DE1283576B - Impulse-controlled high-speed printing unit - Google Patents

Description

FEDERAL REPUBLIC OF GERMANY GERMAN 40S7WW PATENT OFFICE Int. Cl .:

G 06k

EDITORIAL

German class: 42 m6 - 15/04

Number: 1283 576

File number: P 12 83 576.6-53 (S 79676)

Filing date: May 29, 1962

Opening day: November 21, 1968

Impulse-controlled high-speed printing units serve, for example, as a serial printer in connection with Data processing machines or as printing units for data-controlled teleprinters. The invention relates to such a high-speed printing unit with a design in which the type carrier by means of a mechanical Summation gear is adjustable relative to a print hammer, with the setting of the actuators of the summation gear is carried out by an intermittently driven drive element, which during its standstill periods via solenoid-operated coupling elements, which can be triggered by data pulses are, can be selectively coupled to the actuators.

A high-speed printing unit of this type is already known. The drive element consists of the actuators of the summation gear from two drive rails, which via cam sensors from two to one Main shaft running at constant speed with cams offset from one another by 180 ° 180 ° out of phase, intermittent sliding movements are driven, and the over simple acting coupling elements, which for each data pulse a certain fixed direction of actuation own, can be selectively coupled to the actuator in question. The drive rails are alternating effective per half-turn of the main shaft, so that each value of a data pulse always the same direction of displacement of the drive rails is assigned. This is necessary because otherwise the actuators alternate with a certain data pulse during the half-rotations of the shaft be moved in the opposite direction, resulting in the wrong one every other half-turn Type choice would result.

This known high-speed printer works in such a way that the type carrier between the individual printing processes is moved directly from the one set position to the next position without in between to take a zero position. In addition, two are made for every full revolution of the main shaft Settings of the type carrier with corresponding printing processes, what (as well as the avoidance a special zero position of the type carrier) in the interest of the highest possible working speed is in itself very cheap. This mode of operation does, however, in the known high-speed printing unit a doubling of the drive rails with the parts assigned to them is required, with the Rails also regardless of whether the actuator in question is to be adjusted or not, always subject to a drive. This results in a considerable amount of mechanical, pulse-controlled movement High-speed printing unit

Applicant:

Soroban Engineering Inc.,

Melbourne, Fla. (V. St. A.)

Representative:

Dr. Kurt-Rudolf Eikenberg, patent attorney,

3000 Hanover

Named as inventor:

John H. MacNeill, Indialantic;

James E. Bellinger, Eau Gallie;

Thomas G. Holmes, Melbourne, Fla. (V. St. A.)

Claimed priority:

V. St. v. America June 12, 1961 (116 524) -

borrowed parts, with the result that the maximum speed the main shaft, i.e. the operating speed of the printing unit, is severely limited and thus the with the use of half-turns of the main shaft, this advantage can be achieved at least to a large extent will be annulled. In addition, there is another factor for limiting the working speed that the summation gear in this known high-speed printing unit, the adjusting wires or generally hitherto customary for such devices -cable that can withstand the very strong impact and tensile stresses that occur at high working speeds have not grown and have incorrect settings after a relatively short run-time of the type carrier or other malfunctions if they are not constantly readjusted will.

The problem of working speed is extremely important in high-speed printing units, because z. B. is the mechanical printing unit in a data processing machine as a rule the slowest component and thus determining the speed. The only limited working speed, which shares the well-known high-speed printer with devices of other types, therefore restricts its usability in practice considerably. This deficiency is now to be eliminated. It is therefore a task the invention to provide a high-speed printing unit that can be moved with only a minimum of Sharing gets by and that even after a long time

809 638/1647

Operating time without loss of accuracy and reliability of the setting of the type carrier is essential allows increased working speeds.

According to the invention, this object is achieved by that as a drive element one with an even number of standstill periods per revolution driven shaft is provided and the coupling members with two in opposite directions of actuation working coils are designed such that the shaft in each standstill period can only ever be coupled to the actuators in one of the two operating directions, and these reverse coupling actuation directions from standstill period to standstill period, whereby through one derived according to the shaft position in the successive standstill periods Control signal the assignment of the data pulses to the two coils of each coupling member alternately is switched.

The proposal of the invention also makes use of the idea of at least two setting processes to increase the working speed to be carried out per revolution of a shaft. However, this is no longer a duplication of any moving drive parts required, as in the known high-speed printing unit constantly are driven, but are only required alternately. Rather, during each partial rotation the intermittently driven shaft always uses the same moving parts, whereby the special, double-acting design of the coupling links in conjunction with the switching of the assignment of the data pulses to the two coils of the coupling links ensures that in each partial rotation the shaft results in a "correct" setting of the actuators. If a certain Data pulse, e.g. B. of the value "1" in a standstill period, a clutch link has triggered and then then the relevant actuator has been moved to the position corresponding to a »1«, the same data pulse in the next following standstill period the coupling between shaft and Cancel actuator so that the actuator remains in its position corresponding to "1", i.e. during the next partial rotation of the shaft is not readjusted.

Thus, there is the only additional expense in the proposal of the invention, compared to one Device that only works with one setting process per shaft revolution, in an additional coil for each coupling member and in the circuits for alternating switching of the assignment of the data pulses to the two coils of the coupling links, that is, in measures that do not require any additional Introduce moving parts into the mechanical adjustment cable of the printing unit. Furthermore, the individual coupling members with all moving parts assigned to them completely from the drive shaft uncouple so that only the absolutely necessary for setting an actuator to be operated Parts have to be moved, but not parts that become actuators that remain at rest belong. The result of all this is that the multiple use of the shaft speed possible increase in the working speed can be made optimally usable and that with the invention trained high-speed printing units easily printed one hundred characters per second without wear or tear even after many thousands of hours of operation even show signs of failure.

The coupling members suitable for the purposes of the invention can be designed in various ways be. It is preferably provided that each coupling member is one on the intermittently driven Shaft rotatable, in constant drive engagement with the associated actuator drive part contains as well as two coupling parts arranged on both sides of it in a rotationally fixed manner on the shaft, which by means of a by the coils in the axial direction of the shaft displaceable engagement part in the successive Periods of standstill of the shaft can be alternately coupled to the drive part, with the coupling Positions of the coupling parts according to the angle of rotation between successive standstill periods are offset from one another. Two different embodiments falling under this principle are for the example of the use of two standstill periods per shaft rotation are described in detail below.

A rotationally fixed to the drive part is advantageous for adjusting the actuators of the summation gear the coupling members connected eccentric provided to each one with the Stellann des relevant actuator connected bearing ring is laid around. This inevitably always results in an exact one Adjustment position of the individual Stellanne, possibly also through with the drive part the coupling members interacting locking means be additionally secured in the uncoupled state and which is important for the accuracy of the setting of the type carrier. In addition, the eccentric disks grant the actuating arms have a slight initial acceleration or final deceleration, which is considerable contributes to increasing the smoothness and service life of the device. Works in the same direction also the further advantageous measure that the intermittently driven shaft of a with constant speed driven main shaft via an intermittently acting gear is that the driven shaft has a slight initial acceleration after each standstill period and given a small final delay before each standstill period and, for example, off one on known gear transmission with a drive pinion eccentrically attached to the main shaft.

Particular attention is paid to the formation of the summation gear so that it is also fully is adapted to the high working speeds. For example, adjusting wires or cables would be unsuitable. On the other hand, it has been found to be very advantageous that the summation gear is one of the number of digits the number of data pulses corresponding to each cooperating with a coupling member Contains actuating arms, which by means of the eccentric disks selectively in two representing the binary data values End positions are longitudinally displaceable and of which the actuating arm for the lowest number of positions with a rack is connected, with which an actuating arm designed with the same stroke for the second Number of digits stored gear meshes while each of the Stellanne for the following number of digits double stroke has like the previous one and each carries a gear in diametrically opposite Areas each with one also with the tooth

wheel of the preceding actuating arm or the next following actuating arm engaged, parallel to the actuating arms longitudinally displaceable two-sided intermediate rack is in engagement, with the second side of the arranged in the actuating direction behind the gear assigned to the highest number of digits Intermediate rack meshes a drive pinion with a stationary axis of rotation.

The type carrier is expediently a longitudinally displaceable and rotatable cylinder with in the longitudinal direction and types arranged in the circumferential direction on the cylinder jacket, for the longitudinal movement as well as the rotation of the cylinder is provided with a separate summation gear, the output pinion of which selects the cylinder via an intermediate gear. adjust tiv in the longitudinal direction or in the circumferential direction. The print hammer is preferably driven by means of an actuating arm of the print hammer arranged on the main shaft scanned control disk, which synchronized with the standstill periods of the intermittent shaft Control surfaces ensure that each printing process is exactly within the individual standstill periods is carried out.

These two measures help to ensure that even at high working speeds error-free character print is guaranteed.

Further details of the invention are provided below explained in more detail in exemplary embodiments with reference to the drawings. In these represents

F i g. 1 an embodiment of the invention Device in a perspective view, FIG. 2 shows a section in line 2-2 of FIG. 1,

F i g. 3 shows an embodiment of a coupling used in the device according to FIG Detail,

F i g. 4 the view of another embodiment of such a coupling,

F i g. 5 shows a section in line 5-5 of FIG. 4, fig. 6 shows a section in line 6-6 in FIG. 4, F i g. 7 is a view of a detail of FIG. 4,

F i g. 8 is a perspective view of part of FIG. 4th

In the embodiment according to FIGS. 1 to 3 a shaft 3 is provided, which is driven by an electric motor 1 via a gear 2 with a toothed wheel and toothed drive belt at a constant predetermined speed. A pinion 4 is mounted eccentrically on one end of the shaft 3. This pinion 4 is permanently connected via two intermediate gears 6 and 7 to a drive gear 8 which is fastened on a shaft 9 and transmits rotational movements to the shaft 9. The gear 6 is kept in constant engagement with the pinion 4 by a connecting member 11 in the form of a pivot lever with two stub axles on which the wheels 4 and 6 are mounted centrally. Similarly, the constant engagement of the gears 6 and 7 is ensured by a connecting member 14, one end of which is mounted on the stub axle 13 of the gear 6 and the other end of which is pivotably attached to a shaft 16 around which the gear 7 also rotates.

The consisting of the gears 4, 6 and 7 and the connecting links 11 and 14 of the Device forms an arrangement for intermittently rotating the shaft 9 with a predetermined Speed relative to the shaft 3. To simplify the explanation, in this case For example, assume that shaft 9 is driven at half the speed of shaft 3 will, d. This means that the shaft 9 rotates 180 ° when the shaft 3 rotates through 360 °. Furthermore, it is achieved by the unit formed from the gears 4, 6 and 7 that the shaft 9 remains at rest for approximately one eighth of a cycle of rotation, one cycle of rotation represents the rotation of the shaft 9 by an amount of 180 °. So if wave 3 with rotates at a speed of 6000 revolutions per minute, the shaft 9 rotates at 50 revolutions per second. One complete revolution takes place in one fiftieth of a second, so that a cycle of rotation takes up a hundredth of a second. Since the wave 9 during one eighth of each cycle is held stationary, consequently is the actual time of the standstill an eighth hundredth of a second. During this time interval takes place in an even below discussed in more detail the selection of the types to be printed.

The operation of the drive arrangement with the gears 4, 6 and 7 is already known from the Article by S. Rappaport, "The Three Gear Drive," Product Engineering, January 1950, p. 120 to 123. However, the invention is not limited to the use of this particular embodiment shown the drive arrangement between the shafts 3 and 9 is limited. Rather, it can be used as a drive arrangement also the type of triangular shape described in U.S. Patent 2,859,816 (John H. MacNei 11) Serve cam with constant diameter. Basically just by training the Drive connection between the shafts 3 and 9 ensure that the shaft 9 is intermittent is driven and remains at rest during part of each rotation cycle. This can the control of the adjusting device for the adjustment of the type carrier relative to the print hammer take place during a period in which any rotational movement is interrupted, causing signs of wear can be reduced significantly. Furthermore, the drive arrangement used must, also to reduce wear, have a relatively low initial acceleration and deceleration. These demands are fulfilled both in the illustrated drive arrangement and in the type of triangular cam.

By means of the adjusting device, which has already been briefly mentioned, a certain type of print is placed on the type carrier 17 brought into position relative to a print hammer 18. The type carrier 17 consists of a cylinder 19, on which the individual types are arranged in eight rows and eight columns, so that a total of sixty-four individual types are distributed around the circumference and along the length of the cylinder. A part the adjusting device drives the cylinder 19 to rotate about its axis and thus causes the selection that horizontally extending row which is to be scanned by the hammer 18 in each case. Simultaneously the cylinder 19 can be moved in the longitudinal direction by another part of the adjusting device in order to bring one of the gaps running in the circumferential direction into the line of the hammer 18. In this way, cooperating Ro-

and the gear 21 holds in a central position in which the gear 21 is disengaged from the Shaft 9 is located. However, the spring is not of particular importance for the operation of the device. Instead of the spring, the return to the center position can also be achieved magnetically, and it is even possible to forego returning to the middle position. In the latter case the coupling of the gears is maintained between the individual rotation cycles of the shaft 9, only when a decoupling of the gears is required, a shift of the Gears is made relative to the shaft. In the case of the solenoid 33, the two can also

tion and translation of the cylinder 19 brought a specific one of the sixty-four letters into the line of action of the hammer 18.

To that part of the adjusting device used for the translational displacement of the cylinder 19 hear three gears 21, 22 and 23, each of which is displaceable along the shaft 9. These three gears are freely rotatably mounted on the shaft 9, so that they do not under normal circumstances with the Rotate shaft 9. As, however, especially from Fig. 3 io for the example of the gear 21, each of the gear 21 to 23 can be coupled to the shaft 9. For this purpose, the shaft 9 is in the area of each of the gears 21 to 23 with two diametrically opposed Pins or small, outwardly protruding 15 counter-rotating coils through a polarized magnet lift 24 to 26 provided. Within the (behavioral coil to be replaced in which the direction of movement nismäßig wide) hub 27 of the gears in question runs parallel to the shaft 9 a continuous Slot 28, the cross-section of which is dimensioned such that one of the pins 24 or 26 is received flush men can be. In the in F i g. 3 the position of the shaft 9 shown, the pin 24 comes in a to the left directed movement of the gear 21 with the slot 28 in engagement, so that upon subsequent rotation the shaft 9, the gear 21 is taken 25. If, on the other hand, the gear 21 is shifted to the right becomes, the massive edge surface of the hub rests against the pin 26 and thus limits the movement the hub and the gear, without a driving connection between the shaft 9 and the 30, a group of solenoid-operated, in opposite directions Gear comes off. The clutch position can be reversed when the actuating directions are rotated by 180 ° of the shaft 9 in FIG. 3 the reverse is true. break down the selectively the intermittently driven

The in F i g. 3 described for the gear 21 shaft 9 with the individual actuators of a sum configuration This is not only repeated with the quantity gear coupling, but also with the longitudinal gearwheels22 and 23, but also with three further 35 position of the pressure cylinder 19 causes. This sum gears 29, 31 and 32, which relate to the part of the setting gears, will be explained in more detail below.

of the armature is determined by the polarity of the current supplied to the magnet. The ones described above Variants do not have any significant changes in the basic characteristics the device result.

The gears 22 and 23 and 29, 31 and 32 are assigned the same actuation units as the Gear 21. The solenoids of these further actuation units are shown in FIG. 1 with 39, 40, 41, 42 and 43, their anchors and adjusting forks have no reference symbols.

The three clutch gears 21 to 23 form together with their associated actuation units

include device that the rotation of the cylinder 19 relative to the hammer 18 worried. The order the gears 29, 31 and 32 and the pins 24 and 26 on the shaft 9 is designed in the same way like the arrangement of the gears 21, 22 and 23 with their associated parts.

Each of the gears 21 to 23 as well as 29, 31 and 32, hereinafter also referred to as "clutch gears" are referred to, an actuation unit is assigned that the gear wheels for coupling or uncoupling moves along the shaft 9. These operating units consist essentially of the same as on Example of the gear 21 in FIG. 1 to 3 can be seen from a solenoid 33 with two in opposite directions Actuating devices acting coils and a common, displaceable armature 34, which is provided with an adjusting fork 36. The adjusting fork engages around the two sides of the with fingers 37 Gear 21. Thus, when the left coil of solenoid 33 is energized, (refer to the illustration in Fig. 1 to 3) the armature 34 is moved to the left, the adjusting fork 36 in the same direction entrained and consequently the gear 21 also shifted to the left, it being in the already described Way is coupled to the shaft 9. The opposite occurs when the right coil is excited of the solenoid 33 a shift of the gear 21 to the right, which in the position of Fig.3 to no coupling of the gear with the shaft 9 leads.

A spring 38 is expediently provided which connects the unloaded adjusting fork 36 and thus the armature 34 A gear 44 which is arranged in a rotationally fixed manner on a shaft 46 is in engagement with the clutch gear 21 is. The shaft 46 also carries an eccentric disk 47, around the circumference of which a rotatable one Bearing ring 48 is wrapped around. When the gear 44 and thus the shaft 46 rotate, the eccentric disk driven in rotation and thereby causes an up and down movement of the Ring 48 and a vertical Stellannes connected to the ring 49. The arrangement is here taken so that the ring 48 and the arm 49 connected to it are either in an upper end position or are in a lower end position, d. That is, the eccentric disk 47 has its center of gravity either just above or just below the axial center line of the shaft 46. As a result the maximum vertical displacement of the arm 49 is achieved during each cycle of rotation of the shaft 9, provided, of course, that gear 21 is connected to the shaft during the cycle in question is.

The actuating arm 49 carries at its lower end a gear 51, which at diametrically opposite Places with vertically displaceable racks 52 and 53 is in engagement. The rack 53 is when the gear 51 rotates (either as a result of a stroke of the actuating arm 49 or as a result of displacement the rack 52) moves up and down. The rack 52 for its part still meshes with one Gear 54, as shown, on the opposite side of gear 51 or alternatively such that the two toothed engagement surfaces of the

9 10

Toothed rack 52 at a right angle to one another has the same stroke as the actuating arm 57, it lying differently. The representation in FIG. 1 is only, however, due to the gearbox training chosen because of the better visibility. The double stroke movement on the rack 53 via gear 54 stands with a further rack 56 carry so that the cylinder 19 is a shift around in engagement, namely at a point that experiences the one 5 two gaps. When rotating only the eccentric grip point with the rack 52 diametrically opposed to 47 finally the "third" actuating arm 49 with the overrides. A movement of the rack 56 has a gear 51 from a vertical movement, as a result Rotation of the gear 54 results in a rotation of the double eccentric stroke twice the hud Gear 54 causes a movement of the teeth bes of the actuating arms 57 and 63 and which is thus rod 52, and a movement of the rack 52 ι ο a displacement of the rack 53 by four strokes to a rotation of the gear 51st steps causes, so that the cylinder 19 by four

The rack 56 is fastened to an actuating arm 57 with columns relative to its starting position, which is via a bearing ring 58 - in which is added. Further stroke stages of the rack 53 are related with the eccentric 47 and the give themselves by joint actuation of several Ring 48 already described - with an Ex-15 adjusting arms. So does an actuation of the first zenter59 is connected. The eccentric 59 is on an actuating arm 57 together with the second actuating arm 63 Shaft 61 attached, on which also a gear 62 reanalized a movement of the cylinder 19 by three columns which is in engagement with the coupling to the hammer 18. An actuation of the third Lungs gear 23 is located. The gear 54 is on the un-actuating arm 49 together with the first actuating arm 57 The lower end of an actuating arm 63 is mounted, which analogously causes a movement of the cylinder 19 by five Via a ring 64 by an eccentric 66 actuated columns relative to the hammer, and an actuation of the is. The eccentric 66 is on a shaft 67 on the third actuating arm 49 together with the second brings, on which a gear 68 is still located- actuating arm 63 causes a displacement of the cylinder det, which is engaged with the gear 22. The one by six columns opposite the hammer 18. One Shafts 46, 61 and 67 are separate and independent »5 simultaneous actuation of all three actuating arms 57, rotatable. They can be mounted independently or 63 and 49 cause the cylinder 19 to move z. B. be designed as coaxial hollow shafts that have around seven columns compared to the hammer 18. The can be rotated depending on each other, but the eighth column of the cylinder is selected together Have bearings. fold in that none of the three adjusting arms 57, 63

The stroke of the eccentric discs 59 and 66 is 30 and 49 is moved, whereby the cylinder 19 in

the same, while the stroke of the eccentric discs 47 remains in its previous position. This situation lies

twice the stroke of the eccentric disk 59 or before if a letter is in the same column

66 is. This configuration allows the preprint to be made.

summation gear described standing a longitudinal To actuate the three actuating arms of the summation shift of the cylinder 19 by up to eight stages, 35 transmission will first be the three digits d. H. a selection of eight clutch solenoids 33, 39 and 40 which correspond in the circumferential direction running columns of the cylinder 19. The actuation according to the binary code value "0" or "1" the summation gear can be excited according to a bi. In doing so, it is necessary to stimulate the när codes are made with three digits, with each clutch solenoids operating in opposite directions Digit position of an actuator (e.g. to make parts 44, 40 directions reversible in order to achieve 46, 47, 48, 49 and 51) and a coupling member (that is, when an actuator arm is set (e.g. 49) z. B. the parts 33, 34, 36, 37, 21, 24, 26, 27 and 28) a certain code value a clutch of his assigned. Depending on the setting of the individual clutch gear (e.g. 21) with the drive actuators the rack 53 experiences, which takes place as "shaft 9 when this actuating arm is adjusted" of the summation gear can be viewed, 45 is, and a decoupling of its clutch one gradual, different stroke. With the gearwheel takes place if the actuating arm has already been done beforehand This rack 53 meshes with another gear 69, which has been set to this code value. Without which is thus rotated by a certain angle, such a reversibility of the clutch solenoids whose size of the transmission ratios would be the repetition of the same code value System depends. The gear 69 remains on a shaft 50 clutch and consequently the adjuster 71 stored, which carries a gear 72 that are wrong with the development of the actuator arm. This could be done Teeth of a connected to the cylinder 19 z. B. also prevent that all adjusting rack 73 is engaged. The arrangement is poor before selecting a next character initially hit in such a way that when the tooth is rotated return to their starting positions, but results rades69 corresponding to a stroke stage of the rack 55 then has a very detrimental effect on the 53 the rack 73 by an amount in the direction of construction costs and the operating speed of the direction is shifted, that of a movement of the cylinder pressure value.

ders 19 by one column relative to hammer 18 For reversing the clutch solenoids 33,

speaks. 39 and 40 a »code reversal switch« is provided.

If, for example, only the "first" actuator arm 57 with 60 hen, which determines the position of the shaft 9 in the individual the rack 56 scanned by 180 ° rotation of the eccentric standstill periods and a control signal lieters 59 is raised, this movement causes over finished, according to which the code values dardas Gear 54, the rack 52 and the gear providing data pulses either to one or the other 51 a stroke of the rack 53 by one stroke stage, so the other coil of the clutch solenoid is applied that so the cylinder 19 via the gear 69, which will be 65, consequently the same data pulse depending on Gear 72 and the rack 73 shifted the clutch solenoid by one column position of the shaft 9 will. If only the eccentric is rotated, neither left nor right is not actuated. This 66 leads the "second" actuating arm 63 with the gearwheel code reversal switch contains in the example shown

11 12

play a scanner 74 in the form of a semicircular shape 87 or 93 and a bearing ring 88 or 92 an adjustable disk 76, which is arm 89 with gear 96 or a rack and pinion at the end of the shaft 9 and depending on the rotational position the shaft 9 an arm 94 is actuated. The rack 94 is located follower pin 77 raises or lowers. The follower pin in engagement with the gear 96 at the end of the actuator cooperates with a spool 78, e.g. B. 5 poor 89. This gear 96 is still in the single magnet on the principle of a variable handle with a rack 97. The actuating arm 86 carries reluctance such that in the position shown at its lower end a gear 98, which is the shaft 9 Re- scanned by the coil 78 is in engagement with the rack 97 and has a certain value with a fluctuation and, according to Dre, the rack 99 is located.

hung the shaft 9 by 180 ° this value increases. On io the rack 99 forms the output of the sum in this way signals are generated in the coil 78 by quantity gears for the rotation of the cylinder 19 grooves which extend in the longitudinal direction and which support the control signals for selecting the hand shaft 102. On this shaft there is also ken or right coil which are clutch solenoids. 15 of the cylinder 19 is arranged. With this arrangement

The code reversal switch also includes both, it is possible to connect the cylinder 19 with the shaft 102

turn the diametrically opposite coupling pin 24 and at the same time move it in the longitudinal direction by

and 26 to move the clutch drive on both sides of the hub 27 via the rack 73 without

Gears. This is based on FIG. 3 explains in more detail that the engagement of the rack 99 is disturbed. That

tert. It is assumed in this illustration that ao transmission ratio between the rack 99

the actuating arm assigned to the gear 21 and the gear 101 is selected so that at

its lowest position, which is a binary displacement of the actuating arm 94 from an end position

May correspond to "1". If a data pulse is now transmitted into the other of the cylinders 19 by a horizontal

arrives, which in turn indicates a binary "1", then rotates the series running down the valley. A movement of the

the gear 21 must be decoupled from the shaft 9 35 actuating arm 98 causes a rotation accordingly

be to the actuating arm in its lowest position of the cylinder by two rows and one actuation

to leave. To do this, the right coil of the coupling arm 86 must be shifted four rows. Through appropriate

lungssolenoids 33 are excited, since only then a combination of the movement of the actuating arms 86, 89

Connection between the hub 27 and the shaft 9 and 94 can thus be any of seven rows on the

is prevented. So the control signal from the 30th cylinder must be detected while the eighth row

Coil 78 ensure that in the illustrated Po- in turn results in that the cylinder is not off

In the position of shaft 9, all data pulses with a value of "1" of its existing position are turned out,

to the right-hand coils of the clutch solenoid - The two parts of the actuating device, one-

ide can be created. If on the other hand, on the one hand to move and on the other hand to twist

starting from the illustration of FIG. 3, a binary 35 hen of the cylinder 19, each of the four-

"0" is to be set, then the signal becomes sixty and sixty individual characters on the cylinder in

the left coil of the solenoid 33, and which bring the pressure position with respect to the hammer 18-

Hub 27 is moved to the left so that it is in line with the gene by the crossing point between one of the

Shaft 9 comes to the coupling. After the next eight lengthways rows and one

Half rotation of the shaft 9 is the situation by exactly 40 of the eight columns running in the circumferential direction

swept. The pin 26 is now opposite being selected. The correct setting in each case

slot 28, and therefore the left spool of the cylinder must be held by pawl rollers 103

Solenoids are energized when the actuating arm is supported in this way on the drive gears 44,

Position should remain, or the right coil when the 68, 62, 79, 81 and 82 of the summation gear act,

Actuating arm must change its position. Therefore, it must now be 45 that these gears do not have an intermediate position.

can take more the control signal from the solenoid 78 for it, but basically only in

ensure that the data pulses from the value "1" move to the one position in which the role of the pawl

left-lying coils and no longer on the right-hand successive surfaces of two adjacent

lying coils of the clutch solenoids applied ter teeth of the gear detected. Pointed out

will. After the third half-turn of the shaft 9 is 50, however, it is assumed that the direct action of the pawl

again the one shown in FIG. 3 roll forward onto the teeth of the drive gears in FIG. 1

act etc. only for the sake of simpler drawing

The representation used to rotate the cylinder 19 and to illustrate the radio part of the actuating device comprises a summation gear principle is selected. Preferably, in the practice with actuators and coupling members, a pawl arrangement is used which has the same structure and the same effect. 4 to 6 for a second exemplary embodiment show how the translational part of the adjusting device is made and that with a double heart-shaped device. The coupling cam 122 is part of the coupling elements. As a result, gear wheels 29, 31 and 32 as well as the clutch vibrations that occur in the case of the FIG. 1 shown solenoids 41, 42 and 43, which in the same way are undoubtedly controllable to a considerable extent as the solenoids 33, 39 and 40. To occur, the gears 79, 81 and belong to the actuators 82, adjustment of the cylinder even safer,
each assigned to the gears 29, 31 and 32. In order to achieve the best possible results, net must be. The gear 79 is on a shaft 83 be the clutch gears, such. B. the gear 21, fixed and adjusted via an eccentric 84 and 65 with respect to the associated drive gears, a bearing ring 90 and an actuating arm 86. Corresponding, for example, to the gear 44, sufficient width, the gears 81 and 82 each have a shaft 85, so that the teeth of the drive gears, or 91, are connected with which via an eccentric regardless of which of the three possible positions

13 14

lungs occupy the clutch gears, completely face to face on the cylinder and consequently

dig stay engaged. there is no pressure even when the hammer is activated

The print hammer 18 can be driven by itself.

be, but the drive must be synchronized with the rest of the 4 to 8, a second embodiment is made part of the device. For Ausfüh- 5 example shown, which particularly relates to the Ausrungsbeispiel the F i g. 1, a formation of the selectively couplable drive transmission cam disk 104 is arranged on the shaft 3, which is detected by a roller movement from the drive shaft to the individual actuating elements 106 . This role 106 in turn is related to poor of the summation gear,
mounted on an arm 107 which is attached to a shaft 108 of the drive shaft 9 of FIG. 1 corresponds to in fastened and by a spring against the curves io F i g. 4 to 8 a shaft 116 which is pressed with grooved disc. This shaft forms the pivot axis and carries two wedged disks 117 and 118 , axis of the arm 107. It carries the print hammer 18 Between these two there is a function and rotates when the part 119, which is rotatably mounted on a hub 121 , rotates , Arm 107, so that the print hammer is wedged on the shaft 116 accordingly. Which is swiveled. The cam disk 104 is circular except for the hub 121 and extends over the two ends of the one recess 114 and con-part 119 and is arranged with the disks 117 centered on the shaft 103 . This makes and 118 come into contact. The functional part 119 entder arm 107 in the course of one revolution which holds on one side a curved shaft 3 except in the area of the recess 114 in the section, which has the double heart-shaped in FIG. 1 held position shown. In the area ao cam plate 122 represents. This cam disk of this recess, on the other hand, swivels the arm 107 is detected by a pawl roller 123 , which gives the downward, which is a partial rotation of the shaft 108 and the functional part a precisely defined standstill position with a swiveling movement of the hammer 18 . Towards the middle, the functional part changes into a sequence, so that the hammer goes over against the cylinder section in the form of an eccentric 124 and hits the 19 . he is on the other side of the functional part

What is important here is such an arrangement of the curve - finally a section in the form of a coaxial disk 104 on the shaft 3 that the hammer 18 has a guide surface 127, the diameter of which is smaller than that of the remaining area of the part 119 only after the entire adjustment has been completed .
ganges is actuated for the character in question and parallel to the shaft 116 extends through which the pressure then takes place in the time in which the shaft 9 30 functional part 119 a pin 128, which is approximately the standstill. This results in a particularly clear print, the length of the hub 121 . The opening provided in the part 119 for the opening provided when the hammer is actuated while the pin 128 is being picked up, the movement of the cylinder is a blurring of the arranged so that a semicircular print-out can occur. The standstill period of the recess in the guide surface 127 is formed, cylinder 19 and thus the working period of the pressure 35 ie the center line of the recess for the pin hammer 18 extends over the one eighth of a 128 is on the guide surface. That part of each cycle of rotation of the shaft 9 in which the shaft pin 128 does not move in the area of this recess. During this working period in the guide surface 127 , in turn the hammer is energized to have a recess 129 , the bottom of which prepares the guide surface for the selection of the next character for the printing 40 again to form a closed cylinder. Immediately after the work period, the coat was added. A ring of the hammer is then placed around the guide surface, the shaft 9 is then placed over the gear 131 , which thus engages in the recess 129 drives with the wheels 4, 6 and 7 of the pin 128 driven in rotation and otherwise with the folding, whereby that movement of the cylinder 19 catches the guide surface 127 is in contact. This is carried out, which is required for the setting of the 45 ring 131 is via an actuating arm 132 with the most selected character. Armature 133 of a two-coil clutch solenoid

To get the print hammer connected at line 134. At an excitation of one of the two od chenzwischenräumen. Like. Remains unactuated, coils of the solenoid 134 is actuating arm beyond the roller 106, an electromagnetic lock 132 and thus the pin 128 to the left or right means 112 provided an anchor 111 with 50 has a recess 109 relative to the position shown in the drawing. When this locking mechanism is pushed in, depending on which of the coils is excited, the free end of the disk 117 has an opening 136 which, with arm 107 , engages in the recess 109 so that the pin 128 is then aligned. when the functional part is independent of the rotation of the cam 104 119 in the position shown. The disk of the arm and thus the print hammer against a 55 118 likewise has an opening 137 which is blocked when pivoting. When the locking pin 128 is locked, when the part 119 is turned 180 ° in the opposite direction, the arm 107 is released, with the shaft 116 pivoting relative to the position shown, the roller 106 again pivoting around the contour of the curve. If consequently, for example, the left disk 104 can follow and a coil of the solenoid 134 is connected to the armature 111 as shown in FIG. 4 is excited, brought stop 113 the downward movement of the 60, the pin 128 moves to the left and enters the arm 107 limited. So if during an Ar opening 136 of the disk 117 a. Since the disk is not to be printed on the working cycle, the shaft 116 remains wedged, the locking device 112 rotates when it is rotated, and thus the part 119 of the shaft 116 rotates with it. In doing so, the hammer causes unactuated. As an alternative to this solution of the eccentric 124 on the part 119, a downward movement can also be provided, the hammer stan- 65 of an actuating arm 138, which is actuated via a bearing ring 126 and engages interspaces under pressure on the eccentric and an element 139 enteine movement of the cylinder in such a position corresponding to one of the gears 51, 54, 96 or 98 to be taken into account in the hammer an empty or one of the racks 56 or 94 in FIG. 1

wearing. If, however, in the one shown in Fig.4 Position the right coil of the solenoid 134 is energized, the arm 132 tries the pin 128 after to the right, but the pin then comes against the solid surface of the disk 118 to the plant and does not intervene in the disc. There is therefore no coupling of the functional part 119 with the shaft 116, and the pawl roller 123 holds the portion 119 during rotation of the shaft 116 fixed in the position shown. If, however, the right coil is used in the next working cycle of the solenoid 134 is energized, the pin 128 now enters the opening 137 of the disc 118 and causes the coupling of the shaft 116 with the functional part 119.

When using the embodiment according to FIG. 4 to 8 can be the drive via gear pairs, such as B. the clutch gear 21 and the drive gear 44, can be eliminated, whereby due to the smaller dimensions the device is particularly well suited for high working speeds. These The fact is of considerable importance when one takes into account that the printing mechanism is running at a printing speed at least 100 characters per second is used. as

In an overall device of the in FIG. 1 find six of the types shown in FIGS Coupling members shown use, in accordance with the six actuating arms in the 1. These coupling members, which then take the place of the coupling and drive gears shown in FIG including the associated parts, are expediently arranged so that the Discs of successive coupling links rest against one another and all coupling links by nuts are pressed together at the ends of the shaft. Through the hub 121 that holds the disks 117 and 118 holds out of connection with the functional part 119, a relative rotation remains of the part 119 with respect to the disks and the shaft 116 ensured. The remaining part of such an overall view corresponds to FIG. 1.

As already indicated above, the connection between the shafts 3 and 9 must be designed in this way be that slight acceleration or deceleration exerted on the various elements will. This measure is further improved by a suitable design of the eccentric disks. The eccentric disks initially cause a slow movement of the actuating arms, which is then followed by an increase in the speed of movement.

Among the possible variants, it should be particularly emphasized that the two parts of the adjusting device do not necessarily have to be driven by a common drive shaft 9. The wave 3 Rather, it can act on two "half" drive shafts arranged parallel to one another, for example, and this configuration can be advantageous if the printing unit does not have the length of the common Wave 9 may assume, but the greater width due to the two parallel "half" May have waves.

Claims (10)

Patent claims: 1. Impulse-controlled high-speed printing unit, its type carrier by means of a mechanical summation gear is adjustable relative to a print hammer, the setting of the actuators of the Sum gear is carried out by an intermittently driven drive element, which during its standstill periods via solenoid-operated coupling elements, which can be triggered by data pulses are, can be selectively coupled to the actuators, characterized in that the drive element is one with an even-numbered Number of standstill periods per revolution driven shaft (9) is provided and the Coupling members (z. B. 33, 36, 21, 24, 26, 28) with two in opposite directions of actuation working coils (z. B. 33) are designed such that the shaft in each standstill period only ever in one of the two actuation directions with the actuators (e.g. 44, 47, 48, 49) can be coupled, and these coupling operating directions from standstill period to standstill period reverse, being by one according to the shaft position in the successive Control signal derived from standstill periods the assignment of the data pulses to the two coils of each coupling member is switched alternately. 2. High-speed printing unit according to claim 1, characterized in that each coupling member (e.g. 33, 36, 21, 24, 26, 28) a rotatable on the intermittently driven shaft (9), in constant drive engagement with the associated actuator (z. B. 44, 47, 48, 49) stationary drive part (z. B. 21) as well as two coupling parts arranged on both sides thereof in a rotationally fixed manner on the shaft (z. B. 24,26), which can be displaced by means of a through the coils in the axial direction of the shaft Steep engagement (e.g. 27, 28) in the successive standstill periods of the shaft alternately can be coupled to the drive part, the coupling positions of the coupling parts according to the angle of rotation between successive standstill periods are offset. 3. high-speed printing unit according to claim 1 and 2, characterized in that each coupling member as a drive and engagement part on the intermittently driven at intervals of 180 ° Shaft (9) rotatable and actuated by means of an adjusting fork operated by the coils (e.g. 33) (36) axially displaceable coupling gear (e.g. 21) is provided, the hub of which (e.g. 27) has a longitudinal groove (z. B. 28), which alternates with two coupling parts in the form of on the Shaft attached to both sides of the clutch gear, offset by 180 ° to each other pins can be brought into engagement (Fig. 3). 4. high-speed printing unit according to claim 3, characterized in that the clutch gear (z. B. 21) constantly meshes with a drive gear (z. B. 44), which together with a Eccentric disc (z. B. 47) is attached to a shaft (z. B. 46), with the eccentric disc a bearing ring (e.g. 48) connected to the actuator arm (e.g. 49) of the relevant actuator is lying around. 5. High-speed printing unit according to claim 2, characterized in that for each coupling member of the drive part one on the intermittent driven shaft (9) rotatably mounted Hub body (119) in which an engagement part in the form of a pin (128) is arranged axially displaceably near the circumference and, as a coupling part, two disks (117 , 118) are provided which each have a hole (136, 137) offset by 180 ° to one another for engagement with the pin (FIGS. 4 to 8). 6. High-speed printing unit according to claim 5, characterized in that on the hub body (119) with the shaft (9) coaxial, by the pin (128) penetrated guide surface (127) is arranged, on which a means of the coils (z. B. B. 134) axially displaceable adjusting ring (131) engaging in a recess (129) of the pin is mounted. 7. High-speed printing unit according to claim 5 and 6, characterized in that each hub body (119) is designed on part of its length as an eccentric disc (124) around which a bearing ring (126) connected to the actuating arm (138) of the actuator in question is wrapped . 8. High-speed printing unit according to one of the preceding claims, characterized in that the coupling members engage in the decoupled position against rotation by spring-loaded locking means (103 or 123) which engage in the gear teeth or in particular with the coupling part of the coupling members connected cam disks (122) are secured. 9. High-speed printing unit according to one of the preceding claims, characterized in that the summation gear contains a number corresponding to the number of digits of the data pulses of actuating arms (z. B. 57, 63, 49) interacting with a coupling member, which by means of the eccentric disks (z. B. B. 59, 66, 47) are selectively longitudinally displaceable into two end positions representing the binary data values and of which the actuating arm (57) for the lowest number of digits is connected to a rack (56) with which an actuating arm (63 ) gearwheel (54) mounted for the second number of digits meshes, while each of the actuating arms (e.g. 49) has twice the stroke for the following number of digits as the previous one and in each case carries a gearwheel (e.g. 51), which in diametrically opposing areas each with one also with the gear wheel of the preceding actuating arm or the next following actuating arm in engagement, parallel to the actuating arms longitudinally displaceable two intermediate rack (e.g. B. 52) engages, with a drive pinion (69) meshing with a stationary axis of rotation with the second side of the intermediate rack (52) arranged in the adjusting direction behind the gear assigned to the highest number of positions. 10. High-speed printing unit according to one of the preceding claims, characterized in that that the intermittently driven shaft (9) is driven by a constant speed The main shaft (3) is driven via an intermittent transmission, which is the driven Wave a slight initial acceleration after each standstill period and before each Standstill period given a slight final delay and, for example, from a known per se Gear drive (4, 6, 7, 8) with a drive pinion eccentrically attached to the main shaft (4) exists. Considered publications:
British Patent No. 662160;
U.S. Patents Nos. 2090920, 2892031,
2984177. 1 sheet of drawings 809 638/1647 11.68 © Bundesdruckerei Berlin