Improvements in Hydraulic Compensating Pumps and Engines, and in Devices for Regulating same.
Year: 1895

page_text: Date of Application, 5th Feb., 1895-Accepted, 23rd Mar., 1895
COMPLETE
SPECIFICATION.
Improvements in Hydraulic Compensating Pumps and Engines, and
in Devices for Regulating same.
We ARTHUR EDWARD CUTLER and REGINALD DONKIN both of Mosman
near Sydney in the Colony of New South Wales, Engineers 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 improvements in hydraulic compensating pumps and
engines and in devices for regulating same whereby the amount of power expended
in such a pump or engine in performing work of varying extent or degree will be
"compensated or regulated by the requirements of the work to be done or in
other words the expenditure of power in raising loads of varying weights will be
compensated or regulated in the ratio of said weights and further where the work
done is of a negative quantity as where a load is lowered the reservoir of power
will be augmented in the ratio of the weight of said lowering load. This invention
is specially serviceable for regulating the quantity of water used in hydraulic
rotary engines, cranes, hoists, elevators inclined tramways and the like according
to the amount of work to be done in raising and lowering varying loads.
An improved bydraulic compensating engine or pump constructed according to
this invention has a crank pin which is held in the compensatory position in a
radial slot in a disc or crank by means of hydraulic pressure acting upon a non-
compressible fluid in a double ended cylinder set radially in or forming part
of the crank or crank dise and whose ram is a double ended extension of the
crank pin. The ends of this double ended ram cylinder are connected through
the crauk shaft and a stationary plug in the end of said crank shaft to regulating
devices which are adapted to be operated by hand or automatically according
to the work to be done or the varying resistance of the "load." The position
of the crank pin being thus alterable in the radial slot of the crank disc or
crank either manually or automatically the leverage of the crank is adjusted to
the load.
The regulating devices for the supply and exhaust of power from the double
ended ram cylinder of the crank or crank disc may take the form of a cataract or
other hydraulic governor by means of which a variation of pressure in the main
cylinder will cause the desired alteration of crank leverage though preferably
these devices would be of one or other of the improved constructions hereinafter
described.
But in order that this invention may be clearly understood reference will now be
made to the drawings herewith in which
Figure 1 is elevation of a hydraulic engine (usable also as a hydraulic pump)
constructed according to this invention and Figure 2 is a central sectional elevation
of same.
Figure 3 is central sectional elevation of regulating device or governor for an
engine or pump such as that shown in Figures 1 and 2 and Figure 4 is sectional
elevation of a fluid supply vessel or intensifier for use in connection with such
regulating devices.
Figures 5 and 6 are elevation partly in section and plan respectively of a
hydraulic pump having an adjustable crank pin which is automatically controlled by
devices in connection with the ram of a multiplying hydraulic lift.
Figure 7 is partial sectional elevation of the cylinder end of a multiplying

page_text: nydraulic nit or hoist or crane having attached thereto devices for regulating a
hydraulic compensating pump from same.
Figures 8 and 9 are front elevation and side elevation of a modified construction
of Figure 7 and Figure 10 is a section on line a a.
Figures 8 and 9 and Figure 11 is an enlarged detail partly in section of parts
of Figures 8 and 9.
Figures 12, 13, and 14 are sections and elevation of an auxiliary valve used in
the regulating devices and
Figures 15 to 21 are diagrammatic views of combination and arrangements of
elevator regulating devices and compensating hydraulic pump.
Referring to Figures 1 and 2 A are the hydraulic cylinders with necessary
valves &c. as well understood and B are the connecting rods to the crank pin C
in or on disc D on end of crank shaft E running in bearings E' the whole having
an appropriate framing. The crank pin C extends radially in reference to crank
disc outwardly and inwardly and takes the form of rains C' working in
cylinders D' in or on dise D in which at the front ends of said cylinders is
a slot D².
To the back ends of cylinders D' the pipes D³3 and D* communicate_from
separate ports or passages D and D longitudinally through the shaft E. These
ports or passages communicate with ports or grooves F' and in or on stationary
plug F which is held on the end of the shaft E by stuffing box E2 and gland E³
and is supported by a bracket arm E to the outside of which are led the feed and
exhaust pipes F and F which are continued in the plug Fas ports or passages F³
and F. The pipe F passage F port F2 passage D and pipe D' always constitute
a through passage while at the same time do also pipe D³ passage D' port Fi
passage F and pipe F the one end of such communications being the back of one of
the disc cylinders C and the other end being the ends of regulating cylinders as in
a cataract or other regulating devices or ports of such devices. The pinion G on
the shaft E shown in gear with wheel G is for transmitting the power to a
hoist &c. as well understood.
The crank cylinders D' and the passages and pipes connecting with same are
filled completely with some incompressible fluid preferably with heavy oil so that
pressure exerted in the regulating cylinders or devices will be transmitted to the
rams C and the crank pin C adjusted at any point in its possible movement in
slot D².
The regulating device shown in Figure 3 consists of cylinders H¹ connected
firmly together by appropriate framing H. In these cylinders H' are rams or
pistons Jon ends of one stem which carries in its centre a helical rack J.
Working in rack is a worn or endless screw K on spindle K having also thereon
hand wheels K and K³ and a friction wheel or driving wheel K. The cylinders H
have sockets H2 at their back ends connected by the pipes F and F to crank
cylinders D' as before described and they also are filled with the incompressible
fluid. It is preferable though not essential in order to make up for any possible
leakage in the plungers or passages to use an intensifier (see Figure 4) consisting
of a cylinder L with inlet L2 and having therein a ram L' and always communi-
cating by pipe L3 with one or other of the pipes F and F. This ram is worked
by piston M in cylinder M whose end is in communication with the source of
hydraulic power so that cylinder L being kept filled with non-compressible fluid
leakage if any will be constantly replaced and the rams C¹ in crank cylinders D'
kept effective in action.
Any motion given to the spindle K' either by hand wheels K' or K³ or by the
gearing wheel K which is driven by some automatic regulating devices actuated
by the lift or by the spindle around which the load is hoisted is by worm K and
rack J transmitted to the rams J' and by means of the connecting pipes F5 and F
as before described to the crank cylinders D¹ where the rams being actuated
the position of the crank C is altered radially and its leverage made to suit the
load to be lifted. Thus the amount of water consumed in and by the cylinders A

page_text: (Figures 1 and 2) is made proportional to the load. Further when the engine is
used where power may be conserved as where a load is lowering it (the engine) is
converted into a pump drawing from the exhaust the amount of water com-
mensurate with the work of the falling load and forcing it back into the
accumulator or the pressure main.
Referring to Figures and 6 the pump cylinders a have plungers connected to
crank c which has ram extensions in cylinders in crank disc d. The ends of
cylinders are connected by pipes d³ d and passages and ports through shaft e
stationary annulus fand pipes f³f to the controlling or regulating devices similar
to those described and shown in reference to the engine of Figures 1 and 2. The
motion of the motive power shaft is communicated to shaft e and according to the
force exerted is the position of the crank pin e in radial slot d² adjusted giving it
more or less leverage and making the pump do more or less work. The motion
may be communicated to the pump shaft by belt or chain or say preferably friction
gearing on to friction pinion g.
A hydraulic compensating pump (such as that shown in Figures 5 and 6) in use
with a hydraulic multiplying lift would have (see Figure 7) a tension device at
the end of the lift cylinder or ram H. A friction or other gearing between the
pulley shaft and the pump shaft and a supply and exhaust valve worked by a
tension device. The sheave bracket marked holds as well as sheaves j an
additional sheave or a sproket wheel or a friction wheel in gearing with the shaft
of the pump say by means of pinion g (see Figure 5) so that such pump would
work according to the power communicated from said sheave pulley or friction
wheel. The adjustability of the crank of the pump is controlled by the tension on
the rope or chain of the lift. In the sheave bracket is the fulcrum of lever k
fixed to end bolt 2 of the fixed end 2 of hoisting rope j. This end bolt slides
in brackets and terminates under said bracket with spring or elastic buffer k
interposed. The end of lever k takes in adjusted position on to the spindle 7 of
an auxiliary valve having ports and connected with ports m' and m² of the
controlling valve of the lift whose spindle m is worked as well understood by cord
through the elevator or lift car. This controlling valve has a pressure supply
port m³ so arranged that when port m¹ is in through communication with it then m²
is in through communication with port m and when port m² is in communication
with it port m¹ is in communication with port m these ports m³ and me being
exhaust ports. The ports 15 and 16 of the auxiliary valve are connected up by
pipe and ports 17 18 by pipe f to the through passages of the crank shaft of a
compensating hydraulic pump as before described thence to the crank pin rams or
cylinders of sanic by pipes (3 respectively that is 18 and 16 connect to d³ and
17 and 18 to 4.
The attendant regulates the controlling valve mx by moving spindle m up or
down while the pull or tension on the rope by compressing or slackening
spring moves lever k and regulates the auxiliary valve L*, the normal position
of this latter valve L* being shown in the drawing. Now in raising a heavy load
the spring would be compressed and lever k be moved upwardly by the tension
on the rope (see Figure 16). Valve stem / would move the valves thereon and
pressure enter the elevator ram cylinder through port m the port m' being the
exhaust passage from said ram cylinder pressure water would also pass to the crank
pin cylinders through pipes and ports m³ m² 1³ and fed to the outer cylinder d
(Figure 5) while the other or inner cylinder would be open to through pipe d²
pipe the through passage of the shaft pipe and ports m' and m. This
causes the crank pin to move inwardly until lever k resumes its normal position
with supply cut off to port 1. The amount of water pumped back into the
accumulator or pressure main is therefore increased or decreased by means of the
tension on the rope and by this means when the car is ascending with a partial load
the water which would be otherwise wasted is pumped back into main or accumulator
as also if the car is descending the water equivalent to the load is so returned to
power reservoir.

page_text: a
Figures 8 to 14 illustrate modifications of the regulating devices of a hydraulic
compensating pump such as that shown in Figure 5 when used in connection with a
multiplying hydraulic lift. In this case the tension device is dispensed with and
speed governor takes up the function of regulating. The cylinder or ram H*
has bracket carrying actuating sheave j¹ and additional friction sheave * for
working the pump. The controlling valve m* is worked by the attendant while a
speed governor worked by turbine N* actuates auxiliary-valve L* similar to that
shown in Figure 7 save that the ports 17 and 18 are dispensed with, ports 15 and 16
are exhaust passages to waste water tank and a supply port is made between the
ports and which latter are connected to pipes and respectively of hydraulic
compensating pump.
[1
The operations of the mechanisms shown in Figures 8 to 11 will be more clearly
understood on reference to the details of the valve shown in Figures 12, 13 and 14.
In raising a light load the spindle m of the valve mx is moved upwardly opening
the port 1 to the pressure water which passes upwardly in groove port or passage
to port 3 whence passing through pipe 4 it enters by way of port 5 the turbine N*
which it causes to revolve with a velocity proportional to the excess of pressure
over the load to be raised. Flowing from the turbine the water passes through
pipe 7 having branches to both ports 8 and 11 of the valve the former port
being closed and the latter port 11 being open through port 10 to the main ram or
cylinder H. The turbine N* is at the same time revolving the governor balls n'
which lift and lower as the case may be the lever n² and move spindle of the
auxiliary valve. When balls fly outwardly owing to increase of speed the valve
spindle is depressed and supply port communicates through port 12 pipe through
passage in shaft e and pipe d to inner crank pin ram cylinder d' while at the
same time exhaust is open from the outer crank cylinder d' through pipes d³
through passage in shaft e pipe port and exhaust-passage to waste water
tank. This action moves rams c¹ and forces crank pin c outwardly from the centre
of shaft e (Figure 5) and so increases the radial leverage or stroke of the pump
and therefore the quantity of water per stroke which it draws from the waste
water tank and forces into the accumulator or back into the main which quantity
corresponds to the excess of power exerted over the load lifted. When the
valve m* has been (by the attendant) placed in its highest possible position as it is
required for elevating loads the supply port 1 and port 9 freely communicate and a
full volume of pressure will pass to the inain ram H as well as the pressure supply
by way of the turbine N* through port 1 passage 2 pipe 3 ports 4 and 5 pipe 7
branch 8 port 11 and port 10. In lowering a heavy load valve spindle mis
depressed and the water froin the main ram H* passes by way of passage 2 port 3
pipe 4 and port 5 to the turbine N* which it revolves similarly as before described
with a velocity proportional to the excess of load over the normal load. Extra
speed depressing the lever the pressure water from port passes as before
described through port 12 pipe f and pipe d to the inner crank ram cylinder and
leaves the outer crank ram cylinder open per exhaust passage to waste water
tank thus causing the crank pin c to move outwardly or increase its leverage. The
exhaust water of the main ram leaving the turbine Nx per port 6 pipe 7 and port 8
(branch 11 being closed) and port 12 to the waste water tank. When valve mx is
in its lowermost position as in lowering loads the passage 9 is open to port 13 and
the exhaust from the ram cylinder passes in volume to the waste water tank.
From the foregoing descriptions and by the aid of the letters of reference to
which such descriptions refer and which are placed upon the diagrams it will not
be necessary to state anything further in relation to Figures 15 to 21 except to
point out in general terms what each figure represents. Figure 15 is a diagram of
a hydraulic lift regulating devices and a hydraulic compensating pump driven from
the gearing of said lift and the arrangement is shown as when the mechanism is at
rest that is neither lifting or lowering a load. Figure 16 is a diagram of similar
gearing with the mechanism as it would appear when a heavy load was being
elevated and Figure 17 is the same when a light load is being elevated. Figure 18

page_text: is a diagram showing the mechanism when a light load is being lowered and
Figure 19 is the same when a heavy load is descending. Figures 20, 21 and 22
are similar diagrams to the above with the modification of regulating devices in
which a turbine and governor balls take the place of a tension device. Figure 20
showing the position of the mechanism when at rest. Figure 21 the same when a
light load is being raised or a heavy load is being lowered and Figure 22 the same
when a heavy load is being lifted or a light load is being lowered.
Having now particularly described and explained the nature of our said inven-
tion and in what manner the same is to be performed, we declare that what we
claim is
First. An improved hydraulic compensating pump or engine in which the radial
leverage or stroke of the crank is regulated according to the requirements of the
work to be done by such pump or engine substantially as herein described and
explained.
Second. In a hydraulic compensating pump or engine the combination and
arrangement with the cylinder and the crank shaft of a double ended ram carrying
the crank pin, a double ended cylinder therefor set radially in or forming part of
the crank or a crank disc passages through the crank shaft connected to ends of
said double ended cylinder and a stationary plug or connection to said crank shaft
carrying supply and exhaust connections to said through passages substantially as
herein described and explained.
Third. The combination and arrangement with the integral parts set out in the
preceding "second" claiming clause of regulating devices consisting of a double
ended ram or pistons whose position is adjustable by hand or other power in
cylinders whose back ends are connected with the stationary plug or connection of
the crank shaft and the through passages to the crank cylinders or rams substan-
tially as herein described and explained.
Fourth. The combination and arrangement with the integral parts set out in the
preceding "second" claiming clause of a cataract or other pressure regulating
device substantially as herein described and explained.
Fifth. In a hydraulic compensating engine or pump the combination and
arrangement with connecting rods such as B on to crank pin such as C of rams or
extensions of said pin such as C a crank disc such as D having therein or thereon
cylinders such as D₁ with connections such as D³ to through passage in the crank
shaft having connection with regulating devices substantially as herein described
and explained and as illustrated in the drawings.
Sixth. In a hydraulic compensating engine or pump the combination and
arrangement with a crank or a crank dise having cylinders such as D¹ and pipes
such as D3 D4 of passages such as D and D and stationary plug such as F having
passages such as F3 and F connected to pipes such as F and F and having ports
such as F and F connecting to revolving grooves at end of passages D'
and D substantially as herein described and explained and as illustrated in the
drawings.
Seventh. In a hydraulic compensating engine or pump the combination and
arrangement with integral parts such as those set out in the preceding "fifth" and
"sixth" claiming clauses of a regulating device constructed and arranged substan-
tially as described and explained and as illustrated in Figure 4 of the drawing with
or without the intensifier constructed and arranged substantially as described and
explained and as illustrated in Figure 4 of the drawings.
Eighth. The combination and arrangement of mechanical parts all together
forming an improved hydraulic compensating pump substantially as herein described
and explained and as illustrated in Figures 5 and 6 of the drawings.
Ninth. The combination and arrangement with a hydraulic compensating pump
driven from (or from gearing of) an elevator ram or cylinder such as H* having a
tension spring such as k³ on end of the hoisting rope such as j¹ and a lever such as k
and a regulating or controlling valve such as m* of an auxiliary valve such as L*

page_text: in communication by ports such as 17 and 18 with the ends of the crank cylinders of
said pump and having ports such as 1 and 2 communicating with a main valve
such as m* and ports such as 15 and 16 communicating to exhaust or waste water
tank substantially as herein described and explained and as illustrated in Figure 7
of the drawings.
Tenth. The combination and arrangement with a hydraulic compensating pump
driven from (or from gearing of) an elevator ram or cylinder such as H* a
regulating or controlling valve such as m* of a turbine such as N* having balls
such as n' and lever such as n an auxiliary valve such as L* and connections as
described substantially as herein described and explained, and as illustrated in
Figures 8 to 11 of the drawings.
Eleventh. The combination and arrangement of mechanical parts and pieces all
together forming a regulating or controlling valve substantially as herein described
and explained and as illustrated in Figures 12, 13 and 14 of the drawings.
Dated this Twenty-first day of December One thousand eight hundred and
minety-four.
minety-100
A. E. CUTLER.
R. DONKIN.
Abel & Imray,
28, Southampton Buildings, London, W.C., Agents for the Applicants.