Improvements in or connected with Steam Engines.
Year: 1899

page_text: PROVISIONAL SPECIFICATION.
Improvements in or connected with Steam Engines.
I, JACOB MISSONG, of 17, Bruningstreet, Hoechst-on-the-Maine, in the German
Empire, Engineer, do hereby declare the nature of this invention to be as
follows:
-
This invention relates to means for increasing the working capacity of steam
engines for a given consumption of steam, the exhaust steam from the engine
being compressed to the initial pressure of the live steam such steam being
superheated in a preliminary and intermediate stage before being admitted to
perform its work, and cooled down before and during compression, so that dur-
ing expansion and condensation, a considerable useful effect is secured.
«
"
The present invention is based upon the laws of thermo-dynamics which
state that heat and work are equivalent; that all substances may, by heating
and cooling, be rendered available for work, or in other words, that motive power
may be derived from any variation of temperature; that losses owing to inter-
change of heat between the steam and the cylinder-walls may be reduced, by
maximum super-heater temperature, by a maximum filling (or charge);
by a high degree of compression, by the possibility of using double-
acting (or compound) cylinders; by an inconsiderable fall (or decline)
of the temperature, by a maximum speed of the piston, and by reduced
dimensions of the cylinder (or cylinders): and that a material increase
of motive power in comparison with single cylinder steam engines and multiple-
expansion engines with preliminary and intermediate superheating may be
effected only where the exhaust steam is restored by compression to the initial.
pressure.
The degree of caloric efficiency of heat motors, as is generally known, is
T – T₁
expressed by the equation
i.e. the fall of temperature divided by the
T
absolute initial temperature. To bring about a material increase in the useful
effect by raising the temperature T (of 360°) is not possible in the existing
steam engines for well-known practical reasons. A lowering of the terminal
temperature T, of such engines is useless if the useful effect of the motor of a
refrigerating machine is not greater than that of the steam motor.
The conditions stated in the introductory part of this specification, which
admit of an increase in the useful effect of steam engines, may in every respect
he most fully complied with in the simplest conceivable manner by compressing
the exhaust steam (which is being at the same time, or has been previously,
cooled, say, by injection or surface cooling,) to the initial pressure; and by
using the whole of the heat imparted, for drying and superheating the com-
pressed steam; such steam being only cooled sufficiently to prevent the super-
heater from burning and to enable the temperature (where the superheater is
heated direct.) to be maintained at a sufficiently high degree to admit of the
fullest possible advantage being taken of the heating rower of the fuel, so that.
consequently. the useful effect shall be due almost exclusively to the heat of
DQ17

page_text: the superheater, and that the loss from cooling shall be reduced nearly to zero
owing to the superheating and to the compression of the steam to its initial
pressure before the completion of the return stroke of the piston. If water be
injected into the superheater direct, the steam may be compressed down to the
dry saturated condition.
The main feature of the present invention is that the latent or evaporation-
heat, which in existing steam engines escapes into the atmosphere, or departs
along with the condensation water, is, restored by compression to the initial
pressure; while at the same time the working steam proper by being dried and
superheated, before being admitted to the cylinder or cylinders is during its
admission and expansion stages in the cylinder or cylinders, sufficiently saturated,
either before or during the subsequent compression, (say, by means of a surface
condenser, or, better still, by injection) to prevent the superheater from burning,
and to obviate, as far as possible, loss arising from cooling.
===
1.135
=
1.383
The work performed under such conditions varies according to different steam
pressures, different "fillings" (or charges) and different superheated tempera-
tures. At the beginning of compression, a sufficient quantity of water is injected
to cause the steam to be compressed in the saturated state, so that the equa-
tion v. 1.135 11.11 expresses its condition; at the end of the compression
stage such steam passes direct into the dry saturated condition; and, with
regard to expansion, its state is represented by the equation pl 333 v
The average of the pressures determines the dimensions of the cylinder (or
cylinders) which will render the losses from cooling very slight if the process
be carried out satisfactorily with a high minimum temperature, with compres-
sion effected early and carried to a high degree, with steam which is dry while
being forced out of the cylinder, and consequently with cylinder walls being
dry during the filling or charging stage, and further with a high average tempera-
ture of the cylinder walls.
The mean pressure is raised by increased charges, higher steam pressures,
higher superheater temperatures and a more considerable cooling of the steam
during compression. The machine is regulated by governing the charge or the
pressure of the steam, or both concurrently and further by regulating the quan-
tity of water injected and the temperature of the superheater.
Even where the excess pressure of the injection water under pressure is main-
tained at a uniform degree, it is still advisable, in view of the varying terminal
expansion pressure, to control the quantity of injection water by means of a
special governor or regulator.
The temperature of the, superheater may be regulated by an attendant, or it
may be controlled automatically by the engine governor, or a regulator of the
expansion-temperature, the sectional area of the smoke or gas flues; or by means
of a chimney steam-jet ventilator" (or fan), operated by the varying surplus
quantity of steam produced from the amount of water injected, in engines (such
as locomotive and marine engines), having varying strains to overcome.
**
Inasmuch as the expansion cylinder cannot be provided with means for surface
cooling (or a cooling jacket), it is necessary, where surface-cooling is employed,
that the process should either be carried out in two cylinders the first being
an expansion cylinder, and the second a compression cylinder, or the cylinder
may be connected at each stroke with a surface or injection-condenser in a similar
manner to what is done in existing condensing engines.
Where the process is performed with single expansion and two cylinders are
used, the cylinders may be arranged either one behind the other or side by side.
When two cylinders are arranged side by side a chamber may be interposed
between them, so that the steam which has expanded in one cylinder being
cooled in the said chamber by injection; and in the other cylinder, during
compression, by the cooling of the cylinder casing. Both in this case and in
cases where a single cylinder is employed and the spaces on the opposite sides
of the piston in such single cylinder are placed in communication alternately

page_text: with a separate space or special chamber into which the water is injected, it
is not absolutely necessary to use distilled injection water; where, however,
the process is carried out in a cylinder into which the water is injected direct,
such water should be first distilled.
Where the cooling effect is obtained merely by a cooling jacket, it is somewhat
difficult to control such cooling if the load or strain put upon the engine varies.
It may, however, be controlled, by causing the governor of the engine to act
either upon a regulating device inserted into the cooling water supply or dis-
charge pipe, or upon a force pump.
In steam engines hitherto employed, whenever it happens that the super-
heating effect and the charge attain such a degree (viz., superheating 360°;
charge 20%) that at the end of the expansion process, the steam no longer passes
into the saturated condition, the said engines exhibit all the defects of a hot
air engine; for in that case the pores in the cylinder walls open, steam escapes
when a high degree of steam pressure is reached, and the parts of the cylinder
and piston which are subject to friction becomes damaged or destroyed, as,
under these circumstances, the steam contributes neither to their lubrication
nor to their cooling.
These disadvantages are obviated by making the engines in question single-
acting, or by using multiple-expansion engines with preliminary and inter-
mediate superheating by a superheater of low temperature.
=
If the
In a steam engine constructed according to this invention these drawbacks
do not arise, if the steam, at the beginning and during the progress of com-
1.135 of the curve
pression be sufficiently cooled to make the formula v 1,1.135
P
of compression representative of the condition of the saturated steam.
steam in front of the piston, (i.e. during compression), continues saturated during
the whole time of the stroke, double-acting cylinders even at very high super-
heater-temperatures and with considerable charges may be used.
When steam is cooled down to such a degree that at the end of the compression
stage it passes from the saturated to the dry condition, the losses to which the
cooling process gives rise during the filling or charging and which, in steam
engines now in use are by no means inconsiderable, will be very slight if the
high steam pressures here contemplated (viz., from 15 to 50 atmospheres), be
kept up, because the temperature of the dry compressed steam, as it is driven
out, approximately coincides with the main temperature of the cylinder walls.
As the temperatures beween the friction surfaces of the cylinder and piston
are very considerably lower than the temperature of the superheating steam which
is being admitted, and as the piston moves towards that side of the cylinder
which contains the exhaust steam, the ordinary mode of admitting oil to the
cylinder (superheated steam lubrication) is disadvantageous at somewhat high
temperatures, whereas the lubrication of the exhaust steam, obtained by admit-
ting the oil to the exhaust steam, together with the injection water, or, if
preferred, by means of an oil force-pump, so that the oil is reduced to spray
by the water injected along with it, or by injecting such oil into the expanding
steam, the difficulties which have hitherto been experienced in connection with
the lubrication of steam engines are removed.
By this improved mode of introducing the lubricants, oils may be used, the
point of evaporation of which is considerably below the superfieater-temperature,
such lubricants evaporate immediately on reaching, or indeed, before they reach
the superheater, and are thereby rendered innocuous and safe, provided they have
been previously separated or vapourised, as far as may be, in a powerfully acting
dephlegmator. During the cooling process, by the injection of water, the
escaping surplus steam carries away the minute traces of oil which had not been
separated or vapourised.
The maximum admissible temperature and the fullest possible charge or filling
of the improved steam engines suitable for this means of lubrication, and the
method of cooling the. exhaust steam during compression, do not, therefore,

page_text: depend upon the temperature at which the superheater becomes red hot. Hence
it is practicable to carry the temperatures to considerably higher degrees than
hitherto, and the engine may be conveniently made to operate with normal
fillings or charges of from 40 to 50%, because the heat of evaporation is recovered,
while the fall of temperature at high pressures and substantial charges, is less
than it is in the high pressure cylinder of a compound steam engine. With
such high temperatures, full charges, and high steam pressures, useful mean
pressures of from 1 to 5 kilogrammes per centimetre square, may be obtained;
the engines may be made double-acting; the dimensions of the cylinders may
be exceptionally small, and consequently the loss from cooling may be reduced
to such a minimum that, where very long steam pistons are used, (fitted with
compressing rings (or packing) at or near the ends and having non-conducting
material, such as asbestos, inserted between them) the expenditure of heat by
a single-cylinder engine, per hour and per effective H.P., will only amount to
from 1300 to 1500 thermal units; while in steam engines now in use, where
the evaporation heat is not recuperated, the expenditure of heat amounts to
from 3000 to 5000 thermal units.
Inasmuch as, in the event of the heating surface of the superheater breaking;
no steam is suddenly evolved, (there being no large volumes of water in the
heating apparatus) very high steam pressures may be utilised, if the steam be
slightly saturated before superheating. if as great a speed as possible be imparted
to the steam in the superheater, and if the steam be so directed that a portion of
it enters the superheater at the point where the heating gases are hottest, and
where the steam and heating gases enter in parallel currents, while the remainder
of the steam enters the superheater at the part where the heating gases are
coldest, and where such steam and the said heating gases enter in opposite
currents.
The injection of water into the superheated steam having the effect of adding
to the weight of the volume of exhaust steam, and also consequently increasing
the weight of the volume of compressed fresh steam, so that the heat, which by the
water injected is converted into steam, becomes lost together with the steam in
excess, it follows that a portion of the heat which has been saved must be lost
again. This loss, however, is slight and may be partly or wholly avoided by
utilising the surplus steam in a special working cylinder. or, for heating and
cooking purposes, in central heat distributing stations, for producing forced
draught in chimneys, or for other purposes.
The steam in excess, where the load or strain which the engine has to over-
come is increasing, serves to make up for the extra expenditure of steam or
of evaporation heat (as the case may be) and therefore answers the same purpose
as that of water in a steam boiler.
As in this improved steam engine the evaporation heat is restored and as
the reduction of temperature in a single-cylinder engine, (given high steam
pressures and the possibility of using considerable charges, or fillings) is less
than in the high pressure cylinder of a compound steam engine, economy of any
consequence can be effected in a compound engine only, or where it is compul-
sory to make the single-cylinder engine work with very considerable charges
and where there is no opportunity of utilising the surplus steam evolved by the
injection of water, or where, for the purposes of a directly heated superheater
and with a view to deriving full benefit from the fuel, the quantity of water
injected, while high temperatures prevail in the combustion chamber, is such.
that the compressed steam enters the superheater at from about 3 to 10° of
saturation.
Let it be assumed, by way of illustration, that the improved engine is con-
structed in the form of a double expansion engine. In that case the steam,
as it passes once through the engine. will be heated once or twice, and the low
pressure cylinder will be worked with either a fixed or a varying charge, such
low pressure cylinder compressing the steam to its initial pressure. If the low

page_text: pressure cylinder be worked with a charge variable by means of the governor,
it will be expedient so to construct the valve gear and regulating mechanism,
that the relation between the charges of the high pressure cylinder and the low
pressure cylinder shall invariably be the same. Where a Rider" piston-
distributing device is employed, both valve gears may be fitted with one common
valve rod and one common governor rod, the angles at which the edges of the
ports and slides are inclined being determined in accordance with the varying
charges.
=
In order to render possible the regular operation of a double-expansion engine,
with intermediate superheating. the arrangement is preferably such that the low
pressure evlinder which compresses the steam to its initial pressure may receive
at one stroke the same quantity by weight (of steam) as that which is admitted
into or discharged from the high pressure evlinder (as the case may be). Where
this is the case the steam, in the superheating process will follow Gay Lussac's
V Τ
law
so that, if V denotes the volume of steam for one stroke of the high
V T,
pressure cylinder: T, the absolute temperature of the steam as it leaves the
high pressure cylinder. V,, the volume, and T₁, the absolute temperature of this
quantity of steam after superheating: the volume which the low pressure
cylinder or condenser must draw in at each stroke may be worked out from
the formula V₁ = V 77 provided that the whole of the exhaust steam is drawn
in and compressed. The process may also be carried out in a double expansion
engine by superheating the steam before it enters the high pressure cylinder,
and by injecting water into the low pressure cylinder, or if desired into a
condenser placed in communication with such low pressure cylinder at a con-
venient moment, the steam being compressed to its initial pressure during the
return of the piston in the low-pressure cylinder.
T₁ 1
This method of carrving out the invention may be adopted with advantage
where. (given a directly heated superheater) it is desired to superheat steam
brought to the maximum degree of saturation.
The steam collector is provided with a directly weighted safety valve, whereby
the surplus steam resulting from the injection of water is conducted into a closed
pipe mounted over the said valve and thence to the place where it is to be
utilised for heating or cooking purposes or for working an ordinary steam engine.
A small safety valve is provided which allows steam to escape into the atmos-
phere and thus serves to control the amount of water injected, the temperature
of the superheater, and the initial pressure of the steam.
Instead of steam. other suitable vapours may be employed.
The mean useful pressure may be raised by increased water injection, or if
preferred by the saturation of the compressed steam to an extent varying between 2
and 10% and also by allowing a portion of the steam in excess to escape dur-
ing compression, through adequate automatic valves or properly controlled
cut-off devices either into a chimney for increasing the draught, into a steam
collector for heating and cooking purposes, or into the atmosphere.
The improved steam engine may be arranged horizontally and be provided
with steam in-let valves worked in the same manner as those of existing engines
and the steam out-let valves may be automatic valves through which the com-
pressed steam is forced, by means of the piston through a powerful dephlegmator
of any well-known construction and thence into a superheater heated directly
or indirectly a spray-producing appliance (one of Korting's "dispersing jets.")
may be emploved fitted with a helical path or course, through which water under
pressure, supplied through a copper pipe and through a valve under an excess
of pressure of from 6 to 10 atmospheres, is, during compression,-i.e. at the
beginning of the return stroke of the piston,--injected into the cylinder, or if
preferred, into a chamber connected with such cylinder at the opportune moment.
for the purpose of bringing about the difference of temperature, (or cooling
effect) required to gain work.

page_text: The quantity of liquid to be injected, which should correspond to the load
or strain to be overcome by the engine at the time, is regulated by means of a
valve which may be either conical or flat seated and operated by a pivoted lever
and provided with a friction roller acted on by a cam to open the valve and keep
it open until the quantity of liquid required for the production of work is
injected. The cam is prevented from turning out of position upon its shaft
by means of a groove and tongue arrangement; while it is capable of moving
upon its said shaft in the axial direction. The cam is so constructed with wedge-
shaped tappets that the valve is invariably opened at the beginning of the stroke
whenever the piston reaches the same predetermined position and to close the
valve sooner or later according to the longitudinal position of the cam on its
.
shaft
53
The axial displacement of the cam may be effected through the agency of a
centrifugal governor. The rolling surfaces or races of the friction roller on
the lever are arranged in relation to the engine shaft, and consequently to its own
axis, so as to correspond with the longitudinal sides of the wedge-shaped tappet
of the cam, that is to say they are partly parallel thereto, and partly inclined at
the same angle as the wedge shaped tappets.
The oil for lubricating the cylinder is admitted in drops in the well-known
manner, by means of a small force pump, through a small copper tube, the
arrangement being such that, as previously described, the oil is dispersel into
spray by the water injected and imparted to the comparatively cold steam in
the compression chamber.
Dated this 23rd day of October 1899
JOHNSONS & WILCOX,
47, Lincoln's Inn Fields, London, W.C., Agents.
COMPLETE SPECIFICATION.
Improvements in or connected with Steam Engines.
I, JACOB MISSONG, of 17, Brunengstreet, Hoechst-on-the-Maine, in the German
Empire, Engineer, do hereby declare the nature of this invention and in what
manner the same is to be performed, to be particularly described and ascer-
tained in and by the following statement:-
This invention relates to means for increasing the working capacity of steam
engines for a given consumption of steam, the exhaust steam from the engine
being compressed to the initial pressure of the live steam, such steam being
superheated in a preliminary and intermediate stage before being admitted to
perform its work, and cooled down before and during compression, so that, dur-
ing expansion and condensation, a considerable useful effect is secured.
The present invention is based upon the laws of thermo-dynamics which
state that heat and work are equivalent; that all substances may, by heating
and cooling, be rendered available for work, or in other words, that motive power
may be derived from any variation of temperature; that losses owing to inter-
change of heat between the steam and the cylinder-walls may-be reduced, by
maximum super-heater temperature by a maximum filling" (or
charge): by a high degree of compression, by the possibility
of using double-acting (or compound) cylinders; by an inconsiderable
fall (or decline) of the temperature, by a maximum speed of the piston, and by
reduced dimensions of the cylinder (or cylinders); and that a material increase
of motive power in comparison with single cylinder steam engines and multiple-
expansion engines with preliminary and intermediate superheating may be
effected only where the exhaust steam is restored by compression to the initial
pressure,

page_text: An increase in the useful effect of steam engines, may therefore be obtained
by compressing the exhaust steam,(which is being at the same time, or has
been previously, cooled, say, by injection or surface cooling,)--to the initial
pressure; and using the heat imparted, for drying and superheating, the com-
pressed steam; such steam being only cooled sufficiently to prevent the super,
heater from burning and to enable the temperature,(where the superheater
is heated direct) to be maintained at a sufficiently high degree to admit of the
fullest possible advantage being taken of the heating power of the fuel, so that,
the useful effect will be due almost exclusively to the heat of the superheater,
and the loss from cooling will be reduced to a minimum owing to the super-
heating and compression of the steam to its initial pressure before the com-
pletion of the return stroke of the piston. If water be injected into the super-
heater direct, the steam may be compressed down to a dry saturated condition.
The main feature of the present invention is that the latent-heat in the exhaust
steam which in existing steam engines either escapes into the atmosphere, or
departs along with the condensation water, is,-restored by compression to the
initial pressure: while at the same time the working steam from the boiler is
dried and superheated, before being admitted to the cylinder (or cylinders) and
is during its admission and expansion stages in the cylinder (or cylinders),
sufficiently saturated, to prevent the superheater from burning, and obviate,
as far as possible loss arising from cooling.
Figures 1, 2, 3 and 4 of the accompanying drawings are diagrams illustrating
the work performed under such conditions the hatched portions representing
the work done which varies according to different steam pressures, different
"fillings (or charges) and different superheated temperatures.
In Fig. 1 represents the constant pressure in superheating from 214°
to 360°.
In Fig. 2 de is the curve of compression when, before compression, steam
is allowed to issue for heating and cooking purposes.
-b constant pressure in superheating from 214° to 360°.
In Fig. 3 - represents the constant pressure in superheating from 197°
to 400°..
In Fig. 4 a represents the constant pressure in superheating from 235°
to 460° bc adiabatic expansion, ad reduction of temperature, de cooling
and compressing the saturated steam down to the dry condition and to its initial
pressure and e-a forcing the dry saturated steam out of the cylinder into a
dephlegmator and superheater.
The shaded parts of the diagrams represent the work gained by means of
the superheating heat.
At the beginning of compression, a sufficient quantity of water is injected to
cause the steam to be compressed in the saturated state, so that at the end of
the compression stage such steam is in a dry saturated condition.
The average of the pressures represented by the hatched surfaces in the
diagrams determines the dimensions of the cylinder (or cylinders) which will
render the losses from cooling very slight if the process be carried out satisfactorily
with a high minimum temperature, with compression effected early and carried
to a high degree, with steam which is dry while being forced out of the cylinder,
and consequently with cylinder walls dry during the filling or charging stage,
and further with a high average temperature of the cylinder walls.
The mean pressure is raised by increased charges, higher steam pressures,
higher superheater temperatures and a more considerable cooling of the steam
during compression. The machine is regulated by governing the charge or the
pressure of the steam, or both concurrently and further by regulating the quan-
tity of water injected and the temperature of the superheater.
Even where the excess pressure of the injection water under pressure is main-
tained at a uniform degree it is still advisable, in view of the varying terminal

page_text: expansion pressure, to control the quantity of injection water by means of a
special governor or regulator.
The temperature of the superheater may be regulated by an attendant, or it
may be controlled automatically by the engine governor, or a regulator of the
expansion-temperature, the sectional area of the smoke or gas flues; or by means
of a chimney steam-jet ventilator" (or fan), operated by the varying surplus
quantity of steam produced from the amount of water injected, in engines (such
as locomotive and marine engines), having varying strains to overcome.
Inasmuch as the expansion cylinder cannot be provided with means for surface
cooling (or a cooling jacket), it is necessary, where surface-cooling is employed,
that the process should either be carried out in two cylinders-the first being
an expansion cylinder, and the second a compression cylinder-or the cylinder
may be connected at each stroke with a surface or injection-condenser in a similar
manner to what is done in existing condensing engines.
Where the process is performed with single expansion and two cylinders
are used, the cylinders may be arranged either one behind the other. or side
by side. Fig. 5 shows an arrangement of two cylinders E, C, arranged side by
side with a chamber K interposed between them, so that the steam which has
expanded in one cylinder E is cooled in the said chamber K by injection; and
in the other cylinder C, during compression, by the cooling of the cylinder casing.
Both in this case and in cases where a single cylinder is employed and the spaces
on the opposite sides of the piston in such single cylinder are placed in com-
munication alternately with a separate space or special chamber into which the
water is injected, it is not absolutely necessary to use distilled injection water:
where, however, the process is carried out in a cylinder into which the water
is injected direct, such water should be first distilled.
Where the cooling effect is obtained merely by a cooling jacket, it is somewhat
difficult to control such cooling if the load or strain put upon the engine varies.
It may, however, be controlled by causing the governor of the engine to act
either upon a regulating device inserted into the cooling water supply or dis-
charge pipe, or upon a force pump.
In steam engines hitherto employed, whenever it happens that the super-
heating effect and the charge attain such a degree (viz. superheating 360°:
charge 20%) that at the end of the expansion process, the steam no longer passes
into the saturated condition, the said engines exhibit all the defects of a hot
air engine for in that case the pores in the cylinder walls open, steam escapes
when a high degree of steam pressure is reached, and the parts of the cylinder
and piston which are subject to friction become damaged or destroyed, as,
under these circumstances, the steam contributes neither to their lubrication
nor to their cooling.
These disadvantages are obviated by making the engines in question single-
acting, or by using multiple-expansion engines with preliminary and inter-
mediate superheating by a superheater of low temperature.
In a steam engine constructed according to this invention, these drawbacks
do not arise, if the steam, at the beginning and during the progress of com-
pression be sufficiently cooled to a condition of the saturated steam. If the steam
in front of the piston,-(.e. during compression) continues saturated during the
whole time of the stroke, double-acting cylinders even at very high superheater-
temperatures and with considerable charges may be used.
When steam is cooled down to such a degree that at the end of the compression
stage it passes from the saturated to the dry condition. the losses to which the
cooling process gives rise during the filling or charging and which. in steam
engines now in use are by no means inconsiderable, will be very slight if the
high steam pressures here contemplated (viz., from 15 to 50 atmospheres) be
kept up. because the temperature of the dry compressed steam, as it is driven
out, approximately coincides with the main temperature of the cylinder walls.

page_text: As the temperatures between the friction surfaces of the cylinder and piston
are very considerably lower than the temperature of the superheated steam which
is being admitted, and as the piston moves towards that end of the cylinder
which contains the exhaust steam, the ordinary mode of admitting oil to the
cylinder (superheated steam lubrication) is disadvantageous at somewhat high
temperatures, whereas the lubrication of the exhaust steam, obtained by admit-
ting oil to the exhaust steam, together with the injection water, or, if
preferred, by means of an oil force-pump, so that the oil is reduced to spray
by the water injected along with it, or by injecting such oil into the expanding
steam, the difficulties which have hitherto been experienced in connection with
the lubrication of steam engines are removed.
By this improved mode of introducing lubricants, oils may be used, the
point of evaporation of which is considerably below the superheater temperature,
such lubricants evaporate immediately on reaching, or indeed, before they reach
the superheater, and are thereby rendered innocuous and safe, provided they have
been previously separated or vapourised, as far as may be, in a powerfully acting
dephlegmator. During the cooling process, by the injection of water, the
escaping surplus steam carries away any minute traces of oil which may not
have been separated or vapourised.
The maximum admissible temperature and the fullest possible charge or filling
of the improved steam engines suitable for this means of lubrication, and the
method of cooling the exhaust steam during compression, do not, therefore,
depend upon the temperature at which the superheater becomes red hot. Hence
it is practicable to carry the temperatures to considerably higher degrees than
hitherto, and the engine may be conveniently made to operate with normal
fillings or charges of from 40 to 50%, because the heat of evaporation is recovered,
while the fall of temperature, at high pressures and substantial charges, is less
than it is in the high pressure cylinder of a compound steam engine. With
such high temperatures, full charges, and high steam pressures, useful mean
pressures of from 1 to 5 kilogrammes per centimetre square, may be obtained;
the engines may be made, double-acting; the dimensions of the cylinders may
be exceptionally small, and consequently the loss from cooling may be reduced
to such a minimum that, where very long steam pistons are used,-(fitted with
compressing (or packing) rings at or near the ends and having non-conducting
material, such as asbestos, inserted between them) the expenditure of heat by
a single-cylinder engine, per hour and per effective H.P., will only amount to
from 1300 to 1500 thermal units; while in steam engines now in use, where
the evaporation heat is not recuperated, the expenditure of heat amounts to
from 3000 to 5000 thermal units.
Inasmuch as, in the event of the heating surface of the superheater breaking,
no steam is suddenly evolved,-(there being no large volumes of water in the
heating apparatus) very high steam pressures may be utilised, if the steam be
slightly saturated before superheating, if as great a speed as possible be imparted
to the steam in the superheater, and if the steam be so directed that a portion of
it enters the superheater at the point where the heating gases are hottest, and
where the steam and heating gases enter in parallel currents while the remainder
of the steam enters the superheater at the part where the heating gases are
coldest, and where such steam and the said heating gases enter in opposite
currents.
The injection of water into the superheated steam having the effect of adding
to the weight of the volume of exhaust steam, and also consequently increasing
the weight of the volume of compressed fresh steam, so that the heat, which by the
water injected is converted into steam, becomes lost together with the steam in
excess, it follows that a portion of the heat which has been saved must be lost
again. This loss, however, is slight and may be partly or wholly avoided by
utilising the surplus steam in a special working cylinder, or for heating and

page_text: '
cooking purposes, in central heat distributing stations for producing forced
draught in chimneys, or for other purposes.
The steam in excess, where the load or strain which the engine has to over-
come is increasing, serves to make up for the extra expenditure of steam or
of evaporation heat (as the case may be) and therefore answers the same purpose
as that of water in a steam boiler.
As in this improved steam engine the evaporation heat is restored, and as
the reduction of temperature in a single-cylinder engine,-(given high steam
pressures and the possibility of using considerable charges (or fillings),) is less
than in the high pressure cylinder of a compound steam engine, economy of any
consequence can be effected in a compound engine only or where it is compul-
sory to make the single-cylinder engine work with very considerable charges
and where there is no opportunity of utilising the surplus steam evolved by the
injection of water, or where, for the purposes of a directly heated superheater
and with a view to deriving full benefit from the fuel, the quantity of water
injected, while high temperatures prevail in the combustion chamber, is such.
that the compressed steam enters the superheater at from about 3 to 10° of
saturation.
Let it be assumed, by way of illustration, that the improved engine is con-
structed in the form of a double expansion engine. In that case the steam,
as it passes once through the engine. will be heated once or twice, and the low
pressure cylinder will be worked with either a fixed or a varying charge, such
low pressure cylinder compressing the steam to its initial pressure. If the low
pressure cylinder be worked with a charge variable by means of the governor,
it will be expedient so to construct the valve gear and regulating mechanism,
that the relation between the charges of the high pressure cylinder and the low
pressure cylinder shall invariably be the same. Where a "Rider" piston-
distributing device is employed, both valve gears may be fitted with one common
valve rod and one common governor rod, the angles at which the edges of the
ports and slides are inclined being determined in accordance with the varying
charges.
V
T
T
In order to render possible the regular operation of a double-expansion engine,
with intermediate superheating (Fig. 6) the arrangement is preferably such that the
low pressure cylinder which compresses the steam to its initial pressure may receive
at one stroke the same quantity by weight (of steam) as that which is admitted
into or discharged from the high pressure cylinder (as the case may be). Where
this is the case the steam, in the superheating process will follow Gay Lussac's
law. == so that, if V denotes the volume of steam for one stroke of the high
T,"
pressure cylinder: T, the absolute temperature of the steam as it leaves the
high pressure cylinder, V,, the volume, and T₁, the absolute temperature of this
quantity of steam after superheating the volume which the low pressure
cylinder or condenser_must draw in at each stroke may be worked out from
the formula V₁ V-
=
provided that the whole of the exhaust steam is drawn
in and compressed. The process may also be carried out in a double expansion
engine by superheating the steam before it enters the high pressure cylinder,
and by injecting water into the low pressure cylinder, or if desired into a
condenser placed in communication with such low pressure cylinder at a con-
venient moment. the steam being compressed to its initial pressure during the
return of the piston in the low pressure cylinder.
Ꭲ
יT
This method of carrving out the invention may be adopted with advantage
where. (given a directly heated superheater,) it is desired to superheat steam
brought to the maximum degree of saturation.
The steam collector is provided with a directly weighted safety valve, whereby
the surplus steam resulting from the injection of water is conducted into a closed

page_text: pipe mounted over the said valve and thence to the place where it is to be
utilised for heating or cooking purposes or for working an ordinary steam engine.
A small safety valve is provided which allows steam to escape into the atmos-
phere and thus serves to control the amount of water injected, the temperature
of the superheater, and the initial pressure of the steam.
Instead of steam, other suitable vapours may be employed.
The mean useful pressure may be raised by increased water injection or if
preferred by the saturation of the compressed steam to an extent varying between 2
and 10% and also by allowing a portion of the steam in excess to escape dur-
ing compression, through adequate automatic valves or properly controlled
cut-off devices either into a chimney for increasing the draught, into a steam
collector for heating and cooking purposes, or into the atmosphere.
Figs. 7, 8 and 9 show by way of example one form of construction of the
improved steam engine with the cylinder arranged horizontally. E' are steam
in-let valves worked in the same manner as those of existing engines. The
steam out-let valves A may be automatic valves through which the compressed
steam is forced, by means of the piston through a powerful dephlegmator of
any well-known construction, and thence into a superheater heated directly
or indirectly.
Z is a spray-producing appliance (one of Körting's "dispersing jets"); fitted
with a helical path or course, through which water under pressure, supplied
through a copper pipe and through a valve v, under an excess of pressure of
from 6 to 10 atmospheres, is, during compression,-i.e. at the beginning of the
return stroke of the piston,-injected into the cylinder, or if preferred, into a
chamber connected with such cylinder at the opportune moment, for the purpose
of bringing about the difference of temperature (or cooling effect) required to
gain work.
The quantity of liquid to be injected, which should correspond to the load
or strain to be overcome by the engine at the time, is regulated by means of
the valve which may be either conical or flat seated and guided by means of
a cylindrical rods and operated by a lever L pivotted at and provided with
a friction roller R acted on by means of a cam S placed upon the working shaft W
and provided with tappets 1 to open the valve and keep it open until the quantity
of liquid required for the production of work is injected. The cam S is pre-
vented from turning upon its shaft W by means of a groove and tongue arrange-
ment, while it is capable of moving upon its said shaft in the axial direction.
Each tappet or projection 1 of the said distributing cam is, as will be seen from
the plan Fig. 8, made to extend in the longitudinal direction of the working
shaft W in the shape of a wedge, one side of the same being parallel to the axis
of the shaft. Consequently the valve is invariably opened at the beginning
of the stroke whenever the piston reaches the same predetermined position, while
the opposite side of the wedge shaped tappet is inclined towards the cylinder,
or in other words towards the axis of the operating shaft W, so that the valve
is closed sooner or later according to the longitudinal position of the cam S on its
shaft.
or
The axial displacement of the cam S takes place in the manner illustrated in
Fig. 9
through the agency of a centrifugal governor G. The rolling surfaces
races of the friction roller R on the lever are arranged in relation to the
engine shaft, and consequently, to its own axis, so as to correspond with the
longitudinal sides of the wedge-shaped tappets D, that is to say they are partly.
parallel thereto, and partly inclined at the same angle as the wedge shaped
tappets I).
The oil for lubricating the cylinder is admitted in drops, in the well-known
manner, by means of a small force pump, through a small copper tube r¹, the
arrangement being such that, as previously described, the oil is dispersed inio
spray by the water injected and imparted to the comparatively cold steam in
the compression chamber.

page_text: Having now particularly described and ascertained the nature of this inven
tion and in what manner the same is to be performed I declare that what I
claim is -
1. Increasing the working capacity of steam engines for a given consumption
of steam, by compressing to the initial pressure of the live steam, the exhaust
steam from the steam engine after it is cooled or while it is being cooled and
then superheating the said steam before admitting it to the cylinder substanti-
ally as herein before described.
2. Means for increasing the working capacity of steam engines by compressing,
after cooling or while being cooled, the exhaust steam from the steam engine,
and then superheating the said steam together with cooling fluid injected into
the cylinder or into the superheater, the said exhaust steam and cooling fluid
being thus converted into workable steam whilst during the return stroke of
the piston as much steam as that generated from the cooling fluid may be per-
mitted to escape from the cylinder in order to raise the mean useful pressure
in the cylinder which escaping steam may be employed for cooking or heating
purposes substantially as herein before described.
3. In the process characterised in the first claim in multiple expansion engines,
determining the dimensions of the sectional area of the low pressure cylinder
and regulating the filling or charge of the same in such a manner that it shall
at each stroke draw in the same quantity of steam as that which leaves the high
pressure cylinder or the medium pressure cylinder (if any).
4. In the process characterised by the first claiming clause the admission of
the cylinder lubricant (during compression or expansion) at steam temperatures
being considerably below that of the superheater.
5. In the process characterised by the first claiming clause regulating the
quantity of water injected by means of a valve operating or controlling cam S
movable in the axial direction and having a wedge shaped projection or tappet I)
and a friction roller R the rolling surface of which is partly cylindrical and
partly conical.
6. The combination of apparatus hereinbefore described for. increasing the
useful effect of steam employed in steam engines substantially as hereinbefore
described.
Dated thi 0Qt1 dow of Tul, 1000
JOHNSONS & WILLCOX,
47, Lincoln's Inn Fields, London, W.C., Agents.