• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A condensing heat recovery steam generator (cHRSG) includes a main chimney for a main flow of hot exhaust gas, a bypass chimney to allow a fraction of the hot exhaust gas to bypass the main flow of gas hot exhaust, and a heat pump. The cHRSG comprises a main water circuit, a secondary water circuit, and a tertiary water circuit. The cHRSG further comprises a feed water pipe, a first heat exchanger for performing a heat exchange between the feed water pipe and the secondary water circuit, and a second heat exchanger for carrying out a heat exchange between the main water circuit and the tertiary water circuit. In cHRSG, the latent heat is partially recovered in the hot exhaust gas flowing in the bypass via the second heat exchanger and additional heat is extracted into the tertiary water circuit by said heat pump. heat, contributing to preheating in a preheater of the main water circuit.
    公开号:BE1025812B1
    申请号:E2016/5889
    申请日:2016-11-30
    公开日:2019-10-25
    发明作者:Nicolas Balczunas；Sébastien Borguet
    申请人:Cockerill Maintenance & Ingenierie S.A.；
    IPC主号:
    专利说明:

    STEAM GENERATOR WITH HEAT RECOVERY
    CONDENSATION
    FIELD
    The present invention relates to the field of boilers, and particularly boilers of the heat recovery steam generator (HRSG) type.
    CONTEXT
    It is known that heat recovery steam generators (HRSG) recover heat from a hot exhaust stream of a gas turbine to produce steam which can be used either in a process (cogeneration) , or in a steam cycle (combined cycle). The exhaust gases consist on the one hand of non-condensable, containing mainly N 2 , O 2 ,
    CO 2 and Ar, and on the one hand condensable consisting of water vapor. So far, in the prior art, the idea of condensation of fumes has been rejected, mainly because of corrosion problems.
    It follows that HRSGs as known in the prior art face two types of limitations in their thermal performance. In the case of HRSG providing a pressurized hot water flow for cogeneration applications, as illustrated in Figure 1 and Figure 2, a compromise exists between the amount of thermal power and the amount of electricity generated by the turbine steam (which is directly linked to the steam production of HRSG). This compromise is illustrated in FIG. 3 where the point “Prior art 1” relates to the arrangement of HRSG of FIG. 1 and the point “Prior art 2” relates to the arrangement of
    HRSG in Figure 2. On the other hand, the presence of sulfur compounds greatly elevates the acid dew point of exhaust gases. As a result, a large loop of
    2016/5889
    BE2016 / 5889 recirculation should be used to heat the feed water above this acid dew point. This leads to a fairly large approach, i.e. the difference between the temperature at the outlet of the preheater and the saturation temperature of the steam at low pressure, as shown in Figure 4.
    Some prior art documents are based on a secondary / bypass chimney where additional heat recovery is performed. In document WO 2015/039840 A2, the additional heat recovered is used to preheat the condensate of the steam cycle. In document WO 2010/136795 A2, the additional heat recovered is used to preheat the combustion air of the boiler. The two documents are however specifically directed towards boilers powered by air and fossil fuel (for example, coal, petroleum), and are not concerned with heat recovery steam generators included in a combined cycle . Both patents lead to improved cycle efficiency by reducing the amount of fuel required to produce a given amount of steam under prescribed conditions of temperature and pressure. Document CN101922821 A presents a method for simultaneously recovering water and latent heat in the high humidity combustion gas, and an absorption heat pump device, relating to the technique of energy saving equipment. This prior art solution is, however, supposed to provide acidic corrosion deposits.
    ABSTRACT
    The present invention provides a condensing heat recovery steam generator (cHRSG) which overcomes the two types of performance limitations of HRSG according to the prior art. Specifically, the cHRSG is arranged to
    2016/5889
    BE2016 / 5889 so as to be able to deal effectively and reliably with the condensation of water vapor as well as acid products (for example, H 2 SO 4 ).
    In one embodiment of the invention, the cHRSG comprises a main chimney for a main flow of hot exhaust gas, a bypass chimney to allow a fraction of the hot exhaust gas to bypass the main flow of hot gas exhaust, and a heat pump. The cHRSG comprises a main water circuit which includes a recirculation loop with a preheater located at the entrance to the main flow of hot exhaust gas into the main chimney, a secondary water circuit provided with an application thermal for an end user, and a tertiary water circuit which includes a spray tower to provide a continuous shower of water in counter-current with the fraction of the hot exhaust gas flowing in the bypass chimney, and an evaporator of the heat pump. The cHRSG additionally comprises a supply water line which receives, at a first end, a condensate, and which is physically connected, at a second end, to the main water circuit, and which is provided with a condenser. the heat pump, a first heat exchanger to carry out a heat exchange between the feed water pipe and the secondary water circuit, and a second heat exchanger to carry out a heat exchange between the main water circuit and the tertiary water circuit. In the cHRSG, preheating carried out in the preheater of the main water circuit benefits from the latent heat partially recovered in the tertiary water circuit from said hot exhaust gas circulating in the bypass chimney through the second heat exchanger heat, and from the additional heat extracted in the tertiary water circuit by
    2016/5889
    BE2016 / 5889 said heat pump, and this latent and additional heat is finally transported to the end user thermal application in the secondary water circuit through the first heat exchanger. The main water circuit, the secondary water circuit and the tertiary water circuit are in thermal contact via the first heat exchanger and the second heat exchanger, but are not fluidly interconnected.
    BRIEF DESCRIPTION OF THE DRAWINGS
    The present invention will be described in more detail below on the basis of the examples given in the drawings. The invention is not limited to the examples of embodiments. All the features described and / or illustrated in this document can be used alone or combined in different combinations in embodiments of the invention. The characteristics and advantages of the various embodiments of the present invention will become apparent on reading the detailed description which follows with reference to the accompanying drawings which illustrate the following:
    Figure 1, already mentioned, schematically shows a first arrangement of HRSG for cogeneration according to the prior art.
    Figure 2, already mentioned, schematically represents a second arrangement of HRSG for cogeneration according to the prior art.
    FIG. 3, already mentioned, is a diagram of the thermal production compared to that of the electricity of an HRSG used for cogeneration which compares the solutions of the prior art with the invention.
    Figure 4, already mentioned, is a theoretical graph of the temperature as a function of the heat exchanged for a
    2016/5889
    BE2016 / 5889 steam generator with single pressure level according to the prior art.
    FIG. 5 schematically represents the general principle of a condensing HRSG according to the invention.
    Figure 6 shows schematically the principle of a
    HRSG condensing according to a first embodiment of the present invention.
    Figure 7 shows schematically the principle of a
    HRSG condensing according to a second embodiment of the present invention.
    Figure 8 schematically shows the principle of a
    Condensing HRSG according to a third embodiment of the present invention.
    Figure 9 shows schematically the principle of a
    Condensing HRSG according to a fourth embodiment of the present invention.
    DETAILED DESCRIPTION
    The present invention relates to the improvement of the thermal performance of HRSGs in the two cases of cogeneration - that is to say "heat" (including cooling) and power combined, as well as power generation only. Consequently, the heat recovered in a bypass chimney for the main flow of hot gas, at the level of a cold end of an HRSG, namely by condensing part of the water vapor contained in the fumes, is transferred to the steam cycle feed water so that it is raised to a temperature above the smoke dew point at the preheater inlet. According to the prior art, this cycle is managed by a recirculation loop.
    The cHRSG according to the invention overcomes the above-mentioned limitations by making the heat transported by the recirculation loop available for other purposes. In the
    2016/5889
    BE2016 / 5889 in the case of cogeneration, cHRSG makes it possible to increase the production of both electricity and heat to a maximum for a flow at enthalpy given at the hot end of the HRSG.
    As shown in FIG. 3, if the electrical consumption of the auxiliary components of cHRSG is neglected, the electrical power of cHRSG corresponds to that of the prior art 2 while at the same time producing a thermal power equal to that of the prior art 1. Including the power consumption of the auxiliary components will slightly reduce the net electric power from the steam cycle, thereby shifting the representative point slightly to the left of the map.
    In the case of problems related to the acid dew point, the present invention makes it possible either to considerably reduce the size of the recirculation loop, or even to remove it. The generation of steam (and thus the electrical production of the steam turbine) can therefore be increased.
    The water vapor present in the combustion products of the gas turbine carries a fairly large amount of energy which is currently released into the atmosphere, but which could in principle be partially recovered by condensing the humidity contained in the gases. exhaust. This additional heat recovery would imply an exchange of latent heat, i.e. heat which is not transferred via a temperature change, but through a phase change of the gaseous medium, in this case the condensation of the water vapor contained in the exhaust gases.
    Figure 5 schematically shows the general arrangement for an HRSG according to the present invention, where attention is paid to the cold side of the HRSG. Therefore, the HRSG is supplemented by a "zone of
    2016/5889
    BE2016 / 5889 condensation ”21, outside the main casing of the HRSG and equipped with additional equipment intended for the recovery of latent heat in the exhaust gases of the HRSG, and for the efficient management of the flow resulting from effluent 8. A “condensing HRSG” is proposed in this document which implements the additional recovery of latent heat in the exhaust gases by the condensation of these. An HRSG which improves the cost compared to the power output is also proposed in this document.
    In one embodiment of the invention, the fraction of exhaust gas flow through the condensation zone is controlled by means of a fan.
    According to one embodiment of the invention, the latent heat is recovered by means of a so-called direct contact heat exchanger. Direct contact heat exchangers may include, but are not limited to, a spray tower, a baffle tray column, and a packed column.
    In some embodiments of the invention, a spray tower is selected as a direct contact heat exchanger because it offers a good overall heat transfer coefficient, generates a moderate pressure loss on the gas side , and is relatively inexpensive. The spray tower can be seen as a sprinkler system located in the bypass chimney of the HRSG providing a shower where cold water is sprayed in a counter-current arrangement through a fraction of the exhaust gas flow which will be cooled. The fumes are then saturated with humidity, and this humidity will condense and release the vaporization energy of the fumes. The mixture of saturated fumes escaping from the bypass chimney with the fumes from the main chimney reduces the risk of the formation of a white plume / cloud.
    2016/5889
    BE2016 / 5889
    In other alternative embodiments of the invention, alternative direct contact heat exchangers are used instead of the spray tower.
    FIG. 6 schematically represents an embodiment of a condensing HRSG according to the present invention. A horizontally arranged HRSG is composed of a main chimney 1 for the hot gas flow as well as a bypass chimney 2 to allow a fraction of the exhaust gas flow to bypass the main flow. In this particular embodiment, the condensing HRSG is based on a direct contact heat exchanger.
    Three closed water circuits are provided which are physically separated (i.e. which are not fluidly interconnected), but thermally in contact via heat exchangers (described in more detail below) . The main water circuit (PWC) is a recirculation loop 10 which includes the first heat exchanger of the HRSG (or preheater / economizer 6), the latter being essentially located at the entrance of the hot gases into the main chimney . The PWC is physically connected to the feed water pipe 13, and is provided with the LP drum 19. The feed water pipe 13 is connected at the feed water inlet 7, and is provided with a heat pump condenser 17 (HPC) (described in more detail below).
    The tertiary water circuit (TWC) is a recirculation loop 11 which includes a spray tower 3 to provide a shower flow of water in counter-current with the rising exhaust fumes. The spray tower 3 is provided at its lower end with a water basin 5 and a heat pump evaporator 16 (HPE) (described in more detail below).
    2016/5889
    BE2016 / 5889
    The tertiary water circuit (TWC) comprises a recirculation loop 12 and an end-user thermal application 9. The feed water pipe 13 / the PWC 10 and the TWC 11 are in thermal contact via of the second heat exchanger 14, while the PWC 10 and the SWC 12 are in thermal contact via the first heat exchanger 15.
    The main, secondary and tertiary water circuits and the supply water line are advantageously provided with a first pump, a second pump, a third pump and a fourth pump respectively. (not shown). These pumps guarantee an appropriate pressure level in the corresponding circuits, and compensate for the additional pressure losses induced by the additional equipment introduced according to the invention.
    In the HRSGs of the prior art, the heating of the feed water is generally obtained by means of a recirculation loop placed on a preheater which mixes the incoming external cold flow of condensate, preferably in the range of 20 ° C to 50 ° C, with a hot flow of pressurized water heated in the loop, preferably in the range of 160 ° C to 190 ° C, to produce the required temperature level at the inlet of the HRSG , preferably in the range of 55 ° C to 80 ° C. The embodiment of the invention shown in FIG. 6 uses the latent heat recovered described above to help carry out this heating of condensate flow, and in addition to use / exchange the heat transported in the recirculation loop 10 to a number of thermal applications 9 possible.
    However, in the embodiment shown in Figure 6, the latent heat can be recovered at a relatively low temperature. Water temperature
    2016/5889
    BE2016 / 5889 in tank 5 of the spray tower 3 can be equal to the dew point of the exhaust gases at this location, i.e. in the range of 40 ° C to 50 ° C for the conditions ambient types and for the combustion of natural gas. Consequently, only part of this low energy heat can be passively transferred to the condensate flow by means of a heat exchanger, such as the heat exchanger 14, which is generally a plate exchanger.
    In the various embodiments of the invention, plate heat exchangers are used in order to take advantage of their high heat transfer coefficient, their narrow pinching, and their limited volume.
    Additional heating of the condensate stream to its required temperature involves moving thermal energy from a hot spot to a warmer spot, which does not happen naturally due to the second law of thermodynamics. Consequently, according to an embodiment of the invention, an industrial heat pump 18 is used to effect this heat transfer. The heat source, where heat is captured by the evaporator 16 of the heat pump (HPE), is the flow of water through the spray tower, while the heat sink, where heat is released from the condenser 17 of the heat pump (HPC), is the condensate flow. The device providing the electrical power necessary for the operation of the heat pump is not shown in the figures. As a variant, the industrial heat pump can be replaced by any system known in the art in order to recover the energy from the sprinkler recirculation flow, and thus to decrease the shower inlet temperature.
    The heat transported in the recirculation loop 10 (PWC) can then be used for other purposes,
    2016/5889
    BE2016 / 5889 particularly for various applications 9 requiring thermal energy at a low to moderate temperature. In order not to mix the water flows of different qualities, i.e. water passing through the HRSG and water used in said thermal applications 9, the heat is transferred to an auxiliary circuit 12 ( SWC) by means of the first heat exchanger 15, which can also be, for example, a plate heat exchanger.
    The flow of hot water generated by the invention could be used, for example, for an application of the following non-exhaustive list of thermal applications for end users: direct use of the flow of hot water to supply a network of district heating, use of the hot water flow in refrigeration machines (absorption and adsorption chillers are 3-source thermal machines that produce chilled water from hot water or steam), and use of chilled water to supply a district cooling network, use of the flow of hot water to produce fresh water from sea water (desalination of water) by a thermal process, such as, for example, multiple effect distillation (MED).
    In other embodiments of the invention, two or even the three above applications can be combined to achieve a so-called trigeneration or even a polygeneration (electricity, heat, cold and fresh water).
    In still other modes of production of the invention , load thermal of the loop of recirculation may be used to increase the production of steam from HRSG and so the generation of
    power of the steam turbine.
    In operation in the permanent state, an effluent stream 8, generated by the partial condensation of the fumes, must be released into the environment in order to
    2016/5889
    BE2016 / 5889 maintain a constant level in the water basin of the spray tower.
    Close contact of the water spray with the fumes makes the water spray acidic. The CO 2 contained in the fumes can dissolve in water. According to one embodiment, a WTU water treatment unit (not shown) can be used to increase the pH of this acidified water in a pH range from 6.0 to 8.0 before releasing the effluent 8 in the environment. One possible treatment is based on alkaline products such as calcium carbonate to neutralize the acidification of the water.
    FIG. 7 schematically represents yet another embodiment of a condensing HRSG according to the present invention. It differs from the embodiment shown in FIG. 6 by the absence of a heat pump. This embodiment may be suitable for cases where the concentration of water vapor in the flue gases is higher (for example, an HRSG behind a wet gas turbine cycle).
    FIG. 8 schematically represents yet another embodiment of a condensing HRSG according to the present invention. The partial recovery of the latent heat contained inside the fraction of exhaust gas circulating in the bypass chimney 2 is carried out by indirect contact means comprising a section of the feed water pipe 13 which is provided with an indirect contact heat exchanger 20 located inside the exhaust gas fraction flowing in the bypass chimney 2, so that, due to the condensation of the exhaust gas on a surface from the indirect contact heat exchanger 20, the latent heat contained in the exhaust gas is transferred as above to the main water circuit 10.
    2016/5889
    BE2016 / 5889
    The partial condensation of the exhaust gases on the external surface of the exchange zone of the indirect contact heat exchanger also generates a flow of excess effluent 8 which must be released into the environment after an appropriate treatment as examined. above.
    FIG. 9 schematically represents yet another embodiment of a condensing HRSG according to the invention. Compared to the embodiment shown in Figure 8, the condensing heat recovery steam generator further includes a heat pump. The section of the water supply pipe 13 provided with an indirect contact heat exchanger 20 situated inside the fraction of exhaust gas circulating in the bypass chimney 2 comprises an evaporator 16 of the heat 18 and a recirculation part of the water supply line 13 comprises a condenser 17 of the heat pump 18, so that additional heat is extracted in said section of the water supply line 13 which is provided with an indirect contact heat exchanger 20, and transferred to the main water circuit 10 by said heat pump 18. The energy transfer capacity is thereby improved because the temperature of the condensate entering the indirect contact heat exchanger is weaker.
    The principles set out in the present application are not limited to the exemplary embodiments presented in this document. In particular, the system can be implemented continuously or intermittently according to the energy demand, the system can be adapted to both vertical and horizontal HRSG.
    In addition, an embodiment of the invention provides additional equipment to an existing or prior art HRSG (non-condensing) and can integrate, in the
    2016/5889
    BE2016 / 5889 limits of a given range, the following characteristics: a prescribed steam production, in terms of pressures, temperatures and mass flow rates (the temperature, pressure and mass flow rate of water to a drum at low pressure (LP) can be unchanged compared to a reference HRSG), a minimum value requested for the supply water temperature at the inlet of the HRSG in order to avoid condensation on the first heat exchanger at finned tube (the supply water temperature at the inlet of the HRSG can be unchanged compared to a reference HRSG), and a maximum allowable level of pressure loss on the exhaust side to guarantee operation correct gas turbine upstream.
    In additional embodiments, the treated effluent stream 8 can be advantageously used as feed at various points in a combined cycle, for example make-up water for the steam cycle, make-up water for the cooling system, or water injection where it is most appropriate in the gas turbine cycle for existing operating conditions. This latter use is believed to increase the water vapor content of the exhaust gases from the gas turbine. This would result in a "snowball effect" with additional condensation of the exhaust gases and additional latent heat recovery.
    Although the invention has been illustrated and described in detail in the drawings and in the description above, these illustrations and description should be considered as illustrative or exemplary and not limiting. It will be understood that changes and modifications can be made by those skilled in the art within the scope of the appended claims. In particular, the present invention covers additional embodiments
    2016/5889
    BE2016 / 5889 with any combination of features from different embodiments described above and below.
    The terms used in the claims should be interpreted as having the broadest reasonable interpretation consistent with the foregoing description. For example, the use of the article "a" or "the" to introduce an element should not be interpreted as being exclusive of a plurality of elements. Likewise, the use of "or" should be interpreted as inclusive, for example the use of "A or B" is not exclusive of "A and B", unless it is obvious from the context or description above that only one of A and B is wanted. Furthermore, the use of "at least one of A, B and C" should be interpreted as one or more of a group of elements consisting of A, B and C, and should not be interpreted as requiring at least one of each of the elements A, B and C listed, regardless of whether A, B and C are linked as categories or otherwise. In addition, the use of "A, B and / or C" or "at least one of A, B or C" should be interpreted to include any singular entity of the listed elements, for example, A , any subset of the items listed, for example, A and B, or the entire list of items A, B and C.
    2016/5889
    BE2016 / 5889
    REFERENCE SYMBOLS
    HRSG
    Chimney to divert a fraction of the exhaust gas flow
    Spray tower
    Fan
    Water basin
    Preheater / economizer
    Supply water inlet (condensate from the steam cycle)
    Exit of liquid effluent to the environment or useful applications
    9 Thermal application of user final 10 Main water circuit (loop of recirculation preheater) or PWC 11 Tertiary water circuit (loop of recirculation turn spray) or TWC 12 Secondary water circuit (loop of recirculation thermal application) or SWC
    Supply water line (low temperature condensate)
    Second heat exchanger (between the supply water line and the tertiary water circuit)
    First heat exchanger (between main and secondary water circuits)
    16 Pump evaporator heat (HPE) 17 Pump condenser heat (HPC) 18 Heat pump 19 LP drum 20 Heat exchanger to contact indirect 21 Condensation area 22 Heat exchanger for cogeneration
    2016/5889
    权利要求:
    Claims (14)
    [1]
    1. Condensed heat recovery steam generator (cHRSG) comprising:
    - a main chimney (1) for a main flow of hot exhaust gas;
    - a bypass chimney (2) to allow a fraction of the hot exhaust gas to bypass the main flow of hot exhaust gas and to circulate in the bypass chimney (2);
    a main water circuit (10) comprising a recirculation loop with a preheater (6), the latter being located at the entrance to the main flow of hot exhaust gas into the main chimney (1), and a secondary water circuit (12) provided with final thermal application (s) (9);
    - a first heat exchanger (15) to carry out a heat exchange between the main water circuit (10) and the secondary water circuit (12), so that the main water circuit and the circuit secondary water are in thermal contact via the first heat exchanger (15), but are not fluidly interconnected;
    - a supply water pipe (13) which receives, at a first end, a condensate, and physically connected at a second end to the main water circuit (10);
    - Means for at least partially recovering the latent heat contained inside the fraction of exhaust gas circulating in the bypass chimney (2) and for transferring said latent heat to the main water circuit (10);
    wherein the means for at least partially recovering the latent heat contained inside the fraction of hot exhaust gas circulating in the
    2016/5889
    18 BE2016 / 5889 bypass chimney (2) and for transferring said latent heat to the main water circuit (10) comprise a condensation zone (21) and are arranged so as to firstly contribute to a preheating of water carried out in the preheater (6) of the main water circuit (10), and secondly transfer heat to the end user thermal application (9) in the secondary water circuit (12) via the first heat exchanger (15).
    [2]
    2. A condensing heat recovery steam generator according to claim 1, wherein acidic condensation specifically occurs in the condensation zone (21).
    [3]
    3. condensing heat recovery steam generator according to claim 1 or 2, wherein the means for at least partially recovering the latent heat contained inside the fraction of exhaust gas circulating in the bypass chimney ( 2) and for transferring said latent heat to the main water circuit (10) are direct contact means comprising a tertiary water circuit (11), comprising a spray tower (3) provided at a lower end a water basin (5) for delivering a shower stream of water exchanging heat directly and in counter-current with the fraction of the hot exhaust gas circulating in the bypass chimney (2), and a second heat exchanger (14) for performing heat exchange between the tertiary water circuit (11) and the supply water line (13), and further the main water circuit (10).
    [4]
    4. A condensing heat recovery steam generator according to claim 3, further comprising a heat pump (18), in which the tertiary water circuit (11) comprises an evaporator (16) of the heat pump.
    2016/5889
    BE2016 / 5889 heat (18) and the supply water line (13) includes a condenser (17) of the heat pump (18), so that additional heat is extracted in the tertiary water circuit (11) and transferred to the main water circuit (10) by said heat pump (18).
    [5]
    5. Steam generator with condensation heat recovery according to claim 1 or 2, wherein the means for at least partially recovering the latent heat contained inside the fraction of exhaust gas circulating in the bypass chimney ( 2) and for transferring said latent heat to the main water circuit (10) are indirect contact means comprising a section of the feed water pipe (13) which is provided with an indirect contact heat exchanger (20) located inside the fraction of exhaust gas flowing in the bypass chimney (2), so that, thanks to the condensation of the exhaust gas on a surface of the contact heat exchanger indirect (20), the latent heat contained in the exhaust gas is transferred to the main water circuit (10).
    [6]
    6. A condensing heat recovery steam generator according to claim 5, further comprising a heat pump (18), wherein said section of the feed water line (13) which is provided with an exchanger indirect contact heat (20) located inside the fraction of exhaust gas flowing in the bypass chimney (2) comprises an evaporator (16) of the heat pump (18) and a recirculation part of the feed water line (13) comprises a condenser (17) of the heat pump (18), so that additional heat is extracted in said section of the feed water line (13) which is provided with an indirect contact heat exchanger
    2016/5889
    BE2016 / 5889 (20) and transferred to the main water circuit (10) by said heat pump (18).
    [7]
    7. Steam generator with condensation heat recovery according to claims 1 or 2, in which the final thermal application (9) is configured to directly use a flow of hot water in the secondary water circuit (12) for supply a district heating network.
    [8]
    8. Condensed heat recovery steam generator according to claim 1 or 2, wherein the final thermal application (9) is configured to use a flow of hot water in the secondary water circuit (12) in cold generators to produce chilled water to supply a district cooling network.
    [9]
    9. A condensing heat recovery steam generator according to claim 1 or 2, wherein the final thermal application (9) is configured to use a flow of hot water in the secondary water circuit (12) to effect water desalination.
    [10]
    10. Steam generator with condensation heat recovery according to claim 1 or 2, in which at least two different final thermal applications (9) are combined so as to produce a polygeneration of energy.
    [11]
    11. Steam generator with condensation heat recovery according to claim 1 or 2, wherein the final thermal application (9) is replaced or supplemented by means for additional steam production.
    [12]
    12. A condensing heat recovery steam generator according to claim 11, in which the final thermal application (9) is combined with means for producing additional steam, so that a
    2016/5889
    BE2016 / 5889 specific separation between the latter can be decided according to needs.
    [13]
    13. Condensed heat recovery steam generator according to claim 1 or 2, in which it
    5 comprises means for releasing an effluent stream (8) generated by a partial condensation of the hot exhaust gas towards the environment or towards any potential use.
    [14]
    14. Steam generator with heat recovery at
    10 condensing according to claim 13, wherein it comprises means for injecting the effluent stream (8) where it is most suitable in a gas turbine cycle, so as to increase the humidity level of the gas exhaust generated by the gas turbine.
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    同族专利:
    公开号 | 公开日
    EP3394402A1|2018-10-31|
    RU2018124841A|2020-01-23|
    CN106895383A|2017-06-27|
    KR20180095808A|2018-08-28|
    EP3394402B1|2019-10-09|
    CN106895383B|2019-11-12|
    PL3394402T3|2020-05-18|
    RU2715437C2|2020-02-28|
    RU2018124841A3|2020-01-23|
    WO2017108355A1|2017-06-29|
    BE1025812A1|2019-07-15|
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    法律状态:
    2019-11-27| FG| Patent granted|Effective date: 20191025 |
    优先权:
    申请号 | 申请日 | 专利标题
    US14975920|2015-12-21|
    US14/975,920|US10221726B2|2015-12-21|2015-12-21|Condensing heat recovery steam generator|
    EP14975920|2015-12-21|
    EP15201518.6A|EP3184757A1|2015-12-21|2015-12-21|Condensing heat recovery steam generator|
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