstill by reclosure of contacts 72 and 79 which causes D.C brake excitation of the motor Thus the motor 64 is rotated to a different position, determined by the induction regulator 84, for each different load on the winder motor As previously stated, rotation of the " motor 64 rotates the contact arms of face plate regulators 82 and 83 over their contact studs and for each load on the winder motor, the contact arms are set in one position The pattern speed

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potentiometer 91 10 ol as in the previous system is connected to a D.C supply and a voltage signal for controlling the speed of the winder motor is derived from between the negative pole and the movable contact 92 The movable con 10 a tact 92 is driven by the decelerating cam (not shown) and the greater the voltage signal, the greater the speed of the winder motor. The positive pole of the D C supply to the pattern speed potentiometer 91 is connected 11 it> teo the contact arm of the face plate regulator 82 The face plate regulator 82 has each of its stud contacts connected to a different point on the potentiometer winding as shown so that on the position of the con 11-5 tact arm depends the voltage per unit length across the potentiometer and thus the change in voltage signal per unit distance moved by the potentiometer contact 92 and thus the rate of deceleration of the winder motor 12 ' The voltage signal is actually developed across a winding 93 and as can be seen the circuit is through the face plate regulator 83 The face plate regulator 83 has each of its studs connected to a different point on the l '2 potentiometer as shown so that upon the position of the contact arm depends the magnitude of the voltage signal for any given position of the potentiometer contact 92. Now the windinc 93 is the equivalent of the 113 ( 785,478 tern by said cam and wherein means is pro 65 vided for varying in effect the shape of said cam and thus said pattern in dependence upon the load on said motor so that the initiation and rate of deceleration of said motor is varied in dependence upon the load 70 on said motor.

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* GB785479 (A)

Description: GB785479 (A) ? 1957-10-30

Improvements in or relating to teflon hermetic seal

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Description of GB785479 (A)

COMPLETE SPECIFICATION -Improvements in or relating to Teflon Hermetic Seal. WeX THE CONNECTICUT HARD RUBBER COMPANY, a corporation organized under the laws of the State of Connecticut, one of the United States of America, of 407 East Street, City of New Haven, State of Connecticut, United States- of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be par ticularly described in and by the following statement. The present invention relates to a novel method of sealing hollow metal fittings, particularly of the type adapted to receive electrical conducting elements inserted through the wall of a housing for connec tion with electrical apparatus hermetically sealed therein. Heretofore seals of the foregoing character have only been partially effective because the success and permanency of the seals has necessarily depended upon the use of special gaskets and clamping devices which are sub ject to wear and deterioration in service. According to the present invention a seal for capacitor housings and similar vessels is provided which eliminates the use of such accessories and wherein characteristics of the material employed are utilized to form a seal permanently resistant to pressure fluctuations within the housing and which will provide a substantially permanent bond between the conductors and the housing in the form of an integral structure. The foregoing objectives are advantage ously secured according to the invention by the use of a polymerized solid tetrafluoro ethylene resinous material of the type, for example, marketed by the duPont Company

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under the trade name "Teflon," and which is characterized especially by a high co efficient of linear thermal expansion and which is further characterized by a long plastic memory and high electrical resistivity. It is found that an unusually effective hermetic seal for electrical connection may be achieved by a method using a substantially cylindrical body or sleeve of a polymerized solid tetrafluoroethylene resin, preferably including a central bore for a conducting element, which is physically distorted to a diameter less than the minimum inner diameter of the brass or other metal fitting attached to the wall of the housing and then inserted into the fitting. The assembly is then heated to instigate simultaneously radial expansion and axial contraction of the resinous body into fluidtight sealing engagement with the metal fitting. The interior of the fitting is provided with a supplemental gasket material consisting of a silicone rubber elastomer. Referring to the drawing, Fig. 1 shows an elevation of a complete unit; Fig. 2 is a plan view of the unit illustrated in Fig. 1; Fig. 3 shows a "Teflon" cylinder with central bore prior to distortion; Fig. 4 shows such a cylinder after distortion through a die or similar drawing device; and Fig. 5 illustrates the invention employing a seal of a silicone- rubber condensation product. Referring to the drawing, it will be observed that a fitting such as a cast brass body or housing 10 is provided at the lower portion with an annular flange 11 for attachment to the wall housing power capacitors and other electrical apparatus. The housing 10 is customarily provided with one or more central conducting pins 12 threaded at the opposite ends and provided with clamping nuts 13 and 14. The housing 10 is preferably formed with inwardly directed flanges or undercuts 15 and 16 at the upper and lower portions which cooperate functionally with the " Teflon " resinous seal in a manner presently to be described. ReferyingNto Fig. 3, it will be observed that a polymerized tetrafluoroethylene resinous material is formed into the general shape of a cylinder 17 and provided with a central bore 18 for the reception of the electrical conduit rod 12. The diameter of this cylin drical body or sleeve 17 is initially somewhat greater than the inside diameter defined by

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the inner face of the flanges or lips 15 and 16 of the brass fitting 10. The polytetrafluoro- ethylene cylinder is then drawn or extruded through a die or similar device to cause it to assume the general configuration and shape indicated in Fig. 4, having a diameter some what less than the inside diameter of the flanges 15 and 16. The cylinder is then in serted into the brass fitting 10 and the entire assembly is heated to within a temperature range of between approximately 400 and 600" F., and preferably around 500 F. This heat treatment causes inherent lateral expansion of the material to an extent beyond the inner extremity of the upper and lower circumferential flanges 15 and 16, causing the material to flow into molding engagement therewith, as illustrated in Fig. 5. It will be appreciated that, as a result of the heat treatment, a substantially permanent and impermeable hermetic seal is established between the resinous body and the metal fitting 10. It is found that this seal will withstand fluctuations in pressure coming from within the housing and extreme conditions ofatmospheric change from the exterior. Referring to Fig. 5, it will be observed that the layer of silicone rubber is positioned within the undercut before insertion of the resinous body into the fitting. This provides a security factor against leakage. The application of heat to the extended or distorted cylinder of resinous material evidently initiates a molecular rearrangement in the resinous structure which tends to cause the material to revert towards its original proportions. This tendency to reshapement is impeded at the points of projection, namely, at the circumferential flanges or lips 15 and 16 where the maximum sealing effect is desired. The resinous body at these points tends to flow over and beyond the inner portions of the flanges, thereby creating compression areas on their inner surfaces. The compressive stress in the seal areas continues to be exerted after the body has cooled for an indefinite period, and the resulting hermetic seal is essentially permanent. The sealing effect is further achieved and augmented by virtue of the fact that the central bore 18 of the cylinder 17 is of a size such

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that following the heat treatment it is of smaller diameter than the electrical conducting rod 12. Accordingly, after the cylinder has been inserted into the fitting 10 and subjected to the heat treatment above described, the conducting rod 12 is pressed through the central opening 18, expanding the resinous body 17 into close intimate sealing engagement with the inner faces oi the flanges or lips 15 and 16 and the silicone rubber elastomer. The rod is then- secured into position by tightening the nuts 13 and 14 on the threaded ends of the rod 12 to an extent where additional endwise compression is applied to the resinous body 17, further enhancing the hermetic seal secured at the indicated areas. Optimum results are found to be obtain able when the inside diameter of the brass fitting 10 is at least 5 5% greater than the inside diameter of the seal flanges 15 and 16. Also it is found desirable to proportion the fitting in such a manner that the length of the undercut is greater than twice the width of the seal flanges. It is further desirable that the seal flanges 15 and 16 are thin enough to cut intro the resinous cylinder without creating undue stretching of the metal body during the heat treatment of the assembly. In a preferred embodiment of the invention, the projection of the resinous cylinder beyond the ends of the fitting should be no less than the width of the seal flanges or lips. In the event of minor heat expansion, the size or diameter of the conducting rod 12 should be sufficiently greater than the inside diameter of the central bore 18 that, when the rod is forced through the cylindrical member, the circumferential extremity of the resinous body is firmly pressed into sealing engagement with the silicone rubber lining. What we claim is: 1. The method of hermetically sealing an inwardly flanged hollow metal fitting. which comprises inserting a silicone rubber elasto

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mer within the flange of the fitting physically distorting a cylindrical body of polymerized solid tetrafluoroethylene resin to a diameter less than the minimum inside diameter of the fitting, inserting the cylinder into the fitting. and heating the assembly, thereby tending to cause the resinous body to resume its original shape and simultaneously expanding the material into fluid-tight sealing engagement with the flanged portion of the fitting and the elastomer. 2. The method set forth in claim 1, wherein the assembly is heated to a temperature between 400" and 6O0F. preferably approxi mately 500"F. 3. The method set forth in claim 1 or 2 wherein a hermetic seal is formed between a central electrical conduit element and a concentral metallic fitting having inwardly flanged portions. 4. An inwardly flanged hollow metal fitting, a silicone rubber elastomer within the range and a solid polytetrafluoroethylene resinous body molded to the elastomer and

* GB785480 (A)

Description: GB785480 (A) ? 1957-10-30

Machine for abrading grains of wheat or other cereals

Description of GB785480 (A)

PATENT SPECIFICATION 735,480 Date of Application and filing Complete Specification: May 10, 1955. No 13500155. Application made in Germany on June 2, 1954. Complete Specification Published: Oct,30, 1957.

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Index at Acceptance:-Class 58, A 2, AH( 4 B 6 A). International Classification:-BO 2 b. COMPLETE SPECIFICATION Machine for Abrading Grains of Wheat or Other Cereals I, EDGARD GRIMARD, of 90 rue Louvrex, Liege, Belgium, of Belgian Nationality, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement:- The invention has for its main object to provide a self-balanced machine for abrading grains of wheat or other cereals The grains are abraded in this improved machine by their passage over abrasive material lining the interior of tubular containers or cylinders, to which an orbital movement is imparted, a plurality of containers being disposed horizontally in the manner of cross-struts between two connecting rods, on each side of the machine, the containers being arranged in two groups working in opposition to one another and being given their orbital motion from a common driving shaft, thus bringing about an automatic balance of the moving parts, so that no equilibrating mass is needed. This great advantage is of primary importance in the construction of high-speed machines from which large outputs can be obtained. For this purpose, the improved abrading machine is characterized by the fact that between parallel, vertical cheek-plates of substantially rectangular shape, there are mounted a driving shaft disposed horizontally and substantially centrally, and at the corners of the cheek plates four secondary shafts, the central driving shaft having on each end and outside of the cheek plates two eccentric discs mounted thereon, in phase opposition and in parallel planes; the periphery of each eccentric disc is engaged by a strap forming the crosshead-of a V-shaped connecting rod at the junction of its two arms, the two rods on each side of the -machine being thus also in opposition but preferably in the same vertical working plane; the ends of the arms of each connecting rod are articulated on lPrice 3 s 6 d l crank-pins upon discs keyed on the outer ends of two of the secondary shafts in such a manner that, on each side of the machine, there are two opposed connecting rods, and each arm at the front of the machine is con 50 nected to the corresponding arm at the back, through openings in the cheek plates, by the tubular abrading containers or cylinders, which act as cross-struts; these containers or cylinders comprise internal means for abrading 55 the grains during their passage through said containers, which inter-communicate at alternate ends, the material to be treated entering at 6 ne end of each upper container and passing downwards in zigzag paths to outlets 60 from the lower containers.

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The invention is hereinafter described with reference to the accompanying drawings, representing by way of explanation, a form of embodiment of the abrading machine in 65 accordance with the invention. In these drawings, Fig 1 represents a front elevation of the machine; Fig 2 represents a plan view thereof; Fig 3 represents by way of example a 70 longitudinal section of one of the several tubular abrading containers or cylinders with which the machine is equipped; and Fig 4 represents diagrammatically the zigzag path followed by the material to be 75 treated in an assembly of four abrading containers or cylinders. Referring to Figs 1, 2 and 4, the numeral 1 represents the ground support or base of the machine frame, provided with two vertical 80 cheek plates 2 and 2 a, which ate parallel to one another and of substantially rectangular shape as seen in Fig 1 The numeral 3 represents a central driving shaft disposed between the cheek plates 2 and 2 a, upon 85 which shaft there is mounted a driving pulley 4 Upon the ends 3 a of the shaft 3, outside of the cheek plates 2 and 2 a which are joined by cross-struts 10, there are disposed two eccentric discs 5, set in phase 90 opposition in one another and in parallel vertical planes The eccentric discs 5, on the same side of the machine in relation to the plane of symmetry marked at X-Y, are engaged by-eccentric straps 8 and those on the other side are engaged by eccentric straps 6 The strap 8 engaging each outer eccentric disc 5 forms the crosshead of a connecting rod 7 which is of V-shape, the ends 8 a of the divergent arms of the rod being connected to crank-pins 13 upon discs 12 carried on one side of the machine, outside the cheek plates 2 and 2 a, by the ends of two secondary shafts 11 Similarly the strap 6 engaging each inner eccentric disc 5 forms the crosshead of a connecting rod 9 which likewise is of V-shape, the ends 9 a of the divergent arms -of this rod' being connected to crank-pins 13 upon discs 12 carried on the other side of the machine, outside the cheek plates 2 and 2 a, by the ends of two secondary shafts 11 In the cheek plates 2 and 2 a, there are provided openings 14 within which are disposed the tubular abrading containers or cylinders, forming two groups on each side of the plane of symmetry X-Y. On the left of this plane (as viewed in Fig 1) are the group 16 a, 16 b, 16 c and 16 d, and the adjacent group 17 a, 17 b, 17 c and 17 d, the two groups forming rigid assemblies connecting the rods 7 on this side of the machine. To the right of the plane of symmetry X-Y, there is seen the other assembly, namely the group 18 a, 18 b, 18 c and 18 d and the adjacent group 19 a, 19 b, 19 c and 19 d, connecting the rods 9 on the other

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side of the machine. The two upper containers 16 a and 17 a of the left-hand assembly and the two upper containers 18 a and 19 a of the right-hand assembly are individually supplied with the material to be treated which enters them at one end by tubes such as 20 and passes at 21 from the other end of each upper container into the container next beneath, then from the latter through a duct 22 into the next lower container, and so on, the last container being evacuated through a tube 23 into a collector duct 24. Fig 4 represents diagrammatically, by the broken line a, the zigzag path of the material in one series of four tubular containers 16 a, 16 b, 16 c, 16 d for example, the entry of air into the containers being indicated by the arrows b and the escape of air from their other ends being indicated by the arrows c. The procedure is similar for the other three series of containers. In Fig 3, which represents a sectional elevation on a larger scale of one of the several tubular containers or cylinders, for example the container 16 a, this container, like all the others, comprises at one end an apertured cover 25, provided with a gauze screen 26, and at the other end another apertured cover 27, also provided with a gauze screen 28, these screens serving to retain the grains in the container The cover 27 is provided with a tubular mouthpiece 29 upon which there may be fitted a flexible pipe (not shown) for connection to a suction device, so that 70 atmospheric air can be made to enter throughl the cover 25, as shown by the arrows b and to issue through the cover 27, as shown by the arrows c; this air current takes -away the. dust or other impurities resulting from the 75 abrasion of the grains on an abrasive surface lining the interior of the tubular container, which surface may be composed of interchangeably removable elements To this end, the central bosses of the covers 25 and 27 of 80 the container are connected by screw-threads to an axial strut 31 with screw-threaded ends, upon which the covers 25 and 27 are screwed respectively until their flanged rims make tight joints upon the ends of the 85 container. It will be observed that by the shape and arrangement of the connecting rods 7 and 9 set in phase opposition and symmetrically in relation to the plane X-Y, the machine is 90 self-balanced, which permits, as already indicated above, of giving the driving motor 3 a high speed of rotation, and of obtaining security of operation of the mechanism for a machine of large output 95 In the example as represented, sixteen abrading containers or cylinders have been shown, but it would easily be possible to provide a larger number. The operation takes place as follows: 100 With the driving shaft 3 in rotation, an orbital movement is communicated to the connecting rods 7

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and 9, moving in parallel vertical planes and thus the material to be treated entering by the tubes 20 into the 105 upper abrading cylinders such as 16 a 17 a, 18 a, 19 a, follows the zigzag path indicated at a in Fig 4, in order finally to drop through the outlet tubes 23 into the collectors 24, while the dust and impurities removed by 110 abrasion are carried off by the air current.

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* GB785481 (A)

Description: GB785481 (A) ? 1957-10-30

Improvements relating to fusible electrical cut-outs

Description of GB785481 (A)

PATENT SPECIFICATION 785,481 Inventors:-RONALD JOHN STANLEY POPE and JOHN WALTER GIBSON. Date of filing Comnplete, Specification: May 8, 1956. lpplication Date: May 11, 1955 No 13666155. Comnplete Specification Publislhed: Oct 30, 1957. Index at Acceptance:-Classes 38 ( 1), G 2 A 1 A, G 4 (A: B: H). International Classification:-1102 d. COMPLETE SPECIFICATION. Improvements relating to Fusible Electrical Cut-Outs. We, ELECTRIC TRA Ns M Iss Io N LIMITED, a British Company, of Etruria, Stoke-on-Trent, Staffordshire, England, 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 fusible electric cut-outs and, more specifically speaking, to cartridge fuses in which fusible units are

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housed in an insulating casing and embedded in an inert arc-quenching powdered material. The object of the invention is to provide a fusible cut-out with a relatively high current-carrying capacity in a compact compass and, to that end, according to the invention, the cut-out has an insulating body formed with a number of parallel bores each containing a fusible unit which comprises a fusible conductor wound around and supported on an insulating core of star-shaped cross-section and embedded in the arc-quenching powdered material. All the fusible conductors may then be connected in parallel between metal terminal caps at opposite ends of the insulating body to form a single fuse of relatively high current-carrying capacity. It is preferred to support each fusible unit flexibly within its bore by means of a wire extending between the unit and the end of the insulating body Each insulating core, for example, may be encircled at each end by a 100 D of wire which is then extended axially and is secured at its end to a metal terminal cap of the fusible cut-out. In order that the invention may be more clearly understood and readily carried into effect, an example of construction of a cutout constructed according to it will now be described in detail with reference to the accompanying drawings, in which:lPrice 3 s 6 d l e 4 s Figure 1 is a central axial section of the fusible cut-out; Figure 2 is a cross-section on the line II-II in Figure 1; and Figure 3 is a perspective view showing a detail of the construction. In the example illustrated, the cut-out has a body or casing a of porcelain and which is of cylindrical shape with a central axial bore b and six further parallel bores bl b 6 passing from one end of the body a to the other and spaced uniformly around the central bore b. Each of the bores bl b 6 contains a fusible unit comprising a core c of insulating material and star-shaped in crosssection and on which is wound helically a fusible conductor d Each unit is flexibly supported at each end by a copper wire e which is shaped with a loop encircling closely the core c near the end and, in fact, engaging in shallow notches f in the tips of the arms of the core c as best seen in Figure 3 The copper wires e have axial extensions at e' which pass out of the bores bl b 6 between the wall of the bore and an asbestos plug g at the left-hand end in Figure 1 and between asbestos plugs h and rings k at the right-hand end The wires e are of such dimensions as to maintain each fusible unit central in its bore The free end of each wire e is then welded to a circular metal cap 1 fitting over the end of the body a and pierced with circular holes to leave the ends of the bores bl b 6 free The end of each fusible conductor d is secured to the copper wire at m and then emnerges from the bore at N past the asbestos plug g or h and is welded to the cap 1 separately from the

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copper wire e. At each end, a metal reinforcing plate o is pressed against the cap 1 and retained by an outer terminal cap p 7 which is pressed 785,481 over the end of the body a on the outside fusible conductor d and the star core c and the walls of the bore bl b 6, are filled with the finely divided arc-quenching powder q such as powdered quartz or marble, which when a conductor fuses, acts to suppress any arcing quickly. In the example, some features already previously known are provided; thus the central bore b contains a high resistance fusible conductor r of coiled tungsten wire also embedded in arc-quenching powder s and this bore b at the right-hand end contains an indicator casing t containing a 15) striker-pin it in front of an explosive capsule v' connected to the end of the tungsten wire r so then when the latter fuses, the capsule v is fired and the striker-Din u forced out. The pin u is provided with fins W which when the striker-Din u is actuated, are engaged by prongs x struck in from the indicator casing t so that the Din it is retained in the extended position to serve as an indicator.

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* GB785482 (A)

Description: GB785482 (A) ? 1957-10-30

Improvements in cutting or shearing machines

Description of GB785482 (A)

PATENT SPECIFICATION 785,482 Date of Application and filing Complete Specification: -May 16, 1955 -

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No 14089/55. Application made in Italy on May 17,y 1954. Complete-Specification Published: Oct 30, 1957. Index at Acceptance:-Classes 31 ( 1), B 3 ( O: C: D: H 2: P 2); and 80 ( 2), C 1 A( 3 A: 4:11 A). International Classification:-B 42 c F 06 d. COMPLETE SPECIFICATION Improvements in Cutting or Shearing Machines. 1 P ERNESTO SAROGLIA, an Italian citizen, of 51 Largo Brescia, Turin, Italy, do hereby delare-the invention, for which I pray that a patent may be granted to me and the method by which it is-to be performed, to be:particularly described in and by the following statement: The invention relates to cutting or shearing machines and especially concerns such machines used in bookbinding work or the like'involving the shearing of paper, cardboard; cloth or the like, Hitherto these machines have been built solely fot hand operation and the original type is that having a curved knife of scimitar-like shape, pivoted at one end and provided with a handle at the opposite endyand adapted to engage with a straight couilterknife In such machines the materials to be cut had to be clamped for the cutting stroke by means of a foot operated device. An -object of -this invention is to -provide the means for obtaining, in an automatic cutting machine -incorporating a straight edged cutting knife and a counterknife, that type of cut in which the portion of the blade in contact with the material to be cut alters as the cutting or shearing stroke occurs, and which is similar to that obtained by the use of a hand guillotine with a scimitar-shaped cutting blade This type of cut will hereinafter be referred to as a guillotine'cut. According to the present invention a cutting or shearing machine including a guillotine knife, a counterknife and a clamp, comprises knife operating means for controlling a detachable coupling between a motor and the guillotine knife and, further, clamp operating means for controlling the clamp whereby it may be operated either manually or automatically in conjunction with the guillotine knife Preferably the detachable coupling comprises a worm positively driven by the motor and driving a worm-wheel loose on a main shaft, a boss fixed to the main shaft, a lPrice 3 s 6 d l spring-biassed pin adapted to couple the boss to the worm-wheel and means for controlling the coupling or uncoupling movement of the pin Preferably also the knife and clamp operating means comprises treadle means 50 The coupling pin controlling means is preferably activated by means of the knife treadle and comprises -a disc which when engaging the coupling pin prevents this from coupling together the boss and the worm 55 wheel

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which-can then rotate iadependently A main shaft may be adapted to drive the guillotine knife through cranks, connecting rods and articulated knife cranks and may also be coupled to the clamp so that this will 60 be operated in timed relationship to the guillotine knife; means may also be provided so as to adjust the pressure exerted by the clamp on the material The clamp may also be lowered manually 65 by means of a main clamp treadle, independently of any automatic operating means. Preferably means are provided releasably to lock the main clamp treadle in its operating position and to release:the locking means 70 after a certain rotation of the main shaft has occurred. A subsidiary clamp treadle may also be provided to release the clamp independently of any automatic clamp operating means 75 Preferably the clamp has a saw toothed edge and illuminating means are positioned beneath the counterknife. The lowering of the clamp may be obtained automatically and in advance of the lowering 80 of the knife whilst the initial lifting of the clamp may be achieved by means of the subsidiary clamp treadle if the knife is in its rest position after the completion of a previous operation whereafter the clamp is 85 lifted automatically after each cut so long as the machine continues to work. The rocking action of the knife, when performing its guillotine cut in a multiplicity of successive operations, facilitates its penetra 90 tion into the materidl thereby, allowing a more exact cut to be made and avoiding the ('i punebing-out " of the material. An example of the invention will now be described with reference to the accompanying drawings, in which:Figure 1 is a front elevation of a cutting machine and illustrates the knife control mechanism, Figure 2 is a further front elevation illustrating the clamp operating mechanisms, Figure 3 is a side elevation of the cutting machine, Figure 3 a is a detail view showing the straight edge and support means, Figure 4 is a detail view of the clamp treadle and linkage therefor, and shows, by means of broken lines, the position of the levers when the treadle is lowered, Figure 5 is a detail sectional view of the coupling device, and Figure 6 illustrates the straight edge when adjusted so that the machine will take only small cuts. Referring to the drawings, a cutting machine includes a knife 9, a counterknife 9 a and a clamp 20, the knife 9 being held in a holder 13 which is pivoted at each end thereof to an articulated crank 10 Each articulated crank 10 is pivotally attached to both the body of the cutting machine and, by means of a joint 12, to one end of one connecting rod 11, the other end of which is attached to the main shaft 4 by means of a crank 5. The articulated cranks 10 and cranks 5 both individually, and in

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phased co-operation, are so designed as to give to the knife 9 a desired guillotine cut when operated by the connecting rods 11 and joints 12. The motor 42 (see Figure 3) is adapted to drive a worm 1 by means of pulleys 40, 41 and a V-belt (not shown) The worm 1 engages with a worm-wheel 2 which is free to revolve on the main shaft 4 A boss 3 is splined onto the shaft 4 to rotate therewith and comprises a coupling pin 6 which is spring-biassed by means of a spring 6 a towards a corresponding recess in the wormwheel 2 A retaining disc 8 is adapted to enter a tapered slot 8 a in the pin 6 and is so arranged that when it is fully housed in said slot 8 a the coupling pin 6 is withdrawn from the worm-wheel and is housed entirely within the boss 3 being held therein against its bias. The disc 8 is operated by a treadle 7 which is connected by means of cranks and levers 14, 15 to the end of the disc 8 remote from the boss 3, the arrangement being such that when the treadle 7 is lowered against the force exerted by a clamp action, the disc 8 is withdrawn from the tapered slot 8 a in the pin 6, which pin then protrudes from the boss 3 and engages with the worm-wheel 2 to couple this to the boss 3 so that the latter and consequently the main shaft 4 rotate with the worm-wheel 2 the cranks 5 connecting rods 11, articulated cranks 10 and knife 9 being operated thereby. After the completion of a revolution i e 70 after the required cut has been performed. the coupling pin 6 is withdrawn by means of the disc 8 which has returned to its original position, acting in the tapered slot $a of the pin 6 75 The clamp 20 is also caused to be raised and lowered in synchronisation with the operation of the knife when the treadle 7 is lowered This is achieved by means of an eccentric 21 fixed on the main shaft 4 and 80 rotated therewith, which eccentric 21 works on one arm 22 a of a bell crank, the other arm 22 of which is adapted to slide a clamp shaft 16 against the action of springs 33 by means of a compression spring 31 acting on 85 a collar 32, which collar is attached to the clamp shaft 16 When the shaft 16 is slidden it actuates the clamp 20 by means of cranks 19 and 19 a and clamp control rods 17 to which latter the clamp is connected 9 Q A crank 34 is provided to regulate the pressure exerted by the clamp 20 and is so arranged that it can alter the respective effective lengths of the two arms 22 22 a-of the bell crank so that when these are operated 95 by the eccentric 21 a different force ratio is exerted onto the clamp shaft 16 and control rods 17. Manual operation of the clamp is controlled by means of the treadle 18 which is 100 connected directly to one of the control rods 17 and to the other by means of crank 19 and clamp shaft 16 When the treadle 18

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is lowered a lever 24 actuated by a spring 26 is adapted to retain the clamp treadle in its 105 lowered position by engagement with a slot 25 in the treadle 18 An eccentric 30 attached to the main shaft 4 is adapted to work on one arm of a bell crank 28 the other arm of which is frictionally engaged with an arm of 110 the lever 24, the arrangement being such that when the eccentric 30 has been rotated through a certain degree the bell crank 28 knocks the lever 24 out of engagement with the treadle 18 releasing this and so allowing 115 the clamp to return to its normal position. The lever 24 has an extension 24 a forming a subsidiary clamp treadle so that the clamp may be released independently of any automatic operating means 120 Manual controls are normally used during the "setting up" of a workpiece in the machine The workpiece is inserted beneath the clamp and then held in position by the clamp on operation of the treadle 18 If it 125is desired further to adjust the position of the workpiece before it is cut, extension 24 a is used to release the clamp After adjustment. the workpiece is again clamped by means of the treadle 18 The machine is then brought 130 785,482 in either claim 2 or claim 3, in which the main shaft drives the guillotine knife through cranks, connecting rods and articulated cranks, said articulated cranks being attached one to each end of the guillotine knife and 70 imparting to said knife its cutting motion. A cutting or shearing machine as claimed in any of claims 2, 3 or 4, -in which means are provided whereby the drive from the main shaft is adapted automatically to 75 raise and lower the clamp in synchronisation with the operation of the knife. 6 A cutting or shearing machine as claimed in claim 5, in which the means comprises an eccentric adapted to operate on one 80 arm of a bell crank, the other arm of which is attached to a clamp operation shaft, the clamp being coupled to said operation shaft by means of cranks and two clamp control rods 85 7 A cutting or shearing machine as claimed in claim 6, in which means are provided to adjust the respective operating lengths of the two arms of the bell crank, so providing pressure control means for the clamp 90 8 A cutting or shearing machine as claimed in any of the preceding claims, in which the knife operating means comprises treadle means. 9 A cutting or shearing machine as claimed 95 in any of the preceding claims, in which the clamp operating means comprises treadle means. A cutting or shearing machine as claimed in claim 9, in which means are pro 100 vided releasably to lock the clamp treadle in its operating position. 11 A cutting or shearing machine as claimed in claim 10, in which an eccentric on the main shaft engages with a crank to 105 release the

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clamp treadle locking means after a certain rotation of the main shaft has occurred. 12 A cutting or shearing machine as claimed in any of claims 9 to 11, in which 110 there is provided a subsidiary press treadle to release the clamp independently of any automatic operating means. 13 A cutting or shearing machine as claimed in any of the preceding claims, in 115 which the clamp has a saw toothed edge to allow of visual control of the material to be cut. 14 A cutting or shearing machine as claimed in any of the preceding claims, in 120 which material illuminating means are positioned below the counterknife. A cutting or shearing machine as claimed in any of the preceding claims, in which a straight edge rule device is provided 125 to assist in the correct measurement of the material to be cut. 16 A cutting or shearing machine as claimed in claim 15, in which the rule device comprises an endless belt positioned over 130 under automatic control and in due course the clamp is released by means of eccentric 30 acting on the bell crank lever 28. A fluorescent lamp 39 is situated below the counterknife 9 a and is protected by means of a shield 35; a special light spreading glass 37 is positioned above the lamp and is supported by means of the case 38 of the cutting machine A series of small openings are situated on the front of the clamp giving it a saw toothed edge to allow a better and more complete diffusion of the light onto that portion of the material to be cut. A straight edge 52 is connected by means of a post 47, toothed rack 46 and attachment means 50 to an endless belt 45, which belt is supported by means of two wheels 44 pivoted on pivots 51 The endless belt 45 has its outer surface 53 graduated to assist in the correct measurement of the material to be cut. The toothed rack 46 is driven by a hand wheel 49 pivoted on a-pivot 48 A lens 43 is provided to read the graduations of the upper surface 53 of the endless belt 45 to accurately position the straight edge 52 by means of the hand wheel 49. When thin sheets of material are to be cut they may be supported by spring biassed pins 54 housed within the straight edge 52 but when a very thin cut is to be made the straight edge 52 is brought extremely close to the counterknife 9 a and the pins 54 are then retained within the straight edge 52 against spring action. -35 Due to the provision of the straight edge 52 sheets may have as small an amount as 1 mm. or less removed from their edges.

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* Accessibility * Legal notice * Terms of use * Last updated: 08.04.2015 * Worldwide Database * 5.8.23.4; 93p