US3232596A - Spring and shock absorber structure - Google Patents

Description

Feb. 1, 1966 E. F. KLEINSCHMIDT ETAL 3,232,596

SPRING AND SHOCK ABSORBER STRUCTURE Original Filed July 24, 1959 2 Sheets-Sheet 1 INVENTORS EDWARD I. KLE/NscHM/DT Hun/m; A. ANDERSON (/0 asp F OHM/Lama BY M, @MWM ATTORNEYS Feb. 1, 1966 E. F. KLEINSCHMIDT ETAL 3,232,595

SPRING AND SHOCK ABSORBER STRUCTURE Original Filed July 24, 1959 2 Sheets-Sheet 2 w M TT 4 3 N0 3 0 3! W K W VI W WMW N 3% w W 5 \I.N I, H1 \P INN a 1 M W 1 .l I y JJxUJI/AJMVFQ 0 3 I v F J H N R H AD mus E fl W ATTORNEYS United States Patent SPRING AND SHGCK ABSGRBER STRUCTURE Edward F. Kleinschmidt, Fort Lauderdale, Fla, and

Hilding A. Anderson, Lake Zurich, and Joseph F. Chinlun-d, Northhroolr, 111., assignors to SCM Corporation,

New York, N.Y., a corporation of New York Original application July 24, 1959, Ser. No. 829,446, now

Patent No. 3,150,235, dated Sept. 22, 1964. Divided and this application Nov. 22, 1963, Ser. No. 325,705

7 Claims. (Cl. 267-4) This application is a division of co-pending United States application Serial No. 829,446, filed July 24, 1959 and now Patent No. 3,150,235. This invention pertains to shock absorbers for mechanisms related to telegraph apparatus such as receiving printer-reperforator combinations capable of recording visual representations of corresponding characters at any speeds up to at least 4500 operations per minute.

Although there are presently known many high speed printers as well as high speed reperforators, there are no printer-reperforations performing both functions at speeds higher than 600 operations per minute (368.1 operations per minute being the normal speed for telegraph apparatus). The primary purpose behind the development of the present invention was to provide a printer-reperforator apparatus that would punch a coded message on a tape, print this same identical message on one edge of the tape, and to accomplish both of these functions at the exceptionally high speed of 4500 operations per minute (this is 75 operations per second) and still retain reliability of operation over extended periods of time. It was desired to develop and construct such a high speed typing reperforator as a production model for use in fixed plant and military installations. In accomplishing this development, it was determined that selection and operation of the printing and perforating functions would be mechanical under the control of an electronic signal receiver and controller.

To realize the extremely high speed mechanical operations, the mechanical printer-reperforator structure utilizes the transfer of energy between the structural components by elastic impact and reaction forces in each of the high speed motion transmitting mechanisms. The initial impetus is provided from rigid code rod elements mounted in rotating wheels, the force of which is transferred to operating elements which perform mechanical functions of printing-reperforating and tape feeding. Because of the extremely rapid selection and repositioning of the code rod elements, this invention deviates from the normal practice of using a selected number of code elements having permutated notches or some other form of mechanical signal representation, each of which code elements corresponds to one of the signal impulse combinations of the Baudot code combination signal group. In this invention each of the Baudot codes is represented by an independent rigid code rod element and therefore we have thirty-two (32) of such rod elements. The code rod elements are selected by elastic impact plungers controlled by electro-magnets which receive signals from the electronic receiver selector and controlling unit. Elastic impact transfer of operational forces is correlated and coordinated with suitable shock absorbing means constructed in accord with this invention to prevent any vibratory or reaction bounce of the structural operating elements. In other words, once an element has undergone its mechanical function cycle, it must immediately stop its movement and be ready for a next operation.

The primary object of this invention resides in a novel highly effective element rebound steel ball type shock absorber assembly. In conjunction with this object, a

ice

further object resides in providing a plurality of shock absorber units in a compact block assembly.

Further novel features and other objects of this invention will become apparent from the following detailed description, discussion and the appended claims taken in conjunction with the accompanying drawings showing a preferred structure and embodiment, in which:

FIGURE 1 is a perspective partially sectioned view of the punching, printing and tape feeding components of a printer-reperforator utilizing the present invention and shown somewhat schematically for clarity;

FIGURE 2 is a schematic front view of the tape punch components with retracting bail and shock absorber block shown in section;

FIGURE 3 is a section view through the shock absorber bl-ock assembly seen in FIGURE 1;

FIGURE 4 is a top plan view of the shock absorber assembly block;

FIGURE 5 is a right-hand side elevation of the shock absorber assembly block of FIGURE 4;

FIGURE 6 is an enlarged and sectioned detail View of one of the individual shock absorber units located in the shock absorber block of FIGURE 4;

FIGURE 7 is an enlarged sectioned detail view of a modified shock absorber unit in which the steel balls are arranged in a different manner from that shown in FIG- URE 6; and

FIGURE 8 is a section taken on line FIGURE 7.

The complete exemplary printer-reperforator is disclosed in the aforementioned parent application to which reference may be had, if deemed necessary. FIGURE 1 illustrates a skeleton arrangement of mechanical printing and punching components to provide a general understanding of the utilization of the shock absorber devices.

The basic principle of operation for the mechanical punching, printing and feed functions of the reperforator 5i) resides in rotation of thirty-two (32) code rods past a reference point (or points having a common time base). Each rod has the mark element or elements of its representative character machined in as interference flanges. To facilitate the high speed aspect, the thirtytwo (32) code rods are separated and placed in two code wheels and there are sixteen (16) code rods per wheel. Within each code wheel the sixteen (16) rods are arranged in two groups, eight (8) code rods protruding from each 8-8 through end of each code wheel. Four code rod selector magnets actually control latches for spring 'biased selector plungers, one for each group of eight (8) code rods. Each selector plunger is reciprocable in a path parallel with the code rods and aligns with each code rod as the code rods are rotated past the plunger locations.

Each function (print, five-code punch assembly, feed hole punch, punch retraction and tape feed control) has mechanisms enabling operation by code rods in both of the two code wheels. A type wheel rotates above the print hammer, and the two code Wheels and the type wheel rotate at 3750 rpm.

Whenever an electronic controller, through a received code signal combination, actuates one of the selector magnets MM, MS, SS, SM, the associated selector plunger latch arm will be attracted by the magnet, releasing the plunger which moves to an interference condition with the desired code rod. The pop-out plunger hammer moves into the path of the selected rotating rod just before it arrives at its reference or selection point. This causes an impact between the pop-out plunger hammer head and the code rod head experiencing an elastic impact between the two elements with the result that both will be driven 0 away from each other. The pop-out plunger moves back plunger ready for its next release. The impacted code rod will be driven into the wheel, a distance of 0.05 inch, and will be secured by an associated latch located within the code wheel. In this latched position, the code rod interference flanges engage intermediate transfer arms to operate associated function mechanisms including print hammer, code punches, code punch retractors and feed release pawl. As the rotating wheel carries the code rod on around its path, an internal cam pulls the code rod latch away from the code rod and a second cam shifts the code rod slightly out of the code wheel into a non-interference, normal position ready for another impact positioning operation. The cycle of afo-re-described functions of a code rod require one revolution of the code wheel.

Tape feed is realized through a sprocket feed wheel which is kept under continuous rotational bias from a motor driven pulley wheel operating through a friction clutch, and a torsion spring drive rod. The tape feed sprocket wheel itself is retained against rotation by a feed release pawl and whenever an operation occurs, the feed release pawl is removed permitting the type wheel feed sprocket to rotate under torsion spring bias. The movement of the feed release pawl is timed to occur in less time than that required by the sprocket feed ratchet wheel to move one tooth (one space of the tape). Therefore the feed release pawl is always back in a position to engage the next tape feed sprocket ratchet tooth before the tape has been fed past its next position. An ink ribbon is carried on two spools (not shown) and can be power driven in either direction through a reversing clutch mechanism.

Drive power for the code wheels, the type wheel, the coincidence selector, the tape sprocket feed and ink ribbon 'feed is derived from an induction type motor.

The aforementioned portion of this description provides a brief explanation of the mechanical operation of printer-reperfcrator 50 and a more detailed description of the structure follows. The mechanical components are assembled on a base casting 242, a portion of which forms an oil reservoir 248. Two studs, only one being shown in FIGURE 3, project vertically in a front to rear aligned relationship and are firmly secured in the base of casting 242 to provide mounting support for a shock absorber block 580 and the punch assembly 610.

The aforedescribed oil reservoir 248 is located under the punch shock absorber block 580 and retains oil used in lubricating the code selector wheels. To accomplish this lubrication, two oil wicks 268 extend upwardly from the reservoir 248, diverge and pass under the positions which will be occupied by the code selector wheels. Oil wicks 268 are biased by leaf springs against the periphery of the associated code wheel and under each code wheel wick is located an oil drip plate 270. The lower ends of these two drip plates 279 are above the top of oil reservoir 243. I

Viewing the dual code wheel assembly from the front of the machine, as shown in FIGURE 1, the right-hand code wheel 282 will be rotating counterclockwise. The left-hand code wheel 284 rotates at the same speed but in a clockwise direction as indicated by the arrow. To accomplish this opposite rotation, a helical toothed gear (not shown) is secured on the right-hand code wheel shaft 292 behind the support rear wall 246 and the left-hand code wheel shaft has secured thereto a second helical toothed gear in meshed engagement with the helical gear on shaft 2292.. Both code wheels must rotate in unison, at the same speed and in opposite directions.

In accord with the principle of operation of this machine, type wheel 286 must also rotate at the same rotational speed as code wheels 232 and 284. Type wheel 236 is secured for rotation to a shaft 310 which extends to the rear and has secured thereto a helical gear, having the same diameter and the same number of teeth as the helical gears on code rod Wheels 282 and 284. Drive a power is transferred from one of the code wheel helical gears through an idler gear to the type wheel shaft gear.

The motor through a shaft 329 and a friction clutch, provides a rotational drive biasing force to the tape feed sprocket 324. Actually, shaft 326 is a music wire torsion spring as is described and claimed in the parent application.

Code wheels 282 and 284, their shafts, mounting components and gear assemblies are similar in detail, diifering only in the shapes of the individual code rods and in that the right-hand code wheel shaft 292 is the longer shaft, as has been previously described. The schematic representations shown in FIGURES l and 2 show the structural correlation between the two code wheels, intermediate impact transfer arms and the punches, print hammer, tape feed mechanism and punch retractors.

The body of each code wheel is a cylindrical block 394 through which pins can be driven into matching diametrical bores in the code wheel shafts to non-rotatably secure the cylindrical code wheel blocks to the drive shafts. Adjacent the peripheral portion of cylindrical block 394 are sixteen (16) axial through bores spaced at 22.5 equiangular positions. These axial bores constitute code rod receptacles or carriers. Around the cylindrical surface of the code wheel block 394 and formed circular, radially directed annular, combing grooves 404, 405, 4%, 407, 438, 4&9, 410, 411 and 412. For purposes of correlation in the functioning of this apparatus, the first groove 404 (rear groove) will be termed the tape feed groove; the second groove 495 is the code punch retractor groove; grooves 496-411 are punch grooves, 198 being the feed punch groove; and groove 412 is the print hammer groove. Alternate code rod bores 402 receive code rods inserted from opposite ends of the code wheel block to form two groups of eight (8) code rods, each of which rods will be located 45 apart.

The code rods are made of surface hardened steel. Each code rod includes a beveled impact head 442, a narrow positioning limit flange spaced slightly behind head 442, a front guide and interference land and a rear guide land. Between the front and rear guide lands are located various operating flanges and lands.

Seen in FIGURE 1, a series of impact transfer lever arms ride in the manner of a comb in each of the grooves 464-412 of both of the rotating code wheel blocks 394 and the transfer levers correspond to the various functions noted for the series of grooves 4tl4412. If a code rod has been positioned to an operative position Within the code block, any portion of that code rod which shifts into an interference position in an associated groove 404412 will impact the lever which rides in that groove and cause the lever to transfer the impact power to some associated mechanism such as the code punches and the print hammer. If any specific lever must remain idle during the transfer of the code symbol represented by the selected code rod 440, then that portion of the code rod 449 which would normally move into interference with a combing groove, in which the lever not to be actuated is disposed, must be eliminated. This is accomplished by removing desired ones of the interference flanges or a portion of the lands on a specific code rod. The code rods and code wheels are completely described in the aforenoted parent application. I

The code rod selector plunger latch and magnet release mechanism are only generally disclosed in FIGURE 1. All four (4) of the plungers, latches and magnets are essentially identical. The printer frame provides the mounting support for the magnets, latches and code rod selector plungers. Three (3) of the plungers are shown in the schematic representation of FIGURE 1, as markspace plunger 520, mark-mark plunger 521 and spacemar plunger 522. Each plunger 520 is made of cold rolled steel, heat-treated and phosphate-coated before a hardened steel ball 526 is secured in its end socket and in direct alignment with the circular path through which the code wheel rotates all of code rods 44%). The opposite end 532 of plunger 520 acts as a recoil abutment surface, and closely adjacent the recoil abutment end is an annular latch receiving recess. Magnet operated latches 548 coperate with the plunger recesses to hold and selectively release a plunger. It is seen that the two code wheels are arranged with their axes parallel and in side-by-side relationship. Between the circumferential portions of the two code wheels 282 and 234 is disposed a block shaped shock absorber assembly 580. Disposed slightly above the shock absorber block 580 is a dual assembly of intermediate transfer arms, the duplicate components of which provide identical combing and interference coaction with both of the code wheels 282 and 284.

Turning now to FIGURE 3, there will be seen the transfer members, the means by which mechanical transfer of the code representations from any selected code rod 440 in either code wheel 282 or 284, to the various mechanisms such as punches, feed release mechanism, punch retractors and print hammer is accomplished.

It will be recalled that two vertical parallel studs are disposed in the code wheel support casting. One of these two studs 266 is shown in FIGURE 3 and the two studs provide support for the block shaped shock absorber assembly 580 which includes front and rear vertical bores 581 and 582 (FIGURES 4 and enabling the shock absorber assembly 580 to be slipped down over the two studs. Shock absorber block assembly 580 is maintained in elevation by set screws 583 which rigidly secure block 580 on the two mounting studs midway between the two code wheels 282 and 284. The shock absorbing functions and details of shock absorber 580 will be described in relation to functional operation of the apparatus. The two studs, see 266 (FIGURE 3) project a considerable distance vertically above the shock absorber block 580. The purpose of such projection is to enable the stud to also provide a means for mounting the punch block assembly.

FIGURES 2 and 3 illustrate the relative arrangement of the dual groups of intermediate transfer levers. Each group of levers is pivotally disposed on a respective horizontal shaft 584 or 586. The left-hand shaft 584 carries intermediate transfer levers which cooperate with the lefthand code wheel 284, whereas the right-hand shaft 536 carries levers which cooperate with the right-hand code wheel 282. The two shafts 584 and 586 are spaced on either side of the shock absorber block 589 and extend over portions of their associated code wheels in fore and aft relationship with the shaft axes parallel to the code wheel axes. The two shafts 584 and 586 have their front and rear ends spigoted in appropriate bores in the printer frame structure, being maintained in rigidly secured disposition by set screws. I

Reading backwards, i.e., from rear to front, the intermediate transfer levers are designated by reference characters 598 (tape feed release), 591 (punch retractor), 592 and 593 (numbers 1 and 2 code punches), 594 (feed hole punch), 595, 596 and 597 (numbers 3, 4 and 5 code punches), and 598 (print hammers). These intermediate transfer levers have duplicate counterparts on both of shafts 584 and 586. All of the intermediate transfer levers 590-598 include downwardly depending arms, some of which vary in shape, which ride in the corresponding combing grooves of the associated code wheels 284 and 282, such grooves being identified for the appropriate functions in the preceding description. The transfer levers 590 and 592-598 each have laterally extending arms projected over the shock absorber block 580, the arms of opposite identical intermediate transfer levers being slightly spaced apart above the shock absorber block 580. The shock absorber assembly 580 includes a plurality of shock absorber units, one of which is disposed under and engaged by the adjacent ends of the aforenoted intermediate transfer arms 590 and 592-598. The left-hand transfer arm shaft also serves to pivotally mount a tape feed release pawl 600 which cooperates with both of the tape feed release intermediate transfer levers 520.

In FIGURE 1, it will be seen that the punches 616-621 and a plunger 660 for operating the print hammer (648, 654) are disposed immediately above the ends of the horizontal arms of the intermediate transfer levers 592- 558 in a punch block assembly 610 (see FIGURE 2) which includes the punch retractor and print hammer.

Punch block assembly 611 is mounted with upper portions of front and rear studs 264 and 266 extending through punch block bores, and is secured in position by set screws. Carried in the punch block base member 612 for vertical reciprocatory movement are six (6) tape punches 616, 617, 618, 619, 620 and 621. Punch 618 is the feed hole punch whereas punches 616, 617 and 619- 621 are the five (5) code hole punches. The punches are provided with heavy shank portions extending to an intermediate point on the punches and guided through bores in an intermediate wall 622 of the punch block base 612. The punches have light compression coil springs disposed above the intermediate wall 622 and the punch stripper plate 626 in which the cutting ends of all punches are disposed. Coil springs 624 abut the underside of stripper plate 626 and have their other ends disposed on small washers resting on the shoulders at the upper ends of the heavy shank portions just above the intermediate wall 622. These coil springs are not retraction springs but merely create a bias force to maintain the punches in a retracted position whenever they are not being selected and reciprocated. The lower ends of all punches are provided with laterally flanged heads 629.

Secured to the punch block base 612 above stripper plate 626 is a hollow die block 630, the lower wall of which includes the di holes aligned immediately above the punch guide holes in stripper plate 626.

Pivotally secured on the front vertical wall of the punch block base below stripper plate 626 is a printer hammer arm 648 which is made of nylon. Print hammer arm 648 extends horizontally under the die stripper plate 626 and, at its free end, carries a hammer head 654 which can be seen in FIGURE 1. A coil spring secured at its other end of the print hammer arm 648 biases the print hammer arm to its retracted position.

Longitudinally aligned with and in front of the tape punches 616-621 is a vertically disposed print hammer operating plunger 666. The lower end head 662 of hammer plunger 66% is disposed at the same level as the heads 629 of punches 616-621, whereas the upper end of hammer plunger 66% is disposed in vertical alignment with and under the print hammer arm 648.

Extending between and rotatably journalled in the die block base front and rear walls are two punch retractor operating shafts 672 (see FIGURE 2) one disposed to the left and one disposed to the right of the punches and hammer plunger. Secured to the lower side of each of shafts 672 by rivets are punch retracting bails which extend horizontally to a position adjacent the shanks of punch-es 616-621 and print hammer plunger 660 and overlying the flanged heads 529 and 662 of all punches and the print hammer plunger. The front edge of each bail is formed with a forwardly extending ear constituting an anchor for a coil spring the other end of the spring being anchored to an associated spring post. The two coil springs bias the retract bails against the lower punch block wall 628 whenever punch retraction is not occurring. A cylindrical steel sleeve 682 is non-rotatably secured to the rearwardly projected end of each of shafts 672. A short portion of each sleeve 682 is provided with an actuating notch 634 shown in FIGURE 2. When the punch block assembly 610 is secured in position on the two mounting studs 264 and 266, the notches 684 in sleeve 682 of the retracting shafts 672 will cooperate with portions of the associated intermediate transfer retract levers 5%.

Whenever a selected code rod 440 is driven into the wheel 232 or 284 by one of the code rod selector plungers 52tl-523 appropriate interference flanges on the code rod 44%) move into the interference position in combing grooves 4%4-412 in which the intermediate transfer levers are riding. Any selected code rod 440 excepting the Space" and Figures code rod has an interference flange which shifts into the comb groove within which the print hammer intermediate transfer lever 598 is riding. Hence, for every code rod selection excepting the Space and Figures selection, an interference flange on the code rod rotates into engagement with the depending arm 688 of the hammer transfer lever 598. Similarly, if the code combination represented by the selected code rod 44 includes mark impulse representations which are represented by flanges moved into the combing grooves 466, 407, 419 and 411, these interference flanges will engage the depending arms 688 of the code punch intermediate transfer levers 592, 593, 595, 596 and 597. Every one of the thirty-two (32) code rods includes an interference flange which, when the code rod is selected, shifts into combing groove 4% enabling the interference flange to engage the feed hole punch intermediate transfer lever 594.

As the code wheel 24 continues to rotate clockwise, the selected code rod print hammer and punch interference flanges will engage the depending arms 688 of the selected code punch transfer levers, the feed punch transfer lever, and the print hammer transfer lever, imparting in essence a camming action against the engaged intermediate transfer levers causing them to rotate counterclockwise. Note: if the code rod which is selected were on the righthand wheel 282, the code rods would be rotating in a counterclockwise path and would engage the associated transfer levers to shift them in a clockwise pivotal movement.

The camming force of the interference flanges of the selected code rod against the intermediate transfer levers is transferred through the horizontal arms 6% of the transfer levers to the underside of the heads 629 and 662 of the selected punches 616-621 and the print hammmer plunger 660, driving such selected punches and the print hammer plunger in an upward direction. The selected punches 616-621 drive through and punch the paper tape 2 66 while the print hammer plunger 650 (Figures 65 and 66) impacts the underside of the nylon print hammer arm 648 causing an elastic impact reaction forcing the print hammer arm 648 up into abutment against the underside of the die stripper plate 626. The head 654 of the print hammer is made as a loose fitting aluminum plunger inserted in a bore in the end of the hammer arm 648. When the hammer arm 648 engages a solid stop, the underside of die stripper plate 626, the light weight aluminum plunger 654 over-travels approximately .015 inch pressing the paper tape 206 and an ink ribbon against the face of the rotating type wheel 236. As has been previously described, the type wheel is in accurate, direct, rotational register with the code wheels through appropriate gearing, and therefore the correct character will be in position above the front edge of tape 206 and above the hammer head when the print hammer arm 648 is actuated.

As the code rod 440 rotates ten (10) degrees beyond punch and print actuation position, a retractor interference flange in groove 495 strikes a cam rise on the retractor bail intermediate transfer arm 591 (all code rods have an interference flange for the retractor bail intermediate transfer arm). Camming action by such interference flanges on the retractor intermediate transfer arm 591 causes rotation of the retractor bail 674 creating a bias tending to pull the six (6) punches 616-621 and the print hammer plunger 66% to retract position. This retraction force occurs just before the punch actuation flanges pass their interference levers and retraction thus immediately follows the punch actuation. The long lower end 713 of the retractor transfer lever arms 591 serves to momentarily hold the bail and the punches and hammer plunger in retracted position. Even so, the punches and the print hammer plunger, as a result of this rapid retraction action, strike their associated intermediate transfer arms. To completely prevent any rebound movement and assure positioning of the members for a subsequent operation, the energies from these moving masses are absorbed in the shock absorber assembly 58!).

Turning to FIGURES 3-8, the shock absorber assembly 586 contains individual shock absorber units 715 for each of the intermediate transfer arms excepting the retracting transfer arms 591. Each shock absorber unit 715 is identical and, accordingly, details of only one (FIGURE 6) will be described.

Block 580 includes a series of vertical bores 716, constituting enclosure cylinders for each shock absorber unit 715. Located at the bottom end of each bore 716 is a small metal plunger 713 which rests on top of a spring finger 720. There is one of these spring fingers 720 under each of the shock absorber unit bores 716 and all spring fingers 720 are integral with a spring plate 721 (FIGURE 2), which is secured by rivets'722 to an auxiliary plate 724 secured on one side of the shock absorber block 580 by screws 726 and 727. The upper edge of plate 724 has a horizontal flange 728 which extends a slight amount over the aligned bores 716 to be disposed freely in a wide notch 73% provided under the heads of each shock absorber unit top plunger 692, thus permitting a slight amount of vertical play for each top plunger 692 yet also retaining the plungers in the shock absorber assembly 589.

In the embodiment shown in FIGURE 6, between the upper and lower plungers 692 and 718, a group of steel balls 732 and 733 are loosely packed into the bores 716. The diameter of the larger balls 732 is slightly greater than one half the diameter of bore 716, thus causing the group of balls 732 to engage each other and the side wall of bore 716 in point-to-point contact. Yet the balls '1' 32 cannot wedge between each other and the wall surface 716. The smaller balls 733 are of such a diameter as to contact the surfaces of upper and lower larger balls 732. Whenever the punches and the print hammer plunger are retracted and strike the intermediate transfer arms, which in turn strike the heads of upper plungers 692, the resulting knietic energy will be completely dissipated through the numerous point-to-point. engagements'between balls and side walls of bore 716 causing the punches and the print hammer plunger to be immediately settled down with no rebound and ready for another operation. The spring fingers 720 serve to impart a small flexing action to the pile of balls assuring that they remain loose after an energy absorbing function.

FIGURES 7 and 8 illustrate a different manner of stacking the steel balls in the bore 716a of the shock absorber block 580a. In this embodiment, which is preferred, the ball stack consists of a layer of three (3) large balls 732a alternated with a layer consisting of one small ball 733a. The three (3) large balls are of identical size, fitting slightly loose in a horizontal plane within bore 716a and the smaller ball 733a nests in the center of and between the layers of three (3) balls. Variations in diameter of the balls in both embodiments will vary the amount of impact which can be absorbed.

Inasmuch as sequential code rod selection, under certain character selection sequences, can occur up to times per second, it will be realized that no rebound of any punch or print hammer plunger can be tolerated. Hence, the need for these highly effective shock absorber units.

As the code rod 440 travels another 5", an interference flange strikes the depending arm 764 of the sprocket feed release intermediate transfer arm 5% (all code rods have an interference flange for the sprocket feed release intermediate transfer arm). 7 The cam'ming impact force transferred to feed release intermediate transfer arm 590 is im- 9 mediately transferred to the sprocket feed pawl 690 (FIG- URE 45) which releases the pawl end 762 from a sprocket ratchet to permit tape feed movement. When the feed release pawl 600 is removed from engagement with a tooth of a ratchet wheel connected to the feed sprocket, it must be back in position to engage the next tooth of the tape feed ratchet wheel before the tape has completed movement in its next stop position. The pawl 600 is pulled back into place by a restoring spring. Actuating energy imparted to pawl 94 and its intermediate transfer lever 590 by the code rod impacts is dissipated by a shock absorbing plunger (not shown). Rebound movement of pawl 600 and the intermediate transfer arm 590 is absorbed by one of the energy absorbing plungers 692 and they are thereby settled down ready for the next operation.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiment is therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by Letters Patent is:

1. For use in combination with a telegraphic recording device in which the recording means (such as punches, print hammer) are actuated by an impact caused by a rotating actuation element, upon hitting one or more transfer levers, a shock absorber device including a body and shock absorber means associated with indivi dual ones of the transfer levers, said shock absorber means comprising an elongate chamber disposed in said body, a spring loaded plunger provided at one end of said chamber, a number of different diameter steel balls disposed within said chamber on top of said plunger, the diameters of said balls being dimensioned so as to prevent wedging action between the balls and the inner wall of said chamber and permitting a plurality of contact points between each ball and adjacent balls and the inner Wall of said chamber, and an impact plunger slidably fitted in the other end of said chamber on top of said stack of steel balls and including an impact head adapted to be engaged by the associated transfer lever in its retract movement.

2. A device according to claim 1, wherein means providing the spring loading for said spring loaded plunger includes a spring finger secured on the lower side of said body and engaging the projected end of said spring loaded plunger.

3. A device according to claim 2, wherein individual shock absorber means are provided for each of said transfer levers and are disposed within said body in which a plurality of said chambers are formed by a corresponding number of parallel bores.

4. A device according to claim 1, wherein two sizes of steel balls are utilized, said balls being alternately arranged in groups within said chamber, one of said groups comprising three large balls lying substantially in one plane and having a diametral dimension less than onehalf the diameter of the chamber, Whereas the second group consists of a smaller single ball resting centrally of said three large balls.

5. A device according to claim 1, wherein two sizes of steel balls are utilized, the diameter of the larger of said balls being slightly greater than one-half the diameter of the chamber and the diameter of the smaller of said balls being less than one-half the diameter of the chamber, and said large and small balls being alternated along the chamber.

6. A shock absorber device for use in high speed printer-repertorator mechanisms comprising: a base member; a bore in said base member; a plunger having a portion projected into one end of said bore; resilient means engaging said plunger; a series of steel balls disposed Within said bore adjacent the end of said portion of said plunger, the sizes of said balls preventing wedging action between balls and the walls of said bore and permitting plural points of contacts between each ball and adjacent balls and the wall of said bore; and an impact plunger slidably fitted in the other end of said bore adjacent the other side of said series of steel balls and having an impact head at said other end of said bore.

7. A shock absorber device with multiple individual shock absorbing units for use with associated movable mechanical components in high speed printer-reperforator mechanisms comprising: a base member; a plurality of parallel through bores in said base member; a plunger disposed in the end of each of said bores; a spring finger engaging a projected end of each of said plungers; a series of steel balls disposed Within each of said bores with an end of said series of balls engaging an end of said plunger in the associated bore, the sizes of said balls preventing wedging action between balls and the walls of said bore and permitting several points of contacts between each ball and adjacent balls and the Wall of said bore; and an impact plunger slidably fitted in the other end of each of said bores engaging the other end of said series of steel balls in the associated bore and each impact plunger including an impact head disposed exterior of and adjacent said other end of its associated bore.

No references cited.

MILTON BUCHLER, Primary Examiner.

Claims (1)

1. 6. A SHOCK ABSORBER DEVICE FOR USE IN HIGH SPEED PRINTER-REPERFORATOR MECHANISMS COMPRISING: A BASE MEMBER; A BORE IN SAID BASE MEMBER; A PLUNGER HAVING A PORTION PROJECTED INTO ONE END OF SAID BORE; RESILIENT MEANS ENGAGING SAID PLUNGER; A SERIES OF STEEL BALLS DISPOSED WITHIN SAID BORE ADJACENT THE END OF SAID PORTION OF SAID PLUNGER, THE SIZES OF SAID BALLS PREVENTING WEDGING ACTION BETWEEN BALLS AND THE WALLS OF SAID BORE AND PERMITTING

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