CA2689224A1 - Turbine having compact inflow housing thanks to internal control valves - Google Patents
Turbine having compact inflow housing thanks to internal control valves Download PDFInfo
- Publication number
- CA2689224A1 CA2689224A1 CA002689224A CA2689224A CA2689224A1 CA 2689224 A1 CA2689224 A1 CA 2689224A1 CA 002689224 A CA002689224 A CA 002689224A CA 2689224 A CA2689224 A CA 2689224A CA 2689224 A1 CA2689224 A1 CA 2689224A1
- Authority
- CA
- Canada
- Prior art keywords
- turbine
- control valve
- nozzle group
- secondary control
- valve
- 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.)
- Abandoned
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
- F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
Abstract
The invention relates to a turbine having an inflow housing (1), which comprises an inlet (3) for an inflowing working fluid, wherein the inlet can be closed by a quick closing valve (4), a plurality of control valves (91, 8) and at least two nozzle groups (21, 22), the flow of the working fluid being controllable by the inlet (3) into the nozzle groups (21, 22) via the control valves (91, 8). Furthermore, the inlet (3) can be connected via an inlet line (7) to the first nozzle group (21), wherein the inlet line (7) is guided through the primary control valve (8) such that the flow of the working fluid along the inlet line (7) can be controlled by means of the primary control valve (8). According to the invention, the secondary control valve (91) connects the first nozzle group (21) to the second nozzle group (22) such that the flow of the working fluid from the first nozzle group (21) into the second nozzle group (22) can be controlled by means of the secondary control valve (91).
Description
PC`1'/EP2008/055095 / 2007P09250W0US
Description Turbine having compact inflow housing thanks to internal control valves The present invention relates to a turbine with an inflow housing which comprises an inlet for an inflowing working fluid, wherein the inlet can be closed by a quick closing valve, a plurality of control valves and at least two nozzle groups, the flow of the working fluid being controllable from the inlet into the nozzle groups via the control valves.
This type of turbine is known from the publication DE 1 915 267 Al of the same applicant. The inflow housing is the part of the turbine housing into which the working fluid flows into the turbine and in which the working fluid is directed onto the rotor. For applying the fluid to the rotor the inflow housing has a number of nozzle groups which extend in the shape of a ring sector at a common diameter around the rotor.
Each nozzle group combines a number of nozzles which are directed onto the rotor. The inflowing working fluid flowing in through the inlet is directed into the nozzle groups, exits from the nozzles and flows through the rotor blading. The division of the nozzles into nozzle groups is used for power regulation. Since the mass throughput is restricted by the nozzle cross section, the overall mass throughput and thereby the power of the turbine can be controlled by variation of the nozzle groups to which the working fluid is applied. The distribution of the working fluid to the individual nozzle groups and the individual mass throughput per nozzle group is controlled by the control valves. A quick closing valve is provided for an emergency shutdown which closes off the inlet and can therefore suppress the overall flow through the turbine.
The inflow housing of a known steam turbine is shown in Figure PCT/ffP2008/055045 / 2007P09250W0US
Description Turbine having compact inflow housing thanks to internal control valves The present invention relates to a turbine with an inflow housing which comprises an inlet for an inflowing working fluid, wherein the inlet can be closed by a quick closing valve, a plurality of control valves and at least two nozzle groups, the flow of the working fluid being controllable from the inlet into the nozzle groups via the control valves.
This type of turbine is known from the publication DE 1 915 267 Al of the same applicant. The inflow housing is the part of the turbine housing into which the working fluid flows into the turbine and in which the working fluid is directed onto the rotor. For applying the fluid to the rotor the inflow housing has a number of nozzle groups which extend in the shape of a ring sector at a common diameter around the rotor.
Each nozzle group combines a number of nozzles which are directed onto the rotor. The inflowing working fluid flowing in through the inlet is directed into the nozzle groups, exits from the nozzles and flows through the rotor blading. The division of the nozzles into nozzle groups is used for power regulation. Since the mass throughput is restricted by the nozzle cross section, the overall mass throughput and thereby the power of the turbine can be controlled by variation of the nozzle groups to which the working fluid is applied. The distribution of the working fluid to the individual nozzle groups and the individual mass throughput per nozzle group is controlled by the control valves. A quick closing valve is provided for an emergency shutdown which closes off the inlet and can therefore suppress the overall flow through the turbine.
The inflow housing of a known steam turbine is shown in Figure PCT/ffP2008/055045 / 2007P09250W0US
2a of DE 1 915 267 Al. With the housing design basically still manufactured today the control valves are located in what is referred to as a valve housing or valve compartment above the actual turbine housing. The working fluid flows in laterally through arl inlet, passes through a quick closing valve and reaches the valve compartment from which five parallel-switched supply 1_ines above a control valve in each case branch off to nozzle groups. Each valve group thus has its own supply line available to it and a separate control valve. The respective feed lines and valves are connected in parallel.
The enclosed Figure 1 shows a circuit diagram of this arrangement. With current designs of such a valve arrangement the linearly-guided valve spindles of the control valves are each driven with an individual motor and not, as shown in this publication, via a control bar.
In another known design of steam turbines the control valves are arranged outside the turbine housing and linked via welded-on pipes or pipe bends to the nozzle housing. The fresh steam flow divided up remotely from the inflow housing is thereby guided through the comparatively long pipes to the nozzle groups.
However both designs have the disadvantage that the inflow housing with the external valve compartments or the pipes occupy a great deal of space. In addition these constructions are very costly, since very high-quality materials must be used for the cast housings of the valves, pipes and flanges.
The many diversions of the flow in the pipes or in the supply pipes to the nozzle groups inevitably lead to significant energy losses. In addition the control valves described in DE
1 915 267, through which the flow is axial, also demand high setting forces.
In respect of this prior art the present invention is based on the object of developing a turbine of the type described at PC'1'/EP2008/055095 / 2007P09250WOUS
The enclosed Figure 1 shows a circuit diagram of this arrangement. With current designs of such a valve arrangement the linearly-guided valve spindles of the control valves are each driven with an individual motor and not, as shown in this publication, via a control bar.
In another known design of steam turbines the control valves are arranged outside the turbine housing and linked via welded-on pipes or pipe bends to the nozzle housing. The fresh steam flow divided up remotely from the inflow housing is thereby guided through the comparatively long pipes to the nozzle groups.
However both designs have the disadvantage that the inflow housing with the external valve compartments or the pipes occupy a great deal of space. In addition these constructions are very costly, since very high-quality materials must be used for the cast housings of the valves, pipes and flanges.
The many diversions of the flow in the pipes or in the supply pipes to the nozzle groups inevitably lead to significant energy losses. In addition the control valves described in DE
1 915 267, through which the flow is axial, also demand high setting forces.
In respect of this prior art the present invention is based on the object of developing a turbine of the type described at PC'1'/EP2008/055095 / 2007P09250WOUS
the outset so that its inflow housirig is as compact a design as possible, and that the flow losses caused by long lines are reduced. This object is achieved first of all by the control valves being functionally divided into a primary control valve and at least one secondary control valve. Furthermore the inlet is to be connected to the first nozzle group via the inlet line, whereby the inlet line is to be guided through the primary control valve such that the flow of the working fluid along the inlet line is able to be controlled by means of the secondary control valve. In accordance with the invention the secondary control valve connects the first nozzle group to the second nozzle group such that the flow of the working fluid from the first nozzle group and the second nozzle group is able to be controlled by means of the secondary control valve.
The present invention is based on the underlying idea of no longer controlling individual nozzle groups with control valves connected in parallel, but of connecting the nozzle groups in series via the secondary control valves. This measure basically allows savings to be made in pipe runs in the inflow housing and thus to achieve a more compact construction. The flow losses are also reduced by the savings in pipes. The valve control of a primary control valve is decisive in the control of turbine since this can control the entire flow of the working fluid through the turbine. Since the first nozzle group is connected directly to the inlet via the primary control valve and the quick closing valve working fluid is always applied to the first nozzle group when the primary control valve and the quick closing valve are open. To increase the power, the subordinate rlozzle groups are successively switched in by the secondary control valves.
A preferred development of the invention makes provision for at least three nozzle groups connected in series to be Qrovided in the inflow housing, so that at least two secondary P(_1'/EP2008/055045 / 2007P09250W0US
The present invention is based on the underlying idea of no longer controlling individual nozzle groups with control valves connected in parallel, but of connecting the nozzle groups in series via the secondary control valves. This measure basically allows savings to be made in pipe runs in the inflow housing and thus to achieve a more compact construction. The flow losses are also reduced by the savings in pipes. The valve control of a primary control valve is decisive in the control of turbine since this can control the entire flow of the working fluid through the turbine. Since the first nozzle group is connected directly to the inlet via the primary control valve and the quick closing valve working fluid is always applied to the first nozzle group when the primary control valve and the quick closing valve are open. To increase the power, the subordinate rlozzle groups are successively switched in by the secondary control valves.
A preferred development of the invention makes provision for at least three nozzle groups connected in series to be Qrovided in the inflow housing, so that at least two secondary P(_1'/EP2008/055045 / 2007P09250W0US
control valves are necessary that connect the first nozzle group to the second or the second nozzle group to the third.
To enable the power to be controlled in even smaller steps, it is also recommended that an additional fourth or fifth nozzle group be provided; the number of secondary control valves necessary would consequently increase to three or four.
As already mentioned the entire flow of the working fluid flows to the primary control valve. To keep the actuation forces low and to allow a soft start-up of the turbine, it is recommended that this valve being equipped with a pilot valve.
The starting up of such a turbine is preferably undertaken by the following steps: With the turbine at rest the quick closing valve is initially opened which causes the pressure of the working fluid to build up as far as the valve seat of the primary control valve. The first nozzle group is activated directly by the primary control valve. With the aid of a small pilot valve on the primary control valve the turbine is initiated and brought up to its operating speed. After the machine has accepted a load and the first nozzle group has been fully activated, the main control valve is started and thus releases the entire cross-section for the overall mass flow of the working fluid. Since the mass throughput is capped by the valve cross sections of the first group, the power of the turbine remains constant on reaching the maximum mass throughput. If the power of the turbine is to be increased further, the first secondary control valve is opened so that the flow now also reaches the second nozzle group. This increases the mass throughput. Provided the turbine has available to it further downstream nozzle groups, these will be switched-in later by opening the respective secondary control valves.
The inventive circuit of the individual nozzle groups allows the shut-off facilities of the secondary control valves to be PC'I'/EP2008/055045 / 2007P09250WOUS
arranged directly between the nozzle groups extending in the shape of a ring sector around the rotor, i.e. at the same radius as the nozzle groups. The flow paths in the inflow housing are further shortened in this way.
The space occupied by the irlflow housing can be significantly reduced in this design by the axes of actuation of the secondary control valves being arranged radially to the axis of rotation of the rotor. The actuation path of the shut-off facilities is then not actually located tangentially to the diameter of the nozzle groups, but radially. The necessary external diameter of the inflow housing is reduced in this way.
Preferably in this embodiment the shut-off facilities of the secondary control valves are designed as rotationally-switchable control flaps so that the actuation axis involved is an axis of rotation. The rotationally-switched shut-off facilities occupy less space than the linearly-switched shut-off facilities, require lower actuation forces and do not have to be completely sealed. The use of rotationally-switched, not completely sealed shut-off facilities is also possible since no quick closing function is required for the secondary control valves. This quick closing function is performed by the quick closing valve and the downstream primary control valve. Preferably the inflow housing of the inventive turbine is an essentially annular design and is subdivided into at least two housing halves, with the inlet line being an integral component of a housing half. The advantage of this embodiment is that the line of the working fluid can be welded on without a flange connection, that only one entry into the turbine housing must be sealed off with the piston ring and that all components warm up well during the start of phase.
With a large volume of steam the two housing halves can each be provided with an integrated inlet in order to double the PLl'/EP2008/055045 / 2007P09250W0US
normal width of the inlet steam connection overall.
'I'he present invention is preferably employed in the area of axial designs of steam turbine.
The present invention will now be explained in greater detail with reference to an exemplary embodiment. The figures show:
Fig. 1: a conventi_onal valve circuit (prior art);
Fig. 2: an inventive valve circuit;
Fig. 3: an inflow housing in a part-exploded perspective view;
Fig. 4: an inflow of housirlg in a part-exploded rearview;
Fig. 5: a section through the inflow housing;
Fig. 6: an inflow housing with two inlets.
Figure 1 shows a schematic diagram of the last circuit of a conventional steam turbine, as is known from the publication mentioned at the start. The housing of the turbine comprises an inflow housing 1 in which the rotor not shown in the diagram is supported to allow rotation. The rotor has working fluid applied to it via four nozzle groups 21, 22, 23, 24 which extend in the shape of an annular sector on a common diameter D around the rotor.
'I'he working medium - steam in the case of a steam turbine -flows through an inlet 3 into the inflow housing 1. Directly behind the inlet 3 is arranged a quick closirlg valve 4 through which the inlet 3 can be rapidly closed in an emergency.
Behind the quick closing valve 4, the flow fans out in four supply lines 51, 52, 53, 54 which connect the inlet 3 with the nozzle groups 21, 22, 23, 24 in each case. The flow of the working fluid through the supply lines 51, 52, 53, 54 is controlled by respective control valves 61, 62, 63, 64. The nozzle groups 21 through 24 are consequently connected in parallel via their respective supply lines 51 through 54 and the associated control valves 61 through 64.
The inventive circuit is shown in figure 2. Here the inlet 3 (fresh steam connection) able to be closed off via the quick closing valve 4 is connected via an inlet line 7 directly and exclusively to the first nozzle group 21. The inlet line 7 is routed through the primary control valve 8 which controls the overall flow through the turbine. The primary control valve 8 i.s advantageously equipped with a pilot valve which can be realized for example by a pilot valve connected in parallel (not shown in the diagram). Quick closing valve 4, primary control valve 8 and first nozzle group 21 are thus connected in series via the inlet line 7. The series circuit continues into the second to 22, third 23 and fourth nozzle group 24.
The second nozzle group 22 is connected to the first nozzle group 21 exclusively via a first secondary control valve 91.
The connection of the second nozzle group 22 to the third nozzle group 23 is made in the same way via a second secondary control valve 92, the connection into the fourth nozzle group 24 is made accordingly via a third secondary control valve 93.
The shut-off facilities 10 of the secondary control valves 91, 92, 93 are located on the same diameter D as the nozzle groups 21, 22, 23, 24. In this way an especially compact design of the inflow housing 1 is achieved. The axes of actuation 11 of the secondary control valves extend radialiy to the axis of rotation of the rotor, i.e. the center of the housing. Through these measures the setting motors 12 of the actuation facilities can be arranged outside the inflow housing 1.
Concrete proposed layouts of this design can be seen in Figures 3 through 5. The secondary control valves 91, 92, 93 are to be activated rotationally here so that the shut-off facilities 10 are rotary flaps. The setting motors 12 are placed on the inflow housing 1, i.e. in the pressure-free area. Only the axis of actuation left in the housing 11 must be sealed, which is easy to do with axes of rotation.
The inflow housing 1 itself is therefore essentially annular PC'T/EP2008/055045 / 2007P09250W0US
and far more compact than in the prior art since it merely accommodates the nozzle groups 21, 22, 23 and the shut-off facilities 10.
The inflow housing 1 is cast and divi_ded up into and upper housing half la and a lower housing half lb, with the inlet line 7 being an integral component of the lower housing half lb. Prirnary control valve 8 and quick closing valve 4 are arranged outside the housing 1. Thus only one steam feed into the turbine housing is to be sealed with piston rings. The steam line can thus be welded on without a flange connection.
With a very large volume of steam it is likewise possible to provide the inflow housing with two inlet lines, in order to double the nominal width of the inflowing steam connection in this way. Two primary control valves and two quick closing valves are then accordingly also required, one for each inlet.
Figure 6 shows and inflow housing with two integrated inlet lines 7.
As well as the compact dimensions and the lower flow losses, a particular advantage of the construction shown lies in the lower setting forces of the valves. Thus especially the inner control flaps only need small setting forces and especially no quick closing facility since they are connected in series with the primary control valve 8 and the quick closing valve 4. In addition the inner control flaps can be removed and replaced without opening the turbine housing.
To enable the power to be controlled in even smaller steps, it is also recommended that an additional fourth or fifth nozzle group be provided; the number of secondary control valves necessary would consequently increase to three or four.
As already mentioned the entire flow of the working fluid flows to the primary control valve. To keep the actuation forces low and to allow a soft start-up of the turbine, it is recommended that this valve being equipped with a pilot valve.
The starting up of such a turbine is preferably undertaken by the following steps: With the turbine at rest the quick closing valve is initially opened which causes the pressure of the working fluid to build up as far as the valve seat of the primary control valve. The first nozzle group is activated directly by the primary control valve. With the aid of a small pilot valve on the primary control valve the turbine is initiated and brought up to its operating speed. After the machine has accepted a load and the first nozzle group has been fully activated, the main control valve is started and thus releases the entire cross-section for the overall mass flow of the working fluid. Since the mass throughput is capped by the valve cross sections of the first group, the power of the turbine remains constant on reaching the maximum mass throughput. If the power of the turbine is to be increased further, the first secondary control valve is opened so that the flow now also reaches the second nozzle group. This increases the mass throughput. Provided the turbine has available to it further downstream nozzle groups, these will be switched-in later by opening the respective secondary control valves.
The inventive circuit of the individual nozzle groups allows the shut-off facilities of the secondary control valves to be PC'I'/EP2008/055045 / 2007P09250WOUS
arranged directly between the nozzle groups extending in the shape of a ring sector around the rotor, i.e. at the same radius as the nozzle groups. The flow paths in the inflow housing are further shortened in this way.
The space occupied by the irlflow housing can be significantly reduced in this design by the axes of actuation of the secondary control valves being arranged radially to the axis of rotation of the rotor. The actuation path of the shut-off facilities is then not actually located tangentially to the diameter of the nozzle groups, but radially. The necessary external diameter of the inflow housing is reduced in this way.
Preferably in this embodiment the shut-off facilities of the secondary control valves are designed as rotationally-switchable control flaps so that the actuation axis involved is an axis of rotation. The rotationally-switched shut-off facilities occupy less space than the linearly-switched shut-off facilities, require lower actuation forces and do not have to be completely sealed. The use of rotationally-switched, not completely sealed shut-off facilities is also possible since no quick closing function is required for the secondary control valves. This quick closing function is performed by the quick closing valve and the downstream primary control valve. Preferably the inflow housing of the inventive turbine is an essentially annular design and is subdivided into at least two housing halves, with the inlet line being an integral component of a housing half. The advantage of this embodiment is that the line of the working fluid can be welded on without a flange connection, that only one entry into the turbine housing must be sealed off with the piston ring and that all components warm up well during the start of phase.
With a large volume of steam the two housing halves can each be provided with an integrated inlet in order to double the PLl'/EP2008/055045 / 2007P09250W0US
normal width of the inlet steam connection overall.
'I'he present invention is preferably employed in the area of axial designs of steam turbine.
The present invention will now be explained in greater detail with reference to an exemplary embodiment. The figures show:
Fig. 1: a conventi_onal valve circuit (prior art);
Fig. 2: an inventive valve circuit;
Fig. 3: an inflow housing in a part-exploded perspective view;
Fig. 4: an inflow of housirlg in a part-exploded rearview;
Fig. 5: a section through the inflow housing;
Fig. 6: an inflow housing with two inlets.
Figure 1 shows a schematic diagram of the last circuit of a conventional steam turbine, as is known from the publication mentioned at the start. The housing of the turbine comprises an inflow housing 1 in which the rotor not shown in the diagram is supported to allow rotation. The rotor has working fluid applied to it via four nozzle groups 21, 22, 23, 24 which extend in the shape of an annular sector on a common diameter D around the rotor.
'I'he working medium - steam in the case of a steam turbine -flows through an inlet 3 into the inflow housing 1. Directly behind the inlet 3 is arranged a quick closirlg valve 4 through which the inlet 3 can be rapidly closed in an emergency.
Behind the quick closing valve 4, the flow fans out in four supply lines 51, 52, 53, 54 which connect the inlet 3 with the nozzle groups 21, 22, 23, 24 in each case. The flow of the working fluid through the supply lines 51, 52, 53, 54 is controlled by respective control valves 61, 62, 63, 64. The nozzle groups 21 through 24 are consequently connected in parallel via their respective supply lines 51 through 54 and the associated control valves 61 through 64.
The inventive circuit is shown in figure 2. Here the inlet 3 (fresh steam connection) able to be closed off via the quick closing valve 4 is connected via an inlet line 7 directly and exclusively to the first nozzle group 21. The inlet line 7 is routed through the primary control valve 8 which controls the overall flow through the turbine. The primary control valve 8 i.s advantageously equipped with a pilot valve which can be realized for example by a pilot valve connected in parallel (not shown in the diagram). Quick closing valve 4, primary control valve 8 and first nozzle group 21 are thus connected in series via the inlet line 7. The series circuit continues into the second to 22, third 23 and fourth nozzle group 24.
The second nozzle group 22 is connected to the first nozzle group 21 exclusively via a first secondary control valve 91.
The connection of the second nozzle group 22 to the third nozzle group 23 is made in the same way via a second secondary control valve 92, the connection into the fourth nozzle group 24 is made accordingly via a third secondary control valve 93.
The shut-off facilities 10 of the secondary control valves 91, 92, 93 are located on the same diameter D as the nozzle groups 21, 22, 23, 24. In this way an especially compact design of the inflow housing 1 is achieved. The axes of actuation 11 of the secondary control valves extend radialiy to the axis of rotation of the rotor, i.e. the center of the housing. Through these measures the setting motors 12 of the actuation facilities can be arranged outside the inflow housing 1.
Concrete proposed layouts of this design can be seen in Figures 3 through 5. The secondary control valves 91, 92, 93 are to be activated rotationally here so that the shut-off facilities 10 are rotary flaps. The setting motors 12 are placed on the inflow housing 1, i.e. in the pressure-free area. Only the axis of actuation left in the housing 11 must be sealed, which is easy to do with axes of rotation.
The inflow housing 1 itself is therefore essentially annular PC'T/EP2008/055045 / 2007P09250W0US
and far more compact than in the prior art since it merely accommodates the nozzle groups 21, 22, 23 and the shut-off facilities 10.
The inflow housing 1 is cast and divi_ded up into and upper housing half la and a lower housing half lb, with the inlet line 7 being an integral component of the lower housing half lb. Prirnary control valve 8 and quick closing valve 4 are arranged outside the housing 1. Thus only one steam feed into the turbine housing is to be sealed with piston rings. The steam line can thus be welded on without a flange connection.
With a very large volume of steam it is likewise possible to provide the inflow housing with two inlet lines, in order to double the nominal width of the inflowing steam connection in this way. Two primary control valves and two quick closing valves are then accordingly also required, one for each inlet.
Figure 6 shows and inflow housing with two integrated inlet lines 7.
As well as the compact dimensions and the lower flow losses, a particular advantage of the construction shown lies in the lower setting forces of the valves. Thus especially the inner control flaps only need small setting forces and especially no quick closing facility since they are connected in series with the primary control valve 8 and the quick closing valve 4. In addition the inner control flaps can be removed and replaced without opening the turbine housing.
Claims (10)
1. A turbine with an inflow housing featuring an inlet for an inflowing working medium able to be closed off by a quick closing valve, a plurality of control valves and at least two nozzle groups, with the flow of working fluid able to be controlled from the inlet into the nozzle groups by means of the control valves, characterized in that the inflow housing (1) comprises a primary control valve (8) and at least one secondary control valve (91), the inlet (3) is connected via an inlet line (7) to the first nozzle group (21), with the inlet line (7) being routed through the primary control valve (8) such that the flow of the working fluid along the inlet line (7) is able to be controlled by means of the primary control valve (8), and with the secondary control valve (91) connecting the first nozzle group (21) to the second nozzle group (22) such that the flow of the working fluid from the first nozzle group (21) into the second nozzle group (22) is able to be controlled by means of the secondary control valve (91).
2. The turbine as claimed in claim 1, characterized by a third nozzle group (23) and by a second secondary control valve (92), with the second secondary control valve (92) connecting the second nozzle group (22) to the third nozzle group (23) such that the flow of the working fluid from the second nozzle group (22) into the third nozzle group (23) is able to be controlled by means of the second secondary control valve (92).
3. The turbine as claimed in claim 1 or 2, characterized in that The primary control valve (8) is equipped with a pilot valve.
4. The turbine as claimed in one of claims 1 to 3, With the turbine comprising a rotor supported to allow rotation in the inflow housing (1), with the nozzle groups (21, 22) extending in the shape of a ring sector at a common diameter (D) around the rotor, and with each secondary control valve (91, 92) featuring a shut-off facility (10) and an axis of actuation (11), characterized in that the shut-off facilities (10) of the secondary control valves (91, 92) are arranged on the diameter (D) of the nozzle groups (21, 22, 23).
5. The turbine as claimed in claim 4, characterized in that The axes of actuation (11) of the secondary control valves (91, 92) extend radially to the axis of rotation of the rotor.
6. The turbine as claimed in claim 5 characterized in that The shut-off facilities (10) of the secondary control valves (91, 92) can be switched rotationally so that the axis of actuation (11) involves an axis of rotation.
7. The turbine as claimed in one of claims 4, 5 or 6, characterized in that The inflow housing (1) is essentially annular and is divided into at least two housing halves (1a, 1b), with the inlet line (7) being an integral component of one housing half (1b).
8. The turbine as claimed in one of the previous claims, With the nozzle groups (21, 22, 23) each being provided with a plurality of nozzles directed onto the rotor, characterized in that the nozzles are directed axially onto the rotor so that the flow through the turbine as an axial turbine by the working medium is in parallel to the axis of rotation of its rotor.
9. The turbine as claimed in one of the previous claims, characterized in that the inflowing working fluid involved is steam.
10. A method for operating a turbine as claimed in claim 3, especially for starting it up, characterized by the following steps:
a) Opening the quick closing valve (4), b) Opening the pilot valve of the primary control valve (8), c) After the operating speed of the rotor is reached, complete opening of the primary control valve (8), d) Opening the first secondary control valve (91).
a) Opening the quick closing valve (4), b) Opening the pilot valve of the primary control valve (8), c) After the operating speed of the rotor is reached, complete opening of the primary control valve (8), d) Opening the first secondary control valve (91).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP07011268.5 | 2007-06-08 | ||
| EP07011268A EP2000632A1 (en) | 2007-06-08 | 2007-06-08 | Turbine with a compact inflow casing due to inner control valves |
| PCT/EP2008/055045 WO2008148607A1 (en) | 2007-06-08 | 2008-04-25 | Turbine having compact inflow housing thanks to internal control valves |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2689224A1 true CA2689224A1 (en) | 2008-12-11 |
Family
ID=38668641
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002689224A Abandoned CA2689224A1 (en) | 2007-06-08 | 2008-04-25 | Turbine having compact inflow housing thanks to internal control valves |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20100178153A1 (en) |
| EP (2) | EP2000632A1 (en) |
| CN (1) | CN101680308A (en) |
| BR (1) | BRPI0812409A2 (en) |
| CA (1) | CA2689224A1 (en) |
| WO (1) | WO2008148607A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009010608B4 (en) * | 2009-02-25 | 2011-06-16 | Siemens Aktiengesellschaft | Design of the inflow chamber with radial inflow and distribution of live steam flow in 2 sections |
| ITMI20091740A1 (en) * | 2009-10-12 | 2011-04-13 | Alstom Technology Ltd | AXIAL STEAM TURBINE POWERED HIGH TEMPERATURE RADIAL |
| DE102010041704A1 (en) | 2010-09-30 | 2012-04-05 | Siemens Aktiengesellschaft | Regulating valve for controlling flow volume inside pipeline, is arranged in pipeline rotatable around rotational axis and corresponding to its rotational position decontrols flow cross-section inside pipeline |
| JP6448974B2 (en) * | 2014-10-03 | 2019-01-09 | 三菱日立パワーシステムズ株式会社 | Steam chamber of geothermal turbine, geothermal turbine provided with the same, and steam supply method of geothermal turbine |
| US10480417B2 (en) * | 2016-07-14 | 2019-11-19 | Hamilton Sundstrand Corporation | Air turbine start system |
| JP6938139B2 (en) * | 2016-11-28 | 2021-09-22 | 三菱パワー株式会社 | Steam turbine equipment |
| CN113027544A (en) * | 2021-05-13 | 2021-06-25 | 西安热工研究院有限公司 | Equal-nozzle-number multi-arc-section high-regulation valve-nozzle group arrangement structure |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1473690A (en) * | 1922-05-31 | 1923-11-13 | Oscar H Wolner | Serial-flow turbine |
| DE679924C (en) * | 1936-08-30 | 1939-08-17 | Erich Koepke | Switching device for steam turbines |
| DE676982C (en) * | 1937-11-02 | 1939-06-16 | Fried Krupp Germaniawerft Akt | High pressure single seat valve for steam turbines |
| DE690631C (en) * | 1939-02-12 | 1940-05-03 | Siemens Schuckertwerke Akt Ges | |
| US2304993A (en) * | 1941-06-20 | 1942-12-15 | Westinghouse Electric & Mfg Co | Steam turbine apparatus |
| US2376212A (en) * | 1945-03-22 | 1945-05-15 | Gen Electric | Elastic fluid turbine arrangement |
| DE1915267B2 (en) * | 1969-03-26 | 1971-05-06 | Siemens AG, 1000 Berlin u 8000 München | INPUT BOX FOR NOZZLE GROUP CONTROL OF STEAM TURBINES |
| JPS57143106A (en) * | 1981-02-26 | 1982-09-04 | Toshiba Corp | Geothermal turbine |
| US4456032A (en) * | 1982-01-18 | 1984-06-26 | Elliott Turbomachinery Company, Inc. | Fluid admission valve structure |
| JPS5990703A (en) * | 1982-11-15 | 1984-05-25 | Fuji Electric Co Ltd | Stage for adjusting speed of steam turbine |
| DE4214775A1 (en) * | 1992-05-04 | 1993-11-11 | Abb Patent Gmbh | Steam turbine with a rotary valve |
| US6398518B1 (en) * | 2000-03-29 | 2002-06-04 | Watson Cogeneration Company | Method and apparatus for increasing the efficiency of a multi-stage compressor |
-
2007
- 2007-06-08 EP EP07011268A patent/EP2000632A1/en not_active Withdrawn
-
2008
- 2008-04-25 CA CA002689224A patent/CA2689224A1/en not_active Abandoned
- 2008-04-25 BR BRPI0812409-4A2A patent/BRPI0812409A2/en not_active Application Discontinuation
- 2008-04-25 EP EP08736568A patent/EP2153029A1/en not_active Withdrawn
- 2008-04-25 US US12/602,891 patent/US20100178153A1/en not_active Abandoned
- 2008-04-25 WO PCT/EP2008/055045 patent/WO2008148607A1/en active Application Filing
- 2008-04-25 CN CN200880019281A patent/CN101680308A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| US20100178153A1 (en) | 2010-07-15 |
| EP2000632A1 (en) | 2008-12-10 |
| WO2008148607A1 (en) | 2008-12-11 |
| EP2153029A1 (en) | 2010-02-17 |
| CN101680308A (en) | 2010-03-24 |
| BRPI0812409A2 (en) | 2014-12-02 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |