or Grooving Steel Rollers and Analogous Objects.
Year: 1885

page_text: or Grooving Steel Rollers and Analogous Objects.
I, HERBERT JOHN HADDAN, of 67, Strand, in the City of Westminster, Civil
Engineer, do hereby declare the nature of said Invention for IMPROVEMENTS IN
MACHINERY FOR POLISHING, DRESSING RIFFLING OR GROOVING STEEL ROLLERS AND
ANALOGOUS OBJECTS, a communication to me from abroad by the firm of Escher
Wyss and Company, Engineers, of Ravensburg, in. the German Empire, to be as
follows:-
:
3
These machines are worked with an automatic back and forward movement.
All the movements of the machine are effected by the pulleys a and b fixed
direct on the guide spindle.
The larger pulley b serves for the slow movement, while the fluting or cutting
tool is in action; the smaller one a for the quick return movement of the fluting
tool.
These pulleys sit loosely on the guide spindle c and are set in motion by an open
and a crossed strap d and e; they effect the back and forward movement of the
slide-rest by their alternate connection with the clutch f.
The automatic back and forward movement is initiated by the regulating-
collars h h, which are fixed to the disengaging bar gand move the lever k, attached
to the bolt i, a little over the centre.
The spring l, which is continually in tension, now begins to act to the right or to
the left and pushes the bar g more to the side, and so the movable clutch f
connected with the shaft c by a key is again in gear and produces the back or
forward movement at pleasure.
By this direct action of the strap all wheels, shifting of belts and turning of
weights are avoided, and the machine therefore, works very smoothly, which is
most essential for such precise work.
If the machine is to be used for polishing or grinding, the fluting-rests f³ are
removed and replaced by the polishing rests f³ Fig. IV.
These machines bave automatic feed motion, Fig. III.

page_text: The worm wheel segment n is mounted loosely on the shaft m, to which is
keyed the worm-wheel o Fig. I.
When the segment n is set in motion by the bevel wheels p and r (Figs. I
and VII), oblique grooves are cut on the rolls.
The division, or the number of flutings or grooves is determined by the ratchet
wheel 8, the gears to t₁ t and the worm u.
On the spindle of the ratchet-wheel a there is a pawl or ratchet-lever v; during
the backward movement of the cutting tool, the worm-wheel segment n revolves,
causing the ratchet-wheel 8 to descend, and the ratchet-lever v with the pawl wis
suppported at 9, or held on the pulley q₁ (Figs. I and III).
By this movement the ratchet-wheels is turned slightly round.
By means of the gears to t₁t this movement is communicated to the worm u and
the firmly keyed worm-wheel o of the axle m, with which the rolls are firmly
connected.
In order to flute right or left at pleasure, the bevel wheel p is adapted to be
placed inside or outside, as shown by dotted lines in Fig. VII.), and thus a contrary
movement may be imparted to the worm wheel-segment m.
The ratchet lever vis connected with the heel-point q by a cross muff q'.
In order to permit all requisite movements the parts of the muff are loosely
connected by screw-pin and eye gs; thus the lever V is held in position by shifting
to the right or to the left and, at the same time, it can move in any direction.
For dividing machines, which are not required to cut oblique grooves, or teeth,
the shifting is effected by the tool rest f³.
In this case the ratchet lever v hangs downward, and on the return of the rest,
the latter pushes the lever v until the buffer rests on its collar ², and thus the
feed motion is accomplished.
On the rest moving forward, the lever vis pushed forward by the buffer-
springs and catches other teeth for a fresh feed motion.
The buffer ¹ can also be a fixed cam, and, in this case, the lever v is provided
with a counterpoise, Fig. VI, which causes such a displacement, that the lever v or
the ratchet wheel gears in other teeth.
The displacement of the lever v, on the backward movement of the rest f¹, is
also effected by elastic buffers 24, and thus breakages in the machinery are avoided,
when the rests run back too far.
'

page_text: ☐ Grooving ;Steel Rollers and Analogous Objects.
!
I, HERBERT JOHN HADDAN, of 67 Strand, in the County of Middlesex, Civil
Engineer, do hereby declare the nature of this invention a communication to me
from abroad by the firm of Escher Wyss and Company, Engineers, of Ravensburg,
in the German Empire, and in what manner the same is to be performed, to be
particularly described and ascertained in and by the following statement:-
The improvements in polishing and riffling or grooving machines relate chiefly to
the driving and reversing gear or mechanism for automatic forward and backward
travel, and to the automatic feed motion for inclined (helical) and straight grooves,
In the annexed drawings Fig. I is a front view of the machine prepared for
riffling, and provided with a single slide-rest for riffling a single roller mounted in
the machine.
Fig. II a plan of this machine.
Fig. II bis shows separately the riffling slide-rest set out of action.
Fig. III is an end view of the disengaging gear and therefore also of the driving
gear.
Fig. IV a rear view of the feed motion or mechanism.
Fig. Va front view, on a larger scale, of the ratchet mechanism for the feed
motion.
Fig. VI. a horizontal section of the same.
Figs VII and VIII represent a modification of a ratchet mechanism in front
view and plan.
Fig. IX is a front view of a machine with countershaft and two polishing slide
rests.
Fig. X a plan of the same.
'
Figs XI and XII are rear view and side view of a feed mechanism for straight
riffling.
.
Fig. XIII a modification of the ratchet lever.
These machines are worked with automatic back and forward movement.
All the movements of the machine are derived from the pulleys a and b fixed
direct on the guide spindle c, see Figs I, II, III.
The larger pulley serves for the slow movement, while the grooving..or riffling
tool is in action, and the smaller one a for the quick return motion of the grooving
tool.
These pulleys sit loosely on the guide-spindle c and are set in motion by an open
and a crossed strap d and e; they effect the back and forward movement of the
slide rest F by their alternate connection with the coupling muff or clutch f
The disengaging bar g carries adjustable stops 9', against which abut the slide
rests at the end of their travel to the right and to the left (with fo of Figs. I
and IX); the motion of the slide rest is therefore imparted to the disengaging
bar g, on which are fixed the regulating-collars h, h. These collars h, h initiate
the back and forward movement of the slide rest by moving the double-armed
lever / (mounted on the pivotal bolt i) a little to the right or to the left.

page_text: The spring, which is always in compression, now begins to act to the right, or
to the left, and pushes the bar g more to the side, whereby the movable clutch f,
connected with the shaft c by groove and feather, is again brought into gear, and
produces the back or forward movement, as required.
The helical spring is coiled on a spindle A, hinged with its head to the lower
end of the lever k and allowed to slide at the other end in a guide sleeve l³, which
is pivoted in a fixed bearing 13.
The spring abuts at the top against the head of the spindle and rests at the
bottom on the top of the bearing 13 or on the top of the guide sleeve l³.
In the middle position, shown by Fig. I, the spring is in a state of unstable
equilibrium, any deviation from which will tend to throw the lever into its
extreme position either on the right or on the left.
This occurs because in the middle position of the spring the spindle A is at the
minimum of its free length and therefore the spring in a state of maximum com-
pression, while any deviation to the right or to the left will increase the free
length of the spindle l' and allow the spring to expand.
This alternate compression and reaction of a spring, for throwing a reversing
lever into one or other of its two extreme positions, may be obtained by other
details of construction, without departing from the nature of this invention.
As much as possible simultaneously with the reversal of the motion of the
riffling machine (that is to say of the guide spindle c and the slide rest of the
same), the grooving tool is set out of action for the quick return movement of
the latter. For this purpose adjustable abutments or stops h¹ are secured to the
bed of the machine, against which strikes a projection of the tool holder f*
mounted in the slide f¹. With the abutment is connected a cam k³ which
removes the tool holder, after the forward movement, Fig. II, (in the direction of
the arrow) has been terminated, during which motion the groove has been cut in
the cylinder R, the mufff having been coupled with the pulley b.
The tool holder is pivoted on the pin f, and the quick back motion will take
place, while the tool holder has the position represented by Fig. II bis, and the
coupling muff fis coupled with. pulley a. At the termination of the backward
movement, the lever arm strikes against the abutment h¹ on the right and
the tool holder is disengaged, so as to be brought again into the working position
Fig. II by the spring f. In order to prevent breakages by inaccurate position of
the abutments, the abutment h¹, Fig. I, is so constructed, that, even if the slide Fƒ³
should get beyond the abutment h¹, the latter is shifted to the side.
•
For this purpose the base plates h¹ of the abutments h¹ are secured to the cheek
of the machine by screw-bolts h³ exposed to the pressure of springs. Consequently,
the abutments are not rigidly connected with the cheek, but offer sufficient
resistance to effect the disengagement or removal of the tool, provided the travel
is correctly regulated. The connection of the abutment with the cheek, therefore,
depends on the friction of the base plate and the counter plate h', which friction
may be regulated by more or less tightening the nuts, and therefore by more or
less compression of the springs.
By this direct action of the strap, all tooth wheels, shifting of belts and over-
turning of weights are avoided, and the machine therefore works very smoothly,
which is essential for precise work.
These riffling machines have automatic feed motion, Figs. I, II and IV.
In a head stock, resembling that of an ordinary lathe, is mounted a spindle m
provided near the roller R with an appliance for securing the roller axle, so that, when
mounted, the roller R is rigidly connected with the spindle m. Loosely mounted
on the shaft m is a segment n, while the worm wheel o is keyed on the said shaft.
With the segment n or with the hub of the same is rigidly connected the bearing
for the ratchet wheels (see also Figs. V to VIII) for the wheels t², t¹ and t, and
for the worm u. The worm u gears into the worm-wheel o.
If now the ratchet-wheel did not act, the segment n alone being turned, the
worm wheel o would make the same angular motion, because n (by the practically

page_text: rigid connection of u with n as well as with o through the worm wheel gearing) is
coupled with.o in the direction of rotation.
It is possible, however, to obtain besides this rotary motion also the feed or
ratchet motion which, also causes the wormwheel o (and consequently also the
spindle m, and the roller axle) to turn during the first mentioned rotary motion.
This is effected by turning the ratchet wheel 8 by means of the ratchet lever v,
and its point of support q.
On the spindle of the ratchet-wheel 8, there is a pawl w, Figs. I and V.
The tooth or pawl w is situated in a recess of the lever vand is pressed by
a helical spring against the ratchet wheel 8. When the centre of the ratchet-wheel.
changes its position (vertically) relatively to the fulcrum or support q of the lever,
a slight turning of the ratchet wheel is caused by the pawl w situated between the
centre and the support or fulcrum.
In other words: If, for instance, by the turning of the segment n the ratchet
wheels (on account of its connection with n) moves downward, that part of the
ratchet lever v which is situated above q remains in its position.
A vertical shifting takes place, therefore, between the pawl w (Figs. V to VIII)
and the axle of the ratchet wheel 8. Thereby s turns slightly, which minute
motion is transmitted by the wheels 2 t¹t upon the worm u, therefore also upon
the worm wheel o keyed upon the spindle m, and consequently also upon the
axle m and the axle of the roller R. The two motions of the axle m are therefore
independent of each other; the motion first described is produced by the turning
of m and the rigid connection of n with m through the worm-gearing, and the
motion last described by the turning of the ratchet-wheel 8 during the motion of
the segment n. The first motion determines the incline of the riffling on the roller
during the feed motion of the riffling tool; the second motion determines the pitch
of the rifling, that is the distance between the grooves so that, when the tool
arrives at the end of its backward travel, the feed motion for the next riffling or
groove has been completed.
The pitch or number of the grooves is determined by the ratchet wheel 8, the
gears t, t¹, t and the worm u, with its worm wheel o.
The ratchet lever v, Figs. V and VI, is connected with the heel point q by a cross
muff q2; this muff serves to permit right and left hand ratchet motion.
.
In order to permit all requisite adjustments, the parts of the muff are connected
by a pin screwed into the eyelet q3 or by equivalent means. Thus the lever vis
held in position for right- or left-hand feed motion, but allowed to slide in the.
muff q².
The rod g may serve as a support for the lever v, either alone, or in connection
with a friction roller q¹, as shown by Figs. I, II, VII and VIII. The latter two
figures show also a modification of a ratchet-lever v, in which the pawl w recedes
by turning in one direction. Moreover, other ratchet levers, than those shown,
may also form part of the combination.
In order to cut grooves to the right or to the left, at pleasure, (right and left
hand screw) the bevel wheel p may be placed inside or outside (as shown by dotted
lines in Fig. II) and thus a contrary movement may be imparted to the worm
wheel segment n.
For dividing machines, which are not required to cut oblique grooves or teeth,
the feed motion is produced by the slide or carriage f¹, Figs. XI and XII.
In this case, the ratchet lever v hangs downward, and on the return of the
carriage the latter pushes the lever v until the buffer rests on its collar z², and
thus the ratchet motion is accomplished. Simultaneously the motion of the guide
spindle has been reversed; the rest fl moving forward, the lever vis pushed
forward by the buffer spring 23 and catches other teeth for a fresh ratchet motion.
Fig. XII also shows an elastic buffer 2, placed in the carriage or rest f¹ for
pushing during the backward motion of the rest (instead of a direct push by the
carriage f¹) so as to avoid breakages in the machinery, when the carriage runs
back too far,

page_text: The buffer z¹ may, however, be replaced by a counterpoise, Fig. XIII, applied to
an arm of the lever v, and adapted to cause such a displacement, that the lever vor
the ratchet-wheel gears into different teeth.
.
If the machine is to be used for smoothing or grinding, the grooving rests f³
are removed and replaced by the polishing rests fƒ³, Figs IX and X.
to
In this case the cylinders or rollers are turned directly by the pulley x¹; that is
say independently of the other mechanism, the riffling slide rests f² are removed
and replaced by the polishing slides f³, which are actuated by a drum on the
countershaft. As the cylinders (if several) are connected by a coupling x, one
driving pulley for the cylinders or rollers is sufficient.
The chuck m¹ is loosened, and thereby the connection between the axles of the
cylinders and the axle m broken, so that the axles of the cylinders or rollers (driven
by x) can turn independently of the axle m.
Having now particularly described and ascertained the nature of my said
invention and in what manner the same is to be performed, I declare that what
I claim is
1. A reversing mechanism, comprising in its construction a lever k, and a spring 7,
which in the middle position of the lever is in unstable equilibrium and in a state
of maximum compression, while any deviation from this position allows the spring
to expand so as to throw the lever into one or other of its two extreme positions by
the reaction of the spring.
2. The combination of a guide spindle c, with direct automatio belt driving
gear, and elastic reversing gear, the said driving gear chiefly comprising a pair of
pulleys a, b, and a coupling muff f with its disengaging lever, while the reversing
gear chiefly comprises a lever k with a spring 7 adapted to produce an automatic
and instantaneous coupling action (in consequence of the impact of the lever k with
collars h when the carriage or slide F has, towards the end of its travel, come in
contact with the corresponding stop gl on the disengaging bar) and to keep the
muff coupled with the respective pulley during the travel of the slide rest or
carriage.
3. The elastic contact device (h', h²,) applied to the bed of the lathe, for setting
the tool in and out of action.
4. The automatic feed motion or mechanism for producing oblique grooves or
teeth, chiefly comprising a ratchet wheel 8, pawl lever v, and a rest q adapted to
receive a roller q¹ or a movable sleeve q2, according to requirements.
5. The automatic feed motion or mechanism for producing straight grooves or
teeth, chiefly comprising a ratchet wheel s, and weighted pawl-lever v, Fig. XIII,
or a ratchet wheels, pawl-lever v, and buffers Z', Z+, Fig. XII.
The whole substantially as described and illustrated.
Dated this 18th day of November 1885