EP0000135A1 - Installation de production centralisée d'énergie thermique - Google Patents

Installation de production centralisée d'énergie thermique Download PDF

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Publication number
EP0000135A1
EP0000135A1 EP78100136A EP78100136A EP0000135A1 EP 0000135 A1 EP0000135 A1 EP 0000135A1 EP 78100136 A EP78100136 A EP 78100136A EP 78100136 A EP78100136 A EP 78100136A EP 0000135 A1 EP0000135 A1 EP 0000135A1
Authority
EP
European Patent Office
Prior art keywords
heat
turbine
compressor
transfer medium
steam
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Withdrawn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
EP78100136A
Other languages
German (de)
English (en)
Inventor
Karl-Heinz Schüller
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.)
BBC Brown Boveri AG Germany
Original Assignee
BBC Brown Boveri AG Germany
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 BBC Brown Boveri AG Germany filed Critical BBC Brown Boveri AG Germany
Publication of EP0000135A1 publication Critical patent/EP0000135A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • 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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the invention relates to a system for the central generation of thermal energy for the remote supply of consumers with at least one turbine, in particular a back pressure steam turbine, which is followed by at least one heat exchanger for delivering useful heat to at least one heat transfer medium.
  • the invention is based on the object of specifying a system for the central generation of useful thermal energy of the type mentioned, in particular a system for the remote supply of consumers, which has at least largely the thermodynamic advantages of the coupled generation of mechanical and thermal useful energy with simultaneous independence from the generation of electrical energy.
  • the structure of the system should be simple and fully meet the operational requirements.
  • the solution to this problem in "a system of the type mentioned in the present invention is that the turbine is designed to drive the compressor of a heat pump that raises the ambient heat to a higher temperature level and emits useful heat to the heat transfer medium.
  • thermoelectric The heat energy obtained from fossil and / or nuclear fuels and transferred to a working medium such as steam or propellant gas is converted into mechanical drive energy in the steam or gas turbine and used to drive the heat pump, whereby the ambient heat raised by the heat pump to a higher temperature level, and at least the waste heat of the turbine, is given off as useful heat to the heat transfer medium.
  • the system according to the invention gains importance because of its economy and its simple structure with regard to efforts to save energy and substitute high-quality fossil fuels.
  • a system according to the invention can of course also have several, possibly multi-stage compressors, and several heat pumps can also be provided.
  • the heat pump has an expansion turbine which is coupled to the compressor designed as a turbocompressor and which via at least one heat exchanger which emits the compression heat to the heat transfer medium to the pressure side of the compressor connected.
  • the heat pump can have a closed circuit for the working medium with at least one second heat exchanger, which is connected into the circuit between the expansion turbine and the compressor, for the supply of ambient heat.
  • a steam can be used as the working medium, e.g. Refrigerant and gas such as Serve carbonic acid or air.
  • the system can also be used to generate useful cooling.
  • a particularly recommendable further development can consist in the heat pump having an open circuit for the working medium, the compressor being used to draw in ambient air. is formed and the air outlet of the expansion turbine opens into the environment. Since the ambient heat is fed into the system with the ambient air drawn in, no heat exchanger is required for the supply of ambient heat and the construction effort is reduced.
  • the main advantage of the aforementioned design of the heat pump is, however, that high heat carrier temperatures in the range around 100 ° C can be reached with a good performance figure and the performance figure deteriorates only slightly with falling temperature of the ambient heat.
  • At least one third heat exchanger through which a coolant can flow can also advantageously be connected to the air outlet of the expansion turbine.
  • the system can be used in a simple manner to generate useful cold and / or useful heat.
  • the working medium of the heat pump 8 is supplied to the compressor 2 via an intake line 1.
  • this compressor which is designed as a turbocompressor
  • the gaseous working medium is increased pressure specified by the design of the system is compressed, whereby the working medium heats up.
  • This is then fed to the first heat exchanger 4 via a line 3.
  • the heat exchange between the working medium and the colder heat carrier introduced into the first heat exchanger 4 via the line 5 takes place via heat exchange surfaces.
  • heating water is provided as the heat transfer medium, which is supplied to the heat consumer (s) 10 via the heating water supply line 9 at a predetermined flow temperature.
  • the cooled heating water is fed via line 11 and pump 12 into the heating water return line 13.
  • a predetermined portion of the returning heating water can be regulated via a valve 14 or a regulating element and can be supplied to the first heat exchanger 4 via the line 5.
  • the working medium cooled in the first heat exchanger 4 is fed to the expansion turbine 7 via the line 6. Here it expands and cools down through the expansion process.
  • the cooled and relaxed working medium is introduced via line 40 into the second heat exchanger 41.
  • the working medium is supplied with ambient heat, for example through ambient air, which is supplied to the second heat exchanger 41 via a line 50.
  • the ambient air is conveyed by a fan, not shown.
  • the working medium loaded with ambient heat is discharged through the suction line 1, so that the circuit of the heat pump 8 is closed.
  • the power requirement for driving the compressor 2 is greater than the power released by the expansion of the air in the expansion turbine 7.
  • the still missing drive power for the compressor 2 is applied by the turbine 16, which in the exemplary embodiment according to FIG. 1 is designed as a tap-back pressure steam turbine.
  • the turbine 16 is mechanically connected to the compressor 2 via a shaft section 17.
  • the turbine 16 could, however, also be equipped with its own generator for generating electricity and the machine group consisting of the compressor 2 and the expansion turbine 7 could be driven by an electric motor which is fed by the generator.
  • the working steam of the turbine 16 is obtained in a steam generator 18 by using fossil or nuclear fuel.
  • the steam generator 18 is equipped with an overheating device 19 for overheating the working steam.
  • the working steam is supplied to the turbine 16 via the live steam line 20 and the turbine inlet valve 21.
  • the turbine 16 supplies the heat exchangers 22 and 23 with the required exhaust steam and / or tapped steam for heating a partial heat flow, which is removed from the heating water return line 13 and via the shut-off and control element 24 and the line 25 to the heat exchangers 22 and 23 is supplied.
  • the heating steam pressures at the steam extraction points 26, 27 of the turbine are chosen so that approximately the same heating margins of the heat transfer medium occur in the heat exchangers 22 and 23 and the required flow temperature is reached.
  • the heated partial flow of the heat transfer medium is then introduced into the common heating water supply line 9.
  • the extraction points 26 and 27 provided on the turbine 16 for the exhaust steam or bleed steam are connected to the heat exchangers 22 and 23 via lines 29 and 30.
  • the steam condensate from the heat exchanger 23 is introduced via line 31 into the steam space of the heat exchanger 22 which is at a lower vapor pressure and together with the condensate of the heat exchanger 22 via line 32, the condensate pump 33 and the line 34 into the degassing mixer preheater 35 headed. This is via a heating steam line 36 from a suitable heating steam extraction point, e.g. Tapping point 27, supplied with heating steam.
  • Another tapping point 28 is provided for supplying heating steam to a surface feed water preheater 37.
  • a surface feed water preheater 37 Analogously, several feed water heaters connected in series on the feed water side can also be used. Instead of the shown two-stage heating water heating can also be selected one-stage or heating water heating with still further stages. Contrary to the illustration, the working steam of the turbine can be reheated after part expansion, or the working steam can be completely overheated. The details of the circuit in the steam section of the proposed system can be modified according to the respective requirements.
  • the feed pump 38 conveys the feed water via the feed water preheater 37 and the line 39 into the steam generator 18, whereby the water-steam cycle of the system is closed.
  • a partial stream of the heat transfer medium is taken from the heating water return line 13 during operation of the system, heated in the heat exchangers 22 and 23 and 4 and fed to the heating water supply line 9.
  • the heat required for the heating is taken from the exhaust steam and / or bleed steam from the turbine 16 and the heat pump 8. Since the heat pump 8 is essentially driven by the turbine 16, it is thus possible with the present system to take advantage of the thermodynamic advantages of the coupled energy generation for the sole generation of thermal useful energy.
  • FIG. 2 shows an embodiment variant of the system according to FIG. 1.
  • the system according to FIG. 2 has an open circuit heat pump for the working medium.
  • the intake line 1 opens into the environment, and the compressor 1 thus draws in ambient air with ambient pressure and temperature.
  • the line 40 which is connected to the air outlet of the expansion turbine 7, opens into the environment.
  • a third heat exchanger 44 through which a coolant flows, is switched on in line 40.
  • the heated coolant coming from the cold consumers, for example air conditioning systems enters the third heat exchanger 44 via the line 42, is cooled here with the release of ambient heat and flows to the cold consumers via the line 45.
  • a pump 43 maintains the circulation.
  • the fluids already mentioned can be used as the coolant.
  • FIG. 3 finally shows an embodiment variant of the plant according to FIG. 2, the plant according to FIG. 3 having a gas turbine for generating the mechanical energy.
  • a gas turbine is used as the turbine 16, which is supplied with propellant gas as working medium via a line 46, which is generated in a combustion chamber 47.
  • the air required for the combustion of the fuel such as gas or oil, is compressed together with the secondary air required to maintain the specified design temperature of the working gas in a turbocompressor 48 and is fed to the combustion chamber 47 together with the fuel.
  • the turbocompressor 48 is coupled to the turbine 16 for driving, so that the compressor 2, expansion turbine 7, turbine 16 and turbocompressor 48 are connected to one another on the drive side.
  • the expanded propellant gas is supplied to the heat exchanger 49 which, like the heat exchangers 22, 23 in the exemplary embodiment according to FIG. 1 or 2, is acted upon by the heat transfer medium.
  • the main advantage of the systems according to the invention is, above all, the reduction in the use of primary energy in the supply of useful heat compared to known heating plants or compared to individual furnaces and in avoiding the disadvantages of known heating plants.
  • the required fuel heat that is to be supplied to the steam generator 18 is calculated from:
  • the ratio of the fuel utilization factors is a measure of the possible reduction in the primary energy use of a system according to the invention compared to a heating supply with known heating plants.
  • the average efficiency of the heat transfer to the heating water can be approximately at best can be expected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP78100136A 1977-06-15 1978-06-12 Installation de production centralisée d'énergie thermique Withdrawn EP0000135A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2726924 1977-06-15
DE19772726924 DE2726924A1 (de) 1977-06-15 1977-06-15 Anlage zur zentralen erzeugung von thermischer nutzenergie

Publications (1)

Publication Number Publication Date
EP0000135A1 true EP0000135A1 (fr) 1979-01-10

Family

ID=6011555

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78100136A Withdrawn EP0000135A1 (fr) 1977-06-15 1978-06-12 Installation de production centralisée d'énergie thermique

Country Status (3)

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EP (1) EP0000135A1 (fr)
DE (1) DE2726924A1 (fr)
DK (1) DK266878A (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0008680A2 (fr) * 1978-09-02 1980-03-19 Chemische Werke Hüls Ag Procédé de production d'énergie thermique en combinant une unité de puissance thermique avec une pompe à chaleur
FR2503335A1 (fr) * 1981-04-01 1982-10-08 Energiagazdalkodasi Intezet Installation pour utiliser la chaleur perdue de faible potentiel d'une station de compression pour pipelines de gaz
EP0093826A1 (fr) * 1982-05-07 1983-11-16 Shell Austria Aktiengesellschaft Installation pour la réalisation d'un processus de pompe à chaleur en vue de chauffage
EP0099501A2 (fr) * 1982-07-15 1984-02-01 BROWN, BOVERI & CIE Aktiengesellschaft Méthode pour changer la production d'énergie électrique d'une centrale de chauffe sans influencer la livraison de chaleur aux consommateurs de chaleur
FR2696506A1 (fr) * 1992-10-05 1994-04-08 Sprolant Van William Centrale combinée hydraulique et thermique pour production simultanée de l'électricité et d'énergie calorifique.
WO2006078215A1 (fr) * 2005-01-21 2006-07-27 Mecmaster Ab Installation pour la production d'eau chaude
EP2159247A1 (fr) 2008-08-27 2010-03-03 Shin-Etsu Chemical Co., Ltd. Compositions de résine de silicone polyimide sans solvants et produits durcis correspondants
CN106352579A (zh) * 2015-12-30 2017-01-25 李华玉 第一类热驱动压缩式热泵

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3018450C2 (de) * 1980-05-14 1985-10-03 Bergwerksverband Gmbh, 4300 Essen Verfahren zur Bereitstellung von Prozeßwärme für Hochtemperaturprozesse unter Verwendung einer Wärmepumpe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219815A (en) * 1939-01-18 1940-10-29 Carrier Corp Refrigerating and heating system
CH304499A (de) * 1952-04-10 1955-01-15 Melan Herbert Ing Dr Kombinierte Anlage zur Kraft- und Wärmeerzeugung.
US2721728A (en) * 1951-10-12 1955-10-25 Henry B Higgins Heat concentrator
FR2245920A1 (en) * 1973-09-27 1975-04-25 Cottin Armand Heating and refrigerating unit - air compressor and expansion turbine are driven by common power unit
DE2532850A1 (de) * 1975-07-23 1977-02-10 Bbc Brown Boveri & Cie Verfahren zur fernwaermeversorgung von verbrauchern
DE2545609A1 (de) * 1975-10-11 1977-04-21 Bbc York Kaelte Klima Verfahren zur wahlweisen erzeugung von nutzkaelte und/oder nutzwaerme
DE2553024A1 (de) * 1975-11-26 1977-06-02 Bbc Brown Boveri & Cie Nutzenergie-versorgungsanlage

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2219815A (en) * 1939-01-18 1940-10-29 Carrier Corp Refrigerating and heating system
US2721728A (en) * 1951-10-12 1955-10-25 Henry B Higgins Heat concentrator
CH304499A (de) * 1952-04-10 1955-01-15 Melan Herbert Ing Dr Kombinierte Anlage zur Kraft- und Wärmeerzeugung.
FR2245920A1 (en) * 1973-09-27 1975-04-25 Cottin Armand Heating and refrigerating unit - air compressor and expansion turbine are driven by common power unit
DE2532850A1 (de) * 1975-07-23 1977-02-10 Bbc Brown Boveri & Cie Verfahren zur fernwaermeversorgung von verbrauchern
DE2545609A1 (de) * 1975-10-11 1977-04-21 Bbc York Kaelte Klima Verfahren zur wahlweisen erzeugung von nutzkaelte und/oder nutzwaerme
DE2553024A1 (de) * 1975-11-26 1977-06-02 Bbc Brown Boveri & Cie Nutzenergie-versorgungsanlage

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0008680A2 (fr) * 1978-09-02 1980-03-19 Chemische Werke Hüls Ag Procédé de production d'énergie thermique en combinant une unité de puissance thermique avec une pompe à chaleur
EP0008680A3 (fr) * 1978-09-02 1980-04-02 Chemische Werke Hüls Ag Procédé de production d'énergie thermique en combinant une unité de puissance thermique avec une pompe à chaleur
FR2503335A1 (fr) * 1981-04-01 1982-10-08 Energiagazdalkodasi Intezet Installation pour utiliser la chaleur perdue de faible potentiel d'une station de compression pour pipelines de gaz
EP0093826A1 (fr) * 1982-05-07 1983-11-16 Shell Austria Aktiengesellschaft Installation pour la réalisation d'un processus de pompe à chaleur en vue de chauffage
EP0099501A2 (fr) * 1982-07-15 1984-02-01 BROWN, BOVERI & CIE Aktiengesellschaft Méthode pour changer la production d'énergie électrique d'une centrale de chauffe sans influencer la livraison de chaleur aux consommateurs de chaleur
EP0099501A3 (en) * 1982-07-15 1985-09-18 Brown, Boveri & Cie Aktiengesellschaft Method of changing the electric energy release of a heating power plant without influencing the heat release to the heat consumers
FR2696506A1 (fr) * 1992-10-05 1994-04-08 Sprolant Van William Centrale combinée hydraulique et thermique pour production simultanée de l'électricité et d'énergie calorifique.
WO2006078215A1 (fr) * 2005-01-21 2006-07-27 Mecmaster Ab Installation pour la production d'eau chaude
EP2159247A1 (fr) 2008-08-27 2010-03-03 Shin-Etsu Chemical Co., Ltd. Compositions de résine de silicone polyimide sans solvants et produits durcis correspondants
CN106352579A (zh) * 2015-12-30 2017-01-25 李华玉 第一类热驱动压缩式热泵
CN106352579B (zh) * 2015-12-30 2020-01-31 李华玉 第一类热驱动压缩式热泵

Also Published As

Publication number Publication date
DK266878A (da) 1978-12-16
DE2726924A1 (de) 1978-12-21

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