Improvements in and relating to Governors for Steam Engines.
Year: 1890

page_text: COMPLETE SPECIFICATION.
Improvements in and relating to Governors for Steam Engines.
I, FRANZ JOSEPH WEISS, of Basle, Switzerland, Civil Engineer, do hereby declare
the nature of my said invention and in what manner the same is to be performed, to be
particularly described and ascertained in and by the following statement :-
:-
In the governors heretofore generally employed the principal object has been to
secure as uniform a speed as possible for the steam-engines with which they were
connected, such governors being, for instance, particularly suited for engines con-
nected with a system of gearing and subject to quickly varying resistances.
In the governor forming the subject of the present invention the object is to
provide a governor for direct acting engines, as distinguished from engines for
driving a system of gearing by means of which the speed of the steam-engine, and
therefore that of the machine coupled with such engine such for instance as water or
air pumps or the like may be varied or adjusted at will within the widest limits. This
variation may be effected either automatically, or by hand, or by both combined, while
the engine is running, the abovementioned object being attained exclusively by the
action of the governor upon the expansion valve gear of the steam-engine, the
regulator valves being kept quite open all the while and no recourse being had to
throttling.
In order to render this specification better understood as regards the construction
and manner of working of my invention and also in order to reduce the necessity
of subsequent repetitions as much as possible without thereby impairing the clearness
of the specification I will here state two principles having special reference to the
case at issue.
Firstly. The work expended by a steam engine in overcoming the friction of the same
and that of a machine coupled therewith is the same for each revolution irrespective
of the number of revolutions of the engine per minute provided the resistance
remains the same. It is often wrongly assumed that the said work increases with an
increase in the number of revolutions of the engine.
Secondly. If a machine requiring a certain given useful effect per revolution be
coupled with an expansion engine and the sectional areas of the steam inlet and
exhaust passages of the engine and also that for the liquid, in case of a pump, be
sufficiently large so as not to cause a throttling of the said passages or at least
only to a very limited extent, within the limit of speed of the machine, and also if a
throttling of the steam be not produced by other artificial means, for instance by
screwing down the regulator-valve, then the engine, all other things remaining equal,
will always require the steam to be cut off at the same point no matter whether it is
running fast or slow.
Supposing for instance, that an air-compressor is driven by an expansion-engine,
then the area of the indicator diagram of the steam cylinder must be equal to the
total of the area of the indicator diagram of the air cylinder plus the area of a surface
representing the frictional effect of the entire engine per single stroke or revolution of
the same.
When the air-pressure remains uniform the indicator diagram of the air cylinder
will also remain uniform irrespective of the speed of the engine. As above stated
the frictional work or effect per revolution is likewise uniform under the same con-
ditions hence the total of both must also remain uniform, the steam cylinder diagram
must therefore also remain uniform.
It follows from the above that under the same conditions and with a fixed steam-
pressure, the point of cut off must remain uniform throughout. This uniformity in
the cut off I will bereinafter call the requisite point of cut off. Contrary to the

page_text: popular idea, it is not possible to change the number of revolutions of such an engine
by varying the expansion without, at the same time throttling the steam. If the
steam cylinder is given more than the requisite amount of cut off, then the engine
will run away, if on the other hand, the cut off is not sufficient then the engine will
stop.
I will now explain the construction and peculiar manner of working my improved
apparatus with reference to the accompanying drawing the figures of which are
hereinafter referred to.
G, Figure 1 represents a conical pendulum or governor. It may here be stated
that the governor will, throughout this specification, be supposed to be a highly
static one, that to say, each variation in the outward position of its balls or,
in other words, each variation of the angle a will correspond to a different rotary
speed of the governor shaft. This static governor must have a great regulating
power, by which I mean the result obtained by dividing the greatest number of
revolutions of the governor at the most outward position of its balls by the
simallest number of revolutions thereof at the least outward position of the balls.
It will hereinafter be shown how static governors should be constructed in order
to ensure the greatest regulating power, a special kind of such governors will also
be described. The governor G acts upon the valve rod of a "Rider" expansion
valve gear of an engine by means of the nut F, regulating lever F D C, connecting
rod CB and lever BA.
The regulating lever F D (, which serves for the transmission of movement to the
connecting rod CB from the nut F, consists of two separate levers, that is to say
of the lever FD having an elongated portion D D₁ at its rear end, and of the
lever D C. Both of these levers have a common fulcrum D². The rear portion D D¹
of lever F D D is pressed against the lever D C by means of a strong spring f
which admits of being tightened by the nut s; or, in other words the spring f
tends to enlarge the angle ẞ shown in the drawing as 180. The movement
towards the lever D D on the part of lever D C, however, is limited by the set
screw S against which the said lever DC presses from below. It is evident that,
as long as the parts thus connected are left unchanged, the levers F D D and DO
may be considered as one rigid lever F D C and will act as such that is to say,
they will, in the usual manner, transmit movement of the nut F of the governor to
the connecting rod CB and thus also to the mechanism for regulating the cut off.
In order to more clearly explain the peculiar action of the mechanism, I will
describe the same by an example. Supposing the regulating device shown in Figure 1
to be applied to an engine for driving a compressor coupled thereto, then the steam
cylinder will, according to the explanations hereinbefore given, require a certain cut
off under a certain steam and air pressure. This amount of cut off we have called
the requisite cut-off and, as previously shown, it will remain uniform, no matter
whether the engine be running fast or slow.
As long as no change of any kind takes place, or is produced the governor will,
in the usual manner, maintain a certain number of revolutions and, accordingly the
compressor will supply a certain amount of compressed air per minute. Supposing,
however, that the amount of compressed air required from the machine becomes less,
then the object of the governor forming the subject of this invention will be in such a
case to enable the attendant to correspondingly reduce the speed of the machine in
accordance with the reduced amount of work or effect required from the same. In
order to do this, the set screws Figure 1 will have to be screwed down.
By reason of inertia the balls, etc. will in the first moment, still retain their original
position and hence also the nut F, and only the lever D C will be in a somewhat lower
position, or in other words, the angle ẞ will be smaller. In consequence of this the
adjusting lever BA of the expansion valve gear will be pressed down by the con-
necting rod C B thus reducing the cut off correspondingly.
"
The cut-off for the steam cylinder having been thus reduced below the uniform or
requisite" amount will no longer be sufficient to enable the engine to overcome the

page_text: pressure in the compressor plus the frictional effect of the engine for each revolution,
and in consequence thereof the engine would stop. This, however, is automatically
prevented in my improved device in the manner which I will now explain.
It is evident that, before stopping altogether, the machine, while consuming part
of the working energy or momentum accumulated in the balance or fly wheel will be
running at a slower speed so that the balls of the governor will assume a different,
that is to say, a lower portion of equilibrium thereby pressing the nut F down and
causing the lever mechanism F D C, to turn in a direction opposite to that of the
bands of a clock. This causes the connecting-rod C B to be lifted and the adjusting
lever B A of the expansion valve gear to again produce a larger cut-off, until the
requisite" amount of cut-off be again attained, this being the same with the reduced
rotary speed as it was with the greater speed. After all these movements have taken
place the adjusting lever B A will automatically, assume its previous position and
only the "configuration" of the other parts of the governor and the intermediate
mechanisms between the same and the valve-gear will have become changed with the
different speed of the governor.
"
It is obvious that, on the other hand, if the set screw were turned in an opposite
direction so as to make the angle ẞ larger, this would cause the opposite result from
that above described, that is to say, it would cause the engine to run at a higher
speed. The same purpose and the same effect as shown with regard to the mechanism
in Figure 1 may also be attained by constructing the regulating lever F D C in one
piece, as shown in Figure 3 the elongated portion D D' and the parts S, f and s being
in this case, dispensed with, and providing means for varying the length of the con-
necting rod C, B, Figure 1.
For this purpose the one end of the said connecting rod is formed with a screw-
thread engaging with a nut movably secured to the head C of the lever, the said nut,
on its part, carrying a hand wheel E, as shown in Figure 3. By turning the wheel E
in such a direction as to cause the point B to move further away from the point C
the same result will be attained as in screwing down the set-screw S in the con-
structioned arrangement shown in Figure 1. In either case the adjusting lever B, A
will be pressed down thus producing a smaller cut-off which would tend to stop the
engine, the latter effect, however, being prevented as already shown, in consequence
of the weights, of the static governor being brought to a different position of equi-
librium corresponding to a reduced speed, this, in turn, causing the adjusting
lever B A to be raised and thereby again giving the requisite cut-off for the steam
cylinder. By turning the handwheel E in an opposite direction the opposite result
would be attained, that is to say, the engine would be made to run at a higher
speed.
The above described modification of the original arrangement shown in Figure 1 as
well as the original arrangement itself, and those to be hereinafter described always
refer to the combination of a static governor of very high regulating power with an
intermediate mechanism between the said governor and the expansion valve gear, the
said intermediate mechanism having a part or parts which, while the machine is in
motion, admit of being adjusted with reference to the other parts of the said
mechanism in such a manner as to alter the relative positions of the expansion valve
gear with regard to the balls of the governor proper, without at the same time,
materially changing the total proportion of transmission between the movements of
the nut of the governor and the stroke or movement of those parts of the expansion
valve gear which regulate the cut-off in the steam cylinder.
The most frequent use for governors of this kind will be for engines intended for
driving water or air pumps. In such cases it is desirable to provide means for
regulating the said pumps not only by hand, as heretofore described, but also auto-
matically and in such a manner as to cause the working speed of the engine to be
automatically reduced when the water or air pressure shall have reached a pre-
determined point.
Constructional arrangements of this kind are shown in Figures 2 and 3 and I will
proceed to describe the same in the first placé with reference to Figure 3. For the

page_text: •
present it will be well to pass over the peculiar construction of the governor proper
shown in the drawing, this will be hereinafter explained, and to suppose that a
strongly static governor of the kind shown in Figure 1 be arranged in its place. The
movements of the nut F of the governor proper Figure 3, are by means of the inter-
mediate mechanism that is to say, the lever F D C, and connecting rod C B, trans-
mitted to the device for regulating the cut-off, the latter, in this case also being the
expansion valve of a "rider" gear.
The connecting rod (B is here shown as formed in two portions that is to say, an
upper portion rigidly connected at its lower end with the barrel H and a lower
portion, connected at its upper end with a plunger J tightly fitting in the barrel H
and capable of moving within the latter. When the screw L is screwed down the
plunger J is, by reason of the arrangement of the cross-pieces K' connecting bars K
and spiral spring f pressed against the bottom of the barrel H with a certain force,
which may be regulated. As long as the parts remain in this position, the entire
dynamometric apparatus thus formed between the joints C and B, acts as if it did
not exist at all, that is to say, as if C and B were connected by one rigid con-
necting rod.
o is a flexible tube of gutta-percha or other suitable material so as not to interfere
with the movement of the other mechanism, it communicates, on the one hand,
with a space between the bottom of the barrel H and the plunger J, and on the other
hand, with the pressure conduit of the pump the work of which is to be regulated.
For the purpose of explaining the device in connection with the example already
referred to above, we will again assume the same to be applied to a steam engine for
driving an air-compressor, the said air-compressor being intended for working, say,
12 rock-drills. In this case, the flexible tube is arranged so as to communicate direct
with the pressure conduit of the compressor in such a manner that the pressure
of compressed air within the barrel H is exerted below or, as here shown, above, the
plunger J.
Supposing it is required that the air pressure shall not exceed a certain limit, say
atmospheres for instance. The pressure of the spiral spring f will by means of the
screw L, be first adjusted in such a manner as not to permit the plunger J to be lifted
from the bottom of the barrel until the tension of the air above the said plunger shall
have become equal to 7 atmospheres. We will suppose that the quantity of air
required for working the twelve rock-drills were such as the compressor will furnish
at say 100 revolutions per minute. The engineer will then, by turning the hand-
wheel E in the manner as herein before described give the engine such a number of
revolutions per minute as will either be equal to the required maximum number
of 100 per minute or a little above. This done, the engine is allowed to work on by
itself. The apparatus will then act as follows:-that is to say:-
As long as the air pressure does not attain the predetermined limit of 7 atmospheres
the plunger J will remain at the bottom of the barrel H and the dynamometric
apparatus between C and B will not come into action but will simply act the same as
a rigid bar or connection between C and B the entire regulating apparatus
maintaining the speed of 100 or a little more as originally secured by the adjustment
of the hand-wheel E.
Supposing now that six of the twelve rock drills were stopped, as the compressor
will, for a while, still maintain the previous speed, because less air is being consumed
than is being supplied by the compressor. As soon as the air pressure exceeds the
predetermined limit of 7 atmospheres, however, the pressure of air exerted upon the
plunger J will overcome the resistance of the spring and the plunger will be pressed
down within the barrel H thereby in turn pressing down the adjusting lever BA of
the regulating valve gear and thus causing a shorter cut off in the steam cylinder. As
previously explained, the result would be that the engine would now come to a stand-
still, since the cylinder is no longer receiving the requisite cut off. This, however, is
again automatically prevented on the part of the apparatus, as the engine, and with it
also the static governor, will, before coming to a stop, first begin to run slower, thus
causing the governor balls to drop into a lower position of equilibrium, the adjusting

page_text: lever BA thereby being lifted into its previous position again through the intermediate
devices FDCB and again securing the
" requisite amount of cut-off in the steam
cylinder; at the same time, the governor shaft, and also the engine, will in accordance
with the lower position of the governor balls, make a smaller number of revolutions
per minute.
It will be understood from the character of the apparatus as described that the
movements of the plunger J will be such as to cause the balls of the governor to drop
so far, and the rotary speed of the engine to be in consequence reduced to such an
extent, as to cause the compression at all times to supply just the amount of air that is
required under the varying circumstances, for if the compressor, supplies a greater
amount of air, then the pressure will increase still more and the plunger will be lifted
still further, which will cause the speed of the engine to be still further reduced
through the regulating device above described.
Supposing a contrary case, that is to say, a case in which a greater amount of air is
required which may be caused for instance, by four of the six rock drills previously
stopped being set to work again. In this case, the compressor by reason of the slow
speed which it is as yet retaining, will he supplying less air than is required; the air
pressure will therefore, become reduced, this will, at the same time, cause the
air pressure exerted upon the plunger J to become reduced to such an extent as to
make it less than the pressure of the spring f. The plunger J will therefore be drawn
back into its barrel which will, in turn, cause the end B of the adjusting lever BA
to be lifted, thus giving the steam cylinder a larger cut-off. The previous cut-off
having been the "requisite" amount of cut-off now becomes too great and the engine
will have a tendency to run away. This, however is again automatically prevented by
the apparatus the increased speed lifting the governor balls into a more elevated
position of equilibrium and the adjusting lever B A being again lowered through the
intermediate devices F D C B, to sucli an extent as to again give the "requisite"
amount of cut-off for the steam-cylinder.
"
Unless provision is made for limiting the extent of movement of the plunger Jas
it is being pressed out of its barrel, it may occur that the engine will be automatically
brought to a standstill through the apparatus shown in Figure 3 when no compressed
air is further required as in such case, even if the number of revolutions be ever so
small, the air pressure will still always be increasing and the plunger J to be still
further pressed out of the barrel, until finally the cut-off is brought below the
requisite "amount.
"
In practice it is by no means desirable to have the engine thus automatically
brought to a standstill. It is therefore advisable to limit the extent of the outward
movement of the plunger in its barrel. This may be effected by arranging the upper
cross-piece K¹ in such a manner as to strike against the upper ond or continuation of
the barrel H thereby preventing the plunger J from being pressed out of the barrel
any further than would be sufficient to secure the "requisite" amount of cut-off for
the steam cylinder during the lowest position of the governor balls, and hence also
during the smallest possible speed of the governor and engine. It is also advisable to
provide means for allowing the extent of movement of the plunger to be adjusted.
By this arrangement the engine is secured from being brought to a standstill by
the apparatus, but it will remain in motion with a minimum number of revolutions.
The small quantity of compressed air (or water) as the case may be, supplied by the
machine at such a minimum speed of the engine may be removed or blown off
through a properly constructed safety valve.
Figure 2 shows a modification of the apparatus represented in Figure 3, and
consists in rendering the adjustment of lever F D D with regard to lever DC
automatic. Instead of being adjusted by hand through a screw S as in Figure 1
a dynamometric apparatus o M HJK, Figure 2 is provided between the said two
levers the said apparatus actuated by the pressure of a liquid. The flexible pipe
connected with the pump to he regulated, and receiving from the same liquid,
communicates at its other end with an air-tight chamber below an elastic membrane of
arranged within a casing H provided on or connected with lever D C.
t
0

page_text: ! The movements of the membrane are transmitted to the lever F D D' by means of
a piston J and rod K. The rear portion of lever F D D' is drawn towards lever D C
by a spring f the tension of which may be regulated at will by means of the
screw-nut L. The said screw-nut L is tightened to such an extent as not to allow the
piston J on the membrane to be lifted until the pressure of the working liquid
exceeds a predetermined point, say 8 atmospheres. By subsequently turning
the hand wheel E the speed of the governor is so adjusted as to make the pump, to be
regulated thereby supply the maximum quantity per minute that may be desired for
the present or rather a trifle more.
As long as the tension of the liquid does not exceed the above predetermined.
pressure of 8 atmospheres, the piston above the membrane will remain in its lowest
position and the parts F D D¹ C will act the same as one rigid lever FD C.
As soon, however, as the pressure of 8 atmospheres is reached and about to be
exceeded the membrane M and piston J will be lifted from their lowest position
of rest and the levers D D¹ and DC will be pressed away from each other or in other
words, the angle ẞ will become reduced. As the lever F D D¹, by reason
of the inertia on the part of the static governor connected with the nut F. will, in the
first moment, still remain in its position the lever D C will be pressed down,
the speed of the governor and hence also that of the engine connected with the same,
will, in consequence, be automatically and correspondingly reduced, in exactly the
same manner as already explained with reference to the construction shown in
Figure 1.
Supposing that the pressure of the working liquid now becomes reduced again
(say, in consequence of an increase in the consumption of the same) the piston on
the membrane, by reason of spring f, will again be lowered, lever DC will be raised
and the speed of the engine will thereby be automatically increased. What has been
previously said about the advisability of limiting the extent of movement of the
plunger J, Figure 3, applies also in case of the piston J Figure 2.
It is obvious that the construction of my apparatus as described with reference to
Figures 2 and 3 may be applied in all cases where a pump driven by an expansion
steam-engine is to be regulated in such a manner as to be first given such a number
of revolutions by hand as to secure the maximum supply of liquid or gaseous fluid
as may for a time be required and to enable the speed of the engine to be auto-
matically reduced to any desired extent when the pressure of the working liquid or
fluid exceeds a predetermined limit.
The particular construction of the apparatus as above described is not suitable,
however, for regulating the following classes of pumps, that is to say, firstly, force
pumps for hydraulic accumulators driven by water or air and, secondly, into a
reservoir situated at a certain height.
In the pumps above mentioned the pressure of the working liquid always remains
uniform and in pumps of the first kind depends on the pressure exerted upon the
piston of the accumulator and, in pumps of the second kind on the height at which
the reservoir is situated above the pump. It is not possible to regulate such pumps
by the varying pressures in the manner above described, for this reason, that varying
pressures are, in these cases, not intended or do not occur. Another kind of regula-
tion, however, is desirable for cases of this kind, that is to say, in pumps of the first
kind above referred to, it is desirable to slacken the speed of the pump as the piston
of the accumulator approaches its highest position, and in pumps of the second kind
to slacken the speed of the pump as soon as the water, in the reservoir reaches a
certain level.
These objects may in the case of pumps for accumulators be attained by means of
the auxiliary devices shown in Figures 3° and 3d in connection with the governors
forming the subject of this specification and, in the case of reservoir pumps, by
means of the arrangement of pipes shown in Figure 4.
Instead of arranging the flexible pipe o, Figure 3, so as to communicate with the
water of the accumulator direct, it is first connected with a three-way-cock M,
Figure 3, by means of the pipe of another pipe o³ likewise entering the three-way

page_text: cock M communicates with the water in the accumulator, and a third pipe o is
provided for discharging the liquid into the open air. In the position of the cock as
shown in the drawing, that is to say, when the handle a of the plug is lowered, the
water is not in communication with the regulating apparatus, and the plunger J,
Figure 3, is not under pressure, since the space above it within the barrel H is in
communication with the open air through the pipe o and its continuation o¹ as. well
as cock M and discharge pipe o².
As already stated, the regulating device, Figure 3 will now act in the same
manner as if the dynamometric apparatus between C and B were entirely dispensed
with and as if the lever C were simply connected with the end B of the adjusting
lever B A by a rigid bar C B. The static governor will, therefore, give the engine the
number of revolutions for which it has been adjusted through the hand-wheel E.
We will now suppose that the amount of water consumed becomes less. The
piston of the accumulator will then rise and it will be desirable to automatically
reduce the speed of the pump in accordance with the reduced consumption of water.
This will be effected through the governor forming the subject of my invention and
shown in Figures 3 and 3 in the following manner, that is to say, as soon as the
piston of the accumulator has risen to a certain height an arm, connected therewith
but not shown in the drawing, will strike the handle a of the three-way cock M from
below and as the piston continues to rise, will lift it up still further until it ultimatoly
reaches the position a'. In this position the water in pipe o³ will, by means of the
said three-way-cock M and the pipes o' and o be brought into communication with
the space above the plunger J the latter will be pressed out of its barrel thereby
pressing down the adjusting lever B A and causing the number of revolutions of the
engine to become reduced, by reason of the lower portion of the governor balls
resulting therefrom the adjusting lever will be subsequently drawn back into its
previous position, thus again securing the "requisite" cut-off for the steam cylinder,
all as hereinbefore described. If the consumption of water subsequently increases
and the piston of the accumulator be correspondingly lowered then a second arm
connected therewith, but not shown in the drawing, will press, down the handle of
the three-way cock M into the position a, thus again causing the same position of the
cock and its connections as shown the drawing.
The water within the pipe o³ will be again cut-off and the space above the
plunger J will be brought into communication with the open air again through the
cock M and discharge pipe o². The water collected above the plunger J being thus
allowed to discharge into the open air the said plunger will be drawn into the barrel
again through the spring f. As previously shown, this will again cause the number
of revolutions of the governor and hence also of the engine, to be increased and; at
the same time, the regulating mechanism. will be brought back into its original
position.
"
Figure 3 shows a modification of the arrangement of the auxiliary apparatus in:
Figure 3. In this arrangement the pipe o³ is likewise in communication with the
water, the pipe o² discharges into the open air and the pipe o' is connected with pipe o
and hence also with the barrel H, Figure 3. When the piston of the accumulator
rises an arm connected therewith, but not shown in the drawing will strike against
an elongation of a valve v from below and thereby lift the said valve v, thus causing.
the water to be admitted from pipe o into o' and o and to enter the barrel H above
the plunger J pressing the same out of its barrel and thereby tending to reduce the
speed of the engine. Of course, some of the water will, at the same time escape into
the open air through the open discharge pipe o²; however the discharge opening of
the said pipe o2 being made of a much smaller sectional area than those of the
pipes o, o¹ and o, a certain pressure, although of reduced volume, will still prevail
within the said pipes and connections, this pressure being still sufficient in its action
upon the plunger J to overcome the pressure of the spring f.
When the piston of the accumulator is subsequently lowered again the arm, above
referred to as being connected with it, will likewise be lowered with it, causing the

page_text: valve and its elongation to drop and to again cut off the water within the pipe o³
from the regulating apparatus, whereupon the spring f will again draw the plunger J
back into its barrel, the water collected above the plunger being forced out of the
discharge pipe o into the open air and the engine will begin to run faster.
The discharge o², Figure 34, may also be entirely dispensed with by arranging the
elongation of the valve so as not to fit quite closely with the valve chamber, say by
dispensing with a stuffing box and simply allowing it to enter the valve chamber
through an aperture with a certain amount of play, the space thus formed will then
take the place of the special discharge pipe o².
The auxiliary apparatuses shown in Figures 3 and 3d may be applied in exactly
the same manner in connection with the construction represented in Figure 2 as well
as with that in Figure 3. It is also obvious that, in applying the auxiliary apparatus
of Figures 3 and 3d, it is not necessary neither as regards Figures 2 nor 3, to give
the spring f, any special tension to depend just exactly from the pressure of the
working liquid within the accumulator; all that is required in this respect is that, on
the one hand, this tension shall be less than the full pressure exerted upon the
plunger J, Figures 2 and 3 on the part of the working liquid in case of the device
in Figure 3° and less than the reduced pressure, in the case of the device in Figure 3d
and, on the other hand that the tension shall be at least sufficient to draw the
plunger J back into its position of rest, when the pressure of the working liquid has
ceased to act upon the plunger and, at the same time to overcome the resistance of the
intermediate parts for transmitting the movements between the governor and expansion
valve gear.
These two opposite limits for the tension of the springs f are so far removed from
each other as to render it very easy to secure some intermediate degree of tension by
properly adjusting the screws L, Figures 2 and 3.
What has been previously stated with regard to automatically bringing the engine
to a standstill and automatically producing a minimum number of revolutions of the
same, without causing a dead stop, through the mechanism in Figures 2 and 3, is of
special importance in the case of such pumps for accumulators as those in which the
pistons are nearly always working in their highest position, which they must not be
allowed to exceed. Now supposing that, by certain means the particulars of which
do not here concern us, provision had been made for automatically bringing the
engines for the forcing pumps to a standstill each time the piston of the accumulator
had attained its highest position (this very often occurring several times in the course
of one minute,) in such case it may very easily occur that, when the piston of the
accumulator is lowered the engine will not at once move again by itself which may
prove of very serious consequences for the machinery and the people employed on
the same as for instance in still works, foundries and the like. It is therefore,
preferable not to bring the forcing pumps to a standstill at a high position of the
accumulator piston but merely to automatically give them a minimum number of
revolutions. The small quantity of water that is still being lifted by the pumps at
such a small number of revolutions may be allowed to escape through safety valves
or discharged through a suitable valve arranged so as to be opened by the accumu-
lator piston when reaching its highest position, unless some other use may be found
for the water.
In the arrangements shown in Figures 2 and 3 the engine, instead of being brought
to a standstill is simply given a minimum number of revolutions as already stated
this is attained limiting the extent of outward movement of the plunger J, Figures 2
and 3, preferably by means of an adjustable collar or similar device in such a manner
as to allow the said plungers to move out of their barrels only so far at the lowest
position of the governor balls as to barely secure the requisite cut off through the
adjusting lever BA, Figure 3.
Figure 4 shows an arrangement of pipes serving as an auxiliary apparatus by
means of which the automatic governor as represented in Figures 2 and 3 may also
be applied in the case of pumps for reservoirs. The water is by means of a pipe Q

page_text: conveyed to a reservoir R having an overflow S, Figure 4. A pipe o' communicates
with the reservoir R at a a, a little below the level of the overflow S. At its lower
end the said pipe o¹ is provided with a discharge o2 of smaller section than the pipe o¹
for automatically removing the liquid from pipe o¹ and discharging it into the open
air; the pipe o connected with the pipe o' laterally is the same flexible pipe already
referred to as communicating with the apparatus for regulating the steam engine of
the reservoir pump.
So long as the water within the reservoir R remains below the level a a the automatic
regulating device, Figures 2 or 3 will remain inactive and the engine will be making
that number of revolutions to which it has been adjusted by means of the hand-
wheel E, Figures 2 or 3. Supposing however, that the water within the said reservoir
Figure 4 begins to rise above the level a a then the pipe o' will be filled with water
although part of the water will escape through the discharge o' the latter being of
much smaller section. The pressure of the water will pass through the flexible pipe o
into the dynamometric apparatus, Figures 2 or 3, and will bring the same into action
as already described in such a manner as to reduce the speed of the engine, thus causing
the pump to lift a correspondingly small amount of water.
If the consumption of water from the said reservoir R increase again then the water
level will sink the water within the pipe o' will be discharged through o³ the pressure
within pipe o and hence also within the dynamometric apparatus will cease, the said
apparatus resuming its previous position and thereby causing the engine to regain its
former speed as already described.
For the sake of stating a concrete example and thereby rendering the peculiar
action of my apparatus more intelligible, I have in Figures 1 and 3 and throughout
this specification so far always assumed the governors hereinbefore described as being
connected with and acting upon a Rider expansion valve gear. It is obvious however
that these governors may also be supplied to any other kind of expansion valve gear,
such as the Corliss-Sulzer, Colmann or any other kind just as governors of various
kinds such as Watt's Porter's Proll's Buss or others may be applied to all kinds of
expansion valve gears. I may even go so far as to say that the valve gears above
named so effective in connection with engines for running a system of gearing are
rendered still more capable developing their peculiar advantages more particularly for
engines used for driving pumps and other machines when applied in connection with
a governor of the kind hereinbefore described.
The limits within which the number of revolutions of engines may be regulated by
means of these governors will be greater the more static the governors proper used
in connection therewith, will be, or, to use a more concise expression already pre-
viously employed the greater their regulating power will be. In the case of the
governor proper or conical pendulum G, Figure 1, the regulating power will be
found as follows by analysis when applying the same letters of reference as in the
n max. being supposed to designate the maximum number of revolutions of the
governor shaft for the greatest angle a max., and n min., to mean the smallest number
of revolutions of the governor shaft for the smallest angle a min. and supposing at the
same time that u designate the proportion between the distance of the fulcrum of
the pendulum from the governor axis on the one hand and the length / of the said
pendulum on the other hand, that is to say, supposing

page_text: and that it will become the greater the larger this proportion u is made. In
Figures 3, 3ª and 3b a new form of governor is shown in which this proportion u may
be made relatively great in a very small space thus rendering this construction
particularly well adopted for governors of the kind hereinbefore referred to.
In the projection, Figure 3 and plan, Figure 3* N designates cylindrical weights
having the diameter d and suspended from pivots T so as to turn eccentrically on
the same, the said pivot being arranged at a distance away from the vertical axis Q
of the governor and carried in the cross piece P. The upward and downward
movement of the governor weights N is transinitted to the nut F of the governor in
a very simple, effective and cheap manner as follows.
A revolving chamber RVS, Figure 3, provided with a recessed groove below
for receiving the nut F is so mounted on the vertical shaft Q of the governor as to
admit of freely moving up or down on the same. If desired, it may also he so
arranged on the shaft as to be capable of freely rotating on the same, this however is
immaterial. The inner surfaces of the top cover R and bottom S of the revolving
chamber are turned smooth, forming right angles with the governor shaft Q, their
distance d¹ from each other being equal to, or a fraction of a millimeter larger than
the diameter d of the two cylindrical weights N. By reason of the varying
centrifugal force of the weights N the latter will, from time to time assume a higher
and a lower position as the case may be (the angle a will become larger and smaller),
the cylindrical weights, in performing these movements will carry the revolving
chamber RVS, with the grooved recess formed thereon for the nut F, up and down
with them, the said revolving chamber, as already stated, being arranged to slide
freely on the governor shaft Q. These movements are in turn transferred to the
expansion valve gear of the engine by means of the intermediate devices F DCB in
the same manner as previously explained. The weight of the chamber RVS serves
to increase the " energy of the governor and in spite of this weight, the
regulating power as represented by the equation (I) still applies also for
governors of the construction here shown.
66
33
This would not under the same circumstances apply in case of a governor as the
one designated by G in Figure (1) as in such a governor the regulating power would
at once become reduced by applying a weight of this kind.
According to this the number of revolutions of an engine may by means of this
governor in connection with the intermediate mechanisms herein before described, be
regulated within such wide limits that the maximum number of revolutions will
be 4-80 times as great as the minimum number of revolutions or in other words the
capacity of the engine may be increased to 4.80 times from the single; it may
also be adjusted for any intermediate value. It will thus be seen that such a
variation in the number of revolutions may be secured as could not even approxi-
mately be obtained heretofore by any other means and without having recourse to a
throttling of the steam.
Applying the term "energy" according to the definition therefor given by
Grashof in his treatise on theoretical engineering second volume, and supposing G to
signify the weight of one of the cylindrical weights N, and Q the weight of the

page_text: will be found to be.
E 2 x G + Q
"
(III)
that is to say it is equal to the total weight of all the movable parts of the governor
proper and independent of its "configuration or in other words independent of
the angle
a as formed hy the revolving weights. The latter does not apply in
case of the governor G in Figure 1 the energy here decreasing as the angle
becomes smaller.
a
When the revolving chamber RVS is made sufficiently heavy so that its weight
alone will be sufficient to overcome the resistance of the intermediate mechanisms
between the governor proper and the expansion valve gear of the engine then the
construction of the governor proper as shown in Figures 3 and 38 and 3° may be
simplified inasmuch as, in that case it will be sufficient to let only the upper
surface R of the chamber touch or engage with the cylindrical weights N, or in
other words to let the entire chamber RVS rest upon the said cylindrical weights N
with its top cover having a smoothly finished lower surface, the bottom S of the
chamber need not in this case touch the cylindrical weights and will, not therefore,
require to have a finished surface.
G - 0
E =
In this arrangement the energy E of the governor will become less when the
governor drops into a lower position (that is to say EQ in the equation III
being inserted) than when it rises (in which case according to equation III
2 GO. This however will be at no moment unless a great amount of energy
and an instantaneous action on the part of the governor are particularly required.
Such an arrangement would answer well enough on an engine for driving say a
compressor. If however great energy and an instantaneous action be required
say for an engine to drive an accumulator pump such reduction of the energy of
the governor even with regard to the one direction of its movement only cannot
be recommended.
It is obvious that so far as the character of the governor proper hereinbefore
described is concerned it is immaterial whether the cross piece P be made to surround
the cylindrical weights N as shown in the plan, Figure 3 or whether the cylindrical
weights N be made to surround the cross-piece P as shown in the plan Figure 3b.
I may also with a view to obtain as rounded and solid a shape as possible
round off the corners of the cylindrical weights N at A, as indicated in the same
Figure 3.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed I declare that what I
claim is :-
First. In steam engines with variable expansion the combination with a governor
of a movable lever and a connecting rod between the said lever and the regulating
valve gear of the engine substantially as and for the purpose specified.
Second. In steam engines with variable expansion the combination with a governor
of a front lever having a rear elongation and a rear lever both of the said levers
having a common fulcrum an adjustable spring actuating the said levers means for
limiting the extent of movement of both levers with regard to each other and a
connection between both levers and the regulating valve gear of the steam engine
substantially as and for the purpose set forth.
Third. In steam engines with variable expansion the combination with a governor
of a front lever having a rear elongation and a rear lever both of the said levers
having a common fulcrum an adjustable spring actuating the said levers, a screw for
regulating the position of the two levers with regard to each other and a connection
between the said levers and the regulating valve gear of the engine substantially as
and for the purposes set forth.
Fourth. In steam engines with variable expansion the combination, with a
governor, of a movable lever an adjustable connection between the said lever and the

page_text: regulating valve gear of the engine a pump barrel and plunger arranged on the
connecting rod, a spring pressing the said plunger into the said barrel and means for
increasing or decreasing the distance between the bottom of the said barrel and the
said plunger substantially as and for the purposes set forth.
Fifth. In steam engines with variable expansion the combination with a governor,
of a movable lever an adjustable connecting rod between the said lever and
the regulating valve gear of the engine a pump barrel and plunger arranged on
the said connecting rod, a spring pressing the said plunger into the said barrel and a
pipe o entering the pump barrel between the bottom of the said barrel, and the
plunger, the said pipe o communicating with the pressure conduit of the working
machine substantially as and for the purposes set forth.
Sixth. In steam engines with variable expansion the combination with a governor
of a movable lever an adjustable connecting rod between the said lever and the
regulating valve gear of the steam engine a pump barrel and plunger arranged on
the said connecting rod a spring pressing the said plunger into the said barrel a
pipe o entering the said barrel between the bottom of the said barrel and the plunger
the said pipe o communicating with the pressure conduit of the working machine
and an adjustable device for limiting the extent of movement of the said plunger
substantially as, and for the purpose, set forth.
Seventh. In steam engine with variable expansion the combination with a governor
of a front lever having a rear elongation and a rear lever both levers having a
common fulcrum an adjustable spring actuating the said levers a dynamo metric
apparatus arranged between the said levers and actuated by a pressure liquid and an
adjustable connection between the levers and the regulating valve gear of the engine
substantially as, and for the purpose set forth.
Eighth. In steam engines with variable expansion the combination with a governor
of a front lever having a rear elongation and a rear lever both levers having a
common fulcrum an adjustable spring actuating the said levers a membrane acting
upon the rear elongation of the front lever a pipe o entering below the said membrane
and communicating with the pressure conduit from the working machine and an
adjustable connection between the said levers and the regulating valve gear of the
engine substantially as, and for the purpose, set forth.
Ninth. In steam engines with variable expansion the combination with a governor
of a front lever having a rear elongation and a rear lever both levers having a common
fulcrum an adjustable spring actuating the said levers a membrane acting upon the
rear elongation of the said front lever a pipe o entering below the said membrane and
communicating with the pressure conduit from the machine an adjustable device for
limiting the extent of movement of the said membrane and an adjustable connection
between the levers and the regulating valve gear of the engine substantially as and
for the purpose set forth.
Tenth. The combination with the pipe o of a three-way-cock a connection between
the said three-way-cock and the pressure water from an accumulator a discharge pipe
for the said three-way-cock and a connection between the plug of the said three-
way-cock substantially as and for the purpose, set forth.
Eleventh. The combination with the pipe o of a valve a connection between the
said valve and the pressure water from an accumulator, a discharge pipe o² and a
connection between the said valve and the plunger of an acumulator substantially as,
and for the purpose set forth.
Twelfth. The combination with the pipe o of a pipe entering the upper part of a
reservoir a pipe for conveying water and an overflow for the said reservoir and of a
discharge pipe o substantially as and for the purpose set forth.
Thirteenth. In steam engines with variable expansion (as distinguished from engines
connected with a system of gearing) the arrangement of a device between the lever
of a strongly static governor of great regulating power and the adjusting lever
regulating the cut off for transmitting the movement from the governor to the
regulating valve gear in such a manner that an adjustment by hand, or (in the case of
pumps) an automatic adjustment by means of the liquid will produce a change in the

page_text: relative positions of the device regulating the cut off in the steam cylinder on the
one hand and of the outward position of the weights of the governor proper on the
other hand without thereby altering the total proportion of transmission between the
movement of the governor weights or of the governor nut and the stroke or move-
ment of the device regulating the cut off for the purpose of producing variable rotary
speeds the steam inlet valves being kept entirely open and no recourse being had to
throttling of the steam.
Fourteenth. The combination with a steam engine of a governor and means for
securing great energy and an instantaneous action on the part of the said governor
substantially as and for the purpose set forth.
Fifteenth. The combination with a steam engine of a governor and means for
securing on as small a space as possible great energy and an instantaneous action
on the part of the said governor, substantially as and for the purpose set forth.
Sixteenth. In combination with a governor eccentrically suspended weights a
chamber arranged on the governor shaft so as to move freely thereon and surrounding
the said weights and a nut connected with the said chamber and with the regulating
gear of the steam engine substantially as and for the purpose set forth.
Seventeenth. In combination with a governor eccentrically suspended weights a
chamber arranged so as to move freely on the governor shaft and surrounding the
said cylindrical weights by means of interior horizontal top and bottom surfaces and a
nut connected with the said chamber and with the regulating valve gear of the steam
engine substantially as and for the purpose set forth.
Eighteenth. In combination with a governor eccentrically suspended weights a
chamber arranged so as to move freely on the governor shaft and resting upon the
said weights with its interior horizontal top surface and a nut connected with the said
chamber and with the regulating valve gear of the steam engine substantially as and
for the purpose set forth.
Nineteenth. In combination with a steam engine a governor having eccentrically
suspended cylindrical weights the upward and downward movements of which are
transmitted to a nut arranged on a chamber surrounding the governor shaft but
otherwise freely movable, the said chamber either surrounding the cylindrical
swinging weights by means of interior horizontal top and bottom surfaces or simply
resting on the said weights with an interior horizontal top surface substantially as and
for the purpose set forth.
Twentieth. In a steam engine the combination with the governor shaft Q of the
swinging weights N the chamber RV S the nut F and the devices F D C B for
transmitting movements to the regulating valve gear substantially as and for the
purpose set forth.
HASELTINE, LAKE & Co.,
45, Southampton Buildings, London, W.C., Agents for the Applicant.