IMPROVEMENT an Invention of THE WORKING AND CONSTRUCTION OF HYDRAULIC MACHINERY
Year: 1880

page_text: LETTERS PATENT to Alexander Melville Clark, of 53, Chancery Lane, in the
"IMPROVEMENTS IN
County of Middlesex, Patent Agent, for an Invention of
THE WORKING AND CONSTRUCTION OF HYDRAULIC MACHINERY." A communi-
cation from abroad by Ernest Adolphe Jouvet, of Paris, France.
-
PROVISIONAL SPECIFICATION left by the said Alexander Melville Clark
at the Office of the Commissioners of Patents on the 2nd February 1880.
ALEXANDER MELVILLE CLARK, of 53, Chancery Lane, in the County of
Middlesex, Patent Agent. "IMPROVEMENTS IN THE WORKING AND CONSTRUCTION
OF HYDRAULIC MACHINERY,." [A communication from abroad by Ernest Adolphe
Jouvet, of Paris, France.]
This Invention relates to improvements in hydraulic apparatus, and has for its
object to obtain the division of the maximum of the available motive power into
any number of equal or unequal parts. In hydraulic apparatus heretofore employed
for utilising the energy or motive power of a head of water, the power expended to
overcome a resistance, even when working unloaded, is generally the maximum
available motive power. There is consequently a considerable loss of power when-
ever the resistance to be overcome does not correspond to the maximum of the
motive power.
The object of the present Invention is to reduce and even entirely prevent this
loss of power by the employment of apparatus whereby the division of the
maximum of the motive power is effected according to one or other of the two
following general principles :-
1st. Principle." Expenditure of a constant volume of water, and variation of
the pressure of the accumulator."
2nd. Principle.-"Variation of the volume of water expended and maintenance
of the pressure constant."
The motive power may be derived either from an accumulator or from a head of
water either natural or artificial. By a combination of these two principles the
division of the maximum of the power may be practically effected in as perfect and
economical a manner as can be desired.
It should be noted that in each principle the course of the principal piston or
pistons or other equivalents employed.is a constant.
APPLICATION OF THESE 2 PRINCIPLES, AND DESCRIPTION OF THE APPARATUS
EMPLOYED.
1st Principle" Expenditure of a constant volume of water, and variation of

page_text: The division of the maximum of the available motive power of the water under
pressure is obtained by dividing the total load acting on the plunger of the
accumulator into a certain number of equal or unequal parts, and combining these
together so as to put different loads upon the plunger, each corresponding to a
fraction of the maximum of the total pressure, and consequently of the motive
power which each apparatus connected with such accumulator is capable of
developing, so that in each case the apparatus works with an expenditure of the
same volume of water, but at a different pressure to that due to the total load
of the accumulator.
2nd. Principle." Variation of the volume of water expended, the pressure being
maintained constant."
This principle permits of dividing the maximum of the available motive power
of water acting under constant pressure in an apparatus, 1st, into a certain
number of equal or unequal parts by the employment of one or more differential
pistons, combined with one or more sliding sockets, whereby the variation of the
volume of water under constant pressure expended, and consequently that of the
motive power expended, is effected, as hereinafter fully described; 2nd, auto-
matically whatever may be the relation between the resistance and the maximum
of the available power of the apparatus by the employment of a compensator of the
power in excess expended in the principal apparatus. The operation of this
compensator is such, whatever may be the resistance to be overcome, that it is
equivalent to the restitution of the power in excess expended in the principal
apparatus to the source of power, and consequently the combined action of the two
apparatus corresponds to that of a single apparatus having an effective area varying
proportionately to the total resistance. In the first case, in order to overcome a
given resistance, the fraction equal or immediately superior thereto of the maximum
available motive power is utilised, and the loss of power is therefore equal only to
the difference between the two.
In the 2nd case to a given resistance equal to or less than the maximum of the
available power the motive power employed exactly corresponds, and there is
consequently no loss of power.
The following is a description of different arrangements of apparatus embodying
the principles before indicated, reference being had to the accompanying Drawings:-
First Principle.-"Expenditure of a constant volume of water, and variation of
the pressure of the accumulator."
It has been seen that the variation of the pressure of the accumulator is obtained
by the division of the load acting on its plunger into a certain number of equal or
unequal parts. If the loads be 7 in number, and be to one another as 2:3:4:
5:6:7 is to 8, which corresponds to the entire load, the value of each fraction of
the total load will be proportionate to the difference of two successive loads
2, 1, 1, 1, 1, 1, 1. The partial weights composing the total load in the accumulator
may be applied and removed either automatically, or by a mechanical arrangement,
or by hand.
The following is a description of an arrangement of accumulator in which the
mechanism for applying and removing the weights is worked by hand:-
In Figure 1 of the annexed Drawings A is the accumulator; B, the cylinder;
P, the plunger; C, C, C, guide columns fixed in the base plate F, and united at
their upper ends to a tie bar T; D¹, D³, D³, columns upon each of which are collars
V³, V, V, V, V, Vs, fitting freely thereon, and having lugs upon which the partial
weights E, E, E³, E6, E7, E³, are supported at the upper part of the accumulator
when they are not required to act on plunger P; E2, weight permanently attached
to plunger by means of a frame G. The remaining weights are superposed
successively upon weight E³ to form the various loads upon the accumulator;
H³, H, H³, H, H7, H8, toothed rings gearing with a toothed segment S upon each
of the collars V³, V, V, V, V7 V8. Each ring gears with the three collars
supporting each weight; a³, vertical shaft by which ring H³ is operated through a
pinion p³ on the upper end of said shaft. At the bottom end of this shaft is a

page_text: bevel pinion g³ in gear with a pinion o³ on the crank shaft m³. The remainder of
the toothed rings H*, H³, Hº, H7, H8, are similarly operated; R, water inlet pipe to
the cylinder of accumulator; U, retaining valve; I, cock for distributing the water
to the several machines operated by the accumulator; q³, q', q, q, q, q³, forks
embracing the guide columns C, C, C, three being provided for each weight;
b³, b, bº, 6º, 67, 68, supports by which each weight rests on the one next below;
p, rod of plunger P guided in cross bar T. The cranks m³, m*, m³, m³, m³, m³, may
be all connected together, and operated either mechanically or by hand. To apply
the weight E³ upon E2 in order to obtain a load E* + E³ upon plunger P, plunger P
is first raised until weight E' raises Es slightly from the collars V³, and the crank
m³ which operates the ring H³ is then caused to turn the collars V³ a quarter round,
whereupon the load on the accumulator will be E³, E³.
To remove weight E³ the operation is reversed; the weight E³ is first raised until
it is slightly above collars V³, and the crank m³ is then operated to turn said
collars a quarter round, so as to bring their lugs beneath the weight E³, which is
then lowered thereupon. The load upon the accumulator is now only E. The
application and renewal of the remaining weights is performed in a similar
manner, whereby 7 different loads may be applied to the accumulator.
This method of weighting the accumulator may be utilised for working all kinds
of hydraulic machinery, whatever may be their mode of action or the purpose for
which they are employed, such as hoists, presses, hauling machinery, and the like.
It is chiefly of advantage in cases where each machine employed is not required
during a certain period of time to furnish more than a fraction of the motive power
it is capable of developing.
Second Principle." Variation of the volume of water expended, and maintenance
of the pressure constant."
1st Arrangement. Division of the maximum of the power of water under constant
pressure into a determinate number of equal or unequal parts by the employment
of one or more differential pistons combined or not with one or more movable
sockets operated automatically.
I will proceed to describe by way of example some arrangements of apparatus on
this principle.
Figure 2 shows a hoist having 6 different powers.
This apparatus, which acts on the tackle by direct thrust, comprises two
differential pistons A, B, and two movable sockets I, J, the parts being represented
in the position of rest; K, fixed cylinder; A, piston whose diameter is D and
the diameter of whose rod is a; B, piston whose diameter is also D and the
diameter of whose rod is b, a, <b; I, movable socket with which is combined the
pulley block No. 1, said socket being fitted to slide freely upon the end i of
cylinder K, and also on the end of piston rod B; J, movable socket carrying pulley
block No. 2, and sliding freely on the end j of cylinder K and also on the end of
piston rod a; R¹, R³, R6, sheaves mounted on pulley block No. 1; R³, R, R, sheaves
imounted on pulley block No. 2; the chain G is attached at g to the pulley block
No. 1, and thence passes round the several pulleys, of which there may be any
number n in each block; N, guide pulley mounted on the fixed support t; H, chain;
E, maximum stroke of a piston in either direction; TD, water inlet between
pistons A and B; Ta, water inlet to the annular portion whose diameter is D-a;
Tb, water inlet to the annular portion whose diameter is D - b; 0, O, packing of
piston A; V, V, packing of piston B; p, packing in socket J; q, packing in
socket I.
The water under pressure may be admitted to act,―
1st. Between the pistons A and B whose diameter is D (maximum effect);
TD, open to pressure; Ta, Tb, open to exhaust. The two pistons and with them
the two socket I, J, are thus caused to move apart (see Figure 3) a distance equal
to E or /, E for each socket on either side of the line X, Y. The motion of the
chain H= (2 n + 1) E.
2nd. Upon the annular piston Da; Ta, open to pressure; Tb, open to

page_text: exhaust; TD, closed. The pulley block J in this case remains against cylinder K, as
in Figure 4, and piston A carries B, together with its pulley block I, along with it
a distance equal to E in the direction from J to I, which corresponds to a movement
(2n+1) E of the chain H.
3rd. Upon piston B and upon the annular piston D b; TD and Tb open to
pressure and Ta closed, Figure 5. The piston A and pulley block J remain
stationary while piston B moves pulley block I a distance equal to E in the
direction J to I, producing a movement (2n+1) E of the chain H.
4th. On the annular pistons D
T D, closed, Figure 6.
-
-
a, D
1
bi
T
a and Tb open to pressure;
The pulley block J remains stationary upon cylinder K, and piston A moves B
and pulley block I with it a distance equal to E in the direction from J to I, which
corresponds to a movement (2 n + 1) É of chain H.
5th. On the annular piston (D - b); Tb, open to pressure; Ta, open to exhaust;
and TD, closed. The pulley block I remains against cylinder K, and piston B
moves A together with the pulley block J a distance equal to E in the direction
from I to J which corresponds to a movement (2 n E) of chain H
6th. On piston A and on annular piston (D - a); TD and Ta open to pressure,
and Tb closed (minimum effect), Figure 8. The piston B and pulley block I
remain stationary, and piston A moves block J a distance equal to E in the direction
from I to J, which corresponds to a movement (2 n E) of the chain H. The exhaust
from the capacities corresponding to D (D-a, D-6) is into a special receiver
provided with an overflow pipe and placed slightly above the cylinder K in order
that the internal volume comprising these 3 areas shall be always filled with water
whatever may be the position of one or of both the pistons.
From the foregoing it will thus be seen that 6 powers may be obtained in the
same machine with the same pressure of water by employing two differential pistons
combined with two movable sockets operated automatically, and with a proportionate
expenditure of water for each power. If, for example, the areas corresponding
to D (D − a) (D - b) have the following relative proportions, viz.: area D = 1,
area (D a) % of area D, area (D - b) = 1/8 of area D, which gives
diameter D 1, diameter a = 0.408 D, diameter 6 = 0·817 D (or b = 2a), and
that E 1 m 50, and n - 3 sheaves in each pulley block.
-
-
The results set out in the following table would be obtained by the several ways
of working above enumerated :-
--
-
-
It will be seen that the different powers of the machine are proportionate to
1000 833.3 666 6500-333-3-166-6, so that in order to raise to the
normal height any load less than that which corresponds to the maximum power
the machine may be worked by the power next higher than that which corresponds
to the load, thereby economising the difference which exists between the maximum
power of the machine and that which it is necessary to employ. The power D -
(Da) should not be less than is required to work the machine unloaded.

page_text: valves, cocks, &c., and I will here describe an arrangement of balanced valve which
answers the conditions required, Figures 9 and 10. For the central capacity whose
diameter is D, AD is a balanced inlet valve; a d, valve rod; TA, triple branch
inlet pipe; ED, balanced exhaust valve; ed, valve rod; TE, triple branch outlet
pipe; TD, pipe to cylinder.
For the annular chamber (D- a) the admission and exhaust valves A a,
Ea, as also their operating gear, are similar to the above. Ta, pipe leading
to (D-a).
For the annular chamber (D-6) the inlet and outlet valves A b, Eb, and their
operating gear, are similar to the above. Tb, pipe to (D-b); N, rock lever for
working valves AD; ED, the ends x, y, of the lever working in slots p. g, on the
upper ends of the valve rods, and acting thereon, except when the lever N is in its
mid position; L, rod for operating rock lever N; S, bearing of same; U, crossbead
guide for piston rods fixed on bearing S; m, n, springs for holding the valves A D,
ED, down in their seats.
Figure 11, DE, face grooved cam for operating lever L mounted on shaft O.
Figure 12, V, connecting rod jointed to rod T and lever L. The rod T, on which
cam DE acts, works in a guide G; H, bearings of shaft O; M, hand wheel for
operating shaft O.
Figure 13, C, dial plate fixed on hand wheel M, the dial being marked with
divisions corresponding to the different powers of the hoisting machine.
In each group A signifies admission full open, and E exhaust full open. When
either of the principal divisions bearing the index of one or other of the powers,
and also bearing the letter F, is brought opposite the fixed pointer Z, all the valves
will be in their seats, where they are retained by the pressure of the fluid. RA,
RE, inlet and outlet safety valve cocks. The shaft O also carries other cams a E,
bE, for operating valves A a, Ea- A b, Eb, in a similar manner to those before
described.
The hoisting apparatus being in the starting position (Figure 2) the division
1=6666 of the dial is brought opposite pointer Z, and when a weight of any kind,
either less or equal to that which corresponds to the maximum power of the machine,
is to be raised, the dial is turned by bringing the principal divisions in succession
in their numerical order opposite the pointer Z until the weight is hoisted, after
which the boisting speed is reduced by bringing a point of the division comprised
between the marks A and F opposite to the pointer Z. When the load is to be
maintained at any height the mark F is brought opposite the pointer Z so as to
close all the valves of the three series, and as the fluid can no longer escape the
pistons remain stationary. When the weight is to be lowered the dial is shifted
until a point more or less near E is brought opposite the pointer Z, so that the rate
of descent of the load shall be suitably regulated.
From the foregoing it will be seen that the entire machine is controlled by the
hand wheel M. When it is necessary to move the dial C from one main division
to another of lower power the safety valve cock RA should be closed to prevent
shocks, which might be caused if the dial only were moved. The areas of the
orifices of the inlet and outlet valves of each group are proportionate to the corre-
sponding volume of water expended, in order that for all the powers employed the
speeds of raising and lowering may be constant.

page_text: Figure 16. This apparatus, which acts by direct outward thrust, has two
principal pistons A B, two auxiliary pistons, CA, DA, and two sliding sockets I, J,
carrying pulley blocks Nos. 1 and 2. The pistons A and B, CA, and A, D A, and B
abut one against the other in their normal position, as shown in the Drawing, and
the rods a, b, of pistons A, B, slide through the rods c, d, of pistons CA, DA,
respectively a distance greater than 2 E. I, socket carrying pulley block No. 1,
sliding freely on end i of cylinder K, and guided by it; J, socket carrying pulley
block No. 2, sliding on and guided by the end j.
a <b<c<d, 12 powers are obtained corresponding to the effective capacities:—

page_text: combined action of the principal apparatus and compensator corresponding to that
of a single apparatus having effective areas varying in each case in proportion to
the total resistance."
When the total resistance is less than the maximum of the motive power
developed by the principal apparatus of single power, there is an excess of power
expended, and consequently a loss of power equal to the difference between
the two.
This excess of power is utilised to actuate a compensator, by which this loss of
power is automatically economised in two different ways, with the exception of a
small fraction absorbed by the working of the compensator.
1st. By automatically restoring this available fraction of power expended in
excess to the energy of the water.
2nd. By rendering this available fraction of power expended in excess auto-
matically equal to zero, whatever may be in each case the value of the total
resistance relatively to the maximum power which the apparatus is capable of
developing. In the first case the compensator returns to the accumulator, or to
the head of water, a volume of water under pressure corresponding to the available
fraction of power expended in excess. In the second case the compensator forces in
to the principal apparatus a volume of water under pressure corresponding to the
available fraction of power expended in excess, so that the volume of water under
pressure which enters the principal apparatus from the source of power corresponds
only to the total resistance to be overcome, including the power which is absorbed
by the compensator. The volume of water actually furnished by the source of
power being equal in each case to the difference between the two volumes of the
principal machine and the compensator, it follows that the combined action of these
two apparatus will be equivalent to that of a single apparatus whose effective area
is automatically variable in proportion to the total resistance.
The automatic division of the power, according to the above principle, may be
carried out in practice in various ways, and I will here give, by way of example,
some of the mechanical arrangements which may be employed.
1st. Figure 20 shows a hoist acting by outward thrust on the pulley block No. 1,
the pulley block No. 2 being fixed and the load attached to the part H of the chain.
The longest possible stroke of the piston of the compensator is considerably less
than that of the piston of the principal apparatus, and the compensating cylinder
is fixed; K P, cylinder of principal apparatus whose plunger AP carries pulley
block No. 1, and whose greatest stroke is EP. The pulley block No. 2 is attached
to the end of cylinder KP; KC, cylinder of compensator; AC, its plunger
operated by rock lever BC oscillating at OC and connected to the plunger AC
by links b, c. The rock lever BC carries two lever arms DC slotted at CC;
PC weights counterbalancing plunger A C and its connections; BP principal rock
lever, which is made double, and oscillates on an axis at OP, and is operated by
plunger AP through the connecting rods b, P, fixed on the axis of the sheaves of
pulley block No. 1 on either side of cylinder K P. Each rock lever BP has an
arm DP slotted at CP; N, joint pin of independent slide blocks NP, NC, placed
in the slots of armis DC, DP, respectively; Q, suspension rod, one end of which is
connected to the adjusting crank M, and the other to axis N. There is a similar
rod on either end of N; p, q, extreme positions of slide blocks NP, NC, in
slots CP, cc; R, worm wheel mounted on crank shaft S; V, endless screw rotated
by hand wheel U; T, pipe supplying water under pressure to cylinder KP of
principal apparatus. This pipe serves to put the two cylinders KP and KC in
communication with each other by the branch pipe t on cylinder KC; X, X, framing
of machine.
2nd. Figure 21 shows a hoisting apparatus on the same principle as shown in
Figure 20. The cylinder of the compensator oscillates, and the longest possible
stroke of its plunger is less than that of the plunger of the principal cylinder.
Similar letters of reference indicate similar parts to those in Figure 20.
KC, cylinder oscillating at o c. The rod of plunger AC is attached to a cross-

page_text: head N having a slide block CN working in a slot CP in each rock lever B P.
Each end of crosshead N carries a suspension rod Q connected to the adjusting
crank M on shaft S. Each crank is moved by a rack rod J and pinion keyed on
a shaft I, upon which is a worm wheel R in gear with endless screw V. Pipes t, n,
from the trunnion of cylinder KC establish constant communication between the
upper part of cylinder KC and cylinder KP, pipe t being connected with the pipe T
supplying water under pressure.
3rd. Figure 22 shows another hoisting apparatus on the same principle as
Figure 20.
The cylinder of compensator is fixed, and the longest possible stroke of its
plunger is equal to that of the principal apparatus. The same letters of reference
indicate the same parts as in Figure 20. The rock lever BC has two side arms DC,
each of which is slotted at CC.
The mode of adjusting the axis or crosshead N which carries the two slides, and
unites the two rock levers, is similar to that in Figure 21. EP, longest stroke of
plunger AP; EC, longest stroke of plunger AC, EC=EP. The cylinder KP
is in constant communication with the upper part of compensator cylinder KC by
the branch pipe t on pipe T. It will be seen that in Figure 20 the plungers A P
and AC move in opposite directions, while in Figures 21 and 22 they move in the
same direction, and that in each Figure the length of stroke of the compensator
plunger is variable according to the position occupied by the axis N of the slide
blocks on the principal rock lever. It will also be seen that if both apparatus be
filled with water immediately the pressure acts in pipe T, it is transmitted to each
plunger, and that the compensator plunger discharges in the course of its stroke
a certain quantity of water into the principal cylinder, so that the volume of water
under pressure which must be supplied by the source of power at a stroke of the
principal plunger corresponding to that of the compensator plunger is equal
to the volume of the principal plunger less that supplied by the plunger of com-
pensator. Thus the power in excess, which would be uselessly expended in the
principal apparatus were it not for the compensator, is restituted every time that
the volume of water under pressure furnished by the compensator corresponds
exactly thereto.
In practice this result cannot be peferctly obtained, as a fraction of the motive
power must overcome in each case the additional resistance due to the compensator.
Let TRV represent the total power absorbed in working the entire machine
unloaded, including the compensator, and TMT the total motive power developed
in a full stroke of the plunger of the principle apparatus without the compensator.
This gives TMT-TRV=TE as the value of the available fraction of power
expended in excess to be compensated when working without a load. This
compensation is effected in each case by so proportioning the piston of the
compensator that the value of the volume of water it can furnish, as compared with
that of the principal plunger, shall be equal to TMT
TE
If the axis N be brought in a line with the centre of oscillation OP of the rock
lever BP the compensator piston will remain stationary, and when N is moved to
the furthest point from said centre allowed by the slot CP (which corresponds to
the position for working the hydraulic apparatus unloaded) the piston of the
compensator moves its full stroke. Now as in the foregoing arrangements the
axis N cannot be brought in a line with the centre OP, the motion of the
compensator plunger cannot be reduced to zero, and this plunger consequently
restitutes a fraction of the power developed by the principal apparatus when the
working corresponds to the maximum of the available useful power. Thus by
calling TEI the compensated power, which corresponds to the smallest volume
supplied by the compensator, and TR M the corresponding resistance due to the
working of the various parts, we get TMT - (TEI + TRM) = TUM for the
maximum of the useful power of the hydraulic apparatus. When the total
resistance is less than TMT the axis N should be placed at a point of the slot CP

page_text: such that the power expended in excess will be restituted by the compensator. In
order to readily attain this result after each time of working, the axis N should be
placed at the furthest point from the centre OP, which corresponds to working
unloaded, proceeding as follows when the hydraulic apparatus is to be again
worked:
-
1st. Place the apparatus in communication with the source of power.
2nd. Bring the axis N gradually nearer the centre OP until the plungers
move.
3rd. Fix the axis N in this position.
4th. Cut off communication between the apparatus and the source of power when
the load is raised to the desired height.
5th. Open the exhaust when it is desired to lower the load or to return the
plungers to their starting position.
6th. Shift the axis N away from centre OP, as above mentioned, when the
plungers have been returned to position.
During their return the water enters and fills the compensator cylinder. The
volume of water supplied from the source of power is discharged into a reservoir
placed a little higher than the apparatus, and remaining in communication there-
with so long as the plungers are in their starting position, in order that both
cylinders may be completely filled with water at the commencement of each
operation. Also to ensure this latter condition of working, water may be directly
introduced under pressure into the compensator through a pipe from the principal
apparatus. When the pressures on the plungers are relatively weak the shifting of
the axis N may be effected as above described, but when these pressures are
considerable the mechanism described in Figures 20 and 21 could not be adjusted
in the way described, and it is consequently necessary to so arrange it that the
shifting of axis N at starting shall not produce any movement of the compensator
piston. This result is obtained by the arrangement shown in Figures 23 and 24,
in which K is a connecting rod attached to the slide block axis N, aud whose
length is equal to the mean radius of slot CP, and is the centre of the arc when
the apparatus is in the starting position, which ensures this point remaining
immovable when the slide block axis N is shifted in slot CP. The same result is
attained in Figure 21.
If the compensator be isolated from the principal apparatus by omitting the
pipe t, Figures 20 to 24, and the compensator be connected with the source of power,
whether an accumulator or a column of water, and also with a special reservoir
when the exhaust takes place from the principal apparatus, the effect above
indicated is realised in each case, viz., the restitution of the available fraction of
power expended in excess to the source of power.
If the hoisting apparatus described are intended to work by a tractive instead
of by a thrusting action the same conditions of automatic working may be realised
in Figures 20 and 23 by employing pistons instead of plungers in each cylinder,
and in Figures 21, 22, 24, by employing a piston instead of a plunger in the
principal cylinder, and a plunger in the compensating cylinder. The piston of
the principal cylinder would in each case start from the upper end of the cylinder,
and the pulley block No. 2 would be fixed above No. 1.
When the hydraulic apparatus has a number of powers, as previously explained
with reference to Figure 2 and the following Figures, a compensator may also be
added for the purpose of automatically dividing each power, it being simply
necessary to so regulate the size of the compensator that the power expended in
excess may be compensated when the bydraulic apparatus is working or loaded
with the maximum available power.

page_text: B, connecting rod working the crank F fixed on the shaft O; V, fly wheel; G, P,
crosshead guides of piston rod A P; g, slide blocks; B P, lever, operated by piston
rod A P. This lever has a long curved slot CP, whose mean radius is equal to
the length of connecting rod E attached at O E, to the lever BC, which is pivoted
The rod of piston
at O C, and by which the compensator piston A. C, is worked.
A C is prolonged on either side at C1 C2 these two parts being of same diameter.
G, C, crosshead guides of piston rod A, C; Q, links for connecting rod E to crank M
on a shaft S; p, q, extreme positions of slide block axis N in slide CP; R, worm
wheel on shaft S; n, worm rotated by a hand wheel U for placing slide block N in
the desired position; L, eccentric for working distributing valve; l, eccentric rod;
J, slide valve; j, valve box; T, supply pipe for water under pressure; R, inlet
valve or cock; E T, exhaust pipe; t1t2 pipes for placing the ends of the main
cylinder in communication with opposite ends of compensator cylinder; X, base
plate. A governor is employed in connection with the water inlet valve to ensure
a uniform rate of speed of piston. A special governor may also be employed for
shifting the slide block N in slide C P to regulate the power developed, and con-
sequently the speed of the pistons. In this Figure both pistons A P and A C
move in the same direction, and the compensation of the power developed in the
main cylinder is effected in the compensator cylinder in a similar manner to that
before described. The area of the compensator cylinder is moreover determined, as
before explained with reference to Figures 20 to 24.
It will be seen by the foregoing that the apparatus described in Figures 20 to 25
inclusive enable the automatic division of hydraulic power to be practically realised
by utilising the principle enunciated.
VARIATION OF THE VOLUME OF WATER EXPENDED UNDER CONSTANT PRESSURE.
The employment of a compensator also permits of obtaining a variable effective
power, either increasing or decreasing at each point of the stroke of the piston of a
hydraulic apparatus by simply shifting the position of slide block N in slot CP
according to a certain law, such that the effective pressures exerted upon the main
piston shall be equal at each point of its stroke to those which are required to be
produced. This mode of working may also be applied with advantage to the
different kinds of presses in which a varying power is required; such, as for
example, those for moulding and pressing bricks, tiles, briquettes, and other materials,
stamping presses, oil presses, hay presses, &c.
It will be understood that all that precedes equally applies, whatever may be the
fraction of the stroke of the main piston which is utilised. This second principle,
which includes the two special divisions previously described, is applicable to all
apparatus utilising the pressure of water in one or more cylinders, or their
equivalents, for producing a useful effect, whatever may be the mode in which the
water power is obtained; such, as for example, hoisting apparatus, hauling apparatus,
different kinds of presses, hydraulic motors, &c.
The two principles of working hydraulic apparatus herein before described permit
of recuperating the power due to the descent of the load, which acts on the piston
by returning the water to the accumulator or head of water. The apparatus which
5 work on the automatic principle more especially enable this result to be obtained
almost completely, whatever may be the load acting on the piston, inasmuch as the
water can be returned at a pressure equal, or even superior, to that of the
accumulator, as will be readily understood.
COMBINATION OF THE TWO PRINCIPLES.
"Variation of the pressure of the accumulator combined with the first mode of
division of the 2nd principle, viz., the division of the hydraulic power into a certain
number of equal or unequal parts."
The union of these two principles permits in certain cases already specified of

page_text: relatively large number of parts, which procures the advantage of overcoming a
resistance by employing a motive power only just above that which exactly corre-
sponds to such resistance, m being the number of differential weights on accumulator,
and n that of the varying powers obtained by means of differential pistons. m x n
is the number of powers which may be obtained theoretically. If m = 7 and
n = 12, m n = 84 powers.
The employment of an accumulator with varying pressures may also be combined
with that of an hydraulic apparatus with automatically varying powers, in order
to obtain a better utilisation of the motive power which actuates the accumulator
when the apparatus in connection with such accumulator are not required to work
at above a certain fraction of the maximum of their available power. These
combinations of the two principles are capable of the same applications as those
indicated above for the second principle.
The maximum motive power actuating an accumulator may be furnished by any
suitable motor operating by the aid of water, steam, air, or gas, and in order to
most perfectly utilise the maximum of this power, it is proposed to divide it into
two or more equal or unequal parts, each composed of an independent motor
working without dead points, and arranged under the most economic conditions
for utilising the power. Such an arrangement permits for a certain fraction of the
available maximum power absorbed during a period of time of certain duration by
the hoisting or other apparatus in connection with an accumulator of working in
the most economical way the motors which correspond to a fraction of the total
power utilised. Other motors less economical in working may be similarly
employed for the purpose as usual.
The supply to the accumulator is in all cases regulated automatically by the
accumulator, whether the motors are stopped or continue working when the
plunger of the accumulator has risen to its highest point. By connecting several
accumulators they may all be supplied on the above principle. This division of the
power is applicable, not only to the apparatus before described, but also to those
at present in use. If, for example, the load on the accumulator be divided
proportionately to 2, 3, 4, 5, 6, 7, 8, the total motive power which corresponds to 8
may be divided into two equal parts.
BALANCING THE PULLEY BLOCKS.
In applying either of the apparatus before described to the raising of weights the
forces acting upon the pulley blocks are not entirely balanced, which causes
transverse strains tending to jam the pistons in their guides. In order to avoid
these objections one of the two following arrangements may be employed :-(1). By
means of guide pulleys the distance between one or more of the portions of the
leading part of the chain and the longitudinal axis passing through the centres of
the sheaves of the two blocks is varied, so as to balance the various forces acting
thereon. Each guide pulley may be either mounted on a fixed point outside or
upon one of the pulley blocks. (2). To one or both of the pulley blocks one or more
auxiliary sheaves are added, mounted upon one or more spindles parallel to those
of the other sheaves. The spindles of these auxiliary sheaves are mounted in the
pulley block, either on the inside or outside of the principal sheaves, and each
auxiliary sheave enables the leading part of the chain to be passed twice on the
same side of the axis of the corresponding principal sheave.
The guide pulleys employed in the first arrangement may also be employed in
connection with these auxiliary sheaves. The number of sheaves in each block
may be varied and the connection above indicated may be applied to one or more
portions of the leading part of the chain.
Figures 26 and 27 of the Drawing show the application of these improvements.
The leading part of the chain H after passing round the fixed guide pulley T passes
round the sheave No. 1, and then round sheave No. 2, and so on to F, where it is
attached to the pulley block No. 1 at a distance E from the centre line 2 - 1 equal

page_text: -
to the radius of one of the principal sheaves. C, traction, 1st upon the running
part Hon raising the load, 2nd upon the standing part F in lowering the load;
R, passive resistances of a sheave, including the resistance due to the lapping round
it; a, additional resistance due to the auxiliary sheave; M, N, fixed guide pulleys;
P,q, movable pulleys mounted on the pulley blocks; A, auxiliary sheave outside
the pulley block; a tangent from this sheave parallel to the axis 2-1 on the
returning side of the chain does not meet the principal sheave. If the auxiliary
sheave be mounted inside the pulley block it will not be met by a tangent to the
principal sheave parallel to the axial line 2-1 on the returning side of the chain.
Figure 26. 1st mode of balancing; number of sheaves, 1 on each pulley block.
1.
Ascent. Pulley block No. 1: C + R above axial line 2
Pulley block No. 2: R above axial line 2-1.
Descent. Pulley block No. 1: C + R above axial line 2 1.
Pulley block No. 2: R beneath axial line 2 - 1.
The pulley block No. 1 is balanced in each case by approaching the standing
part F to such a distance I from the axial line 2-1 that the difference of the
movements of traction of C + 2R may be equal to C+ R, and by guiding the
leading part of the chain parallel to 2 1 by means of fixed guide pulleys M, N.
The pulley block No. 2 is balanced on raising the load by approaching the
portion C+2 R of the leading part of the chain by means of guide pulleys P to
Buch distance from the axial line 2-1, that the difference of the movements
of C+2 R are equal to R. In lowering there remains below the axial line 2 - 1
an unbalanced force 2 R; it is preferable not to balance pulley block No. 2.
Forces
to be
balanced.
-
Figure 27 shows the second mode of balancing; number of sheaves: 2 to each
pulley block.
The sheave 3 is supplemented by an auxiliary sheave A; the leading part of the
chain passes round sheave No. 1, then round Nos. 2 and 3, then around the
auxiliary sheave A, then passes above sheave 3, sheave 4, round which it passes
to point F where its end is attached.
Forces
to be
balanced.
Ascent Pulley block No. 1: C above axis 2
Pulley block No. 2: 0 (zero).
Descent.
-
1.
-
Pulley block No. 1: C+ 4R + a above axis 2 1.
Pulley block No. 2: 0 (zero).
Pulley block No. 1 is balanced by making the leading part act on the centre of
the sheaves in the direction 2 - 1, by means of guide pulley Q on the pulley block
and fixed return pulley T.
The pulley block No. 2 being naturally balanced, it follows that both pulley
blocks are completely balanced both in raising and lowering the load. The guide
pulley may be dispensed with if the radius of the principal sheaves is great
enough to be the diameter of a sheave suitably proportioned, see Figure 28.
The excess of tractive force generally sustained by each pulley block on one side
of the central plane of the tackle perpendicular to the direction of the axes of the
sheaves is balanced by shifting the sheaves at either side or at one side only of the
central plane.

page_text: SPECIFICATION in pursuance of the conditions of the Letters Patent filed by
the said Alexander Melville Clark in the Great Seal Patent Office on the 31st
July 1880.
ALEXANDER MELVILLE CLARK, of 53, Chancery Lane, in the County of
Middlesex, Patent Agent. IMPROVEMENTS IN THE WORKING AND CONSTRUCTION
OF HYDRAULIC MACHINERY." A communication from abroad by Ernest Adolphe
Jouvet, of Paris, France.
This Invention relates to improvements in hydraulic apparatus, and has for its
object to obtain the division of the maximum available motive power into any
number of equal or unequal parts.
In hydraulic apparatus heretofore employed for utilising the energy or motive
power of a head of water, the power expended to overcome a resistance, even when
working unloaded, is generally the maximum available motive power. There is
consequently a considerable loss of power whenever the resistance to be overcome
does not correspond to the maximum of the motive power. The object of the
present Invention is to reduce and oven entirely prevent this loss of power by
the employment of apparatus whereby the division of the maximum of the
motive power is effected according to one or other of the two following general
principles:
-
1st Principle." Expenditure of a constant volume of water and variation of the
pressure of the accumulator."
2nd Principle." Variation of the volume of water expended and maintenance of
the pressure constant."
The motive power may be derived either from an accumulator or from a head
of water, either natural or artificial. By a combination of these two principles the
division of the maximum of the power may be practically effected in as perfect and
economical a manner as can be desired. It should be noted that in cach principle
the course of the principal piston or pistons, or other equivalents employed is a
constant.
APPARATUS EMPLOYED.
1st Principle." Expenditure of a constant volume of water and variation of the
pressure of the accumulator."
The division of the maximum of the available motive power of the water under
pressure is obtained by dividing the total load acting on the plunger of the accu-
imulator into a certain number of equal or unequal parts, and combining these
together so as to put different loads upon the plunger, each corresponding to a
fraction of the maximum of the total pressure, and consequently of the motive
power which each apparatus connected with such accumulator is capable of
developing, so that in each case the apparatus works with an expenditure of the
same volume of water, but at a different pressure to that due to the total load of
the accumulator.
2nd Principle. "Variation of the volume of water expended, the pressure being
maintained constant."
This principle permits of dividing the maximum of the available motive power
of water acting under constant pressure in an apparatus, (1), into a certain
number of equal or unequal parts by the employment of one or more differential
pistons combined with one or more sliding sockets, whereby the variation of the
volume of water under constant pressure expended, and consequently that of the
energy expended, is effected, as hereinafter fully described; (2), automatically
whatever may be the relation between the resistance and the maximum of the

page_text: available power of the apparatus by the employment of a compensator of the power
in excess expended in the principal apparatus. The operation of this compensator
is such, whatever may be the resistence to be overcome, that it is equivalent to the
restitution of the power in excess expended in the principal apparatus to the
energy of the motive water, and consequently the combined action of the two
apparatus corresponds to that of a single apparatus, having an effective area,
varying proportionately to the total resistence. In the first case, in order to
overcome a given resistence the fraction, equal or immediately superior thereto of
the maximum available motive power, is utilised, and the loss of power is therefore
equal only to the difference between the two. In the second case, to a given
resistence equal to or less than the maximum of the available power the energy
expended exactly corresponds, and there is consequently no loss of power.
The following is a description of different arrangements of apparatus embodying the
principles before indicated, reference being had to the accompanying Drawings
First Principle.-" Expenditure of a constant volume of water, and variation of
the pressure of the accumulator."
It has been seen that the variation of the pressure of the accumulator is obtained
by the division of the load acting on its plunger into a certain number of equal or
unequal parts. If the loads be 7 in number and be to one another as
2:3:4:5:6:7 is to 8, which corresponds to the entire load, the value of each
fraction of the total load will be proportionate to the difference of two successive
loads 2, 1, 1, 1, 1, 1, 1. The series of weights composing the total load in the
accumulator may be applied and removed either automatically, or by a mechanical
arrangement, or by hand.
The following is a description of an arrangement of accumulator in which the
mechanism for applying and removing the weights is worked by hand :-
In Figure 1, A is the accumulator; B, the cylinder; P, the plunger; C, C, C,
guide columns fixed in the base plate F, and united at their upper ends to a tie
bar T; D¹, D3, D³, columns upon each of which are collars V, V, V, V, V, V8,
fitting freely thereon, and having lugs upon which the set of weights E³, E³, E³, Eº,
E7, E, are supported at the upper part of the accumulator, when they are not
required to act on plunger P; E2, weight permanently attached to plunger by
means of a frame G. The remaining weights are superposed successively upon
weight E to form the various loads upon the accumulator; H³, H*, H³, Hº, H², H³,
toothed rings gearing with a toothed segment S upon each of the collars V³, V4, V5,
V, V, V8. Each ring gears with the three collars supporting each weight; a³,
vertical shaft by which ring H³ is operated through a pinion p³ on the upper end
of said shaft. At the bottom end of this shaft is a bevel pinion q³ in gear with
a pinion o³ on the crank shaft m³. The remainder of the toothed rings H*, H³,
H4, H7, H8, are similarly operated; R, water inlet pipe to the cylinder of accu-
mulator; U, retaining valve; I, cock for distributing the water to the several
machines operated by the accumulator; q³, q', 95, 96, 97, q³, forks embracing the
guide columns C, C, C, three being provided for each weight; 63, 64, 65, 66, 67, 68,
supports by which each weight rests on the one next below; p, rod of plunger P guided
in cross bar T. The cranks m³, m³, m³, m³, m7, m³, may be all connected together
and operated either mechanically or by hand. To apply the weight Es upon E in
order to obtain a load E² + E3 upon plunger P, plunger P is first raised until
weight E raises Es slightly from the collars V3, and the crank m³ which operates
the ring H³ is then caused to turn the collars V3 a quarter round, whereupon the
load on the accumulator will be E² + E³. To remove weight E³ the operation is
reversed, the weight E³ is first raised until it is slightly above collars V³, and the
crank m³ is then operated to turn said collars a quarter round so as to bring their
Jugs beneath the weight E³, which is then lowered thereupon. The load upon the
accumulator is now only E2. The application and removal of the remaining
weights is performed in a similar manner, whereby 7 different loads may be applied
to the accumulator. This method of weighting the accumulator may be utilised
for working all kinds of hydraulic machinery whatever may be their mode of

page_text: action or the purpose for which they are employed, such as hoists, presses, hauling
machinery, and the like. It is chiefly of advantage in cases where each machine
employed is not required during a certain period of time to furnish more than a
fraction of the motive power it is capable of developing.
Second Principle.-"Variation of the volume of water expended and main-
tenance of the pressure constant."
1st Arrangement. Division of the maximum of the power of water under constant
pressure into a determinate number of equal or unequal parts by the employment
of one or more differential pistons combined or not with one or more movable
sockets operated automatically.
I will proceed to describe by way of example some arrangements of apparatus on
this principle. Figure 2 shows a hoist having six different powers. This apparatus,
which acts on the tackle by direct thrust, comprises two differential pistons A, B,
and two movable sockets I, J, the parts being represented in the position of rest;
K, fixed cylinder; A, piston whose diameter is D and the diameter of whose rod
is a; B, piston whose diameter is also D and the diameter of whose rod is ba<b;
I, movable socket with which is combined the pulley block No. 1, said socket being
fitted to slide freely upon the end i of cylinder K, and also on the end of piston
rod B; J, movable socket carrying pulley block No. 2, and sliding freely on the
end of cylinder K, and also on the end of piston rod a; R', R³, R³, sheaves
mounted on pulley block No. 1; R2, R*, Rº, sheaves mounted on pulley block No. 2.
The chain G is attached at g to the pulley block No. 1, and thence passes round
the several pulleys, of which there may be any number n in each block; N, guide
pulley mounted on the fixed support t; H, chain; E, maximum stroke of a piston in
either direction; TD, water inlet between pistons A and B; Ta, water inlet
to the annular portion whose diameter is D-a; Tb, water inlet to the annular
portion, whose diameter is D-b; 0, 0, packing of piston A; V, V, packing of
piston B; p, packing in socket J; q, packing in socket I. The water under pressure
may be admitted to act,-
(1st.) Between the pistons A and B whose diameter is D (maximum effect).
TD, open to pressure, Ta, Tb, open to exhaust.
The two pistons, and with them the two sockets I, J, are thus caused to move
apart (see Figure 3) a distance equal to E or half E for each socket on either side
of the line X, Y; the motion of the chain H (2n +) E:
(2nd.) Upon the annular piston D
a.
-
Ta, open to pressure, T b, open to exhaust, TD, closed.
The pulley block J in this case remains against cylinder K, as in Figure 4, and
piston A carries B, together with its pulley block I along with it, a distance
equal to E in the direction from J to I, which corresponds to a movement (2n+1) E
of the chain H.
(3rd.) Upon piston B and upon the annular piston D - b.
Td and Tb open to pressure, and Ta closed (Figure 5).
The piston A and pulley block J remain stationary while piston B moves
pulley block I a distance equal to E in the direction of J to I producing a
movement (2n+1) E of the chain H.
(4th.) On the annular pistons D-a, D - b.
Ta and Tb open to pressure, Td closed, Figure 6.
The pulley block J remains stationary upon cylinder K, and piston A moves B
and pulley block I with it a distance equal to E in the direction from J to I, which
corresponds to a movement (2n + 1) E of chain H.
(5th.) On the annular piston (D b).
-
Tb open to pressure, Ta open to exhaust, and TD closed.
The pulley block I remains against cylinder K, and piston B moves A
together with the pulley block J a distance equal to E in the direction from I to J,
which corresponds to a movement (2n E) of chain H.
(6th.) On piston A and on annular piston (D - a).
TD and Ta open to pressure, and Tb closed (minimum effect), Figure 8.

page_text: The piston B and pulley block. I remain stationary, and piston A moves block J
a distance equal to E in the direction from I to J, which corresponds to a
movement (2n E) of the chain H. The exhaust from the capacities corresponding
to D (Da, D- b) is into a special receiver provided with an overflow pipe and
placed slightly above the cylinder K in order that the internal volume comprising
these three areas shall be always filled with water whatever may be the position of
one or of both the pistons.
From the foregoing it will thus be seen that six powers may be obtained in the
same machine with the same pressure of water by employing two differential
pistons combined with two movable sockets operated automatically and with a
proportionate expenditure of water for each power. If, for example, the areas
corresponding to D (D − a) (D — 6) have the following relative proportions, viz.:
area D =1, area (D − a) =/eths of area D, area (D-6)=1/3rd of area D, which
gives diameter D= 1, diameter a = 0.408 D, diameter b = 0.817 D (or b
that E =1m 50; n = 3 sheaves in each pulley block.
-
-
-
=
2 a) and
The following table sets out the results obtained by the several ways of working
the above enumerated.
It will be seen that the different powers of the machine are proportionate
to 1000833.3 - 666 6-500-3333-1666, so that in order to raise to the
normal height any load less than that which corresponds to the maximum power
the machine may be worked by the power next higher than that which corresponds
to the load, thereby economising the difference which exists between the maximum
power of the machine and that which it is necessary to employ. The power
D (Da) should not be less than is required to work the machine unloaded.
-
DISTRIBUTING APPARATUS.
The distribution of water in each of the capacities corresponding to D, D-a, D-b
may be effected in any suitable manner, either by means of slide or any other
valves, cocks, &c., and I will here describe an arrangement of balanced valve which
answers the conditions required (Figures 9 and 10).
For the central capacity whose diameter is D, AD is a balanced inlet valve;
ad, valve rod; TA, triple branch inlet pipe; ED, balanced exbaust valve;
ed, valve rod; TE, triple branch outlet pipe; TD, pipe to cylinder.
For the annular chamber (D-a), the admission and exhaust valves A a, Ea,
as also their operating gear, are similar to the above. Ta, pipe leading to (D-a).
For the annular chamber (D-b) the inlet and outlet valves Ab, E b, and their
operating gear are similar to the above. Tb, pipe to D-b; N, rock lever for
working valves AD, ED, the ends x, y, of the lever working in slots p, q, on the
upper ends of the valve rods, and acting thereon except when the lever N is in
its mid position; L, rod for operating rock lever N; S, bearing of same; U, cross
head guide for piston rods fixed on bearing S; m, n, springs for holding the valves
A D, ED, down in their seats.
Figure 11. DE, face grooved cam for operating lever L' mounted on shaft O.
Figure 12. V, connecting rod jointed to rod T and lever L. The rod T on which

page_text: cam DE acts works in a guide G; H, bearings of shaft O; M, hand wheel for
operating shaft O.
Figure 13. C, dial plate fixed on hand wheel M, the dial being marked with
divisions corresponding to the different powers of the hoisting machine. In each
group A signifies admission full open, and E exhaust full open. When either of
the principal divisions bearing the index of one or other of the powers, and also
bearing the letter F, is brought opposite the fixed pointer Z all the valves will be
in their seats, where they are retained by the pressure of the fluid.
RA, RE, inlet and outlet safety valve cocks. The shaft O also carries other
cams a E, 6 E, for operating valves A a, Ea-Ab, Eb, in a similar manner to those
before described.
The hoisting apparatus being in the starting position (Figure 2) the division
1=1666 of the dial is brought opposite pointer Z, and when a weight of any kind,
either less or equal to that which corresponds to the maximum power of the
machine, is to be raised, the dial C is turned by bringing the principal divisions in
succession in their numerical order opposite the pointer Z until the weight is
hoisted, after which the hoisting speed is reduced by bringing a point of the
division comprised between the marks A and F opposite to the pointer Z. When
the load is to be maintained at any height the mark F is brought opposite the
pointer Z, so as to close all the valves of the three series, and as the fluid can no
longer escape the pistons remain stationary. When the weight is to be lowered
the dial is shifted until a point more or less near E is brought opposite the pointer
Z, so that the rate of descent of the load shall be suitably regulated.
From the foregoing it will be seen that the entire machine is controlled by the
hand wheel M. When it is necessary to move the dial C from one main division
to another, indicating a lower power, the safety valve cock RA should be closed to
prevent shocks, which might be caused if the dial only were moved. The areas of
the orifices of the inlet and outlet valves of each group are proportionate to the
corresponding volume of water expended in order that for all the powers employed
the speeds of raising and lowering may be constant.
(2). HOIST HAVING THREE DIFFERENT POWERS.
Figure 14. This apparatus, which acts by direct traction on the tackle, has two
differential pistons, a main piston B and an auxiliary piston DA. The rod t of
piston B has attached to it a pulley block M 1, No. 1; the pulley block No. 2 is
attached to a fixed point. The rod 6 passes through the rod d of piston DA, and
terminates in a head n, by which DA is returned to its starting point, which is
determined by the head m on rod d abutting against the guide of cylinder K.
E, piston stroke, t <b<d. The three powers obtained correspond to the areas of
the effective capacities:-

page_text: abut one on the other in their normal position. The rod of piston B slides within
the rod d of piston DA a distance exceeding the stroke E. The powers obtained
correspond to the effective capacities:—
D
T
T
2.
n 21
n
Figure 16. This apparatus, which acts by direct outward thrust, has two
principal pistons A B, two auxiliary pistons CA, DA, and two sliding sockets I J
carrying pulley blocks Nos. 1 and 2. The pistons A and B, C A. and A, DA and B
abut one against the other in their normal position, as shown in the Drawing, and
the rods a, b, of pistons A, B, slide through the rods c, d, of pistons CA, DA,
respectively a distance greater than 2 E.
I, socket carrying pulley block No. 1 sliding freely on end i of cylinder K and
guided by it; J, socket carrying pulley block No. 2 sliding on and guided by the
end j.
a b c d
12 powers are obtained corresponding to the effective capacities :-
-
A greater or lesser number of powers than those above indicated may be
obtained either by modifying the number of parts employed or by separating the
pistons a distance equal to the length of stroke. The variation of volume may
also be obtained by varying the diameter of the cylinder at the part where any
one piston acts independently of the variation produced by the differing diameters
of the piston rods, as shown in Figure 17. The distribution of fluid in the above
apparatus is effected in a similar manner to that described in the case of six powers,
whatever may be the purpose to which the apparatus is applied.
Each apparatus is provided with a governor for controlling the speed of the
pistons in case the inlet or outlet valves are too wide open.
The governor may be arranged in any suitable manner, and is operated by a
friction roller or other means, to which motion is imparted by a piston or a part
operated thereby. The governor is connected by a suitable arrangement of rods
and levers to two valve cocks, one, RA, placed upon the main supply pipe in the
valve box, and the other, RE, upon the main outlet pipe. Each valve cock is
closed more or less entirely by the governor when the normal speed of the pistons
is exceeded, and when the speed is reduced to its normal rate the valve cock before
operated is again opened by the governor. These valve cocks or others similar to
them are automatically operated to limit the stroke of the pistons. This automatic
□ 9

page_text: arrangement may either be applied to the piston or pistons, as is generally the case
in apparatus acting by direct traction or thrust now in use, or in the case of a
hoist at any suitable point of the tackle. In hoists acting by direct traction or
thrust I may, in order to reduce the length of the machine, place several sheaves
upon each pulley block, and attach the chain to one of the movable pulley blocks
of an auxiliary tackle, whose other pulley block is fixed, the load being hoisted by
the chain of said auxiliary tackle. This latter may be placed in any suitable
position, and may have any number of sheaves desired.
av auy
LACKIC
10 TOISE Song by u
thrust I may, in order to reduce the length of the machine, place several sheaves
upon each pulley block, and attach the chain to one of the movable pulley blocks
of an auxiliary tackle, whose other pulley block is fixed, the load being hoisted by
the chain of said auxiliary tackle. This latter may be placed in any suitable
position, and may have any number of sheaves desired.
(5.) HYDRAULIC MOTORS.
Figure 18 shows a pair of engines having three powers and each of the piston
rods acting by traction. The Drawing represents the pistons working at the
maximum power. Tt, open to pressure; Tb, open to exhaust; Td, closed.
Figure 19 shows a pair of engines having four powers, each piston rod acting by
outward thrust. The Drawing represents the working of the pistons corresponding
to the power (D-b); Tb, open to pressure; T d, open to exhaust; TD, closed.
In both engines the pistons are single acting; O, crank shaft; E, piston stroke.
The distribution of the water may be effected by any suitable arrangement, and
the one indicated in the Drawing by way of example gives good results. This
consists of a special slide valve T for each cylinder operated by a cam CT on a
shaft OT. This shaft upon which all the cams for operating the slide valves are
mounted is driven by an eccentric ET, operating through a rod on a lever L loose
on the shaft OT.
The lever acts on the shaft when it is fixed on a disc I indicating the different
powers and mounted on said shaft. When the power requires varying the
corresponding portion of the disc is brought opposite the lever which operates the
cam shaft, and the two are then fixed together Cocks or valves balanced or of
other kind controlled in the manner described may also be employed. The
cams CT for working the slide valves of each cylinder are similar to those
previously described for the six power hoist; the disc I which indicates the power
also resembles the dial indicator C of the said apparatus. One or two sliding
sockets may also be combined with the differential pistons for obtaining a greater
number of powers than is obtainable with those above described.
2nd Principle." Variation of the volume of water expended and maintenance
of the pressure constant."
Second Arrangement. "Automatic division of the maximum of the motive
power of the water under pressure whatever may be the proportion of the resistance
to the maximum available power of the apparatus by the employment of a com-
pensator of the power in excess expended in the principal main apparatus, the
combined action of the principal apparatus and compensator corresponding to that
of a single apparatus having effective areas varying in each case in proportion to
the total resistance."
When the total resistance is less than the maximum of the motive power
developed by the principal apparatus of single power, there is an excess of power
expended, and consequently a loss of power equal to the difference between the
two. This excess of power is utilised to actuate a compensator, by which this loss
of power is automatically economised in two different ways with the exception of
a small fraction absorbed by the working of the compensator. (1). By auto-
matically restoring this available fraction of power expended in excess to the
energy of the water. (2). By rendering this available fraction of power expended
in excess automatically equal to zero, whatever may be in each case the value of
the total resistance relatively to the maximum power which the apparatus is
capable of developing. In the first case the compensator returns to the accumulator
or to the head of water a volume of water under pressure corresponding to the
available fraction of power expended in excess. In the second case the com-
pensator forces in to the principal apparatus a volume of water under pressure

page_text: corresponding to the available fraction of power expended in excess, so that the
volume of water under pressure which enters the principal apparatus from the
source of
power corresponds only to the total resistance to be overcome, including
that due to the compensator. The volume of water actually furnished by the
source of power, being equal in each case to the difference between the two volumes
of the principal machine and the compensator, it follows that the combined action
of these two apparatus will be equivalent to that of a single apparatus, whose
effective area is automatically variable in proportion to the total resistance.
The automatic division of the power according to the above principle may be
carried out in practice in various ways, and I will here give by way of example
some of the mechanical arrangements which may be employed.
The
(1.) Figure 20 shows a hoist acting by outward thrust on the pulley block No. 1,
the pulley block No. 2 being fixed, and the load attached to the part H of the chain.
The longest possible stroke of the piston of the compensator is considerably less than
that of the piston of the principal apparatus and the compensating cylinder is fixed.
KP cylinder of principal apparatus whose plunger A P carries pulley block No. 1,
and whose greatest stroke is E P. The pulley block No. 2 is attached to the end of
cylinder KP, KC, cylinder of compensator; AC, its plunger, operated by rock
lever BC, oscillating at OC, and connected to the plunger AC by links bc.
rock lever BC carries two lever arms DC, slotted at CC. PC, weights counter-
balancing plunger AC and its connections. BP, principal rock lever which is made
double, and oscillates on an axis OP, and is operated by plunger A P, through the
connecting rods 6 P, fixed on the axis of the sheaves of pulley block No. 1 on either
side of cylinder KP. Each rock lever BP has an arm DP, slotted at CP; N, joint
pin of independent slide blocks NP, NC, placed in the slots of arms DC, DP,
respectively. Q, suspension rod, one end of which is connected to the adjusting
crank M, and the other to axis N. There is a similar rod on either end of N;
pq, extreme positions of slide blocks NP, NC, in slots CP, cc; R, worm wheel
mounted on crank shaft S; V, endless screw rotated by hand wheel U; T, pipe
supplying water under pressure to cylinder KP of principal apparatus; this pipe
serves to put the two cylinders KP and KC in communication with each other by
the branch pipe t on cylinder KC; XX, framing of machine.
(2.) Figure 21 shows a hoisting apparatus on the same principle as that shown
in Figure 20. The cylinder of the compensator oscillates, and the longest possible
stroke of its plunger is less than that of the plunger of the principal cylinder.
Similar letters of reference indicate similar parts to those in Figure 20; KC, cylinder
oscillating at o c. The rod of plunger AC is attached to a cross-head N, having a
slide block CN, working in a slot CP, in each rock lever BP. Each end of cross-
head N carries a suspension rod Q, connected to the adjusting crank M, on shaft S.
Each crank is moved by a rack rod J and pinion keyed on a shaft I, upon which is
a worm wheel R in gear with endless screw V. Pipes tn, from the trunnion of
cylinder KC, establish constant communication between the upper part of
cylinder KC, and cylinder KP; pipe t being connected with the pipe T supplying
water under pressure.
(3.) Figure 22 shows another hoisting apparatus on the same principle as
Figure 20. The cylinder of compensator is fixed, and the longest possible stroke of
its plunger is equal to that of the principal apparatus. The same letters of reference
indicate the same parts as in Figure 20. The rock lever BC has two side arms DC,
each of which is slotted at CC. The mode of adjusting the axis or crosshead N,
which carries the two slides, and unites the two rock levers, is similar to that in
Figure 21; EP, longest stroke of plunger; A P, EC, longest stroke of plunger A. C,
EC EP. The cylinder K P is in constant communication with the upper part of
compensator cylinder KC, by the branch pipe t on pipe T. It will be seen that in
Figure 20 the plungers AP and AC move in opposite directions, while in Figures
21 and 22, they move in the same direction, and that in each Figure the length of
stroke of the compensator plunger is variable according to the position occupied by
the axis N of the slide blocks on the principal rock lever. It will also be seen that

page_text: if both apparatus be filled with water, immediately the pressure acts in pipe T, it is
transmitted to each plunger, and that the compensator plunger discharges in the
course of its stroke a certain quantity of water into the principal cylinder, so that
the volume of water under pressure, which must be supplied by the source of power
at a stroke of the principal plunger corresponding to that of the compensator plunger
is equal to the volume of the principal plunger, less that supplied by the plunger of
compensator. Thus the power in excess, which would be uselessly expended in the
principal apparatus, were it not for the compensator is restituted every time that
the volume of water under pressure furnished by the compensator corresponds
exactly thereto.
TE
TMT.
In practice this result cannot be perfectly obtained, as a fraction of the motive
power must overcome in each case the additional resistance due to the compensator.
Let TRV represent the total power absorbed in working the centre machine
unloaded, including the compensator, and TM T, the total motive power developed
in a full stroke of the plunger of the principal apparatus without the compensator.
This gives TMT-TRV=TE, as the value of the available fraction of power
expended in excess, to be compensated when working without a load. This
compensation is effected in each case by so proportioning the piston of the com-
pensator, that the value of the volume of water it can furnish as compared with that
of the principal plunger shall be equal to If the axis N be brought in a
line with the centre of oscillation OP of the rock lever, BP, the compensator
piston will remain stationary, and when N is moved to the furthest point from said
centre allowed by the slot CP (which corresponds to the position for working the
hydraulic apparatus unloaded) the piston of the compensator moves its full stroke.
Now as in the foregoing arrangements, the axis N cannot be brought in a line with
the centre OP, the motion of the compensator plunger cannot be reduced to zero,
and this plunger consequently restitutes a fraction of the power developed by the
principal apparatus when the working corresponds to the maximum of the available
useful power. Thus by calling TEI the compensated power which corresponds to
the smallest volume supplied by the compensator, and TR M, the corresponding
resistance due to the working of the various parts, we get TMT-(TEI+TRM):
TUM, for the maximum of the useful power of the hydraulic apparatus. When
the total resistance is less than TM T, the axis N should be placed at a point of
the slot CP, such that the power expended in excess will be restituted by the
compensator. In order to readily attain this result after each time of working, the
axis N should be placed at the furthest point from the centre OP, which corresponds
to working unloaded, proceeding as follows when the hydraulic apparatus is to be
again worked :-
-
1st. Place the apparatus in communication with the source of power.
I
2nd. Bring the axis N gradually nearer the centre OP, until the plungers
move.
3rd. Fix the axis N in this position.
4th. Cut off communication between the apparatus and the source of power when
the load is raised to the desired beight.
5th. Open the exhaust when it is desired to lower the load or to return the
plungers to their starting position.
6th. Shift the axis N away from centre OP, as above mentioned, when the
plungers have been returned to position.
During their return, the water enters and fills the compensator cylinder. The
volume of water supplied from the source of power is discharged into a reservoir
placed a little higher than the apparatus, and remaining in communication there-
with so long as the plungers are in their starting position, in order that both cylinders
may be completely filled with water at the commencement of each operation. Also
to ensure this latter condition of working water may be directly introduced under
pressure into the compensator through a pipe from the principal apparatus. When
the pressures on the plungers are relatively weak the shifting of the axis N may

page_text: be effected as above described, but when these pressures are considerable the
mechanism described in Figures 20 and 22 could not be adjusted in the way
described, and it is consequently necessary to so arrange it that the shifting of
axis N at starting shall not produce any movement of the compensator piston.
This result is obtained by the arrangement shown in Figures 23 and 24, in which
K is a connecting rod attached to the slide block axis N, and whose length is
equal to the mean radius of slot CP, and L is the centre of the arc when the
apparatus is in the starting position, which ensures this point remaining immovable
when the slide block axis N is shifted in slot CP. The same result is attained in
Figure 21.
If the compensator be isolated from the principal apparatus by
omitting the pipe t, Figures 20 to 24, and the compensator be connected with the
source of power, whether an accumulator or a column of water, and also with a
special reservoir when the exhaust takes place from the principal apparatus, the
effect above indicated is realised in each case, viz., the restitution of the available
fraction of power expended in excess to the source of power.
If the hoisting
apparatus described are intended to work by a tractive instead of by a thrusting
action the same conditions of automatic working may be realised in Figures 20 and
23 by employing pistons instead of plungers in each cylinder, and in Figures 21,
22, 24, by employing a piston instead of a plunger in the principal cylinder, and a
plunger in the compensating cylinder. The piston of the principal cylinder would
in each case start from the upper end of the cylinder, and the pulley block No. 2
would be fixed above No. 1.
When the hydraulic apparatus has a number of powers, as previously explained
with reference to Figure 2 and the following Figures, a compensator may also be
added for the purpose of automatically dividing each power, it being simply neces-
sary to so regulate the size of the compensator that the power expended in excess
may be compensated when the hydraulic apparatus is working unloaded with the
maximum available power.
(4.) HYDRAULIC MOTOR WITH AUTOMATICALLY VARYING POWERS.
Figure 25.
KP principal cylinder, and AP its piston, the rod of which is
prolonged at either side at P1, P2, the diameters of these two parts being equal;
D, connecting rod working the crank F fixed on the shaft O; V, fly wheel; GP,
crosshead guides of piston rod AP; g, slide blocks; BP, lever operated by piston
rod A P. This lever has a long curved slot CP whose mean radius is equal to the
length of connecting rod E attached at OE to the lever BC, which is pivoted at
OC, and by which the compensator piston A. C is worked. The rod of piston AC
is prolonged on either side at C1, C2, these two parts being of same diameter; GC,
crosshead guides of piston rod AC; Q, links for connecting rod E to crank M on
a shaft S; pq, extreme positions of slide block axis N in slide CP; R, worm wheel
on shaft S; n, worm rotated by a hand wheel U for placing slide block N in the
desired position; L, eccentric for working distributing valve; 1, eccentric rod; J,
slide valve; j, valve box; T, supply pipe for water under pressure; R, inlet valve
or cock; ET, exhaust pipe; t¹, t, pipes for placing the ends of the main cylinder
in communication with opposite ends of compensator cylinder; X, base plate. A
governor is employed in connection with the water inlet valve to ensure a uniform
rate of speed of piston. A special governor may also be employed for shifting the
slide block N in slide CP to regulate the power developed, and consequently the
speed of the pistons. In this Figure both pistons AP and AC move in the same
direction, and the compensation of the power developed in the main cylinder is
effected in the compensator cylinder in a similar manner to that before described.
The area of the compensator cylinder is moreover determined, as before explained,
with reference to Figures 20 to 24.
It will be seen by the foregoing that the apparatus described in Figures 20 to
25 inclusive enable the automatic division of hydraulic power to be practically
realised by utilising the principle enunciated.

page_text: VARIATION OF THE VOLUME OF WATER EXPENDED UNDER CONSTANT PRESSURE.
The employment of a compensator also permits of obtaining a variable effective
power either increasing or decreasing at each point of the stroke of the piston of a
hydraulic apparatus by simply shifting the position of slide block N in slot CP,
according to a certain law, such that the effective pressures exerted upon the
main piston shall be equal at each point of its stroke to those which are required
to be produced. This mode of working may also be applied with advantage to the
different kinds of presses in which a varying power is required, such as, for example,
those for moulding and pressing bricks, tiles, briquettes, and other materials;
stamping presses, oil presses, hay presses, &c.
It will be understood that all that precedes equally applies, whatever may be
the fraction of the stroke of the main piston which is utilised. This second prin-
ciple, which includes the two special divisions previously described, is applicable to
all apparatus utilising the pressure of water in one or more cylinders, or their
equivalents, for producing a useful effect, whatever may be the mode in which the
water power is obtained, such as, for example, hoisting apparatus, hauling apparatus,
different kinds of presses, hydraulic motors, &c.
The two principles of working hydraulic apparatus herein before described permit
of reciprocating the power due to the descent of the load which acts on the piston
by returning the water to the accumulator or head of water; the apparatus, which
work on the automatic principle more especially enable this result to be obtained
almost completely, whatever may be the load acting on the piston, inasmuch as the
water can be returned at a pressure equal, or even superior, to that of the accumu-
lator, as will be readily understood.
"Variation of the pressure of the accumulator, combined with the first mode of
division of the second principle, viz., the division of the hydraulic power into a
certain number of equal or unequal parts."
The union of these two principles permits in certain cases, already specified of
dividing the maximum power of the hoisting or other hydraulic apparatus into a
relatively large number of parts, which procures the advantage of overcoming
a resistance by employing a motive power only just above that which exactly
corresponds to such resistance, m being the number of differential weights on
accumulator, and n that of the varying powers obtained by means of differential
pistons; m x n is the number of powers which may be obtained theoretically.
If m 7 and n = 12, m, n, = 84 powers.
The employment of an accumulator with varying pressures may also be combined
with that of an hydraulic apparatus with automatically varying powers in order
to obtain a better utilisation of the motive power which actuates the accumulator
when the apparatus in connection with such accumulator are not required to work
at above a certain fraction of the maximum of their available power. These
combinations of the two principles are capable of the same applications as those
indicated above for the second principle.
The maximum motive power actuating an accumulator may be furnished by any
suitable motor operating by the aid of water, steam, air, or gas, and in order to
most perfectly utilise the maximum of this power it is proposed to divide it into
two or more equal or unequal parts, each composed of an independent motor
working without dead points and arranged under the most economic conditions for
utilizing the power. Such an arrangement permits for a certain fraction of the
available maximum power absorbed during a period of time, of certain duration by
the hoisting or other apparatus in connection with an accumulator of working in
the most economical way the motors which correspond to a fraction of the total

page_text: The supply to the accumulator is in all cases regulated automatically by the
accumulator itself, whether the motors are stopped or continue working when the
plunger of the accumulator has risen to its highest point. By connecting several
accumulators they may all be supplied on the above principle. This division of
the power is applicable not only to the apparatus before described but also to those
at present in use. If, for example, the load on the accumulator be divided
proportionately to 2, 3, 4, 5, 6, 7, 8, the total motive power which corresponds
to 8 may be divided into two equal parts.
BALANCING THE TACKLE
In applying either of the apparatus before described to the raising of weights
the forces acting upon the pulley blocks are not entirely balanced, which causes
transverse strains tending to jam the plungers in their guides. In order to avoid
these objections one of the two following arrangements may be employed :-(1.) By
means of guide pulleys the distance between one or more of the portions of the
leading part of the chain and the longitudinal axis passing through the centres of
the sheaves of the two blocks is varied so as to balance the various forces acting
thereon. Each guide pulley may be either mounted on a fixed point outside of or
upon one of the pulley blocks. (2.) To one or both of the pulley blocks one
or more auxiliary sheaves are added, mounted upon one or more spindles parallel
to those of the other sheaves. The spindles of these auxiliary sheaves are mounted
in the pulley block, either on the inside or outside of the principal sheaves, and
each auxiliary sheave enables the leading part of the chain to be passed twice on
the same side of the axis of the corresponding principal sheave.
The guide pulleys employed in the first arrangement may also be employed in
connection with these auxiliary sheaves. The number of sheaves in each block
may be varied, and the correction above indicated may be applied to one or more
portions of the leading part of the chain.
Figures 26 and 27 of the Drawing show the application of these improvements.
The leading part of the chain H after passing round the fixed guide pulley T passes
round the sheave No. 1, and then round sheave No. 2, and so on to F, where it is
attached to the pulley block No. 1 at a distance E from the centre line 2-1 equal
to the radius of one of the principal sheaves. C, traction, 1st, upon the running
part H on raising the load; 2nd, upon the standing part F in lowering the load;
R, passive resistance of a sheave, including the resistance due to the chain lapping
round it; a, additional resistance due to the auxiliary sheave; M, N, fixed guide
pulleys; P, q, movable pulleys mounted on the pulley blocks; A, auxiliary sheave
outside the pulley block; a tangent from this sheave parallel to the axis 2-1 on
the returning side of the chain does not meet the principal sheave. If the auxiliary
sheave be mounted inside the pulley block it will not be met by a tangent to the
principal sheave parallel to the axial line 2-1 on the returning side of the chain.
Figure 26.
1st mode of balancing. Number of sheaves, 1 on each pulley
block.
Forces
to be
balanced.
Ascent. Pulley block No. 1: C + R above axial line 2-1.
Pulley block No. 2: R above axial line 2-1.
Pulley block No. 1: C + R above axial line 2-1.
Pulley block No. 2: R beneath axial line 2-1.
Descent.
The pulley block No. 1 is balanced in each case by approaching the standing
part F to such a distance I from the axial line 2-1 that the difference of the
moments of traction of C + 2R may be equal to C + R, and by guiding the leading
part of the chain parallel to 2 1 by means of fixed guide pulleys M, N.
The pulley block No. 2 is balanced on raising the load by approaching the
portion C+2 R of the leading part of the chain by means of guide pulley P to
such distance from the axial line 2-1, that the difference of the moments of

page_text: C+2R are equal to R. In lowering, there remains below the axial line 2-1 an
unbalanced force 2 R. It is preferable not to balance pulley block No. 2.
Figure 27 shows the second mode of balancing.
pulley block.
Number of sheaves, 2 to each
The sheave 3 is supplemented by an auxiliary sheave A, the leading part of the
chain passes round sheave No. 1, then round Nos. 2 and 3, then around the
auxiliary sheave A, then passes above sheave 3 to sheave 4, round which it passes
to point F, where its end is attached.
Forces
to be
balanced.
Ascent.
-
Pulley block No. 1: C above axis 2-1.
Pulley block No. 2: 0 (zero).
Descent. Pulley block No. 1: C + 4R + a above axis 2-1.
Pulley block No. 2: 0 (zero).
Pulley block No. 1 is balanced by making the leading part act on the centre of
'the sheaves in the direction 2-1 by means of guide pulley Q on the pulley block
and fixed return pulley T.
The pulley block No. 2 being naturally balanced, it follows that both pulley
blocks are completely balanced both in raising and lowering the load. The guide
pulley may be dispensed with if the radius of the principal sheaves is great
enough to be the diameter of a sheave suitably proportioned, see Figure 28.
The excess of tractive force generally sustained by each pulley block on one side 2
of the central plane of the tackle perpendicular to the direction of the axes of the
sheaves, is balanced by shifting the sheaves at either side, or at one side only, of
the central plane.
Having described the nature of the said Invention and the manner of performing
the same, I declare that what I claim as my Invention to be protected by the 2
herein before in part recited Letters Patent is,―
1st. The employment of an accumulator having a variable load, and the obtaining
thereby the division of the maximum power of each machine operated by such
accumulator into a given number of equal or unequal parts by the expenditure
of a constant volume of water under variable initial pressure, substantially as 3
herein specified.
2nd. The employment in the cylinder of a hydraulic apparatus acting by direct
traction or outward thrust of differential pistons in combination, or not, with
automatically movable sockets, and the obtaining thereby the division of the
maximum of the available power of the said apparatus in a given number of equal 3
or unequal parts by modifying the volume of water expended under constant
pressure, substantially as herein specified.
3rd. The employment in combination with a hydraulic apparatus of a com-
pensator of the power in excess which would be uselessly expended in the principal
apparatus, and the obtaining, by means thereof, the automatic division of the 4
maximum of the available power by automatically modifying the volume of
water expended under constant pressure, substantially as herein specified.
4th. The combination of a variably loaded accumulator with one or more
hydraulic apparatus, each composed of a cylinder containing one or more differential
pistons in combination, or not, with one or more movable sockets, the combination 4
having for object, 1st, to obtain the division of the maximum of the available
power into a relatively large number of equal or unequal parts; 2nd, to obtain a
better utilization of the motive power which actuates the accumulator, substantially
as herein specified.
5th. The combination, as herein specified, of a variably loaded accumulator with 5
one or more hydraulic apparatus, compensated, as herein described, for the purpose
of obtaining a better utilization of the power which actuates the accumulator.
6th. The division of the total motive power which actuates an accumulator into
a number of equal or unequal parts for the purpose of obtaining a better practical
utilization of the power required for working the accumulator, whether all the 5
apparatus actuated by it do not work at the maximum available power, or
whether some only of these apparatus are utilized, as herein described.

page_text: 7th. The employment in hydraulic apparatus acting by traction or by direct
outward thrust of tackle on which the strain wholly or partly balanced either
by means of fixed or movable guide pulleys acting on one or more parts of the
tackle, in combination or not with anxiliary sheaves fixed on the pulley blocks,
the whole having for object to ensure the proper working of the pistons and piston
rods of the apparatus as herein described.
8th. The employment in hydraulic apparatus of an apparatus for distributing
the water by means of valves or slide valves balanced or not, such as that described,
whereby by the automatic action of a single controlling lever to effect in ordinary
working the distribution of the liquid in each of the chambers in use of the apparatus
above described, to obtain any one of the powers which the apparatus is capable of
developing.
9th. The employment in hydraulic apparatus of a regulator of the speed of the
piston or pistons, operating as herein specified.
10th. The application to all hydraulic apparatus in which water pressure acts
in a cylinder or analogous chamber, of the two general principles specified, whereby
to obtain the division of hydraulic power according to the various methods
herein described, and the arrangements and mechanism for ensuring their proper
working.
In witness whereof, I, the said Alexander Melville Clark, have hereunto set
my hand and scal, this Thirty first day of July, in the year of our Lord
One thousand eight hundred and eighty.
A. M. CLARK. (LS.)