Improvements in Speed Regulators or Governors.
Year: 1893

page_text: Date of Application, 21st Dec., 1893-Accepted, 24th Feb., 1894
COMPLETE SPECIFICATION.
Improvements in Speed Regulators or Governors.
I, FRÉDÉRIC ALBERT WEYHER of Pantin (Seine) in the Republic of France
Mechanical Engineer do hereby declare the nature of this invention and in what
manner the same is to be performed to be particularly described and ascertained in
and by the following statement:-
The improved speed regulator or governor forming the object of my invention is
based upon the utilisation of the variations in the vis viva or force of momentum
produced by variations or changes of speed of a moving body or in other terms upon
the direct utilisation of the forces due to the inertia of a mass or weight moving at
different or changing speeds.
"
This direct utilisation of the forces of inertia for regulating purposes has for its
principal object and advantages (in addition to others hereinafter specified) the
protection of the regulating mass or weight hereinafter referred to as the "weight"
from the influence of all forces other than those which are directly utilised in the
operation of the apparatus.
When, in order to elucidate the foregoing statement, we compare the regulating
apparatus or governor forming the object of my invention with an ordinary
centrifugal governor for example this being the type most commonly employed for
regulating or controlling speed we find that in the centrifugal governor the
regulating action depends on the centrifugal force of moving weights or pendulums.
Now the disturbing actions or influences which render the action of centrifugal
force more or less defective for the purposes of regulation are as follows: namely-
1. The inertia of the regulating weights or pendulums and of their counter-
weights.
2. The frictional resistance of the several moving parts.
In the improved governor constructed according to my invention the regulating
action is produced by the inertia of the moving weights. Disturbing influences are
nonexistent the inertia of the parts and the friction co-operate in obtaining the
normal working of the regulating action without introducing any disturbing
influence.
The means employed according to this invention for utilising for regulating or
governing purposes the variations in the momentum (or vis vira) of a weight moving
at different speeds are the following namely:-
A heavy weight is engaged between two drivers which alternately impel it in
opposite directions so as to impart to it a reciprocating or oscillating motion.
This reciprocating movement necessarily involves variations in speed or rate of
motion of the weight the direction of the motion being changed or reversed at each
oscillation. These variations in the speed modify the momentum or impetus of the
weight and cause it to exert correspondingly varying reactions or forces upon the
drivers. The value of these reactions as exerted on each driver passes from zero to a
maximum and from the maximum to zero in the course of each double oscillation.
One of the drivers is applied to the weight by a constant and predetermined
pressure less than the maximum force exerted by the weight upon this driver by
reason of its inertia during one normal oscillation. This driver is consequently
displaced at each oscillation during the whole of the time during which the force of
inertia of the weight is greater than the force applied to it by the driver. This
displacement is consequently proportionate to the force of inertia of the weight and
consequently proportionate to the square of the speed.
The other or second driver is moveable and subject to two movements, on the
one hand it moves with the weight when the first driver yields to the force of

page_text: inertia and afterwards prevents the weight from returning to its original position
when the force of inertia ceases to be greater than the force by which the first
driver is applied to the weight; on the other hand it is brought back or caused to
return at each oscillation, by a movement in the opposite direction to the first
movement, to an extent which is constant or uniform and is independent of the
forces of inertia and of the speed.
In short the first driver acts with constant force and is subjected to an extent of
displacement varying with the square of the speed and the second driver is
constantly displaced in the opposite direction to the first and exerts a force
varying with the square of the speed. This second driver moreover partakes of
the variable displacements of the first driver moving in the same direction as the.
latter.
The action of the apparatus is as follows:-
The weight partakes of an oscillating motion which is communicated to it by the
intervention of the two drivers. This oscillating motion develops in each driver
reactions due to the inertia of the weight which cause a displacement of the first
driver and consequently of the weight and of the second driver to a variable
extent proportionate to the forces of inertia that is to say to the square of the
speed.
The second driver and consequently the weight and the first driver are subject
to a constant displacement in an opposite direction to the first. This displacement
is regulated by a direct transmission of motion and is independent of the forces of
inertia and of speed.
When these two displacements (variable displacement and constant displacement
in the opposite direction) are equal the weight performs in space during the
forward and backward movement of one oscillation two similar movements corre-
ponding in each direction with the length of the oscillation proper plus one of the
two displacements.
This condition corresponds with the normal speed of the motor or engine which
is to be maintained by the action of the regulator or governor.
The displacement of the second driver being constant and that of the first being
a function of the speed and of the force with which this driver is applied to the
mass the normal speed to be maintained by the action of the governor may be
regulated as required by suitably adjusting the force with which the first driver is
applied to the weight.
The governor working at normal speed and the displacement of the weight being
equal in both directions the displacement of the first driver increases when the
speed is accelerated. The displacement of the second driver being constant, the
limits of the movement of the weight are displaced to an extent equal to the excess
of the displacement of the first driver over its normal displacement. Each
oscillation thus contributes to displace the limits of the movement of the weight
until the normal speed is regained. At this moment the displacements of the two
drivers again become equal and the oscillations of the weight again become similar
to those which it described before the disturbance took place but the limits of its
movement occupy in space a position different from that which they occupied
before the disturbance.
When the speed diminishes in place of increasing the displacement of the first
driver diminishes. The displacement of the second driver being constant the limits
of the movements of the weight are displaced as in the preceding instance but in
the opposite direction to an extent equal to the difference between the displacement
of the first driver and its normal displacement.
This displacement of the limits of motion of the weight takes place at each
oscillation until the normal speed has been regained.
All changes from the normal speed consequently have the effect of displacing in
space the limits of the movements of the weight and this displacement is utilized for
actuating devices employed for restoring the normal speed such for example as the
distribution valve or throttle valve of a steam engine.

page_text: By these means the variations in the momentum of a weight moved at variable
speeds are utilized for controlling speed by means of the displacement of the limits
of the movement of the weight partaking of an oscillating motion this oscillating
motion being communicated to the weight in one direction by a driver having a
constant force and a displacement varying in proportion to the square of the speed
under the action of the force of inertia and in the opposite direction by a second
driver having a constant displacement which is independent of the speed and of the
force of inertia.
And in order that my said invention may be fully understood I shall now proceed
more particularly to describe the same and for that purpose shall refer to the
several figures on the annexed sheets of drawings the same letters of reference
indicating corresponding parts in all the figures.
Figure 1 of the accompanying drawings illustrates in elevation a simple
arrangement of apparatus or speed governor constructed according to my invention.
Figure 2 is a diagram shewing the force or reaction exerted by the weight of
the governor upon each of the drivers.
Figures 3 and 4 represent in section and in side elevation respectively a modifi-
cation in the construction of the governor according to which the regulating
weight partakes of a circular motion.
Figures 5 and 6 illustrate this modification in elevation and partly in section with
the parts occupying different relative positions.
Figures 7, 8 and 9 illustrate this arrangement in section the sections being taken
on the lines 1-2, 3-4, and 5-6 respectively in Figures 3 and 5.
Figure 10 illustrates a detail of the apparatus in section on the line 7-8
Figure 9.
Figure 11 illustrates in elevation a modification of the part employed for
actuating the regulating device.
Figures 12 to 18 illustrate other modifications in the construction of the governor
as hereinafter described.
The governor illustrated in Figure 1 is provided with a weight a supported upon
a rod b on which it is capable of sliding longitudinally, a spring c (constituting the
driver hereinbefore referred to as acting with constant force the tension or stress
of this spring being equal to the force X hereinafter referred to), and a pawl d
connected to the weight a being caused by the action of a spring to engage with a
screw thread provided on the rod b so as to act as the second driver. The weight a
is connected by a rod e with the controlling device consisting of the throttle or
expansion valve of the steam engine for example.
The rod 6 is supported by lever arms factuated by suitable mechanism for
transmitting motion worked by the engine or motor to be governed and imparting
a vibrating or oscillating motion or movement to the said arms. This movement
is transmitted to the weight a through the intervention of the spring c and pawl d.
The rod 6 also receives through suitable mechanism worked by the motor or engine
to be governed a rotary motion which displaces the pawl d acting in the same way
as a nut to a regulated distance in the opposite direction to that indicated by the
arrow y.
We will now proceed to consider with reference to the diagram (Figure 2) the
forces or reactions exerted by the weight a upon each of the drivers.
Those points in the curved line represented in this diagram (Figure 2) where
the said line bisects a straight line Z correspond with the moments at which these
forces are nil owing to their change of direction. The parts of the curved line
situated above the straight line Z represent the forces exerted upon one of the
drivers and those situated below the line Z represent the forces exerted upon the
other driver. Assuming that the parts situated above the line Z represent
the force of inertia exerted upon the driver which acts with constant force for
example the extreme constant distance W of the part of this curve farthest from
the line Z represents the maximum force which the inertia of the weight would
exert upon.this driver if it were stationary. The constant force with which this

page_text: :
driver is applied to the weight will be according to the foregoing statement inferior
to the force W. Let it be equal to a force represented by the line ✗ for example.
At the moment when the weight passes to the point corresponding with this
force X there will be equilibrium between this force applying the driver to the
weight and that due to inertia by which the weight a is applied to the driver. The
weight a will consequently be displaced beyond this position carrying the two
drivers with it as hereinbefore explained.
We will now proceed to consider further the two movements of the rod b. The
first of these two movements namely that of oscillation transmitting motion to the
weight a produces upon the spring cand upon the driving pawl d the reactions
represented by the curved line in Figure 2. When the force of the reaction upon
the spring c exceeds the tension or pressure of this spring the latter yields and the
weight a slides upon the rod 6 in the direction of the arrow y drawing the pawl d
with it. At the end of the sliding movement or displacement of the weight a upon
the rod b the pawl d has slipped over the screw threads and moved along this rod
to a distance equal to three threads of the screw for example when the speed is
normal. It then re-engages with the threads and consequently prevents the
weight a which has been displaced and has compressed the spring e from returning
to its former position under the action of this spring when the reaction due to inertia
again becomes inferior to the tension of the spring.
The second movement of the rod b namely the rotary movement produces as
hereinbefore explained a displacement of the pawl d and this displacement is equal
to that of the weight a upon the rod 6 in the direction of the arrow y at normal
speed being consequently equal to the width of three screw threads.
As the result of the combined or successive action of these two displacements
'the weight at the end of one double oscillation returns to the same position which
it occupied at the commencement.
When the speed increases the first displacement due to inertia of the weight is
greater being augmented to say four threads for example in place of three in the
direction of the arrow y. The displacement in the opposite direction being
constant the limits of the movement of the weight a are now moved to the extent
of one thread in the direction of the arrow y. This movement causes the weight a
to act in a suitable manner through the rod e upon the regulating device of the
motor and restore the latter to the normal speed. A similar effect is produced but
in the opposite direction when the speed diminishes.
The tension of the spring c is maintained (by suitably proportioning the same)
practically constant in all positions. The displacement of the limits of the move-
ment of the weight a upon the rod consequently continues in case of any
continued disturbance or irregularity until the speed has recovered its normal rate
it being only at this rate of speed that the movements of the weight a upon the
rod b are equal in both directions.
The governor herein before described and illustrated in Figure 1 in its original
or most simple form is preferably constructed in practice in a form such as that
represented in Figures 3 to 10 which enable the same principle to be applied with
more advantage in practice.
As represented in these figures the regulating weight a is of circular shape
being in the form of a fly wheel and capable of rotating freely upon two annular
bearings 9 on which it is supported by rings or cups h working on anti-friction
balls. This fly wheel carries a toothed ring engaging with driving pawls d.
These pawls are carried by a sleeve i loose upon a tubej attached to a drum k and
capable of rotating upon the said tube. An endless screw or worm / gears with
a worm wheel m fixed ou the sleeve
working in two bearings carried by the
shaft n upon which it is tree to rotate.
movement to the drum k.
This worm is carried by a shaft
drums k. This drum is supported by a
A connecting rod o imparts an oscillating
The regulating weight or fly wheel a carries a stud or shaft p connected by a
rod to one extremity of a levers the other extremity of which is supported by

page_text: a pint attached to the drum k. The lever is connected by a pin u situated
nearly in a line with the central shaft or axis n to a connecting rod v, acted on
by a spring c, which constantly tends to move the said rod upwards or in the
direction of the arrow y' (Figure 4). The tension or stress of this spring is
transmitted through the lever s, and rod r to the regulating weight or fly wheel a,
and acts upon the latter in a direction tangential to its circumference. This force
is applied in a direction which tends to press the teeth of the toothed ring b
against the pawls d. The regulating weight a is consequently engaged between
two drivers acting similarly to the two hereinbefore described one of the said
drivers being formed by the spring e and the other by the pawl or pawls d.
The angle or inclination of the lever s and that of the rod r, are adjusted in
such a manner that the pressure of the spring e, which varies according to the
compression of the spring, produces a constant force exerted at the circumference
of the fly wheel or weight a, within the limits of the movements of the parts.
The oscillating movement communicated in the direction of the arrow y to the
drum & by the connecting rod o, is transmitted by the intervention of the worm 1,
to the wheel m sleeve i, pawls d, and to the weight a. This weight then exerts
upon the driver acting with constant force or pressure formed by the spring c,
reactions which vary with the square of the speed according to the curves in
Figure 2. When this force of reaction exceeds the tension of the spring (repre-
sented by Figure 2,) the latter yields and the weight a, becomes displaced, that is
to say in addition to the general oscillating motion of the system in which it
participates, it rotates upon the rings or bearings g. The toothed ring b, then
moves relatively to the pawls d, to an extent of say three teeth, for example in
the direction of the arrow y. The pawls d, prevent the weight a from returning
to its former position under the action of the spring e, when the force of inertia
again becomes inferior to the pressure or tension X of the said spring.
A ratchet wheel (Fig. 10) is fixed upon the shaft of the worm l. A pawl or
driver m' is worked by a connecting rod n¹ and the lever o vibrating on a pin p¹
carried by the drum k. The other arm or extremity of the lever o' is connected by
a rod with a fixed pin or pivot s'. This pin or centre being stationary_the
oscillations of the drum k, cause the lever o¹ to oscillate upon the centre p'. This
movement produces by the intervention of the pawl or driver m', a rotary motion of
the worm, which displaces the pawls d, in the opposite direction to that indicared
by the arrow y to an extent which is fixed and constant, being independent of
the force of inertia and depending exclusively upon the angle of oscillation of the
drum k. This displacement of the pawls d, in the direction opposite to that of the
arrow y produces a corresponding movement of the weight a in this direction.
When the motor is running at normal speed this movement is equal to the previous
displacement of the weight a in the direction of the arrow y, which is assumed in
the present instance to be equal to three teeth of the ring b.
In the course of one double oscillation of the drum k, which actuates all the
other parts of the governor, the weight a assuming the speed to be normal, is
displaced upon the bearings g, as follows viz. :-
(1) In the direction of the arrow y to an extent equivalent to 3 teeth of the
ring 6 by the action of the forces of inertia resulting from the variations in the
speed.
(2) In the opposite direction to the arrow y to an extent likewise equivalent
to 3 teeth of the ring by the action of the worm I, worked by the pawl or
driver m² and lever o¹.
In case the speed increases beyond the proper limits the reactions due to
inertia become correspondingly greater or more powerful-the first displacement
increases and becomes equal to 4 teeth of the ring for example. The second
displacement being unchanged or constant, the limits of the motion of the weight a
are moved about the central axis n until the normal rate of speed has been
resumed.
When the speed diminishes, the same action takes place in the opposite direction.

page_text: As the result of the position of the pin or centre u, which is practically in line
with the main or central shaft n, the said centre does not become displaced laterally
by the oscillation of the drum k.
This oscillation simply produces a partial rotation of the pin u, and does not act
upon the connecting rod v. On the other hand the rotation of the weight a upon
the bearings g, cause the levers to vibrate within the limits or between the two
extreme positions, represented by the dotted centre lines in Figures 4 and 5. This
vibrating movement is transmitted directly to the connecting rod v. It may be
utilised for actuating the regulating devices (throttle valves expansion valves and
the like).
These devices may also be actuated by means of a connecting rod directly
connected to any suitable part of the weight a, the rotation of the said weight
upon the bearings y, having the effect of displacing the trajectory or line described
by the extremity of the said rod. The regulating devices may also, as represented
in Figure 11, be worked by the extremity of a lever centred at 1 upon the
drum, and pivotally connected at k', to the weight u or vice versa.
The spring e acts upon the connecting rod v, at the extremity c¹. The other
extremity of the said spring bears upon a screwed sleeve or guide (Figure 3)
provided with a hand wheel o³, which enables the tension or pressure of the spring
to be adjusted for the purpose of changing the normal speed, which is to be
maintained by the action of the apparatus.
Moreover by completely lowering the guide c² into the position represented in
Figure 6 its lower extremity can be caused to bear upon a shoulder e¹ formed upon
the rod so as to retain the weight a of the governor in one of the extreme
positions, being for example the position which corresponds with the stoppage of
the engine controlled by the said governor.
The force represented by the line X, Figure 2, (which balances the reactions
exerted by the inertin of the regulating weight upon the driver acting with constant
force until the moment when the weight is displaced in overcoming, this force) is
not exclusively produced by the tension of the spring c, but is derived from
3 sources namely,
(1) The tension of the said spring
(2) The resistance due to the inertia of the accessory parts transmitting the
movement resulting from the displacement of the weight to the regulating devices,
and
(3) The friction of the moving parts actuated by the regulating or governing
action of the apparatus.
The two first of these 3 elements are constant or invariable, the third is likewise
practically constant, its fluctuations being quite insignificant relatively to the total
force X (Figure 2). This is what is herein before referred to in the statement,
setting forth that all disturbing actions are obviated in the improved governor, the
friction and inertia of the parts which are elements of irregularity in the centrifugal
governor, being directly utilised in the present apparatus and caused to contribute
to the normal action of the governor.
An additional advantage of the improved apparatus is the following namely :-
In the centrifugal governors heretofore employed for regulating the speed of
steam engines and other like motors the disturbing action of the friction must
always be sufficient to cause the fluctuations of speed, which occur during one
revolution of the shaft to have no effect upon the governor in order to obviate
oscillations of the latter. In the improved governor on the other hand, the
fluctuations or variations in speed which arise during one revolution of the shaft
have no effect upon the governor, the controlling weight of the latter not being in
constant equilibrium like the weights of the centrifugal governor. The condition
of equilibrium exists momentarily only at the precise moment, in which the reaction
exerted by the inertia of the weight upon the driver acting with constant force is
equal to the force X in Figure 2. In all other positions one of the two forces is
in excess over the other. The governor is consequently influenced solely by the

page_text: variations in the normal speed which cause corresponding variations in the
governor at the moment when it is in equilibrium.
This condition combined with the absence of disturbing forces hereinbefore
referred to enables a mathematically constant or uniform speed to be obtained in
all positions of the improved governor.
According to the modification illustrated in Figure 12, the spring c is subjected
to tensional force, in place of compressing force but the action is the same as in the
arrangements illustrated in Figures 3 to 10 as will be readily understood by
reference to the drawing, without further explanation.
Figure 13, illustrates a modification of this arrangement in which a counter-
weight and lever acting in the same direction are simply substituted for the
spring c.
According to the arrangement illustrated in section, and in elevation respectively
in Figures 14 and 15, a spirally coiled spring t is employed to perform the
functions of the spring c, herein before described, one extremity of the said spring t
being connected with the sleeve or tube j, and the other extremity being attached
to the pin or centre p, on the weight a.
Figures 16 and 17 illustrate in sections taken in planes, at right angles to one
another a modified arrangement of the driving pawls d, which in this case act by
friction. In place of engaging with the teeth of a toothed ring, they are so formed
that the rotation of the mass a, in the direction of the arrow y tends to take them
off the sleeve, i, and allow the weight to rotate independently but when the
weight a rotates in the opposite direction to the arrow the pawls or drivers
resist this motion being wedged against the sleeve i. Springs are provided as
represented in Figure 16 for the purpose of maintaining the drivers in contact
with the said sleeve.
Figure 18, illustrates in elevation an arrangement in which the regulating weight
is divided into two parts a and a¹. Two ratchet toothed wheels" and are
connected together, and a lever g' partakes of an oscillating motion which is
communicated to it by a connecting rod 4. Driving pawls are suspended on
centres carried by this lever and are connected by rods with a fixed point or
stationary centre . In consequence of this arrangement the two pawls are .
caused to act upon the teeth of the wheel and slip over them alternately.
The weights a a carry driving pawls d engaging with the teeth of the wheel
The weights a a' are carried by an arm or lever ². The wheels ff the lever g¹
and the arms n are loose or free to rotate independently of one another upon the
central shaft or axis o*.
a¹
When the lever g' moves in the direction of the arrow y³ it carries with it the
wheels and through the intervention of one of the pawls 2 engaging the teeth
of the wheel f. The wheel then moves the weights a a' through the action of
the pawls d. When the force of traction generated by the inertia of the weights a,
exerted on the spring c, by which the lever g' is connected to the arms n³, becomes
greater than the tension or stress X (Figure 2) of this spring, the weights a a' are
displaced in the direction of the arrow y, and being moved relatively to the wheel f³,
the pawls & travel over the periphery of the said wheel.
During the second period of the oscillation that is when the lever g' moves
in the opposite direction to the arrow y³ the force resulting from the inertia of
the weights a a' cause the pawls or drivers d to act upon the teeth of the wheel ƒ³
and consequently cause the wheel to act upon the pawls. One of these pawls
escapes from the teeth of the wheel f¹ in consequence of its oscillation upon the
centre or pin and allows the wheels and and the weights a a¹ to be displaced
under the combined action of the forces of inertia, and of the spring c in the
opposite direction to that indicated by the arrow y until the teeth of the wheel f¹
engage with the second pawl.
At normal speed this displacement is equal to that of the weights a a' in the
direction of the arrow y' under the action of the force of inertia. Any change in
the speed creates a corresponding change in the second of these two displacements,
J

page_text: but as the first is constant, this change has the effect of displacing the limits of the
movement performed by the weights a a' as herein before described.
In this form of construction the spring c constitutes the driver acting with
constant or uniform force the pawls d, and wheel constituting the driver acting
with constant displacement.
In case of need the springs or counterweights producing the constant force may
be dispensed with this force being produced by the weight of the regulating or
governing weight itself. In this case the rod b in the arrangement illustrated in
Figure 1 is placed in a vertical position and the pawl d is placed at the lower part
of the said rod. With this arrangement the normal rate of speed can be adjusted
by altering the travel or stroke of the rod b.
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 :-
1. A speed regulator or governor utilising the variations in momentum produced
by variations in speed and constructed with a regulating weight (a) engaged
between two drivers one of the said drivers (e) exerting a constant and adjustable
force, the other (d) exerting variable force the said weight being connected wich
the regulating device (throttle or expansion valve) of a steam engine or other
motor and having imparted to it by the action of the said drivers a reciprocating
or oscillating motion transmitted from the engine or motor to be governed and
producing on each driver reactions due to the inertia of the weight which have the
effect of displacing the first driver and consequently of displacing the weight and
the second driver to an extent proportionate to the forces of inertia that is to say
to the square of the speed the second or variable driver and consequently the
weight and the first driver being subjected to a displacement in the opposite
direction to the first by the intervention of driving mechanism actuated by the
engine or motor to be governed; the simultaneous action of these two movements
(oscillation of the regulating weight and displacement of the driver exerting
variable force) producing as regards the weight on the occurrence of a departure
from the normal speed, a relative displacement which causes it to act upon the
regulating device and compel the motor to resume its normal speed without exerting
any disturbing influence upon the normal operation of the regulating action all
substantially as herein before described.
2. In a speed regulator or governor constructed and operating as hereinbefore
described and claimed the arrangement consisting of a weight a placed upon a
screwed rod b partaking of an oscillating movement and of a rotary movement
which movements are transmitted to it from the engine or motor to be governed
the said weight being placed between a spring c of adjustable tension and a driving
device formed by a pawl d hinged to the said regulating weight and by the screw
thread on the rod with which thread the said pawl engages the said weight
partaking of a reciprocating motion and exerting upon the spring and upon the
driving pawl reactions resulting from its inertia when the driving pawl by this
reciprocating motion of the weight and by the rotary motion transmitted to the
rod bis caused to change its position according to the speed and at each change
of speed alters the relative position of the weight which acts upon the regulating
device of the motor and compels the latter to resume its normal rate of speed
substantially as hereinbefore described with reference to Figure 1 of the accom-
panying drawings.
3. In a speed regulator or governor constructed and operating as hereinbefore
described and claimed in the first claiming clause the arrangement consisting of
a circular regulating weight a supported upon bearings 9 and caused to partake
of an oscillating movement by means of a rod o acting through the intervention
of a drum (enclosing the said weight) and the parts I mi and d in combination
with a spring exerting a constant force and to which it is connected by the parts a
and and with the pawls d actuated by the parts r¹ o' a' m² l' and m the said
0

page_text: spring and the pawls performing the functions of the driver acting with
constant force and of the driver acting with variable force respectively the said
weight acting upon these drivers and the driver acting with varying force limiting
or augmenting according to circumstances the amplitude of the movements of
oscillation of the weight in the manner and for the purpose substantially as
hereinbefore described with reference to Figures 3 to 10 of the accompanying
drawings.
4. A speed regulator or governor constructed as set forth in the preceding
claiming clause and in which the spring constituting the driver acting with
constant force upon the weight a is inverted or arranged to act by tension in
place of by compression substantially as hereinbefore described and illustrated in
Figure 12 of the accompanying drawings.
5. A speed regulator or governor constructed as hereinbefore described in the
third claiming clause and in which the spring e constituting the driver acting
with constant force upon the controlling weight a is replaced by a counter-
weight performing the same functions substantially as hereinbefore described
and illustrated in Figure 13 of the accompanying drawings.
6. A speed regulator or governor constructed as herein before described in the
third claiming clause in which the spring e constituting the driver acting with
constant force upon the regulating weight a is replaced by a spirally coiled
spring performing the same functions substantially as hereinbefore described
and illustrated in Figures 14 and 15 of the accompanying drawings.
7. A speed regulator or governor constructed in accordance with the third
claiming clause in which the pawls d engaging with the toothed ring connected
to the regulating weight a are replaced by friction pawls hinged to the said weight
and acting in combination with the sleeve i in the manner and for the purpose
herein before set forth with reference to Figures 16 and 17 of the accompanying
drawings.
8. In a speed regulator or governor constructed as herein before described and
claimed in the first claiming clause a regulating weight divided into separate parts
attached to a lever in combination with a spring c pawls d and and ratchet
wheels and all operating in the manner and for the purpose hereinbefore
described and illustrated in Figure 18 of the accompanying drawings.
9. The arrangements and combinations of parts constituting the improvements
in speed regulators or governors substantially as 'herein before described and
illustrated in the accompanying drawings.
Dated this 21st day of December 1893.