Improvements in Steam Turbines.
Year: 1890

page_text: Date of Application, 22nd Jan., 1890
Complete Specification Left, 22nd Oct., 1890-Accepted, 22nd Nov., 1890
PROVISIONAL SPECIFICATION.
Improvements in Steam Turbines.
1, The Honourable CHARLES ALGERNON PARSONS of the firm of C. A. Parsons and Co.
Engineers, Heaton Works, Newcastle-on-Tyne in the County of Durham, Engineer,
do hereby declare the nature of this invention to be as follows:-
In steam turbines of the kind at present in use the steam is caused to perform
work by alternate impact upon and reaction from a large number of rotating vanes or
blades, and the steam is suitably directed or guided by fixed vanes or blades of
convenient shape and disposition. In such motors it is impossible to obtain the
maximum economy in the consumption of steam unless the clearances between the
rotating blades and the enclosing conical, disc or cylindrical surfaces and the fixed
blades and rotating surfaces is very small. This necessitates considerable delicacy in
the adjustment and accuracy in the construction of the motors, and renders it difficult
to keep them in such condition as to bearing surfaces that the best economy may be
obtained in practical work through a long term of years. The main object of my
invention is to improve the arrangement and details so as to obtain a greater economy
and efficiency from steam turbines than has been hitherto possible while avoiding
unduly small clearances. At the same time I simplify the construction and diminish
the expense of manufacture.
According to one part of my invention as applied to turbines of the inward flow
type-I arrange a series of inward flow turbine wheels, upon one rotating shaft or
spindle and enclose in one cylinder or case containing the directing vanes or guide
blades, in such manner that steam entering the first of the series passes successively
through each before being discharged into the atmosphere or condenser. The turbine
wheels consist of metallic discs combined with bushes which are slipped upon the shaft
Each disc
or spindle and firmly keyed or fixed to it in any other convenient manner.
carries upon a face or faces or upon an edge or edges one or more series of blades of
suitable shape and curvature in which the general direction is that of radiation from
the centre towards the circumference. The enclosing case or cylinder, preferably made
in halves, carries ring projections and guide blades or vanes, and the ring projections
are arranged so as to form a series of chambers in which the turbine wheels rotate.
Each wheel chamber may for facility of construction consist of two rings projecting
from the interior of the cylinder or case to enclose a wheel and the steam is caused
to pass outwards by the first partition or ring and then over a space between it and
the case to the annular space behind the fixed guide blades or vanes which are disposed
around the circumference of the wheel and direct the flow of steam tangentially upon
the blades or vanes of the rotating wheel. After passing the rotating wheel vanes or
blades it flows towards the centre and is brought almost to rest thus giving up the
greater part of its energy of motion to the wheel. The steam then flows through an
annular space around the rotating bush or spindle and is directed outwards by the
next projecting ring partition to the fixed vanes or guide blades of the next wheel in
the series, there to experience a further fall in pressure and a further expansion,
and so on until the desired expansion is accomplished. In order to prevent leakage
from any wheel chamber to the next whereby a portion of steam would be allowed to
pass without flowing through the guide blades, I carry the first partition ring of each
chamber close to the rotating bush carrying the wheel or close to the spindle itself,
and I sometimes turn grooves or a series of grooves in the portions of bush or spindle,
and ring, opposing each other, which grooves and projections may alternately project
into each part without touching or nearly touching laterally or longitudinally. In

page_text: order to reduce leakage past the faces of the rotating vanes or blades moving near the
enclosing partition, I sometimes cast or otherwise attach a ring to the lower edge of
those vanes or blades or otherwise sbroud the blades which project under the fixed
partition ring and by so baffling the steam I diminish leakage. At all surfaces where
leakage is likely to occur, which surfaces of course cannot be packed or rotated in
close contact with pressure I may arrange alternate recesses and projections or recesses
only to give the steam a tortuous path and reduce leakage. The fixed guide blades I
prefer to form part of one of the partition rings and I bore and turn the case in a
suitable way to allow of the easy manufacture and insertion of the rings. I may
however cast case and vanes with its partition rings together, if I desire to do so, and
this course may be the more convenient in the construction of large turbines.
The series of turbine wheels may be mounted on a conical, stepped or cylindrical
spindle, as circumstances may require and the successive wheels may be of the same
diameter or different diameters, generally increasing, as determined by the desired
amount of expansion, the number of, and discharge area at, the guide blade orifices;
and the number and configuration of moving blades, is also varied to suit the various
conditions of steam pressure and expansion. Although I prefer the inward flow
turbine, an outward flow steam turbine may also be arranged in the inanner and
with the distinctive features I have described, in which case the annular
herein before described are reversed in order-the rotating blades or vanes discharging
from centre to circumference to the fixed blades instead of from the fixed blades to
the rotating.
passages
According to another part of my invention which relates to the spindle or bearing
arrangements of steam turbines, I construct hollow spindles to rotate in bushes at
both ends of the turbine spindle, and in these hollow spindles I carry the ends of the
turbine spindle so connected by rings, alternately fitting the interior and exterior
surfaces and clipped under elastic pressure, that when the turbine wheels revolve at a
high velocity any departure from true dynamic balance is self correcting-that is,
the ends of the turbine spindle nove within the rotating tube ends until they find the
position where the dynamic or principal axis coincides with the axis of actual rotation.
When this occurs the turbine runs without vibration at the highest velocities. This
freedom of adjustment may be obtained in various ways, as for example by turning
cup or disc projections upon the ends of the hollow spindles external to the bearings
and fitting the adjusting plates, spring arrangements or other moving pieces, in
these ends to allow of movement within pre-determined limits. Instead of allowing
freedom of the rotating spindle to settle at its dynamic axis I sometimes damp the
vibration caused by slight want of balance by means of the following contrivance ;-
The spindle ends run in a bush fixed into another bush, with slight freedom of fit and
this into another and so on, giving a number of concentric bushes having slight
play the one within the other. Tho ends of these bushes I fit into a case with some
nicety of end fit, and fill the case with oil, the outer bush being fixed securely. Any
vibrating movement is now checked or damped by the forcing out of oil between the
bushes and the ends and circumferentially around the bushes, so that although a
slight movement is possible yet it is resisted in whatever direction it may tend to
move. Spring supported bearings may be used and hydraulic resistance of other
kinds may be interposed such as that due to a small cylinder or ram. Sometimes
I surround the bush in which the spindle runs with segments of a thin cylinder or
tube which segments may be of greater or less curvature than the outer surface of
the bush and so cause bearing of the segment ends upon the exterior of the bush
or the interior of the bored surface holding it. This arrangement gives a spring
or elastic movement and when oil or other liquid is present the hydraulic resistance
already hereinbefore described is also brought into play.
In order to prevent leakage of steam past the spindle, I arrange a series of grooves
or projecting collars upon the spindle fitting into or working easily in a similar series
of grooves in an end bush and by using a sufficient number, leakage may be reduced
to any desired extent. Instead of this metallic packing rings may be used. When
.

page_text: the steam turbine is arranged so that there is end thrust in any direction and to obviate
end wear for an inevitable small end thrust, I may take that end thrust in a thrust
block of construction similar to those used in marine engines, but in order to secure
that each thrust collar shall take its share of the pressure and so produce a uniform
slight pressure over a considerable surface which uniformity is necessary to run cool
at high velocities, sometimes I arrange my thrust collars or flanges to have a slight
elastic movement bringing them to bear with a predetermined pressure upon their
respective collars on the turbine spindle. I thus distribute the pressure upon the
surfaces accurately and make certain that no one surface is subject to undue pressure.
This end may be accomplished in many ways the essence of which consists in allowing
each thrust collar or flange a small movement in the direction or rather opposing the
direction of thrust and keeping each up to its work by backing springs or so arranging
the collars that each from its construction has a slight elasticity without separate
springs being requisite.
The governing may be accomplished by driving a small high or low speed
centrifugal governor from the turbine spindle by suitable friction gearing and so
actuating a throttle valve, to diminish or increase the steam supply as required.
Sometimes, however, I prefer when the highest economy is desired for all loads to
cause this governor to act as an automatic variable cut off and this may be done in
any well known way, the steam admission valve being arranged to leave as little
clearance as possible between itself and the set of guide blades of the first turbine in
inward flow turbines or between itself and the first turbine in outward flow turbines.
The cut off arrangements are so designed that full steam may be kept on all the time
or cut off at every revolution of the governor spindle and kept off for greater or less
portions of that revolution. One method consists in the use of a conical cam surface
terminating in a cylindrical portion upon the governor sleeve, upon which surface
there rolls a wheel at the end of a lever or slide and by its motion it opens and closes
a valve of any convenient kind. When the speed is slightly too low and full load is
on the motor the wheel rolls upon the cylindrical portion of the sleeve and the steam
valve is kept full open all the time; but as it comes more and more on the rotating
cam surface steam is cut off at every revolution of the governor for a period depending
upon the portion of the cam surface upon which it runs. Thus the full steam pressure
is always applied and the steam turbine is driven by a succession of blasts, of greater
or less duration according to the load. I may cause these blasts to act at regular
intervals and occupy a greater or less part of the interval or 1 may arrange the
governor by suitable gear to have successive blasts of one period of duration but
repeated more or less frequently per minute.
When the engine runs above a certain defined speed or falls below a certain defined
speed so far as is indicated by the governor, I sometimes so shape the cam surface
that steam is entirely cut off.
In order to vary the speed in accordance with the requirements of a dynamo
machine when the steam turbine is utilized to drive a dynamo I arrange the cam or
other cut off contrivance so that it may be controlled from a solenoid suitably
connected; it may also be controlled by an iron bar working between or acted on by
the electro-magnets so that increased excitement of the magnets tends to cut off the
steam supply and diminished excitement tends to increase supply.
In the event of a breakdown I arrange that complete cessation or too rapid
increase or diminution of magnetic intensity alike cut off steam supply. The
solenoid or har movement is suitably resisted by weights or springs. The electrical
governor may act upon a moving sleeve sliding upon a secondary shaft driven from
the main shaft without any centrifugal governor in which case the cut off depends
entirely upon the electrical condition of the dynamo. The steam valve may also be
caused to cut off at intervals by a lever worked by a solenoid and relay arrangement
in which the contact lever periodically sends current to act upon a solenoid whenever
the electric pressure or quantity exceeds normal limits.
A small force pump, either of the centrifugal, rotary, or reciprocating type, is

page_text: sometimes driven from the second motion shaft and serves to force oil for lubricating
the bearings.
Dated this 21st day of January 1890.
MARKS & CLERK,
13, Temple Street, Birmingham, Agents for Applicant.
COMPLETE SPECIFICATION.
Improvements in Steam Turbines.
. I The Honourable (HARLES ALGERNON PARSONS of Heaton Works Newcastle-
on-Tyne in the County of Durham, Engineer, do hereby declare the nature of this
invention and in what manner the same is to be performed, to be particularly
described and ascertained in and by the following statement :-
In steam turbines of the kind at present in use the steam is caused to perform work
by alternate impact upon and reaction from a large number of rotating vanes or
blades, and the steam is suitably directed or guided by fixed vanes or blades of
convenient shape and disposition. In such motors it is impossible to obtain the
maximum economy in the consumption of steam unless the clearances between the
rotating blades and the enclosing conical, disc, or cylindrical surfaces, and the fixed
blades and rotating surfaces is very small. This necessitates considerable delicacy in
the adjustment and accuracy in the construction of the motors, and renders it difficult
to keep them in such condition as to bearing surfaces that the best economy may be
obtained in practical work through a long term of years. The main object of my
invention is to improve the arrangement and details so as to obtain a greater economy
and efficiency from steam turbines than has been hitherto possible, while avoiding
unduly small clearances. At the same time I simplify the construction and diminish
the expense of manufacture.
According to one part of my invention as applied to turbines of the inward flow
type, arrange a series of inward flow turbine wheels, upon one rotating shaft or
spindle and enclosed in one cylinder or case containing the directing vanes or
guide blades, in such manner that steam entering the first of the series passes
successively through each before being discharged into the atmosphere or condenser.
The turbine wheels consist of metallic discs combined with bushes which are slipped
upon the shaft or spindle and firmly keyed or fixed to it in any other convenient
manner. Each disc carries upon a face or faces or upon an edge or edges one or
more series of blades, of suitable shape and curvature, in which the general direction
is that of radiation from the centre towards the circumference. The enclosing case
or cylinder, preferably made in halves, carries ring projections and guide blades or
vanes, and the ring projections are arranged so as to form a series of chambers in
which the turbine wheels rotate. Each wheel chamber may for facility of construction
consist of two rings projecting from the interior of the cylinder or case to enclose a
wheel in which the steam is caused to pass outwards by the first partition or ring,
and then over a space between it and the case to the annular space behind the fixed
guide blades or vanes which are disposed around the circumference of the wheel, and
direct the flow of steam tangentially upon the blades or vanes of the rotating wheel.
After passing the rotating wheel vanes or blades, the steam flows towards the centre
and is brought almost to rest thus giving up the greater part of its energy of motion
to the wheel. The steam then flows through an annular space around the rotating
bush or spindle and is directed outwards by the next projecting ring partition to the
fixed vanes or guide plates of the next wheel in the series, there to experience a
further fall in pressure and a further expansion, and so on until the desired total
expansion is accomplished. In order to prevent leakage from any wheel chamber to
the next, whereby a portion of steam would be allowed to pass without flowing through
the guide blades, I carry the first partition ring of each chaniber close to the rotating
bush carrying the wheel or close to the spindle itself, and I sometimes turn grooves

page_text: or a series of grooves in the portions of bush or spindle, and ring, opposing each
other, which grooves and projections may alternately project into each part without
touching or nearly touching laterally or longitudinally. In order to reduce leakage
past the faces of the rotating vanes or blades moving near the enclosing partition,
I sometimes cast or otherwise attach a ring to the lower edge of those vanes or blades
or otherwise shroud the blades which project under the fixed partition ring and by
so baffling the steam I diminish leakage. At all surfaces where leakage is likely to
occur which surfaces of course cannot be packed or rotated in close contact I may
arrange alternate recesses and projections, or recesses only to give the steam a
tortuous path and reduce leakage. The fixed guide blades I prefer to form part of
one of the partition rings, and I bore and turn the case in a suitable way to allow of
the easy manufacture and insertion of the rings. I may however cast case and vanes
with its partition rings together, if I desire to do so, and this course may be the more
convenient in the construction of large turbines.
The series of turbine wheels may be mounted on a conical, stepped, or cylindrical
spindle, as circumstances may require and the successive wheels may be of the same
diameter or different diameters, generally increasing, as determined by the desired
amount of expansion, the number of, and discharge area at, the guide blade orifices;
and the number and configuration of moving blades, is also varied to suit various
conditions of steam pressure and expansion. Although I prefer the inward flow
turbine, an outward flow steam turbine may also be arranged in the manner, and
with the distinctive features I have described, in which case the annular passages
hereinbefore described are reversed in order, the rotating blades or vanes dis-
charging from centre to circumference to the fixed blades instead of from the fixed
blades to the rotating. I sometimes damp the vibration caused by slight want of
balance by means of the following contrivance: -
The spindle ends run in a bush fixed into another bush with slight freedom of
fit, and this into another and so on, giving a number of concentric bushes having
slight play the one within the other. The ends of these bushes I fit into a case
with some nicety of end fit but this is not always necessary, and fill the case with
oil, the outer bush being fixed securely. Any vibrating movement is now checked
or damped by the forcing out of oil between the bushes and the ends and circum-
ferentially around the bushes, so that although a slight movement is possible yet
it is resisted in whatever direction it may tend it to move. Spring supported
bearings may be used and hydraulic resistance of other kinds may be interposed
such as that due to a small cylinder or ram. Sometimes I surround the bush in which
the spindle runs with segments of a thin cylinder or tube which segments may be
of greater or less curvature than the outer surface of the bush and so cause bearing
of the segment ends upon the exterior of the bush or the interior of the bored
surface holding it. This arrangement gives a spring or elastic movement and when
oil or other liquid is present the hydraulic resistance already herein before described
is also brought into play.
In order to prevent leakage of the steam past the spindle, I arrange a series of
grooves or projecting collars upon the spindle fitting into or working easily in a
similar series of grooves in an end bush and by using a sufficient number, leakage
may be reduced to any desired extent. Instead of this metallic packing rings may
be used. When the steam turbine is arranged so that there is end thrust in any
direction and to obviate end wear for an inevitable small end thrust, I may take
that end thrust in a thrust block of construction similar to those used in marine
engines, but in order to secure that each thrust collar shall take its share of the
pressure, and so produce a uniform slight pressure over a considerable surface which
uniformity is necessary to run cool at high velocities, sometimes I arrange my thrust
collars or flanges to have a slight elastic movement bringing them to bear with a
predetermined pressure upon their respective collars on the turbine spindle. I thus
distribute the pressure upon the surfaces accurately and make certain that no one
surface is subject to undue pressure. This end may be accomplished in many ways
the essence of which consists in allowing each thrust collar or flange a small

page_text: movement in the direction or rather opposing the direction of thrust and keeping
each up to its work by backing springs or so arranging the collars that each from
its construction has a slight elasticity without separate springs being requisite.
The governing may be accomplished by driving a small high or low speed
centrifugal governor from the turbine spindle by suitable friction gearing and so
actuating a throttle valve, to diminish or increase the steam supply as required.
Sometimes, however, I prefer when the highest economy is desired for all loads, to
cause this governor to act as an automatic variable cut off, and this may be done
in any well known way, the steam admission valve being arranged to leave as little
clearance as possible between itself and the first set of guide blades. The cut off
arrangements are so designed that full steam may be kept on all the time, or cut
off at every revolution of the governor spindle, and kept off for greater or less
portions of that revolution. One method consists in the use of a conical cam
surface terminating in a cylindrical portion upon the governor sleeve, upon which
surface there rolls a wheel at the end of a fever or slide and by its motion it
opens and closes a valve of any convenient kind. When the speed is slightly too
low and full load is on the motor, the wheel rolls upon the cylindrical portion of the
sleeve and the steam valve is kept full open all the time; but as it comes more
and more on the rotating cam surface steam is cut off at every revolution of the
governor for a period depending upon the portion of the cam surface upon which
it runs. Thus the full steam pressure is always applied and the steam turbine is
driven by a succession of blasts of greater or less duration according to the load.
may cause these blasts to act at regular intervals and occupy a greater or less part
of the interval or I may arrange the governor by suitable gear to have successive
blasts of one period of duration but repeated more of less frequently per minute.
When the engine runs above a certain defined speed or falls below a certain defined
speed, so far as is indicated by the governor, I sometimes so shape the cam surface
that steam is entirely cut off.
In order to vary the speed in accordance with the requirements of a dynamo
machine when the steam turbine is utilized to drive a dynamo I arrange the cam or
other cut off contrivance so that it may be controlled from a solenoid suitably
connected; it may also be controlled by an iron bar working between or acted on by
the electro-magnets so that increased excitement of the magnets tends to cut off the
steam supply, and diminished excitement tends to increase steam supply.
In the event of a breakdown I arrange that complete cessation or too rapid
increase or diminution of magnetic intensity alike cut off steam supply. The solenoid
or bar movement is suitably resisted by weights or springs. The electrical governor
may act upon a moving sleeve sliding upon a secondary shaft driven from the main
shaft without any centrifugal governor in which case the cut off depends entirely upon
the electrical condition of the dynamo. The steam valve may also be caused to cut
off at intervals by a lever worked by a solenoid and relay arrangement in which the
contact lever periodically sends current to act upon a solenoid whenever the electric
pressure or quantity exceeds normal limits.
A small force pump, either of the centrifugal, rotary, or reciprocating type, is
sometimes driven from the second motion shaft and serves to force oil for lubricating
the bearings.
Referring to the three sheets of accompanying drawings
Figure (1) is an elevation of my improved steam turbine.
Figure (2) is a longitudinal section; and
Figure (3) a half transverse section.
Figures (4) and (4°) illustrate the application of an electrically controlled
governor.
Figures (5) and (6) show a centrifugal governor as applied to my turbine.
Figure (7) is a longitudinal section of one of my improved bearings and
Figure (7) is an end elevation part in section.
Figures (8) and (8) are longitudinal and transverse sections of another form of
bearing having spring as well as hydraulic action.

page_text: Figures (9). (9) and (9°) are longitudinal and transverse sections of my elastic
collar thrust block arrangements and
Figures (10) and (10) are similar sections of my packing device.
In Figures (1) and (2) the base A carries the turbine case, in two halves B. (
bolted together as indicated; and the spindle J suitably carried at the ends D, D¹ has
keyed or fixed on it the rotating turbine wheels r, and which in the particular
machine illustrated, are of two diameters, six of one diameter and seven of a greater
diameter. These wheels carry blades F more distinctly shown in the transverse
section, Figure (3), upon which the actuating elastic fluid is caused to impinge by
the fixed guide blades E attached to the division rings E. Division rings E' with the
rings E each pair form a complete turbine chamber in which rotates a wheel r or r¹.
The steam or other elastic fluid under pressure enters the turbine case by an inlet
pipe, passing through the throttle or cut off valve casing R2, and thence to the
space G, where the steam passes outside the first of the division rings E by the fixed
guide blades E to the blades F on the first rotating wheel. It then passes, after
leaving the first wheel between the next partition rings E' and E2 to the succeeding
guide blades E which direct it on the blades F of the corresponding rotating turbine
wheel. The steam in this manner passes through the whole series of turbines, the
actuating impulse being given on the inward flow; while the outward flow between
the partitions conducts the steam when discharged, from one turbine chamber to the
next in series, so that when the steam is discharged at the end of G¹ to the exhaust
pipe T, the pressure is reduced to the desired extent and expanded as required to
obtain all the available work. The division rings E' are carried very near to the
rotating spindle, which spindle with the sleeves or bosses carrying the turbine wheels
is kept as small in diameter as possible with the object of reducing leakage from
chamber to chamber by way of the spindle, to a minimum. By this arrangement,
practically the whole of the steam passing from chamber to chamber is caused to
discharge from one chamber to another, by way of the fixed guide blades E, and so
impinges on the blades F of the rotating wheels. In the first division ring E on the
steam admission side G I have marked the portion next the spindle s and the boss r³,
and it will be evident from Figure 2 that a very small area is left for leakage of steam
between the inner surface at s and the outer surface of the boss r. Both surfaces
may be turned with alternate rings and grooves, such as are shown for the packing in
Figure 10, when it is considered necessary.
The division plate E' and the plate E carrying the guide blades E may be cast
in one, and the guide blades inserted separately, but I prefer to form them separately,
and turn them to fit each other, and the casing B and C, as shown in Figure 2, so
that I may cut the guide blades E out of the solid, when I desire to do so, or
readily attach them to the guide blade plate, when they are constructed separately.
The division rings and the guide blade rings are made in halves and slipped into each
half B. C. of the casing and the surfaces of junction scraped up in a manner well
known to engineers.
My improved governing devices are indicated at Figures (1), (4), (4*), and (5).
Referring to Figure (1) the turbine spindle projects at M, and by frictional contact
drives the friction wheel N on the second motion shaft Q1, which shaft is thus
rotated at a lower speed than the turbine shaft. The centrifugal spring governor P
of any usual construction is carried on the shaft Q and it controls the position of a
conical sleeve Q on the shaft. When the speed increases, the governor causes the
conical sleeve to slide in one direction along the shaft, and when the speed falls,
the governor spring or springs return the sleeve again. The sleeve although free
to slide along the shaft, rotates with it, and a cam surface cut on the cone moves a
lever or other connection, so that the steam valve is opened by its spindle R against
the spring R. The conical or inclined cam surface is so arranged, that in one position
of the sleeve Q the steam valve is held open during the whole revolution of the
shaft Q; that is, the steam is admitted continuously to the turbine by the steam
valve. When the speed increases, however, the governor pulls the sleeve Q to such a
position, that the steam is admitted to the turbine case for a portion of a revolution

page_text: only, and the higher the speed, the further the sleeve moves along, so that the steam
is admitted to the turbine for a smaller and smaller fraction of a revolution of a
shaft Q. This action of cutting off steam a fixed number of times per minute, but
with shorter and shorter duration of admission, resembles the variable cut off of the
reciprocating engine, and has a similar effect on the expansive use of steam. The
clearance space between the steam valve, and the first turbine wheel should be as
small as is possible.
That portion of the cam sleeve Q where the steam valve is held open during the
complete revolution, is shown as parallel, and the part where the cam sleeve causes
variable cut off, is shown as conical.
The same effect as that of variable cut off, I sometimes obtain without the use of a
centrifugal governor, and one mode used by me is shown at Figure (4), where the
solenoid arrangement U is actuated by the variation of the electric current, and
increase or diminution of speed of the turbine with its dynamo causes the lever U
to overcome the resistance of the spring U₁, or be overcome by it. This moves the
cam sleeve V, on the second motion shaft Q' by the projection U and so controls
the steam valve as I have hereinbefore described."
Other modifications of the variable cut off principle, as applied to steam turbines
may be adopted without departing from this feature of my invention.
Figure (4) illustrates the arrangement of a solenoid where variable cut off is
dispensed with, and the variation of the electrical state of the dynamo is caused by
the solenoid U Figure (4) to act direct on the throttle valve spindle R. In this
case I prefer to fix the solenoid core, U4, and cause the coil to balance on the end
of the throttle valve lever U2. The throttle valve is opened by the spring t, and
closed by the suck of the solenoid acting against the spring t and the weight u.
speed of the turbine I sometimes vary by moving the weight u and by adjusting
the tension of the spring t.
The
The application of a centrifugal governor rotating on the second motion or driven
shaft Q to the control of a throttle valve, is shown in Figures (5) and (6), where
the governor P moves the sleeve W, and so varies the position of a throttle lever W₁
and admits or shuts off steam.
My new methods of damping vibration are carried out by the bushes illustrated
at Figures (7) (7) and (8) and (8"). Referring to Figure (7) the bush K in which
the turbine spindle runs, is surrounded by three concentric tubes a, b, c, preferably
constructed of steel, and turned so as to slip easily over the bush and each other
that is with a slight freedom of fit. In Figures (7) and (7*) considerable spaces
are shown between the rings a, and c, and the bush K, in order to make my
intention obvious; but in practice only a very slight looseness or ease of fit is
required. The tubes a, b, c, are held in position by a ring K¹ or other suitable
contrivance, and move easily between the flange K and the ring K'. The outer
tube a fits into the bored recess in D and D' (Figs. 1 and 2). In Figure (2) the
two bearings of the turbine are shown in position at K and K¹.
When oil gets
access to the tubes a, b, c, which it is allowed to do, by means of holes or grooves,
a slight vibration set up by the spindle J, J' causes the tubes a, b, c, to move or
shake within each other. But the movement is damped by the hydraulic and
'capillary resistance of the oil between the rings, which must be squeezed out from
between the tubes a, b, c and at the ends K³, K'. This hydraulic resistance is
considerable, so that although some motion is permitted, yet it is resisted powerfully
and vibration is avoided. The arrangement shown in Figures (8) and (8) combines
'hydraulic resistance with spring resistance, and it consists of two tubes a, e, sur-
rounding the bush K ; but having in the annular space between them, spring
segments f, g, h, formed by cutting a tube of suitable diameter into three parts.
These segments act as springs, as I have hereinbefore described, and have shown at
Figure (8) freedom of lateral movement being allowed.
:: I take up the unbalanced end thrust by means of the thrust block L Fig. 2 which
is made. in two halves and slipped over the corresponding grooves and recesses in
the spindle at L'. This block find answers well in practice, but in-some machines

page_text: I prefer to adopt the block shown at Figs. 9 & 9 & 9° where the thrust surfaces are
pressed against the corresponding surfaces on the spindle by their elasticity and so
equally divide the total pressure among them. This elastic action is obtained by
constructing the thrust pieces i, j, k, l, m, separately from the block L of sufficient
diameter & thickness to be elastic; sometimes I cut out slots as seen in Fig. 9a to
give greater elasticity. The elasticity may also be obtained as shown in Fig. 9b
where the washers i, j, k, l, m, are held up to their work by springs.
Figs. 10, 10 show my packing arrangements to avoid loss of steam, and consist of
a bush H fastened on the spindle and contained in a block O in halves, grooves n,
& projections p, p, p³, being formed in both as shown, & by engaging prevent
leakage.
:
Having now particularly described and ascertained the nature of my said inven-
tion, & in what manner the same is to be performed, I declare that what I
claim is;
I. In radial flow steam turbines in which steam passes through a series of turbine
chambers, arranged along a shaft or spindle carrying rotating blades; the combination
of a ring or disc as E' with the spindle J or boss of small diameter for the purpose
of minimising leakage, substantially as hereinbefore described and illustrated with
reference to the accompanying drawings.
II. In radial flow steam turbines in which steam passes through a series of
turbine chambers arranged along a shaft or spindle; that construction of turbine
chamber consisting essentially of two turned rings or discs such as E³, E¹, or similar
to E E', one ring or disc forming the division between contiguous chambers & the
other carrying the guide blades E, substantially as herein before described & illustrated
with reference to the accompanying drawings.
III. Governing or actuating a steam or elastic fluid turbine of any type radial
flow (inward or outward) parallel flow or any combination of parallel flow with radial
flow, by means of a variable periodic cut off, acting on the steam supply, so as to
vary the ratio of expansion of the steam or other elastic fluid in the turbine & to work
more expansively at reduced loads.
'
IV. Governing or supplying motive fluid to a steam or elastic fluid turbine of any
type by means of a governing or cut off gear driven on a second motion shaft, which
shaft is rotated at a lower speed than the turbine spindle and geared to the turbine
spindle by frictional or other gearing.
V. The use of a centrifugal governor as applied to steam turbines, which governor
is rotated at a lower speed than the turbine, and acts to control a throttle valve, or
variable cut off gear, substantially as hereinbefore described & illustrated with specific
reference to Figs. 1 & 5.
VI. In steam turbines, governing electrically by means of a solenoid acting
directly on a throttle valve or a variable cut off gear substantially as hereinbefore
described & illustrated in the accompanying drawings with special reference to
Figs. 4 & 4.
VII. In steam turbines the use of a multiple surface thrust block to resist
unbalanced end thrust on the turbine spindle substantially as hereinbefore described.
VIII. In steam turbines, the use of a multiple surface thrust block to resist
unbalanced end thrust on the turbine spindle in which the thrust block surfaces are
attached to the thrust block by elastic connection so that each separate thrust block
surface is held to the corresponding spindle surface with a pre-determined pressure
and the work of taking up the thrust is thus distributed uniformly substantially as
and for the purpose herein before described & illustrated with special reference to
Figs. 9, 98, 9 of the drawings.
IX. In steam turbines the use of bearings consisting essentially of a bush surrounded
by concentric tubes fitting easily so that a slight lateral movement of the bush is
permitted with reference to the recess containing the external tube, the construction
and action being substantially as herein before described & illustrated with reference
to Figs. 7, 7" in the drawings.

page_text: ✗. In steam turbines the use of bearings consisting essentially of concentric
tubes surrounding the bush with interposed spring segments or spring pieces
substantially as hereinbefore described & illustrated with reference to Figs. 8 & 8ª
of the drawings.
XI. In steam turbines the use of packing consisting of alternate grooves and
projections substantially as herein before described & illustrated at Figs. 10, 10° of
the accompanying drawings.
XII. Steam turbines constructed as hereinbefore described and illustrated in
Figs. 1, 2, & 3 of the accompanying drawings.
Dated this 21st day of October 1890.
L
MARKS & CLERK,
13, Temple Street, Birmingham, Agents for Applicant.