Improvements in or relating to Variable Speed Apparatus for Transmitting Power.
Year: 1896

page_text: Date of Application, 8th Apr., 1896
Complete Specification Left, 8th Feb., 1897-Accepted, 8th July, 1897
PROVISIONAL SPECIFICATION.
Improvements in or relating to Variable Speed Apparatus for
Transmitting Power.
I, JOHN WILLIAM HALL, of 1, Wiltshire Road, Brixton, in the County of
Surrey, Engineer, do hereby declare the nature of this invention to be as follows:-
I have before now described a form of variable speed reducer or starter which,
though well adapted for gradually starting or stopping a vehicle without inter-
fering with the speed of the engine, did not when running slowly (i.e. geared down
relatively to the engine) give increased hill climbing power instead of speed,
but simply allowed the surplus engine power to run to waste. The apparatus
may be shortly described as a disc fitted on the end of a short shaft which rotates
in suitable bearings and round the face of the disc are fitted several force pumps
or cylinders, the connecting rods of the pistons or plungers of which are operated
or driven by the engine shaft either by a crank or by gearing. The pumps
draw the working fluid from a casing which surrounds the disc and delivers it
into a central hole in the short shaft, and motion is given to the vehicle by suit-
able gearing from this shaft. When the outer end of the hole in the shaft is
open, the pumps will deliver their fluid without resistance and therefore the disc
and shaft will remain at rest, but when it is closed by a valve, the pumps will
be unable to deliver their contents and therefore the disc and shaft will be com-
pelled to rotate and so give motion to the vehicle, the rate of speed depending
on whether the shaft hole or pump delivery is wholly or partly closed.
According to my present invention I so construct the mechanism above des-
cribed, that, in addition to being a means of gradually applying or taking away
the power, it will also be able to give greater hill climbing or pulling power in
place of speed.
One way of accomplishing this result is as follows:-
On the end of the short shaft opposite to that which carries the disc I fix
radially to the shaft preferably three or more cylinders which rotate with the
shaft, the connecting rods of their pistons being connected to a crank which is
fixed, the cylinders revolving instead of the crank.
These cylinders are of greater collective capacity than the total capacity of
the pump cylinders according to the number of times it is desired to gear the
revolutions of the disc and shaft below the speed of the engine shaft.
The valves for the distribution of the working fluid (which may be air, water,
oil or other convenient medium) to the large cylinders can be worked by an
eccentric on the fixed crank shaft above mentioned, and the passages for the
flow of working fluid from the small to the large cylinders can be made through
the body of the short shaft.

page_text: The arrangements by which the passage of the working fluid from the small
to the large cylinders is regulated may be operated by the driver, or automa-
tically by a governor driven by the engine.
For the purpose of completely stopping or partly slowing down the motion of
the vehicle an arrangement may be used to allow the working fluid to pass away
from the pump cylinders without doing work on the vehicle, or the valves of
the large cylinders may be so fitted 'as to allow the fluid to pass them without
doing work, and when the hill climbing gear is not in use, I prefer to so con-
struct the fixed or non-rotating crank pin on which the large cylinder connect-
ing rods work, that it may be drawn into line with the centre line of the disc
and short shaft so as to stop the working of the pistons and prevent friction.
The large engine may be separate and connected by gearing.
I do not by any means bind myself to use the above described details of con-
struction only as they can be greatly varied without departing from the spirit
of this invention.
This invention may be used for gearing up instead of or in addition to. gear-
ing down, the details of construction being varied as required for this purpose.
In an alternative arrangement the cylinders would be fixed and the crank
revolve.
I prefer to place the cylinders radially stated 'but I may arrange them in any
other manner--parallel with the shaft for example if preferred.
The range of accommodation may be increased by: working the: fluid pressuré
expansively.
Instead of cylinders and pistons: I may, use other mechanism; for example
one similar to a Root's blower.
. Dated this 8th day of April '1896
BOULT & WADE,
Agents for the Applicant.
COMPLETE SPECIFICATION (AMENDED).
Improvements in or relating to Variable Speed Apparatus for
Transmitting Power.
I, JOHN WILLIAM HALL, of 1, Wiltshire Road, Brixton, in the County of
Surrey, Engineer, do hereby declare the nature of this invention and in what
manner the same is to be performed, to be particularly described and ascertained
in and by the following statement :-
This invention relates to power-transmission apparatus comprising an appli
ance in which the relative speed of the driving and driven parts is variable. by.
varying the freedom of circulation of the fluid circulated by and operatively.
connecting them.
Examples of such an appliance are described in the Specification of prior Letters
Patent No. 6590 '96 granted to me..
According to my present invention apparatus of the type above. referred to is
employed in combination with a motor preferably of a different capacity prima-
rily, which is variable in the manner hereinafter described; in such apparatus
variation of the turning effort transmitted may be effected solely by altering
the capacity of the motor, or by varying the freedom of circulation of the circu-
lating fluid in addition to varying the capacity of the motor. Preferably the
apparatus is so constructed that the cylinders of the fluid -circulating device
(hereinafter referred to as the pump) and the motor are connected rigidly together
and rotate in company, the rotating mass being coupled to the road wheel of a

page_text: self-propelled vehicle for instance, or to any other apparátus which it is desired.
to-drive. with varying power and speed from a prime mover; which is intended
to-run at a speed approximately constant. But if desired the. rotating cylinders.
of the pump can be geared directly to the part to be driven' and the rotating:
cylinders of the motor can similarly be directly connected to the-driven part,
in which case the total power transmitted by, the" separate connections between
pump and 'motor and the part driven will be the sameras if both these-appliances
were employed (as in the: préceding example) to transmit their reombined' effort'
through a single connection."
The capacity of the motor is variable by means of an adjustable crank-pin, to
which the motor piston-rods are connected by adjusting the eccentricity of this
crank-pin relatively to the axis about which thermotor cylinders rotate, the move
ment of the motor pistons relatively to-the motor cylinders can be varied between
nil and a maximum, so as to vary the capacity of the motor for fluid delivered:
thereto by the pump.
In the accompanying drawings.
Fig. 1 is a view partly in plan, and partly in section on the planet of the axis
of rotation X Y of one construction of 'apparatus according to this invention;
Figure 2. is a view of the same apparatus, in section on the three: transverse:
planes 22 of Figure :1;.
Figure 3.is a plan of one' set of cylinders and the corresponding valve: chest; .
partly in section 'on the line 3-3 of Figure 1Ę
Figure 4'is a view half in' section in the plane- of the axis X Y. and half-in's
elevation, illustrating mechanism for control of a valve/such as is' hereinafter.
referred to with regard to. Figures. 1, 2, and 3.
Figure-5 is an end elevation of the 'apparatus illustrated in Figure 4:
Figures 6, 7, and 8 are details of apparatus by which the" angular-advance of
an eccentric sheave forming: part of Figure 1 is controlled,. Figure. 6 being a face
view of the cap Ja of the crank pin Jof Figure 1 and Figure. 7 being: a section on
the line-7-7 of Figure 8;
Figures 9, 10 and 11 are details of an' arrangement of mechanism: which can'
be employed to control the valves F of Figure-1 instead of the apparatus shown
in that figure, the view shown in Figure 9' corresponding to a transverse section.
on the line 9-9 of Figure 1; Figures 10 and 11'being-half sections on the radial
lines 10 and 11 of Figure 9.
A is the driving: shaft, to which a motion of rotation is imparted from a prime
mover by the spur wheel A¹ keyed thereon, or otherwise; this shaft is supported
by the frame B in bearings B', as also is the shaft C the two shafts being-in line;
the-shaft C is stationary, and constitutes a 'fixed eccentric bearing as will herein-
after appear:
A casing D supported partly. on the driving: shaft A so as
to encircle the latter within one of the bearings B; and partly supported 'on the
shaft or bearing C so that it can turn about both shafts, comprises a series of
single-acting pump cylinders D in each of which is a piston D. The cylinders Di
are. three in number and are disposed radially at angles of 120°, around the
driving shaft A which latter is provided with a crank pin A engaged by the
connecting rods D³ of each of the three pump-pistons D². D is a diaphragm
which closes the side of the casing: D opposite to that through which the driving
shaft A passes. In cach piston D2 is a non-return valve D5 loaded lightly by a
spring, and in a diaphragm D extending across each pump cylinder D' just beyond.
the outer limit of the travel of the piston is a similar spring-loaded non-return
valve D, the outer end of each cylinder being closed by a cover Ds, and the inner
end being. open to communicate with the interior of the casing D. From the
outer end of each pump cylinder a passage D9 (Fig. 1) leads into a valve cham-
ber E, into which is forced a cylindrical liner E¹ within which is a piston-valve F
operated by valve-gear, as is hereinafter described. From the valve-chamber E
the circulating. fluid delivered into it by the pumps can return into the chamber
in which the crank pin A2 revolves by either of two courses, or by both these

page_text: courses simultaneously. Ports E2 are provided in the liner to admit the fluid
delivered from the passages D into the interior of the liner whence it may pass
below the upper piston F1 of the piston-valve F through the upper ports E³ in
the liner into the adjacent motor cylinder G, by way of the passages G1, thence
exhausting through the ports E³ over the outer end of the piston Fi and by way
of circulation or exhaust passages E4, (Figs. 2 and 3) leading from the outer end
of each of the valve-chambers E, back into the crank chamber in which the
crank pin A2 revolves; this is one of the two courses above referred to. The
other course is by way of circulation-passages E or their equivalent (Fig. 2)
leading from each valve-chamber at the point opposite the ports Es to the neigh-
bouring valve-chamber and connecting them all to the interior of a cylindrical
shell E secured inside the casing D and communicating with the interior of
that casing by way of a valve K which operates to vary the freedom of circulation
of the fluid and will hereinafter be more particularly described; these circula-
tion-passages E³ are in free communication with each other through the several
valve-chests E.
Motor cylinders which in the present example are shown as having greater
capacity than the pump cylinders D¹ are attached to the casing D as shown;
they are three in number like the pump cylinders D' and each is disposed in line
with its companion pump-cylinder so that the three motor cylinders are at equal
angular distances apart around the axis of rotation X Y of the apparatus. H are
the motor pistons, each being channelled as at H¹ so that when it is at the outer
extreme of its travel the fluid coming from the valve-chest E by way of the pas-
sages G' shall pass easily to the outer end of each cylinder G with a minimum
of resistance. H² are connecting-rods which connect the motor-pistons H to a
crank-pin J as shown; normally this crank pin and the shaft Care stationary,
but the pin forms part of what will hereinafter be termed a secondary shaft J
journalled eccentrically within the said shaft C which affords a long and rigid
bearing therefor, in which it is adjustable, but in which it is normally prevented
from rotating as will hereinafter appear. The eccentricity of the secondary shaft J'
relatively to the axis of the shaft C (which is also the axis of rotation of the
apparatus) is such, and the throw of the crank J is such relatively to the actual
longitudinal axis of the secondary shaft J', that by rotating the secondary shaft J¹
within its long bearing in the shaft C, the radial distance of the crank pin J from
the axis of rotation XY, that is to say, its effective throw, can be varied from
the maximum distance (at which it is shown in the drawings) to nil, the latter
condition obtaining when the secondary shaft J is so far rotated as to bring the
axis of the crank pin J into coincidence with the axis of rotation X Y. J² is a
worm wheel fixed on the outer end of the secondary shaft J¹, so that by suitable
gearing, not shown in the drawings, the latter can be rotated within the fixed
shaft C, the worm-gearing serving also to prevent its accidental rotation. D10 is
a chain wheel keyed upon the casing D as to transmit to, say the road wheel of
an autocar, the rotary motion of the casing set up as hereinafter explained.
It is intended that the part of the casing D which forms a crank-chamber for
the crank pin A shall be filled with a circulating fluid which fills also the pump
cylinders D', the passage D, the interior of the valve-chamber E between the
pistons F1 F of the piston valve, the outer ends of the motor cylinders and valve
chest E and the passages E4 E5, (Fig. 2) and that by the rotation of the driving
shaft A, the pump pistons D2 shall circulate this fluid from the crank chamber
containing the crank pin A through one or both of the paths hereinbefore referred
to into the crank pin chamber again. It will be observed that the casing D, the
motor and pump cylinders G D₁ and valve chests E are rigidly connected together,
and that they, like the driving shaft A, are rotatable relatively to the shaft C.
The casing D turns about the axis of rotation X Y but the pistons H and con-
necting-rods H2 rotate about another axis which can be made eccentric thereto
in order that the motor pistons shall have a variable reciprocatory movement

page_text: relatively to their cylinders G, the amount of reciprocation being dependent upon
the eccentricity of the crank pin J to the axis of rotation X, Y.
Assuming that the valve K in the shell E (Figs. 2 & 4) is shut, and that the
crank pin J is concentric with the axis of rotation XY, rotation of the driving
shaft A would have the effect of rotating the casing D with an equal angular
velocity, for the fluid in the apparatus could not be circulated, and therefore
being practically incompressible, would transmit the rotative effort of the crank
pin directly to the casing D through the connecting-rods D³ and pistons 1)², and
thence to the apparatus driven thereby. But if it be assumed that the valve K
in the casing E' be so widely opened that communication between the outer ends
of the pump cylinders and the interior of the casing D be practically unimpeded.
(the crank pin J still being concentric with the axis X Y) the rotation of the
driving shaft A would simply circulate the fluid from the casing D through the
circulation passages E into the crank chamber again, only exerting a trifling
rotative effort upon the casing.
If, however, the crank-pin J be moved outward from the axis X Y and the
valve K in the shell E be shut, all the fluid from the casing D must pass from the
cylinders D¹ back to that casing by way of the motor cylinders G and their exhaust
passages E4; in doing this it exerts a rotative effort upon the casing D which
depends upon the amount of eccentricity of the crank pin J relatively to the
axis X Y. If the eccentricity be a maximum then the rotative effort will be a
maximum also, for a given volume of fluid forced between the pistons H and
covers of the motor cylinders will produce a smaller angular movement of the
casing D when the eccentricity of the pin J is a maximum than when it has a
lesser eccentricity. If, whilst the crank pin is eccentric as in the instance just
considered the valve K in the shell E' be opened, some of the circulating fluid
instead of going into the motor cylinders to effect the relative movement of those
cylinders and their pistons will be short-circuited" through the shell E into
the casing again, thus lessening the rotative effort upon the casing D.
The valve K in the shell E of the apparatus by which it is operated will now
be described with reference to Figs. 4 and 5.
The valve K consists in part of a mitred disc K', which seats itself upon a coned
portion E of the shell E, and in part of a piston K² with hydraulic packing
sliding in a cylindrically-bored portion E of the shell E. This valve is pro-
vided with a screw-threaded spindle E10 engaging with a correspondingly screw-
threaded portion D11 of the casing D and passing to the exterior through a stuffing-
box D12 outside which it is provided with a pinion E. This pinion E¹¹ gears
with a toothed ring L which encircles and can turn on a portion of the casing D
and is geared to another toothed ring D13, which is fixed to the casing and rotates
therewith; the fixed ring D¹³ and the rotatable ring L are geared to each other
by an idler N and intermediate train supported on a shaft M in bearings B₂ on
the framing B, and having its individual members disposed in a manner well
understood, so that normally the ring L is caused to travel with the casing D
at the same angular velocity and in the same direction as the latter by the inter-
mediate gear driven by the ring D13; this intermediate gear is carried within
a casing O which has teeth O' around its periphery geared with a manually con-
trolled pinion P. So long as this pinion P is not operated the casing O has no
angular movement around the shaft M, but by turning the pinion P, the casing O
and the contained gearing can be turned about the shaft M relatively to the
ring D and by such movement the ring L will be turned relatively to the
casing D (whether the latter happens to be at rest or in motion) so as to turn
the pinion E and adjust the valve K as desired. Instead of the spindle E
being rigid it may be provided with a spring so as to allow of the valve K to
yield to any sudden increase of pressure in the passages E; or these passages
instead may be fitted with a release valve loaded to the desired pressure.
The piston valves F of Figs. 1 and 2 which are balanced are each operatively
connected by means of an eccentric rod F with an eccentric sheave Q.

page_text: An oil hole A³ is drilled through the shaft A to which a charging pump for
keeping the interior spaces of the apparatus fully charged with oil can be applied
in the manner indicated in the Specification of prior Letters Patent No. 6590
of 1896 aforesaid.
The whole of the interior spaces of the casing D, and not merely those pre-
viously specified, can if desired be filled with fluid. The circulating fluid might
be circulated to and from a chamber distinct from that in which the crank-pin A²
turns; such chamber could be attached to or formed as part of the casing D, and
preferably should be symmetrical and concentric with the axis X Y.
The circulation which in the examples hereinbefore referred to occurs in a
circuit which is wholly internal, might be differently arranged; for instance the
pumps might draw their supply from any convenient source through the pump
crank shaft, and the motor might exhaust to any other point through the motor
crank shaft or bearing, or the circulation may be otherwise effected.
It is necessary to have the eccentric sheave Q so arranged and adjustable that
although the crank pin J (Fig. 1) has an angular and radial adjustment relatively
to the axis of rotation X Y, a line joining the centre of the pin J with that axis
shall always be at right angles to another line joining the axis of rotation with
the centre of the eccentric, ie., it is necessary to keep the angular advance of
the eccentric constant. This result is obtained in the example illustrated in
Figure 1, whereof the details are shown more clearly in Figs. 6, 7 and 8, by
pivotting the eccentric sheave Q eccentrically on a stud R, which is co-axial
with the axis XY, and fixing upon it guides such as Q Q which intersect each
other at the stud R (Fig. 1) at right angles and have upon the centre line of
one of them (Q2, Fig. 8) the centre Q of the sheave. In these guides are
blocks A A; the block A+ is engaged by a pin A (Figs. 1 and 6) which projects
from the crank pin cap J3 and is in line with the centre of the crank pin J, and
the block A is engaged by a similar pin A7, this latter being at one end and the
pin A at the other end of a diameter of the dotted circle S (Fig. 6) in which the
crank pin J travels in its adjustment by the secondary shaft J. When the
crank pin J (which in Figs. 1 and 0 is shown as having its maximum eccentricity)
is turned to bring it nearer the axis X Y, the block A travels along the guide Q
towards its intersection with the guide Q2 along which the block A5 travels. In
this movement, both blocks travel in the dotted circle S and consequently by
their action on the guides Q1 Q2 turn the same and the sheave Q about the stud R
(Fig. 1) keeping the centre Q³ (Fig. 8) of the sheave always 90 degrees in advance
of a line $1 drawn from the axis X Y to the crank pin J and constituting the
virtual throw of the crank.
The employment of two blocks A4 A5 and pins A A7 is necessitated by the
fact that at certain points in its travel the pin A may become concentric with
the axis of rotation of the apparatus, and also with the point of intersection of
the two channels of the guides Q1 Q2 and if there were only this one pin the
casing D in its rotation would under such circumstances turn the eccentric sheave
with it, and therefore the valve worked from the sheave would obtain no recipro-
cation, for they, the casing and the valves, would spin about the axis of rotation
as one mass; but the provision of two blocks A4 A5 only one of which can at
any time be concentric with the axis of rotation obviates this difficulty. By
continuously moving the pin A in the circle S from the position in which it is
now shown to and past the axis of rotation (at which the virtual throw of the
crank pin J disappears) it will be found that the eccentric, which as now shown
has, say, positive advance, will change from positive to negative advance in
every alternate revolution in that circle as the pin A passes the axial line, i.e.
the eccentric will have become properly set for running the apparatus in a direc-
tion the reverse of that shown by the arrow in Figs. 6 and 8. As it is not
necessary that the rotation of the pins A A7 should be stopped at any particular
point in the circle S, the device described could constitute an "all round revers-
ing gear, applicable to many types of motor in addition to that to which its appli-

page_text: cation is herein described as a reversing gear utilizing only a part of its possible
range.
In the operation of the apparatus hereinbefore described it happens under
certain circumstances that the casing D rotates at times when the motor cylin-
ders G are not required to receive the working fluid. At such times it is not
necessary that the valves F in the valve chests E should be operated at all, for
the fluid will circulate through the passages E without going through the motor.
In order to avoid the friction losses which occur if the valves F are operated
unnecessarily an arrangement such as is illustrated in Figs. 9, 10 and 11 may be
employed.
In these figures a single eccentric sheave Q adjustable by means similar to
those described with reference to Figures 6, 7 and 8, is provided with a strap Q+
which instead of being coupled directly to the several valves F is linked by the
rods to rockers T pivotted in brackets T¹ carried by a ring T adapted to turn
about a flanged portion of the base plate R¹ of the stud R concentric to the axis
of rotation X Y of the casing D. These rockers are so formed that with the
ring and brackets T in the position relatively to the valves F in which they
are shown in Fig. 9 the motion of the eccentric rods F4 is transmitted to the
valves almost without modification. But if the ring T12 be rotated in the direc-
tion of the arrow (Fig. 9) so as to bring the brackets T¹ in line with the ends
of the valves F, the rockers in the rotation of the casing D will be operated by
the sheave Qas before, but the valves, being supported by the rockers T at points
opposite the pivots T³ about which the latter turn will not be reciprocated. The
manner in which the rockers are pivotted and in which the brackets are formed
to receive them may be clearly seen from Fig. 11 which is a section on the radial
line of Fig. 9. The rockers are journalled between the brackets T¹ in order
that the pivots in the latter may be brought directly into line with the normal
path of the valves. Conveniently the lower ends of the valves and the bottom
of the channels in the rockers near the pivots may be curved with a radius taken
from the centres of the pivots; in such case the vibratory movement of the rockers
will have no effect upon the valves when the brackets and the valves are in
line. In the example illustrated the periphery of the ring T2 is formed as a
worm wheel with which engages a worm U journalled in the casing D as shown.
This worm may be operated from the exterior whilst the casing D is in rotation
by the provision of gearing such for instance as has been hereinbefore described
with reference to Figs. 4 and 5; in the drawing it is shown as geared to an
electric motor U₁ carried on the casing. Where an electric motor is employed
for operating the worm it can be controlled by an automatic switch arranged to
be operated by the secondary shaft J (Fig. 1) aforesaid; for example, the valves F
should be inoperative at such times as the crank pin J is concentric with the axis
of rotation XY; on the other hand they should have their full travel whenever
the crank pin is not thus concentric. It is a simple matter to arrange contacts
on the shaft J in connection with contact rings on the casing D electrically
connected to the motor, the several contacts being so disposed that when the
crank pin is concentric as described the current is transmitted to the motor in
such a manner as to cause the latter to move the ring T2 to one extreme of its
travel in the direction of the arrow in Figure 9, whereas movement of the
secondary shaft J' to adjust the crank pin J into any other position effects the
reversal of current and causes the worm U to move the ring T2 into the position
in which it is shown in Figure 9.
In order to prevent waste of current means may be provided upon the worm U
or ring 12 to shut off the current to the motor as soon as the ring arrives at either
of its extreme positions.
The valves F are merely indicated diagrammatically in Figure 9 for the sake
of simplicity, and shown with a slot and pin to limit their movements. They
might have rollers at their lower ends where they bear on the rockers and they

page_text: employed in the apparatus.
In-apparatus-of-the-kind-hereinbefore described-an-elastic-fluid such as air miny
be-employed-for-the-transmission-of-power, instead of an elastic fluid in order that
such-elastic-fluid may-be-employed expansively in thre-meter-ylinders-a-slide-valve
of the type-common-in-expansion-engines or other equivalent device is employed,
and-operated by appropriate gearing The variations of power would-be obtained
not-by-varying the travel of the pistons of the motor cylinders, but-by-varying the
expansion-of-the-fluid-in-them.
The valve K or its equivalent may if desired be arranged to be operated by a
governor, instead of by hand; similarly the crank pin J might be adjusted auto-
matically.
I do not by any means bind myself to use the above described details of con-
struction only as they can be greatly varied without departing from the spirit of
this invention.
In-an-alternative arrangement the cylinders would be fixed-and-the-cranks
revolved
I prefer to place the cylinders radially as stated but I may arrange them in
any other manner-parallel with the shaft for example and geared together by
bevel gear if desired.
Instead of cylinders and pistons I may use other mechanism for example devices
similar to those in-use in a Roots' blower.
It is possible, though not mechanically desirable, that a single pump cylinder
and single motor-cylinder should be employed instead of groups of pump and
motor cylinders, or there might be a single pump-cylinder and two or more
related motor-cylinders; but it is preferable that both the pump and the motor
should be multiple-cylindered.
Having now particularly described and ascertained the nature of the said
invention, and in what manner the same is to be performed, I declare that what
I claim is
1. The employment of a power-transmission apparatus in which a fluid is used.
substantially in the manner and for the purpose hereinbefore described.
2. A power-transmission apparatus in which a turning effort is transmitted to
the driven part by or through fluid circulating devices arranged and operating
substantially as and for the purpose described.
3. A power-transmission apparatus in which a turning effort is transmitted to
the driven part by fluid-circulating devices which rotate in company and operate
substantially as and for the purpose described.
4. A power-transmission apparatus in which a turning effort is transmitted to
the driven part which has an adjustable crank-pin by or through fluid-circulating
devices substantially as and for the purpose described.
5. In power-transmission apparatus of the kind hereinbefore referred to the
combination of pump and motor cylinders and a crank of variable throw for the
motor cylinders substantially as and for the purpose described.
6. In a power-transmission apparatus the combination with a driving shaft
such as A, rotatable casing with cylinders such as D' G, fixed eccentric bearing
such as C supporting an adjustable crank pin, and mechanism whereby the circu-
lation of a fluid is regulated in one or more paths for the purpose described.
7. A power-transmission apparatus of the kind claimed in the preceding claim-
ing-clauses, so constructed as to be capable of reversal.
8. In power-transmission apparatus of the kind described the combination with
circulation-passage such as E a control valve therein and a rotatable casing
such as D of an intermediate gear and mechanism by which the valve may be
controlled whilst it is rotating in company with the casing D.
9. In power-transmission apparatus of the kind hereinbefore referred to the

page_text: combination with a crank adjustable relatively to a given axis of rotation, of
mechanism substantially as hereinbefore described, controlling the "angular
advance" of the sheave.
10. In power transmission apparatus of the kind hereinbefore referred-to-the
combination with an eccentric, of rockers such as T and an adjustable-ring T
arranged and operating substantially as and for the purpose described.
10. H. In power-transmission apparatus of the kind hereinbefore referred to,
the combination and arrangement of parts constituting a reversing valve-gear sub-
stantially as described and illustrated in Figures 6, 7 and 8 of the accompanying
drawings.
11. 2. The combination and arrangement of parts constituting the complete
power-transmission apparatus substantially as described and illustrated in
Figures 12 and 3 of the accompanying drawings.
Dated this 8th day of February 1897.
BOULT & WADE,
Agents for the Applicant.
BOULT & WADE,
Agents for the Applicant.