BE509135A - - Google Patents

Description

       

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  CARD RECORDING MACHINE - MORE PARTICULARLY MACHINE
TABULATOR.



   The present invention relates to a recording card machine, preferably designed as a punch card machine, and particularly suitable for the use of combinations of perforations.



  In punched card machines, the recordings are made by punching holes in the columns, at pre-determined locations. Although the invention can be adapted to every possible kind of registration mark and can therefore be suitable for any type of card recording machine, we will speak in what follows for simplicity only of punched cards and machines. punched cards.



   In punch card machines (in particular in tabulators), a control effect, in particular for the transfer of a value represented by a perforation, can advantageously be achieved by two methods.



   According to the first method, which finds its application especially in known HOLLERITH machines, the perforation causes the recording mechanism to be coupled to a continuous drive member, synchronous with the advance of the cards. The uncoupling is carried out during the passage of the row of zeros of the columns under the brushes. In this way is therefore transferred a path corresponding to the distance from the perforation to the line. zeros, and consequently, on the recording mechanism, a value corresponding to this path.



   The other method has long been used in POWERS machines. According to this second method, all the perforation locations of a column are simultaneously explored by feeler rods and the rod having passed through a hole serves as a stop for a positioner with reciprocating oscillation movement. The path traveled by the positioner is transferred to the recording mechanism, for example to the totalizers

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 and the printing device. Since this path is equivalent to the distance from the perforation to the zero line, the registration corresponding to the meaning of the perforations is obtained.



   In recent times, the use of combinations of perforations is more and more appreciated, especially because the current needs involve, in the processes with perforated cards, the processing of texts comprising letters. The representation of letters and numbers (i.e. a minimum of 36 characters) leads to the use of systems with combinations of perforations., If we do not want the card to have exaggerated dimensions and the paper consumption to take on burdensome proportions. crippling the economy of the process.



   However, the two aforementioned methods have this inherent, that they are unusable with combinations of perforations deserving this denomination, that is to say for which one employs the minimum of perforation locations for a given total. of signs. In fact, they are based on the system of single perforation, according to which a sign is symbolically expressed by a single perforation in the card column, while in the system of combinations of perforations, many must be used. signs several perforations? their relative position having a meaning as well as their number. To allow the use of these combinations, several methods have already been proposed, which can be classified into a few large groups.



   In order to exploit the combinations of perforations, it is often proposed to employ conversion bars or discs, each of which is assigned to a perforation location and is moved during the perforation. Depending on the different displacement of the conversion bars relative to each other, only one conversion slit is released, which corresponds to the meaning of the sign formed by the combination of the perforations. Once the combination of perforations is transformed into this unique control effect, it follows that control operations can then proceed according to one of the two methods mentioned at the beginning.

   But this arrangement of the conversion members requires for each column of perforations a number of conversion bars corresponding to the number of the perforation locations.



  To explore the conversion bars, a number of exploration bars must be provided corresponding to the number of signs, or it is necessary to have another exploration device, which restores in time or in space. the exploration result, depending on the position of the selected conversion member corresponding to the sign. It is therefore clear that the arrangement of such mechanical converters complicated the machine, making it very cumbersome and therefore expensive, if one considers that a modern tabulator machine has about one hundred rows of printing members and totalizers. .



   For electrical machines, equivalent electrical embodiments have also been proposed for the mechanical conversion members mentioned above. They are based on the principle according to which each perforation location controls a certain number of electrical conduction paths, the serialization of which selects a single circuit corresponding to the sign of the combination of perforations. The different circuits are electrically exploded one after the other, so that isolated pulses differentiated in time are obtained. These can then be used in the same way as the isolated control pulses triggered by the single holes per board column in HOLLERITH machines.

   As, in these machines with electric converters, there is a need for an organ. conversion rate for each perforation column to be exploited, what has been said for machines with mechanical conversion members is also valid in the present case, as regards the size, the complication and the price.



   Because of the drawbacks observed, \) which have just been explained, of machines working with conversion members, various possible embodiments of machines controlled by combinations of perforations have already been proposed, machines which can be considered in in whole or in part, as devoid of conversion organs. These machines almost describe

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 exclusively on the principle that a determined value is assigned to each perforation location and that the sum of the perforation values of a card column determines the meaning of the sign represented by the combination of perforations.

   The command impositions triggered by the perforated locations are added, so that the total result faithfully provides a command action having the meaning of the combination of perforations.
In a group of these known machines, at each perforation location is assigned a drive of the recording mechanism by means of gears. The toothed drive wheels of the different locations have different numbers of teeth which come into action in succession. The connection of the recording mechanism to the drive required, for each perforation location, a special coupling to the electromagnet.

   Similarly, many other devices, to which for example the control paths are added, have for each perforation location its own positioner and coupling member.



  If one thus avoids the above-mentioned conversion components, mechanical or electric9, this is compensated well beyond by the relatively large number of drive wheels and coupling electros, because it is necessary to imagine that in order to use the alphabet, it is generally necessary to have at least six perforation locations per column and a corresponding number of cogwheels and coupling electros.



   An electrical equivalent of the last mentioned embodiment is possible by using electrical stepping mechanisms which perform for each puncture location a number of steps corresponding to the value of the location.



   But as in these devices the duration of the advance must be calculated in such a way that one can execute for the numbers and the alphabet at least 36 steps, it follows that these devices are limited in efficiency and in speed. In addition, the electric advancement mechanism causes movements, must have sufficiently large dimensions and consequently the numerous relays require a lot of space.



   Apart from the devices listed above, various other devices are also known which allow the use of combinations of perforations without using conversion members. In all these devices, analogous methods are used, which amount to adding the currents or the magnetic fields corresponding to the distinct perforation locations of different values, and which have the drawbacks specific to the aforementioned devices under one or more of these devices. other form.



   Compared to these known devices, the present invention offers a new main principle, the advantages of which appear particularly in the use of perforation combinations without conversion members, but which can find its use with the so-called single perforation system. , when this is advantageous in specific cases. Although the inventive idea is particularly suited to the perforated card process, it will emerge from the description that it can also be applied in machines, for which the registration marks are carried on the cards other than by perforations.



   The invention therefore uses the aforementioned card-recording machines without conversion members, in which each of the marks provided in one of the recording locations of a card column exerts a control action on the control unit. record assigned to the column., the magnitude of this action always corresponding to the values assigned to the locations in the column
But the essential originality of the invention lies in that for all the locations of a column there is provided a common drive member for the recording unit which can be coupled to it member which performs a forward stroke for each location, this course varies automatically:

   during the successive exploration of the locations, according to the values assigned to the locations.

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   The use of a common advancement arm, for example at all the perforation locations, is eoxanu according to the aforementioned machines without conversion members, but the advancement arm still only performs a single stroke, so that an essential feature of the invention is precisely that the travel stroke can vary in accordance with the value of the location. The use of advancement strokes of different amplitudes for the different perforation locations is also known from the aforementioned machines without conversion members, but there is provided for each location a drive member for advancement and even a clean coupling, while in the invention these parts are common to all locations.

   It is obvious that this simplification according to the invention results in great advantages for the construction.



     The advantages of the invention appear immediately if we consider the simplest embodiment. This consists of an advancement arm suitably actuated by a pawl which engages on its side with a control wheel. Whereas in the known devices, for example in electric stepping meters, the arm always executes only the same stroke, but a different number of times for each location, the advancing arm does not execute. according to the invention for each location only one race. But the amplitude of this stroke is automatically adjusted according to the value corresponding to the location and the progression of the ratchet wheel is obtained by a single stroke regardless of the location.



   This new principle therefore makes it possible to connect the recording mechanisms of several units at once, each partial value of the combination being transferred at once. This principle therefore offers efficiency possibilities similar to those of the machines already mentioned Hollerith and Powers, in which the value is also transferred at once.



   Another very important characteristic consists in that both the coupling of the recording mechanism (for example printing device or totalizer) and the uncoupling of said mechanism from its drive are obtained independently of the variable stroke of the drive, always in one of the two reversal points of the driving oscillatory motion where the driving speed is going. This even gives an advantage over Hollerith and Powers machines, because by coupling and uncoupling at the moment of speed cancellation, extremely safe operation is achieved with minimal wear.



   The modification of the advance stroke of the driving member is preferably obtained by a stroke shift device, common to the driving members of all the recording units. Therefore, the shift device is only necessary once and for all the machine
In a preferred embodiment of the invention, the variation of the advance stroke is obtained, during the successive exploration of the locations, by displacement of a slide guide in a crank bar of the drive. If a slide guide is moved in the crank bar during a crank-to-arm stroke the curve described by the end of the crank bar not connected to the crank varies.

   Thanks to a link and a balance, this curved movement can be transformed into an oscillation whose amplitude corresponds to the value of the perforation locations.



   The variation of the advance stroke can be adapted according to the needs to the particular necessities, but in the exemplary embodiment which will be described below ,. it is carried out in the ratios 1: 2: 4: 8: 16: 16. It should be noted that the last two advancement races were divided into 16 units; we thus obtain that, although the greatest possible number of signs can be translated, the maximum advance stroke and the modification

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 fication of lever ratios remain within acceptable limits
Other preferred features of an embodiment of the invention result from the following description and the accompanying drawings.



  This embodiment consists of a tabulator machine controlled by punched cards with two stages and which is suitable for printing amounts and totals. The machine according to 1-'invention without conversion members allows such a compact construction, that a small-format model can be produced, capable of nearmony, thanks to its construction according to the invention, of a considerable flow.



   The appended drawings represent: - Figures 1a and 1b of the perspectives of the machine viewed from the side, and respectively from the right and from the left; - Figs 2 and 3, the perforation code, according to which the cards are perforated, Fig. 3 showing more particularly the code of the digits.



  In column P is indicated the rank of the location in Roman numerals, and in column E the values assigned to the different locations These values are different in Figs. 2 and 3, because the printing mechanism is positioned according to the values in Fig. 2 and the totalizer in accordance with that of FIG. 3. In the upper row of figures of Fig. 2 the position which takes the sign at the periphery of the type wheel has been indicated by a number, and the signs themselves are carried in the lower row.



  In Fig. 3, only the numbers corresponding to the perforation combinations are shown in the lower row.



  FIG. 4 shows a perforated card, as used for the present invention; - Figs. 5 to 9 schematically show 1-crank actuation in its various positions; , - Fig. 10 shows the crank actuation in its actual embodiment, as it appears, when the bottom plate is removed and when the machine is viewed from below; - Fig. 11 is a section taken on line A-B through the crank actuator of Fig. 10; - Fig. 12 shows part of the crank actuator in rear view; - Fig. 13 is a side view of the right side of the machine, housing removed; - Fig. 14 is a section of the machine; - Fig. 15 is a partial view of a type wheel;

   - Fig. 16 shows in section the electro coupling of a type wheel. or totalizer; - Figo 17 shows the coupling mechanism of the type wheel, in section perpendicular to the axis; - Fig. 18 shows the coupling mechanism of the type wheel, partly in section and in top view; - Figs. 19 and 20 show the coupling mechanism of a totalizer unit, in longitudinal section and in section perpendicular to the axis; - Fig. 21 shows from 1-before the arrangement of the wheels of the types of the printing mechanism without showing the types themselves, - fig. 22 shows the distribution of the coupling levers; - Fig. 23 shows the distribution of the couplings ;.



  - Fig. 24 shows a cross-section of the totalizer, - Fig. 25 shows a totalizer unit, viewed longitudinally with respect to the axis;

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 - Figs. 26 to 29 represent the different cams for exploring the position of the totalizers; - Fig. 30 is a circuit diagram for suppressing printing of zeros in front of the highest significant digit of a number; - Fig. 31 is a section through the card scanning device; - Fig. 32 is a device for lifting the brushes during the interval between cards; - Fig. 33 is a rear view of the machine, totalizers removed ;.



  - Figs. 34-36 show details of the card drive mechanism; - Fig. 37 schematically shows the arrangement of the connection panel, in plan view; - Fig. 38 schematically shows the arrangement of the connection panel in perspective; - Fig. 39 shows part of the connection board, in section; - Fig. 40 shows the various zones of the connection panel in plan view; - Fig. 41 shows part of the connection board with a socket for the totalizers; - Fig. 42 shows part of the connection board with a socket for group control; - Fig. 43 is the circuit diagram of the machine; - Fig. 44 is the diagram of the relays and cams of the machine; - Figures 45 to 47 represent the various contacts controlled by cams.



   The tabulator mechanism has been designed to work according to a code which is shown in figure 2. The layout of the code is such that the meaning of a sign is determined by the value which results from the addition of the partial values. assigned to the different locations.



  The assignments of values to the different rows have been chosen in such a way that a given value can only be indicated by a single combination of perforations. In establishing the code. ,, it has also been admitted that for the numbers, the alphabet and the other signs, it is necessary to have about 45 combinations of perforations.



   To leave a certain margin, the code was designed for 47 signs plus 1 empty space, so that in figure 2 we can still assign two signs at will.
The allocation of signs can be carried out arbitrarily for the different combinations of perforations except for the numbers, and the position of a sign in the series of signs is therefore determined only by the numerical significance of the combination of perforations. By arranging the types on a type wheel, it must therefore be divided into forty-eight equal parts. To each of these parts a determined sign is assigned.



   The printing mechanism is made up of a series of juxtaposed printing wheels. There is provided a drive common to all said wheels, drive to which these wheels can be coupled. Mating is performed when a puncture is detected at the location explored. The disconnection takes place automatically when the type wheel has been positioned on the corresponding value and the map is advanced to the next location. We only print when the 6 locations of a column have been explored. Therefore, for each location a coupling can be made, which coupling is then automatically undone for the next location wherever it has just been; performed.

   Thus, it is possible that the

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 type wheel is moved several times in succession before printing.



   The drive is arranged so that the advance stroke which it causes varies from one location to the next with the exception of the two lower locations. If there are several perforations in a column, the feed strokes corresponding to their partial value are added to each other. Assuming, for example, that in a column the third and fifth locations are perforated, the type wheel advances by 4 units when exploring location III and 16 units when exploring location III. location V. In exploring locations I, II, IV and VI, there is no advancement because no perforation exists in these locations and therefore no mating results.

   The type wheel has therefore progressed by 20 units, which corresponds to the letter E according to the sign code.



   Values,! in column E of Fig. 2,, are only valid for the printing mechanism. For the totalizing mechanism, another distribution of the values has been provided which is however similar to that of the printing mechanism, which is given in column E of: FIG. 3.



  Of course, in both figures .. one? same combination of perforations also has the same numerical meaning = Thanks to the different use of the positions, however, it is possible that the zero is effectively transferred into the printing mechanism without being transferred into the totalizing mechanism. In addition, the code gives for the totalizing mechanism, 9 by adding the partial values of the different perforation locations, the exact numerical value, while the types of the digits of the printing mechanism are located in places other than those corresponding to their numerical meaning.



   For example, the number 3 is made up in the totalizing mechanism by the partial values 1 and 2 and by the partial values 2 + 4 = 6 in the printing mechanism, that is to say that the number 3 is at the sixth place at the periphery of the order of types.



   The positioning of the printing and totalizing mechanisms according to the assigned values is obtained from a common drive, a different transmission ratio being provided for one or the other mechanism.



  In addition, the current is controlled by cam contacts and directed to the coupling ele @ tros of the totalisers in such a way that no current flows to the totalisers for the exploration of locations I and VI.



   The punch card (Fig. 4) is constructed as a two-tiered card, each tier having thirty columns each with six punch locations. The perforation columns of each of the two stages are explored simultaneously, one location after another, and the exploration results are fed to the printing and totalizing mechanisms. The machine is provided with 80 printing units which can be connected through the connection board .. to each brush or column. The connection mode will be described more precisely later. The printing and totalizing mechanisms are driven by a crank device. This type of device was chosen because it allows safe and favorable coupling and uncoupling at its dead points.

   In addition, the return movement which necessarily exists in a crank stroke can be used for uncoupling. The positions that the parts of the crank device take during the exploration of a stage are illustrated in the block diagrams of Figures 5 to 9.



   Crank 11 is driven continuously at constant speed in an anti-clockwise direction. During a crank revolution the map is always moved forward by one location. For each complete rotation of the crank 11, the crank 12 advances one division counterclockwise. This progression will be described more exactly below. On the crank 11 is articulated the rod-14 which can slide by a reciprocating movement in a guide or slide 15 (this guide is only represented symbolically on

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 Figures 5 to 9, its actual realization is different).



   The right end of the rod 14 describes an ellipsoidal curve.



   If the slide 15 is moved this curve changes. The balance beam 13 is articulated at the right end of the rod 14 by a coupling bar 16 which moves in an oscillating movement following the said curve. The angle of oscillation of the balance 13 depends on the shape of the curve. The slide 15 is then moved in such a way that the different angles of oscillation of the balance 13 are proportional to the values in FIG. 2. But for the five positions (the sixth being identical to the fifth), an angle must still be deduced. constant within which the balance oscillates when empty, as a result of the play between gears, etc. This play is necessary for another reason, as will be shown later.



  It is further increased artificially so that the drive stops at the time of mating. If the game did not exist, there would always be, even at a standstill! a training movement. The stopping moment would then be reduced to an extremely small instant.



   The position and dimensions of the members of the crank device have been determined so that in a dead center of the balance 13 the slide 15 can be moved as well as the auxiliary crank drive member which cooperates with the slide and which has not yet been described.



   Said movement is effected without the position of the balance, 13 being modified; is necessary because the coupling of the recording units to their drive must always take place in the same place, regardless of the position in which the slide 15 is at that moment. It is therefore necessary to ensure that the slide 15 has reached the positions corresponding to the explorations of the locations of the perforations (positions indicated in FIGS. 5 to 9 by Roman numerals in correspondence with the meaning of the perforation locations) at the second neutral point of balance 13 (shown in dotted lines in Figures 5 to 9), because the position of this point gives the amount by which the type wheel must be offset.



  The displacement of the slide 15 is carried out by the crank 12. The latter performs one revolution by passage of the card. The dimensions and positions have been calculated for this purpose so that the irregular spacings of the slide 15 between its adjustment positions on the rod 14 correspond to regular movements of the crank 12. This results in the advantage that can be achieved. have in addition to the step by step advancement, a continuous drive of the crank 12 from the crank 11 if this is desired.



   As seen in Figure 2, the same value 16 is assigned to locations V and VI. The position of the cranks for these two locations is shown in Fig. 9 and as indicated above, in both cases it should provide the same advance stroke although the crank 12 has turned one division. . This is achieved by the fact that the crank rod 17, which is drawn in solid lines in FIG. 9 for the position V, give in the position VI, drawn in dotted lines? the same position of the slide 15.



   The practical realization of the crank mechanism is illustrated in Figures 10-11-12. The rod 14 which in fact consists of two bars next to each other, is articulated on the crank 11. It has a rectangular recess 14a in which a guide ring 20 (Fig.ll) can slide. The guide ring 20 can turn idle on the axis 18; in addition, on this axis 18, there are also idle guide rings 19, which can slide in the guides 21 arranged on each side of the rod 14, these guides being fixed to the frame. In order to prevent the rod 14 and the guides 21 from interfering with each other and that the guide rings do not move sideways., Between the guide rings 20 and 19, washers 22 have been provided.

   The arrangement of the guide rings allows the sliding of the axis 18 in the guides 21, the sliding of the rod 14 on the axis 18 and the rotation of the rod 14 around the axis 18 relative to the fixed guides 21. The guide rings are moved by means of two coupling bars 23 which are fixed integral with the axis 18. At the right end of the rod

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 14, the balance 13 is linked to articulation with the coupling bar 16.



  The rocker 13 can pivot on the pivot 24 fixed to the pivot frame around which the toothed segment 25 can also turn crazy. The rocker 13 can drive the toothed segment 25 thanks to the two stops 26 of the latter. stops is calculated in such a way that the balance 13 can turn idle with respect to the segment 25 by a certain angle during the change of direction. This idle rotation is necessary for the drive member to be at rest when the recording mechanisms are coupled; coupling which takes place in a dead center, as already said. The toothed segment 25 is engaged with the pinion 27 which transmits the movement to the printing mechanism and to the totalisers.



   The displacement of the tie rods 23 and therefore that of the slide 15 is obtained from the crank 12 which has practically the shape of a ratchet wheel. The connecting rod 28 linked to articulation to the coupling bars 23 can turn by its right end on the pivot 30 fixed to the frame. The connecting rod 28 is necessary to always ensure the correct position of the tie rod 23 and therefore also of the guide.



   The progression of the ratchet wheel 12 is obtained by the pawl 29. The pawl 29 is pivotally mounted on the balance 31 (Pin 10 and 12) and is elastically pushed on the ratchet wheel 12. The balance 31 is driven. by an eccentric 33 and the eccentric bar 34. The eccentric 33 is on the same shaft as the crank 11, so that for a crank tpur '11.9 the balance 31 sorrel once. As a result, the ratchet wheel 12 is driven by a notch thanks to the pawl 29. This progression results in the offset of the slide 15 by means of the rod 17 which is mounted in articulation on the wheel. ratchet 12 and through the tie rod 23.



   The position of the elements guided in the guides 21 must be exact when the balance 13 has reached its neutral point in the position of extreme oscillation. This is necessary because - at this time the type wheel is uncoupled. As said above, this dead point also indicates the value of the location corresponding to that moment. During the rest of the time, the slide can be moved without this movement having an influence only on the positioning of the type wheel. The position of the slide has no effect on the coupling, since the crank stroke and the position of the guides 21 have been chosen so that the position of a neutral point does not depend on the movement of the slide.



   Precautions have been taken so that the forces which can intervene and tend to move the slide from the position assigned to it - which must absolutely not occur during neutral in the extreme oscillation position - do not may have any effect.



   This is why the ratchet wheel 12 is stopped at this time and blocked for both directions of rotation, so that unforeseen movements do not take place. This blocking is achieved by means of the lever 35 having a semi-circular notch 35a. The notch 35a of the lever 35 can be housed around the screw head 36 which prevents any rotation of the ratchet wheel 12 in both directions. This stop must be maintained for some time. In addition, it is desirable to have a quick release, which is achieved by a tilting joint. The arm 37 (Fig. 12) can pivot around the pin 38 fixed to the frame and it is linked by the coupling bar 39 to the balance 31. The arm 37 therefore oscillates at the same rate as the balance 31.

   On the stud 38, the lever 35 is also pivotally mounted and linked to the arm 37 by the spring 410. As a result of the oscillating movement of the arm 37, the lever 35 continuously rocks between the stop 42 and the screw 36. The rocker has was calculated so that the lever 35 meets the screw 36 when the slide and screws 36 have reached their exact position.



   In order to be able to compensate for the tolerances and the eu and to allow the exact adjustment of the strokes, provision has been made for the various screws 36 and teeth 43 of the ratchet wheel for the possibility of an individual offset. The wheel at

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 ratchet 12 is formed as a single disc to which the teeth 43 are individually secured by screws 36. The screw holes in the disc are a little larger than necessary, allowing some adjustment. To prevent the teeth 43 from turning, they internally touch a disc 44. In order to be able to equalize the differences in subdivision which may exist during assembly, there is provided for the pawl 29 a greater stroke than necessary for the normal subdivision.



   The six screws 36 and teeth 43 which are necessary for the different positions of the slide 15 have a smaller mutual distance than the other three. These last three screws were necessary to bring back the crank device, used to position the slide? to its starting position. During this time the printing and replacement of one card by another is also carried out. The distance between these three screws was taken a little larger in order to be able to carry out in three steps the course equivalent to 4 normal steps.



     The mechanism for coupling the wheels of the types will now be described.



   The oscillatory movement forward and backward of the pinion 27 fixed on the shaft 71 (Figs. 10 and 23) is transmitted by gears., In a manner which will be explained later, to the shaft 78 integrally supporting the wheels. toothed 45 (Figs. 17 and 18). The arrangement of these wheels in Figures 17 and 18 does not exactly correspond to their position in the machine; it was chosen to allow a clearer visible cut in figure 18.



  A toothed wheel 45 is assigned to each wheel of the types this toothed wheel being in engagement with the wheel 46 which is force-fitted on the ring 47. A notch 47a is provided on the ring 47; in this notch are mounted the pawl 48 and the spring 49. The pawl 48 can always be maintained, thanks to the spring 49, in one of two rest positions. The ring 47 can only rotate on the teeth of the drive wheel 51. The toothed wheel 52 is force-fitted on the drive wheel 51 and is in mesh with the toothed wheel 53. The drive wheel 51 can rotate on the drive wheel 51. 'axis 50 and toothed wheel 53 is integral with character wheel 54.



   Each ring 47 driven by its toothed wheel 45 rotates in correspondence with the value of the active perforation locations. Shortly before, if the electro coupling was excited by a perforation existing in the card, the lever 81 strikes the pawl 48 which is pressed into an interval of the teeth of the control wheel 51, driving the latter in clockwise. Through the gears 52 and 53, the type wheel is moved in a corresponding manner. The coupling by the pawl can be achieved only in a determined position to which we will come back.

   The starting position of the pawl is fixed by the crank stroke, as has already been said. The displacement of the control wheel 51 always corresponds to a multiple of the gear pitch? so that the teeth are always in a favorable position for mating.



   In the return movement of the ring 47, the type wheel 54 (and hence the toothed wheel 53) is blocked in its movement in the opposite direction, which is achieved by the spring 56 (Fig. 14). The spring 56 rests on the locking wheel 57 which is fixedly linked to the toothed wheel 58 which meshes with the toothed wheel 53. As a result, the toothed wheel 51 is also unable to turn in the opposite direction. the movement of the hands of a watch (Fig. 17). The pawl 48 is pushed by the inclined sides of the teeth towards the outside until it remains in the external position where it is held by the spring 49; it is then automatically uncoupled from the start of the backward movement.

   The ring 47 then rotates backwards until neutral is reached for the new coupling.



   In the totalizer (Fig. 19 and 20) the positioning is carried out in a manner analogous to what occurs for the type wheel. The drive is operated from the toothed wheel 58 which meshes with the wheel

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 toothed 59 is force-fitted on the ring 61 in which the notch 6a containing the pawl 62 is located. The coupling is effected by means of the lever 63. The prison 61 rotates around the control wheel 64 which does not have only 10 teeth instead of the 13 teeth of the wheel 51 of the printing mechanism The displacement by the ring 61 thanks to the drive member 58 is carried out so that the position of the toothed wheel 64 indicates the position of the totalizer and wheel 64 thus represents at the same time the totalizer wheel.



   The printing mechanism and its drive means will be described in what follows.



   The crank device is placed in the bottom of the machine so that it is easily accessible from below (Fig. 14). The cranks are driven from the motor 65 (Fig. 33), through the gears 66-67 (figo 14) and the bevel gear 68 and 69 (Fig.



    14). On the worm-shaft 112, on which the bevel gear 69 is mounted, the crank 11 is also mounted. The device is actuated while the machine is in operation. The movement produced by the crank mechanism already described is transmitted from the pinion 27 through the shaft 71 (Fig. 10 and 13) and the bevel gear 72-73 and 74.



  The bevel gear 73 (Fig. 23) is fixed with the toothed wheel 75 on the shaft 76.



  The pinion 75 is engaged with the two toothed wheels 77a and 77b which each drive a shaft 78 on which are mounted all the drive wheels, all designated by the reference 45 for all printing rows, in view of the coupling with the wheels of the types. The division of the couplings into two groups has been adopted in order to obtain a small lateral spacing of the types. As a result, we succeeded in having a spacing between printing columns of 3 mm (Fig. 21). To house the coupling electrodes, we were led to divide them into six groups. The appliances are arranged in such a way that there are always three groups of appliances which act on one of the two coupling groups. It can be seen in FIG. 17 that the position of the pawl 48 or of the ring 47 is irrelevant for the coupling.



  It is only necessary that the point of the pawl is always above any recess between the teeth of the control wheel 51 during coupling. The position of the pawl is thus only a question of mounting and arrangement. coupling levers. The position and shape of the coupling levers (Figs 14 and 22) have been chosen in this example so as to have parts as small as possible and few bearings.



  The coupling levers are pivotally mounted on the three axes 79 and directed alternately on each axis up and down. The levers 81 of the two end shafts 79 act on the same coupling group while the levers 82 of the central shaft 79 act alternately on one of the two coupling groups, The springs 83 keep the coupling levers in their position starting point. On each coupling lever acts an electro coupling Do
In order to be able to be conveniently housed, the D appliances are constructed in an unusual way., Their realization is visible in figure 16.



  This method of construction also offers the advantage that these appliances can be grouped easily eh forming an assembly mounted on a wall.



   The appliances are here fixed to the intermediate wall 85. The electro comprises a core 86 which can slide in the sleeve 87; its movement is limited by the nut 88 and the disc 89. The latter is riveted to the core 86. The sheath 87 is pulled by the nut 91 against the wall 85. Between the wall 85 and the sheath 87 the shield 92 is strongly tightened by the action of nut 91. This shielding is necessary to close the magnetic circuit of the electro. Inside the shield 92 is the coil 93 on the armature 94. There are two slots in the shield 92 through which the solder lugs 95 can protrude. The nut 88 presses on the lever 81 or 82 (Figo 14) and is pushed into the rest state by the spring 83 by means of the lever 81 against the sleeve 87.

   If the electro- is energized (in the position drawn in Fig. 16), the plate 89 is attracted

  <Desc / Clms Page number 12>

 against the shield 92. The nut 88 presses on the coupling lever which in turn pushes the pawl 48 into the bottom of the teeth of the control wheel 51. A short current pulse is sent to the electro D, because only a brief attraction is needed for mating. This allows relatively large currents to flow through the winding without the latter being destroyed by excessive heating. As a result, rather large magnetomotive forces corresponding to these relatively large currents can be obtained while this would not be the case with normal electros of marl dimension.



   The wheels of the types 54 (Fig. 14 and 21) can rotate on the axis 98. A notch 54a is provided in the wheels of the types, in which a notch is located a pawl 99. The pawl 99 can rotate on the axis 101 which is integral with the toothed wheel 53. As has already been said above, the toothed wheel 53 and the type wheel 54 are integral with one another.



  The pawl 99 is urged by the spring 102 against the pin 98. The pin 98 has a groove 98a. When the types wheel is in place, it turns clockwise and the pawl 99 slides on the axis 98. As the axis 98 is actuated by the crank system this axis turns. do in an oscillatory way in one direction and the other. The rhythm of the oscillation is chosen in such a way that it matches the exploration of the cartons. When the wheels of the types come to take their place the axis 98 turns contrary to the direction of the needles of a watch. In this movement the pawls 99 can jump over the groove 98a. After printing, the axis 98 begins to rotate clockwise.



  The pawls 99 are grasped according to the position of the type wheel by the groove 98a and are driven by it, whereby the wheels are returned to their starting position. The oscillation of axis 98 has also been chosen such that it covers just over 47/48 of a total revolution. The purpose of this is that for resetting all wheels of the offset types are driven while resetting has no effect on those not offset. We will come back to the drive of axis 98 later.



   When printing, the types must be exactly arranged along a line. This result is achieved thanks to the fact that shortly before printing the caliper 103 - Fig. 14-15- is pushed against the wheels of the types.



  In the type wheels, grooves 54b are provided in which the angle 103a of the caliper 103 which aligns the type wheels enters. Types 104 are recessed in dovetail grooves
The paper roll is placed in front of the machine (Fig. 1 and 14) and can be changed easily. The paper is led on the roller 106 between the type wheels and the ink ribbon 107, thick between the rollers 108 and 109. The roller 108 causes the paper to be drawn. Over the ink ribbon 107 is the printing hammer 111.

   The types are protected from direct contact with the ink ribbon, which has the advantage of preventing the types from getting dirty. A particular advantage of this arrangement is that the writing is readable immediately after printing.



   The work cycles for the alignment of the wheels of the types, for the printing and for the zeroing take place in the same operation, so that their movements can be obtained from the same drive. This drive is performed from the worm 112 and the tangent wheel 114 (Fig. 14). The worm 112 is located on the same shaft as the crank 11 of the crank system and as the bevel wheel 69. The transmission ratio between worm and tangent wheel was taken equal to 1/9. This is imposed by the return of the crank system to its starting position after 9 revolutions of the crank 11. The tangent wheel 114 is mounted integral with the shaft 113 which protrudes from the side wall 115 to the left (Fig.33).



   On the left end of shaft 113 is crank 116 (Fig. 33 and 13). On the crank 116 is connected the balance 118 by the intermediary of the bar 117. The balance 118 can pivot on the axis 119. The

  <Desc / Clms Page number 13>

 balance 122 is moreover linked in articulation with the lower part of the balance wheel 118 by means of the coupling bar 121. The balance 122 can rotate around the axis 123. In addition, the rack 124 is connected with articulation to the balance 118. This rack is in engagement with the pinion 125. This pinion 125 is fixed on the axis 98 which causes the resetting as has already been described above The rack 124 is prevented from falling by the roller 127. Balance wheel 122 oscillates at the same rate as balance wheel 118.

   The lever 128 can rotate around the upper articulation point of the balance 122 and is pulled by its lug 128a against the balance 122 thanks to the spring 129, this lug abutting against the balance. 'If the pendulum 122 moves to the left the lever 128 butts against the lever 131, which causes the lever 128 to swing to the right and engage behind the lever 131. If the pendulum 122 moves to the right again , the lever 128 cannot tilt because of the lug 128a and it drives the lever 131 until the latter slides over the lever 128 and suddenly returns to its starting position by the spring 132 The starting position is ensured by a rubberized pad 133 adjustable on the angle iron 130. The lever 131 is fixed on the shaft 134 as well as the printing hammer 111 (Fig.



  14). This is the rest position of the printing hammer which is shown in figure 14. This position is adjusted by the rubberized pad 133 so that the paper is easily drawn. As said, the hammer is cocked by the lever. 131. During its rapid return, the rubber stamp gives way a little under the impact, so that the marteua presses the tape; inkpad and paper on types.



   If the rocker 122 moves to the right (Fig. 13) it reaches the roller 135, which is on the lever 136. The lever 136 is integral with the shaft 137 and is pushed by the spring 138 against the stop 139. On the shaft 137 is also mounted fixed but yielding to the action of a spiral spring, the movable stirrup 103 (Figo 14) serving for the alignment of the types. In its movement, the rocker 122 moves the lever 136 towards 7, the straight line so that, as described above, the caliper is pressed against the wheels of the types and types are aligned. In addition, on the shaft 137, are mounted idle the locking wheels 57 of the wheels of the types.



   The paper drive is obtained by the roller 108 (Fig. 14) which is fixed on the shaft 141. The ratchet wheel 142 (Fig. 13) is also mounted fixed on the shaft 141. The ratchet wheel 142 rotates by the pawl 143 pivotally mounted on the balance 118 and which is pressed by the spring 144 against the ratchet wheel. The locking of the ratchet wheel is achieved by the spring 145 which is fixed to the bracket 146 and which is adjusted in exact position.



  As the balance 118 moves to the left, the pawl 143 advances the ratchet wheel 142 by one step. The size of this pitch corresponds to an interline of the printing on the paper.



   The position of the crank 116 has been chosen so that the balance 118 reaches the right neutral point once the positioning of the type wheels has just been completed. When the pendulum moves to the right, the printing hammer arms the type wheels line up and printing is done. If the rocker 118 moves to the left, the reset is performed as well as the paper feed. The return of the crank and the passage of a new card are carried out independently The pressure rollers 1t9 which press the paper against the drive rollers 108 can turn on the axis 147, which is fixed in the two levers 148. Each lever 148 can rotate on an axis 149.

   The roller 109 is pressed against the roller 108 by the lever 148, thanks to the spring 151. The spring has been arranged in such a way that by moving the lever 148 upwards, by hand, the latter can swing back and forth. back. This allows convenient placement of the paper.



   In Figure 13, there is further shown a device for easily placing and extracting the paper roll. The paper roll 105 has been pushed by its axis in the notch 152 against the action of the spring 153 until this axis rests behind the lever 154 and is held by

  <Desc / Clms Page number 14>

 this one in this position. The lever 154 is pushed by the spring 155 against the stopper 1560 If you want to remove the paper roll, you push the lever 154 to the right by hand (Fig. 13) which releases the axis of the paper roll and spring 153 sprung? the axis with the roller outward.



   The adder mechanism and its drive will be described below. The totalizers add up the partial values transmitted to them and send the result to the printing mechanism in the form of partial values.



   This is necessary because the printing mechanism can only be positioned according to partial values.
The positioning of the totalizers is obtained by a coupling similar to that of the printing mechanism as mentioned above.



  The totalizers are located on the rear of the machine (Figs. 14 and 24) in two rows each comprising 25 units. The machine can therefore work with a total of 50 totalizer units. Each group of 25 totalizing wheels is free to rotate on axes 160a or 160b. The distribution of the totalization units according to the orders of decimal units can be easily planned during the assembly. In the present case, it is carried out in such a way that the different totalizers are subdivided into groups, at the end of each of which the transfer is interrupted and for this there is provided a coupling for resetting to zero which we will come back to later.



   The driving of the two rows of totalizers is obtained from the shaft 161 on which the toothed wheels 58 are fixedly mounted. The toothed wheels 58 act directly on the upper totalizer units and through the wheel 162 on the lower totalizer units. The intermediate gear 162 is mounted idle on the axis 163. The coupling is effected by the lever 63a or 63b thanks to the electro Z as has already been said above. The uncoupling is also carried out in a known manner by rotating the drive in the opposite direction.

   Locking the totalizer to prevent it from turning in the opposite direction is achieved by the ratchet wheel 157 and the spring 170 (Fig. 24). The ratchet wheel 157 is also used simultaneously for the transfers.



   The transfer system is similar to that known on Hollerith machines. The pawl 164 can rotate freely on the lever.



  165 and is pushed by the spring 166 against the ratchet wheel 157. The lever 165 is rotatably mounted on the axle 160 and is pulled by the spring 167 in the counterclockwise direction of the clockwise movement. - be, but it is prevented from doing so by the projection 168a of the lever 168. The lever 168 is urged by the spring 169 against the lug 165a (Fig. 25) of the lever 165.



  If the totalizer wheel turns, the pawl 164 jumps as the teeth of the ratchet wheel 157 pass. On the pawl 164 is fixed a pin 171 which passes under the lever 168 of the previous totalizer unit. The teeth and the pin 171 are made in such a way that the normal teeth raise the ankle 171 only by a small amplitude, insufficient to reach the lever 168. On the ratchet wheel are outside the normal teeth. a larger tooth 157a. The position of the latter corresponds to position 9 of the totalizer. If tooth 157a goes under pawl 164, it means that the totalizer goes from 9 to 0 and the pawl 164 is lifted high enough that the pin 171 drives the lever 168 of the totalizer unit order. immediately higher.

   This last lever 168 releases the lever 165 from the corresponding order of unity which, under the action of its spring 167, turns rapidly to the left until it strikes the caliper 172. If the pawl 164 in passing touches the tooth 157a, higher than the others, it releases in the manner which has just been described, the locking of the lever 165 for the unit order close to the totalizer. Once positioning is complete, caliper 172 moves clockwise and returns levers 165, which have been released, to their starting position. The pawl 164 drives by one unit in this movement the wheel to

  <Desc / Clms Page number 15>

 ratchet 157, which ends the transfer.



   Resetting the totalizers does not need to be performed for the totalizers all together. On the contrary, this resetting, if desired, can be carried out individually for each totalizer.



  This may be necessary when the machine is to be equipped in a known way, with double group control (main group and subgroups).



  To allow this possibility, sheaths, 173 are provided on the axis 160, the length of which corresponds in each case to the length of the totalizers or to the number of unit orders of the totalizer. There is provided in the ratchet wheel 157 a notch 157b in which the spring 174 is located. This spring slides during the positioning of the totalizer on grooves which are provided in the sleeve 173. The sleeve 173 is stationary during movement. positioning of totalizers. If the totalizer is to be reset, the sleeve rotates clockwise once. Depending on the positioning of the totalizer units the springs 174 fall at different times in the groove, so that the totalizer units are driven by the sleeve and reset to zero.

   The rotation of the sleeve is effected by means of a toothed wheel (not shown) mounted integral with the sleeve 173. For each totalizer there is always such a toothed wheel provided at its end. Said toothed wheel engages with toothed wheel 175 (Fig. 24) which idles on shaft 176. Shaft 176 rotates after each positioning. A groove is provided on the shaft 176 so that the gear 175 can be connected to the shaft by a one-turn coupling. After reading the sum, the reset electro N (shown only diagrammatically in figure 43) is energized. The reset electro is in the same row of electros as those of the Z coupling and is of similar construction.

   The energization of the reset electro moves the lever 177 which releases the pawl 178. The pawl 178 is rotatably mounted on the toothed wheel 175 and is urged by the spring 179 against the shaft 176. The pawl falls into the groove of shaft 176. After reading the totalizer units, shaft 176 begins to rotate. The sleeve 173 is driven by the pawl 178 and the toothed wheel 175, which causes the reset. At the end of one revolution, the pawl 178 is released from the groove by the lever 177 which, in the meantime, has been returned to its rest position by the spring 181. At the same time, the shaft 176 is stationary. All totalizer units are reset to zero from the same tree 176.

   The continuation of the movement is obtained here by the intermediate wheel 182 which can turn on the axis 1630
The drive for resetting and transfers is obtained from the shaft 113 which executes, by card passage, one revolution.



  At its left end (Fig. 33) the chain wheel 182 is force-fitted.



  The chain wheel 182 drives through the chain 183 (Fig. 13) the chain wheel 184. The chain wheel 184 can rotate on the axis 185 and it is integral with the toothed segment 186 and the toothed wheel 187. toothed segment 186 extends over 1/3 of the periphery and it meshes with toothed wheel 188 .. The transmission ratio between; the toothed segment 186 and the toothed wheel 188 is 1/3.



  Therefore, the toothed wheel 188 makes one revolution when the segment makes one revolution, but the rotation of the toothed wheel 188 takes place for 1/3 of the time, while it remains at rest for the other two thirds. The toothed wheel 188 is fixed on the axis 176 (Figs. 14 and 24) which causes resetting as we have already said. The position of the segment 186 is chosen such that it engages with the toothed wheel 188 only when the positioning of the totalizer or its exploration is completed.



   Postponements can occur at the same time as they can occur immediately after positioning. The deferral transmission is cut off again until the exploration which takes place in the next work cycle.



  The drive to oscillate the caliper 172 can therefore be taken from the toothed wheel 188. The crank 189 (Fig. 13) is rigidly linked to the toothed wheel 188. The balance 192 is linked in articulation to the crank 189. by a connecting rod 191. The balance 192 is fixed on the axis 160a on which is also fixed the caliper 172. The oscillation must also be

  <Desc / Clms Page number 16>

 transmitted to the lower totalizer group.

   In this regard, it should be noted - that the oscillation must be carried out in the opposite direction since the lower group of totalizers is arranged symmetrically with respect to the upper groupo This is obtained by the transmission of the oscillation movement to the balance 194 by means of the tie rod 1939 which is fixed on the axis 160 corresponding to the lower group of totalizers.



  If the toothed wheel 188 or the crank 189 makes one revolution, the two rockers 192 and 194 or their calipers 172, execute a back and forth movement and return the levers 165 to their starting position. The starting position of the two balances and the toothed wheel 188 must always be established exactly. When the rotation is fast, the toothed wheel 188 should not become entangled. In addition, the toothed wheel 188 must not turn idle when it is not engaged with the toothed segment 186. This is achieved by means of the spring 195 which pulls the balance 192 in a neutral position which fixes the position of the crank 189 or the toothed wheel 188.



   The drive for the positioning of the totalizer units (or wheels) is obtained from the bevel gear 74 (Fig. 13) via the shaft 196 and the bevel gears 197 and 198.



   The exploration of the totalizer units must be carried out in such a way that the result of each unit can be composed of partial values. Another condition is that the zeros existing before the highest significant digits of a number must not be printed and, therefore, the corresponding totalizer units must not be connected to the printing mechanism. These conditions are fulfilled by the device described below.



   Each totalizer unit has four cam discs 201, 202, 203, 204 for reading the results (Fig. 25). The position of the various cam discs has been chosen so that the cams provide the partial values of the positions of the totalizers. The cam discs are integral with the toothed wheel 64 (Fig, 20) which indicates, as has been described, the positioning of the counter. In addition, the ratchet wheel 157 (Fig.



  24), which is used for locking against reverse rotation and for transfers, is fixed to toothed wheel 64. The four cam discs are sufficient to represent the figures, because, apart from the zero position, the code of the figures does not apply. 'extends over' four positions. The shape and position, with respect to each other, of the disks are shown in Figures 26 to 29. The disk 201 corresponds to position II (Fig. 3) with the partial value 1; the disk 202, at position III with the partial value 2; the disc 203, in position IV, with the partial value 4 and the disc 204 in position V with the partial value 8. Each disc is provided with a contact blade 205 which can be pushed by the cam-disc on the conductor common 206.

   Depending on the position of the totalizer, the four blades are brought into contact with the common conductor according to the adopted code (Fig. 3). All the blades 205 are fixed to the plate 208 by means of a bracket 207. Two insulating plates 209a and 209b (Fig. 24) isolate the blades from one another and from the ground. The cam discs are separated from each other by discs 211. The exploration of the position of the totalizers by the blades 205 is caused by the cams 213. The exploration of the totalizer unit is carried out by in a manner analogous to exploring a map column. As a result, it is obtained that the machine can work in a continuous and regular manner to extract the totals, and that only the supply of cards is interrupted.



   The exploration of the map is carried out as already described above in six periods. Correspondingly for the total extraction, the exploration is also divided into six periods. But, the actual exploration only relaxes from the second to the fifth position (Fig. 3).



  The first position is used only for zero and the sixth is irrelevant for digits.



   If the totalizer is to be explored, the shaft 212 (Fig. 24) will turn step by step, the size of this step has been chosen so that the shaft 212

  <Desc / Clms Page number 17>

 returns to its starting position after six steps.



   The shaft 212 has six faces on which the cam discs 213 are threaded. One of these discs 213 is provided for each blade 205. The cams are always offset with respect to each other by 1/6 of a turn.



  The blades 205 are pressed by the cams one after the other onto the contact bar 214. The contact bars 214 are provided separate for each totalizer unit and fixed to the insulating support 215. The bar 214 is connected by a connection to the corresponding coupling electro of the printing mechanism, electro on which the totalizer unit must act. The pressure of the blades on the contact bar corresponds in its succession over time to the exploration of the perforation locations of the card. But; current can then flow through the blades only when they are simultaneously pressed by the totalizer cams 201 to 204 on the common conductor 206.

   The position of the cams 213 has been chosen such that, of the six periods or not, the second, third, fourth and fifth act on the cams. The first step is empty, because in this position the 'zero is transmitted. We will come back to this point later.



  The sixth step is also empty because it is not necessary for the coding of digits. The sixth step also corresponds in this exploration to the rest position of the shaft 212.



   The drive of the shaft 212 takes place step by step thanks to the electro 216 (Figa 13). If the totalizer is to be scanned the electro 216 receives current pulses. The sequence of pulses matches the rotation of the crank .11 of the crank mechanism. We will come back to the succession in time and to the limitation of the pulses later when we describe the assembly diagram. Electro 216 attracts its armature 217 with each pulse. The armature 217 is returned to its rest position by the spring 218. The pawl 219 can turn on the armature 217 and is pushed there by the spring 221 against the control wheel. control 222. Each time the electro 216 is energized, the control wheel 222 advances by one step. The control wheel 222 can turn on the pivot 223 and is integral with the toothed wheel 224.

   This wheel 224 is engaged with the toothed wheel 225 and, through the intermediary of the wheel 226, with the toothed wheel 2270 The toothed wheel 227 is fixed on the shaft 212a of the upper totalizer group while the toothed wheel 225 is fixed on the shaft 212b. The transmission ratio between wheels is 1/1.



   The condition was stated above that the printing of zeros in front of the highest significant digit of a number should be suppressed.



  This result is achieved by a particular assembly of the contacts. (Fig. 30) Fig. 30 shows only schematically the elements used for the suppression of zeros. Other elements which are in fact in the circuit, but which have other roles, are left aside and will be described later when describing the general diagram. Each totalizer unit is assigned a set of contacts generally designated by bIV.



  This comprises four contact blades of which the two upper blades (Fig. 24) touch each other in the relaxed state. In the zero position of the totalizer wheel the longer contact blade is pressed down, causing the three blades below the upper blade to make an electrical connection and the contact through the upper blade is interrupted ( Fig. 27). The actuation of these contacts is controlled by the cams 211a on the intermediate disc 211. The position of the cams is chosen so that the set of contacts bIV is actuated for the “zero” position of the totalizer. If the totalizer wheel is moved out of the "zero" position, the described reversal of the contacts follows.



   In figure 30 the exponent in Arabic numerals of the coupling electrodes D and the bIV contacts indicates to which totalizer unit they are assigned. In doing so, we assume that the rank of the units is designated by the exponent 1 and the following ranks by the exponents 2, 3, 4, 5. If we admit, for example, that the number 3050 must be explored in the totalizer, contacts bIV2 and bIV4 are reversed; their positions are shown on

  <Desc / Clms Page number 18>

 
 EMI18.1
 FIG. 3g the row of tens (corresponding to b IV2) and the row of thousand (corresponding to bIV4) being those where the totalizer wheels are offset.



  The zero position of the printing mechanism therefore takes place for the row of totalizer not shifted within the number as follows:
 EMI18.2
 zero "coupling is carried out on the electro-coupling of the printing mechanism via contacts W'IV.I1 bv4.11 bq3, for electro-coupling D and by contacts wIV.I1 b-y2p brvI.9 for 19 coupling electro I3 The assembly is therefore established in such a way that when the crank mechanism is placed on value 1 (in the part of the printing mechanism) or on
 EMI18.3
 replacement 1.1) a current pulse passes through rl and D3 and D- are excited.l1 so that the totalizer wheels assigned to these appliances are positioned on "zero".



   Current cannot flow through D5 and the coupling electrodes of higher totalizer rows because contact bIV4 has interrupted the connection in this direction o It cannot flow current through D4 and D2, because for these electrodes , the link is interrupted at contacts bIV4 and bIV2 (which have been inverted by their corresponding totalizer unit).



   The positioning of the digits 3 and 5 is then carried out for the following positions of the crank mechanism in the manner which has already been described above.



   The card is driven by the two chains 227 (fig. 14 and 33). The card is pushed in a known manner by the knives 228 which extract it from the magazine 229. The two knives 228 are mounted on a slide 231 which is guided on the two rods 232. The movement of the slide 231 is obtained by means of a crank. . The crank 233 is integral with the chain wheel 234 mounted on the shaft 2350 The dimensions of the chain wheel have been calculated so that a complete rotation of the chain wheel
 EMI18.4
 corresponds to the routing of a carteo The tie rod 236 is connected by the connecting rod 237 to the crank 233.

   The coupling bar is connected by its upper end to the slide 231 and by its lower end to the beam 238. The balance 238 is pivotally fixed by its left end (Figo 33) on the square 239. On the shaft 235 are also fixed the two rollers 241 (figo13) On these press two rollers 242 (Figo 33) which are mounted to pivot on the arms 243. Likewise the said arms 243 are mounted to pivot on the brackets 244 .

   The arms 243 and the gates 242 are pressed by the springs 245 down
The card is pushed by the knives 228 between the rollers 241 and the rollers 242 and is driven by them. The pressure of the rollers 242 has been established in such a way that for a determined resistance
 EMI18.5
 of the card the rollers 24à begin to slide in relation to the card.



  The diameter of the rollers 21, 1 is somewhat larger. than that of the pitch circle of the chain wheel, so that the drive by the rollers is a little faster than by the chain If the card is gripped by the rollers
 EMI18.6
 241 and the rollers 21 * 29 it circulates faster than the chains until it strikes by its front edge the projections 227a of the two chains 227. In this way any biasing engagement of the card is compensated from the start. As soon as the end of the card leaves reels 241, the
 EMI18.7
 subsequent protrusions 227a assume 1-interlacing. The area between two protrusions is exactly equal to a board height.

   The chain only has the load of driving the card o The card rests on track 246 which serves simultaneously to guide the chain (Fig. 14 and 33) The card is guided laterally by the two guides 250 fixed to the side walls of the
 EMI18.8
 machine. This reinforces at the same time the support of the card extraction and exploration devices. The card first arrives under the first bump 247 (Fig-31) which serves only for group control.

   Then the card goes under the
 EMI18.9
 second brush 248 which has the role of the actual exploration (Figs 14-31 and 33). Both brushes are of similar construction and are supported

  <Desc / Clms Page number 19>

 by the two supports 2490 The brush 247 includes twice 30 'brushes 251 because the two' stages of the card must be explored simultaneously. The brushes are supported by the plates 252 and guided separately in the combs 253. The brushes 251 are pressed against the contact plate 254 fixed by means of insulating plates 255 on bars 256. The bars 256 are fixed on the guides 250 at the same time as the combs 253 (Figo 33).



   For each brush there are provided rollers 257 and 258 serving as auxiliary drive means, these rollers driving the card under the brushes. The rollers must have the same speed as the chain. But since the rollers have a larger diameter than the pitch diameter of the card wheel, the drive rollers have to turn more slowly which is achieved by a gear transmission. o The rollers are mounted to be able to rotate on the axes 259 or 261. The axis 261 is linked fixed with a chain wheel 262 (Fig. 14), the axis 259 is driven by the chain. Furthermore, the toothed wheel 263 is integral with the chain wheel 262 and the toothed wheel 264 is linked to the rollers.

   The toothed wheel 264 is driven by the toothed wheel 263 by means of a gear comprising the toothed wheels 265 and 2660 The axes 259 and 261 (Figo 31) as well as the intermediate gears are mounted in ', the brackets 260 (Figs 14 and 33) The transmission has been calculated so that the driving speed of the rollers is equal to that of the chain. The card is pushed by the rollers 267-268 on the rollers 257- 258. The rollers are fixed on the pins 269 and 271 which can rotate in the supports 2490 The supports 249 can 8 = -Also pivot in the brackets 272, these being screwed onto the guides 250 (Figo 33). The springs 273 push the supports or brushes and the rollers back down.



   Cards are transported more quickly during card change to reduce the empty stroke of the machine. To be able to perform this rapid training without disturbances, the brushes are raised, which is achieved by tilting the supports 249 upwards (Fig. 32). On the shaft 261 is, fixed the cam-disc 274. The shaft 261 performs one revolution, during a progression of the chain equal to the advance of a card, since the chain wheel 262 is fixed on said. tree. The disc-cam is adapted in its form to the succession in time of the explorations of a map. The cam disc 274 can lift the lever 2750 This is fixed on the shaft 276 ;, as can the levers 277.

   Levers 277 engage under rod 271 and push up brackets 249. Shaft 276 is mounted in brackets 278 which are screwed to side wall 2790 The shape of the cam has been chosen as such. so that the lever 275 is lifted when a card is replaced by another or when the exploration is finished;
The movement of the chain or the drive of the cards is carried out step by step. The step-by-step advance has been designed in such a way that the board moves slowly during exploration and that the boards are replaced quickly. The rhythm of the card training matches that of the crank device. It is subdivided into 6 working steps and three empty steps.

   It can be obtained from the same drive as that of the crank device.



   The drive of the card drive member is performed from the toothed wheel 67 which also serves as a crank. The balance 281 (Fig. 33) is connected by the coupling bar 282 to the crank. The balancer 281 is pivotally mounted on the axle 283 which is screwed into the bracket 260. The pawls 284 and 285 are mounted to be able to rotate on the balancer 281 and they operate the ratchet wheels 286 and 287. which are both fixed on shaft 261 (Fig. 34-35). The teeth on the ratchet wheels are not distributed over the entire periphery. They are distributed so that a pawl replaces the cavity in its function.

   The oliquet 284 and the corresponding wheel 286 serve for the rapid transport for the passage of the cards. The pawl 285 and the corresponding wheel 287 assume the slow drive during the exploration. While one pawl is working, the other slides over the part of the periphery of the wheel on which there is no tooth. Through

  <Desc / Clms Page number 20>

 As a result of the fast transport, the pawl 284 has a larger stroke and the ratchet wheel 286 has a larger tooth spacing while the pawl 285, as a result of the slower drive has a smaller stroke and the wheel 287 smaller tooth spacing.

   The difference in the strokes is achieved by the fact that the pawls mounted on the balance 281 have different lever arms. The exact positioning as well as the locking preventing reverse rotation is achieved by the locking wheel 288 and the locking blade 289 (Fig. 36). The drive wheel 288 is also fixed on the shaft 261. The blade 289 is screwed to the side wall 279 and is adjustable through oblong holes so that the position of the card can be exactly fixed. The teeth i.e. the intervals between teeth have been set on the locking wheel 288 so as to be distributed in correspondence with the advance of the pawls. A stopper 291 (Fig.



  34) has been designed to prevent blade kickback during rapid training; this stop 291 has been screwed with the blade 289 on the wall 279 and it is also adjustable by means of oblong holes.



   If one wants to extract the sum or if the group control is energized, the card training must stop. It is then possible that the group control is already energized when exploring the first perforation location. But card training should not stop immediately, the card should be explored to the end. This is achieved by lifting the fast drive pawl 284 so that it does not engage with the wheel 286. The exploration pawl 285, however, causes the dragging until the exploration is complete.



   The lifting of the pawl 284 is obtained by means of the lug 292a of the armature 292. The armature 292 is attracted by the electro K. The armature is brought back and maintained in this rest position by the spring 294.



  This rest position is fixed by the stop 295. The electro K is fixed by its bracket 296 to the intermediate wall 97 (Fig. 14); this electro is however not drawn in figure 14 to make it clearer. If the group control relay G (which will be discussed later when describing the connection diagram) is energized, this closes the circuit of the electro K which lifts the pawl 284 by the armature 292. Nevertheless ;, the movement continues with the pawl 285 until the exchange of their functions. If the armature 292 falls back, the pawl 284 falls on the corresponding wheel 286 and still drives the same pi.



   When the exploration of a card is finished, it is dragged by the rollers 258 into the receiving box 297 thanks to the card path 298. The card path is guided by rollers 299 along the wall. 301 and it is pushed upwards by the springs 302. If the card path reaches the low position it opens the contact ma which disconnects the machine. The machine connections table will be described below.



   In the exemplary embodiment described, it is possible to connect the exploration brushes, the type wheels and the totalisers at will. In addition, group control relays can be connected to each column of the card. The connection mode is obvious and the way to operate very simple. For this purpose9 cordless plugs which are known in the telecommunications art have been used.



   Each element of the assembly that must be selected, such as for example brushes, totalizers, etc., is assigned to a bar. These bars are arranged with respect to one another in such a way that they cross those of the elements with which they must be joined electrically. The crossing bars are at different heights.



  Wherever there is a cross, there is a hole in the bars. By means of plugs, the connection between the bars can be established by inserting the plugs at the corresponding crossing point.



   In Figure 37, there is schematically shown the distribution in the different groups and Figure 38 'indicates the stacking of groups.



  In zone D of the bars, the electrical coupling of the printing mechanisms

  <Desc / Clms Page number 21>

 mants are connected, in the area bII are connected the brooms of the brush 248 and in the area bI the brooms of the brush 247. The layers bI and bII are arranged Si'one above the other as seen on Figure 38. The - two layers for the two group control relay connections are in the GI and GII zone. 6 group control relays are provided for this machine. The coupling relays for the totalizer units as well as the scanning device for the positioning of the totalizers are located in the areas of the Z and bIII bars.



   The practical layout of the connection board can be seen in Figures 39 to 41. Figure 39 shows the table of plugs in area D x bII; FIG. 40 shows the arrangement of the various stacks seen in plan.



  In FIG. 41 we see the stacking of the zone D x Z / bIII and in FIG. 42 the stacking GI / GII x bI / bII. the stacking of the bars is carried out between the -L-L insulating plates 305.



   In zone D x bII, at each crossing, there are only two bars one above the other so that at this point a single 306 card is sufficient. In zone GI / GIIxbI / bII, we obtain the connection of two groups, namely: 1 - of bI on GI and, 2 - of bII on GII of the group control relay. The double plug 307 is then necessary, the plug of which the two connection points are insulated from one another. In the zone D x Z / bIII, a connection of D x Z and D x bIII can be obtained as desired; For the first connection it is sufficient to use the short plug 306, while for the second one must use a plug 308. This is insulated at its upper part so that there can be no contact. by Z.



   With this method of cordless plugs, it is possible to combine several assembly elements with each other or to put them in parallel by connecting several bars on one single plug. But it is not useful here to dwell on the multiplicity of combinations and possibilities of use, because these depend on the problems which may be posed to the machine. The connection board (Figs. 14 and 33), generally designated 304, is easily accessible on the machine and is protected by cover 309.



   The machine connection diagram will be described below.



  In the representation of the diagram of the tabulating machine, a simplified form has been chosen which is customary in telecommunications technology.



  Since there are several similar elements, such as the electric coupling or the brushes, only one of these elements has been shown on the diagram, the others being only indicated by the repair connections. - titi on .. The number of units is provided by the Arabic numeral as a subscript.



  The relays and appliances are designated by capital letters, and "the contacts which they actuate by the corresponding lowercase letters. The contacts actuated by hand are shown schematically by a hook in the shape of a key at the upper end of the switch. 1-movable contact device In general terms, in the reference indications, these lie to the right of the corresponding electros, relays and contacts or on the diagram symbol, provided that the diagram is not legible. The position of the contacts is shown for the idle state of the machine.



   The connection diagram is shown in figure 43. To make it easier to read, the relay or cam diagram is also shown in figure 44. This diagram gives the energization or closing times of the relays or contacts as a function of the switching cycle. machine work for the example described here such as ;? after the passage of a card, a total extraction cycle follows, then after this, the first card of a new group. As a unit of work cycle, we have chosen a revolution of the crank 11 of the crank device. This unit is the exploration of a single row of hole punch locations on the card. So

  <Desc / Clms Page number 22>

 that we indicated previously there are in a cycle of cards 9 'of these units therefore 9 cycles of work.

   If the machine switch is turned off the machine does not yet start to run. It is only when the start button is depressed that the motor M receives current from this button and the magazine contact m.a. The motor begins to turn and brings cards to the brushes At the same time, the motor begins to rotate the cam discs acting on the cam contacts w (Figo 13, 45 to 47) But these have no effect as long as the well-known card lever is not reached by the cards As the arrangement of the card lever contacts is known per se, it does not appear on the offset to make them clearer.

   When the first card reaches the second brush 248 FIG. 31, the card lever assigned to this brush is actuated and closes its two contacts ka- and kaII. If these are closed, the actuation button can be abandoned. your cam contacts are generally designated by w and different from each other by their indices in Roman numerals.



  The movement of their cams can therefore derive from toothed wheel 187 (Figo 13) which makes one revolution per card cycle. The cams are mounted on the shaft 312 and rigidly linked to the toothed wheel 311 being in engagement with the toothed wheel 187. The contacts w are fixed on a caliper 3130 For the various contacts wI to wV, 3 different cams are provided which are visible in figure 45 to 47. The duration of actuation of the contacts in relation to the cycle of the cards can be seen on the relay diagram. In addition, a pulse contact i (Fig. 10) is provided which is actuated by the cam 11a located on the crank 11 of the crank device. This contact supplies the pulses to the electros Z and D.

   The position of cam lla has been chosen so that contact i always supplies an impulse to the coupling electrodes at the moment when the crank mechanism has reached neutral point during which the coupling takes place. as indicated above.



  At the start of the exploration (work cycle 1, Fig. 44) the contacts wI and i are reversed. \! so that the current can flow from at least the contacts kaII, ma, kaI, wI, i, hI, the brushes bII, the connection board represented symbolically by a dotted circle and the electro D, up to the pluso According to the perforations existing in the card, the D appliances are energized and coupling the wheels of the types.

   At the same time, the current can flow through bII, the connection board, the contact gI 'through 1-the left winding of the group control relay G, up to the plus If the group number of the following card matches that which has just been explored, a current flows from contact hI through the first brush bI, contact gII, the connection board and the right-hand winding of relay G, up to plus. The group control relay G is made up of a differential relay and does not energize when it receives current on its two windings.



   Before moving to the next perforation location, contact i has returned to its rest position. The board is advanced, reversed, and the circuits just described are closed again corresponding to the perforations in the columns of the next perforation location. By exploring location II, the contact wIII is closed by its cam, so that the coupling impulse can then also pass through the coupling electrodes Z of the totalizers. As the group numbers cannot of course be added together, these are brushes which are connected to the upright columns and consequently to the printing mechanism and the totalisers, but not to the group control. The process is repeated, contact WIII remaining closed until the position, V included.

   By exploring position VI, WIII is again inverted and does not allow pulses to pass through the electros of the totalizers, which was also prohibited in position I. After exploring position VI; the cam contact w returns to its rest position so that in the following three empty cycles, when switching from one card to another, the circuit going to the D, Z and G appliances remains cut. While exploring the next map

  <Desc / Clms Page number 23>

 the same phenomena are repeated.



   If the group number of the next card does not match the previous card, one of the bI or bII brushes has its circuit cut off by the card.



  A current then circulates in one of the windings of the differential relay G so that the latter is excited and actuates a dense contacts gI to gIV, contacts whose role is specified below. The contact gI is reversed. As a result, a current flows from at least through contacts kaII, ma, gI through the left winding of relay G, up to plus. At the same time, the gII contact is reversed but no current can flow through the right-hand winding because the circuit is interrupted by the wII contact. The group control relay G therefore remains energized even if the card. is advanced.



  In addition, the gIII contacts have closed the circuit of the uncoupling electro K which is energized and interrupts the drive of the cards, But the card stops only at the end of the exploration, what has already been described above.



   The exploration of the electro K resulted in the closure of its contact k. If contact wI returns to its rest position at the end of scanning a map, \) the circuit passing through auxiliary relay H is closed; this relay energizes and activates its hI to hIV contacts. Relay H prepares, thanks to this contacta, the extraction of the total from the machine.



  At the start of the cycle of the following cards, used for the exploration of the totalizer and during which the advance of the cards stops and the exploration of the cards is disconnected from the voltage supply by the contact hI, the contact wI is inverted again. Relay H does not de-energize, because a holding circuit passes through contact hIV. Contact hi has in fact disconnected the bI and bII brushes, but it has connected bIII and bIV used to explore the totalisers. The contact bIV serves for this purpose., As has already been said., For the suppression of the printing of the zeros in front of the highest significant digit. The exploration of the totalizer by the blades 205 has been indicated in a general way to make the matter clearer, by the contact bIII.

   When the crank device is positioned on position I, the contacts w, i, hI, are reversed and the contact wIV is closed, so that in the case where the bIV contact is reversed the pulse for "zero" has been taken to electros D of the mechanism printing subsequent totalizer units ,? what has already been described above. In the changeover to the following perforation replacement, the contact wIV has been reversed again in the meantime so that the voltage pulse now passes through the contacts hI, bIII, the connection board and the electro D up to more.



  No current can flow through the Z electro since this circuit is interrupted by the hII contact.



   The step-by-step advance for exploring the totalisers is obtained by electro A. It receives its impulses through contact i and contact closed hIII. At the start of the exploration of the totalizer the wV cam contact closes so that a current can flow from at least kaII, ma, hIV, wV, gIV, through the reset electro N, to more.

   This electro gets excited and triggers the one-turn clutch for resetting o As already described above ,? however, resetting only occurs once the exploration of the totalizers is completed.
If the exploration of the totalizer is finished, \! the contacts wI and wV return to their rest position, which means that the circuit passing through the reset electrodes N and the electros A is interrupted and they de-energize. Shortly after, \) the contact wII closes so that a

  <Desc / Clms Page number 24>

 current flows through contacts hIV, wII, gII; - the right-hand winding of the differential relay G, up to the maximum.

   The two windings of the differential relay are then traversed by a current so that the relay is de-energized and the contacts g return to their rest position. As a result, the circuit passing through the electro-coupling K and the contact gIII is interrupted so that this relay de-energizes and cuts, by its contact k, the circuit passing through the auxiliary relay H which also de-energizes and which at new prepares the machine by its contacts h, for the exploration of the following map o
If the receiving magazine is full of cards, the carriage 298 opens the contact ma, which causes all circuit passing through the machine to be cut off and the machine to stop. The same is true when there are no more trained cards and the card lever returns to its rest position, the two contacts kaI and kaII being open.



   For the subtraction, the principle of the addition can be used as well as for the addition, thanks to the addition of the complement. As it is only necessary for this purpose to use known means in association with the devices which have been described above, it is not necessary to describe in all its details the operation of the subtraction.



   We know that a number can be subtracted by adding the complement. Most of the tabulating machines in use today work on this principle. It is only necessary, in the application of the present invention to the subtraction to choose a code of perforations in which the non-perforated locations always represent the nine complement of the perforated locations of a cipher As the mode of operation according to the invention can be obtained with any additive perforation code and, if it is necessary, that the totalizing mechanism can be actuated by means of its own crank mechanism according to a law other than that of the printing mechanism, it does not There is no difficulty in adapting the invention to the useful perforation code.

   The device for exploring the positions of the totalisers must however be adapted to the values of the codes of the hangers so that it acts on the printing mechanism. If in the chosen and appropriate perforation code, it is the perforated positions (for positive uprights) or those not perforated (for negative uprights) which are used for the control (which is possible by operating with a working or quiescent current. ) the complementary value is added for a negative amount.



   The choice of the transfer of the true value or complementary value is determined by a pilot hole characterizing the value as negative. In a known manner, it is possible to obtain the introduction of the additional value 1 as well as the determination of the positive or negative sign of the balance.
From the above, it follows in any case that the subtraction by complementary value, which is in reality an addition, can also be carried out with the aid of the invention.


    

Claims (1)

ABSTRACT. 1. Card recording machine in which each of the marks provided in one of the locations of the card column or signs exerts a control action on the recording unit assigned to the column, the amplitude of which always corresponds to the values assigned to the locations., the machine being such that a drive member common to all the marked locations and performing an oscillating movement is provided for the recording unit which can be coupled to it, member which runs a course which varies automatically in successive exploration of the different locations in accordance with the values assigned to the locations. Said machine may also be characterized by the following points taken individually or in combination; 2. The coupling of the recording mechanism (for example, <Desc / Clms Page number 25> printing or totalizer) with the drive member is performed., as well as the uncoupling independently of the variable amplitude of the drive stroke, at one of the two points of reversal of the back and forth movement drive while the drive speed is zero. 3. The variation of the stroke of the drive members (balancers, pawls, etc.) is obtained from a stroke offset device (crank device) common to the drive members of all the drives. recording units. 4. A said reversal point always occupies the same position regardless of the positioning of the stroke offset device, position in which the coupling of the recording units to the drive member takes place, The drive member moves momentarily off-load with respect to its drive at the reversal point so that an increase in the duration of the stoppage is obtained at this point. 6. The change of the stroke during the successive exploration of the mark locations is carried out by moving a slide on a crank rod, one end of which is linked to an oscillating drive member common to all. the units via a tie rod and the other end of which is connected to a continuously rotating crank. 7. The movement of the slide is also obtained by a crank mechanism which is actuated in steps, the crank of which makes one revolution for a map exploration. 8. The crank device is stopped in the position corresponding to the mark locations explored at this time by means of a pawl which prevents rotation in both directions. 9. The teeth of the crank formed as a ratchet wheel are movable within certain limits, allowing exact adjustment of the position and compensation for manufacturing tolerances of the crank device. 10. By using 6 locations of marks in a column of cards, the variation of the course is carried out in the ratios: 1, 2, 4, 8, 16, 16. 11. The drive member of each recording unit is constituted by a pawl-holder swinging more or less far when exploring the mark locations from its rest position, which pendulum can be coupled by a ratchet with the recording member by means of a ratchet wheel acting only in the direction of positioning, while the ratchet wheel blocked so as not to rotate in the opposite direction. causes disconnection when the pawl moves in the opposite direction. 12. The coupling pawl is mounted on a ring rotatable on the ratchet wheel and this pawl can be pushed into the ratchet wheel by an electro coupling and held by a stopper so that it drives the wheel to the ratchet. pawls coupled to the recording unit during oscillation of said ring. 13. The electro coupling has a movable core linked to a disc which is attracted against the shield, during the energization of the electro and which transmits the movement through the core and by the armature thereof. on the coupling pawl. 4 ' 14. The extension of the stopping time at the reversal points is obtained by a coupling with stops operating with play in both directions. 15. A single movement device common to the recording mechanism and the totalizing mechanism is provided for the advance. <Desc / Clms Page number 26> 16. The same advance is transmitted to the recording mechanism and to the totalizing mechanism with different transmission carryovers. 17. The exploration of the positions of the totalizers as well as the subsequent transmission of the positions of the totalizers to the printing mechanism is carried out according to the same combinations of partial values as for the transmission of digital data from the card to the printing mechanism. 18. The totalizer units are provided with cam disks and are explored electrically and successively in correspondence with the shift device. 19. To drive the totalizers, the positions assigned to the values corresponding to the different locations are in the ratios 0, 1, 2, 4, 8, the value "O" being obtained by interrupting the coupling circuit by a contact. cam and the values 1, 2, 4, 8, by a different gear transmission than that of the printing mechanism, so that the "0" is transferred in the printing mechanism as a unit, but not in the totalizers. 20. A totalizer unit located out of the "0" position supplies the printing mechanism., When the total is extracted through a contact, a current pulse for the value "0" passing through. by lower totalizer units, but it closes itself to pulses from a higher order totalizer unit.