Improvements in Valve Gearing with Governor for Water-power Machinery.
Year: 1898

page_text: Improvements in Valve Gearing with Governor for Water-power
Machinery.
I, JOHANN STUMPF, of 19, Lessing Strasse, of Berlin, Kingdom of Prussia,
German Empire, Professor, do hereby declare the nature of this invention to
be as follows:-
This invention relates to a valve gearing for water-power machinery, in which
the valves opening against the water are closed by an improved gearing just
before the completed stroke of the piston, whereby in consequence of the previous
cut off of the valves, a delivery or suction action is effected in the valve chest
according as to whether the inlet or the outlet valve has been closed. If for
instance just before the ending of the delivery, the inlet valve has been closed,
the further movement of the piston exerts a suction action, whereby the outlet
valve opening towards the inside is caused to open before the end of the stroke,
whereas inversely of course, the previous closing of the outlet valves before
the ending of the piston stroke, creates a delivery pressure in the valve-chest
which presses against the inlet valve, opening towards the outside against the
pressure of the water.
This improved gear is connected with a governor which actuates the gear
rods in such manner, that the previous cut off of the valves can take place at
any optional point of the piston stroke. This regulation can be effected both
by changing the point of the previous or early cut off of the inlet valves, as
also that of the outlet valves; if for instance with a double working motor, when
the piston has finished a definite part of its stroke, the inlet valves are closed,
the piston will then during the remaining portion of the stroke suck discharged
water through the outlet valve. Thus in such a case, work is only effected
during the time the inlet valves are open.
In the case of motors arranged according to the differential system, this
regulation can also be advantageously employed and here the outlet valves will
correspondingly be previously closed whereby the pressure continually resting
upon the small piston ring surface will be compelled during a portion of its
stroke to act against the full water pressure which rests upon the large piston
surface, and in this manner an even working will be maintained on both sides
of the piston.
Figure 1 in the accompanying drawings shows firstly a double acting motor
half in plan and half in section The general arrangement of the motor repre-
sented in these figures is that two single acting motors coupled together in such
manner that the plungers are arranged in the same axis, and actuate or set in

page_text: motion a crank-shaft common to both. The two plungers a are rigidly connected
together by rods b. From the cross-heade the movement is transmitted by a
connecting-rod to the shaft & bearing the fly-wheel.
The plungers operate in a valve chest e having inlet valves f and outlet valves g
which open in the direction of the inflowing water.
The early cut off or closing of the outlet valves takes place regularly viz.
shortly before the change of stroke, and commences by the movement of an
eccentric rod h actuated by a shaft d. Hereby a double crank lever h¹ is set
in rotation, said double crank-lever by means of rods ha actuating the lever h³.
The shafts of the levers 3 convey this swinging motion to the cams proper h³,
which engage by means of projections with the valve-spindles gl and press these
against the spiral springs 2 in an upward direction whereby the outlet valves
are closed.
The actuation or guiding of the inlet valves is started by an eccentric rod k;
said rod actuating a double crank lever 1, which by means of rods actuates
the levers and thereby also the levers upon the shafts . These levers
act upon f of the valves f against the springs f2. Both in or upon the rods h²
as well as upon the rods buffer-springs 12 are provided which obviate the valves
or the gearing snapping or breaking should impurities become lodged between
the valves and the valve-seats or, should the valve-gear not be properly adjusted.
To regulate the working of the motor, the lower crank lever is not tight
but is movable in a vertical direction, the same being adjusted by the governor R.
The crank-lever has its bearing upon a plunger this plunger at its ends.
is guided within two short cylinders 1/2 which are attached to the machine frame
in any suitable manner. The governor connects either the top or the under
surface alternately with the delivery or the discharge water chamber. Hereby
this said governor directly actuates a slide in the slide-box or casing S..
The arrangement of this slide box is shown in Figure 2. In the casing t
is the inlet for the water from the delivery chamber, the opening effects the
connection towards the surface of the said piston 7, and the opening the con-
nection towards the under surface of the same. The openings and lead
into the open air. The slide proper consists of the rod m with the pistons m¹
and m².
This slide is so dimensioned or proportioned that in the position shown in
Figure 2, the connecting-openings and 23 with the surfaces of the said
plunger can be closed by means of the pistons m¹ and m², so that in this position
the plunger is not influenced by the governor. As soon however as the slide m
ascends, the delivery water will pass through the openings towards the
upper surface of the plunger 1, whilst the water under the plunger can flow off
through the openings and In the machine represented in Figure 1 the
pipe connects the opening 2 (Figure 2) and the top-cylinder of the plunger 1,
whilst the tube 2 connects the lower cylinder with the opening (Figure 2).
In Figures 3 & 4 a differential motor is shown in elevation and section. Here not
only the closing of the inlet valves, but also that of the outlet valves is influenced
by the governor. The shaft d actuates by means of the eccentric rod k a double-
crank lever 1, which also, as described with reference to the construction of
Figure 1, has its bearing upon the plunger 7. The two cylinders 1 and 2 of
this plunger are arranged in the same manner as the machine represented in
Figure 1, viz. with the slide box or casing S, connected by the tubes n1 n2. Upon
the outlet valve the crank lever operates by means of the rod which engages
with the lever of the shaft upon the shaft rests then the lever . Upon
the inlet-valve operates the cam h5 of the shaft 4, said shaft being actuated by
the lever, said lever 3 being connected to the double-crank lever by the
rods Also here upon both the rods and buffer-springs are employed.
I will now proceed to explain the modus operandi of the differential motor.
The proportion of the piston surfaces F¹ to F3 I will assume as 2: 1; if the
motor works at a full filling, the work will be represented by the diagram, shown

page_text: in Fig. 5. By the movement of the plunger to the left, there operates on the
right, the surface F' against the surface F, which is half as large. The work
accomplished corresponds to the surface A (Figure 5). Upon the return of the
plunger the surface F only operates and the same amount of work A' (Figure 5)
results.
If the valves are so arranged, that the motor has only a 0.75 filling, the diagram
of the work would be represented in Figure 6. By the movement of the piston
towards the left, (upon three quarters of its path,) the piston surface F¹ reduced
to the extent of 12, would act; the obtained diagram being the surface B.
During the last quarter of the piston path, no pressure would be upon the
surface, but the surface F2 must be moved against the full pressure, so that
negative work so obtained, corresponding to the surface C₁of the diagram
Figure 6. Upon the return of the piston operates firstly upon the small sur-
face the full pressure and produces positive work corresponding to the
surface B (Figure 6), whilst upon the closing of the inlet-valve, the water in
the valve-box must be forced through the inlet valve to the delivery service, so
that here also negative work C₁ (Figure 6) results. . The diagram shows that
at 0.75 filling the obtained result equals 0.5.
The work obtained at a 05 filling is shown by the diagram of Figure 7;
After
viz. during the half piston stroke the surface D of the diagram is formed.
the inlet-valve is closed, in consequence of pressure upon the differential surface
the negative work E will result, whereby the piston sucks dead water into the
valve box. Upon the return of the piston, the differential surface when the
outlet valve is open produces the positive result or work D. When the piston
is at half stroke, the outlet valve closes, whereupon the water must be forced
from the inlet valve back again into the delivery pipes, whereby the negative
work E would result. The diagram shows the correspondence of the separate
surfaces as regards their size and thus enables it to be understood that at a half
filling the differential motor will effect no real work. If less than 0.5 filling
is given, the algebraical sum of the separate work quantities will be negative,
that is to say, the motor will act as a pump. In this case the motor could with
advantage be employed for such purposes where large work-quantities are required
to be absorbed by brake action such as for instance is the case with lifting
machinery in general and with railways. In such cases the stored positive force
or energy is taken up by the action of the pump, this energy of the pumping
action being available for use in the next following period of work.
Much more simple is the operation of the double acting pump represented
in Figure 1, viz. as here only the previous closing of the inlet valves is a
changeable one; here also the quantity of work is almost entirely proportional
to the filling. As soon as the inlet-valves are closed, the plunger sucks from the
discharge service, dead water into the valve chests without effecting any work.
Thereby, of course, it would be also possible with double action motors at the
same time to fix the closing of the in- and outlet valves. Also here, as in the
case of the differential motor, at a 05 filling no work would be effected, whilst
the delivery water coming into the valve box during the half piston stroke must
be forced again into the delivery service, and it may also be remarked that a
filling of 075 would effect a work quantity equal to 075, because the delivery
water could only act during 075 of the forward stroke of the piston path,
whilst during 025 of the return stroke of the piston, delivery water must again
be brought back into the delivery service.
Figure 8 shows in conclusion a modification of a differential motor in which
the regulation of the closing of the valves is not effected by a governor, but
by hand. This device may even be used to reverse the direction in which the
motor is running. An eccentric rod k mounted or suspended in known manner
(see Figure 9) actuates at its free ends the rods and . By means of a hand
lever o
provided with the toothed adjusting sector or arch p, the suspended
device is suitably adjusted so that the varying degrees of filling as also a

page_text: complete reversion of the direction of the motor can be attained. In conclusion
it is of course clear, that instead of the last described steering-mechanism for the
regulation of the valves as shown in Figure 8, any other suitable mechanism
could be employed.
Dated this fith day of Soniomhan 1908
GEO. H. RAYNER,
37, Chancery Lane, London, Agent for the Applicant.
Improvements in Valve Gearing with Governor for Water-power
Machinery.
I, JOHANN STUMPF, formerly of 19, Lessing Strasse, at present 27, Ranke Strasse,
in the City of Berlin, Kingdom of Prussia, German Empire, Professor, do hereby
declare the nature of this invention and in what manner the same is to be per-
formed, to be particularly described and ascertained in and by the following
statement:-
This invention relates to a valve gearing for water-power machinery, in which
the valves open in the direction contrary to the stream of the inflowing water
and are closed by an improved gearing just before the completed stroke of the
piston, whereby in consequence of the previous cut off of the valves, a delivery
or suction action is effected in the valve chest according as to whether the inlet
or the outlet valve has been closed. If for instance just before the ending of
the delivery, the inlet valve has been closed, the further movement of the piston
exerts a suction action, whereby the outlet valve opening towards the inside is
caused to open before the end of the stroke, whereas inversely of course, the
previous closing of the outlet valves before the ending of the piston stroke, creates
a delivery pressure in the valve-chest which presses against the inlet valve,
opening towards the outside against the pressure of the water.
This improved gear is connected with a governor which actuates the gear
rods in such a manner, that the previous cut off of the valves can take place at
any optional point of the piston stroke. This regulation can be effected both
by changing the point of the previous or early cut off of the inlet valves, as
also that of the outlet valves; if for instance with a double acting motor, when
the piston has finished a definite part of its stroke, the inlet valves are closed,
the piston will then during the remaining portion of the stroke suck discharged
water through the outlet valve. Thus in such a case, work is only effected
during the time the inlet valves are open.
In the case of motors arranged according to the differential system, this
regulation can also be advantageously employed and here the outlet valves will
correspondingly be previously closed whereby the pressure continually resting
upon the small annular piston surface will be compelled during a portion of its
stroke to act against the full water pressure which rests upon the large piston
surface, and in this manner an even working will be maintained on both sides
of the piston. My invention will be readily understood with reference to the
drawings filed with my Provisional Application, in which drawings Figure 1
illustrates a double acting motor partly in section and partly in elevation. The
general arrangement of the motor represented in these figures is that two single
acting motors are coupled together in such a manner that the plungers are
arranged in the same axis, and actuate or set in motion a crank-shaft common
to both. The two plungers a a are rigidly connected together by rods b. From

page_text: the cross-head c the movement is transmitted by a connecting-rod to the shaft d
bearing the fly-wheel.
The plungers operate in a valve chest e having inlet valves f and outlet valves g
which open in the direction contrary to the stream of the inflowing and out-
flowing water in each case.
The early cut off or closing of the outlet valves takes place regularly viz.
shortly before the change of stroke, and commences by the movement of an
eccentric rod h actuated by a shaft d. Hereby a double crank lever h¹ is set
in rotation, said double crank-lever by means of rods h² actuating the lever h³.
The shafts of the levers h³ convey this swinging motion to the cams proper h³,
which engage by means of projections with the valve-spindles g¹ and press these
against the spiral springs in an upward direction whereby the outlet valves
are closed.
The closing of the inlet valves is effected by an eccentric rod k; said rod
actuating a double crank lever 1, which by means of rods actuates the levers k³
and thereby also the tappets upon the shafts. These tappets act upon
the projecting annular rod f¹ of the valves f against the influence of the springs f
which normally keep the valves f open around the rods and around the
rods buffer-springs are arranged which obviate the valves or the gearing
snapping or breaking should impurities become lodged between the valves and
the valve-seats or, should the valve-gear not be properly adjusted.
To regulate the working of the motor, the lower crank lever is not tight
but is movable in a vertical direction, the same being adjusted by the governor R.
The crank-lever has its bearing upon a plunger; this plunger at its ends
is guided within two short cylinders which are fixed to the machine frame
in any suitable manner. The governor connects either the top or the under
surface alternately with the delivery or the discharge water chamber. Hereby
this said governor directly actuates a slide in the slide-box or casing S.
The arrangement of this slide box is shown in Figure 2. In the casing i i
is the inlet for the water from the delivery chamber, the opening effects the
connection towards the surface of the said piston, and the opening the con-
nection towards the under surface of the same. The openings and lead
into the open air. The slide proper consists of the rod m with the pistons m¹
and m².
This slide is so dimensioned or proportioned that in the position shown in
Figure 2, the connecting-openings and with the surfaces of the said
plungers can be closed by means of the pistons m¹ and m², so that in this position
the plunger is not influenced by the governor. As soon however as the slide m
ascends, the delivery water will pass through the openings towards the
upper surface of the plunger 7, whilst the water under the plunger can flow off
through the openings and . In the machine represented in Figure 1 the
pipe n¹ connects the opening (Figure 2) and the top-cylinder of the plunger,
whilst the tube 2 connects the lower cylinder 2 with the opening (Figure 2).
In Figures 3 & 4 a differential motor is shown in elevation and section. Here not
only the closing of the inlet valves, but also that of the outlet valves is influenced
by
the governor. The shaft actuates by means of the eccentric rod k a double-
crank lever 1, which also, as described with reference to the construction of
Figure 1, has its bearing upon the plunger 1. The two cylinders and 2 of
this plunger are arranged in the same manner as the machine represented in
Figure 1, viz. with the slide box or casing S connected by the tubes n' n².
Upon
the outlet valve the crank lever ¹ operates by means of the rod which engages
with the lever of the shaft upon the shaft rests then the lever .
the inlet-valve operates the cam 5 of the shaft h, said shaft being actuated by
the lever h³, said lever being connected to the double-crank lever by the
rods 2. Also here around both rods 2 and buffer-springs are arranged.
Upon
I will now proceed to explain the modus operandi of the differential motor.
The proportion of the piston surfaces F¹ to F2 I will assume as 2:1; if the

page_text: '
motor works at a full filling the work will be represented by the diagram, shown
in Figure 5. By the movement of the plunger to the left there operates on the
right, the piston surface F¹ against the piston surface F³, which is half as large.
The work accomplished corresponds to the area A (Figure 5). Upon the return
of the plunger the surface 1 only operates and the same amount of work results,
(viz. an amount of work equal to the area A Figure 5).
If the valves are so arranged, that the motor works only at % filling, the
diagram of the work would be represented in Figure 6. By the movement of
the piston towards the left (upon three quarters of its path) the piston surface F¹,
reduced to the extent of F, would act; the obtained diagram being the area B.
During the last quarter of the piston path, no pressure would be upon the
surface F, but the surface 12 must be moved against the full pressure, so that
negative work so obtained, corresponds to the area C¹ of the diagram Figure 6.
Upon the return the piston full pressure acts upon the small surface F2, and
positive work corresponding to the area B (Figure 6) is produced whilst upon the
closing of the inlet valve, the water in the valve-box must be forced through
the inlet valve back again into the delivery service, so that here also negative
work corresponding to the area C1 (Figure 6) results. The diagram shows that
at filling the obtained result is half work, viz. filling less ½ of negative
.work.
The work obtained at half filling is shown by the diagram of Figure 7; viz.
during the half piston stroke the area 1) of the diagram is formed. After the
inlet-valve is closed, in consequence of pressure upon the differential surface
the negative work indicated by the area E will result, whereby the piston sucks
dead water into the valve box. Upon the return of the piston, the differential
surface when the outlet-valve is open, produces the positive result or work
indicated by D. When the piston is at half stroke, the outlet valve closes,
whereupon the water must be forced from the inlet valve back again into the
delivery pipes, whereby the negative work illustrated by the area E¹ would
result. The diagram shows the correspondence of the separate areas as regards
their size and thus enables it to be understood that at a half filling the differential
motor will effect no real work. If less than half filling is given, the algebraical
sum of the separate work quantities will be negative that is to say, the motor
consequently acts as a pump. In this case the motor could with advantage be
employed for such purposes where large work-quantities are required to be
absorbed by brake action. In such cases the stored positive force or energy is
taken up by the action of the pump, this energy of the pumping action being
available for use in the next following period of work.
Much more simple is the operation of the double acting pump represented
in Figure 1, viz. as here only the closing of the inlet valves is a changeable one;
here also the quantity of work is almost entirely proportional to the filling. As
soon as the inlet valves are closed, the plunger causes a small quantity of water
to return into the valve chests without effecting any work. In the case of double
action motors the closing of both in- and outlet valves would have to be properly
regulated. Also here, as in the case of the differential motor, at half filling no
work would be effected, whilst the delivery water coming into the valve box
during the half piston stroke must be forced again into the delivery service,
and it may also be remarked that a 34 filling would effect a work quantity equal
to 05 because the delivery water could only act during of the forward stroke
of the piston path, whilst during 1 of the return stroke of the piston, delivery
water must again be brought back into the delivery service.
Figure 8 shows in conclusion a modification of a differential motor in which
the regulation of the closing of the valves is not effected by a governor, but
by hand. This device may even be used to reverse the direction in which the
motor is running. An eccentric rod k mounted or suspended in known manner
(see Figure 9) actuates at its free ends the rods hand. By means of a hand
lever provided with the toothed adjusting sector or arch p, the suspended

page_text: device K is suitably adjusted so that the varying degree of filling as also a
complete reversal of the direction of the motor can be attained. In conclusion
it is of course clear, that instead of the last described mechanism for the regulation
of the valves as shown in Figure S, any other suitable mechanism could be
employed.
Having now particularly described and ascertained the nature of my said
invention, and in what manner the same is to be performed, I declare that what
I claim is
1. An improved valve-gearing for water power machinery in combination with
a governor actuating the rods of the gear for effecting the cutting off of the valve
at any optional point of the piston stroke, for the purpose as described.
2. An improved valve gearing for water power machinery, in combination with
a double crank lever K oscillated by the engine and actuating the valve, a
plunger forming the bearing of the double-crank lever and being adjustable
in height by means of water pressure, for the purpose as described.
3. In an improved valve-gearing for water power machinery, the combination
of valves (f) with a mechanism actuating the valves, means for reversing the
direction of run, thus allowing a transformation into a pump, substantially and
for the purpose as described.
Dated this 97th day of Mar 1800.
GEO. H. RAYNER,
Agent for the Applicant.