US2852131A - Transfer mechanism for typographical machines - Google Patents

Description

P. HILPMAN 2,852,131 TRANSFER MECHANISM FOR TYPOGRAPHICAL MACHINES Sept. 16,1958

- 4 Sheets-Sheet 1 Filed Aug. 1, 1955 i INVE NTOR. .1 4 171/ 414 Sept. 16, 1958 P. HILPMAN I 2,852,131

I mmsmn MECHANISM FOR TYPOGRAPHICAL MACHINES Filed Aug. 1, 1955 4 ShO ecs-Sheet 2 '-6 J5 INVENTOR- flaz ZZZ/0W Sept. 16, 1958 P. HILPMAN 2,352,131

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P. HILPMAN Sept. 16, 1953 TRANSFER MECHANISM FOR TYPOGRAPHICAL MACHINES 4 Shee'fs-Sheet 4 Filed Aug. 1, 1955 INVENTOR. R404 Ma /v4 United States Patent TRANSFER lVIECHANISM FOR'TYPOGRAPHICA MACHINES Paul Hilprnan, Garden City, N. Y., assignor to Mergenthaler Linotype Company, a corporation of New York Application August 1 1955, Serial No; 525,541 17 Claims. Cl. 199-36) This invention relates to typographical machines, such as Linotype machines of the general organization represented in U. S. Letters Patent to O. Mergenthaler No. 436,532 wherein circulating matrices are released from a magazine in the order in which they are to appear in print and then assembled in line with spacebands, the composed line transferred to the face of a mold, the mold filled with molten metal to form a type bar or slug, and the matrices returned through a distributing mechanism to the magazines from which they started while the space bands are returned to their own separate magazine or box. The machine functions are carried out in proper sequence and in timed relation to one another under the control of a plurality of cams mounted on a main cam shaft which makes one revolution for each machine cycle. At the completion of each cycle of operation, all parts have reached their normal position ready for the next cycle.

More particularly, the present invention is directed to mechanisms for delaying completion of certain machine operations until after the cam cycle has been completed or until the machine enters into a second cycle of operations. Specifically, it is concerned with the transfer mechanisms which return the matrices and spacebands to their respective magazines after the casting operation.

Heretofore, during line transfer, a cam controlled transfer lever operates to shift the matrices and spacebands from the first elevator into the upper transfer channel. wherein the teeth of the matrices engage corresponding teeth on the second elevator bar while the spacebands, being without teeth, remain supported in the channel. After the matrices are lifted free of the upper transfer channel, the cam controlled transfer lever moves the spacebands nearer to the spaceband magazine and into position to be engaged by the spaceband lever pawl, whereupon the transfer lever is returned to its normal position to await the next line to be transferred. The spaceband lever is returned at the same time to its normal position by virtue of a scissor like connection between the two levers, the spaceoand lever pawl engaging the spacebands and dragging them into the spaceba'nd box. The matrices, upon being brought into alignment with the distributor box by the upward movement of the second elevator, are immediately transferred into the box by the distributor shifter and then fed, one by one, to the distributor for return to their proper magazine channels.

While these transfer mechanisms have been employed for many years, nevertheless they have not been entirely satisfactory in the newer high speed machines, such as the Comet. The speed at which the transfer mechanisms operate is directly proportional to the speed of operation ofthe machine inasmuch as the cams which control actuation of the transfer lever and the second elevator are mountedon the same cam shaft which'cont-rols the speed of other machine functions. These transfer operations QCcur during the last stages of the machine cycle and,

Patented Sept. 16, 1958 therefore, are controlled by steep rises of the cam surfaces, causing rapid operations of the mechanisms. Such rapid operations result in severe impacts to machine components, e. g. the second elevator bar and the distribution box, or, in the case of the spaceband lever, cause the spacebands to skew on the guide rails ,of the upper transfer channel and become dislodged therefrom, thus interfering with the proper line transfer or leading/to damage of the parts.

The present invention provides an improved transfer mechanism whereby the matrices and spacebands may be transferred to the upper transfer channel at the necessary high speed (during this transfer, the spacebands are pre vented from skewing by the matrices between which they are interspersed) and whereby the transfer lever may be returned to its normal position waiting for subsequent line transfers also at the necessary high speed, but whereby the spacebands are shifted from the upper transfer channel into the spaceb'and box at a comparatively low' speed. The invention also provides improved transfer mechanism whereby the matrices may be lifted from the upper transfer channel to the I distributor box also at a comparatively low speed notwithstanding the increased speed of operation of the main cam shaft.

Other features and advantages of the invention Will be apparent from the specification which follows.

In the drawings:

Fig. l is a front elevation of a portion of the machine, showing the line transfer and the sp'aceband return mechanism in normal position;

Fig. 2 is a View similar to Fig. 1, showing the transfer mechanism position at the time the matrices are lifted from the upper transfer channel;

Fig. 3 is a view similar Fig. 2, showing the relationship of the transfer and spaceband levers at the time the transfer lever is returned to normal position and the spaceband lever is returnin'g thc spacebands to their storage box;

Fig. 4 is a view of the spaceb'and lever return-motion retarding dash-pot;

Fig. 5 is a section taken along line 5-5 of Fig. 4;

Fig. 6 is a section taken along line 66 of Fig. 5;

Fig. 7 is a side elevation-at view showing the second elevator and its operating cam mechanism;

Fig. 8 is a front elevational view, reduced in size, showing thecam mechanism of Fig. 7;

Figs. 9, l0 and ll are schematic representations show. ing the relationship between the second elevator cam segments at different periods of a machine cycle; and

Fig. 12 is a perspective view showing a segment of the distributor shifter mechanism and its operating cam carried by the second elevator cam.

Referring toFig. l, the matrices 10 and the spacebands 11 are delivered, one by one, to the assembling elevator 12, wherein they are composed in line in the usual way. Upon completion of a line, the elevator 12 is raised to the dotted line position shown, and" the matrices and spacebands then transferred by the line delivery carriage 9 through the intermediate channel 13 to the first elevator 14, which immediately descends to locate the line in casting position. After the type bar or slug has been cast, the line of matrices and spacebands is raised by the first elevator to upper transfer position where the V-shaped bar 15 depresses the-spaceband wedges and the matrices standing in auxiliary position. In this manner, the

.matrices and the spacebands are prepared for transfer from the first elevator head 16.- The foregoing parts and their mode of operation are well known and need not be further described. a

The present invention is directed to improvements in the transfer mechanism and a preferred arrangement of such mechanism will now be described. It will be assumed that the second elevator 17, which raises the matrices to the distributing mechanism, is positioned to accept transfer of the matrices from the first elevator. This assumption is made simply to assure that the machine is ready for a transfer operation to take place inasmuch as all machine operations are timed by cams.

As the line of matrices and spacebands reach the upper transfer position, the transfer cam has been rotated to a position where the cam dwell 21 is arriving opposite cam roller 22, carried by cam lever 23. Lever 23 is rigidly fastened to shaft 24, as is transfer lever 25, and consequently as lever 23 is rotated, by its roller 22 following the contour of cam 20, transfer lever 25 is also rotated. Tension spring 26 (Fig. 2) maintains engagement between roller 22 and the cam surface. As roller 22 rides down the dwell of the cam, urged by spring 26. transfer lever 25 is rotated in a clockwise direction. Connected to lever 25, by link 27, is transfer finger 30 which engages the outermost matrix and pushes the line of matrices and spacebands towards the second elevator bar 31. The line is moved as a unit to prevent any single matrix or spaceband from becoming dislodged during line transfer movement. the art), may be provided to insure compactness of the line and its unitary movement. Pawl 32 on intermediate bar 15 guides the matrices vertically onto the second ele-- vator bar 31, the teeth of which engage corresponding teeth of the matrices.

It will be noted that a slotted link. 33 and pin 34 connection is provided at the lower extremity of transfer lever 25. One end of link 33 is connected to the spaceband lever 36, rotatable about shaft 37, by v threaded member 35. This member 35 provides for adjustably connecting the two levers. When transfer lever 25 is rotated clockwise as above described, pin 34, which is formed on transfer lever 25, bears against the end of the slot in the link 33, as shown in Fig. 1, to rotate spaceband lever 36 counterclockwise. Thus, while the transfer lever is acting to move the matrices to the second elevator bar 31, spaceband lever 36 is also moving toward the second elevator to he in position to engage the spacebands and return them to their storage box.

When the transfer lever 25 has moved the outermost matrix onto the second elevator bar 31, the second elevator cam is timed to, at that instant, raise the second elevator and carry the matrices to the distributing mechanism. This elevating mechanism will be hereinafter described. The spacehands 11, not being provided with teeth as are the matrices, are not disturbed by the movement of the second elevator 17, but remain in the upper transfer channel 40 supported on tracks 41 and guided at their lower slotted ends by rail 39. While the matrices are being lifted from the upper transfer channel, roller 22 has not yet reached the low point. on the'carn contour i (see Fig. 2) and consequently clockwise rotation of transfer lever 25 has not been arrested, nor has counterclockwise rotation of spaceband lever 36 been completed. This, of course, prevents interference between the spaceband lever pawl 43 and second elevator bar 31. After the matrices have been lifted clear of the upper transfer channel 40, as shown in phantom view in Fig. 2, cam 20 is further rotated so that transfer finger 30 brings the spacebands still nearer to the spaceband box, that is to say, to a position where they can be engaged by spaceband pawl 43 which is moving leftwardly (Fig. 2). By the time roller 22 moves into the low point of the cam contour, the spacebands are spanned by pawl 43, which is then lowered to engage the outermost spaceband.

Further rotation of transfer cam 20 brings higher portions of the cam surface into engagement with roller 22 and consequently transfer lever 25 is rotated counterclockwise for return to normal position." This action is completely under the control of the cam contour and is rapidly effected in order that the transfer lever may be A mechanism, not shown (but known in i in position to transfer the next following line of matrices and spacebands. It will be observed that When transfer lever 25 is returned to its normal position, pin 34 is free to slide in the elongated slot of link 33. Therefore, during return of the levers to their normal position, there is no positive connection therebetween. Rather, transfer lever 25 is returned through positive cam action but spaceband lever 36 is returned by tension spring 44 under the restraining influence of dash-pot 47. A connecting rod 45 is pivotally joined to lever 36 and fastened to piston 46 of the dash-pot. I

The dash-pot 47 (Fig. 6) is pivotally mounted on the machine frame 50 as by pin 51 and collar 49. In this manner, as the spaceband lever is oscillated and rod 45 assumes various positions with respect to the horizontal, the dash-pot 47 can accommodate itself to permit free movement of rod 45 through end Wall 52.

The opposite end of the dash-pot is Provided with an adjustable plug 53 having a threaded central cavity 54 which is connected to the chamber 55 by passageway 56. Into cavity 54 (Fig. 5) is inserted stud 57 which is flattened on two sides 60 to provide a vent leading from the cavity. By turning stud 57, the cushioning action of the dash-pot, and therefore the speed at which spaceband transfer is effected, can be regulated. A lock nut 61 is provided to fix stud 57 in its adjusted position.

When the spaceband lever is being rotated countcr clockwise, the force so moving it is quite large and the dash-pot is ineffective to retard the transfer of, the matrices to the second elevator bar 31, nor does it affect the rapid return of the transfer lever 25 to normal position. However, as has been described, the spaceband lever returns to normal position under the force of the tension spring 44. Due to the dash-pot action, this movement takes place rather slowly and consequently the spacebands are not dislodged from the supporting tracks 41 and rail 39 as they are being returned to the spaceband box. As is shown in Fig. 3, the transfer lever 25 is in its normal position while the spaceband transfer is still taking place.

Referring now to Fig. 7, second elevator 17 is shown controlled by composite cam 62 and tension spring 63. Operating lever 18 is pivotally mounted on shaft 64, as is arm 65, the two being joined by sleeve 66. A safety pawl 67, secured to sleeve 66, engages latch 70 which is pivotally mounted on support member 71 and actuated under control of means not shown, but well known in the art. Cam roller 72 is carried by member 73 which pivots on support member 71 and is pivotally connected to arm by link 69. Thus with latch out of engaging position, when roller 72 rides into the dwell of cam 62, spring 63 urge lever 18 in a clockwise direction, or downwardly away from the distributor box 74 towards upper transfer channel 40, wherein the second elevator bar 31 finally comes to rest in position to receive the matrices as they are transported from the first elevator head 16 by transfer lever 25.

Cam 62 in profile and the remainder of the machine components described in conjunction with Fig. 7 are similar to mechanisms now well known. However, as will be apparent from Figs. 7 to ll, cam 62 is formed of two sections or parts which will be designated 75 and 76. Section 75 is keyed to machine cam shaft 77 and, therefore, rotatable therewith. Section 76, on the other hand, is free to turn on shaft 77 and consequently can change its angular position with respect to cam section 75. A tension spring 80, extending between lug 81 on cam section 75 and cam section 76, urges the latter into a position determined by abutment 82 carried on the fixedly mounted cam section 75. Also connected with the two cam sections is a dash-pot 83, the cylinder 84 of which is secured to section 75 while the piston'of which is connected through rod 85 to cam section 76. The connections between the dash-pot components and their respec-r tive cam sections. are pivotal, inasmuch as the cam sections assume various positions relative to each other.

Opposite the cam surface of section 76 is a curved rack 86 to mesh with a pinion 87 which is driven from the main cam shaft 77 through gear 90 and pinion 91, the latter of which is on the same shaft as pinion 87. By proper selection of the gear, pinion, and rack,cam segment 76 is rotated at a lower speed than cam segment 75 when rack 86 engages pinion 87. In-this manner, cam section 76 is moved out of engagement with abutment 82, thereby tensioning spring fitland driving the piston rod 85 into the dash-pot cylinder When the section 76 is rotated to such extent that rack 86 and pinion 87 are no longer in engagement, spring .80 acts to restore section 76 to its neutral position or back into engagement with the abutment 82. However, in doing so, spring 80 works against the restraining action of dash-pot 83 so that the return of the parts to their neutral position is effected slowly and gradually.

The action of the composite cam 62 is clearly depicted in Figs. 7, 9, l0 and ll. In Fig. 7, the cam is shown in neutral position and the second elevator is in its upper and normal position with bar 31 in alignment with the distributor box 74. As the machine cycle progresses, the cam is rotated clockwise so that for approximately 180 of cam rotation, roller 72 rides on a concentric surface and the second elevator remains in elevated position. It is during this period that other machine functions, e. g. casting, are taking place. It is only when that portion of the cam designated 92 reaches roller '72 that the elevator starts to descend to its matrix receiving position shown by dotted lines in Fig. 7.

As is apparent, there is only ashOrt interval of the machine cycle remaining in which to elevate the matrices to the distributor b X. It is duringthis return movement that rack 36 engages pinion 87 (Fig. 9) andthe rotation of section 76 is slowed sothat the two cam sections separate (Fig. 10). Thus, the elevation time of the second elevator carrying the matrices is materially lengthened. Fig. 11 shows that, even after the machine cycle is ended and the rotation of shaft 77 arrested, the second elevator hasnot reached its final upward position for distribution of the matrices. Rather, rack 86-has run' free of pinion 87 and spring 89 is returning cam section 76 to its neutral position against the restraining influence of the dashpot 83, thereby lifting the second elevator, at a low speed, to its final position in alignment with the distributor box.

With the second elevator brought to position at the distributor box, the distributor shifter thereupon engages the matrices to remove them from the second elevator bar and transfer them to the distributor box for ultimate dis tribution. Heretofore, in the operation of linecasting machines, the movement of the distributor shifter was controlled by an appropriate cam which activated the shifter at the extreme end of amachine cycle. It was therefore possible to locate this cam on any of the other machine cams, or specifically, on the machine cam nearest to the cam follower for the shiften. Now, however, operation of the distributor shifter must be synchronized with operation of the second elevator inasmuch as it cannot be operated before the second elevator is seated in its upper position. Consequently the distributor shifter cam is mounted on stow-acting section '76 of the second elevator cam as shown in Fig. 12.

The distributor shifter cam 93, which is the same as heretofore provided, is illustrated as mounted on spacing studs 4 secured to cam section 76. These studs extend through openings in any intervening machine cams, such as 95 and 96, as well as cam section 75 so that cam 93 is positioned immediately adjacent bell crank follower 97. The follower is integral with extension 101 of collar Hi2 which is rotatably mounted in the machine frame 166. The distributor shifter arm 1:33 is formd integral with collar res and, as a result, as hell crank follower 97 engages Cam 93 to rock collar 1'92, the shifter arm is like- 6 wise pivoted. Distributor shifter lever 104=is secured to arm 103 and in turn leads to conventional parts not shown. It is clear that by this arrangement, the line transfer operation ofthe distributor shifter is delayed by the slow-acting cam section 76 so as to be synchronized with the line transfer operation of the second eleva tor. The normal position of the distributor shifter is within the distributor box and it is moved outwardly beyond the second elevator .bar before the latter is raised into alignment with the bar. Hence, the line transfer operation of the distributor shifter is effected by its movement back to normal position.

It is not intended to set forth all-the variations that may be made, but it is contemplated that certain features of the invention disclosed may be carried out in Ways other than those specifically described and that many apparently widely different embodiments of the invention can be made without'departing from the spiritand scope thereof. It is therefore intended that all matter contained in the above description or shownin the'accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

What is claimed is:

1. In a typographical machine wherein the matrices and spacebands are transferred from one organ to another during their circulation through themachine, the combination of a second elevator movable inopposite directions from and to a normal position of rest at each cycle of operation, the movement of said second elevator back to normal position being its effective transfer movement, a main cam shaft, "a composite cam mounted on said shaft for controlling both such movements of the second elevator and adapted to make one complete rotation during each machine cycle, and means for retarding the return movement of the second elevator in order to delay the transfer operation, said composite cam forming part of the retarding means and having relatively movable sections which make up the track surface and which vary said surface during. the return movement of the second elevator.

2. In a typographical machinewherein the matrices and spacebands are transferred from one organ to another during their circulation through-the machine, the combination of a distributor shifter movable in opposite di 0 rections from and to a normal position of rest at each cycle of operation, the movement of said distributor shifter back to normal position being its effective transfer movement, a main cam shaft, a composite cam mounted on said shaft for controlling. both such movements of the distributor shifter and adapted to make one complete rotation during each machine cycle, and means for retarding the return movement of the distributor shifter in order to delay the transfer operation, said composite cam forming part of the retarding means and having relatively movable sections which make up the track surface and which vary said surface during the return movement of the distributor shifter.

3. In a typographical machine of the Linotype class, the combination of an upper transfer slide operating lever, a spaceband transfer lever, 'a slotted link connection between said levers whereby movement of said upper transfer slide operating lever in onedirectio'n pivots said spaceband transfer lever in the opposite direction while permitting movement of said slide operating lever in the other direction without affecting said spaceband transfer lever, means for pivoting said spaceband transfer lever in the direction opposite to its first movement, and means for reducing the rate of movement of said spaceband transfer lever in response to said last named means.

4. In a typographical machine of the Linotype class, the combination of an upper transfer channel, a line transfer: lever for transferring matrices and spacebands to said channel, means for actuating said line transfer lever first to effect the transfer and thereafter to restore said lever to normal position, a spaceband transfer lever,

means whereby movement of the line'transfer lever in the transfer direction is transmitted to said spaceband transfer lever to cause movement thereof in one direction, a spaceband storage box, additional means for moving said spaceband transfer lever in the other direction to shift the spacebands from the upper transfer channel into said spaceband box, and means for reducing the rate of movement of said spaceband transfer lever in said other direction.

5. In or for a typographical machine of the Linotype class, the combination with an upper transfer channel, a second elevator, and a distributor box, of a rotary cam for moving the second elevator downwardly from the distributor box to the upper transfer channel and then upwardly from the upper transfer channel back to the distributor box during each machine cycle, said cam comprising two relatively movable parts which make up the track surface and which vary said surface during the return movement of the second elevator to delay such return movement of the second elevator, the first partof the cam controlling the descent of the second elevator to the upper transfer channel, and the second part of the cam controlling the ascent of the second elevator from said channel to the distributorbox.

' 6. The combination according to claim 5, including a main shaft on which the second elevator is mounted,

, the first part of said cam being fast to the shaft and the second part of said cam being rotatable on the shaft in moving relatively to the first part.

7. The combination according to claim 6, including a dash-pot, the cylinder of which is pivotally secured to one part of the second elevator cam and the piston of which is pivotally secured to the other part of said cam. 8. The combination according to claim 7, including an abutment member on the first part of the second elevator cam, anda spring for urging the second part of said cam into engagement with said abutment member.

9. The combination according to claim 8, in which the second part of the second elevator cam is provided with a rack segment. 1

10. The combination according to claim 9, including a. pinion for engaging said rack segment whereby the second part of the second elevator cam is rotated at a lower speed than the first part of the cam so as to become angularly displaced with respect thereto and to tension the spring.

11. The combination according to claim 10, wherein said pinion is driven from the main cam shaft and in which the rack segment runs free of the pinion prior to the completion of a cam shaft cycle.

12. The combination according to claim 5, including a distributor shifter for transferring the matrices from the second elevator into the distributor box when the elevator is in its upper line distributing position, and means for effecting such transfer movement of the distributor shifter, said means being governed in its operation by themovement of the second part of the second elevator cam relatively tothe first part of said cam in controlling the ascent of the second elevator, whereby the transfer movement of the distributor shifter is delayed in harmony with the delay of the return movement of the second elevator.

13. In a typographical machine of the Linotype class, the combination of an upper transfer slide operating lever, a spaceband transfer lever, a one way connection between the two levers whereby the active stroke of the transfer slide operating lever effects the idle stroke of the spaceband transfer lever, a rotarycam on the main shaft of the machine for controlling both the active and inactive strokes of the upper transfer slide operating lever, and mechanism distinct from said cam for effecting the active stroke of the spaceband transfer lever, said mechanism including a motion retarding device to delay the spaceband transfer operation.

14, In a typographical machine of the Linotype class, the combination of a second elevator movable downwardly from line distributing position to line receiving position and return, a rotary cam on the main shaft of the machine for effecting both such movements, said cam comprising a first section fast to the main shaft and which controls the downward movement of the elevator and a second section rotatably mounted on the main shaft and which controls the upward movement thereof, means actuated during the upward return movement of the second elevator for rotating the second section with reference to the first section in a direction opposite to the direction of rotation of the main shaft in order to slow down such movement of the elevator in relation to the speed of rotation of the main shaft, and means for'rotating the second section back to its normal position with reference to the first section to complete the upward movement of the elevator after the main shaft has completed its rotation.

15. The combination according to claim 14, wherein the means for returning the second cam section of the second elevator cam to its normal position with reference to the first section include a spring under the restraining influence of a dash-pot.

16. The combination according to claim 14, including a distributor shifter for transferring the matrices from the second elevator into the distributor box when the elevator is in its upper line distributing position, and means for delaying the transfer operation of the distributor shifter until after the elevator has completed its full upward movement.

17. The combination according to claim 16, wherein the means for delaying the transfer operation of the distributor shifter includes an operating cam attached to the second section of the second elevator cam.

References Cited in the file of this patent UNITED STATES PATENTS 436,532 Mergenthaler Sept. 16, 1890 786,155 Rogers Mar. 28, 1905 958,530 Pickett May 17, 1910 1,866,976 Keeler July 12, 1932 2,019,856 Hilpman Nov. 5, 1935 FOREIGN PATENTS 373,579 Germany Apr. 13, 1923 536,432 Great Britain May 14, 1941

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