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    • 专利摘要:
    In a steam power plant (1) with a working fluid circuit (2) for a working fluid, the working fluid circuit (2) - viewed in the direction of flow of the working fluid - a first heat exchanger system (3) for vaporizing the working fluid, a steam turbine system (4), a second heat exchanger system ( 5) for condensing the working fluid and a working medium pumping system (6), it is proposed that at least one refrigerant circuit (7) of an absorption heat pump (8) at least partially comprise the first heat exchanger system (3) and at least partially the second heat exchanger system (5) Absorption heat pump (8) for the introduction of heat energy from the second heat exchanger system (5) to the first heat exchanger system (3) is formed, and that an expulsion line (9) from a turbine tap (11) of the steam turbine system (4) via an expeller system (12) of the Absorption heat pump (8) to a feed (13) in the Arbeitsmittelkreisl to (2), wherein the working fluid in the exhaust duct (9) provides heat energy for an expulsion process of the absorption heat pump (8).
    公开号:AT517535A1
    申请号:T419/2015
    申请日:2015-06-30
    公开日:2017-02-15
    发明作者:
    申请人:Rudolf Dipl Ing (Fh) Gutscher；
    IPC主号:
    专利说明:

    The invention relates to a steam power plant according to the preamble of claim 1.
    There are known steam power plants, in which the exhaust steam from steam turbines or steam engines is liquefied in a condenser system before it can be pumped back to the heat generator, such as reactor, steam boiler or CCGT plant.
    The disadvantage of this is that the heat of condensation is lost as heat loss.
    The object of the invention is therefore to provide a steam power plant of the type mentioned, with which the mentioned disadvantages can be avoided, and which has a high efficiency.
    This is achieved by the features of claim 1 according to the invention.
    As a result, the efficiency of the steam power plant can be increased and thus emissions of the steam power plant can be avoided. Furthermore, conventional cooling systems such as, for example, hydro-flow cooling, dry cooling systems, air coolers, or cooling towers may be replaced or partially replaced, depending on the scope of the invention. By the absorption heat pump, the heat of condensation can be at least partially recovered. In this case, the energy demand of the absorption heat pump additionally caused by the expulsion system of the absorption heat pump can be provided by the working medium itself. Turbine tapping utilizes steam for the expeller system, which has already been able to deliver some of its available energy in the steam turbine system, thus reducing only slightly the power available for power generation. As a result, the additional energy required for the absorption heat pump remains lower than the heat of condensation recovered and usable by the absorption heat pump. As a result, an overall system can be provided, which overall has an increased efficiency and is easily realizable. With the present invention, it is also possible to realize the normal operation of such a system designed meaningful.
    Furthermore, the invention relates to a method for operating a steam power plant according to claim 13.
    The object of the invention is therefore further to provide a method of the type mentioned, with which the mentioned disadvantages can be avoided, and which has a high efficiency.
    This is achieved by the features of claim 13 according to the invention.
    The advantages of the process in this case correspond to the advantages of the steam power plant.
    The subclaims relate to further advantageous embodiments of the invention.
    It is hereby expressly referred to the wording of the claims, whereby the claims at this point are incorporated by reference into the description and are considered to be reproduced verbatim.
    The invention will be described in more detail with reference to the accompanying drawings, in which only preferred embodiments are shown by way of example. Showing:
    Fig. 1 is a conventional steam power plant as a schematic representation;
    Fig. 2 is an absorption heat pump as a schematic representation;
    3 shows a first preferred embodiment of a steam power plant as a schematic representation;
    4 shows a second preferred embodiment of a steam power plant as a schematic representation;
    5 shows a third preferred embodiment of a steam power plant as a schematic representation; and
    Fig. 6 shows a fourth preferred embodiment of a steam power plant as a schematic representation.
    3 to 6 show preferred embodiments of a steam power plant 1 with a working fluid circuit 2 for a working fluid, wherein the working fluid circuit 2 - viewed in the direction of flow of the working fluid - a first heat exchanger system 3 for evaporation of the working fluid, a steam turbine system 4, a second heat exchanger system 5 for condensing of the working fluid and a working fluid pumping system 6. The first heat exchanger system 3 is provided to supply the working fluid with heat energy until it at least evaporates. Conversely, the second heat exchanger system 5 is provided to cool the working fluid until it condenses at least. As a working medium, water can be used with particular preference.
    It is provided that at least one refrigerant circuit 7 of an absorption heat pump 8 at least partially the first heat exchanger system 3 and at least partially the second heat exchanger system 5, wherein the absorption heat pump 8 is designed to transfer heat energy from the second heat exchanger system 5 to the first heat exchanger system 3, and that Exhaust line 9 from a turbine tap 11 of the steam turbine system 4 via an expeller system 12 of the absorption heat pump 8 leads to a feed 13 in the working fluid circuit 2, wherein the working fluid in the Austreibungsleitung 9 provides heat energy for a Austreibungsprozess the absorption heat pump 8.
    Furthermore, a method for operating a steam power plant 1 is provided in the control mode, wherein in a working fluid circuit 2, a working fluid is evaporated in a first heat exchanger system 3 and fed to a steam turbine system 4, wherein the working fluid is condensed after the steam turbine system 4 in a second heat exchanger system 5 and via
    Arbeitsmittelpumpsystem 6 is again supplied to the first heat exchanger system 3, characterized in that by means of at least one refrigerant circuit 7 of an absorption heat pump 8 heat energy is spent by the second heat exchanger system 5 to the first heat exchanger system 3 that at a turbine tap 11, a part of the working fluid from the steam turbine system 4 in an expulsion line 9 branched off, in one
    Exducer system 12 of the absorption heat pump 8 is liquefied and recycled at a feed 13 back into the working fluid circuit 2, which is provided by this part of the working fluid heat energy for a Austreibungsprozess the absorption heat pump 8.
    Thermodynamic cycles are known as both left-handed and right-handed processes. Right-handed processes are mainly used for the operation of power and work machines in thermal power plants such as power plants, left-handed processes for heat pump or chiller processes used. With regard to this indication of direction, the processes designated as left-handed or right-handed running refer to the usual thermodynamic direction indication and not to the flow direction of the respective working medium.
    The combination of thermodynamically anti-clockwise Absorbtionswärmepumpenprozesse in the refrigerant circuit 7 proves to be advantageous with a thermodynamically clockwise Clausius Rankine cycle in the working fluid circuit 2. Namely such that the heat loss of the working fluid circuit 2 in the second heat exchanger system 5, which was previously discharged by means of cooling media, now for evaporation a suitable refrigerant and thus can be used to operate a left-handed cyclic process, from the clockwise cycle, which is based on the operation of power or work machines as the basis, at a suitable location, namely the second heat exchanger system 5 is removed. Thereafter, the extracted heat loss is again at another appropriate point of the same thermodynamic clockwise cycle from which this heat comes, with additional increase in the energy content of Absorptionswärmepumpenkreisprozesses, recycled in the clockwise cycle, namely the first heat exchanger system 3, whereby the efficiency of the resulting new combined , At the same time, coupled with separate streams, the two applied to the circle processes, operated overall process is increased.
    As a result, the efficiency of the steam power plant 1 can be increased and thus emissions of the steam power plant 1 can be avoided. Furthermore, conventional cooling systems such as, for example, hydro-flow cooling, dry cooling systems, air coolers or cooling towers, depending on the scope of the invention, can be partially or completely avoided or replaced. By the absorption heat pump 8, the heat of condensation can be recovered at least in part. In this case, the additional energy demand of the absorption heat pump 8 caused by the expulsion system of the absorption heat pump 8 can be provided by the working medium from the working medium circuit 2 itself. Through the turbine tap 11, a steam is used for the expeller system 12, which could already deliver some of its available energy in the steam turbine system 4, whereby the power available for power generation is only slightly reduced. As a result, the additional energy required for the absorption heat pump 8 remains lower than the heat of condensation recovered and usable by the absorption heat pump. As a result, an overall system can be provided, which overall has an increased efficiency and is easily realizable. With the present invention, it is also possible to realize the normal operation of such a system designed meaningful.
    Dotted lines illustrate in Figs. 1 to 6 each type of vaporous working fluid, in particular water vapor, and its piping and transport systems. Dotted lines illustrate in the following representations each type of condensed working fluid from the working fluid circuit 2 and its piping and transport systems. Short dashed dotted lines illustrate in the following illustrations each type of vapor refrigerant and its piping and transport systems. Long dashed dotted lines illustrate in the following illustrations each type of condensed refrigerant and its piping and transport systems. Dotted lines illustrated in the following representations illustrate each type of cooling water and its piping and transport systems. Doppelkurzgestrichelt illustrated lines illustrate in the following representations each type of a highly enriched solutions with refrigerant and refrigerant solvent and its piping and transport systems, so-called strong solutions. Short dashed lines, illustrate in the following
    Representations of any kind weakly enriched solutions or only the solvent of a refrigerant solution and its piping and transport systems, so-called poor solutions. Black arrows indicate the flow direction of a system medium in its associated system.
    In Fig. 1 to 6 known details of steam power plants such as feed water tank, feedwater and the like are not shown for clarity, but can be used if necessary.
    1 shows, in a form shown as a process diagram, a simplified conventional working fluid circuit 2, which can be operated as a clockwise running thermodynamic Rankine Rankine cycle and how he knows known thermally operated plants such as thermal power plants, CHP cogeneration plants, so-called gas turbine and steam turbine power plants, as a simplified basic process is based. Beyond that, for example, efficiency-enhancing auxiliary equipment such as feedwater, reheater, but also system-relevant units such as feed water tanks and so on, are not shown due to the awareness in the following descriptions for Fig.1 to Fig.6, since this is the clarity of the description of the invention would restrict too much.
    In Fig. 1, the Arbeitsmittelpumpsystem 6 promotes the condensate of water vapor, which preferably serves as a heat transfer and working fluid of the present clockwise thermodynamic Rankine Rankine cycle, with pressure increase, this to the first heat exchanger system 3, and makes it available as so-called feed water. In FIG. 1, the first heat exchanger 3 comprises only one steam generator system 14.
    A heating energy supply system 24 provides in Fig. 1 the required heat energy for generating the water vapor in the steam generator system 14. The heating energy supply system 24 stands for any type of fuel or Heizenergiezufuhrsystem, for the purpose of generating and supplying heating heat for a steam generator system 14 heated therewith also waste heat from gas turbine exhaust gas are used and thus this is understood as well. The heating energy supply system 24 thus stands for any form of heat supply system for the production of vaporous working fluid. In the steam generator system 14, the condensate, also called feed water before the steam generator system 14, is vaporized and steam with a higher pressure and temperature than in the second heat exchanger system 5, which comprises only one cooling water condensation unit 20 in FIG.
    Through a live steam line 25, the generated steam finally flows to the steam turbine system 4. The steam turbine system 4 stands for any type of steam turbine system or steam powered engine system for the purpose of converting thermal, kinetic and potential energy into mechanical energy. With the steam turbine system 4, a part of the energy of the generated water vapor is converted into mechanical energy and transmitted to a work machine system or a generator system 26 which is coupled to the steam turbine system 4 and whereby this transferred energy portion is largely made technically usable. The generator system 26 refers to any type of generator system, or other work machine system, coupled to an engine system for the purpose of generating electrical energy or performing mechanical work.
    After the steam turbine system 4, steam of lower temperature and lower pressure than before the steam turbine system 4 flows out of it into the second heat exchanger system 5 to condense. In the second heat exchanger system 5, the water vapor is finally condensed, whereby the state of aggregation of the steam is converted from vapor to liquid.
    This condensation takes place in Fig. 1 in a conventional steam power plant 1 using cooling water or other cooling media such as air. The cooling medium flows through a cooling water supply line 10 in the second heat exchanger system 5, then takes in the second heat exchanger system 5 largely the heat of vaporization or condensation heat of the water vapor, whereby the steam introduced his
    State of aggregation changed from vapor to liquid. The heat absorbed which is now in the cooling medium is decoupled from the process by a cooling water return line 22 and often discarded. The return of this heat loss is so far in the vast majority of systems not the case, since the heat is present in a no longer technically useful form in terms of their thermodynamic state variables. This aspect is responsible for the largest thermodynamic loss of the entire clockwise Clausius Rankine cycle in the working fluid circuit 2. After the second heat exchanger system 5, the liquid condensate of water vapor is returned to the process by means of Arbeitsmittelpumpsystems 6 and the cycle of the working fluid starts again, the decoupled lost heat content is lost to the environment.
    2 shows by way of example, in a form shown as a process diagram, a known absorption heat pump 8. In this case, the refrigerant is vaporized by means of external heat supply of a material stream to be cooled in an evaporation unit 19. The refrigerant vapor is then passed into an absorber system 27 where it is solubilized with a suitable solvent. The strong solution, preferably ammonia with water, but also other known solutions for operating absorption heat pump 8, is then sucked by means of a suitable solvent pumping system 28 and passed into a, designed in particular as Zweistromwärmetauscher, solution heat exchange system 29, where the poor solution, which from the expeller system 12 is supplied via the return line 39, transfers to the enriched solution more heat. Thereafter, the rich solution additionally charged with heat flows into the subsequent expeller system 12, which is operated with the supply of external energy. In this case, in the expeller system 12, the refrigerant is expelled thermally from the saturated solution and the pressure, temperature and energy content of the refrigerant increased, which is now in vapor form. This refrigerant vapor is then fed to a liquefaction unit 15, which at the same time also serves as a heat exchanger for heat transfer to an external material flow to be heated. In this case, the previously introduced heat is transferred to this external material flow and condensed at the same time in the liquefaction unit 15 of the refrigerant vapor. The dissipated heat is dissipated by the heated material flow. The unsaturated solvent is discharged in the form of a poor solution from the expeller system 12 via the return line 39 and the solution heat exchanger system 29, where it releases its useful heat. A solvent throttling system 31 throttles the poor solution so that it can be recycled via the return line 39 into the absorber system 27 to again absorb refrigerant and thus convert the non-enriched, poor solution into an enriched, strong solution. The condensed refrigerant is also supplied to a refrigerant center throttle system 30 and thermodynamically throttled so that it corresponds to its initial state. Thereafter, it is supplied to the evaporation unit 19, to extract heat from the material stream to be cooled externally and thereby evaporate and to be available for further repetitive heat absorption.
    The invention is based on the idea of using the heat loss energy of a clockwise-running thermodynamic cycle process for the operation of power and / or work machines. This was hitherto due to the fact that they do not make sense thermodynamically reusable in terms of the thermodynamic properties of the medium water as a result of the condensation need of water vapor in the cooling water condensation unit 20 of the second heat exchanger system 5 for the operation of the clockwise Clausius Rankine process Form before. It remained largely unused and was discharged by means of cooling medium to the environment. The reuse of the heat loss is achieved by, as described above, the clockwise cycle with one or more parallel connected left-handed cycles, which are operated as absorption heat pump 8, coupled in the first heat exchanger system 3 and the second heat exchanger system 5, at the same time operates in regular operation and the then heat to be reused, at the appropriate point, by means of the or the left-hand cycle, from the clockwise cycle removes and with the help of or the left-rotating cycles, which are operated as absorption heat pump 8, the thermodynamic state variables of the refrigerant changed in a suitable manner, so that the taken heat of the clockwise cycle process this Clausius Rankine process itself, using the absorption heat pump 8, at a suitable location leads back.
    In this case, the heat required to expel the refrigerant heat is removed during regular operation of the system of a turbine tap 11. The removal point is selected such that the required extraction steam energy content for the operation of the expeller system 12 is available. In particular, it may be provided that the extraction pressure at the turbine tap 11 is higher than the pressure of the condensed working fluid for the boiler feed in the first heat exchanger 3, so that the working fluid can be returned after passing through the expeller system 12 in the working fluid circuit 2 of the clockwise cyclic process.
    Particularly preferably, it can be provided that the second heat exchanger system 5 has the evaporation unit 19 of the refrigerant circuit 7. In particular, the evaporation unit 19 can be designed as a heat exchanger, in which the working medium circuit 2 is connected to the primary side of the evaporation unit 19, and the refrigerant circuit 7 is connected to the secondary side of the evaporation unit 19.
    It can preferably be provided that the first heat exchanger system 3 has the steam generator system 14 of the working medium circuit 2 and the liquefaction unit 15 of the refrigerant circuit 7, and that the liquefaction unit 15 is designed as a heat exchanger between the working medium circuit 2 and the refrigerant circuit 7. In the first heat exchanger system 3, therefore, the working fluid in the liquefaction unit 15 can be preheated and then vaporized in the steam generator system 14.
    Furthermore, it can be provided that the feed 13 of the discharge line 9 is arranged in the working medium circuit 2 between the steam generator system 14 and the liquefaction unit 15. Here, the feedback of the working fluid from the Austreibungsleitung 9 is energetically particularly advantageous at this point.
    In particular, it may be provided that a further working medium pumping system 16 is arranged between the feed 13 of the expulsion line 9 in the working medium circuit 2 and the steam generator system 14. As a result, the working fluid can be reliably brought to the pressure necessary for feeding into the steam generator system 14. If the working fluid pumping system 6 can be dimensioned large enough and the pressures in the Heizdampfentnahmen on the turbine tap 11 and / or the live steam tap 17 allow this, the elimination of the further Arbeitsmittelpumpsystems 16 is possible.
    In addition, for startup and shutdown of the steam power plant 1, as long as the steam turbine system 4 is not yet in operation, or in case of failure as redundancy, the expeller system 12 are supplied by means of live steam extraction from the main steam line 25. The switching to the control mode should preferably be done as quickly as possible, since the live steam is energetically higher than the steam from the turbine tap 11 and thus can be used to reach the turbine tap 11 energetically in the steam turbine system 4, so that a higher overall efficiency of the system adjusted as operating the expeller system 12 by means of live steam. The arrangement of both the live steam tap 17 and the turbine tap 11, the energy consumption during startup and or shutdown of the steam power plant 1 can be kept low. Furthermore, this results in the advantage that when a load change of the steam power plant 1, as this is more often necessary due to the increased use of renewable energy in the networks, the absorption pump 8 can be operated flexibly, whereby the absorption pump 8 is not on a constant load of the steam power plant 1 instructed.
    It can be provided that the expulsion line 9 on the input side in addition to the turbine tap 11 has a specifiable closable live steam tap 17, which live steam tap 17 between the first heat exchanger system 3 and the steam turbine system 4 is arranged. It can be provided that the specifiable closable live steam tap 17 can be closed by means of a live steam tapping valve 33 in order to be able to later switch over to the turbine tap 11.
    Furthermore, the live steam tap 17 may be provided with a live steam tap 32 to adjust the live steam condition to the ejector system 12. A throttle is a system for system pressure control and thermodynamic throttling of system media.
    Preferably, a steam conversion station may be used for the live steam tap throat 32 to control both pressure and temperature. The injection water used for the steam conversion station can in particular be taken from the working medium circuit 2, preferably between the working medium pumping system 6 and the steam generator system 14.
    In particular, it can be provided in the case of a live steam tap 17 that the turbine tap 11 is provided with a first backflow safety system 34. The backflow safety system 34 stands for any type of backflow preventer system for the purpose of preventing the wrong flow direction of system media, in this case the working medium of the working medium circuit 2.
    Furthermore, it can be provided that a presettable closable bypass line 18 of the working medium circuit 2 leads from the live steam tap 17 to the second heat exchanger system 5. The bypass line 18 can be closed by means of a bypass valve 35. Furthermore, a second backflow safety system 36 may be arranged in the working fluid circuit 2 downstream of the steam turbine system 4 in order to prevent live steam from the bypass line 18 from entering the outlet of the steam turbine system 4.
    Furthermore, it can be provided in the method that in the start-up operation and / or shutdown operation of the steam power plant 1, the working fluid is guided past the steam turbine system 4 to the second heat exchanger system 5 and / or the expeller system 12 of the absorption heat pump 8. In this case, the working fluid is guided past the steam turbine system 4.
    In addition, at least parts of the vaporized working fluid from the working fluid circuit 2 via an outlet valve 37 to the up to the achievement of intended steam parameters of the vaporized working fluid or in case of failure
    Be discharged environment, in particular via an external process water supply 38 of the output via the outlet valve 37 mass flow of working fluid from the working fluid circuit 2 is compensated. The intended steam parameters of the vaporized working medium, in particular pressure and temperature, may preferably be selected such that they are sufficient for operating the expeller system 12. Preferably, an absolute pressure greater than 1 [barabs] is provided here. The maximum pressure at the turbine tap is to be designed so that the energy content of the steam sufficient for the operation of the expeller system 12 and the condensate is sufficient and can be returned as previously described. In particular, it can be provided that the absolute pressure at the turbine tap 11 is at least 10% lower than the inlet pressure of the live steam from the live steam line 25 at the steam turbine system 25.
    Furthermore, it can be provided in particular the steam transformation station in the Austreibungsleitung 9 in front of the expeller system 12 for pressure and temperature control.
    3 shows, in a form shown as a process diagram, a first preferred embodiment as a combination of the left-handed and the right-handed cyclic process, as it can be realized as an overall process by means of an absorption heat pump 8. In this case, the refrigerant of the absorption heat pump 8 is evaporated by condensation heat of the exhaust steam from the steam turbine system 4 from the working fluid circuit 2 in the evaporation unit 19 of the refrigerant circuit 7. In this case, the evaporation unit 19 replaces the cooling water condensation unit 20 of FIG. 1 and simultaneously serves as the evaporative unit 19 for the refrigerant of the absorption heat pump 8, which changes its aggregate state from liquid to vapor on the secondary side of the evaporation unit 19 by applying the steam flowing from the steam turbine system 4 withdraws its heat until it also changes its state of aggregation from vapor to liquid on the primary side of the evaporation unit 19.
    The effluent condensate of the working fluid is sucked in the first preferred embodiment of the working medium pumping system 6 and means
    Pressure increase by the working fluid pumping system 6, transported in the direction of liquefaction unit 15 of the refrigerant circuit 7. In this refrigerant circuit 7, the condensate of the working fluid now removes its charged heat energy from the simultaneously operated, superimposed, coupled absorption heat pump process and thus increases its energy content. Subsequently, the so-preheated working fluid is sucked as feed water by means of the further Arbeitsmittelpumpsystems 16 higher pressure than the above-described Arbeitsmittelpumpsystem 6 from, increased pressure by means of the downstream further Arbeitsmittelpumpsystems 16 and fed into the steam generator system 14. As a result of the previously described preheating of the working fluid from the working fluid circuit 2 in the liquefaction unit 15, the fuel requirement from the heating energy supply system 24, which reduces the remaining heat energy until it reaches the required level, is thus reduced
    Total system design heat output of the steam generation plant. As a result of the described preheating by means of recovery of the heat of vaporization from the exhaust steam of the steam turbine system 4, the fuel or heating energy requirement, compared with conventional processes as described in FIG. 1, is significantly reduced and the efficiency of the new overall system correspondingly increased. In the steam generator system 14 now changes the liquid working fluid by supplying heat from the Heizenergiezufuhrsystem 24 its state of aggregation from liquid to vapor. The vaporous working fluid exits the steam generator system 14 as so-called live steam and is led to the steam turbine system 4.
    In the steam turbine system 4, the live steam is now deprived of its energy so far as to operate the mechanically coupled work machine system or generator system 26. The useful work done here is dissipated by the generator system 26 to a consumer in the form of useful energy. The exhaust steam from the steam turbine system 4 is returned to the clockwise running part of the overall process, which corresponds to the working fluid circuit 2.
    The right-rotating part of the overall process in the regular operation at the same time, coupled, superimposed left-handed cyclic process by means of absorption heat pump 8 for the first preferred embodiment now works as follows. The Indian
    Evaporation unit 19 resulting refrigerant vapor flows into the absorber system 27 and goes in this with the solvent in an enriched, strong solution. This is then sucked by the solvent pumping system 28 and pressure increased. Thereafter, the strong solution is supplied to the solution heat exchange system 29, wherein in this already a first additional heat energy absorption takes place by exchange with the effluent from the expeller system 12 via the return line 39 unsaturated, poor solution. The thus preheated strong solution of higher energy flows into the expeller system 12, where the refrigerant in solution with the aid of supplied heat from the expulsion line 9 is thermally expelled. The remaining poor solution is discharged via the return line 39 as already described, exchanges its heat energy in the solution heat exchange system 29 as far as possible with the strong solution and is fed to a solvent throttling system 31. This solvent throttling system 31 now throttles the poor solution to such an extent and forwards it via the return line 39 in the direction of the absorber system 27, so that it can again change into a strong solution with the refrigerant vapor. The refrigerant vapor released in the expeller system 12 is sent to the liquefaction unit 15. In this liquefaction unit 15, the refrigerant vapor exchanges its heat energy content as far as the condensate of the working fluid of the working fluid circuit 2, until it condenses. Subsequently, the refrigerant condensate is passed to a refrigerant mean throttle system 30, which in turn throttles the inflowing refrigerant condensate that it then the evaporation unit 19, again reaches its thermal state variables as the initial time of the system run, thus the left-handed cycle of the refrigerant circuit 7 is closed by being evaporated again can. The superimposed leftward process then begins again with the evaporation of the refrigerant while supplying heat energy from the exhaust steam of the steam turbine system. 4
    In order to provide the heat energy required for the thermal expulsion of the refrigerant in the expeller system 12, a removal of the heating steam from a turbine tap 11 is in normal operation of the
    Steam turbine system 4 is provided. In addition, the portion of the steam generated in the steam generator system 14 for the entire system from the main steam line 25 to the steam turbine system 4 can be diverted. A system-external steam supply is also a viable option, but is not explicitly shown here. All three or both variants shown can also be realized at the same time for redundancy reasons.
    Preferably, the first backflow preventer system 34 may be provided on the turbine tap 11 to prevent steam from the steam generator system 14 from flowing into the steam turbine system 4 via the turbine tap 11 due to its higher pressure.
    The extracted heating steam to operate the expeller system 12 is supplied to this changes its state of aggregation in the expeller system 12 from vapor to liquid and is then returned as condensate in the working fluid circuit 2. The advantage of the turbine tap 11 is that the thermodynamically considered high-quality live steam until the tap parameters at the turbine tap 11 for the utilization of energy by means of working machine and / or generator system 26 can be used. This significantly improves the overall efficiency of the overall system.
    The turbine tap 11 is to be designed so that the extraction steam has a sufficiently high energy content to operate the expeller system 12 and the resulting condensate in the expeller system 12 via the feed 13 to the working fluid circuit 2 can be fed again. When designing the turbine tap 11, it should be noted that the extraction steam from full operation to reaching the minimum load of the steam turbine system 4 enables the supply from the expeller system 12. Preferably, an absolute pressure greater than 1 [barabs] is provided here. The maximum pressure at the turbine tap 11 is to be designed so that the energy content of the steam is sufficient for the operation of the expeller system 12 and the condensate can be returned as described above.
    In particular, it can be provided that the absolute pressure at the
    Turbine tap 11 by at least 5%, preferably 10%, more preferably 15%, is less than an input pressure of the live steam from the main steam line 25 to the steam turbine system. 4
    In order to start or stop the steam power plant 1, the live steam can be discharged via an outlet valve 37, even before reaching the necessary live steam parameters in the live steam line 25, which enable the steam turbine system 4 to be triggered, or when the steam turbine system 4 is shut down or in the event of incidents. or be passed via the bypass line 18 by means of the predetermined lockable bypass valve 35 to the second heat exchanger 5. When using the bypass line 18, the second backflow safety system 36 is preferably provided, so that no steam can flow back into the steam turbine system 4. In regular operation, the bypass line 18 remains closed. As long as steam is discarded via the outlet valve 37 is from an external process water supply 38 to replace the Verwurfdampfmenge in the same amount. A parallel operation of the exhaust valve 37 for discarding the live steam and the bypass line 18 is possible and provided for starting and stopping the steam power plant 1.
    During operation of the bypass line 18, the introduced heat can be dissipated in the second heat exchanger system 5 by the operation of the refrigerant circuit 7, wherein the Austreibungsleitung 9 is supplied via the opened Frischdampfanzapfungsventil 33.
    By the present first preferred embodiment of the steam power plant 1 as a superimposition of a clockwise-running with a clockwise cyclic process thus creates a novel overall process, the efficiency is significantly higher than that of FIG. The use of the absorption heat pump 8 in comparison to a compression heat pump has the advantage that larger material flows can be transferred technically easier to implement. In addition, in this first embodiment, the cooling water condensation unit 20 of FIG. 1 is completely replaced.
    Preferably, it can further be provided that the second heat exchanger system 5 has a cooling water condensation unit 20 of the working medium circuit 2.
    This is illustrated by way of example in FIG. 4 in the second preferred embodiment. In this case, the second heat exchanger system 5 may in particular contain both an evaporation unit 19 and the cooling water condensation unit 20. Thereby, the absorption heat pump 8 can be made smaller in capacity, and / or the steam power plant 1 can perform better load changes, since rapidly occurring heat of condensation can be easily dissipated via the cooling water.
    It can be provided that the evaporation unit 19 and the cooling water condensation unit 20 with respect to the heat exchange capacity form substantially the same size. As a result, complete redundancy can be ensured in the event of a fault.
    Furthermore, it can be provided that the heat exchange capacity of the cooling water condensation unit 20 is only so great that it is sufficient for the starting operation. It can thus be ensured that the heat of condensation can be dissipated during the starting operation, while during normal operation it is dissipated at least mainly via the evaporation unit 19.
    It can preferably be provided that the working medium circuit 2 in the second heat exchanger system 5 leads in parallel through the evaporation unit 19 of the refrigerant circuit 7 and the cooling water condensation unit 20. In this case, the working fluid circuit 2 after the steam turbine system 4 can be divided into several lines, which lead in parallel through the evaporation unit 19 and the cooling water condensation unit 20, wherein the working fluid circuit 2 is then brought together again. Thus, the working fluid of the working fluid circuit 2 after the steam turbine system 4 can be divided into several lines, the parallel flow of steam from the working fluid circuit 2 is ensured by the evaporation unit 19 and the cooling water condensation unit 20, wherein the working fluid circuit 2 then after exiting the evaporation unit 19th and the cooling water condensation unit 20 is brought together again. Here, the evaporation unit 19 and the cooling water condensation unit 20 may each be designed as a separate and for the heat transfer to the refrigerant or coolant specially optimized heat exchanger, whereby these heat exchangers can be optimized with respect to choice of material, flow resistance and heat transfer. Furthermore, the absorption heat pump 8 can be easily integrated into existing systems. Furthermore, in the case of the parallel arrangement and / or steam inflow from the working medium circuit 2 into the evaporation unit 19 and the cooling water condensation unit 20, the enthalpy of entry can be the same, so that the effectiveness of the refrigerant circuit 7 can be optimized overall.
    Furthermore, it can be provided that the second heat exchanger system 5 has a valve system 21 for the predefinable division of a working medium flow between the evaporation unit 19 and the cooling water condensation unit 20 arranged in parallel. Thereby, the amount of heat to be discharged for condensing the working fluid in the second heat exchanger system 5 can be selectively divided between the absorption heat pump 8 and the cooling water condensation unit 20, whereby the steam power plant 1 can easily change the power, and the absorption heat pump 8 can be operated in the optimum parameter range.
    In the second preferred embodiment in FIG. 4, unlike FIG. 3, the cooling water condensation unit 20 shown in FIG. 1 remains and the exhaust steam of the steam turbine system 4 is divided according to the overall system design valve system 21, so that a part of this waste heat the evaporation unit 19 is available for dissipating heat to the refrigerant and / or a portion of the waste heat of the cooling water condensation unit 20 is supplied and discharged by means of cooling medium through the cooling water return line 22 to the environment. In this case, only that portion of the waste heat from the steam turbine system 4, which passes in the evaporation unit 19 to the refrigerant, to increase the efficiency of the overall system compared to the process in Fig. 1. On both sides in the evaporation unit 19 and / or the cooling water condensation unit 20 is the Condensed working fluid and after the exit of the condensed working fluid 2 from the evaporation unit 19 and the cooling water condensation unit 20 again brought together and transported together in the right-handed Kreisprozessteil of the overall system further transported. All other system functions of this second preferred embodiment are similar to those described in the first preferred embodiment of FIG. If the live steam is conducted via the bypass line 18 into the evaporation unit 19, the mode of operation is as described in FIG. In addition to FIG. 3, the live steam can now also be discharged via the bypass line 18 directly to the cooling water condensation unit 20, which improves the operational flexibility of the steam power plant 1 and increases its availability. The illustrated arrangement is used inter alia compared with Fig. 3 for easier integration into existing systems and is to be understood as a partial and / or partial superposition of left and rechtsläufigen cycles using an absorption heat pumping process. It also serves to include financial or local aspects of existing plants or in new projects in the design of the steam power plant 1 more.
    Alternatively it can be provided that a leading from cooling water condensation unit 20 cooling water return line 22 through the evaporation unit 19 of the refrigerant circuit 7 leads. Here, a heat exchange between the working fluid circuit 2 and the refrigerant circuit 7 in the second heat exchanger system 5 is not directly via a heat exchanger, but via the cooling water as a carrier medium. The advantage of this is that in an existing steam power plant 1, the working fluid circuit 2 in the second heat exchanger system 5 can remain unchanged, making retrofitting is particularly easy.
    5 shows, in a form shown as a process diagram, a third preferred embodiment of the steam power plant 1. Here, the existing evaporation unit 19 as shown in FIG. 4 and the heat of vaporization of the refrigerant is removed from the cooling water return line 22 of the cooling water condensation unit 20. The remainder of the process is similar to that in FIG. 3, where no division of the exhaust steam flow as in FIG. 4 is required. The valve system 21 of Figure 4 thus deleted. Due to the low temperatures of the cooling water, the thermodynamic design based on the overall efficiency in this case is the least productive compared to the other preferred embodiments of FIGS. 3 and 4.
    Furthermore, it may be provided that a further refrigerant circuit 23 at least partially comprises the first heat exchanger system 3 and at least partially the second heat exchanger system 5, wherein in particular the further refrigerant circuit 23 in construction corresponds to the refrigerant circuit 7. The absorption heat pump 8 can then have a plurality of parallel refrigerant circuits 7, 23, which can be switched on as needed and utilization. This allows a very flexible reacting to power changes steam power plant can be achieved. For design, manufacturing and cost reasons, one can then divide the left-running absorption heat pump cycle process into a plurality of refrigerant circuits 7, 23 to be operated in parallel.
    6 shows by way of example, in a form shown as a process diagram, a fourth preferred embodiment of the steam power plant 1. Here, a steam power plant 1 shown in FIG. 3 with two parallel running left-side absorption heat pump processes, each having its own refrigerant circuits 7, 23. Furthermore, even more parallel arrangements with three, four or even more refrigerant circuits 7, 23 can be provided, which at the same time provide for the lost heat displacement. In this case, in each of these parallel processes, that portion of the waste heat is displaced from the clockwise circulating process part of the working medium circuit 2, which corresponds to the design of the refrigerant circuit 7, 23. This parallel operated multiple arrangement is useful to optimize the overall system for greater part load capacity, while reducing redundancy in terms of availability for the entire system.
    For design, manufacturing and cost reasons, it is also possible in the preferred embodiments of FIGS. 4 and 5 to divide the left-running absorption heat pump cycle process part of the overall system into a plurality of refrigerant circuits 7, 23 to be operated in parallel, as shown in FIG. In each of these parallel processes, that proportion of the
    Lost heat shifted from the clockwise circuit process part, which corresponds to the design of the respective refrigerant circuit 7, 23.
    Here, the individual embodiments of the second heat exchanger system 5 of the different preferred embodiments can be combined with each other to combine the advantages of the individual preferred embodiments. For example, it may be preferable that the preferred embodiment in FIG. 6 is additionally formed with a cooling water condensation unit 20 operated according to the second or third preferred embodiment.
    claims:
    权利要求:
    Claims (15)
    [1]
    1. Steam power plant (1) with a working fluid circuit (2) for a working fluid, wherein the working fluid circuit (2) - viewed in the direction of flow of the working fluid - a first heat exchanger system (3) for vaporizing the working fluid, a steam turbine system (4), a second heat exchanger system ( 5) for condensing the working fluid and a working medium pumping system (6), characterized in that at least one refrigerant circuit (7) of an absorption heat pump (8) at least partially comprises the first heat exchanger system (3) and at least partially the second heat exchanger system (5) Absorption heat pump (8) for the introduction of heat energy from the second heat exchanger system (5) to the first heat exchanger system (3) is formed, and that an expulsion line (9) from a turbine tap (11) of the steam turbine system (4) via an expeller system (12) of the Absorption heat pump (8) to a feed (13) in the Arbeitskreiskreislau f (2), wherein the working fluid in the exhaust duct (9) provides heat energy for an expulsion process of the absorption heat pump (8).
    [2]
    2. steam power plant (1) according to claim 1, characterized in that the first heat exchanger system (3) has a steam generator system (14) of the working medium circuit (2) and a liquefaction unit (15) of the refrigerant circuit (7), and that the liquefaction unit (15) as a heat exchanger between the working medium circuit (2) and refrigerant circuit (7) is formed.
    [3]
    3. steam power plant (1) according to claim 2, characterized in that the feed (13) of the expulsion line (9) in the working medium circuit (2) between the steam generator system (14) and the liquefaction unit (15) is arranged.
    [4]
    4. steam power plant (1) according to claim 2 or 3, characterized in that a further working medium pumping system (16) between the feed (13) of the expulsion line (9) in the working medium circuit (2) and the steam generator system (14) is arranged.
    [5]
    5. steam power plant (1) according to one of claims 1 to 4, characterized in that the expulsion line (9) on the input side in addition to the turbine tap (11) a predetermined closable live steam tap (17), which live steam tap (17) between the first heat exchanger system ( 3) and the steam turbine system (4) is arranged.
    [6]
    6. steam power plant (1) according to claim 5, characterized in that of the live steam tap (17) leads a predetermined closable bypass line (18) of the working medium circuit (2) to the second heat exchanger system (5).
    [7]
    7. Steam power plant (1) according to one of claims 1 to 6, characterized in that the second heat exchanger system (5) has an evaporation unit (19) of the refrigerant circuit (7).
    [8]
    8. steam power plant (1) according to one of claims 1 to 7, characterized in that the second heat exchanger system (5) has a cooling water condensation unit (20) of the working medium circuit (2).
    [9]
    9. steam power plant (1) according to claim 7 and 8, characterized in that the working medium circuit (2) in the second heat exchanger system (5) in parallel through the evaporation unit (19) of the refrigerant circuit (7) and the cooling water condensation unit (20).
    [10]
    10. steam power plant (1) according to claim 9, characterized in that the second heat exchanger system (5) has a valve system (21) for the predeterminable division of a working fluid flow between the evaporation unit (19) and the parallel arranged cooling water condensation unit (20).
    [11]
    11. steam power plant (1) according to claim 7 and 8, characterized in that a cooling water condensation unit (20) leading cooling water return line (22) through the evaporation unit (19) of the refrigerant circuit (7) leads.
    [12]
    12. steam power plant (1) according to one of claims 1 to 11, characterized in that a further refrigerant circuit (23) at least partially the first heat exchanger system (3) and at least partially the second heat exchanger system (5), in particular the further refrigerant circuit (23 ) corresponds in structure to the refrigerant circuit (7).
    [13]
    13. A method for operating a steam power plant (1) in normal operation, wherein in a working fluid circuit (2) a working fluid in a first heat exchanger system (3) evaporated and a steam turbine system (4) is supplied, wherein the working fluid after the steam turbine system (4) in a second heat exchanger system (5) is condensed and fed back to the first heat exchanger system (3) via a working medium pumping system (6), characterized in that by means of at least one refrigerant circuit (7) of an absorption heat pump (8) heat energy from the second heat exchanger system (5) to the first Heat exchanger system (3) is spent that at a turbine tap (11) a part of the working fluid from the steam turbine system (4) branched off in a Austreibungsleitung (9), liquefied in an expelling system (12) of the absorption heat pump (8) and at a feed (13 ) is returned to the working fluid circuit (2), said by this Te il the working fluid heat energy for a drive-off process of the absorption heat pump (8) is provided.
    [14]
    14. The method according to claim 13, characterized in that in a start-up operation and / or shutdown operation of the steam power plant (1) the working fluid to the steam turbine system (4) over to the second heat exchanger system (5) and / or the expeller system (12) of the absorption heat pump (8 ) to be led.
    [15]
    15. The method according to claim 13 or 14, characterized in that until reaching steam provided parameters of the vaporized working fluid or in case of failure at least parts of the vaporized working fluid from the working fluid circuit (2) via an outlet valve (37) are discharged to the environment, and that in particular via an external process water supply (38) of the output via the outlet valve (37) mass flow of working fluid from the working fluid circuit (2) is compensated.
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    同族专利:
    公开号 | 公开日
    PL3317497T3|2020-07-13|
    EP3317497A1|2018-05-09|
    CN107849946A|2018-03-27|
    WO2017001241A1|2017-01-05|
    US20180187573A1|2018-07-05|
    EP3317497B1|2019-11-20|
    AT517535B1|2018-03-15|
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    US2982864A|1956-05-21|1961-05-02|Furreboe Anton|Improved heat cycle for power plants|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA419/2015A|AT517535B1|2015-06-30|2015-06-30|Steam power plant|ATA419/2015A| AT517535B1|2015-06-30|2015-06-30|Steam power plant|
    PCT/EP2016/064281| WO2017001241A1|2015-06-30|2016-06-21|Steam power plant|
    US15/740,297| US20180187573A1|2015-06-30|2016-06-21|Steam power plant|
    PL16732571T| PL3317497T3|2015-06-30|2016-06-21|Steam power plant|
    CN201680038862.0A| CN107849946A|2015-06-30|2016-06-21|Steam electric power generator|
    EP16732571.1A| EP3317497B1|2015-06-30|2016-06-21|Steam power plant|
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