US2750111A - Multiplying machines - Google Patents

Description

June 12, 1956 M. MAUL MULTIPLYING MACHINES l3 Sheets-Sheet 1 Filed Feb. 20, 1953 Fig. I

Inventor? Michael Maul Arr! June 12, 1956 M. MAUL I 2,750,111

MULTIPLYING MACHINES Filed Feb. 20, 1953 15 Sheets-Sheet 2 Fig.3 Fig.4

Inventor:

Michael Maul June 12, 1956 M. MAUL MULTIPLYING MACHINES l5 Sheets-Sheet 3 Filed Feb. 20, 1953 m N N 8 3 Mm Q I NM I um mm mm Inventor: Michael Maul June 12, 1956 M. MAUL MULTIPLYING MACHINES 13 Sheets-Sheet 4 Filed Feb. 20, 1953 3N mwN NwN m2 QNN NNN EN MN NNN MN mNN qNN mmN mNN N 2 m2 NNN qwN :N g @NN Inventor:

Michael Maul June 12, 1956 M. MAUL MULTIPLYING MACHINES l3 Sheets-Sheet 5 Filed Feb. 20, 1953 Nam ohm NMN 4 .Dwemon M/cha el Maul RN .mMN RNN QNN June 12, 1956 M. MAUL MULTIPLYING MACHINES Filed Feb. 20, 1953 2L9 I33 252 I33 I 137/ 131 L20 134 I I f I/ k M 13 Sheets-Sheet 6 Fig.12

,225 223 /22 /226 ,195 247 -2w W? M -237 jm eman' Michael Maul June 12, 1956 M. MAUL 2,750,111

MULTIPLYING MACHINES Filed Feb. 20, 195:: 13 Sheets-Sheet '7 r 1,185 177 m 176 207 215 q, 18 131 175 1 183 g- I 236 185 173 194 I65 166 214 s Z 1 v M 11/1111. I'll) lIlIII/IIIIIIIIIIIIJ "my 154 '57 us I63 125 155 Inventor Michael Maul June 12, 1956 M, MAUL 2,750,111

MULTIPLYING MACHINES Filed Feb. 20, 1955 13 Sheets-Sheet 8 June 12, 1956 Filed Feb. 20, 1953 Fig.2!

MULTIPLYING MACHINES l3 Sheets-Sheet 9 III/Ill A [ll// All ll/l/ll/ jm/entarz' Michael Maul June 12, 1956 M. MAUL MULTIPLYING MACHINES l3 Sheets-Sheet 10 Filed Feb. 20, 1953 Inventor: Michael Maul June 12, 1956 Filed Feb. 20, 1953 M. MAUL 2,750,111

MULTIPLYING MACHINES l3 Sheets-Sheet l1 Fig.28a

Fig.29a

fm/eman' Michael Maul ATTX June 12, 1956 MAUL 2,750,111

MULTIPLYING MACHINES Filed Feb. 20, 1953 15 Sheets-Sheet l2 Fig.

Fig. 29b

Inventor Michael Maul June l2, 1956 M. MAUL MULTIPLYING MACHINES l3 Sheets-Sheet 13 Filed FeS. 20, 1953 Fig. 30

fnvemon' M ichael Maul ,cand is repeatedly added as end and product device.

United States Patent Oflice 2,750,111 Patented June 12, 1956 MULTIPLYING MACHINES Michael Maul, Schwabach, near Numberg, Germany Application February 20, 1953, Serial No. 338,070 Claims priority, application Germany March 4, 1952 21 Claims. (Cl. 23561.6)

This invention relates to multiplying machines and more particularly pertains to improvements therein resulting in a simplified, yet fully efiicient and effective, machine.

In multiplying machines operating on the basis of the decimal system the simplest method of multiplication is that of repeated addition. In this method, the multiplimany times as is indicated by the digit of a multiplier denomination. Such addition is repeated for all multiplier denominations under consideration of the necessary column shifting between multipli- This method permits a very simple construction of the machine since in fact the machine acts essentially as an adding machine. However, a comparatively slow operating speed is inherent in such a system due to the numerous adding operations necessary.

In order to reduce the multiplying time, it has been proposed to use multiplication devices which immediately form partial products. In machines of this type, the digit of a decimal denomination of the multiplier is simultaneously multiplied by all decimal denominations of the multiplicand and the product thus obtained, usually referred to as a partial product, is entered into the product device. Thereafter, the same operation takes place for the next decimal denomination under consideration of the above mentioned column shifting between the product device accumulating all partial products and the multiplicand. The faster operation of this second mentioned method must, however, be purchased at the price of a more complicated construction, which chiefly is due to the multiplying device.

Further suggestions have already been made to compose the digit of the factors expressed in the decimal system according to a predetermined code in component values the additive sum of which corresponds to the respective digit, and to form so called sub-products by the multiplication of the component values. Thus, in each instance, all multiplicand denominations are multiplied by each component value of a multiplier denomination by means of a multiplying device. The machine according to this known suggestion needs, however, a special multiplying device for each sub-product and moreover the same device must be provided separately for each multiplicand denomination.

One object of the present invention is to provide a machine which operates faster than those according to the principle of the repeated addition, which, however, is of more simple construction than the machines according to the above mentioned second and third methods. This is obtained by means of a unitary sub-product device adapted to multiply any two components, represented in retaining means, by each other to form an individual sub product, means being provided for controlling said sub-' product device for the successive individual multiplication of each component of the multiplier digit by all components of the multiplicand digit through said sub-product device by entering different components thereinto, and sub-product accumulating means being provided in which said sub-products are entered successively as they are formed. Thereupon in a manner known per se after multiplication of a multiplier denomination the column shifting between multiplicand and product device takes place in accordance with the successive multiplication by the various multiplier denominations.

As has been mentioned above, in the known suggestion working with sub-products, not only separate sub-product devices are used for each sub-product but these devices are also separately necessary for each denomination of the multiplicand. Accordingly, it is another object of the invention to provide means whereby the component multiplication device may not only be common to all subproducts but also to all decimal denominations of the multiplicand.

It is another object of the present invention to provide a multiplying machine which efficiently combines the advantages of the above mentioned known methods of multiplication and at the same time avoids their disadvantages. In any event, the invention permits an extraordinarily simple multiplying device.

Still another object of the instant invention resides in the selection of such component values, the highest sub product of which does not become higher than 9. In this instance, a single accumulator device with the conventional tens transfer can be used in contrast to conventional devices in which products are formed being higher than 10 and which therefore require separate accumulators for entering of the units and tens values.

Preferably, each digit is represented by component values which may be formed by single components or by combinations of the components 1, 2, 3, 3. In this instance, all digits from 1 to 9 may be represented additively by the component values and the highest sub-product is not higher than 9. The sub-products are then 1, 2, 3, 4, 6 and 9. However, the component values 1, 2, 2, 2, 2 may also be chosen in which instance, however, a greater number of settings for the component values is required which is still smaller than the number of sub-products in the above mentioned component selection. Consequently, the less different component values are necessary to represent a digit, the less different sub-products are required to be represented by the multiplying device. In this way, the number of the operating cycles is, however, increasing and thereby more time is required for the multiplication.

The invention may be carried out in various manners. A preferred embodiment, as described in the following, possesses, however, a number of features which are emphasized in the specification and in the claims. One of the most essential features is the application of a specially constructed and controlled crank drive acting as a multiplying device.

For the scope of the invention, it is also immaterial how the entering of the factors and the manifestation of the product is effected. In the embodiment hereinafter described, the entering of the factors takes place under perforated record card control and the manifestation of the product by punching the controlling record card. The illustrated embodiment would therefore belong to the group of the punched card controlled so called multiplying punches. The storing of the factors is therein efiected in storing devices and product punching under the control of the product accumulator. It is, however, obvious that the perforated record card control may equally well be replaced by a key control or that the entering of the factors can be etfected in any other way, and it is also evident that the manifestation of the product instead of being effected by punching is possibly carried out by printing or by any other conventional method.

A preferred embodiment of the invention is illustrated in the accompanying drawings:

Fig. 1 shows a perforated record card which for reasons of simplicity, is only punched in the middle deck with two factors and the product of the same.

Fig. 2 shows a perspective illustration of the multiplying punch.

Fig. 3 shows the component value code according to which the machine operates and in accordance with which the card is punched.

Fig. 4 shows the principle of the division of the multiplication in component values and sub-products.

Figs. 5 and 6 show diagrammatically two embodiments of the crank drive which can be set to different actuating strokes by two variables.

Fig. 7 shows diagrammatically the crank drive as employed in the embodiment illustrated in the drawings.

Fig. 8 shows a view of the machine from the bottom, the cover being removed, from which view the arrangement of the crank drive may be seen.

Fig. 9 shows a section according to sectional line 9-9 of Fig. 8.

Fig. 10 shows a longitudinal section of the machine.

Fig. 11 shows the front view of the machine with the cover removed.

Fig. 12 shows a section across the machine.

Fig. 13 shows a section according to sectional line 1313 of Fig. 8, from which the arrangement of ratio gears of the sub-product device may be seen.

' Fig. 14 shows a detail of the gears.

Fig. 15 shows a view of the machine from the right hand side with the cover removed.

Fig. 16 shows a section through the control for zero- 12mg.

Fig. 17 shows a section according to sectional line 17 17 of Fig. 16.

Fig. 18 shows a view of the machine from the left side with the cover removed.

Fig. 19 shows the wiring of the column shift operation device.

Fig. 20 shows a circuit diagram from which can be seen the suppression of the zero-perforation above the highest significant denomination of the product accumu lator.

Fig. 21 shows a detail from which more particularly may be seen the construction of the accumulator.

Figs. 22 and 23 show the clutch system for the accumulator adjustment.

Figs. 24 to 27 show the arrangement of the cams for the analysis of the accumulator denominations.

Figs, 28:; and b which are to be put side, by side illustrate the circuit diagram of the machine.

Figs. 29a and 2911 which are also to be put side by side show the relay and the cam diagram.

Fig. 30 shows diagrammatically the division of the plug board.

Fig. 31 shows a perspective the arrangement of one contact bar of each of the various shifting elements.

Fig. 32 shows a circuit diagram for a key board by means of which one factor may be entered into the machine by key depression.

General explanation In the machine hereinafter described the two factors are taken ofi? the one and the same deck of the card and theproduct is punched in this deck at the end of the multiplication. The factors are transferred from the card to storing devices from which the removal proper of the component values for the multiplication is effected. The products of the various multiplication operations are added one by one into an accumulator. The accumulator shows consequently at the end of all multiplication operations the complete product and is therefore designated asthe product accumulator. When the multiplication is finished the product accumulator is analyzed and its setting is transferred to a punching device under which thecard has been passed in the meantime; punching of the product isnow effected in said card. With the punch ing of the card the following card is analyzed at the same time and the factors are entered into the storing devices from which then in turn the component values for the multiplication are derived.

A card which is used in the machine is illustrated in Fig. 1. The card consists of three decks each comprising 30 columns each of the columns having six hole positions. Punching in the card is effected by hole combinations as indicated by the code in Fig. 3. According to this code the meaning of one hole combination is composed of the various component values associated with the various hole positions. These values are indicated in the column W while the column P indicates the positions (IV). If for instance the first and third position is punched the value is composed of the value 1 (position I) and of the value 3 (position III) which amounts to the value 4. In a similar manner the meaning of each of the numerals 0-9 will follow from the component values punched in the positions I to V. As shown in Fig. 3 five hole positions are used for the representation of the numerals. The division of the card according to Fig. 1 shows, however, six hole positions for the representation of letters which, however, is of no importance for the present invention.

In order to permit a simpler construction of the machine the two factors and the product are punched into the same deck of the card. It is herein of no importance in which deck the factors and the product are provided. The selection of the decks is possible by means of a simple device in the plug board to which reference will be made in the description of the circuit diagram. Moreover it is immaterial in which column the factors and the product within one deck are provided; for it is possible to connect through a plug board each column with each storing denomination or product accumulator denomination.

The device for the analysis of the factor storage device is so constructed that the component values may be obtained again in the same manner as indicated according to the code in Fig. 3. But for the multiplication itself the agreement is not absolutely necessary. For the multiplication there is only neccssary a code which is suitable for the same whereas the factor perforation in the card maybe effected according to any known code. This is possible since the combinations represented in the storing devices are effective only within the multiplication device but, are not transferred to the punching device. The setting of the punching device is rather effected through the product accumulator, the setting of which must thereafter represent the combinations in accordance with the code according to which the card has been punched. The arrangement chosen for the described embodiment in which the code for the perforation of the card is the same as isused for the multiplication, has the advantage that the same crank drive may be used for the entering of the values into the storing devices as well asfor the multiplication. The multiplication is effected in several consecutive setting operations, whereby within each settingoperation a component value of a multiplier digit is multipliedsuccessively by all component values of a multiplicand digit.

At first all digits of the multiplicand are multiplied at the same time by the lowest digit of the multiplier and after each forming of the sub-product the sub-product is entered into the product accumulator. Subsequently displacement to the tens place of the multiplier and displacementof. allmultiplicand denominations with respect to theproductaccumulator by one denomination is effected, whereupon again multiplication of all multiplicand digits andentering of the sub-products into the accumulator is effected.

The multiplication by one digit of the multiplier is, however, not effectedas has been already indicated in a single stroke but consecutively by the various component values of the multiplier digit. Thereby a complicated sub product device is avoided since only the various com- '5. ponent values are multiplied by each other. The same are selected in such manner that the highest product of the same is always smaller than 9. This affords the advantage that a simple accumulator device can be used as the product accumulator.

The performance of a calculation with the various component values may be seen from the example in Fig. 4. In this example 24 871 is to be multiplied by 7. The division of the numerals of the two factorsin accord ance with the values W in Fig. 3may alsobe seen in Fig. 4. In the first step the first component value of the numeral 7namely 1-is multiplied simultaneously by the first component value-which is also l-of each denomination of the number 24 871. The multiplication is, however, only effected in those denominations of the multiplicand having a significant figure, that is to say where there is no zero. Subsequently the second and thereafter the third and finally the fourth component values of the number 24 871 are multiplied by the first component value of the numeral 7. After all component values of the multiplicand have been multiplied by the first component value of the numeral 7 further displacement to the second component value of the numeral 7 takes place. But since this is zero the device will be immediately set to the third component value (namely the component value 3) and again all component values of the number 24 871 are multiplied successively. Subsequently the machine will be set to the fourth component value of the numeral 7 (again component value 3) and the same will be also multiplied by all component values of the number 24 871.

The translation for the setting of the storing device and for multiplying is preferably effected by means of a crank drive with two variables and by a continuously rotating crank. Three different embodiments are shown diagrammatically in Figs. to 7. The crank drive has been chosen because it permits a safe clutching and uncoupling of the accumulator elements at the dead centers and because the return movement can be used for an automatic unclutching which will be referred later to below.

Fig. 5 shows diagrammatically a crank drive having a crank 11 with variable crank radius and with a variable rocking point of the pusher bar 12. The possibility of the variation has been illustrated diagrammatically in this picture by screwthreaded spindles. To the right hand end of the pusher bar 12 there is pivoted a pawl 13 acting upon a ratchet wheel 14 of the product accumulator. The stroke of the pawl may now be varied on the one hand byvariation of the radius of the crank 11 and on the other hand by moving of the guide 15 and consequently of the rocking point. Accordingly also the ratchet wheel 14 will be displaced through more or fewer teeth. Depending on the setting of the crank 11 and the rocking point the latter being determined by the guide 15, a definitely determined stroke of the pawl will follow. If the setting of the rocking point and of the crank radius takes place in agreement with the component values of the factors the stroke of the pawl will result as a product of the two settings.

A further diagrammatic embodiment is illustrated in Fig. 6 which embodiment uses a crank 16 with constant radius and two pusher bars 17 and 18 which are arranged in series. The connection between the two pusher bars 17 and 18 is jointed. Each pusher bar has an own rocking point which is variable for itself. The rocking point may be varied by moving of the guides 19 and 20 and in similar manner as in the arrangement according to Fig. 5. A pawl is pivoted to the right hand end of the pusher bar 18, said pawl acting upon a ratchet wheel of the product accumulator in a similar manner as in Fig. 5. If the crank 16 is rotated the pusher bar 17 will rock about its rocking point. Depending on the position of the guide 19 its right hand end will carry out a larger or smaller movement. Due to the pivotal connection the left hand end of the bar 18 is forced to follow this rocking movement whereby the bar 18 rocks about its pivot which is determined by the guide 20. Depending on the position of the guide 20 the rocking at the right hand end, to which the pawl is pivoted, is diminished or increased. The stroke of the pawl therefore depends on the position of the two guides 19 and 20. The positioning of the guides 19 and 20 is determined by the component values of the factors so that the stroke of the pawl will result as the product of the two settings.

If only a small number of component values is to be multiplied by each other, as is, for instance, the case in the machine hereinafter described in detail, in which, in fact only the numerals 1, 2 and 3 are multiplied by each other and by themselves, one of the variables of the crank drive may be replaced by different ratios of the gears. With the employment of the component values 1, 2 and 3 its is then possible to work with three transla tions. A diagram of a crank drive which operates according to this principle is shown in Fig. 7. The diagram corresponds to the practical embodiment as it is used in the machine described below, only the gear ratio has been illustrated somewhat differently in order to facilitate the explanation.

The arrangement in the machine is such that the storing devices of the factors as well as the product accumulator are driven by a single crank drive, the setting of which is effected cyclically with regard to the card analysis and to the multiplication operations respectively, and to which the various storing devices or accumulator elements are clutched for the time during which a transfer is effected to them. The guide setting is effected in accordance with the component values-synchronously with the analysis of the card or with the analysis of the storing devices and of the product accumulator respectively.

The crank 21 is continuously driven with constant speed in counterclockwise direction. On the other hand upon each full revolution of the crank 21 the crank 22 is displaced one step in counterclockwise direction. This displacement will be described in more detail later on. A rod 24 is pivoted to the crank 21, said rod being provided for reciprocating movement in the guide 25. (This guide is only symbolically indicated in Fig. 7 while actually it is constructed differently therefrom). The right hand end of the rod 24 describes an ellipse-like curve. If the guide 25 is moved the curve will change. At the right hand end of the rod 24 there is a rocker 23 connected thereto by the link 26 which latter rocks in accordance with the curve. The angle through which the rocker 23 swings is dependent upon the shape of the curve. The guide 25 is now moved in such a way as to cause the various angles of swing of the rocker 23 to be proportioned to each other in the same manner as the component values I to IV in Fig. 3 (i. e. l:2:3:3). In all four positions (the third position is identical with the fourth position) a constant angle must be subtracted in which the rocker runs idle on account of the play between the gears, and other parts. This play is also necessary for another reason as will be shown later, it is intentionally increased so that the drive can remain stationary at the moment of clutching.

The position and dimensions of the crank drive have been chosen in such a manner that at the lower dead centre of the rocker 23 the guide 25 as well as the auxiliary crank drive cooperating therewith (described later) may be adjusted without changing the position of the rocker 23. This is necessary since the clutch for the clutching of the storing device and accumulator places respectively to their drive must be always in the same position independently of the position in which the guide 25 happens to be. It is only necessary to take care that the guide 25 has already reached the positions (indicated in Fig. 7 by Roman numerals in accordance with the hole position designation according to Fig. 3) associated with the hole position at the upper dead centre of the rocker 23 (indicated in dash lines in Fig. 7) since the position of this point is a measure for the component value by which the storing device wheel and the product wheel respectively will be advanced.

The adjustment of the guide 25 is effected by the crank 22. Dimensions and position have been chosen here in such manner that the unequal distance between consecutive positions of the guide 25 on the rod 24 are transformed into equal movements of the crank 22. This is an advantage in so far as in addition to the step by step shifting also a continuous drive of the crank 22 can be derived from crank 21, if desired.

The rocker 23 is connected to the toothed segment 27 meshing with the toothed wheels 28 and 29. The ratio of the diameters of the segment and the two gears has been here so chosen that they have the same relation to each other as do the component values 3:2: 1. The drive to the clutches for the accumulators may now be directly clutched to the segment or to one of the two gears 28 and 29. According to whether the clutching is to the toothed segment or to one of the two gears so is the respective translation effective upon the drive. Consequently the rocking movement of the rocker 23 is multiplied by the ratio of the gears. This arrangement permits a simplification of the crank drive serving for the multiplication, since only one of the two factors needs to be set up on the crank drive itself while the other factor may be transferred into. the ratio. This latter circumstance again permits an easy skipping of the component values and therewith avoidance of idle cycles.

Construction of the crank drive The actual construction of the crank drive is shown in Figs. 8 and 9. The rod 24 consisting of two adjacent metal strips is linked to the crank 21. It has a rectangular cut out portion 24a in which can slide a guide piece 31 (Fig. 9). The guide piece 31 is loosely seated and rotatable upon the pivot pin 32. On the pin 32 there are further mounted the two loose guide pieces 33 adapted to slide in the guide bars 34 which are provided on both sides of rod 24 and are fast to the base plate. As a protection against mutual interference of rod 24 and the guide bars 34 and in order to prevent the guide pieces from sliding off, the disks 35 are provided between the guide pieces 31 and 33. The arrangement of the guide pieces permits sliding of the pin 32 in the guide bars 34, sliding of the rod 24 on the pin 32 and rocking of the rod 24 relative to the fixed guide bars 34 about the axis 32. The displacement of the guide pieces is effected by the two links 36 which are screwed fast to the pin 32. At the left hand end of the rod 24 the rocker 23 is connected by the link 26.

The positioning of links 36 and therewith of guide 25 is effectedby crank 22 which in practice takes the form of a ratchet wheel. The rocker 37 connected to the links 36 is rotatably mounted at its right hand end on the stud 38- which is fast in the casing. The rocker 37 is necessary in order to safeguard the proper positioning of the link 36 and thereby also of the guide.

Movement of the ratchet wheel 22 is effected by pawl 39. The pawl 39 is rotatably mounted on the rocker 41 and is resiliently held against the ratchet wheel 22. The rocker 41 is driven by an eccentric 42 by the eccentric rod 43. The eccentric 42 is mounted upon the same shaft as the crank 21 so that the rocker 41 will rock back and forth once at each revolution of the crank 21. By this means the ratchet wheel 22 will be moved one step by means of pawl 39. By this movement the movement of the guide 25 is effected through rod 40 and the link 36, the rod 40 being pivotally mounted on the ratchet wheel 22.

The position of the guiding pieces in the guide bars 34 must be exactly defined after the rocker 23 has reached the outer dead centre. This is necessary since in this moment declutching of thev storing; and product device wheel respectively takes place. As indicated above, this dead centre position also indicates the value for the associated position. During the remaining time the guide may be moved, this movement having however no influence upon the adjustment. The position of the guide has no influence upon clutching since the crank drive and the position of the guide bars 34 have been chosen in such manner that the position of the one dead centre is independent of the positioning of the guide.

Provision must be made that forces occurring and tending to move the guide from the predetermined position which must in no event occur at the outer dead centre, cannot have any influence. Therefore the ratchet wheel 22 is arrested at this moment and is blocked in both directions of rotation so that no unforeseen movements can arise. Blocking is effected by the lever 44 with its semicircular cut out portion 45. The cut out portion 45 of lever 44 can engage over the screw heads 46 thus blocking the rotation of the crank disk 22 in both directions. This blocking must be maintained for some time. Moreover, a quick engagement is desired which is obtained by a snap-action mechanism. The arm 47 is rotatably mounted upon the stud 48 fast to the casing and is connected through link 49 to the rocker arm 41. Therefore the arm 47 will rock synchronously with the rocker arm 41. Upon the stud 48 there is also rotatably mounted the lever 44 which is connected by spring 51 to the arm 47. Under the influence of the rocking move ment of arm 47 the lever 44 will now continuously snap back and forth between the stop 52 and the screws 46. The dead centre has been positioned in such manner that the lever 44 engages the screw 46 when the guide or the screws 46 respectively have reached the proper position.

In order to compensate for tolerances and play and to permit an exact adjustment of the strokes the various screws 46 or the teeth 53 of the ratchet wheel are individually adjustable. The ratchet wheel 22 is constructed as a simple disk to which each of the teeth 53 isfastened by means of a screw 46. The screw holes in the disk are somewhat larger thereby providing a limited adjustability. In order to prevent rotation of the teeth 53 the latter engage inside with a disk. in order to compensate for differences in the division which possibly might occur by the assembling, a larger stroke has been provided for the pawl 39 than for the normal division.

The rocker 23 acts upon a set of gears (Figs. 8, l3 and 14) from which may be derived the various ratios in accordance with the values. in order to obtain a simple clutching operation and an axis for the drive which will be common to all ratios a planctary gearing is provided. The rocker 23 is constructed as a triangle and mounted on the shaft 54. Further the shaft 55 passes through a hole of the rocker 23 thereby providing a wider play in order to obtain a larger idle running and therewith a longer coupling period as has been already described above. In accordance with the rocking movement of the rocker 23 the shaft 55 will be taken with it, on which shaft are fast the gears 56, 57, 58 and 59. The shaft 55 is mounted in the sleeves 61 of the arms 62 and 63. These arms are fast on the shaft 54 which is mounted on the stud 64 of the shaft 65 and in the sleeve 66 of the stirrup 67. The stirrup 67 is fastened to the base plate and serves as a support for the gearing. The two arms 62 and 63 are, moreover, kept together by a pin 68.

The gears 56, 57, 58 and 59 are in engagement with the gears 69, 71', 72 and 73. The gear 69 is fast on the shaft 65 from which a drive for the accumulator setting is derived; The gears 71, 72 and 73 on the other hand are loosely mounted on the shaft 54. If one of the gears 71, 72 or 73 is arrested the associated gear 57, 58 or 59 of the reciprocating set of gears will roll upon the first one. Due to the different diameter with respect to gear 56 engaging the gear 69, the gear 69 and therewith the shaft 65 will receive a rotating movement in the sense opposite to that of the rocking movement of the set of 9 gears. Depending on the selection of the. diameters of the gears the respective ratio will follow therefrom. The ratios of the diameters have been here so chosen that if the gear 71 is arrested a ratio of 1:1 results, upon arresting of the gear 72 a ratio 1:2 will result and upon arresting of the gear 73 a ratio 1:3.

Arresting of the gears is effected by the levers 74 and 75 (Fig. 8) which are mounted on the pin 77 and of which the noses 76 engage the teeth of the toothed wheels whereby arrest of said toothed wheels is effected. In this gearing always one of the three gears 71, 72 or 73 respectively must be arrested since otherwise a displacement of the gearing and therewith of the whole setting of the machine might occur. For this reason the lever 74 is permanently pressed by the spring 78 against the gear 71 by means of which a 1:1 relation is attained. A pin 79 is riveted to the lever 74, the pin 79 projecting past the two levers 75. If one of the levers 75 is rocked in clockwise direction it will encounter the pin 79 and take with it the lever 74. During this rocking movement the lever 75 reaches the teeth of the corresponding gear while the lever 74 is withdrawn from the teeth.

Rocking of the two levers 75 is effected by the magnets K and K the armature 81 of which is linked to the levers 75 with the bars 82. The levers 75 are held in their rest position by the springs 83, the rest position being determined by the stop 84. Moreover the armatures 81 act upon the contacts k or k respectively, the function of which will be referred to in the description of the wiring diagram below.

Consequently the ratio 1:1 is normally set up. If the magnet K is energized the ratio 1:2 will be set up and by the magnet K the ratio 1:3 is set up and the rocking of the crank drive is multiplied accordingly.

Clutch system for the storing device and product accumulator places The construction of the clutch system for the storing device wheels and for the product accumulator wheels is the same so that it will be suflicient to describe the arrangement for the wheels of the storing device. The back and forth movement of the pinion 69 (Fig. 13) is transferred through a gear mechanism, which will be referred to later, to the shaft 91 having the gears 92 (Figs. 12 and 22) fast thereon. For each wheel of the storing device a pinion 45 is provided. The latter meshes with the pinion 93 which is firmly pressed upon the ring 94 (Fig. 23). In the ring 94 there is provided a slot 95 accommodating the pawl 96 and the spring 97. By spring 97 the pawl 96 may always be held in one of two rest positions. The ring 94 only rotates upon the teeth of the actuating wheel 98, which is mounted on the sleeve 99.

According to the value of the effective hole position each ring 94, driven by its pinion 92 will be rotated. If the clutch magnet has been energized slightly earlier by a hole in the card, the lever 101 will encounter the pawl 96, which will be pressed into the gap between the teeth of the actuating wheel 98, said pawl taking the wheel 98 with it in clockwise direction. Engagement of the pawl can only occur in a predetermined position, which is controlled by the cam contact it which is referred to latter on in the circuit diagram. The position of the pawl is determined during clutching by the crank drive as has already been mentioned. The movement of the actuating wheel 98 always takes place for a multiple of the pitch so that the teeth wil always be again in the proper position for engagement.

Upon backward movement of ring 94 the actuatingwheel 98 is locked against backward movement which is attained by spring 102 (Fig. 21). The spring 102 engages with a locking wheel 103 which is fast to the actuating wheel 98. The pawl 96 is forced outward by the inclined back face of the tooth until it reaches its outer position in which it will then be held by the spring 97. Accordingly, declutching will automatically take place right at the beginning of the backward movement. The ring 94 will now run back until the dead centre for the next clutching operation is reached.

The actuation through the ring 94 from the drive 92 takes place in such a manner that the position of the actuating wheel 98 indicates the setting of the storing device.

Storing device for factors and product accumulator The storing devices and the product accumulator are arranged at the rear side of the machine (Fig. 12). Their drive is effected by the gear 69 and the shaft 65.. as has been already mentioned above. On the shaft 65 there is provided the worm wheel 100, which drives the. worm wheel 105 of the shaft 106. On the shaft 10.6. there is also mounted the crank 107 (Fig. 18) to which the crank 109 is connected by means of the link 108. The crank 109 has the same length as the crank 10.7 and carries out the same rocking movements as the latter. With the link 108 there also engages the auxiliary crank 111 serving to avoid dead centres during the trans.- fer. The crank 109. is rigidly connected to the gear 112 which meshes with the gear 113 on the shaft 91.

As already described above, the drive of the clutch systems for the denominational elements of the storing device is effected from the shaft 91. The drive to the clutch systems of the denominational elements of the product accumulator is transferred through idle gears 104 (Fig. 12). The elements of the storing device are mounted on the shaft 115, while the elements of the product accumulator-in the following always called accumulator elementsare mounted on the shaft 116. Each storing device comprises 8 elements and the accumulator: comprises 16 elements. The setting of the storing and accumulator elements is effected by similar clutch systems of which one has been already described above. The construction of the accumulator and of the storing device are similar to each other so that the operation of both may be explained in connection with Fig. 21 which only represents an accumulator element. The storing device differs from the accumulator element only in that it has no tens transfer mechanism.

Clutching of the accumulator and storing device elements is effected by means of the levers 101 through the magnets S or Z respectively, which are fast to the plate 117. The levers 107 are alternately arranged and mounted on the shaft 118. They are pressed against the plate 121 by means of the springs 119. If a magnet is energized it will press upon the lever 101 thereby clutching its accumulator or storing device element respectively. Setting of the storing elements is now effected from the crank drive value by value in accordance with the subsequent analysis of the individual hole positions.

The analysis of the storing devices for the multiplication is effected again in component value combinations, as has been already described above. For this purpose each storing denomination has been furnished with four cam disks 122, 123, 124, and (Figs. 24 to 27).

The positions of the cams on each of the various cam disks have been chosen in such manner that the cams indicate again the component values of the accumulator setting. The cam disks are fast on the actuating gear 98 (Fig. 23) which represents the accumulator setting as already described. Further, the ratchet wheel 103 (Fig. 21) for locking against backward movement is fixed to the gear 98. The four cam disks are suflicient for the representation of the numerals since with the exception of the zero-position the numerical code extends only over four hole positions. The shapes and the relative positions of the cams with regard to each other is shown in Figs. 24-27. The cam disk 122 corresponds to the position I (Fig. 3) with component value 1, the cam disk 123 to the position II with component value 2, the cam disk 124 to the position III with component value 3 and the cam disk 125 to the position IV, also with component value 3. With each cam disk is associated a contact spring 126 which can be pressed by the cams upon the common conductor 127. Depending upon the setting of the accumulator the four springs are brought into contact with the common conductor according to the code in Fig. 3. All springs 126 are fastened on the stirrup 128 by means of the plate. Two insulating places 129 (Fig. 21) insulate the springs from each other and from earth. The cam disks are separated from each other by the disks 149.

The analysis of the storing elements for the multiplicand is effected simultaneously for all denominations but consecutively for the various positions. The analysis of the storing elements for the multiplier however takes place successively for all positions of a denomination at the same time. This will be referred to in the description of the circuit diagram again later on. The various positions of all storing elements of the multiplicand are analyzed in compliance with the settings of the crank drive wherein one revolution of the crank 21 corresponds to the analysis of one position. According to the setting of the crank drive also, the analysis had been divided in six steps in which case four steps are provided for the analysis itself and two for the idle run.

-If the storing device is to be analyzed the left hand shaft 131 (Fig. 12) is shifted step by step. The extent of the steps has been so chosen that the shaft 131 reaches its home position after six steps.

Each shaft 131 on which the cam disks 132 are mounted is of hexagonal section. For each spring 126 is provided a cam disk 132. The cams are offset relatively to each other by one sixth. The springs 126 are pressed by the cams one by one against the contact bars 133. A separate contact bar 133 is provided for each accumulator element, said bars being fastened to the insulating bar 134. The timing of the engagement of the springs with the contact bar corresponds to the analysis of the hole position on the card or to the settings of the crank drive respectively. However, current can only flow through the springs if the same are pressed at the same time against the common conductor 127 by the accumulator cams 122, 123, 124 and 125. The position of the cams 132 has been chosen in such manner that during the first four runs said cams press their springs 126 one by one against the common conductor 133.

When the multiplication is completed zeroizing of the storing devices will be effected so that new factors can be entered into the same. For this purpose a recess 135 is provided in the ratchet wheel 103 which is provided for each storing denomination, a spring 136 being situated in the recess. Upon setting of the storing devices this spring will slide through slots, which are provided in the sleeve 99. The sleeve 99 rotates during the setting of the storing devices in counterclockwise direction (Fig. 12) which, however, has no influence on the storing elements since the springs 136 may slide over the slots in the sleeve. If the storing devices are to be zeroized the sleeve will rotate once in clockwise direction. Depending upon the setting of the accumulator elements the springs 136 drop into the slots at different times so that the storing elements are taken with it by the sleeve and are zeroized.

The analysis of the storing devices or their multiples are transferred to the product accumulator and are added in the same. The determination as to whether the analysis itself of the storing devices, or a multiple thereof is to be transferred to the product accumulator will follow from the description later on. The sub-products are entered one by one into the accumulator elements and are added in the same. While there always is entered only a single number into the storing devices the accumulators receive one by one all sub-products. Accordingly, the accumulator wheel is completely rotated up to the final setting more than once on account of which a tens transfer is necessary.

The tens transfer mechanism is of a known construction similar to that of the Hollerith machines. The pawl 137 is rotatably mounted on the lever 138 and is pressed by spring 139 against the ratchet wheel 103. The lever 138 is rotatably mounted on the sleeve 99 and the spring 141 tries to rock the lever in clockwise direction. The lever 138 is however prevented from displacement by the nose 142 of lever 143. The lever 143 is pressed by spring 144 against the lug 145 of lever 138. When the accumulator wheel rotates, the pawl 137 will slide over the teeth of the ratchet wheel 103. To the pawl 137 a stud 146 is fastened which passes below the lever 143 of the next higher denominational accumulator place. The teeth as well as the stud 146 are formed in such a manner that the normal teeth will raise the stud 146 only so far that the latter cannot reach the lever 143. On the ratchet wheel there is provided adjacent to the normal teeth a larger tooth 147. Its position corresponds to the 9-position of the accumulator. If the tooth 147 passes the pawl 137 which means that the accumulator wheel has been moved from 9 to 0 the pawl 137 will be raised so far that the stud 146 engages the lever 143 of the next higher denominational accumulator place. The lever will release the lever 138 of its associated denominational place which latter lever will rotate under the tension of the spring 141 in clockwise direction until the lever engages the yoke 148. If at this time the pawl 137 engages the larger tooth 147 it will release, in the manner just described, the lever 143 for the next higher denominational place.

After the setting has been completed the yoke 148 will be rocked in counterclockwise direction and will restore to their home position the levers 138 which have been released. Hence the pawl 137 will move the ratchet wheel 103 for one unit thus completing the tens transfer. The analysis of the accumulator elements is effected for punching again in component value combinations, simi lar to the analysis of the storing elements for the multiplicand.

The storing devices and accumulators operate alternately in such manner that zeroizing takes place for the one while setting is effected for the other. The drive for zeroizing through the sleeves 99 and the tens transfer through the yoke 148 is derived from the crank 151 (Figs. 15 and 16). The latter has the same speed of rotation as the crank 21, namely it will rotate once per setting cycle. To the crank 151 is linked the rocker 152 through the link 153 and the rocker 154 through the link 155. The rocker 153 is fast upon the shaft 116, on which is also fast the yoke 148. Accordingly the yoke will reciprocate once per setting cycle.

The rocker 154 is mounted on the stud 156. On said rocker there is provided the pawl 157 which is rocked by the spring 158 in counterclockwise direction until the pin 159 on the pawl 157 engages the rocker. In normal position the pawl reciprocates without causing any effect. It is only if the magnet N is energized, and attracts its armature 161, that the same will move the gear 162 downwards (Fig. 16) by means of which the cams 163 on the gear 162 enter the range of the pawl 157. If now the pawl approaches the cams it will be raised by the inclined face of the cams and will subsequently drop between the two cams thus moving those and therewith also the gear 162 in the rocking movement. The rotation of the gear 162 is transferred to the two gears 164 and 165 which are provided on the two sleeves 99 for the zeroizing. In accordance with the direction of rotation of the gear 162 either the storing devices or the accumulators are zeroized. If the gear 162 rocks in clockwise direction (Fig. 15) the storing device will be zeroized, and if the gear 162 rotates in counterclockwise direction the accumulator is zeroized. The opposite rotation of the respective zeroizing sleeve 99 does not interfere with the setting since, as has been already described above, in this case the spring 136 is urged outwardly by the sleeve.

Upon rotation of the gear 162 the pin 166 temporarily opens the contact a Thereby the holding circuit is interrupted through the magnet N, so that the latter will drop and its armature will be restored to the home position'by a spring. This, however, cannot take place immediately since it is prevented'by the pin 166 which slides on the plate 168 (Figs. 16 and 17). It is only if the gear 162 has reached the final position that the pin 166 may slide ofi the plate and the gear 162 may be brought to the home position by the armature 161. Hereupon the cams 163 are moved out of the range of the pawl 157 so that the latter is now idly reciprocating again. The screws 169 serve as stops and to determine exactly the position as well as the rocking angle of the gear 162. This is required in order to obtain an exact zeroizing. If the magnet N is again energized the return movement of the gear 162 is effected. Upon a single energization of the magnet N the gear 162 will therefore move only in one direction. It is only upon the second energization of the magnet N that the gear will run back again. Consequently always the storing device or the accumulator is zeroized alternatively.

The analysis of the storing device of the multiplicand as well as the analysis of the product accumulator takes place step by step as has been already described above. Moreover the analyzing cycles take place also alternatively, similar to the zeroizing. The step by step shifting for the analysis of the storing device is derived from the rocker 152 which reciprocates once per setting cycle. To the latter the rocker 172 is linked by means of the link 171, the rocker being mounted on the stud 173. On the rocker 172 there are provided the two pawls 174 and 175 which are urged resiliently against the ratchet wheels 176 and 177. The pawl 174 acts here upon the ratchet wheel 176 on the shaft 131 for the analysis of the storing device and the pawl 175 acts upon the ratchet wheel 177 on the shaft 131 for the analysis of the accumulator.

Analyzing as well as zeroizing are effected oppositely to each other and alternately, i. e., if the storing device is zeroized the analysis of the accumulator will become effective and vice versa. Accordingly the setting of the analysis may be derived from the drive for the zeroizing. The position of the gear 162 indicates whether the storing devices or the accumulator have been zeroized so that this fact may be used for the control of the analysis. The gear 162 is connected to the eccentric disk 178. T o the latter there is linked by means of the eccentric rod 179-the arm 181 which is mounted on the stud 182. Depending upon the position of the gear 162 or the eccentric disk 178 respectively the arm 181 is rocked upwards and downwards. Two pins 183 and 184 are provided on the arm against which pins the pawls 174 or 175 respectively are urged. If, however, the arm 181 is in the upper (illustrated) position thereby also the two pins have been moved upwards. the pawl 175 may now drop into the teeth of the ratchet wheel 177 and may shift the same step by step. On the other hand the pawl 174 is kept disengaged from the teeth by the pin 183 so that the pawl will push idly and no step by step shifting of the ratchet wheel 176 will be effected. If the arm 181 is in the lower position the pawl 174 will engage the ratchet wheel 176 while the pawl 175 will push idly. In this case the step by step analysis of the accumulator is etfected. The safeguarding of the ratchet wheels and the locking against backward movement is elfected by the detent springs 185.

In the accumulator there must be provided a device which suppresses the zero-punching before the highest significant figure of a number, but which permits punching of the zero within a number.

This is obtained by a particular wiring of contacts (Fig. 20). The wiring diagram in Fig. 20 shows only diagrammatically the wiring elements for the zero-suppression. Other wiring elements though included in this current circuit but serving other purposes have been In this instance omitted and willbe described later on in connection with the wiring. Each accumulator place has a set of contacts associated therewith generally indicated at zo. These consist of four contact springs of which the two lower ones (Fig. 21) are closed when unstressed. In the 0 position of the accumulator wheel the longer contact spring is pressed upwardly whereby the three upper springs establish a conducting connection between themselves and whereby contact with the lower spring is interrupted (Fig. 24). The actuation of these contacts is effected by the cams 186 on the intermediate disk 149. The location of the cam has been chosen in that way that the set of contacts 20 is actuated when the accumulator wheel is at zero. If the accumulator wheel is moved from the 0-position the above mentioned shifting of the contacts will take place.

In Fig. 20 the Arabic index of the punch selector magnets L and of the contacts zo indicates with which accumulator denomination the same are associated. It has here been assumed that the units denomination is indicated by the Arabic index 1 and the higher denominations by the indices 2, 3, 4, 5. If it is for instance assumed that the number 3050 is to be analyzed from the accumulator, contact Z02 and Z0 will have been moved to the position shown in Fig. 20 since in the tens place (corresponding to Z02) and the thousands place (corresponding to Z0 the accumulator wheel has been moved. The zero-setting upon the selector magnets of the punch mechanism is effected through the contacts a 11, zo, .zo to the selector magnet L and through the contacts a 11, 20 zo to the selector magnets L Accordingly the wiring has been so arranged that when the V-position is positioned past the punching device, a current impulse will pass through the contact a rr and L and L will be energized whereby the punches associated with these magnets will be pressed through the card, thus causing zero-punching.

No current can flow through L and the selector magnets or" the higher places of the accumulator since the contact Z0 has interrupted the line in this direction. Nor can any current flow through L and L since the line to these magnets is interrupted at the contacts Z0 and Z02 (which have been shifted by their own accumulator place).

Moreover a device must be provided which permits all denominations of the multiplicand to be moved by one denomination in relation to the product accumulator after they have been multiplied by a denomination of the multiplier. This is obtained by a step by step selector (Fig. 8) which for reasons of space is divided into two separate selectors operating in parallel with each other. The distribution of the individual contact paths over the two selectors may be made arbitrarily.

The contact paths are comprised in the two contact fields 187, along which the two runners 188 may slide, the runners being driven by the step shift magnets D and D If the step shift magnets are once energized the displacement of the runners for one step is effected. The runners comprise three arms for each path so that always one of them is in engagement with the contact path concerned and no idle run can arise. The runners are supplied with current by the lamellae 189 which are always in connection with the various arms of the runners. The current flow is efiected through the remaining contact lamellae 191 to which the arms of the runners are shifted step by step.

The development of the plugging of the column shift operation device for the multiplicand is shown in Fig. 19. The first row to the left corresponds here to the lamellae 189 (Fig. 8) by means of which current supply is effected to the runners. The analyzing devices of the storing devices for the multiplicand are connected to said lamellae, which for reasons of simplicity are here designated at sk. The Arabic index indicates the denomination in the storing device. The number 1 corresponds

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