CA1161762A - Turbine - Google Patents
TurbineInfo
- Publication number
- CA1161762A CA1161762A CA000377666A CA377666A CA1161762A CA 1161762 A CA1161762 A CA 1161762A CA 000377666 A CA000377666 A CA 000377666A CA 377666 A CA377666 A CA 377666A CA 1161762 A CA1161762 A CA 1161762A
- Authority
- CA
- Canada
- Prior art keywords
- valve seat
- valve
- nozzles
- turbine
- valve member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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- Control Of Turbines (AREA)
Abstract
ABSTRACT
TITLE: TURBINE
Nozzles, which direct working fluid into the blades of a rotor, are divided into a plurality of groups with the nozzles in each group communicating with a respective radial port in a tubular valve seat. A cylindrical valve member is movable axially of the valve seat to open or close the ports in succession, thereby achieving nozzle-governed operation of the turbine. The valve seat is removably mounted between a casing cover and a pressure vessel and can be replaced by other valve seats having ports different in shape, size, disposition and/or number, thereby enabling the operating characteristics of the turbine to be altered.
TITLE: TURBINE
Nozzles, which direct working fluid into the blades of a rotor, are divided into a plurality of groups with the nozzles in each group communicating with a respective radial port in a tubular valve seat. A cylindrical valve member is movable axially of the valve seat to open or close the ports in succession, thereby achieving nozzle-governed operation of the turbine. The valve seat is removably mounted between a casing cover and a pressure vessel and can be replaced by other valve seats having ports different in shape, size, disposition and/or number, thereby enabling the operating characteristics of the turbine to be altered.
Description
TITLE: TURBIN~
_ . _ This invention relates to a turbine.
A ~urbine typically comprises a rotor, a multiplicity of nozzles through which working fluid is directed into blades of the rotor, a supply chamber and valve mean~
controlling the flow of working fluid from the supply chamber to the nozzles. In turbines of the so-called throttle governecl type, the valve means comprises a single valve whlch controls the flow o fluld to all oE the noz~les in unlson. In turbines of the so-called nozæle governed type, the valve means ls composed o~ a plurality of separate valves which are operated sequentially to control flow of the working fluid to separate groups of nozzles. It is generally accepted that throrrtle governed turbines have much lower thermodynamic efficiency under partial load operation than nozzle governed turbines. ~owever, nozzle governed turblnes are more complex and expensive.
An inherent problem of conventional nozzle governed turbines is that the supply chamber has a specific number of control valves of fixed geometry and dimension. Therfore, changes in the mass flow and condition of the working fluid necessitate the use of supply chambers of different pressure/temperature capability, size and control valve configuration. Unless the supply chamber is thus replaced, such conventional turbines are somewhat inflexible in their operational capabilities.
, .
,~
~6~7~
It is an object of the present invention to provlde a turbine of the nozzle governed type which is comparatively simple in construction, relatively inexpensive to produce, and which enables changes in the mass flow and condition of the working fluld to be acc:ommodated ln a simple manner.
According to the present invention, there is provided a turbine lncluding a rotor, a multlplicity of nozæles through whlch working fluld is directed into blade~ of the rotor, the nozzles being clivided lnto a plurality of groups with the noz~les in each group being ~upplied with the working fluld from a supply chamber through respective conduit means, and valve means controlling the flow of the working fluid from the supply chamber to the conduit means, the valve means comprising a tubular valve seat having a plurality of radial ports which communicate with the conduit means respectively and a valve member received within the valve seat and movable relative thereto to open and close the radial ports selectively, the val.ve seat being removably mounted in the turbine and being replaceable by other valve seats having radial ports different in shape, size, disposition and/or number.
In this way, the turbine performance can be modified simply by replacing one comparatively small component, namely the valve seat. Moreover, such replacement can be readily carrisd out on site. The number of radial ~orts -3~ 7~
in the valve seat and their size, shape and dlsposltion will deterimine the sequence ln which the nozzle~ are brought into or out of operation as the valve means is opened or closed, the manner in whlch the nozzles are grouped (i.e. the nozzles which are brought into operatlon at any given posltion of the valve means), the so-called "swallowing capacity" of the turbine, and the modulation of the working fluid.
Deslrably, the supply chamber ls removably mounted on a casing withln which the rotor is rotatably dlsposed, and the valve seat is removably mounted between the casing and the supply chamber co-axially with the rotor axis. In an alternative arrangeme~t, however, the valve seat is contained wlthin the supply chamber and the latter is disposed remotely from the rotar casing, with the radial ports in the valve member being connected to the respective nozzle groups by way of external pipes.
The capabillty of the turbine can be modified still further, with particular reference to the mass flow of the working fluid, by employing a construction wherein the casing comprises an open-ended body part within which the rotor is rotatably mounted and a cover removably closi~l~ the open end of the body part and containing the nozzles, the conduit means is formed by internal passages 3~6~1L7ti2 withln the cover, and the valve seat ls received in a cyllndrical bore in the cover into which the passages open. In this case, the cover can be replaced by other covers having different-sized bores therein for reception of other correspondingly different-si~ed valve seats.
Moreover, the various covers can also have different arrangem~nts of the said passages thereln : for example, passages of dif~erent mean diameter, size and number.
Conveniently, the radial ports are spaced apart axially of the valve seat, and the valve member is movable axially of the latter. In this case the valve member can comprise a hollow tubular body whose peripheral wall covers the radial ports successively as the valve member ls moved axially of the valve seat, the valve member being open at both axial ends thereof. This latter measure ensures that the valve member is pressure balanced.
The valve member can be moved by mechanical, hydraullc, pneumatic or electrical means, for example. Where this is performed mechanically, a linkage preferably connects the valve member to a crank which is mounted on a rotatable shaft for rotation therewith, the crank and the linkage being contained within the supply chamber with the shaft extending rotatably and sealingly through a side wall thereof.
This particular arrangement eliminates pressure differential out-of-balance.
Operation of the valve member can be achieved automatically by means of a control mechanism, which can be governor-operated for example. ~lternatively, the valve member can be manually operated. In one position of the valve member, it can be arranged that all o~ the radial ports are closed off, so that the valve member can be used to effect emergency shut-down of the turbine, for example.
The valve member and preferably also the valve seat can be made of stalnless steel or nitrided steel.
Advantageously, the nozzles are arranged in at least one ring and are divided into a plurality of ~rcuate rows each extending part-way around the rotor axis, and each radial port in the valve seat communicates with the nozzles in a respective one of the arcuate rows. Desirably, the nozzles in each arcuateroware in communlcation with a respective arcuate passage with which the respective radial port in the valve seat also communicates.
An embodiment of the present invention will now be described, by way of example, with reference to the accompanying drawings, in which:-7~i2 Flgure 1 is an axial cross-section of a first embodiment of a turbine according to the present inventlon;
Figure 2 is an enlarged view of a valve which forms part of the turbine shown in Figure 1;
Figure 3 is an end view of a casing cover assembly which also forms part of the turbine shown ln Figure 1; and Figure 4 is an axial cross-section of a second embodiment of a turblne according to the present inventlon, illustrating in particular a control mechanism therefor.
The turbine illustrated in Figures 1 to 3 comprises a casing having an open-ended body part 10 within which a rotor 11 is mounted for rotation about an axis 12. The open end of the body part 1~ is closed by a cover 13 having a plurality of equi-angularly spaced nozzles therein which confront blades 14 (only one shown) on the periphery of the rotor 11. In operation of the turbines, working fluid is expanded through the nozzles and directed into the blades 14 to rotate the rotor 11 in a known manner.
Each nozzle comprises an insert 15 received within a stepped axial bore 16 in the cover 13, the inserts 15 being retained in their respective bores 16 by an annular clamping ring 17 and being sealed against leakage by respective 0-rings 18. Formed within the cover 13 are arcuate 1~61.7G;2 passages 19 ~lndicated by broken llnes in Eigure 3) from which the bores 16 lead. In the illustrated arranyement, eight such passages 19 are prov:Lded in equi-angularly spaced relation, and the nozzles are divided into eight arcuate rows with ~he nozzles in each row communicating with a resp~ctive one of the arcuate passages 19. A
different number o~ arcuate passages can, however, be provided if desired.
A radial pas~age 20 extends from each arcuate pas~age 19 and opens onto a central axial bore 20a in the cover 13. Disposed within the bore 20a is a tubular valve seat 21 which is co-axial with the rotation axis 12 of the rotor. The valve seat 21 is retained axially by a clamplng flange 22 on a hollow spigot 23 of a pressure vessel or supply chamber 24 to which pressurised working fluid is supplied in use, the supply chamber 24 being removably mou~ted on the cover 13. . Radlal ports 25 are formed in the valve seat 21 in axially and angularly spaced relation.
Each port 25 opens into a respective part-annular groove 26 in the radially outer surface of the valve seat 21, each groove 26 communicating with the radial passages 20 and respective arcuate passages 19.
The flow of working fluid between the supply chamber 24 and the nozzles is controlled by a valve member 27 which L7~
is axially movable within the valve seat 21. Both the valve member and the valve seat are made of stalnless steel or nitrlded steel. The valve member 27 is in the general form of a hollow cylindrical piston, and is operatlvely connected to a crank 2~ on a rotatable control shaf t 29 by way of a link 30. The crank 28 and the link 30 are disposed withln the chamber 24, whereas the control shaft 29 extends ro~atably and sealingly through a side wall of the chamber 24 and ls connected to a governor-operated control mechanism (not shown).
Angular movement of the shaft 29 causes the valve member 27 to move axially of the vaLve seat 21. In the position shown in the drawin~s, all of the radial por~s 25 are uncovered by the valve memb~r, and therefore pressurised working fluid can pass from the supply chamber 24 through the valve to all of the nozzles so that the turbine oper~tes at full power, i.e. under fuLl load. I the load on the turbine should lessen, the resultant increase in speed of the rotor will be detec~ed by the control mechanism, as a result of which tne control shaft 29 is rotated to move the valve mem~er 27 so as to reduce fluid flow through one or more of the radial ports 25 the turbine power is consequentl~- reduced in correspondence to the reduction in load. If the load on the turbine then increases, the rotor will momentaril~ slow down and the control mechanism will move the valve me...ber in the reverse direction ~o increase the flow of working fluid through the increased area of the radial ports 25 once aqain.
_9_ L7~i2 If the valve member is ~oved to the extreme left as viewed in Figure 2, it will shut off all of the radial ports 25. Henc~, pressurised working fluid will be unable to flow to any of the nozeles, resulting in a shut-down of the .urbine. This action can be performed under emergency conditions, for example.
As an alternative to a governor-operated control mechanism, the control shaft 2g can be connected to a ~imple hand crank or hand wheel so that the above-described power ad~ustment3 can be performed manually.
The number, size, shape and disposition of the rad~al ports 25 and the corresponding~rooves 26 in the valve seat 21 determine the amount of working fluid which can flow to each arcuate row of nozzles and the seque~tial mode in which these rows are placed into and out of communication with the supply chambér 24. These factsrs can be altered to suit the partlcular application of the turbine merely by replacing the valve seat 21 with another having suitable charac~eristics. Moreover, further alteration of the turbine characteristics can be achieved by replacing the supply chamber 24 and the casing cover 13.
In the former case, various supply chambers can be provided of different sizes, wall thickness and material according to the mass flow and pressure/temperature condltion of the working fluid. In the latter case, various covers 13 can - 1 o z ' be provided having a different number of passages 19 and 20, and wherein the mean diameter of arcuate passayes 19 may be varied. In additlon, covers having different-sized central ax$al bores 20a can be provided for accommodating correspondlngly dlfferent-slzed valve seats 21.
It will therefore be apparent that the configuration and size of the cover 13, the valve seat 21, the valve member 27 and supply chamber 24 are all varlable to a large degree in order to cater for various operational requirements of the turbine. Moreover, the radial passages 20 provide unrestxicted communication between the arcuate passages 19 and radial ports 25 in the valve seat 21 in all cases.
Since thP valve member 27 is open at both of its axial ends, it is completely pressure balanced and lts cut-off action can be modulated to minimise resistlve fluid flow forces. Positive positioning of the valve member can thus be achieved with minimal torque requirement on the control shaft 29, thereby eliminating the need for complex and expensive servo-systems which are normally associated with nozzle governed turbines.
617tiZ
The turbine illustrated in Figure 4 lS generally similar to that described above with reference to Figures 1 to 3, and therefore similar parts have been accor~ed the sa~e reference numerals with 100 added. Reference numerals t40 ar.d 141 denote respectively an ir.let and an outlet for the passage of workir.g ~luid through the turbine.
In Fiqure 4, the governor-operated control mechanism .~hich controls movement of the valve .-.e~ber 127 is sho~n in detaLl, and cor.;pris~s generally a ~echanieal go~;ers.or 142 ~which ls rotated with the turbine ro~cr I 11 D'~ ~,Jay of qearing 143. An axially movable me~ber 144 of th~
governor 142 is connected ~ way of a link 1~; ta a further cran~ 146 on the control shaft 129, the cran~ 146 bei~g disposed externally of the fluid supply cha~ber 124.
As will be appreciated from this Pigure, an increase in speed of the turbine rotor 111 will cause the member 144 to move to the right as viewed, thereby ~oving the valve member 127 to the left.
_ . _ This invention relates to a turbine.
A ~urbine typically comprises a rotor, a multiplicity of nozzles through which working fluid is directed into blades of the rotor, a supply chamber and valve mean~
controlling the flow of working fluid from the supply chamber to the nozzles. In turbines of the so-called throttle governecl type, the valve means comprises a single valve whlch controls the flow o fluld to all oE the noz~les in unlson. In turbines of the so-called nozæle governed type, the valve means ls composed o~ a plurality of separate valves which are operated sequentially to control flow of the working fluid to separate groups of nozzles. It is generally accepted that throrrtle governed turbines have much lower thermodynamic efficiency under partial load operation than nozzle governed turbines. ~owever, nozzle governed turblnes are more complex and expensive.
An inherent problem of conventional nozzle governed turbines is that the supply chamber has a specific number of control valves of fixed geometry and dimension. Therfore, changes in the mass flow and condition of the working fluid necessitate the use of supply chambers of different pressure/temperature capability, size and control valve configuration. Unless the supply chamber is thus replaced, such conventional turbines are somewhat inflexible in their operational capabilities.
, .
,~
~6~7~
It is an object of the present invention to provlde a turbine of the nozzle governed type which is comparatively simple in construction, relatively inexpensive to produce, and which enables changes in the mass flow and condition of the working fluld to be acc:ommodated ln a simple manner.
According to the present invention, there is provided a turbine lncluding a rotor, a multlplicity of nozæles through whlch working fluld is directed into blade~ of the rotor, the nozzles being clivided lnto a plurality of groups with the noz~les in each group being ~upplied with the working fluld from a supply chamber through respective conduit means, and valve means controlling the flow of the working fluid from the supply chamber to the conduit means, the valve means comprising a tubular valve seat having a plurality of radial ports which communicate with the conduit means respectively and a valve member received within the valve seat and movable relative thereto to open and close the radial ports selectively, the val.ve seat being removably mounted in the turbine and being replaceable by other valve seats having radial ports different in shape, size, disposition and/or number.
In this way, the turbine performance can be modified simply by replacing one comparatively small component, namely the valve seat. Moreover, such replacement can be readily carrisd out on site. The number of radial ~orts -3~ 7~
in the valve seat and their size, shape and dlsposltion will deterimine the sequence ln which the nozzle~ are brought into or out of operation as the valve means is opened or closed, the manner in whlch the nozzles are grouped (i.e. the nozzles which are brought into operatlon at any given posltion of the valve means), the so-called "swallowing capacity" of the turbine, and the modulation of the working fluid.
Deslrably, the supply chamber ls removably mounted on a casing withln which the rotor is rotatably dlsposed, and the valve seat is removably mounted between the casing and the supply chamber co-axially with the rotor axis. In an alternative arrangeme~t, however, the valve seat is contained wlthin the supply chamber and the latter is disposed remotely from the rotar casing, with the radial ports in the valve member being connected to the respective nozzle groups by way of external pipes.
The capabillty of the turbine can be modified still further, with particular reference to the mass flow of the working fluid, by employing a construction wherein the casing comprises an open-ended body part within which the rotor is rotatably mounted and a cover removably closi~l~ the open end of the body part and containing the nozzles, the conduit means is formed by internal passages 3~6~1L7ti2 withln the cover, and the valve seat ls received in a cyllndrical bore in the cover into which the passages open. In this case, the cover can be replaced by other covers having different-sized bores therein for reception of other correspondingly different-si~ed valve seats.
Moreover, the various covers can also have different arrangem~nts of the said passages thereln : for example, passages of dif~erent mean diameter, size and number.
Conveniently, the radial ports are spaced apart axially of the valve seat, and the valve member is movable axially of the latter. In this case the valve member can comprise a hollow tubular body whose peripheral wall covers the radial ports successively as the valve member ls moved axially of the valve seat, the valve member being open at both axial ends thereof. This latter measure ensures that the valve member is pressure balanced.
The valve member can be moved by mechanical, hydraullc, pneumatic or electrical means, for example. Where this is performed mechanically, a linkage preferably connects the valve member to a crank which is mounted on a rotatable shaft for rotation therewith, the crank and the linkage being contained within the supply chamber with the shaft extending rotatably and sealingly through a side wall thereof.
This particular arrangement eliminates pressure differential out-of-balance.
Operation of the valve member can be achieved automatically by means of a control mechanism, which can be governor-operated for example. ~lternatively, the valve member can be manually operated. In one position of the valve member, it can be arranged that all o~ the radial ports are closed off, so that the valve member can be used to effect emergency shut-down of the turbine, for example.
The valve member and preferably also the valve seat can be made of stalnless steel or nitrided steel.
Advantageously, the nozzles are arranged in at least one ring and are divided into a plurality of ~rcuate rows each extending part-way around the rotor axis, and each radial port in the valve seat communicates with the nozzles in a respective one of the arcuate rows. Desirably, the nozzles in each arcuateroware in communlcation with a respective arcuate passage with which the respective radial port in the valve seat also communicates.
An embodiment of the present invention will now be described, by way of example, with reference to the accompanying drawings, in which:-7~i2 Flgure 1 is an axial cross-section of a first embodiment of a turbine according to the present inventlon;
Figure 2 is an enlarged view of a valve which forms part of the turbine shown in Figure 1;
Figure 3 is an end view of a casing cover assembly which also forms part of the turbine shown ln Figure 1; and Figure 4 is an axial cross-section of a second embodiment of a turblne according to the present inventlon, illustrating in particular a control mechanism therefor.
The turbine illustrated in Figures 1 to 3 comprises a casing having an open-ended body part 10 within which a rotor 11 is mounted for rotation about an axis 12. The open end of the body part 1~ is closed by a cover 13 having a plurality of equi-angularly spaced nozzles therein which confront blades 14 (only one shown) on the periphery of the rotor 11. In operation of the turbines, working fluid is expanded through the nozzles and directed into the blades 14 to rotate the rotor 11 in a known manner.
Each nozzle comprises an insert 15 received within a stepped axial bore 16 in the cover 13, the inserts 15 being retained in their respective bores 16 by an annular clamping ring 17 and being sealed against leakage by respective 0-rings 18. Formed within the cover 13 are arcuate 1~61.7G;2 passages 19 ~lndicated by broken llnes in Eigure 3) from which the bores 16 lead. In the illustrated arranyement, eight such passages 19 are prov:Lded in equi-angularly spaced relation, and the nozzles are divided into eight arcuate rows with ~he nozzles in each row communicating with a resp~ctive one of the arcuate passages 19. A
different number o~ arcuate passages can, however, be provided if desired.
A radial pas~age 20 extends from each arcuate pas~age 19 and opens onto a central axial bore 20a in the cover 13. Disposed within the bore 20a is a tubular valve seat 21 which is co-axial with the rotation axis 12 of the rotor. The valve seat 21 is retained axially by a clamplng flange 22 on a hollow spigot 23 of a pressure vessel or supply chamber 24 to which pressurised working fluid is supplied in use, the supply chamber 24 being removably mou~ted on the cover 13. . Radlal ports 25 are formed in the valve seat 21 in axially and angularly spaced relation.
Each port 25 opens into a respective part-annular groove 26 in the radially outer surface of the valve seat 21, each groove 26 communicating with the radial passages 20 and respective arcuate passages 19.
The flow of working fluid between the supply chamber 24 and the nozzles is controlled by a valve member 27 which L7~
is axially movable within the valve seat 21. Both the valve member and the valve seat are made of stalnless steel or nitrlded steel. The valve member 27 is in the general form of a hollow cylindrical piston, and is operatlvely connected to a crank 2~ on a rotatable control shaf t 29 by way of a link 30. The crank 28 and the link 30 are disposed withln the chamber 24, whereas the control shaft 29 extends ro~atably and sealingly through a side wall of the chamber 24 and ls connected to a governor-operated control mechanism (not shown).
Angular movement of the shaft 29 causes the valve member 27 to move axially of the vaLve seat 21. In the position shown in the drawin~s, all of the radial por~s 25 are uncovered by the valve memb~r, and therefore pressurised working fluid can pass from the supply chamber 24 through the valve to all of the nozzles so that the turbine oper~tes at full power, i.e. under fuLl load. I the load on the turbine should lessen, the resultant increase in speed of the rotor will be detec~ed by the control mechanism, as a result of which tne control shaft 29 is rotated to move the valve mem~er 27 so as to reduce fluid flow through one or more of the radial ports 25 the turbine power is consequentl~- reduced in correspondence to the reduction in load. If the load on the turbine then increases, the rotor will momentaril~ slow down and the control mechanism will move the valve me...ber in the reverse direction ~o increase the flow of working fluid through the increased area of the radial ports 25 once aqain.
_9_ L7~i2 If the valve member is ~oved to the extreme left as viewed in Figure 2, it will shut off all of the radial ports 25. Henc~, pressurised working fluid will be unable to flow to any of the nozeles, resulting in a shut-down of the .urbine. This action can be performed under emergency conditions, for example.
As an alternative to a governor-operated control mechanism, the control shaft 2g can be connected to a ~imple hand crank or hand wheel so that the above-described power ad~ustment3 can be performed manually.
The number, size, shape and disposition of the rad~al ports 25 and the corresponding~rooves 26 in the valve seat 21 determine the amount of working fluid which can flow to each arcuate row of nozzles and the seque~tial mode in which these rows are placed into and out of communication with the supply chambér 24. These factsrs can be altered to suit the partlcular application of the turbine merely by replacing the valve seat 21 with another having suitable charac~eristics. Moreover, further alteration of the turbine characteristics can be achieved by replacing the supply chamber 24 and the casing cover 13.
In the former case, various supply chambers can be provided of different sizes, wall thickness and material according to the mass flow and pressure/temperature condltion of the working fluid. In the latter case, various covers 13 can - 1 o z ' be provided having a different number of passages 19 and 20, and wherein the mean diameter of arcuate passayes 19 may be varied. In additlon, covers having different-sized central ax$al bores 20a can be provided for accommodating correspondlngly dlfferent-slzed valve seats 21.
It will therefore be apparent that the configuration and size of the cover 13, the valve seat 21, the valve member 27 and supply chamber 24 are all varlable to a large degree in order to cater for various operational requirements of the turbine. Moreover, the radial passages 20 provide unrestxicted communication between the arcuate passages 19 and radial ports 25 in the valve seat 21 in all cases.
Since thP valve member 27 is open at both of its axial ends, it is completely pressure balanced and lts cut-off action can be modulated to minimise resistlve fluid flow forces. Positive positioning of the valve member can thus be achieved with minimal torque requirement on the control shaft 29, thereby eliminating the need for complex and expensive servo-systems which are normally associated with nozzle governed turbines.
617tiZ
The turbine illustrated in Figure 4 lS generally similar to that described above with reference to Figures 1 to 3, and therefore similar parts have been accor~ed the sa~e reference numerals with 100 added. Reference numerals t40 ar.d 141 denote respectively an ir.let and an outlet for the passage of workir.g ~luid through the turbine.
In Fiqure 4, the governor-operated control mechanism .~hich controls movement of the valve .-.e~ber 127 is sho~n in detaLl, and cor.;pris~s generally a ~echanieal go~;ers.or 142 ~which ls rotated with the turbine ro~cr I 11 D'~ ~,Jay of qearing 143. An axially movable me~ber 144 of th~
governor 142 is connected ~ way of a link 1~; ta a further cran~ 146 on the control shaft 129, the cran~ 146 bei~g disposed externally of the fluid supply cha~ber 124.
As will be appreciated from this Pigure, an increase in speed of the turbine rotor 111 will cause the member 144 to move to the right as viewed, thereby ~oving the valve member 127 to the left.
Claims (9)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A turbine comprising a rotor including a plurality of blades, said rotor being rotatable about a rotation axis, a multiplicity of nozzles operative to direct a working fluid in to said blades of said rotor, said nozzles being divided into a plurality of groups, a supply chamber operative. to supply the working fluid to said nozzles, a plurality of conduit means connecting said supply chamber to the nozzles in said groups respectively, and valve means operative to control the flow of the working fluid from said supply chamber to said plurality of conduit means, said valve means comprising a tubular valve seat having therein a plurality of radial ports which communicate with said plurality of conduit means respectively, and a valve member received within said valve seat and movable relative thereto to open and close the radial ports selectively, said valve seat being removably mounted in said turbine and being replaceable by other valve seats having radial ports different in at least one of the group of characteristics consisting of shape, size, disposition and number.
2. The turbine according to claim 1, further comprising a casing in which said rotor is rotatably disposed, and wherein said supply chamber is removably mounted on said said casing and said valve seat is removably mounted between said casing and said supply chamber co-axially within said rotation axis.
3. The turbine according to claim 2, wherein said casing comprises a body part within which said rotor is rotatably mounted and which has an open end, and a cover which closes said open end of said body part and which contains said nozzles, said cover having formed therein a plurality of internal passages which consititute said plurality of conduit means respectively and a cylindrical bore into which the internal passages open and in which said valve seat is removably received, said cover being replaceable by other covers having different-sized cylindrical bores therein for the reception of other correspondingly-sized valve seats.
4. The turbine according to claim 1, wherein the radial ports are spaced apart axially of said valve seat, and said valve member is movable axially of said valve seat.
5. The turbine according to claim 4, wherein said valve member comprises a hollow tubular body having a peripheral wall which covers the radial ports successively as said valve member is moved axially of said valve seat, said valve member being open at both axial ends thereof.
6. The turbine according to claim 4, further comprising an operating mechanism which is operable to move said valve member relative to said valve seat, said operating mechanism including a rotatable shaft, a crank mounted on said shaft for rotation therewith, and a linkage connecting said crank to said valve member, said crank and said linkage being contained within said supply chamber with said shaft extending rotatably and sealingly through a side wall of said supply chamber.
7. The turbine according to claim 1, wherein said nozzles are arranged in at least one ring and are divided into a plurality of rows each extending part-way around said rotation axis of said rotor, and each radial port in said valve seat communicates with the nozzles in a respective one of said arcuate rows.
8. The turbine according to claim 7, further comprising a plurality of arcuate passages, the nozzles in a respective one of said arcuate rows and also the respective radial port in said valve seat communicating with each of said arcuate passages.
9. The turbine according to claim 1, wherein one position of said valve member all of the radial ports are closed thereof.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8016689 | 1980-05-20 | ||
| GB8016689 | 1980-05-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1161762A true CA1161762A (en) | 1984-02-07 |
Family
ID=10513548
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000377666A Expired CA1161762A (en) | 1980-05-20 | 1981-05-15 | Turbine |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1161762A (en) |
-
1981
- 1981-05-15 CA CA000377666A patent/CA1161762A/en not_active Expired
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