Improvements in Rotary Presses.
Year: 1894

page_text: Date of Application, 30th July, 1894-Accepted, 6th Oct., 1894
Improvements in Rotary Presses.
I, FREDERICK LINDLEY HUNT SIMS, of the City of Toronto, in the County
of York and Province of Ontario, Dominion of Canada, Manufacturer, do hereby
declare the nature of my invention to be particularly described and ascertained in
the following statement:-
My invention relates to improvements in rotary presses for the manufacture of
bricks out of pulverized and other forms of clay etc., and for the compression into
solid blocks or billets of peat, bran, sawdust, groceries etc., etc., for convenience in
consumption or conveyance, for purposes of fuel, food, fodder, etc., the object of the
invention being to provide a machine rapid and inexpensive in its operation and of
practically unlimited power and strength.
Fig. 1 of the accompanying drawings is a perspective view of the complete
machine, looking from the rear.
Fig. 2 is a perspective sectional view on the line x-y Fig. 3^ of the body of the
machine, and delivery device;
Fig. 2 is a perspective view of one of the hoppers and Fig. 2B is a detail of the
device for "striking off";
Fig. 3 is a side elevation of the body of the machine and delivery device, with
the adjacent main gear removed, the drum and lower part of frame being in cross
section on the line x―y Fig. 3ª, and the shaft in cross section on the line xx―y y
Fig. 34; the adjacent collar and sleeve also being removed, to afford a clear view
of the adjacent plungers and cam, etc.;
Fig. 34 is a cross section of the machine on a vertical plane, cutting the centre
of the main shaft and looking toward the front or delivery end of the machine.
Fig. 4 is a side elevation of the composite cam, and Fig. 4ª is a cross section of
the same on the line A-B Fig. 4, looking to the left; with the appearance looking
to the right indicated by the dotted outline;
Figs. 5, 5, 5, 50, 50, 5B. and 5* are details connected with the plungers, and
Fig. 6 is a detail of the perforating device for brick machines;
Fig. 7 is a perspective view of one of the doors looking from the front end and
Fig. 74 is a side elevation of same, partly in section.
Fig. 7B is a perspective view of one of the door-dies;
Figs. 8, 84, 8B, and 8" are details of the journal-pins provided for the doors;
while
Fig. 9 is a diagrammatic sketch explaining the action of the doors in closing and
opening.
In the drawings, like letters and numerals of reference indicate corresponding
parts in each figure throughout. Further, the numerals from 23 to 35 inclusive
have special reference to the method by which steam for heating the moulds is
introduced, where the material to be pressed is of a nature such that it would
adhere to the dies, were they not heated. The drawings are of a machine for
making bricks from pulverized clay, and show only six moulds, i.e. three pairs,
though the machine may have sixteen moulds or even a greater number if desired.
As this machine is entirely dissimilar to any other yet invented, before describing
the invention in detail it will be well to give a brief outline of its action.
The main gears A A', revolve in the direction of the arrow (Fig. 3) freely on
sleeves C, C, keyed to the main shaft B, but eccentric to the centre of said shaft.
Said sleeves have a concentric portion c c', on which revolves freely the hollow
cylinder or drum E, containing the moulds G, and thus the shrouds or gibs a, a, a,

page_text: on the inner faces of the gears A, A', constantly approach and recede from the
periphery of the drum. Motion imparted by the gears to the drum causes the
latter to revolve with the gears in such a manner that radii of the gears and drum
which are in a common plane on the "line of centres" (which in this machine is
horizontal, though in peat and other machines it is inclined considerably) are in
parallel planes in all other positions. The object of this is that there shall be no
torsional strain on the shoulders of the doors Z when under the shrouds a, a, a; the
shoulders of the doors being tangent to the drum radii and the gibs or shrouds a, a, a,
being tangent to the gear radii. The doors are free to revolve on radial pins,
extending outward from the periphery of the drum, and are furnished with die-
plates accurately fitting the moulds G. Inside the drum E, keyed firmly to the
main shaft B (which shaft it should be noted is held immovable by its tenoned
ends fitting in the mortises in the frame O) are the main cams, the action of
which in connection with the plungers H will be seen at once on reference to
Fig. 2. Pulverized clay is fed through canvas chutes or pipes, into the
hoppers V, V, whose under surface is accurately fitted to the drum E, and a space
left between them for the free passage of the doors Z as shown.
While passing
under the hoppers the moulds receive their charges of clay and next the curved
cam w, w engages the pin 2 on the doors Z closing the same, i.e. turning it in a
direction the same as the axis of the drum and bringing its shoulders y¹ under the
shrouds a, a, a, on the gears A, A¹, when the gears approaching the drum, owing
to the eccentric axis, cause the dies on the door to enter the moulds G. When
said dies are entered far enough to prevent the escape of clay, the plunger
rollers J engage the rise 2-3 of the main cams D, D', very rapidly and more and
more slowly from 3 to 3¹, as the clay becomes harder, they drive the plungers
outward from the drum centre 8, while the gears pull the door and door-dies inward
until 31, the line of centres, is reached; putting thus first a concussion pressure
from below, which drives all air to the top, and then a steady double pressure, on
the clay. At 3¹ the gears begin to recede, and the "top" pressure ceases; the
plungers however follow the recession from 31 to 4, with a slight rise in excess of
the eccentricity giving the clay a finishing differential pressure of enormous volume.
The pressure ceasing at 4, the lower shoulders of the doors y² (Figs. 7, 7^) engaging
the then receding flange a¹ on the main gears, are lifted thereby away from the
drum entirely out of the moulds; the finished brick resting meantime in the moulds
with their outer face about one-sixteenth of an inch from the top, to preserve the
arrises; and as soon as the dies on the doors are so disengaged from the moulds, as
above, the opening roller 21 (Fig. 7) engages the opening cam w (Fig. 2) and the
door swings open, the pin and roller z entering between the guide bars w², that
steady the doors while opening. The rollers of the plungers H then engage the
rapid rise 5-6 of the cams D, D' and on reaching 6 the bricks being forced by
the plungers entirely out of the moulds G, drop upon the delivery belts o², o², which
convey them to the kiln ready for burning; while the plungers are carried on until
the roller k on the lug K of the sleeve J₁ (Fig. 5A) engages the adjustable rod d',
drawing the plungers back to the bottom of the mould G just as they enter again
under the hoppers V, V, and so on, each pair of moulds alternately filling, receiving
pressure, delivering and returning for filling; the full sized machines delivering
sixteen bricks in the course of each revolution.
Having now given a fair idea of the main features of the machine, for the better
understanding of the details, I proceed to explain the various parts according to
the letters and numerals of reference.
9, on
O is the main frame (Fig. 1) precisely alike on both sides, having suitable
journals as shown for the back-gearing, which consists of the pinions p² on the
pulley-shaft P which mesh into the secondary gears Q on the countershaft
which are the secondary pinions R which mesh into the main gears A, A'. The
pulley-shaft P derives motion from a pulley placed at pl, driven by any suitable
motive-power, said pulley being omitted from Fig. 1 as it would have prevented
the showing of the remote secondary pinion R.

page_text: The main gears A, A¹ revolve freely on the larger portion of the sleeves C,
on a centre 9 about one and one-quarter inches further from the shaft P than the
centre 8 of the main shaft, the "line of centres" joining the centres 8 and 9 being
in this machine horizontal. On the inner faces of the main gears A, A¹, are the
shrouds or gibs a, a, a, at aliquot distances, in the circle, with their faces finished dead
true tangents to the radius bisecting their length, and perpendicular to their plane
of revolution. To facilitate this in construction it will be noticed that they project
below the concentric flange, to give tool-clearance at either end. Below the flange
and shroud a, a, a, is a circular flange or projection a', a', a', (Figs. 3 and 34) turned
true on its outer face, and at a distance from the shroud a, a, a, to easily admit of
the ends of the door Z (between y¹ and y2 Figs. 7 and 74). Still nearer the centre
of the gears A, A', at the angles of the inscribed triangle (square or regular
polygon, as desired) in an imaginary circle (of any radius k, less than the radius of
the drum E minus the distance between the centres 8 and 9-i.e. the amount of
eccentricity of the main gears--plus the radius of the friction-rollers T, now about
to be described) are securely journalled the friction-rollers T, three (or more as
the case may be) in number (see dotted outline Fig. 3 and upper part Fig. 3A)
having their axes perpendicular to the plane of revolution of the gears A, A'.
The drum E, which in actual construction is formed of a centre annulus and two
similar end pieces provided with male and female couplings and securely bolted
together, is in this Specification, drawn as a hollow cylinder which it in effect is,
having the inner side of its periphery thickened at intervals for the placing of the
moulds G as shown (Figs. 2, 3, 34) which are placed in pairs at aliquot distances
in the periphery (Figs. 3, 34) coming out on the outer periphery in the raised or
projecting portions e (Fig. 1) and having on either side, the grooves e¹e (Fig. 1
and Fig. 3A), provided for the shoes v' of the hoppers V (Fig. 24) with the object
of preventing any escape of clay from the hoppers. In the ends of the drum E
are radial slots e² (Figs. 3, 34) into which fit the tenoned ends of the plunger
shafts I, reciprocating therein with the design of taking up all strain of the lower
end of the plungers, and also to force the plunger-shafts I (Figs. 5, 5^) round with
the drum. The moulds G are lined with chilled iron plates 9 (Fig. 3) and evenly
between each pair is bored a radial hole in the periphery of the drum E for the
shanks 14 of the journal-pins 13 (Figs. 8, 84, 8B) on which revolve partially the
doors Z. On the outer faces or ends of the drum E which lie adjacent to
the main gears A, A', at the angles of the inscribed triangle (square or regular
polygon) in an imaginary circle (of any radius k the same as that selected for
ascertaining the location of the centres of the friction-rollers T on the faces of the
main gears A, A') are counterbored the holes S, having a radius equal to the
distance between the centres 8 and 9 (that is the amount of eccentricity of
the gears A, A' to the drum E) plus the radius of the friction-rollers T, and
Now
having their centres perpendicular to the plane of revolution of the drum E.
on examination of Figs. 3, 34 it will be seen that when the drum (revolving freely
about the centre 8 of the sleeve C, C¹ on the smaller portion thereof c, c') has the
main gears placed adjacent to it at both ends (Fig. 3) on the eccentric or larger
portions of the sleeves C. C¹; because the friction rollers T on the gears A, A¹,
have their centres at exactly similar distances from the centre 9 that the counter-
bored holes S in the drum have, as to their centres, from the centre 8 and because
the rollers T and holes S are of the relative proportions above specified the rollers T
will always touch the counterbored holes S on the side of the same toward the
centre 9 as in relation to the centre 8 and the distance between their respective
As the main
centres will be the same as that between the centres 8 and 9.
gear A, A' revolve in the direction of the arrow Fig. 3, the rollers T roll around
the inside periphery of the holes S but in the contrary direction, the one or more
below the line of centres doing the driving and allowing just sufficient lost motion
(owing to its proportion in relation to the hole S) to keep the radii of the drum E:
and gears A, A, which fall in the same plane on the line of centres always in
parallel planes in all other possible positions. The geometrical principle underlying

page_text: this peculiar movement will be understood from the dash and dot triangles and
radii in Fig. 3. Besides avoiding torsion on the doors Z (which would at once
occur if the drum and gear radii inclined toward one another) it provides a
beautifully regular and powerful method of coupling the eccentric gears A, A' to
the drum E.
It will of course be apparent that the mechanical movement just described can
be utilized in all cases where motion is to be imparted from one disc or gear to
another disc or gear, revolving in a plane parallel to each other but on different
centres in such a manner that any radii of the driving and driven discs or gears
which lie in the same plane on the "line of centres" shall lie in parallel planes at
any other point in the revolution.
Keyed to the main shaft B within the drum E are the two split cams D and D'
(Figs. 2, 3, 3, 4, 4) which are held therefore immovable within the drum E, the
drum revolving around them concentric to the centre 8 Fig. 4. The cam D¹ being
that lying to the right in Fig. 3ª differs from the cam D in having cast upon it the
arm d and dove-tail lug d2 (Fig. 4A). The arm d supports the rod or bar d¹
affording it a little end play, by means of the slot shown at the extremity, through
which the pin from the rod d' passes, being kept in place by a cotter-pin or nut on
the further side. Similarly, the dovetail lug d supports the sliding piece M by
means of the lugs at the back of M, allowing M only to move radially from the
centre 8 and back. M has its upper surface m¹ finished to such a curve as shall
form the nearest approximate to a concentric circle about the centre 8, in whatever
position it may at the time rest, and has at the back, above, a short cam m², in
which is secured (free to turn slightly) the pin at the end of the rod or bar d',
remote from the arm d. Projecting from the lower face of the sliding piece M
remote from the cam D₁ is a pin m, designed to engage the horseshoe or slotted
cam N (Figs. 3, 34) which is securely keyed to the shaft n, which passes through
holes in the cap frame o, the collar sleeve C and cam D, and is rotated by means
of a worm and screw-gear movement, not shown, as such movements occur
constantly in mechanics. The object of this means of adjusting the relation of the
rod d' to the centre 8 will be explained in connection with the plungers.
Where steam is to be used holes similar to those provided to the shaft n are
bored through the cap frame o collar c³, sleeve C and cam D (see 27, Figs. 3, 3^, 4)
as far as the centre of the cam D and the feed pipe passed through and screwed
into the cam D. A similar pipe 35 is fitted in a hole 35' in the cam D' on the
remote side. Radial boles are bored to meet the holes thus mentioned as shown in
Figs. 4 and 4 carrying the steam from the feed pipe in cam D to the steam-duct
formed between the flange 24 and the steam tight collar 23 (made in two halves
and bolted together, Figs. 2 and 3), which is caused to revolve with the drum E
by being rigidly connected to its inner periphery by the rod or spoke 25
(Figs. 2, 3, 3). It will be observed that the lower half of this steam duct is
formed by the stationary cam, while the upper half is formed by the moving collar
which, as just stated, moves with the drum. From the collar 23 of the cam D the
nipple 26 conveys the steam to the rubber steampipe 28 which takes it in turn to
the ingress nipple 29 of the series of plungers which travel around the said cam D.
The steam that passes through the cores xx, in the plunger H to the egress
nipple 29¹ and so on through the rubber piping 28 to the last plunger of that set,
whence it is led by the piping 281 (Figs. 2, 3,) to the iron steampipe 30 which
passes around in the middle of the inner periphery of the drum E, having "T's "
or "by-passes " 31 under each journal pin, 13 (Figs. 2, 3, 34 and 8^,) from which
nipples 32 take the steam into the holes 15 bored through the journal pin 13
(Fig. 8) where it is led into the brass tubes 21, projecting downward into the
holes 13 bored in the doors Z, and fitted accurately into the said holes 15, which
tubes conduct steam into the cores 22 (Fig. 7A) into the doors Z. From the iron
piping 30 the rubber steampipe 33 in turn takes the steam to the ingress nipple 29
of the first plunger H of the set revolving around the cam D', and so out at 29¹
through the piping 33¹ to the nipple 34 of the steamtight collar 23 of the cain D'.

page_text: Passing into the duct in cam D', the steam goes through the hole 35 into the
pipe 35 screwed therein (Fig. 3A) and so out at 35' (Figs. 34 and 1).
Of course a current for electric heating could be carried through in a similar
manner, the point being the introduction into the moving drum plungers and doors
through the stationary sleeves.
I shall now explain the manner in which the peculiar form of pressing surface
of the cams D, D¹ is to be ascertained. From the radius i to the radius 2 (while
the doors are closing) the cams D D¹, are concentric to the centre 8, i.e. the centre
of revolution of the drum E, and the concentric portion 1-2 is of a radius that
will allow the plungers H to assume their lowest position in the moulds G when the
rollers J (Figs. 5, 5A) rest upon it. At the point 2 the doors Z have closed and the
dies Y have entered slightly into the moulds G, the cams D, D' rising as abruptly
as is wise (according to the material) outward from the centre 8 until 3 is reached,
when, if the rise 2-3 has been properly adjusted to the material, the latter will
have attained a considerable density, and most of the air in it (which it is beyond
all things necessary to absolutely expel from most material) will have been driven to
the top and permitted to escape, as will be presently shown. At 3, therefore, the
cam rises outward from the centre 8 in a series of portions of Archimedean spirals
of decreasing dimensions, till the line of centres is reached at 3'; the doors mean-
time coming inward owing to the gears revolving about the centre 9. As at 3¹
the doors begin to retreat the cam from 31 to 4 follows, about the centre 9, plus a
small rise to give a maintained pressure, which is differential in its nature, as
though the doors retreat, the plungers follow and slightly overtake them and by
this means a pressure practically irresistible is developed. The location of the
breaking-off point 4 where the pressure ceases, is fixed by the fact that pressure
must cease before the brick quite reaches the top of the mould, as, were it other-
wise, the outer arrises would be damaged. Before the dies Y (Fig. 7 et seq.)
leave the moulds all together, therefore, the point 4 is reached and the rollers J of
the plungers H passing over the "break" all pressure ceases instantly, and if the
material be elastic (as compressed peat) the depression between 4 and 5 must be
considerable. From 4 to 5 the cam is considered as concentric on the radius 8-5
to the centre 8, while from 5 to 6 it rises rapidly to expel the brick (the doors
having opened while passing from 4 to 5); the radius 8-6 being greater by a
little more than the depth of the mould, than the radius of the concentric
portion 1-2. The cam might end at 6, but as in some machines, I use a rotary
brush to clean off the plunger dies between 6 and 7, the cams are formed with
the concentric portion 6-7 about the centre 8 to keep the plungers well out against
the wire bristles of the said brushes. (The brushes are not shown, as their
introduction and the means for operating them would have greatly complicated
this Specification, and they cannot be used at all in connection with other
machines.)
The plungers H are arranged in pairs on the plunger-shafts I (Figs. 5, 54) and
have each a pair of rollers J, the inner rollers being separated by the sleeve.J¹
which has a lug K projecting radially towards the centre 8 and having a friction
roller & journalled at its extremity, with its axis parallel to the shaft I as shown, in
Fig. 5. The shaft I cannot revolve owing to its tenoned ends i, i, playing up and
down in the radial slot (Figs. 3, 34) in the drum E. The plungers H are loose
on the shaft I, i.e. they are not keyed to it, though accurately fitted on the
shaft. The nipples 29, 29' and cores, have already been explained. It will
be observed (Fig. 5) that the lateral slot X' divides the plunger into two
66 prongs "somewhat similar to a tuning fork. These are however bound together
as the top by the rebate in the top plate or die h, which is firmly screwed to
the plunger H as indicated in Fig 5. The die-plate has a stock or frogmark
plate screwed on its upper face and through the two are bored the holes.
for the perforator rods, where such are to be used, in the manufacture of
perforated brick. On its lower side the stockmark plate has the grooves ³ (se
particularly Fig. 5º) which form ducts for the escape of air, which, being at

page_text: right angles to the direction of pressure, do not choke or clog. It will be noticed
that the lower part of the centre hole h (Fig. 5D) is slightly enlarged. This is
to allow the air from the ducts ³ to pass downward around the rod which
would otherwise fill the hole. The long chambers on the ends of the stockmark
(Fig. 5) are to adapt it to cleaning by a rotary brush, without liability to clog
in the corners. Also, (as also is the curved form across-Fig. 5) this form is
adapted to throw additional pressure on the arrises above, through the resulting
parallelograms which occur in the resolution of a vertical force acting in the
direction of the plungers, i.e. radially from the drum centre 8.
"
The slot X gives clearance to the bar or support X (Figs. 5, 5ª, 3 etc.) which
is firmly secured to the end liners of the moulds G and into which are secured the
rods up and down along which the plunger travels in its action. The rods it
will be seen form metal cores in the clay while it is being pressed, and render
possible a new article of commerce, viz. :-a perforated "dry pressed brick
hitherto unknown. These bricks can be burnt more evenly, with less warping, and
cracking, and at less expense than solid brick, and some clay that will not stand
firing is made solid, will fire profitably and make good brick if perforated.
Fig. 6 shows the counterbore al in the perforator rods a.
The counterbore x¹ is
tapped by a number of small holes 2 at that part of the rod a which is about the
centre of the brick while under pressure, while the four holes tap the same
immediately below the plug a, which is introduced to prevent the counterbore
becoming choked by the falling clay as the rods pass under the feed spouts or
hoppers V. This device provides for the exit of any particles of air or gas which
may remain in the material during compression from 3, 31, 4 (Fig. 4) the air
entering through passing up and out at 3, which is then in the holes y
provided for the tips of the rods x in the door dies Y.
The peculiar and novel action of the gates or doors ✗ will be understood, after
careful examination of Fig. 9 in the light of Figs. 7 et seq. and Figs. 2, 3 and 3^.
The doors Z have a hole 13' bored in their bottom-centre, at right angles to the
plane of the dies Y, Y, deep enough to allow the journals 13 to enter until the
shoulder above the tangent 14 (Fig. 8) is flush with the bottom of the doors Z.
(The brass tubes 21 which fit into the holes 15 through the journals 13, leading the
steam from the nipples 32 has already been explained.) On these journals the doors
are moved by the closing cam w, w¹ and opening cam 1 (Figs. 2 and 9) while
they are also pulled in and pushed out by the eccentric action of the gears A, A'
in relation to the drum E. To keep the doors at a determined height above
the drum E, when open, I provide in the journals 13 the semicircular annular
groove 16, in which plays the key 19 whose ends rest in the holes 20 bored
through the doors Z (Fig. 74). In Fig. 8B the key 19 is shown in cross-
section resting in the annular groove 16, and manifestly holding the door from
sliding up or down on the journal, though free to turn. In closing the key 19
carried around a quadrant by the door slides down the shoulder 18 (by the
weight of the door) until as the dies Y, Y, come directly over the moulds G, its
axis is parallel to the chord of the recess 17 (Fig. 8) and one of its sides is
adjacent to the side of the recess 17. That is the key 19 occupies the position
dotted in, in Fig. 8, just as the dies Y are entering the moulds G. As the
dies Y enter the moulds G the key 19 is carried down the recess 17 to the posi
tion 19 (Fig. 8), cross-hatched. As the dies Y with the door Z rise out of the
moulds, the key 19 comes again to the position dotted in Fig. 8, and slides, in
opening up the shoulder 18, by weight (being then beneath the machine) and so to
the position 19, (Fig. 8B). Having now explained how the doors are free to move
for a quarter circle around, and a certain distance up and down in the direction of
the axis of the journal 13 (which journals are firmly fixed radially in the drum E
see Fig. 2 at ), it will be understood that when in the revolution of the drum E
the rounded lace of the closing pins z on the end of the doors Z in advance,
engages the curved face of the closing cam w, the door is swung around on its
journal 13, from its position as shown on the left of Fig. 9 to that shown on the

page_text: 2
right of the same figure, where it will be noticed that the flat face of the closing
pin z lies adjacent to and has travelled its own length along the flat face of the
closing cam w, marked w¹, thus keeping the dies Y of the doors Z steady in exact
position over the moulds G in the drum E, until they are drawn into the same by
the action of the shrouds a, a, a, of the eccentric gears A, A'. The inertia, or
momentum rather, of the doors Z, as they are swung around by the curved cam w
is taken by the check-block wz (Fig. 9) which engages the shorter flat side of the
closing pin z, i.e. the side parallel to the length of the doors Z. It will be noticed
that the space between the check-block wz (Fig. 9) and the point at which the
curved face of the cam w, changes to the straight face w' is just enough to allow
the closing pin z to pass through. The check-block w z is not absolutely necessary
to the movement, as the key 19 coming at the same moment adjacent to the
recess 17 of the journal 13 prevents further revolution, but the check-block w z is
practically necessary to preserve the key 19 and face of the recess 17, and journal
pin 13 from undue wear and strain. (In machines having very heavy doors I also
provide check-blocks projecting from the face of the drum to engage the castings
of the doors Z at either end. These are not shown.) The doors Z having entered
and withdrawn from the moulds, are opened by the friction roller 2 engaging the
opening can * Fig. 9 (dotted) and Figs. 2, 3 ; which cam need only be curved at
its inner corner, and is therefore made straight otherwise to attain quicker action.
The opening pin 2¹ on striking w' is dragged around in the direction of the dotted
arrow, leaving the door z again in the position along the direction of revolution of
the drum E, shown at the left-hand of Fig. 9. At Σ in Figs. 2 and 3 are shown
doors "open," and at Fig. 2 is dotted in a door closed. At o Fig. 3 is shown
the end elevation of a door closed. The shoulders y' are finished dead true at
right angles to the hole 13' and parallel to the dies Y and the shoulders beneath, y³,
are slightly curved in the direction across the door, to facilitate the ends between y¹
and y gliding in, in closing, between the shrouds a, a, a, and circular projec-
tion a¹, a', a', on the faces of the gears A, A¹. The dies Y for the doors Ź have
three features. First, the countersunk holes y¹ (Figs. 7A, 7B) with their fine points
downward also slightly countersunk, into which the perforators x (Fig. 6) enter, as
the dies Y enter the moulds G, the wider clearance above provided by the
expanding of the countersunk hole being to allow the free escape of air &c., driven
by the concussion at 2-3 of the revolution, as to the cams, to the top of the
material in the moulds, as the dies Y have just entered, through the ducts y³, y³, y³.
Second, the dovetailed rebates at either end of the dies Y to slide in between the
dovetailed lugs of the doors Z (Fig. 7, 7A) and third the recess (semi-circular) y
(Fig. 7B) into which a round key is driven through the hole y (Fig. 7A) (of which
the recess y-Fig. 7B-is the lower inner end) to hold the die exactly in position,
after it is in the dovetail that holds it firm to the door Z. This arrangement
fitting
provides a cheap, exact, and lasting method of " "the dies Y to their
respective doors and moulds, by readily taking up any slight inaccuracy of work
manship. When the doors have been opened by the cam w the pins 2, 2¹ lie
between the guide rods w³, to which prevent the doors from getting out of line
until the closing pins of each in turn again reach the closing cam w, and thus the
doors are always under absolute control as to their position, viz.: first of the guide
rods w³, w², then of the closing cam w and its face w', then by the dies Y, Y, being
in the moulds G, then by the opening cam wo³, and so in again between w². The
clearances left at w³ (Fig. 2 top) and in the front below at w³ 2 (Fig. 2) are for the
opening pins ¹ to swing out of the channel and to the further side of the cam w,–
see the long dotted arrow shewing the path of the opening pins 21 at 208 (Fig. 9)
when the doors close, and for the closing pins z to swing into the channel at w² z
(Figs. 2 and 3) which they of course do in advance of the opening pins ¹, when
the doors open. For this reason the guide rod w³, next the spectator, in Fig. 2,
is shorter at the bottom end w³z, than the one that ends in the opening cam w³,
while the remote one (that continued from w*) ends under the bridge W (Fig. 9)
with the other,―see dotted lines Fig. 9.

page_text: The feed spouts or boppers V, V, two in number, are fixed to the guide rods w.
supported by the frame o' and bridge W, and have their undersides finished in arcs
to fit the periphery of the drum E. The flanges or shoes v¹ of the hoppers V fit
nicely into the grooves e¹ of the drum E, leaving the raised or projecting portions e
under the hoppers, so that the moulds G which come out on the periphery of the
drum on the said raised portions e, pass in turn continually under their respective
hoppers V, V, as the drum revolves. The hoppers V are fitted with the sliding
pieces having projections at each end which pass through the slots v on each
side of the hoppers V, and on which rest the springs ³ pressing toward the surface
of the drum E, the said sliding pieces 2. Inside the hoppers V, (see Fig. 2B) are
the lugs, one on each side, to keep the clay from escaping through the slots vº,
and to better retain the sliding pieces in position. The sharp lower corners v v
of the sliding pieces follow the chord of the arc of the circumference of the
projecting portions e of the periphery of the dram E, formed by the sides of the
moulds G, and strike off the surplus clay to the said chord, so that instead of leaving
the feed with a rounded or curved upper surface the clay lies flat in the mould, and
is not touched by the dies Y of the doors Z while the doors Z are closing. The
movement of the sliding pieces or "strikers" is of course equal to the side of the
are cut off by the chord forming the top of the side of the moulds G. The tail V
of the hoppers V prevents escape of clay.
It now only remains to describe the two endless delivery belts o³ (Figs. 1, 2, & 3)
upon which the bricks drop, out of the moulds, on the radius 8-6 of the cams H.
These belts run around pulleys supported on journals on the standards o¹ (Figs. 3, 34)
bringing them in position to catch the brick, but not far enough in to interfere
with the opening of the doors (a point requiring the nicest attention in laying out
the cams) and at the extremity remote from the machine around suitable pulleys,
driven suitably, placed at the kiln, or wherever desired. Their speed is immaterial,
provided it is not so fast as to injure the brick, or so slow as not to take away one
before the other falls. For a machine delivering sixteen brick per revolution I
provide under the belts o2, an oiled plank over which the belt drags above, to
prevent the weight of the brick sagging the belt, and so damaging the end arrises.
It is preferably to run this belt fast enough to leave at least twelve inches between
the bricks, so that there may not be too much weight on the belt at once.
Having now described fully the various details of my machine, the description
of its action in detail, following will be readily understood.
Clay from the hoppers V falls into the moulds G of the drum E, as the same is
caused to pass under the said hoppers by the rollers T in the counterbored holes S
of the drum E imparting the motion of the gears A, A' to the drum E. The
depth of clay is regulated by the position of the plungers H, in said moulds, and
the tails of the hoppers V prevent the escape of clay from the rear end of the
moulds G while the latter are passing under the hoppers V as the tails v are long
enough to cover the moulds before they come under the spouts V. The position of
the plungers H in the moulds G is regulated by the rod d¹ being moved out or in
as desired by rotating the adjustment shaft n, which turning the cam N, moves the
pin m in the slider M, and by the arm m2 communicates inotion to and fixes the
position of the rod d' which acts as a cam drawing the plunger shaft I inwards
towards the centre 8 by the roller k on the lug K of the sleeve J keyed to the said
shaft passing under it, the said rod d', in the revolution around the cams D, D¹.
The plungers H are maintained at the desired height by the said roller k after it
leaves the rod d' rolling along upon the face m of the slider M, while the feed is
in progress. If considerably raised by the slider M, the plungers at 1, when the
feed is finished, drop until the rollers J strike the faces 1-2 of the cams D, D¹,
but as this is after the feed is over, it does not affect matters at all. (Where the
material to be pressed is light or refractory as to feeding, I carry the point 7 up to
just under the feed, and do away with the return movement K, k, d, d', allowing
the plungers to drop of their own weight on a slider M, which simply governs the
fall, and so the material is sucked into the moulds.) While the drum passes with

page_text: the moulds the radius 8-1 and goes on to 8-2 (see Figs. 3, 4) the closing pin z of
the doors Z engaging the curved face of the closing cam w, closing the doors, and
bringing the shoulders y¹, y², of the same between the shroud a, a, a, and
projection a', a¹, a', of the gears A, A', the key 19 of the doors Z gliding down the
shoulder 18 of the journal 13 into line above the recess 17, and the check-block w z
stopping the momentum of the doors Z by the pin hitting the same just as its
point and flat face begin to move along the flat face of the closing cam w, at w¹.
The opening pin has meantime passed through the opening wo and so cleared
itself from the guide rods to w. The face w¹ of the closing cam w, hugging the
flat face of the closing pin z holds the doors Z in position such that the dies Y are
free to enter the moulds G, which they are caused to do by the shrouds a, a, a, of
the gears A, A', bearing down on the shoulders y¹ of the doors Z, owing to the
gears A, A, through their being journalled on the eccentric portions of the
sleeves C, C here approaching the periphery of the drum E. At 8-2 the dies Y
having slightly entered the moulds G, the rollers J on the plunger shafts I engage
the rise 2-3 of the faces of the cams D, D' and drive the shafts I and with them
the plungers H rapidly outward from the centre 8, the action being so quick as to
partake largely of the nature of a blow, the effect being to expel the greater part
of the air or gas in the material to be pressed, said air or gas escaping through the
holes y and ducts y³ of the door-dies Y, above and any air that goes out below doing
so through the ducts ³ and hole 3 (centre) of the frogmark ' and plunger die h
(Figs. 5 et seq.). The clay of course surrounds, while in the moulds, the
perforations a, whose points as the door-dies Y continue to be drawn by the action
of the gears A, A' into the moulds enter the holes y, the plungers H meantime
advancing upwards in the mould by the action of the curved faces 3-3¹ of the
cams D D on the rollers J, the clay between 3 and 31 being thus subjected to a
slowly increasing double pressure. By establishing the pressure-curves of different
materials (which I have done by "plotting out" said curves from data obtained
from actual experiments made at the School of Practical Science, Toronto, by
Prof. Galbraith, myself, et al.) I have been enabled so to proportion the spirals of
the curve 3, 3¹ of the cams D, D' as to make the demand on the power driving the
pulley at p on the pulley shaft P practically uniform during the entire revolution
of the machine.
At 3 the gears A, A¹ begin to retreat and the faces of the cams D, D¹ being
from 3 to 4 based on a concentric to centre 9 (the gear-centre) plus just sufficient
outward trend to give a maintained pressure, force the plungers H to follow the
retreat of the door-dies Y which retire from the moulds G as the gears A, A', from
their eccentric motion leave the periphery of the drum E. Meantime between
3, 3, 4 any little air or gas left in the material at 3 finds its way through the hollow
perforators by means of the ingress ducts 2 the core r¹ and the egress ducts,
and so through the holes y and cross-ducts y³ of the door-dies Y to the outer air.
At 4° the dies Y have nearly left the moulds G, only about one-sixteenth of an
inch remaining in the moulds, when the rollers J pass over the "break" 4 in the
faces of the cams D, D', and all pressure ceases. The gears still continuing out-
ward bring the projecting flange a', a¹, a', against the lower shoulders y' of the
doors Z and lift the doors Z with the dies Y clean out of the moulds & so that
when the opening pins ¹ of the doors Z engage the opening cam w³, the doors are
free to swing open in a quarter circle about the journals 13, the key 19 passing up
the shoulder 18 from across the recess 17 to the annular groove 16, and assuming
the position shown (Fig. 8B), while the closing pin through the clearance
between wo and w³z, Fig. 2 swings in between the guide rods w³ ³ and is followed
by the opening pin or roller z¹. The doors Z and dies Y being now out of the
way the rollers J at 5 engage the rise 5-6 which forcing the plungers clear up to
the top of the moulds G strips the finished bricks or billets off the perforators x,
without injury, and drops them out of the moulds G upon the delivery belts o² 0³
for conveyance away.
Where a brush is used the concentric face 6-7 of the
B

page_text: cams D, D¹ keeps the plungers and plunger-dies h (¹) protruding from the
moulds G as long as may be arranged, and continuing the revolution the rollers k
encounter the rod d', pulling back the plungers to the adjustment set by means of
the shaft n, controlling the position of the slider M, as before fully explained and
so "to the place of beginning," i.e. under the feed spouts or hopper.
Although in the drawings I have shown the cams D, D' designed at 6 to deliver
the block or brick at the bottom of the machine, it will of course be understood
that the portions of the cams which exert the pressure on the plunger may be
varied in length, so as to lengthen the arc of pressure and defer also the delivery
of the block to any desired point preceding the feed; but I wish to lay particular
stress in this Application upon the form of cam by which the block is delivered at
the bottom of the machine thereby obviating the necessity of extra mechanism for
the handling of the bricks or blocks from the machine.
In the drawings I have also shown a pair of moulds one on each side of the
journal pins 13 of the doors Z; but it will of course be understood that the machine
may be wider and more than one mould may be placed in the periphery of the
drum E, on each side of the pins 13.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed I declare that what I
claim is :-
1. In a rotary press a stationary shaft supporting one or more stationary cams,
in combination with a hollow drum revolving around the said shaft and provided
with a set of plungers adapted to reciprocate by the action of the said cam or cams
in radial moulds formed in the periphery of the said drum in such a manner that
the pressure derived from the said cam or cams shall be radial from the axis of
revolution substantially as and for the purpose specified.
2. In a rotary press a stationary shaft around which a pair of gears or their
equivalent are free to revolve eccentrically to the said shaft in combination with a
hollow drum revolving by motion imparted from the said gears concentrically to
the said shaft and carrying around with it a set of doors adapted to rotate for a
quarter-revolution around radial pivot pins or journals situated midway between
pairs of radial moulds formed in the periphery of the said drum lying between the
said gears or their equivalents, said doors being provided with plates on their side
adjacent to the periphery of the said drum adapted to reciprocate in the said radial
moulds when the said doors are turned lengthwise along the said drum, such
reciprocation being caused by the action of shrouds or other means upon the inner
faces of the said eccentrically revolving gears, they engaging the outer end of the
said doors when turned as aforesaid, substantially as and for the purpose specified.
3. In a rotary press a stationary shaft with sleeves firmly attached about the
same upon which freely revolves the main body of the press in combination with
holes bored lengthwise through the said sleeves for the admission of means for
providing supplementary motion or heat within the said press while in revolution
substantially as and for the purposes specified.
4. In a rotary machine having parts rotating on parallel axes but eccentric to
one another though with adjacent faces, a series of holes S counterbored in the
face of one part in combination with a series of journalled rollers T protruding at
right angles from the face of the other adjacent part into the said holes, of the
relative proportions and substantially as and for the purpose specified.
5. In a brick press a device for making perforated brick at a single operation by
means of a rod or rods firmly supported below the delivery-die in each mould, up
and down about which the said die is adapted to reciprocate by means of holes
bored through it in the direction of its motion in combination with the necessary
clearance holes in the other die or cover of each mould for the points of the said
rod or rods substantially as and for the purpose specified.
6. In a brick press, a frogmark plate or die having on its face adjacent to the

page_text: ordinary flat dies channels or grooves forming with the flat dies ducts for the escape
of air in combination with a hole or holes in the ordinary flat dies substantially as
and for the purposes specified.
7. In a rotary press a drum provided with a series of moulds having the corre-
sponding number of plungers therein which derive a radial movement from stationary
cams on the main shaft of the machine, and a pivoted gate or door provided with
dies for each pair of moulds, and having bearings at the ends, in combination with
a pair of eccentrically journalled gears imparting motion to the drum and shrouds
or lugs on the said gears adapted to engage the bearings at both ends of the doors
so that the plates on the doors may be forced into the moulds so as to co-act with
the radially movable plungers as and for the purposes specified.
8. In a rotary press a series of moulds rotating around the main shaft of the
machine and provided with radially moving plungers in combination with a stationary
cam the periphery of which is parallel to the axis of said shaft and is concentric
from 1, to 2, and from 2, to 3, is provided with a sudden rise, as described, from 3,
to 3', with gradually decreasing rises, from 3 to 4, with a complex rise, as
described, from 4 to 5, with a depression from 5 to 6, with a further sharp rise
from 6 to 7, with a concentric portion and following with means whereby a rod or
bar may be adjusted in its relation to the cam and moulds as and for the
purposes specified.
9. The drum E provided with the moulds G, the plungers H provided with the
dies h, and frogmark plates h¹, the shaft I provided with the rollers J, and having
tenoned ends moving in radial slots in the ends of the drum E, and provided also
with the sleeve J' having its lug K and roller k, and the cams D, D', with the
arm d, the rod d', and means for adjusting the same, arranged to operate upon each
pair of rollers, and the rollers k as they rotate, in combination with the feed
hoppers V and pivoted door Z arranged to close the top of the moulds and enter
the same when the pressure is being exercised upon the plungers by the cams D, D'
as and for the purposes specified.
10. A rotary press comprising a frame, a rotary drum journalled therein pro-
vided with raised projections set between grooves in its periphery and in the
said projections at intervals pairs of moulds cutting chords in the circumference
of said projection, with plungers reciprocating in the said moulds and a pair of feed
hoppers for feeding material into the said moulds having slides provided at their
remote ends designed to follow the said chords substantially as and for the purposes
specified.
11. The drum E provided with the moulds G, the plungers H provided with the
top plate the shaft I provided with the rollers J and sleeves J', and having
tenoned ends moving in radial slots, and the cams D, D', with their rod d' arranged
to operate upon each pair of rollers J, and the return rollers k, as they rotate, in
combination with the feed hoppers V (secured to the guide bars w²) the doors Z
provided with the opening rollers z' and the closing pin and the closing cam w,
with its face w', the check-block w and the opening cam w', and the clearances w³
and w², as and for the purposes specified.
12. The drum E provided with the moulds G the plungers H provided with the
top-plate the shaft 1 provided with the rollers J and the sleeve J', and having
tenoned ends moving in radial slots, and the cams D, D' and rod d'arranged to
operate on each pair of rollers J and the return rollers as they rotate, in combina-
tion with the door Z pivoted on the journalled pins 13 which have the annular
groove 16 shoulder 18 and recess 17 cut in them, the keys 19 extending through
the doors and moving in the grooves, shoulders, and recesses, of the pins 13,
substantially as and for the purposes specified.
13. The drum E provided with the moulds G the plungers H provided with the
top-plate the shaft I provided with the rollers J and sleeve J¹, and having
tenoned ends moving in radial slot and the cams D, D' and rod d' arranged to
operate on each pair of rollers J and return rollers k as they rotate, in combination
with the doors Z provided with the closing pins z and opening roller *, pivoted on

page_text: the pin 13 having the grooves 16 shoulders 18 and recess 17 and key 19 and the
guide bars w having clearance at w³ for the roller z¹ and at w z for the pin z, and
the closing cam w, with its straight edge w³, designed to hug the flat side of the
pin z, and the check-block wz and the opening cam w as and for the purposes
specified.
14. The combination with the moulds formed in the drum, and plungers deriving
a radial reciprocating movement in the moulds, from the cams D, D' and the rod d³,
of the doors Z provided with the pin z and roller z¹ and adjustably held on the
journal pins 13, through the key 19, the grooves 16, shoulders 18, and recesses 17,
and having a curved under-shoulder y² and the flange a', a', a', on the eccentrically
journalled gears A, A' substantially as aud for the purposes specified.
15. The combination with the moulds formed in the drum, and plungers deriving
a radial reciprocating movement in the moulds from the cams D, D', and rod d¹ of
the doors Z provided with the pin 2 and roller and adjustably held on the
journal pins 13 through the key 19, the grooves 16, shoulders 18 and recesses 17,
the guide bars w³, the closing cam to, w', the flange a', a', a', and the shrouds a, a, a,
beneath which the shoulders y' of the doors extend as and for the purposes
specified.
16. The combination with the moulds formed in the drum and plungers deriving
a radial reciprocating movement therein from the cams D, D' and rod d' of the
doors Z adjustably held on their journal pins 13 and having dies Y as and for the
purposes specified.
17. The combination with a revolving driving disc or gear and a rotatable disc
or gear to be driven, the two revolving in planes parallel to each other, of friction
rollers carried by the face of the driving disc adjacent to the driven disc and holes
or counter bores in the adjacent face of such driven disc around the sides of which
holes said rollers travel, for the purpose set forth.
18. The eccentrically journalled gears A, A', having on their inner faces the
journalled rollers T in combination with the counterbored holes S, in the ends of
the drum E of a radius proportioned to the eccentricity of the gears A, A¹, and the
radius of the rollers T designed to convey a uniform rotary motion to the drum E
and keep the gear and drum radii which are coincident on the line of centres,
parallel in all other positions substantially as and for the purpose specified.
19. The doors Z provided with the plates Y adjustably held when closed on
their pivot pins 13 above the moulds Ġ in the drum E in combination with the
eccentric gear wheels A, A', having inwardly extending shrouds a, a, a, and the
flange a¹, a, a, on each wheel, between which the shoulders y', y², of the doors when
closed extend and the journalled rollers T extending into the counterbored holes S,
in the ends of the drum E as and for the purpose specified.
20. The combination with the drum E provided with moulds G, the plungers H
radially movable in the said moulds by the cams D, D', of the rod d', sliding
piece M bearing surface m', pin m, slotted cam N, shaft n and means for rotating
the said shaft as and for the purpose specified.
Dis 20th dox of Tul, 1001
F. WISE HOWORTH,
46, Lincoln's Inn Fields, London, W.C., Agent for the Applicant.