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EP3004591A2 - Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit - Google Patents

Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit

Info

Publication number
EP3004591A2
EP3004591A2 EP14725971.7A EP14725971A EP3004591A2 EP 3004591 A2 EP3004591 A2 EP 3004591A2 EP 14725971 A EP14725971 A EP 14725971A EP 3004591 A2 EP3004591 A2 EP 3004591A2
Authority
EP
European Patent Office
Prior art keywords
turbine
stage
heat
heat exchanger
heat pump
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.)
Withdrawn
Application number
EP14725971.7A
Other languages
German (de)
English (en)
Inventor
Daniel Reznik
Henrik Stiesdal
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to EP14725971.7A priority Critical patent/EP3004591A2/fr
Publication of EP3004591A2 publication Critical patent/EP3004591A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor

Definitions

  • Heat pump with a connected in a circuit first thermal fluid energy machine and second thermal fluid energy machine
  • the invention relates to a heat pump with a circuit for a working fluid with a prime mover, a connected as a working machine in the circuit first thermal fluid energy machine and a connected as an engine in the cycle ⁇ run second fluid energy machine.
  • the first fluid energy machine and the two ⁇ te fluid energy machine are mechanically coupled together, for example by a common drive ⁇ strand.
  • a heat pump of the aforementioned kind is known for ⁇ play, from WO 2009/044139 AI. This heat ⁇ pump is used to transport the heat from a cold storage in a heat storage.
  • a first thermal fluid energy machine and a second ther ⁇ mixing fluid energy machine in the form of piston machines are used.
  • These machines are driven by an electric motor, which is always operated when excess electrical energy is available in the electrical network. This is the case with regenerative power generation or when power plant capacities can not be timely adjusted to the current power consumption.
  • the stored thermal energy can be discharged in case of need so in a sub ⁇ supply of the network with electric power by reversing the heat pump cycle, which can be generated by means of a generator electrical power.
  • thermodynamic machines As fluid energy machines on an industrial scale.
  • the cost of the design, construction and construction of such thermodynamic fluid engines is significant.
  • available compressors and turbines operate in other operating ranges and are therefore not available with satisfactory performance. to operate.
  • Steam turbines operate at a different density of the process fluid and are excreted for the sole reason ⁇ .
  • Gaseous process fluids are used in gas turbines, but the gases are heated in gas turbines to over 1000 ° C and are therefore in a lower density than would be required for a heat pump in the thermal energy storage in the present application.
  • the operating point can not be selected by Ver ⁇ application of a commercially available gas turbine itself.
  • the object of the invention is therefore to develop a heat pump of the type specified in that way that available hydrodynamic flow machines can be used inexpensively.
  • the second thermal fluid energy machine has the rotor of a turbine stage of a gas turbine and the first thermal Fluidenergy- machine has the compressor stage of a gas turbine, in which case the following is considered according to the invention.
  • the compressor stage comes from a gas turbine, which has a higher output than the gas turbine, which comes from the turbine ⁇ nenwear.
  • the compressor stage and turbine stage are mechanically coupled together via a first gearbox such that the compressor stage rotates more slowly than the turbine stage.
  • the gear ratio ⁇ between compressor stage and turbine stage causes the turbine stage and the compressor stage can be operated at different speeds.
  • the working gas in the heat pump must be heated to 370 ° C.
  • Proceeding ⁇ based passes by a model calculation, the working gas at 1 bar and 5 ° C to the first thermal fluid energy machine. Compression by means of the first fluid energy machine operating as a compressor leads to a pressure increase to 15 bar and, consequently, to a temperature increase to 370 ° C. This calculation is based on the following formula
  • T 2 is the temperature at the compressor outlet
  • K is the compressibility, which is 1.4 in air.
  • the isentropic efficiency n c can at the
  • the heated working gas now passes through a heat exchanger, where the bulk of the available thermal energy is stored.
  • the working gas is cooled to 100 ° C, while the pressure (apart from strömungsbe ⁇ related pressure losses) at 14.5 bar remains largely intact.
  • the working gas in the turbine stage is relieved so that it arrived at a pressure level of 1.1 bar at ⁇ .
  • the working gas cools to -70 ° C.
  • the working beitsgas can then withdraw the ambient heat and heats up again to 5 ° C basis for this Be ⁇ bill is also the above mentioned formula.
  • engine and work machine are used in the context of this application so that a work machine takes on mechanical work to fulfill its purpose.
  • a thermal fluid energy machine used as a work machine is thus used as a compressor or as a compressor.
  • a thermal fluid energy machine for performing work converts the space available in the working gas thermi ⁇ specific energy.
  • the thermal fluid energy machine is thus operated as a motor.
  • thermal fluid energy machine is a generic term for machines that can extract thermal energy from or impart thermal energy to a working fluid, in the context of this application, a working gas.
  • Thermal energy is understood to mean both thermal energy and refrigeration energy machines can be designed for example as a piston engine.
  • hydrodynamic thermal Fluidener ⁇ energy machinery can be used, the wheels allow a continuous flow of the working gas.
  • turbine or compressor axially acting used Preferably, turbine or compressor axially acting used.
  • the turbine stage is taken from the Siemens gas turbine with the type designation SGT-100. This has an output power ⁇ 4.35 to 5.4 MW at 17,384 revolutions / min, and a compression ratio of 16.6: 1st
  • the gas throughput is about 21 kg / s.
  • combustion gases at about 1100 ° C relaxed. This results in a corrected mass flow for operation as Turbi ⁇ nenge the gas turbine to kg / s. 52 kg
  • the low-pressure part of the turbine stage can be calculated equally ⁇ SEN to
  • the working machine is an electric motor and the mechanical coupling to the turbine stage and the compressor stage is carried out via a second gear, wherein the ratio ⁇ ratio is determined such that the electric motor is operated at its rated speed.
  • synchronous machines with rotational speeds of 3000 revolutions / min can advantageously be used.
  • the gear ratio to the compressor stage can be chosen so that it is also driven at its rated speed.
  • the adaptation of the required speed for the turbine stage is possible.
  • the operation of the electric motor at its operating point advantageously results in a further gain in efficiency of the system.
  • a further embodiment of the invention provides that between the compressor stage and the turbine stage, a first heat exchanger is arranged, which emits the heat to a secondary därniklauf in which a heat storage is provided.
  • This has the advantage that the secondary circuit ⁇ not prevail among the circulation of the heat pump (primary circuit) to the printing conditions must be operated.
  • the heat storage and implemented in this channel system for exchanging the heat can be under a lower pressure, which significantly simplifies the design of the heat storage.
  • the turbine stage comprises a high-pressure part and a low-pressure part ⁇ . This design is common in gas turbines, the high-pressure part is referred to as a compressor turbine and is designed in terms of power to drive the compressor.
  • the low-pressure part of the turbine is power turbine be ⁇ draws, which provides the useful power of the gas turbine, which can be used, for example, for power generation who ⁇ .
  • both the high pressure part and the low pressure part is arranged on a Wel ⁇ le and the overall performance of the turbine stage under ⁇ supports the prime mover in the operation of the compressor stage.
  • a third heat exchanger is connected with its primary connections. Furthermore, a fourth pulptau ⁇ cher is connected between the high pressure part and the low pressure part, which exchanges heat with the environment. Behind the fourth heat exchanger and before the low pressure part of the third heat exchanger is connected with its secondary terminals.
  • This arrangement has the advantage that the Ar ⁇ beitsgas after it flows out of the high-pressure part of the turbine stage, can receive via the fourth heat exchanger heat from the environment, which can be provided to the heat pump process are available.
  • the temperature behind the high-pressure part is as low as possible, the working gas is withdrawn before entering the high-pressure part via the third heat exchanger further heat and fed back to the working gas behind the high ⁇ pressure part. This heat is converted in the low pressure ⁇ part of the turbine stage.
  • a second heat exchanger is provided in the circuit between the turbine stage and the compressor stage.
  • This heat exchanger increases the amount of heat that can be supplied to the working gas on the way from the turbine ⁇ stage to the compressor stage from the environment.
  • This heat is additionally available to the heat pump. supply and thus advantageously increases the amount of heat stored in the heat accumulator.
  • a particularly inexpensive solution is advantageous th preservation if the turbine stage having turbine blades is equipped kitchens ⁇ tet, which was dispensed with a corrosion protective coating and a thermal barrier coating.
  • the coatings mentioned are applied to gas turbines, as these are operated under extreme conditions (corrosive combustion gases above 1000 ° C heat of the process gases). In the heat pump cycle, the operation is carried out at substantially ge ⁇ ringeren temperatures of less than 100 ° and with the working medium air, so such measures for corrosion protection ⁇ are not required.
  • the turbine stage can therefore be used in the heat pump according to the invention as semi-finished component in view of the application in gas turbines.
  • the turbine stage is provided with the said protective layers, as they are also provided in gas turbines.
  • a 3-way valve is provided, with which the mass flow of the process gas can be divided, with a part in the heat pump cycle, which also contains the combustion chamber, and with another part in an additional line leading to an auxiliary turbine, which is operated fluidically independent of the turbine stage.
  • the proportion of the mass flow, the ver ⁇ remains in Wärmpumpenniklauf is quantitatively determined to be present after heat the working gas in the combustion chamber of the required under the thermal conditions corrected mass flow, so that the turbine stage can be ⁇ driven into its operating point. This has already been explained in detail above.
  • the remaining mass flow is diverted and via a fifth heat exchanger, which is provided with its primary connections in the additional power heats. Then this divided mass flow is expanded through the turbine to ⁇ set.
  • the fifth heat exchanger is fed by the waste heat of the turbine stage.
  • FIG. 1 shows a heat pump which has a circuit 11 for a working gas. This can be operated, for example, with ambient air, wherein the
  • Circuit 11 is closed. Via a drive motor M and a first gear 12, a compressor stage 13 is ben ⁇ industry .
  • the working gas which is introduced into the compressor at 5 ° C at 1 bar pressure, leaves it at a temperature of 370 ° C and a pressure of 15 bar.
  • a first heat exchanger 14 the temperature of the working gas to a secondary circuit 15 is delivered, in which a thermal storage is connected ⁇ cher sixteenth In the heat accumulator 16 is not shown in detail channel ⁇ system is formed, which also acts as a heat exchanger between ⁇ the fluid in the secondary circuit and the storage material of the heat accumulator.
  • the working fluid in the secondary circuit is heated by the heat exchanger to 350 ° C and cooled by the heat storage back to 80 ° C.
  • the pressure of the fluid can be substantially constant at 1.2 to 1.25 bar.
  • the working fluid in the circuit 11 (primary circuit) is cooled by the heat exchanger 14 to 100 ° and fed to the turbine stage 17 in a high pressure part 17h. There it is relieved to a pressure of 3.9 bar and leaves the high pressure section for 17h at 5.5 ° C. In this state, the Ar ⁇ beitsgas is then fed into the low pressure part 17n of the Turbi ⁇ nencut 17 and exits at a tempera ture ⁇ from -70 ° C and a pressure of 1.1 bar. The working gas is then fed to a second heat exchanger 18 by absorbing heat from the environment.
  • the second heat exchanger 18 by absorbing heat from the environment.
  • Heat exchanger 18 can be fed, for example, with river water.
  • the working gas leaves the second heat exchanger 18 at a temperature of 5 ° C.
  • the compressor stage 13 comes from the Siemens gas turbine SGT-400.
  • the turbine stage 17 comes from the Siemens gas turbine SGT-100.
  • the compressor stage generates a mass flow of the working gas of 40 kg / s. This is suitable for operating the turbine stage under the given thermodynamic conditions at least near its operating point. Since the compressor stage 13, a lower nominal speed on ⁇ has, as the turbine stage 17 is between the drive shafts 19a, 19b a second transmission 20 for the compressor stage and the turbine stage.
  • the heat pump can be used for charging the heat accumulator 16 when stand excess capacity available in the network elekt ⁇ step.
  • the heat accumulator 16 can be discharged via a discharge circuit 21 and a sixth heat ⁇ exchanger 22.
  • the working fluid liquid or gas
  • the working fluid is cooled from 455 ° C to 90 ° C from ⁇ , wherein the heattient- in a steam circuit 23 is fed.
  • steam is generated at a pressure of 80 bar and a temperature of 430 ° C and expanded by a steam turbine 24, then ver ⁇ liquid via a cooler 25 and fed via a feed pump 26 to the sixth jackettau- shear 22 again, with a Temperature of 32 ° C.
  • the steam turbine generated via a generator G just needed electrical power.
  • a third heat exchanger 27 is provided in the circuit 11, which extracts 17 heat the working fluid before passing through the high-pressure part 17h of the turbine stage.
  • the working gas is cooled from 100 ° C to 50 ° C.
  • the working fluid ⁇ After expansion across the high-pressure part 17h, the working fluid ⁇ then to a temperature of -40 ° C and a pressure of 4 bar. Due to this low temperature, heat from the environment (for example from river water) can be supplied to the working gas via a fourth heat exchanger 28.
  • the working gas reaches a temperature of 5 ° C again.
  • Further heating of the working gas is characterized ⁇ it enough that this is introduced into the third heat exchanger, where it extracts the heat located on the way to the high-pressure part working gas further heat and is heated to 55 ° C.
  • the working gas is the low-pressure part ⁇ supplied to 17n of the turbine stage 17 and biases bar ⁇ ent to 1.1.
  • FIG. 3 shows a fluidic circuit with which a kind of emergency operation can be realized in the heat pump cycle according to the invention, if a demand for electric current is given over a longer period of time and the heat accumulator 16 according to FIG.
  • the first heat exchanger 14 (see Figure 1) bypassed via a non-illustrated by-pass line and the heat exchanger 18 (see Figure 1) is deactivated by that the closed circuit 11 is opened before the compressor stage and behind the low-pressure part 17n.
  • a three-way valve 29 is set so that the mass flow of the working gas at 20 kg / s to the turbine stage 17 and 20 kg / s (ie half) to a
  • a burner 32 is fluidly connected, which is supplied via a feed line 33 with a fuel.
  • the volume flow ⁇ of the working gas is heated to 1100 ° C, whereby the conditions are present ⁇ conditions, which undergoes the SGT-100 turbine stage 17 in the operation as a gas turbine. Therefore, a Halbie ⁇ tion of the volume flow to 20 kg / s is required, since it is in this volume flow to the design volume flow provided during operation of the SGT-100 turbine stage as Gasturbi ⁇ ne. This allows the available in the heat pump hydrodynamic machines according to the principle of
  • Gas turbine can be used to generate in this way via a Ge ⁇ generator G electrical power.
  • the excess capacity of the compressor stage 13 is scale ⁇ builds on the secondary turbine 30th
  • the waste heat from the gas turbine can be introduced via a discharge line 34 into a fifth heat exchanger 35, which heats the working gas in the additional line 31 before passing through the additional turbine 30.
  • the figure 4 can be seen, as in the high-pressure part 17h of the turbine stage 17 as a function of the corrected

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une pompe à chaleur comprenant un circuit (11) dans lequel un compresseur (13) et une turbine (17) sont installés pour compresser et détendre le gaz de travail à tour de rôle et de cette manière charger un accumulateur de chaleur (16). L'invention prévoit d'utiliser des composants des turbines à gaz pour le compresseur (13) et les turbines (17h, 17n). Cependant, comme l'étage turbine (17) de la turbine à gaz fonctionne normalement à d'autres températures, il est nécessaire d'augmenter le débit massique du gaz de travail de sorte que l'étage turbine puisse être exploité à son point de fonctionnement. Dans ce but, l'étage compresseur (13) d'une turbine à gaz plus grande est combiné à l'étage turbine (17) d'une turbine à gaz plus petite. Comme l'étage compresseur (13) exige alors pour fonctionner une vitesse de rotation plus lente que celle de l'étage turbine (17), un mécanisme de transmission (20) est également prévu pour permettre le fonctionnement des machines hydrodynamiques à différentes vitesses de rotation.
EP14725971.7A 2013-05-31 2014-05-05 Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit Withdrawn EP3004591A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14725971.7A EP3004591A2 (fr) 2013-05-31 2014-05-05 Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP13170064.3A EP2808500A1 (fr) 2013-05-31 2013-05-31 Pompe à chaleur dotée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluidique
EP14725971.7A EP3004591A2 (fr) 2013-05-31 2014-05-05 Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit
PCT/EP2014/059063 WO2014191157A2 (fr) 2013-05-31 2014-05-05 Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit

Publications (1)

Publication Number Publication Date
EP3004591A2 true EP3004591A2 (fr) 2016-04-13

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP13170064.3A Withdrawn EP2808500A1 (fr) 2013-05-31 2013-05-31 Pompe à chaleur dotée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluidique
EP14725971.7A Withdrawn EP3004591A2 (fr) 2013-05-31 2014-05-05 Pompe à chaleur équipée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluide montées en circuit

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP13170064.3A Withdrawn EP2808500A1 (fr) 2013-05-31 2013-05-31 Pompe à chaleur dotée d'une première machine thermique à énergie fluidique et d'une seconde machine thermique à énergie fluidique

Country Status (2)

Country Link
EP (2) EP2808500A1 (fr)
WO (1) WO2014191157A2 (fr)

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CN106368751B (zh) * 2016-08-31 2017-12-15 中电投宁夏能源铝业中卫热电有限公司 350mw超临界双抽机组给水泵汽轮机直排空冷岛的系统的背压干扰抑制方法
CN106246261B (zh) * 2016-08-31 2018-02-16 国家电投集团宁夏能源铝业中卫热电有限公司 350mw超临界双抽机组给水泵汽轮机直排空冷岛的系统及其工作方法
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