Improvements in Mechanism for Converting Rotary into Reciprocating Motion.
Year: 1899

page_text: Date of Application, 25th Apr., 1899-Accepted, 29th July, 1899
COMPLETE SPECIFICATIVA.
Improvements in Mechanism for Converting Rotary into
Reciprocating Motion.
A communication from abroad by C. B. COTTRELL & SONS, Co., a corporation
organized under the laws of the State of New Jersey, and having its principal
place of business at Jersey City, New Jersey, and other places of business
at Stonington, Conn., and New York City, New York, United States of
America.
I, JOHN CORRY FELL, of the Firm of Fell & James, of No. 1, Queen Victoria
Street, in the City of London, Chartered Patent Agent, do hereby declare the
nature of this invention and in what manner the same is to be performed to be
particularly described and ascertained in and by the following statement:-
My invention relates to mechanism for converting rotary into reciprocating
motion, and has for its main object the adaptation of mechanism to produce
reciprocatory motion from rotary motion.
In the accompanying drawings:-
1:
Figure 1 is an end view of a mechanical movement embodying my improve-
ments.
Figure 2 is a horizontal section of the same on the line w, w, of Figure 1.
Figure 3 is a longitudinal vertical section of the whole machine, taken on the
line,, of Figure 2.
Figure 4 is an enlarged plan view of the newly-devised mechanism with portions
of certain of the parts broken away.
Figure 5 is a similar view but with the moving parts in different positions.
Figure 6 is a vertical section taken at the line y, y, of Figure 4.
Figure 7 is a similar section taken at the line y, z, of Figure 5.
Figures 8, 9, 10, 11 and 12 are detail sectional views in plan on a smaller
scale to illustrate the operations of the various parts at different times or in
different positions of the rack frame or moving bed,. and which will be herein-
after more specifically referred to.
Figures 13 to 24 inclusive are views similar to Figures 1 to 12 inclusive but
showing a modification of the invention.
The invention has been designed more particularly for use in connection with
the reciprocating beds of printing presses but it may be advantageously employed
in various other kinds of machines.
The bed or other body to be reciprocated is moved longitudinally back and
forth as heretofore by means of two longitudinally-arranged toothed racks con-
nected to the bed or reciprocating part and a constantly revolving toothed pinion
which alternately engages with said racks. Means are provided for properly
guiding the pinion into and out of engagement with said racks at the ends of
the strokes of the bed or reciprocating member; means are also provided for
starting the bed in each direction with a slow movement and gradually accelerat-
ing its speed until the revolving pinion engages with one or the other of the
said racks and moves the bed at full speed, and for also gradually retarding

page_text: the bed during the completion of its stroke in each direction and just prior
to its stoppage and restarting it again in the opposite direction.
The invention will first be described with reference to Figures 1 to 12
inclusive.
For the purpose of this case, 1 may represent the reciprocating bed of a
printing press and this may be mounted for its movement in any suitable way
in the framing 2 of the machine.
To the underside of the bed are rigidly connected two vertically-arranged
straight racks 3 disposed longitudinally of the bed and in this case in the same
vertical plane, or one directly above the other and with the teeth of one rack
facing those of the other. These racks are preferably attached by screws to an
open frame or casting which is rigidly attached to the bed and in the form
shown consists of two longitudinal bars 4, one over the other united at their ends
by integral curved bars or members 5 and vertical bars 6.
At each end of the rack frame and attached to the curved member is a semi-
circular or curved rack 7.
8 designates the driving gear or pinion which alternately engages the straight
racks 3, and 9 designates a smaller gear or pinion, mounted rigidly and eccentri-
cally of the axis of rotation of the gear S, but arranged to turn therewith and mesh
with the curved end rack 7, when the gear 8 is leaving one straight rack and
while it starts to re-engage the other straight rack, and during the time the
gear S is wholly out of mesh with both straight racks.
The driving gear 8 has a slight rising and falling motion to disengage from
one rack and to engage the other, and hence the diameter of this gear is less
than the distance apart of the oppositely, disposed racks. In order to afford the
gearing the necessary up and down movements its rotating shaft 10 is mounted
eccentrically in a bushing 11 fitted in an eye or bearing at the upper end of a
standard or bracket 12 secured to the base of the frame. To the outer end of
said bushing is connected a crank arm 13, to which is jointed at 14 one end of a
link or pitman 15 whose opposite end is slotted or provided with an open frame 16
that embraces and slides upon a square block 17, mounted loosely on a shaft 18,
extending transversely of the machine and mounted in suitable bearings.
Between the ends of the pitman or link is attached a roller 19 that works in
a grooved cam 20 formed in the face of a disk or wheel 21 fast on the shaft 18.
This cam is so shaped and proportioned as that at the proper times it moves the
pitman longitudinally and causes it, through the crank arm, to turn the bushing
and thereby elevate or lower the shaft 10 and the driving gear 8 attached thereto,
so as to cause said gear while it is rotating to move bodily from one straight
rack towards the other, and which movement takes place when one of said
straight racks has run out of mesh with said gear at near the end of its stroke
and while the reversing of the bed is occurring under the action and control of
the mechanism to be hereinafter described. Just before the driven rack and the
gear 8 part company the guiding gear or pinion 9 strikes into mesh with one
of the curved racks and continues its engagement therewith until the main gear 8
has been moved up or down to come properly into mesh with the other straight
rack, which it then proceeds to drive at full speed.
The power may be applied at the shaft 22, which as shown is provided with the
usual pulleys 23, and on the inner end of said shaft, which is mounted in a
bearing 24 in the side frame and in a bearing 25 extended laterally from the
bracket 12, is provided a toothed gear wheel 26 that constantly meshes with and
drives the gear 8, which turns always in the same direction during the operation
of the machine.
The cam shaft 18 is provided with a large spur gear 27 which is driven by a
pinion 28 on the power shaft 22.
The mechanism thus far described comprises the means for giving the bed
its main movements back and forth and means for guiding the driving gear into
and out of engagement with the straight racks with an easy and certain action,

page_text: thus avoiding any shocks or thumping action which might otherwise occur when
the driving gear strikes into fresh engagement with either of the straight racks
immediately following the actual reversing operation to be presently described.
While I have shown the straight racks as located in the same vertical plane
and arranged to have the driving gear swing up and down to alternately engage
said racks, this, of course, is not essential so far as the main features of my
improvement are concerned, and in lieu of such a construction and mode of
operation, the straight racks may be offset and the driving pinion may engage
them alternately by a lateral sliding movement. And although I have shown
the curved end racks as semi-circular and continuous and as co-operating with
a continuous pinion or guiding wheel, it will also be understood that as far
as my invention is concerned these end racks, forming continuations of the main
racks, may be made in the form of sections or segments not continuous and the
guiding gear which co-acts therewith may be only a partial pinion or segments
of gears.
I shall now describe the reversing mechanism proper by which the bed is
gradually retarded at near the end of its stroke in either direction and gradually
accelerated after the end of the stroke has been reached and until the main
driving gear again takes hold of one of the main racks and drives the bed
for the major part of its stroke under the full speed of said gear.
Each of the bars 6 on the rack frame carries or is provided with a vertical
bearer or cross-head 29 with which co-operates a crank pin or stud 30 provided
with an anti-friction roller 31 that traverses the face of said bearer and operates
on one-half thereof gradually to check the speed of the bed and on the other
half gradually to accelerate the speed of the same. This crank pin is fixed at
the outer end of a crank arm 32 that is secured by screws 33 on the face of the
fixed guiding pinion or gear 9 and radially of the axis thereof. The center of
said crank pin is coincident with the pitch circle of the said pinion, which
pinion is one-half the diameter of the driving gear 8 and is so attached thereto
as that its pitch circle passes through the plane of the axis of the gear 8 and
through the pitch line of the teeth of said gear. The pitch circle of the guiding
gear 9 and the center of the crank roll pass through the centers from which the
curved racks 7 are formed; or in other words, as is shown in Figure 3, the pitch
lines of the gears 8 and 9 and the centers of the crank roll and curved rack
all coincide.
As far as the main features of my invention are concerned the bearers 29 may
be curved and concentric with the curved racks with their treads or faces arranged
to coincide with the pitch lines of the teeth of said racks, and the crank roller in
order to co-operate therewith may be fixed axially of the guiding gear 9, as shown
and described in prior patents in this art, but I prefer to use the straight vertical
bearers and the crank roll arranged as shown to work in conjunction therewith.
At each end of the rack frame is a downwardly projecting stud 34, provided
preferably with an anti-friction roller, which during the time of reversal of the
bed is to co-act with a cam-like device which may be attached to or formed of
a piece with a plate or disk 35, which is preferably horizontally arranged. There
are two cams 36 and 37, one arranged over the other, the lower cam 36 co-acting
with the stud 34 on the right of the frame and the cam 37 co-acting with the
stud 34 on the left thereof, the stud on the right being slightly longer than
the one on the left so as to reach the lower cam.
The cams are curved or cresent-shaped and mounted on the upper side of said
disk.
On the under side of the disk is attached by two upwardly passing screws 42
a pinion 43.
The pinion 43 is loosely mounted upon a shouldered stud or bolt 44 that is
threaded at its lower end and attached, eccentrically, by means of a nut 45 to
the back side of a bevel gear 46, and the said pinion 43 is thereby adapted to
rotate in engagement with the teeth 48, formed circularly on the inner edge of

page_text: a ring 49, that is supported at one side upon a short bracket 50, mounted on
a horizontal arm or bracket 51, and at its opposite side upon another short
bracket 52, mounted on the vertical standard 12.
The said bevel gear 46 is driven by a toothed bevel gear 60, fixed at the
inner end of a horizontal shaft 61 which has a bearing at its outer end in the
main frame and, passing through the vertical bracket 12, has an inner bearing
at the inner end of the cross arm or bracket 51, which at this end is attached
to the vertical standard 12 and at its outer end to the side frame of the
machine.
The shaft 61 bearing the bevel driving gear 60 is provided at its outer end with
a toothed gear 63 that engages with an idle or intermediate gear 64 mounted on
a stud or pivot 65 in. the side frame, and the said intermediate gear meshes
with the large spur gear 27 which is driven by the pinion 28 on the power
shaft. Thus by the power through the gear 28, gear 27, intermediate gear 64,
and the gear 63, the shaft 61 is rotated, and through the gear 60 the bevel
gear 46 is rotated, and the pinion 43 mounted thereon or connected thereto, is
caused to turn therewith and travel around the fixed ring 49 with the disk 35
and cams 36 and 37.
The pinion 43 turns independently on its own axis while it is being carried
around bodily with the bevel gear 46, thereby keeping the face of the cam in
contact with the downwardly projecting stud 34, and causing the bed positively
to make its full stroke in case it would otherwise fail to do so by reason of too
little momentum or too much spring resistance to the bed.
It will be understood that in this class of printing presses the bed is provided
with air springs or the like which operate to reduce the momentum of the bed
during the slowing down movements and which subsequently re-act to start the
bed in the reverse direction. It sometimes happens that there is too much
resistance in the springs and hence the momentum is all taken out of the bed
before it has completed its full stroke, and it is to provide for this contingency,
more especially, that the cam is caused to come around behind the depending stud
roll on the bed frame and by the continued rotation of said cam force or push
the bed along to the full end of its stroke. If the bed be nicely balanced as to
momentum and spring resistance the cam will act then simply to hold the
vertical hearer up against the crank roll 31 during the slowing down of the bed
and during the restarting of the bed in the opposite direction. In other words
when the cam is acting on the depending bed roll 34, the crank roll 31 is acting
on the vertical bearer, so that the bed practically is held firmly between the cam
and the crank roll during the entire reversing operation, the cam working on
the outer side of the bed, so to speak, and the crank roller on the inner side,
so that there is a sort of grasping action upon the bed by the aforesaid devices
which prevents any lost motion or excessive motion to the bed.
I shall now describe the operation of the reversing devices, referring more
particularly to Figures 2 and 3, and the series of diagrammatic views at Figures 8
to 12 inclusive.
Figures 2, 3 and 8 show the mechanism in corresponding positions, at which
time the bed has completed its full travel towards the left and has been stopped
and is about to be started in the reverse direction. As will be seen at Figure 3,
the main driving gear 8 is entirely out of mesh with both the longitudinal racks 3,
the guiding pinion 9 is in a position centrally of the curved rack 7 which it
is traversing, and the crank roll 31 is on the dead point or centrally of the
vertical bearer 29. The bed has reached the limit of its movement towards the
left and is about to be started towards the right by the crank roll. which at this
time is rotating upwardly and about the axis 10 of the main driving gear 8.
Immediately the crank roll starts above the horizontal position shown at Figure 3
its pressure upon the vertical bearer causes the bed to begin its movement
towards the right and this movement is gradually increased as the crank
approaches a vertical position. At about the time the crank has arrived in an

page_text: upright position, the main driving gear 8, which has been gradually lifting
bodily, strikes into gear with the upper main rack 3, and takes the bed at full
speed, whereupon the crank roll leaves the vertical bearer and the guiding pinion
leaves the curved guiding rack. The said crank and pinion then make one
revolution with the main driving gear and just before the main driving gear
runs out of mesh with the upper rack at the left-hand end, the guiding pinion
runs into mesh with the left-hand curved rack and the vertical bearer is simul-
taneously brought up against the crank roll, which at this time is near a vertical
line passing through the axis of the driving gear, and the further movement of
the bed towards the right is limited to the speed of the crank roller which soon
passes the vertical line and then descends along the vertical bearer as the latter
advances by the momentum of the bed until the dead point or horizontal center
of the axis of rotation of the crank is reached, the crank roll thus operating at
this time gradually to slow down the speed of the bed and finally wholly to arrest
its movement at such dead point. The travel of the crank roll (beyond the
dead point) on the face of the bearer operates to start the bed again in the
opposite direction, towards the left, and gradually to increase its speed. Just
before the descending crank roller reaches the aforesaid vertical line the main
driving gear comes into mesh with the lower straight rack 3, the guiding pinion,
running in mesh with the left-hand curved rack operating properly to guide the
main gear into mesh with the straight rack as before explained. Thereafter the
gear drives the bed towards the left.
At Figure 8 the crank is represented as in its horizontal position and as about
to move the bed towards the right, or to the position shown at Figure 9, where
the crank has now arrived at a vertical position and at which time the main
driving gear is engaged with the upper straight rack.
At Figure 10 the crank is out of operative engagement with the bearer and the
bed is moving at full speed towards the right by reason of the engagement between
the gear S and the rack 3.
At Figure 11 the movement of the bed to the right by the said gear 8 and
rack 3 has ceased and the bearer has come up against the ascending crank roll
which is substantially in a vertical position and controls the speed of the bed
for the remainder of its movement to the right.
At Figure 12 the movement of the bed to the right is shown as having been
completed and the bed is about to be started towards the left by the descending
crank roll acting on the lower half of the vertical bearer, and, as before explained.
just before or at about the time the crank roll leaves the bearer the main gear 8
runs into mesh with the lower rack 3 and the bed is continued at full speed
towards the left.
During the time the crank roll is operating gradually to reverse the movement
of the bed, the vertical bearer and hence the bed is held up against the crank
roll or prevented from getting away from the same by one or the other of the
rotating cams 36, 37, and one of the bed rolls 34.
Referring to Figure 8, it will be observed that at the time the crank roll 31
is about to ascend and move the bed towards the right the right-hand bed roll 34
is at about the center or dead point of the cam 36. During the ascent of the
crank roller to the vertical position shown at Figure 9 the cam 36 revolving in
the direction of the arrow makes a quarter of a revolution or arrives at the position
shown at Figure 9, and during this movement of the cam from the position shown
at Figure 8 to that shown at Figure 9, the bed roll 34 travels along in contact
with the inner face or edge of the cam and is controlled thereby, the movements
of the cam being properly timed relatively to the movements of the crank, so that
while the crank roll is acting on the vertical bearer the cam is acting on the
bed roller, thus confining the bed between the crank roller and the cam.
While the crank roll is in the horizontal position on the bearer and the bed
roll is at a midway position on the cam, as shown at Figure 8, the pinion 43
and the cam 36 carried thereby are in the position shown at Figure 4. The bevel

page_text: gear 46 rotating in the direction of the arrow marked thereon causes the
pinion 43 to travel in the same direction and by reason of the engagement of
said pinion with the internal toothed ring, said pinion is at the same time caused
to turn on its own axis and revolve in a direction opposite to that of the bevel
gear 46. In consequence of this bodily movement of the pinion with the bevel
gear 46, and of the independent rotary movement of said pinion about its own
axis, the cam 36 is caused to be kept in contact with the stud 34 thereby holding
the bearer 29 in contact with the crank roll 31.
The positions of the parts shown diagrammatically at Figures 8 and 9 corre-
spond with those shown at Figures 4 and 5. Thus while the bed roll is moving
from the position shown at Figure 8 to that shown at Figure 9, the cam 36
is given a movement of translation as well as a rotary movement and when the
parts have arrived in the position shown at Figure 9 the cam is ready to part
company with the bed roll and to allow it to pass by or out between the ends of
the cam,
as shown at Figure 10, at which time the main gear is in mesh with
the straight rack 3.
When the parts have arrived at the position shown at Figure 10 the internal
pinion 43 has made another quarter of a revolution around the internal toothed
ring or has arrived at the horizontal position again on the opposite side of the
center of the crank disk or bevel gear 46. When the pinion 43 has made three-
fourths of a revolution around the fixed ring or has come to the position shown
at Figure 11, the cam 37 comes to the position shown at Figure 11 and continues
to rotate in the direction of the arrow thereon until the position shown at
Figure 12 is reached. While the said pinion 43 is making the aforesaid three-
fourths of a revolution around the fixed ring, or is moving from the position
shown at Figure 10 to that shown at Figure 11, the bed has traveled from the
position shown at Figure 10 to that shown at Figure 11 and the bed roller 34 at
the left-hand end of the bed is now in position to co-act with the cam 37.
When the bevel gear 46 and pinion 43 have arrived in the horizontal position
indicated at Figure 12 the central portion of the cam 37 has arrived at the
bed roll and the bed has reached the limit of its travel towards the right. The
crank roll now begins to travel down the lower half of the vertical bearer and
the bed moves towards the left. During this time the cam 37 runs in contact with
the bed roll and hence keeps the bearer up against the crank roll and co-acts
in conjunction therewith to control this part of the movement of the bed, in a
similar manner to that in which the cam 36 controlled the starting of the bed
to the right, as explained with reference to Figures 8 and 9.
Depending upon the momentum of the bed in its slowing down, the cams will
have a variable action. That is to say, if there be too much momentum or too
little spring resistance, the cam will simply run around in contact with the bed
roll, but if there be too little momentum or too much spring resistance the cam
will then perform the duty of forcing the bed along to the final portion of its
intended stroke; but in the restarting of the bed in the opposite direction the
cam will always control the movement of the bed or confine it to the action of
the crank, whether there be too much spring resistance or too little.
Owing to the fact that the main driving gear 8 has an up and down swinging
motion to and from the main driving racks 3 arranged in the same vertical
plane, it is found in practice that two cams as 36 and 37 produce a better result
than one cam only, adapted alternately to engage the studs at the opposite ends
of the bed. But if the main driving gear be arranged to slide endwise to engage
offset racks a satisfactory result could be obtained with only one cam, as either 36
or 37.
Therefore I do not wish to be limited wholly to the use of two cams in
the following claims excepting where the two cams are specifically set forth.
While I have shown the cams as working in a horizontal position, they may,
of course, be arranged to work in a vertical position; the driving or actuating
parts being suitably mounted for that purpose and the bed rolls instead of

page_text: depending from the bed being arranged to stand out laterally or horizontally
therefrom.
Various other changes in detail construction and in the arrangement of the
parts of the mechanism additional to those hereinbefore pointed out may be made
without at the same time departing from the gist of my invention. For example
the cam may be constructed and mounted to work in the manner shown in
Figures 13 to 24 inclusive. In these views all of the mechanism is the same
as in Figures 1 to 12 inclusive, excepting the cam mechanism proper which
may be described as follows:-
The cam 70 is curved or cresent-shaped and mouthed on the upper side of
a disk 71 and the cam edge or working face of the device is preferably concentric
with the center of said disk.
On the under side of the disk is attached by two downwardly passing screws 72,
a gear wheel 73, at whose center is a downwardly projecting hub or pivot 74
that is seated in a hole or bearing 75 in a crank arm 76 that is attached by.
screws 77 to a pinion 78. The gear wheel 73 is preferably attached to the disk
eccentrically of its center and of the center of the cam face or edge, and hence the
hub or pivot 74 which is arranged centrally to said wheel is eccentrically arranged
with respect to the center of the disk and of the cam.
The pinion 78 is loosely mounted upon a shouldered stud or bolt 79 that
is threaded at its lower end and attached, eccentrically, by means of a nut 80,
to a crank plate or disk 81 provided at its edge with a circular series of down-
wardly and outwardly projecting gear teeth 82, and the said pinion 78 is
thereby adapted to rotate in engagement with the teeth 83 formed circularly on
the inner edge of a ring 84, that is supported at one side upon a short bracket 85
mounted on a horizontal arm or bracket 86, and at its opposite side upon another
short bracket 87 mounted on the vertical standard 12.
Upon the outer side of the fixed ring 84 and above the plane thereof is
mounted a short straight rack 88 which engages at all times the eccentrically
mounted gear or pinion 73 on the under side of the cam disk or plate 71.
The hub 89 of the toothed crank plate or bevel gear 81 is attached by a
spline or feather 90 to the upper end of a vertical shaft 91 that is stepped in a
bearing 92 at the bottom of the framework and is provided with an intermediate
bearing 93 in the cross arm or bracket 86, a collar 94 being attached to said
shaft on the under side of said bracket 86 to prevent it from moving upwardly.
The said bevel gear 81 is driven by a toothed bevel gear 95 fixed at the
inner end of a horizontal shaft 96 which has a bearing at its outer end in the
main frame and, passing through the vertical bracket 12, has an inner bearing
at the inner end of the cross arm or bracket SG, which at this end is attached
to the vertical standard 12 and at its outer end to the side frame of the machine.
The said cross arm 86 at its inner end is forked or formed with two branches 97
that pass around the bevel gear 95 on opposite sides and unite with the shaft
bearing portion of the arm, which at this point has a downwardly projecting
lug 86 that is attached to the vertical standard 12 by horizontally-disposed
screws.
The shaft 96 bearing the bevel driving gear 95 is provided at its outer end
with a toothed gear 98 that engages with an idle or intermediate gear 99 mounted
on a stud or pivot 100 in the side frame, and the said intermediate gear meshes
with the large spur gear 27 which is driven by the pinion 28 on the power
shaft. Thus by the power through the gear 28, gear 27, intermediate gear 99,
and the gear 98, the shaft 96 is rotated, and through the gears 95 and teeth 82
the bevel gear 81 is rotated, and the pinion 78 mounted thereon or connected
thereto is caused to turn therewith and travel around the fixed ring 84. The
crank arm 76 being attached to the pinion 78 moves therewith and the gear 73
pivoted on or in said crank arm moves bodily with the latter, and by reason of
its engagement with the short rack SS the said gear 73 and hence the disk 71

page_text: with
and cam 70 rigidly connected thereto are caused to oscillate about the pivot 74
while the said bodily movement of the gear 3 is occurring. The pitch diameter
of the pinion 78 is equal to one-half the pitch diameter of the teeth on the
inside of the fixed ring 84, and the center of the pivot 74 is on the pitch circle
of the pinion 78, and in consequence of the construction, proportion and arrange-
ment of parts, the pivot 74 is caused to travel always in a straight line parallel
with the motion of the bed or on a line represented by the section lines y¹ y¹
andy, Figures 16 and 17, while the pinion is traveling around in gear
the fixed ring 84 and while the crank arm is turning around with said pinion.
The pinion 78 turns independently on its own axis while it is being, carried
around bodily with the bevel gear 81, and likewise the gear 73 turns inde-
pendently on its own pivot while it is being carried along bodily by the pinion 78
or the crank arm thereon. But while the gear 73 turns on its true center the
disk 71 and the cam 70 do not turn on their own centers but on the center or
axis of rotation of the gear 73 and which is eccentric to the cam center, and
this eccentric movement of the cam is utilized for the purpose of causing the
bed positively to make its full stroke in case it would otherwise be unable to
do so by reason of too little momentum or too much spring resistance to the
bed.
The length of the cam is slightly greater than a semi-circle and one-half of
this cam acts upon the depending stud roll on one end of the bed frame, and the
other half of said cam acts upon the other depending stud roll at the opposite
end of the bed frame.
I shall now describe the operation of the cam mechanism, referring more parti-
cularly to Figures 14 and 15 and the series of diagrammatic views at Figures 20
to 24 inclusive. The crank mechanism and toothed gearing operate in the manner
hereinbefore explained with reference to Figures 1 to 12 inclusive.
During the time the crank roll is operating gradually to reverse the movement
of the bed the vertical bearer and hence the bed are held up against the crank
roll or prevented from getting away from the same by the rotating cam 70 and
bed roll 34.
Referring to Figure 20, it will be observed that at the time the crank roll 31
is about to ascend and move the bed towards the right, the bed roll 34 is at
about the center or dead point of the cam 70. During the ascent of the crank
roller to the vertical position shown at Figure 21 the cam 70 revolving in the
direction of the arrow makes a quarter of a revolution or arrives at the position
shown at Figure 21, and during this movement of the cam from the position
shown at Figure 20 to that shown at Figure 21, the bed roll 34 travels along
in contact with the inner face or edge of the cam and is controlled thereby, the
movements of the cam being properly timed relatively to the movements of the
crank, so that while the crank roll is acting on the vertical bearer the cam is
acting on the bed roller, thus confining the bed between the crank and the cam.
While the crank roll is in the horizontal position on the bearer and the bed
roll is at a midway position on the cam, as shown at Figure 20, the pinion 7S
and the crank 76 carried thereby, are in the positions shown at Figure 16, and
the gear wheel. attached to the cam is at the limit of its movement to the left
The
along the short rack 88, as shown at Figure 16 and also at Figure 20.
bevel gear 81 rotating in the direction of the arrow marked thereon now causes
the pinion 78 to travel in the same direction and by reason of the engagement
of said pinion with the internal toothed ring, said pinion is at the same time
caused to turn on its own axis and revolve in a direction opposite to that of the
bevel gear 81, the arrow being placed on the pinion to show the direction in
which it turns upon its axis. In consequence of this bodily movement of the
pinion with the bevel gear 81 and of the independent rotary movement of said
pinion about its own axis, the pivot or crank pin 74 is caused to travel always
along the line y¹ y₁ and the line y z¹, at Figures 16 and 17, and when the
pinion has moved bodily from the horizontal position of Figure 16 to the

page_text: vertical position of Figure 17, the pivot 74 has traveled from the dotted position
shown at Figure 16 to that shown at Figure 17, or in other words, about one-half
the length of the rack 88. This rectilinear movement of the pivot 74 causes a
bodily movement of the cam 70 in the same direction, and in consequence of
the cam gear 7 meshing with the straight rack SS, the cam is rotated at the
same time that it is being moved bodily along with the pivot 74. The positions
of the parts shown diagrammatically at Figures 20 and 21 correspond with those
shown at Figures 16 and 17, the cam, however, being omitted from Figure 17
in order to simplify the view. Thus while the bed roll is moving from the
position shown at Figure 20 to that shown at Figure 21, the cam is given a
movement of translation as well as a rotary movement and when the parts have
arrived in the position shown at Figure 21, the cam is ready to part company with
the bed roll and to allow it to pass by or out between the ends of the cam, as
shown at Figure 22, at which time the main gear is in mesh with the straight
rack 3.
When the parts have arrived at the position shown at Figure 22, the internal
pinion 78 has made another quarter of a revolution around the internal toothed
ring or has arrived at the horizontal position again on the opposite side of the
center of the crank disk 81, and in consequence of the construction and arrange-
ment the pivot 74 is carried to the end of its travel towards the right, and the
continued rotation of the crank disk and crank pin 78 will cause said pivot 74
to travel back again on the same line or in a direction towards the left, and
this movement of the pivot 74 will carry with it the cam 70, and owing to the
presence of the cam's gear 73 and the rack 88 the cam will rotate in the opposite
direction during this return movement of the pivot 74. When the pinion 78
has made three-fourths of a revolution around the fixed ring or has come to the
position shown at Figure 23, after turning several times first one way and then
the other, the cam comes to the position shown at Figure 23 and continues to
rotate in the direction of the arrow thereat until the position shown at Figure 24
is reached. While the said pinion 78 is making the aforesaid three-fourths of
a revolution around the fixed ring or is moving from the position shown at
Figure 22 to that shown at Figure 23, the gear 73 has traveled the full length
of the rack 88 from right to left and back again towards the right half way
or to the position shown at Figure 23, and in doing so has, of course, rotated or
oscillated the cam first one way and then the other, and of necessity while the said
gear 73 has made this movement for the whole length of the rack towards the
left and back again for one-half its length, the pivot 74, controlled by the
pinion 78 and its crank 76, has made a like excursion along the line y y¹ of
Figure 16, and meanwhile the bed has traveled from the position shown at
Figure 22 to that shown at Figure 23 and the bed roller 34 at the left-hand
end of the bed is now in position to coact with the cam 70 or that half of the cam
on the opposite side of the half which acts upon the right-hand bed roll. During
the rotation of the cam in the direction of the arrow at Figure 23, it is adapted to
run in contact with the beu roll 34 at the left-hand end of the bed and hold the
bed properly against the descending crank roll. When the crank and pinion 78
have arrived in the horizontal position indicated at Figure 24 the central portion
of the cam has arrived at the bed roll and the motion of the cam is reversed,
or the cam begins to run in the direction of the arrow shown at Figure 24, at
which time the crank roll is running down upon the lower half of the vertical
bearer and is moving the bed towards the left. During this time the cam runs
in contact with the bed roll and hence keeps the bearer up against the crank roll
and co-acts in conjunction therewith to control this part of the movement of the
bed, just as the other half of the cam does during the starting of the bed to
the right, as explained with reference to Figures 20 and 21.
Referring again to Figure 20 the cam is in the position of holding the bed
relatively to the crank roll during the initial reversing of the bed by the action
of the crank roll, but before the cam arrived in this position it had a motion in

page_text: the opposite direction and during the last part of the movement of the bed
towards the left the cam followed up behind the bed roll, just as the cam follows
up behind the bed roll during the final part of the movement to the right, as
illustrated at Figure 23.
At Figure 20 it will be understood the bed is shown at the extreme limit of
its stroke towards the left and as about to start again towards the right, at
which time the cam also starts to reverse or move in the direction of the arrow
at Figure 20 to control the movement of the bed and finally to let the bed
roll out.
Thus it will be seen that one-half of the cam acts on the right-hand bed
roll and the other half on the left-hand bed roll; also that during the final or
slowing down movement of the bed, after the main gear 8 has left the straight
rack and the crank is in action, the cam turns in the proper direction to follow
the bed in this final retarded movement until the bed is arrested and then when
the crank roll starts to reverse the bed at an accelerated speed the cam is
reversed and at a proper speed to permit this reversal and yet hold the bed in proper
relation to the crank roll. Depending upon the momentum of the bed in the
slowing down movement of the bed, the cam will have variable action, that is
to say, if there be too much momentum or too little spring resistance the cam
will simply run around in contact with the bed roll, but if there be too little
momentum or too much spring resistance the cam will then perform the duty of
forcing the bed along to the final portion of its intended stroke; but in the
restarting of the bed in the opposite direction the said cam will always control
the movement of the bed or confine it to the action of the crank, whether there
be too much spring resistance or too little. Inasmuch as one-half of the cam
device acts only at one end of the bed and the other half at the opposite end,
it will be understood, of course, that in place of the unitary device shown and
described there may be two separate cams, without departing from the principle
of construction involved.
Having now particularly described and ascertained the nature of the said
invention and in what manner the same is to be performed, I declare that what
1 claim is:
-
1. Combining with a reciprocating bed or member and with means for reversing
the same, cam mechanism substantially as illustrated in Figures 1 to 24 inclusive,
and operating in substantially the manner described in the foregoing specification.
2. The combination of a bed or member, means for reciprocating the same,
means for reversing its direction of travel, and means for co-operating with the
reversing mechanism consisting essentially of a rotatory cam and a part on or
connected with the bed or member and independent of the reversing mechanism
for co-acting with said cam.
3. The combination of a bed or member, means for reciprocating the same,
means for reversing its direction of travel, and means for co-operating with the
reversing mechanism consisting essentially of a pair of rotatory cams and a part
on or connected with each end of the bed or member and independent of the
reversing mechanism and adapted to co-act with one of said cams.
4. The combination of a bed or member, means for reciprocating the same,
means for reversing its direction of travel, a projection at each end of said bed or
member and independent of the reversing mechanism, and a rotatory cam for
co-acting with each said projection during the period of operation of the reversing
means.
5. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism for the bed or member, and a rotatory and bodily movable
cam for co-acting with the bed or member and with the reversing mechanism.
6. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism comprising essentially a bearer on the bed or member

page_text: and a revolving crank, a projection on the bed, and a rotatory cam adapted to
co-act with said projection at the time the crank and bearer are co-acting.
7. The combination of a bed or member having oppositely arranged driving
1acks, a driving gear adapted to co-operate alternately with said racks to cause
the bed to move first one way and then the other, a revolving crank, a bearer
on the bed or member adapted to co-operate with said crank, and a rotatory cam
adapted to co-operate with said bed or member at the same time the crank and
bearer are co-operating therewith.
8. The combination of a bed or member having a pair of main driving racks,
a driving gear adapted to alternately engage said racks, curved rack extensions
at the ends of the bed, a revolving gear adapted to co-act with said racks, a bearer
at each end of the bed, a revolving crank adapted to co-act therewith, and a cam
adapted to engage with a part at either end of the bed and co-operate with the
crank and bearer in the acts of slowing down and stopping the bed and in the
restarting of the same in the opposite direction.
9. The combination of a reciprocating bed or member, a reversing mechanism,
and a cam adapted to act on the bed or member and force the same to the end
of its intended stroke, and also adapted to hold the same in proper relationship
to the said reversing mechanism while the latter is acting to start the bed in the
opposite direction.
10. The combination of a reciprocating bed or member, a reversing mechanism
comprising essentially a crank and bearer, and a rotatory cam adapted to act on
a projection on the bed to hold the said bearer against the said crank during
the restarting of the bed in the reverse direction.
11. The combination of a bed or member having straight racks, a driving
gear for reciprocating the same, a bearer and a revolving crank for slowing down,
stopping and restarting the bed in the opposite direction, and a cam adapted to
act on the bed or member and complete its stroke, after the main driving gear
has disengaged from either of said racks, in case the bed or member should be
unable to complete its stroke by momentum, and adapted also to hold the bearer
in proper relationship to the crank during the restarting of the bed in the opposite
direction and before the driving gear engages with the other one of the main
driving racks.
12. The combination of a bed or member provided with parallel driving racks,
a rising and falling driving gear adapted to engage alternately with said racks,
curved rack extensions at the ends of the bed or member, a pinion connected to
said driving gear and adapted to engage said curved racks, a revolving crank
connected to said driving gear, bearers at the ends of said bed for co-acting
with said crank, projections at the ends of said bed, and cams adapted to engage
with and follow said projections during the time the crank and bearers and
curved rack extensions and pinions are co-operating.
13. The combination of a bed or member, means for reciprocating the same,
means for reversing its direction of travel, a fixed toothed ring, a pinion mounted
on a crank arm or disk and traversing said ring, and a cam connected to said
pinion and adapted to co-operate with the bed or member and with the reversing
mechanism.
14. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism for the bed or member, a fixed toothed ring, and a crank
arm or disk revolving always in the same direction, a pinion mounted loosely
on the same and traversing said fixed toothed ring, and a cam rigidly connected
to said pinion and adapted to co-operate with the bed or member and with the
reversing mechanism.
15. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism for the bed or member, a fixed toothed ring, a disk, means
for rotating the same in one direction, a pinion loosely mounted on said disk,
and traversing said fixed ring, a pair of cams connected to said pinion and a
pair of projections on the bed or member adapted to co-operate with said cams.

page_text: 16. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism for the bed or member, a fixed toothed ring, a pinion
adapted to traverse the same, a disk rigidly attached to said pinion and bearing
a cam, a bevel gear or crank disk having teeth and carrying a pivot or stud for
said pinion, and means for rotating said bevel gear always in one direction
whereby the cam is carried bodily around with the bevel gear and is rotated in-
dependently in the opposite direction about the pivot of the pinion as an axis
of motion.
17. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism for the bed or member, a stud at each end of the bed
or member, a pair of cams, one for each of said studs, a plate carrying said
cams a pinion attached to said plate, a crank disk to which said pinion is
connected, a pivot for said pinion, a fixed toothed ring which said pinion traverses,
and suitable means for driving the crank disk.
18. The combination of a bed or member, means for reciprocating the same,
a reversing mechanism comprising essentially a bearer on the bed or member
and a revolving crank, a projection on the bed or member, a rotatory cam, a
pinion mounted on a crank and carrying said cam, and a fixed toothed ring for
said pinion.
19. The combination of a bed or member having straight racks, a driving
gear for reciprocating the same, a bearer at each end of the bed or member, a
revolving crank for slowing down, stopping and restarting the bed in the opposite
direction, a stud at each end of the bed, a cam for each stud, a pinion carrying
said cams, a fixed toothed ring with which said pinion meshes, a crank disk
upon which said pinion is pivotally mounted, and suitable driving mechanism for
causing the pinion to traverse the fixed ring and carry the cams into and out
of action with the studs.
20. The combination of a bed or member, a reversing mechanism comprising
essentially a crank and bearer, a rotatory cam adapted to act on a projection
of the bed, a pinion carrying said cam, a crank disk on which said pinion is
pivotally mounted, a fixed toothed ring for said pinion to traverse, bevel gearing
for rotating said crank disk, a bevel pinion 60, a shaft 61, the gears 63, 64, 27, 28,
and the power shaft 22.
Dated this 25th day of April 1800