US2097732A - Typographical composing machine - Google Patents

Description

Nov. 2, 1937. R MEAD 2,097,732

TYPOGRAPHICAL CQMPOSING MACHINE Filed Jan. '15, 1936 3 Sheets-Sheet 1 Q N I QR N mi: Qksi 2 INVENTOR A TTORNEI Z Nov. 2, 1937. R. R'MEAD 2,097,732

TYPOGRAPHICAL COMPOSING MACHINE Filed Jan. 15, 1936 5 Sheets-Sheet 2 Nov. 2, 1937. I RRMEAD 2,097,732

TYPOGRAPHICAL COMPOS ING MP CHINE Filed Jan. 15, 1936 5 Sheets-Sheet 3 I 11v VENTOR M A TTORNE 1 .5

Patented Nov. 2, 1937 UNITE. STATES PATENT OFFECE Richard R. Mead, Queens Village, N. Y., assignor to Mergenthaler Linotype Company, av corporation of New York Application January 15, 1936, Serial No. 59,207

22 Claims.

This invention relates to typographical composing machines, such as Linotype machines of the general organization represented in Letters Patent of the United States to O. Mergenthaler No. 436,532, wherein circulating matrices are released irom a magazine in the order in which their characters are to appear in print and then assembled in line, the composed line transferred to the face of a slotted mold, the mold filled with molten metal to form a slug or linotype against the matrices which produce the type characters thereon, and the matrices thereafter returned through distributing mechanism to the magazine from which they started.

More particularly, the invention relates to machines of this character employing matrices of widely varying sizes. Heretofore, it has been the custom to operate the assembler or conveyor belt at but one speed, which speed is designed to allow the matrices to be composed in the assembler elevator at a rate (normally about six lines per minute) consistent with the speed of operation of the casting and distributing mechanisms.

This rate of composition, although not the fastest at which the machine may operate if only the smaller or thinner matrices are used, has nevertheless been found to be a good average and has given satisfactory results. The present trend, however, is toward machines with wider magazines capable of handling full matrix fonts up to 36 pt. size, but here a serious difficulty arises, since it is apparent that a normal rate of speed of composition (which for the smaller matrices would be equivalent to, say, six lines per minute) would for the larger matrices, due to their greater thickness, be equivalent to perhaps eight or nine lines per minute, a speed at which the distributing mechanism can not properly handle matrices of such larger sizes. Then, too, when the larger matrices are delivered at such high rates of speed to the assembler, the pounding of the matrices against each other, due to their greater weight, results in their rapid destruction.

According to the present improvements, these and other difficulties are obviated by providing devices that enable the matrix conveyor belt, which controls the speed of assembly, to be operated at a plurality of different speeds, thus permitting a proper speed of assembly to be selected according to the size of the matrices in use.

In the embodiment illustrated, the conveyor belt is operable at three diiierent speeds, namely,

(1) a high speed for use with matrices of say from 5 pt. to 14 pt., which permits these matrices to be composed at arate ofspeed higher than normal but still one at which the distributing mechanism can readily handle matrices of these sizes, (2) an intermediate speed for use with matrices of say from pt. to 24 pt., and which is comparable to a normal speed of composition, 5 and (3) a low speed for use with matrices of say from pt. to 36 pt., which permits these matrices to be composed at a normal rate of speed as far as lines per minute is concerned, but which lowers their speed of delivery to the assembler elevator and consequently reduces the undesirable pounding, previously alluded to, to a degree that is acceptable. The three speeds of the conveyor belt are obtained through the medium of a gear shift mechanism operated auto- 15 matically from the magazine in operative position and in a manner depending upon the size of matrices stored therein.

The present improvements also contemplate a star wheel operable at three diiferent speeds but in this instance there is employed a gear shift mechanism settable manually by the operator. The speed of the star wheel will not necessarily depend upon the speed of travel of the assembler or conveyor belt, but more upon the size of the matrices being composed and upon the size or form of the star wheel itself. In order that the matrices may be properly compacted in line in the assembler elevator, it is desirable that each matrix strikes the star wheel between two adjacent prongs thereof, and this condition is facilitated by raising or lowering the speed of the star wheel as may be required.

In addition to the foregoing, the invention further contemplates the provision of a clutch mechanism whereby the operator may stop the operation of the conveyor belt and star wheel without stopping any of the other parts of the machine.

Referring to the drawings:

Fig. 1 is a front view of a portion of a Linotype machine equipped with the present improvements;

Fig. 2 is aside elevation of a portionof the machine shown in Fig. l, and illustrating the devices for controlling the speed of operation of the conveyor belt from the magazine in operative position;

Fig. 3 is a front view of the gear shift and clutch mechanisms previously referred to;

Fig. 4 is a horizontal sectional view taken on line dd of Fig. 3;

Fig. 5 is a front view of the clutch mechanism for connecting and disconnecting the conveyor belt and the star wheel from the common drive;

Fig. 6 is a sectional view on line 66 of Fig. 5;

Fig. 7 is a vertical sectional view through the gear shift mechanism controlling the speed of rotation of the star wheel, and showing the adjustment of the parts for driving the star wheel at the highest rate of speed;

Fig. 8 is a vertical sectional View of a part of the mechanism shown in Fig. 7, with the parts set for driving the star wheel at the lowest rate of speed; and

Fig. 9 is a front elevation of the means for setting the gear shift mechanism associated with the star wheel. 7

The matrices of the different fonts are stored in a series of magazines A and are released therefrom under the control of a keyboard 33 which, as usual, through the medium of means including a set of escapement reeds B and escapement levers B effects the operation of the.

escapement devices B associated with the magazine located in operative position. As the matrices are released, they pass down or through a channeled raceway or assembler entrance C onto an inclined conveyor belt C which delivers them to the customary assembler D, wherein they are advanced to the left and compacted as they are composed in line by a rotating star wheel E, the assembler thereafter being raised as usual into registration with the intermediate channel D through which the line is transferred to a line transporter or first elevator (not shown) for presentation to the mold. The magazines A are wider than usual in order to accommodate full fonts of large matrices, say up to 36 pt.

The conveyor belt C extends at an angle transi versely of the machine and is disposed so as to receive matrices discharged from any of the channels of the magazine in operative position. It passes (see Fig. 1) around a driven pulley C rotatably mounted on a stud fixed in the front frame of the machine at the right and near the discharge end of the magazine and around a driving pulley C fixed to a short shaft C mounted at the left and in close proximity to the assembler elevator. The shaft C is journalled (see Fig. 4) in the front and rear plates F and F of a gear box which, in addition to the shaft just mentioned, supports a shaft E on which the star wheel E is fixed as well as a shaft G on which a driving pulley G is fixed and which serves as a common source of power both for driving the conveyor belt and for rotating the star wheel.

The gear box (Figs. 3 and 4), as previously stated, includes the front and rear plates F, F secured together and heldin proper spaced relation by spacing members F and, in addition, a. third intermediate plate F secured to the front plate in spaced relation therewith by elements F similar to the members F This intermediate plate F serves to support some of the parts of the gear shift mechanisms, as will be later described.

The conveyor belt driving pulley C and the star wheel E (see Figs. 3 and 4) are arranged to be driven from a gear G associated with the shaft G on which the main drive pulley G is mounted and which is arranged to be driven from said pulley through a clutch mechanism described below. The drive from the gear G to the star wheel and to the conveyor belt drive pulley is through mechanism which includes in part, a wide intermediate pinion gear I-I meshing with the gear G and also with another gear J splined to" a sleeve J arranged to idle on a reduced portionof the shaft C on which the conveyor belt drive pulley is mounted. Likewise splined to this sleeve are two other gears J and J all three of said gears varying in size, the gear J meshing with the pinion H being the largest and the other two progressively smaller.

Motion is transmitted from the gears J J and J to the star wheel E and the conveyor belt pulley C through two independent sets of complementary gears, one set (including gears K K and K meshing, respectively, with the gears J J and J being mounted on a short foreand-aft shaft L journalled in the rear and the intermediate plates F and F and which serves to drive the star wheel, and the other set (in-- cluding gears M M and M also meshing respectively, with the gears J J and J on a similar shaft N likewise journalled in said plates and which serves to drive the conveyor belt drive pulley. The shafts L and N on which the different sets of gears are mounted are arranged for limited fore-and-aft movement and, depending upon their setting, one or another of the gears thereon will be operatively coupled therewith, while the two remaining gears will merely idle thereon.

The gears K K and K are operatively coupled with the fore-and-aft shaft L (see Figs. 4, 7, and 8) through the medium of a pawl L pivotally mounted in a longitudinal recess L formed in the shaft and having a head portion Z which is urged by a spring L acting on the base of the pawl, into one or another recess K in the nature of a keyway with which each of the gears is equipped. Of course, it will be understood that each gear K K K rotates at a different speed, the shaft L itself consequently rotating at the speed of the gear which happens to be operatively coupled with it.

The shaft L is selectively coupled with a selected gear K K or K merely by shifting the shaft longitudinally until the head portion Z of the pawl alines with the selected gear, and when such gear is turned to bring the recess K therein in registry with the pawl, the latter will, under the action of the spring L enter the recess,

whereupon the shaft L will pick up the speed of rotation of the selected gear.

t will be noted that the head portion Z of the pawl is formed with oppositely inclined bevelled edges, this arrangement allowing the shaft to be shifted while the parts are in motion, for as the shaft is moved longitudinally in either direction to aline the pawl with an adjacent gear, such gear will engage one or the other of the bevelled edges of the pawl (depending upon the direction in which the shaft is moved), camming the same downwardly against the action of the spring L into the recess L in the shaft, in which position the pawl will remain until the recess K in the newly selected gear is brought into registry therewith, whereupon the pawl will engage in said recess in the manner previously described. Should it happen that the recess K in the adjacent or newly selected gear is already in registry with the pawl, the camming action of course, will not take place, since the pawl will enter immediately into the recess.

In Fig. 7 there is illustrated a condition where the shaft L is operatively connected with the rear gear K of the set, and as this gear is smaller than the complementary gear J meshing therewith, the speed of rotation of the shaft L will be stepped up beyond that of the driving sleeve J. In Fig. 8, there is illustrated a condition where the shaft L is operatively connected with the front gear K of the set, and as thisgear is by longitudinally shifting said shaft.

L is shifted (see Figs. 3, 4, and 7) through the larger than the complementary gear J meshing therewith, the speed of rotation of the shaft will be stepped down below that of the driving sleeve J. When the shaft L is operatively connected with the intermediate gear K the shaft will be driven at the samespeedas the driving sleeve J, for here the gears K and J have a unit ratio. 7

'The star wheel E (Figs. 3, 4, and '7), which is mounted at the front end of theshaft E1, is driven from the fore-and-aft miovable shaft L, through the medium of a pair of intermeshing gears, one gear L keyed to said shaft, and the other gear E formed on a collar E loosely arranged on the shaft E carrying the star wheel. The drive from the collar E to the shaft E is through a comparatively heavy torsion spring E fastened at one end to the collar, and anchored at the other end in the shaft. The spring E transmits the driving torque from the collar to the shaft, and at the same time acts as a shock absorber to lessen the strain on the star wheel resulting from the impact thereon of large matrices traveling at high rates of speed.

The different speeds of rotation of the star wheel are obtained by operatively coupling the shaft L with a selected one of the gears K K or K and this, as previously stated, is effected The shaft medium of an arm L secured at the upper end of a short vertical shaft L journalled in an offset portion of the front plate F and bifurcated at its free end where it is provided with opposed inwardly extending pins 1 engaging in an annular recess Z formed in the front end of the fore-and-aft shaft. At its lower end, the vertical shaft has fixed thereto, a forwardly extending arm L formed with a series of bevelled teeth, meshing with a bevelled gear L fixed at the rear end of a short fore-and-aft shaft L journalled in the front plate. Pinned at the front end of the shaft L is a handle L for effecting the manual adjustment of the parts, the arrangement being n such that as the handle is moved in a clockwise direction,the shaftLthroughtheparts just described, will be actuated outwardly, whereas when thehandle is moved in the opposite direction said shaft will be actuated inwardly. Since there are three different positions for the shaft L, there are three corresponding positions of the handle L and these positions (see Fig. 9) are indicated by a pointer L fixed to the handle, and an associated face plate L fixed to the front member F of the gear box and on which there is marked opposite the three different positions of the pointer, indicia representing the speeds of rotation in revolutions per minute of the star wheel for the corresponding settings of the shaft L. The different settings of the handle are maintained by a spring pressed detent Z arranged in the front plate (see Figs. '7 and 8) and adapted to engage in one or another of a series of three recesses 1 formedin the inner face of the handle in positions corresponding to the different settings thereof.

Theshaft N on which the gears M M and M through which the various driving speeds are transmitted to the conveyor belt pulley, is in all respects similar to the shaft L on which the gears K K and K for transmitting the variable speeds to the star wheel, are mounted. That is, it is journalled in the rear and intermediate plates F and F3 of the gear box and is arranged for limited fore-and-aft movement to effect operative coupling with the different gears The various speeds of to the conveyor belt pulley (3 through a gear 'N splined on said shaft and another gear N meshing therewith and formed on a collar N pinned on the pulley shaft C In the embodiment described, the fore-and-aft shifting of the shaft N to bring about operative coupling with the different gears M M and M is effected automatically and controlled from. themagazine A located in operative position, i. e., in registry with the assembler entrance C. To this end (see Figs. 2 and 3) there is provided a vertically disposed gear shift arm N pinned at its lower end to a horizontal rock shaft N journalled in lugs projecting from the rear face of the front plate F and bifurcated at its upper end where it engages in an annular groove .12 formed near the front end of the shaft N. Also secured to the rock shaft is a short arm N extending rearwardly and which is connected with a forwardly extending arm N of a bell crank lever fulcrumed on a bracket plate 13 secured to a stationary part of the machine in the vicinity of the magazines A. The connection just alluded' to is, through the medium of a long link N pivotally connected at its upper end with the arm N of the bell crank lever and similarly connected at its lower end with the arm N. The arrangement is such that, as the bell crank lever is rocked counterclockwise (looking at the machine from the left), the horizontal rock shaft N will be turned clockwise to shift the shaft N outwardly, whereas when the bell crank lever is rockedclockwise, the shaft will be shifted inwardy.

The bell crank lever (see Fig. 2) is turned clockwise through the medium of a spring N fastened at one end to the link N and anchored at its opposite end by a pin 11 fixed in the gear box frame, and counterclockwise against the tension of said spring by cams N located on certain of the magazines. As in the case of the shaft L associated with the star wheel, the shaft N has three different positions of adjustment, the

rear or innermost position (which incidentally is determined by the banking of the arm N against a banking screw n threaded in the gear box frame) for stepping up the speed of rotation of the conveyor belt pulley, an intermediate position wherein a normal speed of rotation for the pulley results, and an outermost or front position for stepping down the speed of rotation of the pulley and consequently providing a speed of travel for the belt that is slower than normal.

It will now be apparent how the proper speed of travel of the conveyor belt for matrices of a given size is selected. Let it be assumed that the matrices in one of the magazines are of comparatively small size, as for instance from 5 pt.

to 14 pt., which may if the operator so desires be composed at speeds greater than normal. In

. such case, the magazine containing these matrices will be devoid of cams N and, when such magazine is in operative position, the shaft N will be located in its innermost position and the conveyor belt C thus will have its highest speed of travel. For matrices say of 18 pt. size, the magazine wherein they are stored will be equipped with a cam N which, in the operative position of the magazine, will cooperate with a cam r 5 follower N located at the end of an arm N of the bell crank lever, and the throw of said cam will be such as to locate the lever in the intermediate position, wherein the intermediate set of gears will be operatively coupled with the shaft N, with the result that the conveyor belt will travel at the normal rate of speed. For matrices of larger size, as for instance 36 pt., the magazine for them will be equipped with a cam N which, in the operative position of the magazine, will likewise cooperate with the bell crank lever, and the throw of said cam will be such as'to locate the bell crank lever so that the shaft N will be adjusted to its outermost position wherein the gear M having the step down ratio with the gear J will be operatively coupled with said shaft- For this adjustment, the conveyor belt will have its slowest speed of travel.

The various adjustments just alluded to are eifected automatically as the different magazines are moved into operative position and, since the shaft N is in all respects similar to that controlling the speed of rotation of the star wheel, they may be made without stopping the operation of the parts.

The pulley G (see Fig. 1), associated with the gear box, is driven from the intermediate shaft through a belt and pulley,O arrangement of the usual construction. In some instances, it may be desirable to stop the operation of the star wheel and conveyer belt without stopping the operation of the machine, and for this purpose there is interposed between the pulley G and the gear G that effects the driving of the pinion H, a clutch device, which will now be described.

As shown in Figs. 3, 4, and 5, the pulley G is splined to the shaft so that the latter is constantly driven by the pulley. Likewise splined to said shaft is a sleeve G on the front end of which there is formed a toothed ratchet wheel G Encircling the shaft, and mounted on spaced collar bearings G so as to be movable relatively to said shaft, is a member G which at one end presents two spaced circular flange portions G and G joined together by a semi-circular rib member G that encircles the toothed ratchet wheel G3 for a portion of its peripheral edge, leaving the remainder thereof exposed. The gear G is screwed to the front face of the foremost flange G while between the flanges in the vicinity of the exposed portion of the ratchet is a dog G pivoted at its center to said flanges and having one end thereof pressed into engagement with the ratchet wheel by a leaf spring G secured to the outer face of the rib portion G At the opposite end of the dog, there is provided a roll G arranged to track along the inner semicircumferential edge of a relatively large flat hook-shaped member P pivotally mounted at one end on the shaft C and adjacent the inner face of the rear plate F of the gear box. The member just alluded to has two positions of adjustment; one as shown in Fig. 5, wherein the dog G is held in engagement with the ratchet wheel, and the other as shown in Fig. 3, wherein the dog is forced by the member P and against the tension of the spring G out of engagement with the ratchet wheel. When the ratchet and dog are in engagement, it is apparent that the flange member G and consequently the gear G2 and the parts driven thereby (the conveyer belt and the star wheel) will be driven, whereas when the dog and ratchet wheel are disengaged, the driving connection will be broken.

The different adjusted positions of the member P (see Figs. 5 and 6) are controlled by a handle P fixed. at the front end of a shaft P journalled in the front and rear plates of the gear box, and which is provided at its rear end with a cam P arranged to cooperate with a flange P struck up at the free end of the member P. Associated with the handle is a plate P formed on a sleeve P surrounding the shaft, and spaced from the front plate F so as to clear the conveyer belt, and on which there are marked two indications On and Off. When the handle is opposite the indication On (see Fig. 5), the low part of the cam P will engage the flange P and the member P will be located in the position wherein the dog G is operatively coupled with the ratchet wheel G whereas when the handle is turned opposite the indication Off, the high portion of the cam will engage the flange, forcing the member P upwardly into a position wherein it will effect the disengagement of the dog and ratchet wheel. The plate P is provided with small protrusions p which cooperate with the handle to determine the different positions of adjustment thereof. It might be stated that the flanges G and G are recessed as at G to provide clearance for the roll G From the foregoing, it will be apparent that the improvements referred to impart great versatility tothe machine as far as varying the speed of assembly is concerned. With the mechanism. disclosed actually nine different speed combinations between the assembler belt and the star wheel are available and, if desired, more could be obtained by increasing the number of gears in the gear box. Especially advantageous are the present improvements in view of the trend toward wider magazines wherein matrices varying widely in size may be employed. Particularly is this true where the wide magazines are made interchangeable with the present magazines of normal width. Then too, where matrices vary greatly in width it may be advantageous to employ star wheels differing in design and which may require different speeds of rotation properly to assemble the matrices in line. These and many other advantages are inherent in the structure herein disclosed, a few only of which are given by way of example.

In the accompanying drawings, the invention has been shown merely by way of example and in preferred form, and obviously many variations and modifications may be made therein which will still be comprised within its spirit. It is to be understood, therefore, that the invention is not limited to any specific form or embodiment,

except insofar as such limitations are specified in the appended claims.

Having thus described my invention, what I claim is:

1. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, stacker mechanism operable at different speeds for advancing the matrices and compacting them in the assembler as the line is being composed, and means adapted upon actuation to effect an instantaneous change from one speed to another as required.

2. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a rotatable star wheel arranged to advance the matrices andcompact them in the assembler as the line is being composed, a variable speed drive for the star wheel, and means adapted upon actuation to set the drive for one speed or another as required.

3. Anassembling mechanism for typographical composing machines including, in combination,

an assembler wherein the matrices are composed in line, a rotatable star wheel arranged to advance the matrices and compact them in the assembler as the line is being composed, means for rotating said star wheel at a plurality of different predetermined speeds, and means for selecting one speed of rotation or another as desired.

4. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a rotatable star wheel arranged to advance the matrices and compact them in the assembler as the line is being composed, means including a plurality of gears operable independently for driving the star wheel at different speeds, and a gear shift mechanism for rendering one or another of the gears active as desired.

5. A combination according to claim 2, wherein the speed of rotation of the star wheel may be varied without arresting its rotation.

6. A combination according to claim 4, wherein the gear shift mechanism is manually operable from the front of the machine.

7. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a rotatable star wheel arranged to advance the matrices and compact them in the assembler as the line is being composed, a plurality of driving gears, a plurality of driven gears meshing therewith, a driven shaft associated with the star wheel and whereon the driven gears are idly mounted, and means for efiecting a driving engagement between the driven shaft and a selected one of the driven gears, whereby to vary the speed of rotation of the star wheel.

8. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, conveyor mechanism for delivering the matrices to the assembler, means associated with the conveyor mechanism for varying the rate of travel of the matrices to the assembler, and means adapted upon actuation to effect an instantaneous change from one rate of travel to another as required.

9. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, a variable speed drive for the belt, and means adapted upon actuation to set the drive for one speed or another as required.

10. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, means for driving the conveyor belt at a plurality of diiferent predetermined speeds, .and means for selecting one speed or another as desired.

11. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, means including a plurality of gears operable independently for driving the belt at difierent speeds, and a gear shift mechanism for selectively rendering one or another of" the gears active.

12. A combination according to. claim 9, wherein the speed of travel of the conveyor belt may be varied without arresting its travel.

13. A combination according to claim 11, wherein the gear shift mechanism is operated automatically.

14. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, a plurality of driving gears, a plurality of driven gears meshing therewith, a driven shaft associated with the conveyor belt and whereon the driven gears are idly mounted, and means for efiecting a driving engagement between the driven shaft and a selected one of the driven gears, whereby the speed of travel of the conveyor belt may be varied.

15. A typographical composing machine including, in combination, a plurality of magazines for storing matrices, means for releasing matrices from a selected magazine, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the as sembler, and means for varying the speed of travel of the belt according to the magazine selected.

16. An assembling mechanism for graphical composing machines including, in combination, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler and means for automatically controlling the speed of travel of the conveyor belt according to the size of the matrices in use.

17. A typographical composing machine adapted to be equipped with magazines for storingmatrices of different sizes, an assembler wherein matrices from the magazine in use are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, and means for varying the speed of travel of the conveyor belt according to the magazine in use, automatically as said magazine is moved into operative position.

18. A typographical composing machine including, in combination, a plurality of magazines for storing matrices, means for moving a selected magazine into operative position, means for releasing matrices from the selected magazine, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, and means for varying the speed of travel of the belt automatically as one or another of the magazines is moved into operative position.

typo- 19. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, a power driven conveyor belt for delivering the matrices to the assembler, a rotatable star wheel arranged to advance the matrices and compact them in the assembler as the line is being composed, a common drive for the belt and star wheel, and intermediate connections for varying the speed of the driven members.

20. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, and means for effecting the delivery of matrices to the assembler at different speeds.

21. An assembling mechanism for typographical composing machines including, in combination, an assembler wherein the matrices are composed in line, means for effecting the delivery of matrices to the assembler at different speeds, and means for automatically selecting the speed of delivery in accordance with the size of matrices in use.

22. A clutch mechanism including, in combination, a driving member, a driven member, a ratchet wheel fixed to the driving member, a

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