Year: 1894

page_text: Date of Application, 13th Feb., 1894-Accepted, 24th Mar., 1894
Fig. 1 is a plan view of the machine.
Figs. 15 and 16 are elevations of two of the cams which operate the toggles.
Fig. 17 is an elevation of the side of the machine opposite to that shown in
Fig. 1.
Fig. 18 is an end elevation illustrating the mechanism for operating the form-
rollers.
Fig. 19 is an enlarged detail showing one of the form roller carriages and a
portion of the rack bar secured thereto.
Fig. 20 is an end elevation of the parts shown in Fig. 19.
Figs. 21, 22, 23, 24 and 25, are details of the mechanism for moving the form
rollers forward and back over the type-forms to ink the same.
My invention relates to that class of platen printing machines where the paper
is taken from a continuous web or roll, and in which two type-beds and two platens
are employed; and my invention consists in certain novel combinations of parts
and details of construction as hereinafter fully set forth and specifically pointed
out in the claims.
In the said drawings A represents the framework of the machine, on the base
of which between the side pieces is mounted a stationary plate B forming a type-
bed, and between the upper ends of the said side pieces is secured a stationary
plate C, forming a platen and arranged directly over and in line with the stationary
type-bed B. D is a vertically reciprocating plate forming a type-bed which
co-operates with the upper stationary platen C, and E is a vertically reciprocating
plate forming a platen which co-operates with the lower stationary type-bed B,
said platens and type-beds being all arranged vertically in line with each other.
On these type beds B, D, the type-forms are imposed in the usual manner. The
reciprocating type-bed D, and reciprocating platen E, are provided at their opposite
ends with arms 19 guided in vertical grooves in the framework A, and are con-
nected together in such manner as to move simultaneously in opposite directions by

page_text: .
means of two double toggles G, G, Figs. 1 and 3, the construction and operation
of which will now be described.
Each of said double toggles is composed of a central oscillating bar or member b,
provided at its ends with central journals c adapted to oscillate in bearings in the
framework A, the upper and lower edges of the members b being jointed
respectively at d, to the upper and lower members g, h, of the double toggles,
the former g being jointed at i to the reciprocating type-bed D, and the latter at k
to the reciprocating platen E, whereby as the two members b, b, are rocked on
their centres c, the upper and lower toggles will be operated as desired. The two
upper toggle joints d, d, are connected by a horizontal bar and the two lower
toggle joints e, e, are similarly connected by a horizontal bar m, said bars serving
to transmit the power from one toggle to the other. The central members b, b, of
the toggles are each provided with two inwardly projecting arms p, p, one near
each end as shown in Figs. 3 and 4, said arms carrying cam rolls q which are acted
upon by cams r, r, s, s, on the main or central shaft I, whereby as said shaft is
rotated the double toggles are closed or straightened out as shown in Fig. 3, and
the movable type-bed and movable platen which are nearly of the same weight,
moved simultaneously in opposite directions to cause them respectively to
co-operate with the stationary platen and stationary type-bed to produce the
impressions, a single revolution of the central shaft I producing two impressions,
one on each side of the sheet, as required in a perfecting press.
By using the upper stationary plate C as a type-bed, and the plate D imme-
diately thereunder as a platen, it will be obvious that the machine can be adapted
for color printing, and two colors can by this arrangement be printed in succession
on one side of the sheet.
Outside the framework A the shaft I is provided with two cams t, u, which act
upon cam rolls w, a', at the outer ends of crank arms 61, e', secured to the journals e
of the central toggle members b, and serve to rock said members in a direction
opposite to that in which they are moved by the cams r, s, thus opening the toggles
as shown in dotted lines in Fig. 1, and returning the parts to their normal positions.
The several cams above described are so formed and timed as to permit the
reciprocating type-bed and reciprocating platen to remain at rest during such time
as is required for the forms to be inked and the paper to be drawn through
the machine for the succeeding impressions, by mechanism to be hereinafter
described.
By thus combining a vertically reciprocating platen co-operating with a
stationary type-bed and a vertically reciprocating type-bed co-operating with a
stationary platen with toggle mechanism arranged directly between and connected
with said reciprocating platen and reciprocating type-bed and adapted to move
the same simultaneously in opposite directions as above described, the power
exerted by the toggles is enabled to do double the work, as I am enabled to utilize
the force hitherto exerted in a downward direction against the stationary base or
bed to which the lower toggle member has been jointed, and which has hitherto
been wasted or rendered unavailable; that is, the downward pressure exerted by
the lower member of a toggle against a stationary bed or base is, by my con-
struction and arrangement of parts now made available to do the work of printing
by connecting the lower platen therewith, and as the weight of the reciprocating
platen is about equal to that of the reciprocating type-bed, it will be obvious that
they will balance each other in their alternate ascent and descent, the weight of
the one in its descent counterbalancing and assisting to raise the other in its
ascent, whereby the power required to operate the machine is reduced to a
minimum, and a great saving thereby effected.
To the main or central shaft I is secured a large gear K which is driven by a
pinion v shown dotted in Fig. 1, on the driving shaft L, the latter carrying as usual
a fly or balance wheel and fast and loose pulleys, not shown.
I will now describe the inking apparatus by means of which the forms are inked
after each impression is taken.
Each of the type-forms is inked by a series of

page_text: form-rollers d', Figs. 1, 5, 6, 17, 18, 19, and 20, the journals or shafts of which run
in bearings in carriages X, said carriages being adapted to run on horizontal
bars M, M, which form tracks or guideways therefor. The shafts of the form
rollers are forced downward to keep said rollers in contact with the type-forms by
means of spiral springs 54 as shown in Fig. 19. The bars M are supported by
rocker arms el pivoted thereto and secured to rocker shafts f¹, g'. The shaft f¹ of
the upper form roller track is provided with a crank arm 15, to which is pivoted a
connecting rod 16 carrying a cam roll h', which is acted upon by a cam wheel N
on the main shaft I, the lower end of the rod 16 having formed thereon a forked
guide, which embraces and slides upon the shaft by which it is supported..
The shaft is also provided with a crank arm k¹ which is connected by a rod
with a crank arm m¹, Fig. 1, on the shaft of the lower track M, whereby as the
connecting rod 16 is actuated by the cam wheel N, both of the tracks M, M, will be
simultaneously raised and lowered at the proper times. When the tracks M are
lowered, the form rollers will be at the proper level to take ink from the distributing
rolls or ink cylinders P at opposite ends of the tracks, and when these tracks are
raised.to their highest position, the form rollers will be at the proper level to ink
the type-forms.
By this construction we are enabled to place the ink cylinders P below the level
of the tracks M, thereby avoiding the wear which would otherwise be occasioned
by the form rollers riding up over the ink cylinders if the tracks M were not
capable of being raised and lowered; it being obvious that if the said tracks were
stationary, it would be necessary to have the ink cylinders project above the level
of the tracks in order that the form rollers might be brought into contact therewith..
The form rollers are moved forward and back over the type-forms to ink the
sane, by mechanism which will now be described, reference being had particularly:
to Figs. 1, 17, 18, 19, 20, 21, 22, 23, 24 and 25.
To each of the form roller carriages X is secured a pair of horizontal 'rack
bars 60, shown in Figs. 17, 18, 19, and 20, which slide in suitable grooves in
the framework and are actuated by gears 61. The upper gears 61 mesh with and
áre driven by two gears 63, Figs. 17 and 18, on a shaft A', said gears 63 also
meshing with intermediate gears 64 which mesh with the lower gears 61.
65 is a cam shaft carrying cams to be hereafter described, said cam shaft being
rotated at half the speed of the shaft I with which it is connected by means of a
shaft 55 and suitable bevel gears 56, 57, 58, 59, as shown in Figs. 1 and 18.
To the gear K on the shaft I is secured a crank pin 66, to which is pivoted one
end of a rack bar B', the opposite end of which is enlarged and so constructed as
to form a rectangular slot or aperture 67, the upper and lower edges or sides of
which are provided with teeth forming racks 68, 69. Placed between and in line
with these two racks upon and secured to the shaft A' is a pinion 70 of such diameter
that it will pass freely between the said racks without engaging with either. The
portion of the rack bar B' containing the racks 68, 69 is supported by and slides
within a guide 71 which is free to oscillate upon the shaft A, the journal box or
block 72 of which fits within a rectangular slot 73 in the guide 71, whereby said
guide is permitted to move vertically with relation to the shaft A' to bring either
one of the racks 68, 69 into engagement with the pinion 70. Upon one side of
the guide 71 is a turned hub or journal 74 Figs. 24 and 25, upon which is pivotally
secured the upper end of a vertical connecting rod 75, the lower enlarged end of
which is provided with a rectangular slot 76, Fig. 17, within which slides a journal
box or block 77 encircling the shaft 65.
Projecting from opposite sides of the lower end of the rod 75 as seen in Fig. 18,
are two studs 78, 79, carrying anti friction rolls 80, 81, arranged one above and
the other beneath the shaft 65. These rolls are alternately operated upon by two
cams 82, 83, secured to the shaft 65, whereby the rod 75 is alternately raised.
and depressed at the proper times to bring the racks into engagement with the
pinion 70 as will now be described.
When the crank pin 66 is at the point 84, (Fig. 22) in its revolution, one of the

page_text: racks, in the present instance the rack 68, will be thrown into gear with the
pinion 70, as seen in Fig. 22, which is accomplished by the cam 83 acting upon
the roll 81, which draws down the rod 75 and rack guide 71 and causes the rack 68
to engage with the pinion 70, holding it in this position while the crank pin 66 is
travelling from the point 84 to the point 85, Fig. 22, or during one half of the
revolution of the shaft I. The moment the rack 68 has reached the limit of its
throw in this direction, and during the momentary rest in changing the direction
of throw, the rack 68 is withdrawn from engagement with the pinion 70 by the
cam 82 acting on the roll 80, which imparts an upward movement to the rod 75
and guide 71, the shape of the cam being such as to raise the guide 71 a sufficient
distance only to throw the rack 68 out of gear with the pinion 70, but not enough
to cause the opposite rack 69 to engage with the said pinion. Both racks are now
in a position to clear the pinion 70 and remain so while the crank pin 66 is moving
from the point 85 back to the point 84, as shown in Fig. 21, thereby permitting the
shaft A' to remain at rest during the latter half of the revolution of the shaft I.
As soon as the crank pin 66 has reached the point 84 the cam 82 acting on the
roll 80 produces a still further upward movement of the rod 75 and guide 71
sufficient to engage the rack 69 with the pinion 70, and as the rack imparts motion
to the shaft A only while the crank pin 66 is travelling from the point 84 to the
point 85, it follows that the shaft A¹ will be rotated in a direction the reverse of
that imparted to it by the rack 68. As soon as the rack 69 has arrived at the limit
of its throw in this direction, it is disengaged from the pinion 70 by the action of
the cam 83 on the roll 81, which draws down the guide 71 and holds the rack 69
just out of contact with the pinion during the remaining half revolution of the
shaft I, immediately after which the cam 83 still further draws down the guide 71
and again engages the rack 68 with the pinion, when the operation continues as
before, the pinion 70 being thus operated upon alternately by the racks 68, 69, with
an interval or period of rest between each engagement equal to that occupied by a
half revolution of the shaft I, and consequently the shaft A' is first rotated in one
direction during a half revolution of the shaft I, which causes the crank pin 66 to
travel from the point 84 to the point 85, then allowed to remain at rest during the
completion of the revolution of the said shaft I, then rotated in the opposite
direction during the first half of the next revolution of the shaft I, which causes
the crank pin 66 to travel from the point 84 to the point 85, and again allowed to
remain at rest during the completion of the revolution of the said shaft I, then
rotated in the opposite direction during the first half of the next revolution of the
shaft I, which causes the crank pin 66 to travel from the point 84 to the point 85
and again allowed to remain at rest during the completion of this revolution of the
shaft I, the operation being then continued as before.
It is obvious that when the racks 68, 69, are both disengaged from the pinion 70 a
locking device must be employed, otherwise the shaft A₁ would be liable to be
turned in either direction by the momentum of the roller carriages X, and thus
throw the teeth of the pinion out of alignment with the racks, so that they would
not properly engage therewith when operated by the cams 82 and 83. To prevent
this I provide a locking device consisting of a wheel 86 having a notch 87 with
which engages a locking dog 88 which is supported by and slides in a suitable
guide 89 and is operated by a lever 90 connected therewith and pivoted at 91 to a
suitable support on the framework, said lever 90 being actuated by the rod 92
forked at its lower end to embrace the shaft 65 as shown in Figs. 21 and 23, and
carrying an anti friction roll 93 working in a cam groove 94 in the face of the cam
wheel 95, the cam being so shaped and timed as to cause the locking dog 88 to enter
the notch 87 of the wheel 86 the instant before the rack 68 or 69 has become
disengaged from the pinion 70, whereby the shaft A' is securely locked and
prevented from being rotated in the slightest degree by the momentum of the roller
carriages X after its pinion 70 has ceased to be acted upon by either of the
racks 68 or 69. The locking dog remains in a notch of the wheel 86 until the
moment that the opposite rack has become engaged with the pinion, when it is

page_text: withdrawn by the action of the cam wheel 95, and the operation continues as
before the holding of the shaft A' in the exact position in which it is left by either
of the racks 68 or 69 being thus rendered certain, whereby all liability of the
mechanism becoming deranged is obviated and its positive action insured.
By means of the above described mechanism, the form-rollers are first moved
across the type forms in one direction to ink the same, then allowed to remain at
rest while the impression is being taken, then moved across the type-forms in the
opposite direction and allowed to remain at rest while the next impression is being
taken, when the operation continues as before.
The roll of paper Q is mounted on a horizontal shaft, the journals of which rest
in suitable bearings in the framework, as shown in Fig. 1. The web of paper R
from this roll Q passes over guide-rods 20, 21, and under a rod 22, thence
horizontally between the reciprocating platen E and the stationary type-bed B,
thence under a guide-rod 23 and over a guide and take-up roller 24 and horizontally.
between the upper stationary platen C and the reciprocating type-bed D, after.
which it passes under a horizontally adjustable guide-rod 25 to the feed or drawing
rolls 26, 27, 28, between which it is tightly gripped and by which it is fed or drawn
forward intermittingly after the impressions have been taken; the length of paper
drawn forward at each operation of the feed-rolls corresponding to that of a single
detached sheet after it is printed. The shaft of the lower or main feed roll 26 is
provided with suitable well known mechanism, not shown, whereby it is
rotated intermittingly at the proper times as required. The upper feed
rolls 27, 28, bear upon the margins of the paper as usual, these rolls
being moved solely by the frictional contact of the lower feed roll 26
with the paper between said roll 26 and the rolls 27, 28. The shafts 29, 30,
of the rolls 27, 28 are mounted in curved arms n¹ projecting from a horizontal
shaft p', the shafts 30 of the rolls 28 being supported in fixed bearings at the outer
ends of the arms n', and the shafts 29 being supported in boxes 31, Fig. 12, adapted
to slide within slots in the arms n', each box having behind it a spiral spring 32,
which acts to force the roll 27 constantly toward the lower roll 26. To one end of
the shaft p is secured an arm q', to the lower end of which is pivotted a rod
having a screw thread at its outer end, over which is fitted a threaded sleeve s¹
provided at one end with a hand-wheel 33, and at its opposite end with a conical
point which enters a correspondingly shaped recess in a bearing block 34, whereby
by turning the screw-sleeve s¹, the rolls 27, 28, may be made to bear with more or
less force upon the paper passing over the feed-roll 26, the springs 32 behind the
rolls 27 causing the latter to bear upon the periphery of the roll 26 with
approximately the same force as the rolls 28, and by thus arranging a series of
pressure rolls to bear at different points around the circumference of the main feed
roll, instead of in a single line only, the hold or frictional contact of the rolls upon
the paper is materially increased, and the positive feed of the web thereby insured,
as all liability of slip is avoided.
As the web R is stretched tightly under the surface of the lower or reciprocating
platen E when the latter descends to produce the impression, it will be evident that
it would become slack on the ascent or return movement of said platen, hence it
becomes necessary to employ a take-up device, which I will now describe. The
journals of the guide-roll 24 are mounted in bearings in blocks t¹ made adjustable
upon horizontal bars S, Figs. 1 and 14, one on each side of the machine; said bars
being arranged to slide horizontally in suitable guideways on the frame A. Each
bar S. is provided on its upper side with rack teeth w', with which engages a toothed.
sector a², secured to a horizontal rock shaft 18 having its bearings in the frame-
work, and provided outside the framework with a slotted arm, to which is
adjustably secured a rod c², the lower end of which is jointed to an arm d' pivotted
to the framework, said rod c³ at its junction with the arm d² carrying a cam roll e³,
which fits within and is acted upon by a cam groove T on the inner face of the
main-gear K, and thus through the connections described, as the shaft 18 and
toothed sectors a² are rocked in the proper direction, the horizontal bars S will:

page_text: be forced outward in the direction of the arrow, Fig. 1, thus causing the roller 24
to take up the slack of the web R as the platen E rises, and keep it tightly
stretched in its proper position against the under surface of the said platen, the
movement of the bars S being properly timed to correspond with its upward and
downward movement.
When that portion of the web R between the guide rod 23 and the guide and
take-up roller 24 assumes different angles, as occurs when said web is to be cut up
into sheets of different lengths, the take-up roller 24 is adjusted on the bars S to
produce the proper register of the two impressions on opposite sides of the sheet,
and at the same time the pivot of the rod c² is adjusted in the slot of the arm 62 to
vary the amount of movement of the bars S to cause the roll 24 to properly take up
the slack of the web; it being necessary to increase the movement of the bars S
in proportion as the roll 24 is moved on the said bars S toward the centre of the
machine.
I will now describe the tympan-frame and its operative mechanism by which it is
raised and lowered to bring the tympan-sheet tightly up against the surface of the
platen, and lowered to enable said sheet to be easily drawn out from under the
"blanket."
Each platen has a tympan frame W, Figs. 7, 8, 9, 10 and 11, which is provided
with lugs f, g, having inwardly projecting pins 35, 36, which are adapted to fit
or hook over and slide upon the lips or flanges 2 at each end of the platen as
seen in Fig. 11, said flanges thus forming guides or tracks which support the
tympan frame W, and upon which it is slid in and out as occasion may require.
The tympan sheet is secured as usual to the cross bar 52 at the inner end of
the tympan frame and has its opposite end fastened to a rotary take-up bar k²,
Fig. 9, provided at one end with a retaining ratchet and pawl, not shown, whereby
the tympan sheet is stretched tightly across the frame in the ordinary manner.
12 is a horizontal rock shaft supported in bearings in lugs projecting from the
platen, and to one end of this shaft 2 is secured a bell crank m² and to the
opposite end an arm n², the horizontal arm 50 of the bell crank m² and the arm n²
being each cut away at the outer end on the upper side as seen at 37, forming a
shoulder, shown dotted; said shoulders forming stops against which the pins 36
are brought into contact when the tympan frame is pushed in as shown dotted in
Fig. 9, in which position the pins 36 rest upon the cut-away ends of the bell
crank lever m² and arm n², and as the lugs g' are of greater length than the lugs f
the tympan frame will incline downward from front to rear when it is fully pushed
under the platen, and consequently the bar 52 of the tympan frame will not come
into contact therewith as it is pushed in.
To the upper arm of the bell crank lever m² is pivotted a rod p² provided at its
opposite end with a handle q² and retaining notches 2, which engage a lug or
projections on the platen to hold the bell crank in place when adjusted, and after
the tympan frame has been pushed in under the platen, the said bell crank is
rocked by pushing in the rod p², which causes the arins 50, n2, on which the pins 36
rest, to raise up the tympan frame into the position shown in full lines in Fig. 9,
and thus bring the tympan sheet tightly up against the under surface of the platen
into its proper working position.
When it is desired to draw out the tympan frame, the rod p² is pulled forward
by means of its handle 92, thereby lowering the inner end of the tympan frame
and causing the tympan sheet to drop away from the platen, when it can be easily
-drawn out as required.
Having now particularly described and ascertained the nature of my said inven-
tion, and in what manner the same is to be performed, I declare that what I
claim is :-
1. In an intermittent web-printing machine, the combination, with two recipro-
cating and two stationary plates OF members arranged in pairs one plate or

page_text: mechanism arranged between said reciprocating plates or members directly under
the one and over the other, whereby the pressure is applied directly under and
over the impression surfaces, said mechanism being arranged to separate or force
the said reciprocating plates or members away from each other to produce the
two impressions, substantially as set forth.
2. A web-printing machine having a lower stationary type-bed and an upper
stationary platen arranged face to face, said type-bed being at the bottom and said
platen at the top of the machine, in combination with a lower vertically recipro-
cating platen co-operating with the lower stationary _type-bed and an upper
vertically reciprocating type-bed co-operating with the upper stationary platen,
whereby the types on both type-beds are held face upward; said type-beds and.
platens being arranged in line one above the other, and the reciprocating platen
and reciprocating type-bed being connected together by toggle mechanism arranged
between said reciprocating platen and reciprocating type-bed directly under the
latter and over the former, whereby the pressure is applied directly under and
over the impression surfaces, said mechanism being arranged to separate or force-
the said reciprocating platen and reciprocating type-bed away from each other to.
produce the two impressions, substantially as set forth.
3. In an intermittent web-printing machine, the combination, with a vertically
reciprocating platen co-operating with a stationary type-bed and a vertically
reciprocating type-bed co-operating with a stationary platen, substantially as
described, of connecting toggle mechanism arranged between said reciprocating
platen and reciprocating type-bed directly under the latter and over the former,.
whereby the pressure is applied directly under and over the impression surfaces,.
said mechanism being arranged to separate or force the said reciprocating platen.
and reciprocating type-bed away from each other to produce the two impressions,.
substantially as set forth.
4. In a web-printing machine, the combination, with a vertically reciprocating
platen, co-operating with a stationary type-bed, and a vertically reciprocating
type-bed co-operating with a stationary platen, substantially as described, of the
toggles G, G, arranged between said reciprocating platen and reciprocating type--
bed and serving to connect the same together, whereby they are caused to move-
simultaneously in opposite directions, and balance each other, said toggles having
central oscillating members provided with arms p, b, c', the central shaft I
provided with cams r, s, t, u, adapted to act upon the arms p, b', c¹ of the
members b, b, to alternately open and close the toggles, substantially as described.
5. In a web-printing machine, the combination, with the reciprocating platen E,.
and a stationary type-bed B, of the toggles G, G, arranged between and connecting
said platen and type-bed and having their central members provided with.
arms p, b, c, the central shaft I provided with cams r, s, t, u, adapted to act upon
the said arms p, b, c, to alternately open and close said toggles, and the horizontal
rods l, m, connecting the upper and lower joints of one toggle with those of the
opposite toggle, substantially as and for the purpose set forth.
6. In an intermittent web-printing machine, the combination, with the type-
form, the form-rollers d', the ink or distributing cylinders and means for traversing
the form-roller carriage to bring the form-rollers over the type-form and then
over the distributing cylinders, of the vertically movable form-roller track or
guideway and means for raising and lowering said track to bring the form-rollers.
alternately into contact with the type-form and ink-cylinders, substantially as
described.
7. In a web-printing machine, the combination, with the form-roller tracks M,.
of the rocker shafts f', g', provided with arms el pivoted to the tracks M, and
suitable connecting mechanism operated by a cam for oscillating the rocker shafts,.
whereby the tracks M are raised and lowered, substantially as and for the purpose
set forth.
8. In a web-printing machine, the combination, with the co-operating type-beds
and platens, of the take-up device for the web consisting of the horizontal sliding

page_text: :
bars S carrying the web supporting roll 24, and means for reciprocating said.
sliding bars whereby the slack of the web is taken up at the proper time,
substantially as set forth.
9. In a web-printing machine, the combination, with the co-operating type-beds
and platens, of the horizontal sliding bars S provided with rack teeth io', and
carrying the web supporting roll 24, the rock shaft 18 with its toothed sectors a
and slotted arm 62, the rod 2, arm 2, and the actuating cam T, all operating
substantially as set forth.
10. In a web-printing machine, the combination, with the feed roll 26, of the
shaft p provided with arms n' carrying rolls 27, 28, the arm q', rod ¹, provided
with the screw sleeve s¹ and the bearing block 34, all operating substantially as and
for the purpose described.
11. In a web-printing machine, the combination, with the lower feed roll 26,
of the rolls 28 mounted in fixed bearings at the ends of the arms n' of the shaft p',
the rolls 27 mounted in yielding bearings in said arms n', the springs 32, the arm g'
secured to the shaft p the rod 1 having the adjusting screw s', and the bearing
block 34, whereby the pressure of the rolls 27, 28, on the paper can be regulated,
substantially as set forth.
12. In a web-printing machine, the combination, with the sliding tympan frame
and the platen, of arms adapted to engage the said tympan frame when pushed in
to raise and lower the same, and means for operating the said arms, substantially as
set forth.
13. In a web-printing machine, the combination, with the platen baving lips
or flanges h², of the tympan frame W provided with lugs f, g, having inwardly
projecting pins 35, 36, adapted to fit or hook over and slide upon the lips or
flanges of the platen, the lug g2 being longer than the lug 2, whereby the
tympan frame is inclined downward from front to rear when pushed in, the
rock shaft with its bell crank m² and arm n² adapted to fit under the pins 36
of the tympan frame, and the rod p² pivoted to said bell crank and provided
with a locking or retaining device, whereby the said bell crank and arm are
actuated to raise and lower the tympan fraine, and hold it in position, substantially
as set forth.
14. In a printing machine, the combination, with the shaft A¹ provided with
a pinion or gear 70, of a rack bar B' having a rectangular aperture or slot provided
with upper and lower racks 68, 69, said pinion being placed within said aperture, a
supporting guide 71 for the rack bar, a crank pin 66 from which the motion is to
be transmitted to the pinion carrying shaft, said crank pin being connected with said
rack bar, a guide rod 75 connected with the rack guide 71, and cams for
operating the same whereby the pinion is alternately engaged with the racks and
is operated thereby only while the rack bar is travelling in one direction; said
racks being held out of engagement with the pinion when the rack bar is travelling
in the opposite direction, substantially as described.
15. In a printing machine, the combination of the shaft I having a crank and
crank pin 66, the rack bar B' provided with the racks 68, 69, the shaft A' carrying
the pinion 70, the guide 71 supporting the rack bar B and provided with a rod 75,
the shaft 65 rotating at a rate of speed different from that of the shaft I, the
cams 82, 83 adapted to raise and lower the rod 75 and guide 71 to throw the racks
alternately into and out of engagement with the pinion 70, said pinion being
rotated by said racks when the rack bar is travelling in one direction only during a
half revolution of the shaft I, and said racks being both held out of engagement with
the pinion during the remaining half revolution of the shaft I, substantially as and
for the purpose set forth.
16. In a printing machine, the combination, with the shaft A¹ and its pinion 70,
and the rack bar B' connected with a crank on the shaft I, of the guide 71 adapted
to support the rack bar and having a slot for the shaft A', the rod 75 depending
from the guide 71 and provided at its lower end with a slot, and anti friction
rolls 80, 81 and the shaft 65 passing through the slot of the rod 75, and the