EP2805026B1 - Turbinensystem mit drei an einem zentralen getriebe angekoppelten turbinen und verfahren zum betreiben einer arbeitsmaschine - Google Patents

Turbinensystem mit drei an einem zentralen getriebe angekoppelten turbinen und verfahren zum betreiben einer arbeitsmaschine Download PDF

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Publication number
EP2805026B1
EP2805026B1 EP13710387.5A EP13710387A EP2805026B1 EP 2805026 B1 EP2805026 B1 EP 2805026B1 EP 13710387 A EP13710387 A EP 13710387A EP 2805026 B1 EP2805026 B1 EP 2805026B1
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EP
European Patent Office
Prior art keywords
turbine
fluid line
fluid
turbines
turbine system
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Application number
EP13710387.5A
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German (de)
English (en)
French (fr)
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EP2805026A1 (de
Inventor
Thomas Müller
Volker Neumann
Marc OVERATH
Matthias Schleer
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Howden Turbo GmbH
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Howden Turbo GmbH
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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
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/12—Combinations with mechanical gearing
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/18—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means
    • F01D1/20—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means traversed by the working-fluid substantially axially
    • 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
    • F01D13/00—Combinations of two or more machines or engines
    • 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
    • F01D13/00—Combinations of two or more machines or engines
    • F01D13/003—Combinations of two or more machines or engines with at least two independent shafts, i.e. cross-compound
    • 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
    • F01D13/00—Combinations of two or more machines or engines
    • F01D13/02—Working-fluid interconnection of machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
    • F01K7/04—Control means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/40—Transmission of power

Definitions

  • the present invention relates generally to the field of turbine technology.
  • the present invention relates in particular to a turbine system which has a plurality of turbines which are connected in series with respect to the flow of a working fluid and which can jointly drive a working machine.
  • the present invention further relates to a turbine system having such a turbine system and a work machine mechanically coupled to the turbine system.
  • the present invention relates to a method for operating a work machine by means of such a turbine system.
  • Turbines and in particular steam turbines are often used to convert thermal energy into mechanical energy.
  • the working fluid or the steam is typically expanded along the direction of flow via a turbine with a turbine shaft.
  • the turbine can be a so-called multi-stage turbine, which has several identical or different arrangements, each consisting of a rotor blade row (rotor blade row) and a stator blade row (guide blade row).
  • the turbine shaft drives a work machine either directly or indirectly via a separate gear.
  • a turbine system in which two separate turbines, each having a turbine housing, are flowed through in succession by the working fluid.
  • the two turbines are arranged on one or on two separate transmission shafts.
  • the two turbines drive the working machine via the gear shaft. Due to the usually small number of rows of rotor blades in both turbines, which are typically used for such a turbine system, the thermodynamic efficiency of such a turbine system is comparatively low.
  • the disclosure of FR 633903 A may be helpful in understanding the present invention.
  • the present invention has for its object to provide an easy to implement turbine system, a turbine system and a method for operating a machine with a good thermodynamic efficiency.
  • the invention consequently relates to a turbine system according to claim 1, a turbine system with such a turbine system according to claim 11 and a method for operating a work machine using such a turbine system according to claim 12.
  • Advantageous embodiments, further features and details of the present invention result the dependent claims, the description and the drawings.
  • Features and details that are described in connection with the turbine system apply, of course, also in connection with the turbine system and the method for operating a work machine. The same applies in reverse, so that reference can always be made to one another with regard to the disclosure of the individual aspects of the invention.
  • a turbine system which has (a) a first turbine, (b) a second turbine, (c) a third turbine, (d) a central transmission which is mechanically coupled on the input side to the three turbines and which has a mechanical connection on the output side to which a mechanical energy-absorbing work machine can be connected, (e) a first fluid line for passing on a working fluid from the first turbine to the second turbine, (f) a second fluid line for passing on the working fluid from the second Turbine to the third turbine, (g) a first connection device which is assigned to the first fluid line and which is set up such that a first partial mass flow of the working fluid can be removed from the first fluid line or can be supplied to the first fluid line, and (h) a second connection device which of the second fluid line is assigned and which is set up in such a way that a second partial mass flow of the working fluid can be removed from the second fluid line or can be supplied to the second fluid line.
  • the turbines of the turbine system are connected in series with
  • the turbine system described is based on the knowledge that in a turbine system which has at least three turbines, not all turbines have to be arranged on a common shaft, but can be mechanically coupled to a central transmission.
  • the working fluid, which has done work in the first turbine and then leaves the first turbine can be transferred to the second turbine by means of the first fluid line.
  • the working fluid, which has done work in the second turbine and then leaves the second turbine can be transferred to the third turbine by means of the second fluid line.
  • the described turbine system with a central transmission offers the possibility of arranging the individual turbines no longer along an elongated row, but flexibly in a spatially compact construction.
  • the described turbine system can thus be implemented within a comparatively small installation space. Due to the possibility of flexibly choosing the spatial arrangement of the individual turbines, the turbine system described can be adapted in a relatively simple manner to a specification specified by a customer. In addition, the turbine system described can be converted relatively easily if necessary and, for example, can be adapted accordingly in the event of changed operating parameters. In the event of a revision, maintenance or repair, particularly easy accessibility of the individual components of the turbine system described are guaranteed. Furthermore, the turbine system described can be implemented comparatively inexpensively.
  • Another advantage of the turbine system described in this document is that, compared to known turbine systems in which the individual turbines are coupled to a common, relatively long shaft, several short individual turbine shafts are used. In this way, a particularly high so-called quick start capability can be achieved in an advantageous manner.
  • the turbines described can in particular be turbines which each take energy from the working fluid only because of an expansion of the working fluid and which, in addition to an expansion stage, have no compressor stage.
  • the working fluid may be any pressurized fluid capable of performing mechanical work as it passes through the turbine.
  • the working fluid can in particular be steam (eg water vapor) be generated by a water vapor generator.
  • the water vapor generator can be a power plant which generates the water vapor primarily for the purpose of use by the turbine system described.
  • the water vapor generator can also be a system which primarily generates the water vapor for other processes (e.g. for the purpose of cleaning and / or sterilization) and which only supplies the water vapor to the turbine system described when the water vapor is not just for these processes is used.
  • the working fluid can also be a simple gas that has been previously compressed to temporarily store energy.
  • the gas compression can be carried out, for example, by a compressor operated with electrical energy in a period in which, for example, a larger quantity of electrical energy is provided by regenerative energy sources than is currently being consumed.
  • the turbines described can be any type of turbine in which the working fluid drives a rotor.
  • the structural design of the turbines depends in a known manner on the working fluid used. If steam is used as the working fluid, these are so-called steam turbines. If the working medium is a gas under pressure, then one usually speaks of gas expansion turbines.
  • the turbine system further comprises (a) a first control device which is assigned to the first connection device for setting the strength of the first partial mass flow and / or (b) a second control device which is assigned to the second connection device for setting the strength of the second partial mass flow.
  • the control devices described can each have an actuator which, for example, due to a Narrowing or widening its cross-section can determine the strength or the height of the respective (partial) mass flow, which is fed into the relevant fluid line from the outside via the connecting device in question or is discharged to the outside through the relevant fluid line.
  • the control devices described can each have a suitable sensor, which detects a state variable, such as the pressure of the working fluid in the relevant fluid line, the actuator, for example an adjustable valve or an adjustable throttle, based on the detection value of this state variable, the relevant (part) Mass flow can set so that this state variable remains at least approximately constant even with changing operating conditions.
  • decoupling or extracting a partial mass flow does not necessarily mean that this partial mass flow is lost for energy generation.
  • This partial mass flow can namely be supplied to the described turbine system again at another point, for example, via another connection device.
  • a (partial) mass flow fed into the turbine system from outside can also have been taken from the main mass flow of the turbine system described elsewhere by means of another connection device.
  • the use of at least one intermediate storage for the temporary storage of working fluid is also possible.
  • the two control devices in conjunction with the associated connection devices, offer the possibility of realizing precisely defined intermediate pressure stages, of which the working fluid removed in a simple and controlled manner and / or to which the working fluid can be supplied in a simple and controlled manner. This significantly increases the flexibility of the entire turbine system, particularly when there are load changes.
  • the first turbine and the second turbine are coupled to the central transmission via a common shaft, in particular one of the two turbines on a first side of the central transmission and the other of the two turbines on a second side of the central transmission is arranged.
  • the first side is opposite the second side.
  • the common shaft can be a one-piece or a multi-piece shaft. In the case of a multi-piece shaft, however, the several pieces of the common shaft should be connected to one another so firmly that the rotors of the two turbines are coupled to one another in a rotationally fixed manner.
  • the rotors of the two turbines can be arranged "on the fly", ie without a bearing on the turbine side in the respective turbine housing.
  • the rotor or the entire turbine is located outside the bearing points of the common shaft. This has the advantage that a suitable mounting of the common shaft only has to be present in or on the central transmission.
  • a suitable bearing can be implemented, for example, by means of two bearings, one of the two bearings on the first side and the other of the two bearings is arranged on the opposite second side of the central transmission.
  • the first turbine and the third turbine are coupled to the central transmission in such a way that the first turbine can be operated with a first rotation frequency and the third turbine with a second rotation frequency, the first rotation frequency being different from the second rotation frequency .
  • suitable transmission ratios in the coupling between the turbine in question and the central transmission a specific ratio between the first rotation frequency and the second rotation frequency can be set.
  • each turbine can then be operated in an optimal speed range. A particularly high efficiency of the individual turbines and thus of the entire turbine system can thus be achieved.
  • the shaft speeds of the first turbine and the second turbine can be adapted to the respective turbines and in particular to the pressure levels assigned to the respective turbines.
  • the described turbine system can be optimized in terms of its efficiency or in terms of its efficiency in a simple manner.
  • At least one of the three turbines is a radial turbine.
  • a radial turbine typically has a shorter design than an axial turbine, the entire turbine system can thus be implemented in a particularly compact design.
  • turbine which has the (compressed) Working fluid is supplied first, be designed as a radial turbine.
  • a radial turbine then represents the first control stage for the entire turbine system, by means of which the total mass flow of working fluid which flows through the entire turbine system is adjusted in a controlled manner.
  • this (first) radial turbine can be equipped with suitable control valves, by means of which the total mass flow of working fluid can be adjusted in a known manner.
  • At least one of the three turbines is an axial turbine.
  • the axial turbine in which the working fluid flows in the axial direction through the corresponding turbine housing and thereby drives the rotor or the rotor, can consist of one stage or preferably of several stages, with one stage (a) in each case a row on the rotor or on Rotor-mounted rotating blades and (b) has a series of stationary vanes attached to the housing.
  • the rotor of the axial turbine is coupled to an axial shaft which is mounted on the side of the central transmission and which is arranged in a housing of the axial turbine without bearing.
  • This means that the rotor or the axial shaft of the axial turbine is arranged "on the fly" on one side.
  • Bearing is therefore only provided on the section of the axial shaft, which section lies outside the axial turbine and is assigned to the central transmission.
  • the bearing on the central transmission can be implemented by means of one or more bearings which are axially offset from one another.
  • the axial shaft is not mounted in the turbine housing but only in or on a housing of the central gear.
  • a "flying" bearing in the turbine housing includes offers the advantage that changes in expansion in the case of fluctuating temperatures, which occur in particular during load changes, do not lead to tensioning of the axial shaft in relation to bearings in the turbine housing.
  • the rotor of the axial turbine has a plurality of turbine stages, each turbine stage arranged around the axial shaft (a) having a row of rotatable rotor blades attached to the rotor and (b) a row of stationary guide vanes attached to the housing.
  • the rotor blades of a row are attached to a rotor blade carrier and the plurality of rotor blade carriers are fixed on the axial shaft by means of a pulling device.
  • the pulling device can be, for example, a so-called tie rod, which comprises a thread formed on the axial shaft and a nut engaging in the thread.
  • tie rod which comprises a thread formed on the axial shaft and a nut engaging in the thread.
  • the turbine system further comprises (a) a fourth turbine which is mechanically coupled to the central transmission, (b) a third fluid line for passing the working fluid from the third turbine to the fourth turbine and (c) one third connection device which is assigned to the third fluid line and which is set up in such a way that a third partial mass flow of the working fluid can be removed from the third fluid line or can be supplied to the third fluid line is.
  • a fourth turbine which is mechanically coupled to the central transmission
  • a third fluid line for passing the working fluid from the third turbine to the fourth turbine
  • one third connection device which is assigned to the third fluid line and which is set up in such a way that a third partial mass flow of the working fluid can be removed from the third fluid line or can be supplied to the third fluid line is.
  • a fluid line which is provided with a connection device, is preferably provided between two turbines which are adjacent from the point of view of the flow direction of the working medium, so that a corresponding partial mass flow of the working fluid can be removed from the relevant fluid line or can be supplied to the relevant fluid line.
  • a control device is further preferably assigned to the connection device in question, so that the strength of the partial mass flow in question can be set precisely and operation which is optimal with respect to the efficiency of the turbine system can be ensured.
  • a turbine system which has (a) a turbine system of the type described above and (b) a work machine which is coupled to the mechanical connection of the central transmission.
  • the turbine system described is based on the knowledge that the above-mentioned Turbine system can be mechanically coupled to a working machine, so that energy contained in the working fluid can be removed from the working fluid and transferred to the working machine in a mechanical manner.
  • a rotor of the working machine can be mechanically coupled to the mechanical connection of the central transmission using a coupling or a flange.
  • the working machine can in particular be an electrical generator, which can be used to generate electricity.
  • the working machine can also be a mechanical machine which uses the mechanical energy that is supplied to it by the turbine system described in a suitable manner for performing mechanical activities.
  • the work machine can be, for example, a pump, a compressor, a fan and / or a press.
  • a method for operating a work machine comprises (a) providing a working fluid containing an energy, (b) supplying the working fluid to a turbine system of the type described above, the turbine system drawing at least part of the energy of the working fluid and at least part of the extracted energy in converts mechanical work, and (c) operating the work machine with the converted mechanical work.
  • the method described is also based on the knowledge that when using the above-mentioned Turbine system the machine can be operated in an efficient manner.
  • the energy is extracted from the working fluid and converted into mechanical energy, which is then transferred to the working machine by means of a purely mechanical coupling.
  • the term “energy-containing working fluid” can be understood in particular to mean that the working fluid has been subjected to energy thermodynamically, so that the working fluid has, in particular, a high temperature and / or a high pressure. If the working fluid is a vapor, for example water vapor, then the hot and / or high-pressure water vapor additionally contains an evaporation energy which occurs when the vapor condenses leads to the release of condensation energy, which can then also be converted into mechanical work.
  • FIG. 1 shows a schematic representation of a turbine system 100 according to an embodiment of the invention.
  • the turbine system 100 has a turbine system 110 which drives a work machine 120.
  • the work machine 120 can in particular be an electrical generator that can be used to generate electricity.
  • the work machine 120 can also be any mechanical machine that uses the mechanical energy that is supplied to it by the turbine system 110 in a suitable manner for performing mechanical activities, for example for pumping, compressing, and / or for pressing processes.
  • Turbine system 110 has four steam turbines, a first steam turbine 151, a second steam turbine 152, a third steam turbine 153 and a fourth steam turbine 154. How out Figure 1 as can be seen, these steam turbines 151, 152, 153 and 154 are connected in series with respect to the general flow direction of a working fluid.
  • the working fluid which is water vapor according to the exemplary embodiment shown here, flows into a fluid inlet 116, strongly overheated by a water vapor generator.
  • a corresponding one Inlet mass flow 116a of water vapor then flows into the first steam turbine 151, in which the water vapor performs mechanical work in a known manner and thereby in Figure 1 drives not shown rotor of the first steam turbine 151.
  • the water vapor emerging from the first steam turbine 151 which still contains a considerable amount of energy which was not converted into mechanical work by the comparatively short first steam turbine 151, then flows via a first fluid line 161 into the second steam turbine 152, in which also in the energy contained in the water vapor is converted into mechanical work.
  • the first fluid line 161 has a first connection device 171, which according to the exemplary embodiment shown here is a simple branch, for example a so-called T-piece.
  • a first partial mass flow 171a of working fluid can be coupled out of the entire mass flow to a first fluid connection 176 via the connection device 171, or an additional mass flow of working fluid can be fed from the first fluid connection 176 into the first fluid line. In this way, the energy which is supplied to the second steam turbine 152 can be adjusted and the power of the entire turbine system 110 can thus be adapted.
  • the first connection device 171 or the first fluid line 161 is assigned a first control device 171b, which has a pressure sensor (not shown) with which the pressure of the working fluid in the fluid line 161 is detected.
  • a pressure sensor not shown
  • the (partial) mass flow can be adjusted based on the detected pressure in such a way that the pressure remains at least approximately constant even under changing operating conditions.
  • the steam turbine 152 can be operated in an optimal operating mode. To this In this way, a high degree of efficiency can be guaranteed for the steam turbine 152 and thus of course also for the entire turbine system 110.
  • the water vapor emerging from the second steam turbine 152 which still contains a considerable amount of energy which has not yet been used, then flows into the third steam turbine 153 via a second fluid line 162.
  • the a (second) connection device 172 designed as a T-piece and a (second) control device 172b are arranged in the second fluid line 162, so that a second partial mass flow 172 is likewise transferred in a controlled manner to a second fluid connection 177 or from the second fluid connection 177 into the second fluid line 162 can be fed.
  • the third steam turbine 153 and the fourth steam turbine 154 connected downstream of the third steam turbine 153 are connected to one another via a third fluid line 163. Furthermore, in the third fluid line there is a third connection device 173, via which a third partial mass flow 173a of water vapor can be branched off from the third fluid line 163 and fed to a third fluid connection 178 and / or via which additional water vapor from the third fluid connection 178 into the third fluid line 163 can be fed.
  • a third control device 173b ensures that the corresponding removal or supply of water vapor takes place in a controlled manner.
  • the pressure sensor of the respective control device 171b, 172b, 173b is preferably arranged upstream in the respective fluid line 161, 162, 163 in relation to the branching of the respective connection device 171, 172, 173.
  • the adjustable valve of the respective control device 171b, 172b, 173b is in relation to the branching of the respective connection device 171, 172, 173 is preferably arranged downstream in the respective fluid line 161, 162, 163.
  • the adjustable valve can be arranged directly in front of or on the housing of the next turbine.
  • an outlet mass flow 118a of water vapor emerges which has flowed through all the turbines 151, 152, 153 and 154 or which has been fed into the turbine system 110 via one of the fluid connections 176, 177 or 178.
  • the escaping water vapor can then be fed to a heater (not shown) in a known manner.
  • This heater can in turn be coupled to the fluid inlet 116, so that a closed circuit of working fluid or water vapor can be implemented.
  • the rotors of the steam turbines 151 and 152 are connected to one another via a common shaft 131a. This means that the rotation frequency of the steam turbines 151 and 152 is the same.
  • a gear (not shown) could also be connected between the two rotors of the steam turbines 151 and 152, so that a first rotational frequency of the rotor of the first steam turbine 151 and a second rotational frequency of the rotor of the second steam turbine 152 are in a fixed relationship to one another.
  • the two rotors of the steam turbines 153 and 154 are connected to one another via a common shaft 132a or, if appropriate, mechanically coupled to one another via an additional gear.
  • a central component of the turbine system 110 described here is a central gear 130, which has a gear 134 and two pinions.
  • a first pinion 131 of the two pinions is attached to the shaft 131a.
  • the second pinion 132 is attached to the shaft 132a. Both pinions 131 and 132 are in engagement with the gear 134.
  • the central gear 130 also has a central drive shaft 136, which connects the gear 134 and the engine 120 to one another.
  • FIG. 2 shows a perspective view of a turbine system 200 according to another embodiment of the invention.
  • the turbine system 200 has a base plate 202 on which at least the main components of the turbine system 200 are attached or mounted.
  • the turbine system 200 has (a) a first steam turbine 251 designed as a radial turbine, (b) a second turbine 252 designed as an axial turbine and (c) a third steam turbine 253 also designed as an axial turbine 253. All turbines 251, 252 and 253 or the rotors of these turbines 251, 252 and 253 are coupled to one another via a central gear 230.
  • the central transmission 230 is mechanically coupled on the output side via a drive shaft 236 to a work machine 220 designed as an electrical generator.
  • An inlet mass flow 216a of working fluid is supplied to the first steam turbine 251.
  • the strength of this inlet mass flow 216a which is regulated by means of a plurality of control valves 251a, thus essentially determines the output of the entire turbine system 200.
  • Working fluid emerging from the first steam turbine 251 is fed to the second steam turbine 252 via a first fluid line 261.
  • Working fluid emerging from the second steam turbine 252 is supplied to the third steam turbine 253 via a second fluid line 262.
  • a first connection device 271 is located in the first fluid line 261 together with an in Figure 2 First control device, not shown, so that a first partial mass flow 271a can be coupled out of the first fluid line 261 or, alternatively, a mass flow, not shown, can be fed into the first fluid line 261.
  • a second connection device 272 is located in the second fluid line 262 together with one in Figure 2 Second control device, not shown, so that a second partial mass flow 272a can be coupled out of the second fluid line 262 or, alternatively, a mass flow, not shown, can be fed into the second fluid line 262.
  • An outlet mass flow 218a of working fluid which has flowed through all the turbines 251, 252 and 253 or which has been fed into the turbine system 200 via one of the connection devices 271 or 272 is then fed to a heater (not shown).
  • This heater can in turn provide the inlet mass flow 216a, so that a closed circuit of working fluid or water vapor can be implemented.
  • Figure 3 shows a turbine system 310 with a first steam turbine 351 designed as a radial turbine, with a second steam turbine 352 designed as an axial turbine and with a third steam turbine 353 also designed as an axial turbine.
  • the first steam turbine 351 and the second steam turbine 352 are connected to one another via a first fluid line (not shown) .
  • the first steam turbine 351 has a first housing 351a
  • the second steam turbine 352 has a second housing 352a
  • the third steam turbine 353 has a third housing 353a.
  • the first fluid line is also assigned a first connection device, also not shown, and a first control device, also not shown.
  • the second steam turbine 352 and the third steam turbine 353 are connected to one another via a second fluid line, not shown, to which a second connection device, also not shown, and a second control device, also not shown, are assigned.
  • the three steam turbines are mechanically coupled to one another by means of a central transmission 330.
  • a central transmission 330 With the transmission 330 there are both a first pinion 331 and a second pinion 332 in engagement with a gear 334.
  • the first pinion 331 has more teeth than the second pinion 332, so that the rotation frequency of the rotors of the first and the second steam turbine 351 and 352 is greater than the rotation frequency of the rotor of the third steam turbine 353.
  • the gear 334 is arranged on a central drive shaft 336, which is mounted in a housing of the central transmission 330 by means of two bearings 338.
  • a mechanical connection 337 designed as a flange, to which one in Figure 3 Drive machine, not shown, can be connected.
  • the two axial turbines 352 and 353 each have a multi-stage configuration of one guide vane and possibly one rotor vane.
  • a rotor blade 381a and a guide blade 381b are assigned to a first stage 381 of the multi-stage axial turbine 353.
  • a rotor blade 382a and a guide blade 382b are assigned to a second stage 382 of the multi-stage axial turbine 353.
  • a rotor blade 383a and a guide blade 383b are assigned to a third stage 383 of the multi-stage axial turbine 353.
  • the rotor blades 381a, 382a and 383a are arranged on an axial shaft 385 of the steam turbine 353.
  • the axial shaft 385 is non-rotatably connected to the shaft 332a.
  • adjacent rotor blades i.e. the rotor blades 381a and 382a as well as the rotor blades 382a and 383a are arranged on the axial shaft 385 in a rotationally fixed manner by means of an axial front toothing.
  • a tie rod connection which is realized by means of a nut 386 in connection with an external thread formed on the axial shaft 385, ensures that the rotor blades 381a, 381b and 381c are firmly locked on the axial shaft 385.
  • the bearings 332b are radial bearings.
  • An axial bearing is realized here by means of the second pinion 332, which, as in FIG Figure 3 can be seen, each has a shoulder on the left and right, the two shoulders engaging with the gear 334 in the axial direction. In this way, one generated during the operation of the steam turbine 353 Axial thrust to the left over the two shoulders of the pinion 332 and the gear 334 transmitted to the bearing 338 and taken up by this.
  • FIG. 4 shows a turbine system 410 which differs from that shown in FIG Figure 3
  • the central drive shaft 336 is thus driven by a total of four steam turbines, the fourth steam turbine 454 being connected downstream of the third steam turbine 353 by means of a third fluid line (not shown).
  • the third fluid line is assigned a second connection device, not shown, and a second control device, also not shown, for regulating the amount of working fluid withdrawn from the third fluid line and / or for regulating the amount of additional working fluid fed into the third fluid line.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • General Details Of Gearings (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP13710387.5A 2012-03-29 2013-03-15 Turbinensystem mit drei an einem zentralen getriebe angekoppelten turbinen und verfahren zum betreiben einer arbeitsmaschine Active EP2805026B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012205159A DE102012205159A1 (de) 2012-03-29 2012-03-29 Turbinensystem mit drei an einem zentralen Getriebe angekoppelten Turbinen, Turbinenanlage und Verfahren zum Betreiben einer Arbeitsmaschine
PCT/EP2013/055341 WO2013143877A1 (de) 2012-03-29 2013-03-15 Turbinensystem mit drei an einem zentralen getriebe angekoppelten turbinen und verfahren zum betreiben einer arbeitsmaschine

Publications (2)

Publication Number Publication Date
EP2805026A1 EP2805026A1 (de) 2014-11-26
EP2805026B1 true EP2805026B1 (de) 2020-06-10

Family

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EP13710387.5A Active EP2805026B1 (de) 2012-03-29 2013-03-15 Turbinensystem mit drei an einem zentralen getriebe angekoppelten turbinen und verfahren zum betreiben einer arbeitsmaschine

Country Status (9)

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US (1) US20150044021A1 (zh)
EP (1) EP2805026B1 (zh)
JP (1) JP2015514897A (zh)
CN (1) CN104204420B (zh)
BR (1) BR112014023698A8 (zh)
DE (1) DE102012205159A1 (zh)
IN (1) IN2014DN07393A (zh)
RU (1) RU2659848C2 (zh)
WO (1) WO2013143877A1 (zh)

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Publication number Priority date Publication date Assignee Title
CA2962461C (en) * 2014-09-25 2022-06-21 Nuhn Industries Ltd. Fluid pump with multiple pump heads
CN112576317B (zh) * 2020-12-08 2023-11-24 内蒙古汇能集团蒙南发电有限公司 一种多级涡轮发电机

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Publication number Priority date Publication date Assignee Title
FR555683A (fr) * 1922-05-13 1923-07-04 Bbc Brown Boveri & Cie Installation de turbines à vapeur pour hautes pressions et hautes températures de surchauffe
GB226232A (en) * 1923-12-14 1925-08-06 Ljungstroms Angturbin Ab Improvements in turbine aggregates
FR633903A (fr) * 1926-05-06 1928-02-06 Locomotive à turbines à vapeur avec turbines de commande disposées dans des enveloppes différentes
CH126468A (de) * 1927-05-19 1928-06-16 Escher Wyss Maschf Ag Verfahren zum Betreiben von Dampfkraftanlagen.
GB370371A (en) * 1929-10-04 1932-04-07 Siemens Ag Multi-stage radial turbine, more particularly for high pressure steam
GB575812A (en) * 1942-12-12 1946-03-06 Bbc Brown Boveri & Cie Ultra-high temperature turbine plant
US3175366A (en) * 1961-07-28 1965-03-30 Taranov Boris Pavlovich Steam turbine with regulated bleeding of steam
US3724214A (en) * 1971-03-05 1973-04-03 Westinghouse Electric Corp Extraction control system for a turbogenerator set
JPS5817358B2 (ja) * 1978-03-07 1983-04-06 川崎重工業株式会社 多段タ−ボ形圧縮機
FR2518644B1 (fr) * 1981-12-18 1986-05-02 Intelautomatisme Turbo-machine
JPS5946303A (ja) * 1982-09-10 1984-03-15 Toshiba Corp タ−ビン制御装置
FR2635561B1 (fr) * 1988-08-16 1990-10-12 Alsthom Gec Installation de turbine a vapeur avec soutirage regle
DE4234739C1 (de) * 1992-10-15 1993-11-25 Gutehoffnungshuette Man Getriebe-Mehrwellenturbokompressor mit Rückführstufen
DE4239138A1 (de) * 1992-11-20 1994-05-26 Bhs Voith Getriebetechnik Gmbh Verdichteranlage
JP4764255B2 (ja) * 2006-05-25 2011-08-31 株式会社神戸製鋼所 小型貫流ボイラ発電システムおよびその運転制御方法
JP2009047123A (ja) * 2007-08-22 2009-03-05 Toshiba Corp 蒸気タービン
JP4993503B2 (ja) * 2008-03-25 2012-08-08 パンパシフィック・カッパー株式会社 蒸気タービンの出力増強方法
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Also Published As

Publication number Publication date
CN104204420B (zh) 2016-08-24
RU2014143499A (ru) 2016-05-20
RU2659848C2 (ru) 2018-07-04
WO2013143877A1 (de) 2013-10-03
BR112014023698A2 (zh) 2017-06-20
EP2805026A1 (de) 2014-11-26
CN104204420A (zh) 2014-12-10
JP2015514897A (ja) 2015-05-21
IN2014DN07393A (zh) 2015-04-24
DE102012205159A1 (de) 2013-10-02
BR112014023698A8 (pt) 2017-07-25
US20150044021A1 (en) 2015-02-12

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