Improvements in Machines for Planing Metal.
Year: 1887

page_text: Improvements in Machines for Planing Metal.
I JAMES YATE JOHNSON of 47 Lincolns Inn Fields in the County of Middlesex
Gentleman do hereby declare the nature of this Invention which has been com-
municated to me from abroad by William Sellers and John Sellers Bancroft of the
City and County of Philadelphia in the State of Pennsylvania in the United States of
America and in what manner the same is to be performed to be particularly described
and ascertained in and by the following statement :-
This Invention relates to that class of planing machines in which the metal to be
operated upon is mounted upon a table which reciprocates back and forth under a
cutting tool which is fed over the work.
In such planing machines as heretofore constructed, the gearing which transmits the
power of the driving belt to the table produces more or less vibration in the machine,
which is communicated to the cutting tool, the effect of which is exhibited upon the
work in the form of wave lines called chatters, at right angles to the motion of the
table and of greater or lesser intensity dependent upon the character of the vibrations,
but always visible to the naked eye, so for the better classes of work scraping and
fitting has to be resorted to.
In all such planing machines the speed of the reciprocating table under the cut
must be limited by the character of metal the tool is operating upon, and in such
machines, as heretofore constructed the reciprocating table being operated directly or
indirectly, through spur or bevel gearing, the speed of the return stroke is limited by
the capacity of this gearing to resist the shocks which a high velocity would impart, and
it is also limited by the necessity of avoiding a very high velocity to the pulley shaft
on the machine, the momentum of the driving pulleys in such case offering a greater
resistance to the reversal of motion at the end of each stroke than is offered by the
gearing and the reciprocating table, and it is also limited by the time in which the
feed can be effected and the tool raised and lowered, when this latter device is
employed; these feed and tool lifting motions having always heretofore been pro-
portioned to the speed of the table, and it is also limited by the shock which would be
produced by reversing the motion of the table at a high velocity when the gearing is
constructed and operated in the manner heretofore used.

page_text: In all planing machines heretofore constructed, the movement of the table in
addition to that required for the cut, must be sufficient to reverse the driving motion,
to raise and lower the tool and to effect the feed, excepting only when the forward
movement of this latter is effected on the return stroke of the table, if it is effected on
the forward stroke of the table and the movement is not completed before the tool
strikes the work, the feed gearing is liable to be broken, but to effect feeds in two
directions from one direction of table movement the gearing which actuates the feed
must be reversable, this complicates it and even if so arranged the operator would
probably neglet to change it.
In all such planing machines heretofore constructed, the movement of the table
reverses the driving motions to determine the length of the stroke, it is difficult
therefore, to stop the table at either extremity of its movement by manipulating the
reversing apparatus because in these positions, this apparatus is more or less under
the control of the table; The feed gearing and the tool lifting device, when this latter
is employed, are connected directly to the table or to the gearing which actuates it,
so that these movements can only take place while the table is in motion and they
are effected automatically either just before or just after the reversal of the table
movement; If the operator desires to reverse the motion of the table while under cut,
he must first throw the feed pawl out of gear to avoid doubling the feed on the
unfinished cut when automatic action is resumed, and if he throws this pawl out of
gear it cannot be replaced so as to continue the original cut and a mark upon the
work is sure to occur. The belt shifting and feeding devices in these machines as
heretofore constructed have been placed upon one side so that it is necessary for the
operator to work the machine from that side in order to control these movements at
will, but frequently occasions arise in which it is almost indispensable for the operator
to be upon the opposite side, this is always inconvenient and is sometimes attended
with risk to the machine or to the work. The reciprocating table in these machines
has heretofore been supported upon the bed in a variety of ways, but the form usually
adopted is that of a V guide in the bed and the converse of it upon the table, the
angle of these guides being such that the weight of the table and its work will be
sufficient to maintain it in position, against ordinary lateral strains from the cutting
tool. Two of such guides upon the bed and two upon the table are almost universal,
but some of the older machines were provided with one V guide and one flat.
Certain classes of work under cut have a tendency to lift the table and slide it side
ways in its guides and to prevent this the angle of the guides must be very sharp,
which involves a great increase of friction, a compromise has heretofore been resorted
to in the use of a more obtuse angle guide which would permit sliding under unusual
side strain, but sufficient in most cases to retain the table in position, and for extreme
cases a lighter cut must be resorted to; to avoid this diminution of work, machines
have been constructed with horizontal and vertical guides, and this involves the use of
a shoe to compensate for wear upon the vertical sides and this again to the adjustment
of this shoo by the workman; if he sets up the shoe too tight at one end, unequal
wear and loss of alignment must result, which destroys the value of the machine, and
practically it is impossible to avoid this, with this form of guide.
In a planing machine constructed according to this invention it is intended to
operate the reciprocating table by gearing which shall communicate the necessary
movement without shock or jar, so that the quality of the work will be improved and
no chatters will be produced, while the speed of the return stroke may be increased,
whereby a corresponding increase in quantity will result.
It is an object of this invention to provide such machines with driving pulleys
which shall always run in opposite directions and to connect and disconnect these
pulleys and the driving shaft at the proper times, in such manner that the parts in
connection with this shaft which have their motion reversed with that of the shaft,
shall be of the smallest possible diameter and weight, whereby the momentum of these
parts will offer the least resistance to the reversal of their motion.
It is a further object of this invention to make use of the table movement for
disengaging the driving motion only, and to provide other means for engaging it, so

page_text: that if the engaging apparatus is thrown out of gear, the table must stop at the end of
its stroke.
It is a further object of this invention to effect this engaging so that the reversal
of motion will take place without shock or jar.
It is a further object of this Invention while operating the engaging apparatus
automatically at prescribed periods, to retain control of it by the operator at all
times.
It is a further object of this invention to provide means for controlling the direction
of the table movement and the operation of the feeds, upon both sides of the machine,
so that the operator may stand upon either side, as the exigencies of his work may
require, and control the machine with equal facility.
It is a further object of this invention to operate the feeding and tool lifting devices
at a uniform speed whether the table be moving in one direction or the other.
It is a further object of this invention to effect these movements while the table is
at rest or changing its direction of movement.
It is a further object of this invention to provide a guide to support the
reciprocating table which shall effectually prevent any side movement of this table
with any character of work and whilst diminishing the friction will avoid the
necessity for any adjustment.
The power of the driving belt is transmitted to the reciprocating table through a
primary system of gearing consisting of a cogged pinion which has the contact
surfaces of its coggs arranged spirally about its axis, gearing with a cogged wheel
which has the contact surfaces of its teeth in straight lines in the direction of their
width, and a corresponding secondary system, which also has a cogged pinion with
the contact surfaces of its cogs arranged spirally about its axis, gearing with the cogs
of a rack upon the reciprocating table which have their contact surfaces in straight
lines in the direction of their width, whereby the necessary movement is com-
municated to the table without shock or jar, the production of chatters is avoided and
the speed of the return stroke may be increased so as to largely increase the quantity
of work produced.
Two driving pulleys are provided which revolve loosely upon the pulley shaft in
opposite directions and each pulley and the shaft are connected and disconnected by
means of a double friction clutch that will not seize, that will release upon the
removal of the clamping pressure, and of the smallest possible diameter that will
transmit the power of the belt and of the lightest construction.
The Invention further consists in providing adjustable stops upon the edge of the
table to operate levers upon the side of the bed through which the table communicates
motion to a shifter shaft connected with the double friction clutch on the pulloy shaft,
so that when the table has traversed the prescribed distance in one direction, one of
the stops will come in contact with one of the levers and disengage the clutch from
the pulley which is then moving the table, and when it is moving in the opposite
direction, the other stop will come in contact with the other lever and disengage the
clutch from the pulley which is moving the table in that direction, but so that motion
cannot be transmitted from the table through this mechanism for reengaging the
clutch with either driving pulley.
It further consists in providing a shaft operated continuously in connection with
which shaft a device for transmitting and arresting motion is arranged so that from
she continuous motion of this shaft, the motion transmitted will be intermittent, and
but half a revolution after each intermission, and determining the times when these
intermitting movements shall occur by the movement of an escapement plate operated
from the levers through which the table disengages the clutch from the driving
pulleys.
It further consists in providing a cam shaft which is operated from the device for
transmitting and arresting motion so as to make half a revolution in the same
direction, whenever the escapement plate is moved by the levers through which the
clutch is disengaged from a driving pulley, so that the half revolution of the cam may
then reengage the clutch with the opposite driving pulley.

page_text: It further consists in providing a clutch connection between this cam and the
double friction clutch on the pulley shaft, so that this clutch connection will yield
upon the occurrence of any undue strain upon the cam.
It further consists in providing an elastic connection between the shifter shaft and
the friction clutch on the pulley shaft, so that the tension of this connection may be
adjusted for either pulley, whereby the pressure with which this clutch will operate as
a brake to retard the motion of the table before it has the power to reverse it and the
time during which it so acts may be controlled.
It further consists in connecting this cam shaft with the feed and the tool lifting
devices so that the feed and the tool lifting shall be effected while the table is at rest
or changing its direction of movement.
It further consists in so arranging this cam that as it completes its half revolution,
it will pass out of gear with the clutch shifting mechanism so as to leave this mechanism
free from control by the machine.
It further consists in transmitting the motion from the levers to the escapement,
through a clutch on the shifter shaft so that when this clutch is thrown out of gear,
the escapement will remain at rest, the feed motions and tool lifting devices will not
be operated and the automatic movement of the table will cease at the end of its.
stroke, but the friction clutch on the pulley shaft may then be operated through a
hand lever on the shifter shaft, so as to move the table back and forth or to control
its position upon the bed.
It further consists in arranging the hand lever on the shifter shaft, so as to throw
the escapement clutch out of gear, so that the same hand lever may suspend all of the
automatic movements, while it will impart motion to the clutch which gives direction
to the motion of the table.
It further consists in extending the shifter shaft across the machine and upon each
end of this shaft providing a hand lever, either of which levers will suspend all of the
automatic movements while it will impart motion to the clutch whieh gives direction
to the motion of the table, so that the operator may have complete control of the
machine upon either side of it.
It further consists in providing the bed with a guide to support the reciprocating
table, which guide has two surfaces slightly inclined to a horizontal plane to sustain
the weight, and two other surfaces, perpendicular to the same horizontal plane or
slightly divergent from this perpendicular, to resist the side strains and in providing
the reciprocating table with a guide the converse of that upon the bed.
It further consists in providing the bed and the reciprocating table respectively
with two guides, one of which has four guiding surfaces and supports the table both
vertically and horizontally, while the other has but one guiding surface and supports
the table in a vertical direction only, whereby the fitting is simplified, undue strains
from variations of temperature are avoided and the friction is.reduced to a minimum.
In the accompanying drawings, Figure 1, represents a plan partly in section, of a
planing Machine embodying the present improvements, Figure 2, is a side elevation,
and Figure 3 an end elevation of Figure 1; Figure 4 represents an enlarged Section
of the bed and table, showing the improved bearing and guiding surfaces. Figure 5
is an elevation, partly in Section, in a vertical plane passing through the centre of the
pulley shaft, of the driving pulleys and clutches and mechanism for shifting the double
friction clutch, shown in gear with the forward motion pulley. Figure 6 is a Section
on the same plane showing the clutch shifting levers and cam in position for the back
motion pulley. Figure 7 is an enlarged Sectional view on the plane of the clutch
shifting levers showing these levers in their middle position. Figure 8 is a plan of the
parts shown in Figure 7, with the compensating springs removed. Figure 9 is a side
elevation of the feed motion stand, partly broken away to show the cam for operating
the double friction clutch, the shifter levers being in position for the forward motion.
Figure 10 is a Sectional plan of Figure 9 on the line. Figure 11 is an end
elevation of Figure 9. Figure 12 is a Sectional view of Figure 11 on the line yyyy
of Figure 10. Figure 13 is an enlarged view of the end of the pulley shaft showing
the slots through which the clutch shifting levers work. Figure 14 is an enlarged

page_text: view of the end of the rod for shifting the double friction clutch showing the enlarged
slotted end in which the ends of the clutch levers work. Figure 15 is an end view
of Figure 7, showing the pulley shaft and clutch shifting rod in Section. Figure 16
is an enlarged view of the bolt for adjusting the compensating spring for the back
inotion pulley. Figure 17 is an enlarged view of the revolving cam for operating
the double friction clutch, with the cord segment and lever for the tool elevator, and
the lever with the safety clutch for operating the driving clutch. Figure 18 is a side
view of the same parts at right angles to Figure 17. Figure 19 is an end elevation,
partly in Section, of the pulley frame and main upright in Figure 1, showing the
train of gearing for driving the escapement shaft. Figure 20 is an enlarged view of
the stops on the side of the table for adjusting the length of travel of the table, shown
in proper relation to Figure 9. Figure 21 is a Section on the line 2, 2, of Figure 9
of the hand reversing lever on the shifter shaft. Figure 22 is a Section through
Figure 21 on the line 1-1. Figure 23 is a Section through the reversing block
showing additional hand lever on the opposite end of the shifter shaft. Figure 24
shows the shifter levers and stops in position for the return motion of the table.
Figure 25 is a Section through a wedge and clamping bolt in the clutch in the return
motion pulley. Figure 26 represents an alternate method of constructing the lever
with the safety clutch for engaging the double friction clutch.
The driving arrangement is an improvement upon a previous Invention of William
Sellers, in which the table was provided with a rack driven by a curved or spiral
toothed gear on a diagonal shaft, operated from the pulley shaft by a primary system
of gearing consisting of a bevel wheel and pinion. With this form of construction
the action of the secondary system, that is, the spiral gear driving the rack is perfecty
smooth, and the planer so constructed does work that has not yet hitherto been
equalled.
The action of the primary system of bevel gears, however, is not so perfectly
smooth, and hence that machine, even with its secondary system of gearing, has a
tremor caused by the successive action of the primary gear teeth, which tremor
produces chatter marks on the surface of the work planed. The speed of the return
stroke is also limited by the speed at which it is possible to run these primary gear
wheels safely and quietly and to obtain the best results it is necessary that the teeth
of the bevel wheel and pinion should be very carefully cut and shaped and this
increases the expense and difficulty of constructing the machine.
C, Figure 1, represents the spiral gear of the secondary System according to the
above mentioned Invention secured to the driving shaft D which runs in suitable
bearings in the bed B and upright E. On the outer end of the shaft D is secured
the spur gear F of the primary system which is driven by its spiral pinion G secured
to the pulley shaft H which runs in bearings formed in the pulley frame J. The
spiral pinion G of the primary system is preferably placed above the spur gear F to
provide room for the driving pulleys above the bottom of the bed of the machine, so
as thereby to avoid the necessity which otherwise would exist, of placing these pulleys
below the floor on all large machines in which the bed rests directly upon the founda-
tion. This pulley frame is securely bolted to the upright E. The teeth of the spiral
pinion G, Sit in the spur gear F and these two gears constitute the primary system of
gearing. The sides of the teeth in the spur gear are tangental to the curved teeth of
the spiral pinion G; the action is then continuous like that of a screw and there is
absolutely no shock as the teeth enter and leave, so that by this arrangement the
motion of the driving pulleys can be cominunicated to the planer table without any
vibration, and the work produced is entirely free from chatters and hence requires
little or no finishing afterwards.
The smooth and uniform action of these spiral gears renders it possible to drive
them at very high speeds without shock or noise, and the return motion of the table
can, therefore, be at a much greater speed than has hitherto been possible.
The pulley shaft H carries two loose pulleys, viz.-one (1) for the forward motion
of the table, and another (K,) for the return motion thereof. These pulleys revolve
freely upon the shaft between the fast collar j, formed with the shaft and the screw

page_text: collars k, k, (Figure 5,). These pulleys are each provided with a taper seat preferably
of wood, adapted to receive the double friction clutch L, which is keyed to the shaft H
so as to revolve with it and at the same time slide freely along it on the raised central
collar. The double friction clutch Lis shown in the drawings as constructed entirely
of metal, to be as light as possible, while the diameter is the smallest that will transmit
the power of the pulleys safely, the object being to reduce the momentum of the
clutch to the minimum, that it may offer the least resistance to the reversal of its
motion when it engages with either pulley.
The interior surfaces of the clutches in each pulley are lined with wood, as two
metal surfaces might cut and seize. The wood is secured in place by a groove or
recess turned out in the pulley rim as shown in Figure 5, and into this groove,
blocks O, of hard wood, are fitted so that the end of the grain will form the friction
surface; the space between these blocks O, is made tapering, see Figure 25, and
wedges PP drawn up by bolts R R set the blocks 0, 0, firmly against the rim of the
pulley and so form a solid clutch, the interior being turned out to the same bevel as
the outside of the double friction clutch L. The weight of half the wooden blocks
and wedges is thus added to the weight of each pulley, the motion of the pulleys
being constant, increased weight of pulley will assist in overcoming the resistance of
the clutch L to the reversal of its motion without shock. When the planer is to be
used principally on short work requiring frequent reversals, producing heating and
expansion of the clutches, it will be found preferable to provide the double friction
clutch with wooden blocks secured, as for example, in the manner described in the
Specification of the United States Patent, No. 260,791, granted to William Sellers,
July 11th 1882, in which case the corresponding clutch seat in the pulleys should be
entirely of metal.
The collar, has a slot in it through which the pin o, slides. This pin fits in the
clutch and serves to couple it with the rod h, by which the clutch L, is engaged
with and disengaged from the clutches in the pulleys I and K In Figure 5, the
clutch L is shown in gear with the driving pulley I. The pulley shaft H has a hole
drilled through its centre to receive the rod h, which slides freely through it. The
rod h, has an enlargement on its outer end which is slotted through to receive the
short ends of the bell crank clutch shifting levers 1, 1, which pass through slots in
the pulley shaft. These clutch levers are pivoted as shown, in the sliding fulcrum
piece which slides easily on the outside of the pulley shaft H (see Figure 7).
The fulcrum piece n, Figures 7 and 8 is limited in its motion in one direction by
the adjustable stop collar p screwed and clamped on the end of the pulley shaft H.
The long ends of the bell crank levers 1, 1, are moved in and out by the diagonal
grooves p² in the sliding cam m, as it is moved along the pulley shaft H, the levers.l
being provided with projections on their ends as shown, which enter the grooves p2
which are continued at each end parallel with the pulley shaft H, so that when the
cam m is moved along the shaft until the ends of the levers 7, enter these parallel
grooves, the end pressure on the shaft H due to moving and holding the levers
ceases, and the parallel grooves resist the tendency of the levers to open or close, as
the case may be. The cam is always moved far enough, in engaging the clutches, to
bring the parallel grooves to the ends of the levers, thus always moving the levers
through the same angle, and hence the position of the adjustable collar P determines
the pressure with which the clutch L is forced into the driving pulley I, when
the cam m is in the position shown in Figure 5. When the cam m is moved into
the position shewn in Figure 6, the clutch is withdrawn from the pulley I by the
rod and drawn into and engaged with the return pulley K, the sliding fulcrum n
in this case has been drawn away from the stop collar pand is now shewn arrested
by the compression of the spring with which it is connected by the pin t, bolt
and adjustable nuts and w, by which the pressure of the spring is adjusted; this
spring abuts against the end of the pulley shaft H, and when compressed as shewn
in Figure 6, holds the clutch L into the pulley K, with the requisite pressure. The
springs, see Figure 7, fits loosely on the outside of the sliding fulcrum, and is
compressed between the adjustable stop collar p, and a shoulder on n. In Figure 7,
9,

page_text: the cam m, is shown in its middle position, the clutch L is now free from both
pulleys I and K, and the shaft H is at rest, the pulleys revolving freely on it without
driving it in either direction. The sliding fulcrum n is now balanced between the
two springs and s, and it will be seen that movement of the cam m in either
direction will first move the clutch levers and the rod h until the double friction
clutch L bears against the clutch in the pulley I or K; further movement of m in
the same direction will compress one of the springs and thus gradually increase the
pressure between the clutches until the maximum pressure required for driving is
obtained when the clutch is engaged, in which position the ends of the levers rest in
the parallel grooves in the cam m, as shown in Figures 5 and 6, thus releasing the
cam m from all end pressure due to the action of the levers 1. and the pulley in gear
with the clutch rests against its screw collar k, the pressure being all self-contained
in the shaft H, thus completely freeing it from all end pressure, and when the pulley
shaft His revolving in one direction, driven by one of the pulleys, and the clutch L
is shifted to the other pulley so as to revolve it in the other direction, by mechanisın
to be hereinafter described, the spring presses the revolving clutch, which has just
been withdrawn from one pulley, against the clutch on the opposite pulley, and its
compression determines the brake pressure which acts to bring the shaft H rapidly
to rest without shock, preparatory to firmly engaging with the clutch on the pulley
to drive in the opposite direction, and by properly proportioning the strength and
amount of compression of this clastic connection and the angle of the clutches, it is
easy to reverse the heavy planer table at high speed, without any shock or jar. The
angle of these clutches must be such that the friction surfaces will part the moment
the pressure which holds them together is removed, as any adhesion after this will
prolong the driving movement and when the opposite clutch is thrown into gear an
occasional shock will occur caused by the varying speed at which the reversal of
movement takes place; we have found, by practice, that when the friction surfaces
are at an angle with their axes of 20°, the reversal may always be effected without
shock. The lever u pivoted at a' in the pulley frame J, Figure 5 is coupled with the
cam m by a collar provided with trunnions resting in a fork in the end of the lever u,
the collar being connected with the cam m which turns freely in it without sliding by
a collared nut as shown in Figures 5 and 7, 8 and 15.
On the hub of the driving pulley I, Figure 5 is secured a spur pinion 61 which
through the intermediate wheel c' drives the gear wheel d' secured to the escapement
shaft M. which turns freely in bearings in the upright E, to the other end of the
shaft M is secured the ratchet wheel T, Figures 10 and 12. Between the ratchet
wheel T and the bearing of the shaft M. is the gear wheel V carrying the escapeinent
pawle (Figure 12). This gear is loosely fitted to the shaft M. so as to allow the
shaft to revolve freely within it, this mechanism with the escapement plate next
mentioned constitute a device for transmitting and arresting motion such as is shown
and described in the Specification of the United States Patent No. 34,217 issued
January 21st 1862 to William Sellers. The pawl e' is in the form of a bell erank
and is pivoted to the hub of the gear wheel V. (see Figure 12) its outer end resting
against the stop on the escapeinent plate W, the spring plunger presses against
the inner end of the pawl e¹ and whenever the stop h¹ is removed will throw it into
gear with the ratchet wheel T secured to the revolving shaft M and thus drives the
gear wheel V The outer end of the pawl e' comes alternately in contact with the
stops and ' on the escapement plate W, which has a motion at right angles to
the axis of the shaft as described for the stops in the Specification of the above
mentioned patent No. 34,217 when it is required to transmit rotary motion in one
direction only, the forward movement of the wheel V; carrying the pawl e then
throws the inner end of the pawl e¹ out of gear with the ratchet wheel T and
compresses the spring on ", the reaction of this spring would tend to reverse the
movement of the gear wheel V and so cause the pawl e¹ to engage again with the
ratchet wheel to be again thrown out by the stop. This would make considerabe
noise and be rapidly destructive of this part of the machine, and to avoid this
difficulty, we provide the retaining pawl which engages alternately with the two

page_text: lugs on the hub of the bevel and spur gear A' driven by the gear V, and thus
prevents re-action and keeps the pawl e¹ out of gear with the ratchet wheel, until the
pawle is again released from the stop g¹ or the pawl is preferably placed
so as to engage with stops on the spur wheel V but is shown on the wheel A' for
convenience in drawing.
The escapement plate W is moved up and down to release the pawl e¹ from the
stops hor g¹ by means of the escapement lever B B Figure 9, one end of which
engages with two lugs on the lower end of the escapement plate W. the other end is
formed as a counter-weight to balance the plate W; The lever B₁ is carried by and
turns freely on the sleeve C Figure 11 which is secured firmly in the stand D¹ bolted
to the feed gear frame E¹. The escapement plate W slides in bearings formed in the
feed gear frame E' and is kept in place by the stand D under which it slides freely.
The escapement lever B' is provided with a friction clutch which engages with the
friction clutch F' secured to the shifter shaft G¹ which is carried by suitable bearings
in the feed gear frame E' and feed stand H¹ on opposite sides of the machine;
secured to the shaft G' is the forked lever I' which is moved back and forth by the
shifter levers J and K operated by the stops L'M' secured to the table A in the
usual manner, sec Figures 9 and 11. The retaining friction clutch S fits loosely
upon the shifter shaft G¹ and is held from turning by the lug which fits oasily
between the short arms of the weighted lover Q supported at i the lever forces the
retaining clutch S against the clutch F secured to the shaft G¹ and so tends to slide
the shaft through its bearings, the clutch F¹ is thus held in gear with the friction
clutch in the escapement lever B₁ by a force due to the action of the weighted lever Q.
The frictional surfaces of these clutches should not be both of metal as indicated in
the drawings but of wood and metal, the wood being secured in the method above
described for the clutches in the driving pulleys, or in the manner described in
the Specification of the United States. Patent No. 260,791 July 11th 1882, granted to
William Sellers.
The retaining clutch S prevents any recoil of the shifter shaft G¹ when it is moved
in either direction by the stops L' M³, the first effect of these stops upon the shifter
shaft G¹ is to release the double friction clutch L from its driving pulley the second
is to press it against the opposite pulley so as to retard its motion without reversing
it and the pressure required for this must be exerted against the inclined surfaces of
the sliding cam m through the springs sor this pressure would cause the shifter
shaft G¹ to recoil after the pressure of the stops L¹ or M¹ was removed, the inertia of
the shifter levers and other parts attached or connected to the shaft Ġ¹ is such that
when these parts are suddenly set in motion by the stops L or M¹ they continue
their motion beyond the point to which the stops would positively push them and
hence leave space between the stop and the shifter lever for the recoil just mentioned
to occur. The retaining friction clutch S, which does not turn about its axis by its
friction reduces the amount of this extra motion and will effectually prevent the recoil
so that the brake pressure produced by the action of the stops will be maintained
until the lever u is further moved by the action of the revolving cam E2 and lever F2
to engage the clutch for driving in either direction. The lever B₁ is coupled with
the shifter shaft G₁ by a friction clutch so that the escapement pawl may be released
at the earliest possible moment when the table-stops come in contact with the shifter
levers and revolve the shifter shaft G₁ as the escapement plate W reaches the end of
its stroke it releases the pawl el from the stop g¹ or h¹ as the case may be, when the
friction clutch slips and allows the shaft G₁ to turn still further in its bearings without
risk of breakage; while the friction clutch is ready to reverse the motion of the
lever B with the first movement of the shaft G¹ in the opposite direction. On the
end of the shifter shaft G¹ is secured the reversing 'lever N which is coupled by
the connecting rod O with the lever u which moves the cam m before described, see
Figures 5 and 11. When for example the stop L¹ Figure 20 is carried by the
forward motion of the table so as to strike against the lever the forked lever I' is
moved and with it the shaft G¹ and reversing lever N this movement continues until
the clutch L Figure 5 has been withdrawn from the driving pulley I and pressed

page_text: :
against the return pulley K so as to retard its motion without reversing it until the
forward motion of the table ceases. If the planer table is running back, the stop M¹
will move the shifter lever K and as the table owing to its high speed has much
greater momentum, and hence requires more space to come to rest, the stop M¹ and
lever Kare so proportioned that when the stop M runs over the end of the lever K¹
the cam m Figure will have been moved far enough to withdraw the cluich L from
the return pulley K and force it against the pulley I with a pressure resulting
from the compression of the spring s sufficient to act as a powerful brake to retard
the motion of the table without however reversing the motion of the pulley shaft.
The stops L M merely withdraw the clutch L from the pulleys I and K and force it
against the opposite pulley so as to form a brake to retard the motion of the table, the
ends of the bell crank levers resting in the diagonal part of the grooves p² after the
brake pressure has accomplished its purpose, the clutch is firmly engaged with this
pulley by mechanism hereinafter described. The bevel and spur gear A Figures 10
and 12 before described, is secured to the shaft U which runs freely in a bearing
provided in the stand ¹ on the outer end of the shaft U is fastened the slotted
crank plate V¹ which by means of an adjustable crank pin and connecting rod moves
the gear segment W₁ pivoted at Z Figure 11 and gearing into the ratchet box X'
through a greater or less distance as the adjustable crank pin is moved from or
towards the centre of the crank plate V. The lower end of the gear segment Wis
provided with an arm which gives motion through the connecting rod to a
similar gear segment on the stand H on the left hand side of the Planer Figure 3.
These gear segments can thus be used to impart a feed motion to slide rests on each
upright of the Planer when such feed is not required, the bevel and spur gear A¹ may
run loose upon a stud secured to the stand E. The bevel wheel A is driven by the wheel A¹
and has a slot extending diametrically across its face in which is secured the crank
pin B2 which can be adjusted to any radius on the face of the bevel wheel A²; a
connecting rod (Figure couples this crank pin with the gear segment which
operates the ratchet box on the end of the feed screw or the feed rod as the case may
be, on the end of the cross head. The bevel wheel A² is formed with or secured to
the cam shaft D2 which turns freely in a bearing formed in the stand E', the inner
end of the shaft D2 has secured to it the cam E which serves to give motion to the
lever F. This lever is pivoted on the pin G2 secured to the stand E and has attached
to its lower end the connecting rod H2 which couples it with the lever N¹ secured to
the shifter shaft G¹. The lever F is formed in two pieces, as shown on larger scale
in Figures 17 and 18, the two parts being coupled together by a tongue and groove
with bevelled sides clamped in contact by a stud and spiral spring as shown. This
arrangement acts as a safety clutch for the system and when the resistance to moving
the lever F is too great from any cause, these bevelled sides ride over each other
compressing the spiral spring and allow the cam E2 to complete its stroke, moving the
upper part of the lever F but only transmitting through the connecting rod H the
strain required to lift the bevelled tongue out of its soat thus avoiding risk of breakage
of the machinery. The two parts of the lever F2 may be coupled by friction clutches
arranged in the same manner as described for the clutches F¹ and S, the friction
surfaces being clamped in contact by a nut and spring as shown in Figure 26 with
sufficient force to engage the clutch L with the pulleys I and K but not too tight to
prevent yielding under any undue strain, thus accomplishing the same purpose as the
bevelled tongue and seat shown and described.
The cord segment J2 is pivoted also on the pin G² and serves to operate the tool
lifting mechanism in the cross head; it is moved up and down by the curved con-
nection K Figure 17, which is pivoted to the segment at L2 and on the outer end has
a pin secured to it which moves freely in a hole in the cam E2 at M² as shown, so that
one half revolution of the cam E throws the segment up in the position shown, and
the next half revolution draws it down, thus giving the necessary motion to the tool
lifting cord at each end of the stroke of the planer table, the inertia of the double
friction clutch and driving gears is sufficient to drive the table on its bearings about
twice as far as it would move of itself as for example if allowed at full speed to run
B

page_text: out of gear with the spiral pinion engaging with the rack on the table, and to avoid
shock in reversing it is essential that the bearings of the gear teeth should be changed
to the reverse side, thus taking up all back lash as soon as possible after the disengage-
ment of the driving motion. Owing to the superior inertia of the rotating parts
connected permanently with the table it is necessary to apply break pressure to the
revolving clutch with sufficient force to reduce its speed so as to change the bearing
of the teeth in both the primary and secondary systems of gearing while the table is
still in motion and the change is therefore made with the difference of velocities of the
table and gearing. This disengagement of the double friction clutch and application
of the brake pressure to change the bearing of the gearing is accomplished by the
table stops; before the device for transmitting and arresting motion which is released
by the action of the table stops, reaches that point in its operation where the engaging
mechanism begins to act upon the lever F for the purpose of increasing the brake
pressure upon the revolving clutch and of finally engaging the clutch with the reverse
pulley by sliding the cam m until the ends of the bell crank levers rest in the parallel
part of the grooves p². The lever which operates the sliding cam on the pulley shaft
moves through a portion of its are to disengage the clutch from the driving pulley and
to apply the brake pressure to the other pulley after a perceptible interval it moves
through the remainder of its are to engage this other pulley with the driving clutch,
this last movement being effected by the engaging mechanism.
In all the drawings excepting Figures 6. 7. 8. and 24 the machine is shown with
the clutches and levers in position for running forward under cut and the relative
operation of the various devices will now be shown. When the table A Figure 20
reaches the end of its stroke, the stop L' strikes against the shifter lever J¹ and this
presses against the forked lever I on the shifter shaft G₁ thus turning the shaft in its
bearings the reversing lever N by means of the connecting rod O' moves the lever u
Figure 5 which slides the cam m a short distance on the pulley shaft H and through
the clutch levers and rod h, draws the friction clutch L away from the driving
pulley I and presses it against the return pulley K with sufficient force to act as a
brake, the clutch S serving to prevent any reaction or release of the break pressure as
herein before described the motion of the table is thus retarded by the friction on the
driving clutch and by this means the teeth in the spiral driving gears are made to
bear on the opposite sides of the teeth from those just employed for driving so that all
back lash is taken up preparatory to engaging the clutch L firmly with the return
pulley K by means of the train which includes the device for transmitting and arrest-
ing motion. The rotation of the shaft G¹also moves the lever F" through a small
angle by means of the connecting rod H2 the lever being cut away as shown at N² to
clear the point of the cam E2 so that in either of the two positions of rest of the
cam E2 the lever F2 is entirely free from it and when required can be moved through
its full stroke without striking E². In the first machine constructed by us with a
train having a device for transmitting and arresting motion to engage the driving
pulleys the lever F2 was not used and motion was communicated directly to the lever u
by a crank and a slotted connecting rod instead of the cam E2 shown, the connecting
rod having at one end a slot for lost motion equal to about one half the throw of the
erank, and the crank was so placed that after having moved the lever u as far as was
required in one direction the crank continued its revolution and stopped at a point
where it just took up the lost motion in the slotted connecting rod, this left the lever u
entirely free from the control of the crank so that it could be moved through its full
stroke when required without moving the crank while the half revolution of the crank
shaft always moved the lever u to its extreme position in either direction but we
prefer the construction shown in the drawing and hereinbefore described.
The rotation of the shaft G Figures 11 and 12 also at the same time, through the
friction clutch F¹ turns the escapement lever B' which lifts the escapement plate W,
thus lifting the stop ¹ clear of the pawl e¹ and raising the other stop g¹ to the proper
height to throw the pawl e' out of gear on completing a half revolution. The spring
plunger throws the pawl e into gear with the ratchet wheel T on the revolving
shaft M. and the pawl then drives the train of gears V. A' A² through a half revolution

page_text: the motion being arrested by the stop gabove described and the train held in position
by the retaining pawl the stops and are fixed upon and form part of the
escapement plate W, as being the cheapest and most convenient arrangement but they
may be pivoted and connected by a link or they may be placed upon the forked ends
of a pivoted lever or their movement may be at right angles to that shown so as to
engage alternately with the pawl e' the designation "escapement plate" being intended.
to refer to the device which presents the stops h' and g¹ alternately to the action of the
pawl e. The half revolution of the wheel A' moves the gear segments and ratchet
boxes through the proper distance determined by the position of the crank pin on
the slotted crank plate V the bevel wheel A² through the adjustable crank pin B³ and
connecting rod C gives motion in one direction to the feed on the cross head while
the half revolution of the cam E secured on the shaft D2 of the wheel A² presses
against the arm 02 on the lever F2 and so moves the lever F2 and through the con-
necting rods H and O' moves the lever into the position shown by the broken lines
in Figure 5 thus moving the cam m still further along the pulley shaft H and gradually
increasing the pressure of the friction clutch Lagainst the return pulley K by the
compression of the spiral spring r until the levers come to rest upon the flats in the
cam m, the clutch is now engaged with and driven by the return pulley K and
the motion of the planer table is reversed and the back lash having been taken up as
before described, the gradually increasing pressure on the friction clutch reverses the
planer table without any shock whatever.
It will be seen that the clutch L is withdrawn from the driving pulley I positively
that is by the motion of the table itself so that there can be no variation in the length
of stroke of the table without a re-adjustment of the stops and that the escapement
train is released and started by the first movement of the shifter levers and begins to
operate the feed and tool lifting mechanism before the planer table has ceased moving
and completes this operation at the time this train completes the engagement of the
double friction clutch with the return pulley.
The motion of the table is now in the opposite direction and the stop M' will, at the
end of the stroke of the table, engage with the lever K' and positively withdraw
the clutch L from the return pulley K, and compress the springs which will press the
clutch Lagainst the pulley I and so produce an effective brake to retard the motion of
the table A through the driving gearing and enable the table to be reversed without
any jar. As the brake is applied on the pulley shaft to retard the motion of the table,
it will be seen that the teeth in the spiral pinions C and G, spur wheel F and rack
under table A, will have their bearings quietly changed to the opposite side so that
when the clutch L is finally pressed in contact with the pulley by the escapement
train, with sufficient force to drive, as the engagement is completed, the lost motion in
the teeth is entirely taken up and there will be no blow or shock in starting up the table.
The reciprocating ratchet boxes which give direction to or suspend the operation of
the feeds, derive their reciprocating motion in the usual way from adjustable cranks
these adjustable cranks, however do not reciprocate or vibrate about an axis as usual,
but revolve about an axis in one direction only, making half a revolution at the end of
each stroke of the machine; they and the tool lifting apparatus together with the
mechanism for engaging the driving clutches are operated by the device for trans-
mitting and arresting motion which makes half a revolution at each reversal of
movement of the planer table (except when disconnected for a purpose hereinafter
described) which device derives its motion from the continuously revolving shaft M
driven as may be most convenient from a pulley on the pulley shaft or from the
countershaft of the machine, consequently all the feeds are made and the tool is raised
or lowered in the same time and also while the clutch for reversing the motions of the
table is shifting. It follows: therefore that the feed motions and the raising and
lowering of the tool take place while the table is at rest or changing its direction of
movement, a condition which I believe is not to be found in any other planing
machine, and the result of which is that the movement of the table may be limited to
the length of the piece to be planed without requiring any feed to be made while the

page_text: tool is cutting or the loss of any time or of table movement to raise or lower
the tool.
:
The hand lever R', Figure 9 has its bearing in the reversing lever N¹ in which it
turns freely; the lower end of R¹ is flatted off on two sides as shown in Figures 21
and 22 and a plunger S¹ sliding freely in its bearings in the reversing lever N¹ just
clears the flats or cams on the lever R when the latter is in the position shown in the
drawings, the other end of the plunger S¹ just clears the end of the bearing T¹ in
the stand E', the reversing lever being entirely clear of the bearing, as shown in the
drawings, so that the full pressure of the weighted lever Q is taken by the friction
clutch Fin the escapement lever B₁ as the hand lever is turned through 90°
in its bearings in the reversing lever N¹ one of the cams on the hand lever R¹
pushes the plunger S₁ through its bearings until it abuts against the bearing T
when the further revolution of the hand lever R¹ draws the shifter shaft G¹
through its bearings, thus bringing the friction clutch F1 out of gear with
the lever B without releasing it from the retaining clutch S., the shaft Gl
can now be rotated in its bearings either by the hand lever R₁ or the shifter
levers J¹ K', as above described without moving the escapement lever B'. If the
hand lever R be again rotated through 90° a flat is again presented to the end of
the plunger S¹ and the lever slides the shifter shaft G through its bearings and
again couples the friction clutch F with the escapement lever B, as shown on the
drawings. The shifter shaft G is supported on the opposite side of the machine in a
bearing in the feed stand H³, as shown in Figure 23, the reversing block N is made
to fit around the bearing so that it cannot move in the direction of the axis of the
shaft, but is forced to rotate with it by means of a sliding feather Y, the shaft G¹
passing partly through the block and supporting it. The hand lever Q' has its
bearing in the block N in which it turns freely and is formed with two flats or cams
like the lever ¹ but these cams are opposite to and operate directly upon the end of
the shifter shaft G' instead of acting through a plunger like that for the opposite side.
When the lever Q is rotated through 90°, in the block N which cannot move end-
ways the shaft G¹ is pushed end ways to release the clutch F so that the shifter
shaft G¹ can be operated with equal facility from either side of the machine.
This arrangement gives the operator complete control of the planer, as, by dis-
engaging the friction clutch F¹ from the lever B¹ the stops on the table will still draw
the double friction clutch L out of gear with the driving pulleys as before; but the
escapement train will not be set in motion and the feed will not take place nor will
the clutch L be engaged with the opposite pulley so as to reverse the motion of the
table at the end of its stroke. By the movement of the levers R' or Q' on either side
of the machine the motion of the planer table can then be stopped, reversed or
adjusted to any position back or forth as required without producing any feed, so that
when the hand lever is rotated to engage the friction clutch in the lever which
releases the escapement train, the movement of the table will again become automatic
and the feeds will recur from the place of their suspension.
A. Figure 4 represents a section through the table of the planing machine. Bis
the upper portion of the bed showing our improved bearing surfaces a and b. on the
bottom of the table A. a is flat on its face and rests upon a flat surface c on top of
the hed B., the surface e is bounded by ribs d. d. which serve to protect the surface c
and to help the lubricant from flowing off of it but they do not guide or confine the
side motion of the bearing a as there is a clear space left on each side as shown. The
rib has on its lower surface two angular faces g. g. forming with each other a very
obtuse angle, and fitting in a corresponding bearing e in the bed B, the angle of this
bearing or guide is made sufficiently acute to resist the side motion of the table due
to the pressure of any ordinary finishing cut and as it thus may approach nearly to a
flat surface, the friction is very little increased over that of a perfectly flat bearing as
at a and c. The thrust of a heavy roughing cut would, however, slide the table
sidewise on the obtuse guide e; to resist this thrust the two walls f. f. are raised on
the bed B on each side of the guide e, these walls f. f. have their internal surfaces

page_text: nearly vertical and the ribbon the table A fits easily within them without quite
touching them. These guides resist the first tendency of the table to be driven up
the side of the obiuse guide e and act only when the planer is used for heavy side
cutting work. In this respect they differ materially from the vertical side guides
heretofore used with flat bearing surfaces, as in the latter arrangement the side
surfaces have not only to resist the side thrust due to heavy cutting but have also to
guide the table accurately for finishing cuts, and hence any wear or lost motion will
seriously impair the character of the work produced. In the present invention, on
the contrary, the side guides ff merely resist the side thrust due to heavy cutting and
are absolutely idle during the finishing cut, the table being then guided sideways by
the obtuse guide alone. With this form of construction the guiding surfaces of the
obtuse guide will wear to fit each other, and hence there will be no lost motion to be
taken up and no adjustment required by the operator.
Having thus described the nature and object of our invention what we claim herein
as new and desire to secure by Letters Patent, is in a machine for planing metal.
1st. In machines for planing metal a primary and a secondary system of gearing,
a forward motion pulley and a return motion pulley in combination with a double
friction clutch, the diameter of which is less than half the sum of the diameter of the
forward motion pulley and its width of face.
2nd. Adjustable stops in combination with shifter levers which levers are So
proportioned to the stops and the speeds of travel of the table, as to operate the
clutch mechanism to disengage the driving pulleys from the table, without re-engaging
them therewith, substantially as and for the purposes set forth.
3rd. Adjustable stops and shifter levers so proportioned to the stops and the speeds
of travel of the table as to operate the clutch mechanism to disengage the driving
pulleys from the table without re-engaging them therewith, in combination with an
adjustable elastic connection between the shifter levers and the clutch substantially as
and for the purposes set forth.
4th. Shifter levers, which disengage the driving pulleys from the table, in com-
bination with a device for transmitting and arresting motion which operates the
mechanism that re-engages these pulleys, at times, determined from the disengaging
movement of the levers, substantially as and for the purposes set forth.
5th. A forward motion pulley, a return motion pulley, a double friction clutch,
a shifter shaft and shifter levers operated by stops upon the planer table, whereby the
friction clutch is disengaged from the driving pulley, in combination with a revolving
cam or crank, operated by a device for transmitting and arresting motion, which
re-engages the double friction clutch with the opposite motion pulley, the re-engage-
ment being effected without dependence upon the amount or the velocity of the table
movement, for the purposes set forth.
6th. A forward motion pulley, a return motion pulley, a double friction clutch,
a shifter shaft with shifter levers whereby the double friction clutch is withdrawn
from one pulley and pressed as a brake against the opposite pulley and a re-engaging
train operated by a device for transmitting and arresting motion which is started by
the disengaging movement of the shifter shaft, in combination with an adjustable
clastic connection, whereby the pressure with which this clutch will operate as a
brake to retard the motion of the table before it has the power o reverse it, and the
time during which it so acts, may be controlled for the purposes set forth.
7th. Shifter levers and a reversing shaft in combination with a retaining clutch,
substantially as and for the purposes set forth.
8th. A device for transmitting and arresting motion provided with an escapement
plate the movement of which determines the times for the transmission and the arrest
of motion in combination with a cam or crank which engages the double friction
clutch with the driving pulleys at the times determined by the movement of the
escapement plate, substantially as and for the purposes set forth.
9th. A double friction clutch and an intermittently revolving cam or crank which

page_text: engages the clutch with the driving pulleys in combination with a safety clutch
connection substantially as and for the purposes set forth.
10th. A double friction clutch and an intermittently revolving cam or crank, which
engages the clutch with the driving pulleys, in combination with an adjustable clastic
connection substantially as and for the purposes set forth.
11th. A device for transmitting and arresting motion, the times for transmission in
which are determined by the movement which disengages the driving pulleys from
the table in combination with a train which communicates motion to feeding
mechanism, whereby the feed will be effected during the interval between the dis-
engagement of the driving pulleys from, and their.re-engagement with the table, for
the purposes set forth.
12th. An intermittently revolving shaft, forming part of the train which re-engages
the driving pulleys with the table, in combination with a device for communicating
motion to tool feeding mechanism, whereby the feed will be effected during the
interval between the disengagement of the driving pulleys from, and their re-engage-
ment with the table, for the purposes set forth.
13th. An intermittently revolving shaft, forming part of the train which re-engages
the driving pulleys with the table, in combination with a device for communicating
motion to tool lifting mechanism, whereby this mechanism will be operated during
the interval between the disengagement of the driving pulleys from, and their
re-engagement with the table, for the purposes set forth.
14th. An intermittently revolving cam or crank, in combination with clutch
shifting mechanism, so that when the cam or crank C is at rest, the clutch shifting
mechanism may be operated at will, substantially as and for the purposes set forth.
15th. The shifter levers and the escapement plate in combination with a friction
clutch through which motion is transmitted from the levers to the escapement plate at
the will of the operator substantially as described.
16th. A shifter shaft, a friction clutch and a reversing lever, in combination with
the hand lever; through which the clutch may be engaged and disengaged, and the
shifter shaft may be vibrated at will, substantially as and for the purposes set forth.
17th. A friction clutch, a shifter shaft and a reversing block, in combination with
the hand lever through which the clutch may be engaged and disengaged, and the
shifter shaft may be vibrated at will, substantially as and for the purposes set forth.
18th. The guide, upon the bed, having four surfaces, two of which are slightly
inclined to a horizontal plane to sustain the weight, while two are perpendicular to
the same horizontal plane or slightly divergent from a perpendicular, to resist the side
strains, in combination with the guide upon the table, having surfaces the converse of
those upon the bed, substantially as and for the purposes set forth.
19th. A flat guide on one side of the bed which sustains the weight of one side of
the table, in combination with a guide upon the other side of the bed, which has four
guiding surfaces, two of which are slightly inclined to a horizontal plane to sustain
the weight, while two are perpendicular to the same horizontal plane or slightly
divergent from a perpendicular to resist the side strains substantially as and for the
purposes set forth.
20th. The arrangement and combination of parts constituting the planing machine
substantially as hereinbefore described and illustrated in the accompanying drawings.
Dated this 13th day of December 1887.