IMPROVEMENTS IN INDIRECT-ACTING GOVERNORS
Year: 1876

page_text: LETTERS PATENT to Carl Pieper, of Dresden, in the Kingdom of Saxony, German
Empire, for the Invention of "IMPROVEMENTS IN INDIRECT-ACTING GOVERNORS."
A communication by Johann Georg Bodemer, of Zschopau, in the Kingdom
of Saxony, German Empire.
Sealed the 21st October 1876, and dated the 27th April 187
COMPLETE SPECIFICATION filed by the said Carl Pieper at the Office of the
Commissioners of Patents on the 27th April 1876.
CARL PIEPER, of Dresden, in the Kingdom of Saxony, German Empire. "IM-
PROVEMENTS IN INDIRECT-ACTING GOVERNORS." A communication by Johann
Georg Bodemer, of Zschopau, in the Kingdom of Saxony, German Empire.
The indirect-acting governors exercise their influence on the prime motor, to be
regulated through an intermediate apparatus, i.e., a regulator or communicator,
the, duty of which is to adapt the introduction of the dynamic medium (water,
steam, &c.) to the existing resistance by the adjustment of a sluice gate, a throttle
valve, an expansion valve, &c.
The regulator consists, for instance, of two loose pulleys, the one with an open
the other with a crossed strap, and a fast pulley between the two. In case now
the resistance decreases, the dynamic medium will produce an excess of power
(i.e., mechanical labour) over that requisite at the time being, and this excess will
cause an increase of speed for restoring the equilibrium between the produced and
the consumed power. In consequence the governor balls will rise and thereby
shift one of the straps, say, the open one, on to the fast pulley, so that the opening
of the sluice respectively of the throttle valve will be reduced. After a certain
lapse of time the sluice will be closed so far that its opening corresponds to the
power required to overcome the existing resistance at the normal speed. At this
moment the speed of the motor has certainly decreased, but it has not yet attained
its mean degree; it is yet too high on account of the circumstance that during the
increase of the speed the revolving masses have taken up an excess of vis-viva, which,
so far, has not yet been expended, and consequently continues to cause too high a
velocity. Meanwhile, the governor balls consequently remain raised and the sluice
is being closed further. The speed of the motor continues to decrease until the
governor balls in descending have arrived in their mean position, and have thereby
put the regulator out of action. At this moment the speed of the motor corre-
Prine S71

page_text: sponds to the mean speed, but the sluice has been closed too far already, as regards
the power required at the time, the speed must therefore yet become lower, and
consequently the regulator is put into action in a sense contrary to the former.
The decrease of speed caused in this manner by the governor may even surpass the
original increase, the fault being so much the greater as the sensibility of the
governor is smaller and the action of the regulator quicker.
The object of the present Invention is to reduce to a minimum these oscillations
of the speed consequent upon a disturbance of the equilibrium between force and
resistance. A governor, which is to fulfil this object, has to be designed according
to the following principles :-
1. It must put the regulator into full action in the required sense as soon as
the governor balls deviate but little from their mean position.
2. It has to keep the regulator in action in the same sense as long as the balls
continue to rise.
3. It has to put the regulator completely out of action immediately after the
governor balls have commenced to recede towards the mean position, as at this
period the position of the sluice will in general correspond to the required power,
although the normal speed is not yet attained.
4. It has to leave the regulator in inactivity whilst the balls are receding further
towards their mean position.
5. It must cause the regulator to renew its action in the original sense, in case
the balls should begin to increase their deviation from the mean position before
having arrived at the same.
The solution of this problem may be attained by different mechanisms which are
represented on the annexed two Sheets of Drawings in Figures 1 to 16.
The design of Fig. 1 may be the most suitable to elucidate the principle of the
Invention; a, a, is the sliding collar or yoke of a governor moving in vertical
guides, which yoke transmits its motion by means of rack and pinion to the two
spur wheel segments b and c placed in different vertical planes and combined with
each other, so that in the mean position b is the upper, c the lower part of the
entire wheel; f, g, is a lever, the arm fof which bears two teeth d and e, which
respectively gear together with the wheel segments b and c; g is a counterbalance
weight for f; and h is the lever which acts on the regulator, i.e., which in this case,
as shewn by the Drawing, shifts the straps; i and k are two weights fastened
respectively to ƒ and g by strings. As long as the lever f, g, is in horizontal
position both weights rest on a fixed support, but if the lever is lifted at one end,
the weight which is thereby lifted imparts to the former an inclination to return
into the horizontal position. If the speed of the engine increases the yoke of the
governor is raised, the combined wheel segments b and c turn in the direction of
the arrow, the first tooth of c lifts f by the tooth e, and moves the strap shifter
by the lever h. At a certain point which corresponds to but a slight deviation of
the governor from its mean position the tooth 1 of the segment c clears the tooth e,
but the lever h has already fully displaced the strap shifter, consequently the first
condition is fulfilled.
As. the governor rises further the tooth No. 2, after that
No. 3, and so on, will come into action, causing the strap shifter to oscillate
slightly it is truc, but without affecting the operation of the regulator; the second
condition therefore is also complied with. If the governor balls now descend the
wheel segment e need turn but for a small part of its circumference in the opposite
direction to let the lever f return to its horizontal position and to put the regulator
out of action; thereby the design corresponds to the third condition. The balls
descending further, the teeth of c, which, so far, have remained. above e, will yet
slightly depress this tooth, but not sufficiently to shift the strap to an effectual
amount; this answers to the demand of point 4. In case the governor does not
fully regain its mean position, so that, for instance, the teeth 3 and 4 of the
segment c embrace the tooth e (which latter is to be supposed in the position of
the Drawing) and the governor begin to rise again, the tooth 4 will immediately
raise the tooth e and exercise the same influence on the regulator as formerly,

page_text: tooth 1; hereby the fifth condition is fulfilled. In case of a diminution of speed
the combined segments b and c turn in the contrary direction, and the teeth of b
come into gear with the tooth d, the teeth of c being meanwhile inactive. The
operation of the apparatus is therefore in this case the same as before only in the
opposite sense. This arrangement may be modified by using racks either instead
of the spur wheel segments b and c or of the lever f. Also the weights i and k.
may be connected loosely to the lever f, g, in any other corresponding manner, or
they may be replaced by springs analogous to Fig. 2. Also the motion of the
segments b and c may be transmitted to the lever f, g, by friction under the con-
dition that the latter oscillates in moveable bearings pressed against the segments
by weights or springs.
The arrangement of Figures 2, 2 a, and 2b, is analogous to the former in the
essential points. The teeth of the segments b and c are here replaced by the
inclined planes 6 1,6 2, &c., and c1, c2, &c., whilst the incline d corresponds to the two
teeth and e of Fig. 1. The said planes b and c are fixed to a sliding bar, and
they are so acted upon from the governor by means of racks and spur wheels that
the stroke of these planes is increased in comparison to the lift of the governor.
The lever h carries at its end the part d inclined to the axis of oscillation c of the
lever, and the latter is pressed towards its centre position by the springs f and f¹.
During the time that the governor is in its mean position the incline d is situated
between the inclines b 1 and c 1. As the governor rises b1 pushes the incline d
towards the right, and the lever acting on the strap shifter causes a closing of
the sluice. The governor rising further, b1 slides past d, and b 2 comes into contact
with the same, after that b 3, and so on, but without altering the action of the
regulator. As soon, however, as the governor recedes d will slide through the
space between any pair of the inclined planes b so as to regain its centre position,
but it is here ready to resume its influence on the closing of the sluice as soon as
the governor may begin to rise again. If the inclines b and c are supposed to be
attached to the periphery of a cylinder, for instance of the wheel m, they represent
two short pieces of a screw with several threads. The arrangement consequently
may also be used in this modified form. But instead of a screw with several
threads one with a single thread divided into two parts may be employed, provided
that it revolves at a proportionately increased speed.
Another practical solution of the proposed problem is shown in Figures 3 to 3 f.
To the yoke a of the governor in this case is attached the piece b, having a cam
slot. With the yoke a a sliding bar c works together by friction. From the
sectional plan, Fig. 3f, it will be seen that c is attached to a by means of a dove-
tailed feather working in a corresponding groove, a spring serving to cause the
necessary amount of friction. h is a lever, the pin g at the upper end of which
projects into the slot f, whilst the lower arm of the same is embraced by a bend at
the lower end of the bar c.
It is to be observed that the slot f is wider than the diameter of the pin g, and
that it is so shaped that those parts of the outline of the same which lie nearer to
the centre line have a distance from the latter equal to the radius of the pin.
Fig. 3 shows the parts alluded to in their mean position.
Supposing, again, the regulator to consist of pulleys, &c., as before, the two straps
will run on the loose pulleys. Upon a decrease of resistance the balls of the
governor, and consequently the yoke a with the part b, will rise, the bar c will be
taken along with the latter by friction, and the lever h be shifted until the pin g
touches the left-hand side of the slot f, whereby it is arrested (see Fig. 3a). At
this position the strap operating the closing of the sluice, &c., has already been
completely shifted on to the fast pulley; the regulator is consequently in full action
according to the requirement of condition No. 1. The governor rising further, the
yoke certainly rises with it (see Fig. 36), but the bar c being arrested by the
resistance which the pin g finds in the slot f, and which overcomes the friction
between c and a, will remain in its place; therefore nothing is altered in the
operation of the regulator according to condition No. 2. But as soon as the governor

page_text: descends but a small amount, the yoke is at liberty to shift the bar c until the pin g
comes into contact with the right-hand side of the slot f; at this moment the centre
position of c as well as that of the strap shifter is attained, and the regulator is
stopped. This position, corresponding to condition No. 3, is shown in Fig. 3 c.
Condition No. 4 is fulfilled by the position of the bar c remaining unaltered by any
further descent of the governor towards its mean position, as the right-hand side of
the slot continues to arrest the pin-g, and to present a resistance against the
downward pressure on the bar (Fig. 3 d). The governor rising from its last position,
the bar e immediately shifts the pin g towards the left, and causes the regulator to
operate a closing of the sluice, as before (Fig. 3 e and condition No. 5).
In case of an increase of resistance or a decrease of the motive power, the
governor necessarily acts in the same manner in the contrary sense as in the first
design.
The Figures 4 a, 4b, and 4c show an arrangement similar to the foregoing, in
which however the two pieces b and b¹, with the slots fand f¹, and two levers h
and h¹ are required. The slots have a width equal to the diameter of the pins g
and g. The bar c has two lateral indents for the reception of the ends of the
levers h and h¹, as shown by Fig. 4a. The governor rising from its mean position,
represented by the Drawing, the yoke a rises with the bar c until the pin g has
come from its centre position, shown in the Drawing, into the lower part of the
slot f. As the latter is situated at the left of the vertical line passing through the
centre position of g, the bar e was at liberty to rise to a certain amount, but as soon
as g is pressed against the left-hand side of the slot, c cannot rise any further with
the yoke a, which latter however may continue to rise. Meanwhile on the other
side of the governor the lever h¹ was maintained in its place by the lower part of
the slot f, which corresponds with the centre position of the pin g¹, but this lever
presented no obstacle to the rising of the bar c, as the lower offset of the indent on
the right-hand side of the latter does not come into action. The governor receding
from an elevated position, the bar c is immediately shifted back to its own centre
position, being arrested by lever h¹, consequently the regulator is put out of opera-
tion by the projection d acting on the intermediate gear; the governor descending
further to within the mean position causes no subsequent motion of these parts.
The centre position of c is so far determined by the lever h¹, which is held by the
pin g¹ and the lower part of the slot f¹. The governor descending from its mean
position, the downward pressure of the bar c on the lever h¹ causes the pin g¹ to
enter into the upper part of f¹ bent towards the right (see Fig. 4 c). The lever turns
as much as the deviation of the upper part of the slot f from the centre line permits,
and limits the downward course of the bar c. Meanwhile the lever h remained at
rest in the centre position, as the upper part of the slot f corresponds with the centre
position of the pin g.
Fig. 5 shows in elevation and in plan a modification of the last arrangements.
The yoke a here acts by means of rack and pinion on a disc b with a cam groove f
which corresponds to the piece b with the slot f of Fig. 3. The bar c, Fig. 3, is
replaced by the disc c, which is pressed against the disc b by a spring, so as to
cause friction between the two. "Into the groove f the pin g fixed to the lever h
projects, and the motion of the disc c is transmitted to the lever h by a link e.
lower end of the lever h acts on the regulator the same as the projection on the
bar c, Fig. 3.
The
Whilst the motion of the bar c, Fig. 3, acted on from the yoke a by friction was
limited and regulated by the shape of the slot f, it is a cam disc b, which in the
modification of Fig. 6 answers the same purpose in an analogous manner. The
yoke a in ascending or descending turns the disc 6 by a certain angle respectively
to the right or to the left, which angle is not to surpass 180 degrees, and thereby
determines the stroke of the bar c the same as the slot fin Fig. 3, together with the
lever h, or as in Fig. 5 the groove f regulates the angular motion of the dise c. As
the Drawing shows, the radius of the disc b is on the one side larger than on the
other, and it is in direct relation to the bar e by the shoulders g and g¹ on the same.

page_text: This arrangement might be modified by applying two discs in a similar manner.as
in the design, Fig. 4. T'wo pieces b and b with slots have been introduced instead.
of the one of Fig. 3.
In the construction of Fig. 7 friction is an essential element, and in so far there
is a conformity between this one and the four preceding, but for the rest the
arrangement is different. The yoke a acts by means of rack, pinion, and wheel on
the rack b, which by its projection c can shift the bars d and d¹, the former between
the fixed points f and h, the latter between f and h². Two springs (which may be
replaced by weights) press these bars towards the centre. The two bars e and e¹,
provided with strap shifters and being in connection with d respectively, d' by
friction can only move between the points ƒ and g on the one side, and fand g¹ on
the other. The governor on rising will cause b by its projection c to shift the bar d
towards the left, and the latter takes the bar e along with it by the existing friction.
As soon as e has come into contact with g, the corresponding strap has been trans-
ferred on to the fast pulley so as to start the regulator for the closing of the sluice.
The governor may continue to rise until d touches h (not taking into account
the thickness and the tension of the spring). The governor in receding causes b to
recede, also the bar d follows by the pressure of the spring, draws e along with
it, and the latter transfers the strap back on to the loose pulley. After this the
governor may continue to descend, as the bar d has yet to travel a considerable
distance until it again touches f. In case the governor should meanwhile begin to
reascend, e will immediately be drawn again to the left so as to repeat its action on
the regulator. The operation of the other part of the apparatus is of course quite
analogous.
Against the arrangements described so far an objection however may be raised;
suppose the governor to have ascended so as to have put the regulator into action,
in case it now recedes a small distance, but sufficiently to put the regulator out of
operation, it may then continue to revolve in too high (or on the other side too low)
a position, so as not to return the motor to its mean speed. In consideration of
this circumstance I have been induced to search for devices which correspond not
only to the five conditions laid down in the introduction, but which also fulfil the
sixth condition :-6. "In case the balls do not return fully to their mean position
the governor has to put the regulator repeatedly into operation, until the mean
position of the former is attained."
Fig. 8 shows an arrangement by which this condition is fulfilled, as well as those
laid down formerly.
The yoke a of the governor acts by means of rack, toothed sector, and lever b
on the friction coupling clutch c. The latter slides longitudinally on the shaft, but
it transmits its rotation to the same by groove and feather, whilst the shaft acts on
a sluice or an expansion valve, &c., by a worm and the worm wheel f. The boss
of the coupling clutch d is lengthened to a tube on which is fitted the tube with
the pulley, but with the interposition of a feather, so that both revolve together.
The tube g is placed in the bearing h, and on it is fixed the worm 1, which gears
into the worm wheel m connected to the ratchet wheel n. is a spring, the object
of which is to push the coupling part.d so far towards the centre as the bar p and
the stop 7 permit. The governor rising, c will be pressed against d, so that the
continuous rotation of the pulley k will be transmitted through g, d, and c to e, and
consequently to f, and the opening of the sluice will be decreased; at the same time
d, and also the bar p, have been pushed back, the ratch o has slipped over the
inclined teeth of n, as it was at liberty to recede on account of a spring placed
behind the same. The wheel n now retains the ratch o, as well as p and d, but as
the wheel m is slowly moved to the left by the worm the spring is free to shift
the aforesaid parts towards the left, according to the circumferential speed of n,
until p is stopped by q. In case the speed with which the governor receded from
its highest towards its mean position surpassed the speed with which d followed the
same, c and d so long remained out of contact with each other, and the worm
wheel was at rest; but in case the governor continued to revolve a short time in

page_text: too high a position the coupling part & necessarily had to overtake the other part-c
after a certain number of seconds, so as to put it and also into renewed rotation
until the governor descended further. It is this overtaking and the repetition of
action in which consists the peculiarity of the construction and the fulfilment of the
given condition
The worm wheel'm, the ratchet wheel n, and the parts combined with the same
for causing a comparatively slow return motion of the coupling part d may be
replaced by a cataract, the weighted piston of which is free to rise by the opening
of a valve, but which in allowing water or other fluid to escape through a small
hole slowly descends, and by interposition of a bell-crank lever operates a corre-
sponding receding motion of the coupling part d. Whilst in the described arrange-
ment a certain time, however short, elapses until the governor, after having
descended and rising again, shifts the coupling part e far enough so as to meet the
part d, which is slowly returning towards the centre position, and to put the
wheel into renewed rotation for operating a closing of the sluice; the latter is
effected immediately after the governor has commenced to rise again in the following
arrangement, represented in Figures 9 to 15-Fig. 9 is a side view; Fig. 10, a
front view; Fig. 11 and 12 are horizontal sections respectively, according to A, B,
and C, D; Fig. 13 is a section according to G, H, of Fig. 11; Fig. 14 is a partial
view from the top, and Fig. 15 plan of friction sheaves, &c.
The construction of the yoke a, the piece b, the bar c, and the lever h, corresponds
to the arrangement of Fig. 3, described formerly, but the action of the same on the
regulator is different. The bar c does not move the strap shifter directly, but it
arrests by its projection d the rotation of a shaft t. The latter bears at its lower
end a friction sheave wl, with which another friction sheave w fixed on the spindle
of the governor is in relation. The sheave w¹ has on its circumference four shallow
concavities, the positions of which correspond with the arms u, u¹, u", and u¹¹¹, of
the cross at the top of the shaft. If one of these concavities is turned towards the
sheave w the sheave w¹ is at rest; on the latter there are four pins z, z¹, 2¹¹, and 2111,
on which a lever y and a spring attached to it act in the manner that the sheave
has the tendency to turn in the direction of the arrow. In the position of the
drawing it is however prevented from moving by the arm u. x is an excentric
which puts the regulator into operation in one sense or the other, or which
arrests it. The governor balls rising from their mean position the projection d of
the bar c ascends and liberates the arm u; at the same moment the lever y pressing
on the pin shifts the sheave w' so far forward that w engages with the corre-
sponding part of the full periphery of w¹ and turns this sheave a quarter of a
circle; at the same time the excentric moves by the same angle and puts the
regulator into gear for closing; consequently the operation of the latter commences
as soon as the yoke a and the bar c have risen to the amount of the thickness of
the projection d. In the moment that the second concavity of w arrives opposite
to the sheave w the cam u¹, placed higher than u to the amount of the thickness
of d, arrests the motion again, the second pin has slipped over the lever y, so
that the latter imparts to w³ a renewed tendency to engage with w.
The governor
may now rise further without altering the operation of the regulator. Upon the
descent of the governor from a point above the mean position, d liberates the arm u¹,
the shaft t turns again as before a quarter of a circle, and the regulator is stopped. A
further descent towards the centre position is without influence on the regulator,
but a renewed ascent will cause the same to be put into operation again for closing,
the shaft t having to make three-quarters of a revolution in this case; the action
of the governor below its mean position is necessarily similar. So far the operation
of the governor is independent of the rest of the mechanism contained in the
Figures, and it answers only to the five conditions laid down in the beginning. This
additional mechanism now serves to put the regulator repeatedly into action in
case the governor, after having begun to recede, continues to rotate in too high or
too low a position.
On the back of the voke of the governor the nisse 41 with the alat £1 Fice 12 ia

page_text: fixed, into which a pin projects without appreciable play. This pin is fixed to the
lever opposite to the horizontal arm k of which, on the front side of the governor,
there is a lever embracing with its forked end the edge of a disc v fixed on the
shaft t. This disc consists for each quarter of its circumference alternately of a right
and a left-hand screw-thread; the high and the low points of which (with regard
to the lever ) correspond with the points of rest of the shaft t. Between these two
levers and, and supported by them on conical centres or in loosely fitting bear-
ings, a spindle m revolves; the latter bears the spur wheel o and the worm wheel n.
and are two worms, the upper with right-hand the lower with left-hand thread,
which by the two spur wheels, q and q', gearing together, are brought into rotation,
the one in the opposite sense of the other. These wheels are driven continuously by a
strap running over the pulley p. In its centre position n does not gear into either
of the worms and . Below m the spindle m', Fig. 12, turns on fixed centres; the
same bears the spur wheel of which gears into the wheel o as long as the latter is in
its lower position. On this spindle is also fixed the tappet discs (drawn separately
under Fig. 12), which, having a greater weight on one side, tends to assume the
position of the Drawing, but which, according to the action of the other parts, shifts
the bar c up or down by one of its tappets coming into contact with the projection e
of the bar.
The operation of the different parts is as follows:-Suppose the governor to have
put the regulator out of action on the return from its attained highest point; if it
now stops receding, i.e., if it continues to revolve above its mean position, so that its
own speed and that of the motor are yet too high, the renewed action of the regu-
lator for the further closing of the sluice has to be caused by other means. In this
too high position the lower part of the slot f¹ in the piece b¹, Fig. 13, has shifted
the lever towards the left, consequently I has been raised and n has come into
gear with r.
On condition that the pulley p turns to the right the wheel n will
revolve to the left. The shaft t stands in a position that the arm u¹¹ bears against
d; therefore one of the low points of the disc vis in front in Fig. 9, or towards the
left, in Fig. 10, and consequently o is in gear with o¹. The lower tappet of s must
therefore rise to push e upwards, so that the projection d slides past the arm u", the
shaft t in consequence turns, and in this case three-quarters of a revolution, as it is
not arrested before u¹ strikes on d. Meanwhile the excentric has certainly started the
regulator a moment for the opening of the sluice, but immediately after it has made
it pass over its point of rest to its position for closing. As the arm u¹ is in con-
tact with d a high point of v, in Fig. 9, is in front, the lever is lifted, o is out of
gear with o', and s is caused to return into the position of the drawing on account
of its centre of gravity being on one side. The regulator will now continue to close
the sluice until the governor has again descended by a certain amount, and the
starting of the same will be repeated until the governor has reached its mean posi-
tion. It may yet be observed that the spindle mon being raised or lowered on one
sideor the other will ever be at a certain incline, but the deviation is too small to be of
prejudicial influence on condition that this circumstance has been duly taken into
consideration in the design, as is the case in the Drawing. The slot fi corresponds
with the centre line for its middle part; the correcting arrangement will therefore not
be put into operation at a slight deviation of the governor from its mean position.
In case of the continuation of a too low speed the worm, with left-hand thread,
comes into action. According to the Drawing this worm acts on the same worm
wheel as the right-hand threaded worm 1. This construction may be objected to,
but by applying two worn wheels close to each other, and by shifting the worms
slightly, the one to the right the other to the left, this incorrectness is easily to be
overcome. Another arrangement of correcting apparatus is shown by Fig. 16. The
same is combined with the arrangement of Fig. 7, the parts a, b, d, f, g, and h, of
which have been retained unaltered. To the part e, however, a ratch i has been
attached, which is kept in gear with the corresponding part of a lever k. The lower
end of serves as strap shifter, or the latter may be connected to the lever in any

page_text: other manner.
A weight imparts to the strap shifter the tendency to be moved
towards the pulley for operating the closing of the sluice. The disc m permits the
motion of the lever towards the right only as long as the part of the smaller radius
is turned towards the projection n. p is a pulley, which is put into rotation in any
suitable manner whilst the strap shifter is opposite to the loose pulley. q is a pin
fixed to the same, by means of which the ratch i is lifted out of gear with at
every revolution of p, so as to give the weight 7 the liberty to draw the lever k to
the right. The motion of the disc m is dependent upon that of the yoke of the
.governor.
Taking into account the former explanations the operation of this arrangement
will easily be understood. If the governor on receding remains in too high a posi-
tion e, i, and the upper end of k are shifted back to the right, and the regulator is
inactive. If this state continues until the pin 7 lifts the ratch i the weight / then
draws the strap shifter to the right, and the sluice is being closed further. During
a decrease of speed the other part of the apparatus is in action but to prevent the
left-hand part to cause a disturbance; meanwhile the disc m has to be turned by the
yoke of the governor, so as to make a shifting of the lever & impossible.
The mechanical arrangements described in the foregoing may be used with
advantage under certain conditions for regulating the height of water in the head
race of a hydraulic motor working coupled with another motor, the speed of which
latter is regulated automatically. In case the supply of water to the former is
irregular, then the opening of the sluice remaining unaltered at one period more
water will be used than is supplied at another, water will run off through the outlet
channel without being utilized. In the first case the water level will therefore
become lower, in the latter it will rise at the beginning. These variations may be
reduced to a minimum by one of the described mechanisms. For this purpose the
balls of the governor are detached, and a float on the surface of the water in the
head race is so combined with the yoke of the governor, that the former in rising
and sinking will respectively cause the regulator to operate an opening and a closing
of the sluice. This will then be peformed under the same conditions as formerly by
the balls, but in the inverted sense. The height of water, for instance increasing,
the regulator will immediately be put into gear for raising the sluice so as to
let pass the increased volume of water and to utilize the same. The operation of
raising continues as long as the water rises, but as soon as a falling of the same has
commenced the raising of the sluice will be discontinued, as at this period its
position may be assumed to correspond to the volume of water supplied.
The regulators as at present in use not only begin their operation too late, but
they continue to raise the sluice until the surface of the water has fallen to its mean
level, the opening thereby becoming too great.
The variations in the power developed by the hydraulic motor, which result from
the variations of the quantity of water that comes into action, have to be com-
pensated by the second motor (steam engine, &c.) and its governor.
Having now described the object of my Invention and different arrangements by
which the same may be carried out in practice, I wish it to be understood that I do
not claim all the details described in this Specification, as they may be varied
without departing from the nature and the principles of the Invention, but I
claim,―
1. The combination with a govenor of the two spur or friction wheel segments b
and c, Figure 1, or their equivalents gearing together with one end of the lever f, g,
or its equivalent provided with the weights i and k or corresponding springs, as
and for the purpose described.
2. The application to a govenor of two or more inclines b', 62, 63, &c., and c¹, c²,
c3, &c., Figure 2, either working in straight lines or placed on the circumference of
an oscillating cylinder in combination with the moveable incline d, as specified.
3. The bar c, Figures 3, 4, and 6, acted on directly or indirectly by the yoke a or
sliding collar of the governor by friction in combination with the cam slot ƒ and

page_text: lever h, Figure 3, or the two cam slots fand f¹, and levers h and h¹, Figure 4, or
one or two cam discs b, Figure 6, or any equivalents of these slots or discs or other
parts, as and for the purpose specified.
4. The disc b, Figure 5, receiving motion from the yoke or sliding collar of the
govenor and acting on the disc c by friction, combined with the cam groove f in
the disc b, the lever h and the rod e or their equivalents, as described above.
5. The bars & and d', Figure 7, moved by the govenor, and acting by friction on
the bars e and e¹ or their equivalents, as specified.
6. In the arrangement Figure 8, the coupling parts c, d, and d¹ in combination with
the springs and, the worms and , the worm wheels m and m¹, the ratchet
wheels n and n¹, the ratchets o and o¹, and the bars p and p¹, or the equivalents of
all these parts, such as, for instance, the cataract alluded to above, as and for the
purpose described.
7. In the modification shewn in Figures 9 to 15, the arms u, u¹, u", u¹¹¹, on the
shaft t combined with the bar c, the friction sheaves w, w₁, the lever y and the
excentric or their equivalents, as and for the purpose described.
8. In the govenor shewn in Figures 9 to 15, the correcting mechanism acting
on the bar c by the combined influence of the disc on the one hand, and the
slot f', the worms and ", and the worm wheel n on the other hand, on the spur
wheels o and o¹, and lastly, on the tappet disc s, all of which parts may be replaced
by others of the same mechanical value, as and for the purpose specified.
9. In the correcting mechanism shewn in Figure 16, the combination of the ratch i,
the lever, the cam disc m, and the rotating disc p, with the pin q or their
equivalents, as described and for the object stated.
10. The transmission of action from the yoke or sliding collar of a govenor to
the regulator of sluice gates, steam valves, &c. by means of one of the described
mechanisms or other constructions of equivalent mechanical value for the purpose of
fulfilling either the five conditions enumerated alone, or these together with the
sixth condition specified above.
In witness whereof, I, the said Carl Pieper, have hereunto set my hand and
seal, this Twenty-fifth day of April, in the year of our Lord One thousand
eight hundred and seventy-six.