IMPROVEMENTS IN STEAM ENGINE AND OTHER MOTIVE-POWER GOVERNORS
Year: 1878

page_text: LETTERS PATENT to Charles Max Sombart, of the Firm of Buss, Sombart, and
Company, Engineers and Patent Agents, of Magdeburg, in the Empire of
Germany, for the Invention of "IMPROVEMENTS IN STEAM ENGINE AND OTHER
MOTIVE-POWER GOVERNORS." A communication from Edward Buss, of Magde-
burg in the Empire of Germany.
Sealed the 3rd December 1878, and dated the 10th July 1878.
PROVISIONAL SPECIFICATION left by the said Charles Max Sombart at the
Office of the Commissioners of Patents on the 10th July 1878.
CHARLES MAX SOMBART, of the Firm of Buss, Sombart, and Company, Engineers
and Patent Agents, of Magdeburg, in the Empire of Germany.
IMPROVEMENTS
IN STEAM ENGINE AND OTHER MOTIVE-POWER GOVERNORS." A communication from
Edward Buss, of Magdeburg, in the Empire of Germany.
The Invention consists in employing special means not only for performing the
ordinary safety valve duties of a governor, but of making them so that their travel
shall correspond proportionately with the energy of the governor; and this special
form of governor is intended to allow its return to the normal state, to be delayed
any desired period by means of periodical mechanism.
One form of performing the Invention consists of a kind of water accumulator
combined with a spring which is acted upon by the equilibrium of pressure being
disturbed. The time occupied in the water passing through a sinall aperture
affords the periodical mechanism or time check used to delay the return of the
governor to its normal position.

page_text: SPECIFICATION in pursuance of the conditions of the Letters Patent filed
by the said Charles Max Sombart in the Great Seal Patent Office on the 6th
January 1879.
CHARLES MAX SOMBART, of the Firm of Buss, Sombart, and Company, Engineers
and Patent Agents, of Magdeburg, in the Empire of Germany. "IMPROVEMENTS
IN STEAM ENGINE AND OTHER MOTIVE-POWER GOVERNORS." A communication from
Edward Buss, of Magdeburg, in the Empire of Germany.
The Invention refers to two different and independent improvements on governors
for revolving machines.
The first improvement is intended to fulfil chiefly the following aims:-
1. To effect that the travel passed through by the sliding box or. gear, both of
astatic directly acting governors and of indirectly acting governors, corresponds
proportionately with the energy of the governor.
2. To effect for the two kinds of governors mentioned above a slow supplementary
adjustment, which has to act until the energy of the governor has been absorbed
and the motor has again obtained its normal speed.
The improvement for astatic directly acting governors consists of a new con-
struction of the cataract frequently applied to governors. By this new arrangement
the sliding box, when being equilibrated or at rest again, has to bend or release a
spring, or to lift a loaded lever as soon as the equilibrium is disturbed; and further,
the tension of the spring or the motion of the lever has to be used for slowly moving
a liquid cataract.
Figures 1, 2, 3, and 4 show four different constructions of the apparatus to be
applied to directly acting governors.
In Figure 1, A, the stationary cylinder fitted with any kind of liquid; a, the
tight-fitting but perforated piston of the cataract; and B, the rod forming the
connection with the sliding box of the governor. The fork-like shaped lower part
of this rod passes over the upper part of the piston rod a¹ and carries between its
two ties b and the collar a" of the piston rod the spiral springs C and C. This
contrivance acts in the following manner :-The liquid having to pass through the
narrow boring of the piston when the latter begins to move, the motion of the
piston must be necessarily a very slow one. If, therefore, the sliding box of the
governor begins suddenly to rise or to fall, the next consequence will be an up or
down motion of the rod B and a corresponding compression or extension of the
springs C and C¹. The governor acts, therefore, with respect to this first movement
exactly like an ordinary governor, and its lift or fall is proportionate to the amount
of force exercised upon the sliding box. The tension of the spring having to produce,
however gradually, a slow dislocation of the piston a, the sliding box too describes
subsequently an extremely slow movement (the supplementary adjustment) which
will last so long until the tension of the spring as well as the energy has been
absorbed and the engine has gained again its normal speed.
Figure 2. The cylinder itself is here moveable, and is vertically guided through
a cylindrical rod. A spiral spring C, connected on one side with the cylinder, and on
the other side with the fixed support, keeps the cylinder at a fixed average position
above the support, whence a rising of the cylinder must produce a stretching, but a
setting of the cylinder a compressing of the spring.
The manner of acting of this apparatus differs from that of the first contrivance
in so far only as in the present case the cylinder also has to follow the quick move-
ments of the sliding box and of the gear. The movements of the sliding box itself
are fully identical with those of the first apparatus.
Figure 3. The liquid cylinder A is provided with two trunnions a, by means of
which it is suspended on the loaded angular lever or pendulum C, the fulcrum of
which is at c. This lever takes here the place of the spring C of the apparatus

page_text: represented in Figure 2, whence the two contrivances, Figures 2 and 3, act in the
same manner.
Figure 4. This apparatus differs from that described above so far as a simple
clock work has been substituted for the liquid cylinder with its piston. The rod B,
which communicates also in this construction with the sliding box of the governor,
is connected with the rod D by means of the spiral spring C. The rod D is provided
on a rectangular bending with the rack d gearing into the pinion e, which is firmly
connected with the wheel E. The movements of the latter are transferred by means
of the pinion f, the spur wheel F, and the pinion g to the fan G. A small movement
of the rod D causes, in consequence of the large proportion of the wheel gear, a
considerably quick rotation of the fan G. The resistance of the air which the
rotating fan has to overcome opposes, however, any quick movement of the rod D,
in the same manner as the resistance of the liquid acts upon the movements of the
piston, Figure 1. The spring chaving also in this case to keep the relative position
of the two rods B and D invariably, the manner of acting of the contrivance
Figure 4 coincides also with those of the apparatus described previously.
The first improvement on indirectly acting governors consists likewise of a new
and extended construction of the cataract, as well as of an addition of new parts,
which in connection with the cataract have to effect for indirectly acting governors
the same mode of operation as the four apparatus described above have produced
on directly acting governors.
The first improvement attains further for indirectly acting governors that a most
rapid action of the indirect transferrer is produced. This contrivance which has to be
applied chiefly to those indirectly acting governors, the transferrer of which is moved
by friction, consists of an arrangement by means of which a part of the transferrer
produces a force opposed to the energy and proportionated to the travelled distance
(of the transferrer), but at the same time limiting the latter. This force opposed to
the energy further diminishes slowly and subsequently only, and produces so long
a continued supplementary adjustment until the energy of the governor has at
last been absorbed and the engine has gained again its average speed.
Figure 5 represents a construction of this apparatus. The two friction discs H and
H' are firmly fastened to the sliding box of the governor, whilst two other friction
discs, i and i, are connected with the bevel wheels I and I', which are geared into
the wheel K. The shaft of the latter wheel is provided with screw threads and
corresponding nut M, which is moved whenever the governor begins to act.
The apparatus corresponds so far with the known and generally applied arrange-
ments for transferring motion, but besides, there are connected with it the two
levers L and N, as well as the liquid cylinder. A, and these are the principal parts of
the improvements. The lower part of the sliding box carries the ring, which is
connected by means of two pivot pins with the lever L, the other end of which being
fastened to the ring K. Between this ring and the liquid cylinder A the spiral
spring C is placed, whilst the piston rod a¹ is coupled with the angular lever N by
incans of a short draw bar l. The lever N is further provided with a pin m, which
strikes against the projections m' and m" of the lever L as soon as the nut M has
attained one of its extreme positions.
The contrivance acts in the following manner :-If the machine exceeds its normal
speed the sliding box of the governor is raised, presses thereby through its friction
disc against the disc i, and transfers in this manner motion to the three bevel
wheels I, I, and K, as well as to the shaft n. The nut M is thus moved towards
the right, causing a rising of the liquid cylinder A, and thus also a compression of
the spring C..
The upward pressure experienced in this manner on the ring k is transferred
through the lever L upon the ring h and the sliding box of the governor.
The tension of the spring being proportionately to the space of the compression,
the pressure of the ring exercised on the sliding box must also be in proportion to
the way travelled by the nut. A power opposed to the energy of the governor, and

page_text: increasing with the travel of the nut, acts therefore on the slide box of the governor;
this power will be finally in equilibrium with the energy, preventing thus a further
action of the friction coupling. The way travelled by the nut in the first instance
is for this reason proportionate to the energy of the governor. The small opening
in the piston a allows, however, a slow flowing after of the liquid, and thus gradually
a going down of the cylinder A.
The tension of the spring c, as well as the pressure exercised by the ring h, on
the sliding box being consequently diminished, the energy of the governor must at
last exceed again the power mentioned above, effecting thus a slow forward move-
ment of the nut M, lasting so long, until the tension of the spring, as well as the
energy, has ceased, and the machine has gained again its normal speed. If the speed
of the machine is reduced below its normal state, all other movements will be altered
in the reverse way.
It is easily to understand that also in this case a loaded pendulum may be substi-
tuted for the spring, and a clockwork for the liquid cylinder, as in Figures 3 and 4
respectively, without a considerable modification of the acting manner of the appa-
ratus. When the nut M. has arrived at one of its extreme positions a further action
of the friction coupling H, i, H', ', has to be prevented through the pin m, and the
projection m¹ and m", the sliding box will be disengaged by means of the lever L
and the ring h, as soon as the pin strikes one of the projections. A drawback fre-
quently found with indirect transferrers, and through which damages, as well as
interruptions of the action of the whole apparatus, are easily produced, is thus
removed.
The contrivance Figure 5 fulfils, as stated already, besides the two chief aims, namely,
attaining proportion between travel and energy, and supplementary adjustment
until the normal speed has been attained. The further purpose of producing a more
rapid action of the governor for number of revolutions and proportion of diameter of
wheels are such, that the nut M requires for one travel over its entire stroke an
extremely short time.
Whilst with the indirectly acting governors known until now, a quicker action is
always connected with a too far going and thus inadmissible adjustment, the
proportion between travel and energy prevents in the present case completely this
disadvantage.
it
The second improvement relates to the addition of a new apparatus to the chief
part of governors, namely, the speed measurer; the new apparatus measures the
acceleration of the revolving machine, and together with the speed measurer,
acts on the delivery of power from the motor. This apparatus, which may be called
acceleration counter, consists of a contrivance by. means of which one or several
heavy bodies moved by a rotating shaft, exercise in consequence of the movement of
inertia, when accelerated, a backward acting pressure, and when retarded, a forward
acting pressure against an organ connected with the driving shaft; this pressure is
transferred by any convenient mechanism on a friction coulping, in order to engage
the two halves of it with each other.
Figure 6 shows a simple form of the acceleration counter itself. The horizontal
shaft O is provided with threads of large pitch, the corresponding nut being formed
by the box of the fly wheel P carrying on its further extension the two friction
cones H and H¹. A third cone K placed between the two other cones is arranged
in such a manner that when coming into contact with one of the other cones, an
extremely small space will be left between it and the third cone.
The fly wheel forms here the heavy body driven by the shaft O, the acceleration
or retardation of which will cause, on the part of the fly wheel, the intention to
start or to quicken its motion.
The mechanism which transfers the power showing itself in the fly wheel at each
acceleration upon the friction coupling is formed here by the screw and the boss of
the fly wheel serving as nut. This apparatus acts now in the following manner:
The fly wheel has always the intention to retain invariably a speed once attained;

page_text: if therefore the motion of the shaft O is accelerated the fly wheel will not alter its
speed, and in consequence of the threads it will be shifted axially until the cone H
comes into contact with the cone K, when the fly wheel cannot further rotate
relatively to the shaft O, but, on the contrary, it is obliged to participate in the
acceleration of the shaft. The power, however, with which the cone H is pressed
against K is proportionate to the acceleration both of the shaft O and of the fly
wheel. The cone K therefore will be turned round so long as the acceleration is
sufficient for overcoming the existing resistance.
In case of retardation the fly wheel will at first not alter its speed, and is there-
fore relatively to the shaft in advance, and this so long until the cone H¹ touches
the cone K, when a reversed rotation of the last-named cone takes place; the power
of the cone H is also in this case proportionate to the retardation. As stated
already, the acceleration counter, together with the speed measurer of the ordinary
governor, has to be applied. It is the same whether the acceleration counter and
the speed measurer are two separate mechanisms connected by any intermediate
contrivance, or whether the two appliances are combined with each other in such a
manner that they form a whole in their combination only.
Figure 7 shows a combination of the speed and acceleration measurer. The
vertically sliding box Q, with the friction coues H and H', rotates commonly with
the upright revolving shaft O. The sliding box carries on two long cross arms the
axles o' and o, the latter of which being connected with the following four parts :—
1. The downwards turned pendulum of inertia P¹. 2. The upwards turned
pendulum of inertia P2. 3. The inclined centrifugal pendulum P³. 4. The bended
arm provided with a friction pulley. The axle o¹ carries analogously the
pendulums P3, P4, P, as well as the arm p². The friction pulleys carried by the
arms p¹ and p² are supported by a straight plate connected with the revolving
shaft O.
If the four pendulums of inertia P1, 2, 3, 4, would be omitted in the construction
an apparatus would remain, the arrangement of which coincided approximately
with known centrifugal governors which have their arms suspended from the sliding
box. The pendulums of inertia take, however, in the lastly-described apparatus,
the place of the fly wheel; the cone K is besides arranged in such a manner that it
leaves between itself and the cones H and H2 but an extremely small space.
When the motion of the apparatus is accelerated the four pendulums of inertia,
as will be seen from the Drawings, show simultaneously the intention to lift the
box and to bring the cone H into contact with the cone K, whilst a retardation
produces the reversed effect, viz., the engagement of the cone H¹².
The two pendulums P5 and Pe acting under the influence both of the centrifugal
force and the gravity, and forming the principal parts of the speed measurer, try
also an engagement of the cone H, either with the cone H¹ or with the cone K;
they produce a lifting of the sliding box, thus a contact with H, if the normal speed
of the revolving shaft is exceeded, but a sinking of the box and a contact with H'
if the shaft O rotates with a speed below the normal one. The acting together
both of the pendulum of inertia and of the centrifugal pendulum produces also in
the box Q two forces, the one of which is dependent upon the acceleration, and the
other upon the variation of the speed. The force produced by an acceleration is in
this case like the force originating from too great a velocity directed towards above,
whilst the force produced either by a retardation or by a velocity too much
diminished acts in a downward direction.
The manner of acting of this apparatus differs from that of an indirectly acting
centrifugal governor principally through an earlier beginning and a sooner stopping
of the action.
In consequence of the earlier beginning of the action the differences of speed
cannot be so great as they would be without acceleration counter. The earlier
action prevents the over adjustment and the vibrating of the governers connected
with it.

page_text: Figure 8 shows a new combination of an acceleration counter with a speed
measurer, the acting velocity being determined here, not by the centrifugal force,
but by the resistance of the air of a fan.
The casting R, consisting chiefly of the boss and of two side arms, and being
firmly connected with main shaft, carries two teethed segments turning round the
vertical shaft q, and gearing into a spur wheel s' which is fastened to the fan 8.
The velocity of the latter will be prevented exceeding that of the main shaft by
means of the spiral spring t, whilst the resistance of the air on the wings will
produce a retardation of the fan.
The fly wheel loosely placed on the main shaft is coupled with the two segments r
by the two rods u. Two pairs of beveled and teethed segments 1, 1, transfer the
motion of the shaft q upon two horizontal shafts v, whilst the pin w gives a rotating
motion to the sliding box. The indirect transferrer, shown in this Figure 8, corre-
sponds in general with that represented by Figure 5. In the present case, however,
the forces of contact of the friction discs are formed through several conical surfaces
which increase the friction.
The apparatus, Figure 8, acts in the following manner-Each relative turning
of the fan 8, as well as each relative turning of the fly wheel P, is connected with
a movement of the box Q in the direction of its axis, and the power with which
the box is pressed against its corresponding friction disc is also in this case
dependent upon the amount of the variation of the velocity as well as upon the
amount of acceleration. The main shaft rotates again, thus, that the energy pro-
duced by the tachometer, when the velocity is exceeded, acts in the same sense as
the force produced by the acceleration counter during an increase of velocity. The
influence of the apparatus upon the delivery of the motor corresponds therefore
completely with that of the apparatus described last.
The apparatus, Figure 9, represents a combination of a speed and of an accelera-
tion measurer, with the application of the improvements shown in Figures 1 and 5.
The speed measurer consists of two identical pendulums of rotation P, and the
spiral springs t belonging to them. The axles of these pendulums as well as the
ends of the springs are fastened to the fly wheel P, whilst the projections of the
pendulums above their fulcrums are directed towards the box Q, with which they
are coupled together through pins. The pin w gives rotating motion to the sliding
box Q, turning the pendulums round their axles, as well as a relative turning of
the fly wheel, being connected with a motion of the sliding box in the direction of
its axis; the apparatus described so far, and supposed it turns in the right direction,
acts exactly in the, same manner as those represented by Figures 7 and 8. The
shaft of the bevel wheel K forms a screw with corresponding nut M. The lever N
transfers the motion of the nut to the box x, which is connected by means of the
spiral spring c with the piston rod a'. The liquid cylinder A is carried by the one
arm of the angular lever L, the second arm of which catches the ring h whilst a
third arm supports the weight 8. The draw bar T, the lower part of which catches
a pin connected with the lever L, is suspended from the lever N. The upper
projection of the vertical shaft of the wheel K is intended for the reception of a
spur wheel or of any convenient mechanism, which transfers the motions of this
shaft to the contrivance of admission. The spring C has to keep invariably the
relative position between the box x and the piston rod a'. A vertical movement
of the nut M produces in the first instance a shifting of the box x on the piston
rod a¹, and thus a tension of the spring c. The piston, provided with a narrow
boring, transfers this pressure to the cylinder A. and to the ring h. The way
travelled in the beginning by the nut will be limited through the pressure exercised
by the tension of the spring on the ring increasing so long until it will lie in
equilibrium with the total energy in the box Q. This energy is, as has been shown,
the sum of two forces proportionated to the acceleration respectively to the varia-
tion of the, speed of the apparatus. As soon as equilibrium has been attained in
the box between the energy and the pressure of the ring h, only an extremely slow

page_text: and on the velocity of the piston a, in the cylinder A, depending motion of the nut
can take place, lasting so long until the energy in the box as well as the tension of
the spring c has gradually disappeared. This is in general not the case with the
apparatus in question when the normal speed is again obtained, but rather at a
moment when the energy depending on the variation of the speed and that
depending on the acceleration are opposed to each other and therefore in equi-
libriumn. The action of this apparatus ceases when the speed of the machine is a
little too much accelerated or correspondingly retarded. The action will also cease
with a too much reduced velocity, as soon as there exists at the same time in the
machine a certain acceleration. The draw bar T disengages the box Q as soon as
the nut M has arrived nearly at one of its final positions, preventing thus a too
long continued action of the apparatus.
The apparatus may be fixed horizontally, vertically, or at an inclined position.
The weight S has to release the box Q as well as the cylinder A, and it has also
to counteract the shocks of the movements to which the apparatus may be exposed.
The apparatus in question differs with respect to the manner of its action from
the governers applied until now through the following chief points:
1. The acceleration counter belonging to the apparatus effects that the apparatus
begins all its operations which it has to carry out at existing variations of the
speed sooner than any other governer.
2. All movements of the shaft U take place much quicker than with other
especially indirect acting governors.
3. The way travelled by the shaft U at the quick action of the apparatus in the
beginning is strictly limited, and it is proportioned to the interruption of equi-
librium which took place momentarily between work of motor and useful effect.
4. The acceleration measurer effects an early ceasing of the action.
5. The apparatus is connected in such a manner, through the improved construe-
tion of cataract, that after the governer has once acted, the normal speed must
always be attained again.
6. A too far going or continued action of the indirect transferrer, and conse-
quently a damaging of the apparatus is prevented.
With respect to point 2 it may be mentioned, that with other indirectly acting
governors a rapid action is therefore not admissible, because the proportion stated
under 3, as well as the early ceasing of the action stated under 4, does not take
place with them.
The apparatus, Figures 7 and 8, may also be provided like the one described last,
with the improved cataract arrangement, and for all three apparatus a suitable
clock work may be substituted for the liquid cylinder and its piston.

page_text: power produced at each acceleration by the vis-inertia of the weights upon a friction
coupling in order to cause an engagement of the latter.
In witness whereof, I, the said Charles Max Sombart, have hereunto set my
hand and seal, this Sixth day of January, A.D. 1879.
CHARLES MAX SOMBART. (L.S.)