CN113294217A - Back pressure type steam turbine heat regeneration system with small steam turbine and thermodynamic balance design method - Google Patents
Back pressure type steam turbine heat regeneration system with small steam turbine and thermodynamic balance design method Download PDFInfo
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- 238000000034 method Methods 0.000 title claims abstract description 20
- 238000013461 design Methods 0.000 title claims abstract description 18
- 230000008929 regeneration Effects 0.000 title claims description 6
- 238000011069 regeneration method Methods 0.000 title claims description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 126
- 230000001172 regenerating effect Effects 0.000 claims abstract description 51
- 238000010438 heat treatment Methods 0.000 claims abstract description 37
- 238000011084 recovery Methods 0.000 claims abstract description 31
- 230000003020 moisturizing effect Effects 0.000 claims abstract description 10
- 230000001105 regulatory effect Effects 0.000 claims description 21
- 238000000605 extraction Methods 0.000 claims description 11
- 238000006392 deoxygenation reaction Methods 0.000 claims description 10
- 238000003303 reheating Methods 0.000 claims description 10
- 238000009835 boiling Methods 0.000 claims description 6
- 239000008236 heating water Substances 0.000 claims description 4
- 238000002347 injection Methods 0.000 claims description 3
- 239000007924 injection Substances 0.000 claims description 3
- 239000013589 supplement Substances 0.000 abstract description 26
- 238000012546 transfer Methods 0.000 abstract description 3
- 238000010304 firing Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 11
- 230000006872 improvement Effects 0.000 description 9
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- 238000004364 calculation method Methods 0.000 description 4
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- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 239000003245 coal Substances 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
- CDBYLPFSWZWCQE-UHFFFAOYSA-L Sodium Carbonate Chemical compound [Na+].[Na+].[O-]C([O-])=O CDBYLPFSWZWCQE-UHFFFAOYSA-L 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 238000005504 petroleum refining Methods 0.000 description 1
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- 239000007921 spray Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
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- 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
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
- F22B31/08—Installation of heat-exchange apparatus or of means in boilers for heating air supplied for combustion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/50—Feed-water heaters, i.e. economisers or like preheaters incorporating thermal de-aeration of feed-water
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Abstract
The invention discloses a back pressure turbine heat regenerative system with a small turbine and a design method of thermal balance thereof, wherein the heat regenerative system at least comprises the back pressure turbine, an auxiliary device which is connected with the back pressure turbine and is used for heating and deoxidizing the water supplement and return water of the heat regenerative system, a water supply power device which provides power for the water supplement and return water of the system and enables the water supply and return water to circularly flow in the heat regenerative system, the small turbine which is connected with the back pressure turbine and is used for driving the water supply power device, and a condenser which is connected with the small turbine; the condenser is except as the exhaust condensing equipment of little steam turbine, still regards as elementary deoxidization, the firing equipment of whole heat recovery system moisturizing and return water, the exhaust of little steam turbine as the deoxidization vapour source of condenser all is used for deoxidization, the heating of system moisturizing and return water, and the heat transfer difference in temperature reduces and does not have the cold junction loss, and system efficiency can promote.
Description
Technical Field
The invention relates to the field of cogeneration equipment, in particular to a back pressure steam turbine heat regenerative system with a small steam turbine and a thermal balance design method thereof.
Background
In the fields of petroleum refining and coal chemical industry, a large amount of high-grade steam is often required in the process flow. At present, the domestic industrial park can be generally matched with a high-power and high-parameter cogeneration back-pressure steam turbine during construction.
The existing back pressure steam turbine has a simple heat recovery system, and usually adopts a mode of heating a system for replenishing water after steam exhaust and pressure reduction, and the efficiency of the mode is low; in some domestic projects, a plurality of lower-pressure through-flow stages are added behind the last-stage steam extraction point of the back pressure turbine, so that high-quality steam continues to work and then is heated to supplement water to the system, although the mode improves the system efficiency, the back pressure turbine needs to monitor the steam exhaust pressure and the overflow steam quantity during operation, so that the operation regulation is complicated, and the flexible regulation and the safe operation of heat supply load are not facilitated; on the other hand, although a small turbine for driving a feed pump is arranged in a large-power back-pressure turbine in a few projects, the exhaust steam of the large-power back-pressure turbine is often led to an independent condenser and cooled by circulating water, the heat of the exhaust steam is not effectively utilized in the method, and certain cold end loss still exists.
Therefore, how to improve the heat energy utilization rate of the back pressure turbine without increasing the operation adjustment difficulty is a problem to be solved at present.
Disclosure of Invention
For the problems in the prior art, the invention adopts the back pressure type steam turbine heat regeneration system with the small steam turbine, the scheme utilizes the small steam turbine steam exhaust heating system to supplement water and return water, the steam exhaust heat of the back pressure type steam turbine is effectively utilized during operation, no cold end loss exists, and meanwhile, the adjusting system does not need to monitor the overflow steam quantity and the steam exhaust pressure, so that the whole system is more convenient and safer to operate, and the heat load adjustment is more flexible.
The purpose of the invention is realized by the following technical scheme:
a back pressure turbine heat recovery system with a small turbine at least comprises a back pressure turbine, an auxiliary device which is connected with the back pressure turbine and used for heating and deoxidizing the water supplement and the return water of the heat recovery system, a water supply power device which provides power for the water supplement and the return water of the system and enables the water supplement and the return water to circularly flow in the heat recovery system, the heat recovery system also comprises a small turbine which is connected with the back pressure turbine and used for driving the water supply power device, and a condenser which is connected with the small turbine; the condenser is used as the primary deoxidization and heating equipment for water supplement and water return of the whole heat recovery system, except for the exhaust steam condensing equipment of the small steam turbine, the exhaust steam of the small steam turbine is used as the steam source of the condenser for deoxidization and heating of the water supplement and water return of the system. The small steam turbine exhaust steam is completely used for heating, water replenishing and water returning, the heat exchange temperature difference is reduced, no cold end loss exists, and the system efficiency is improved; in addition, when the unit is started or stopped and operates under a variable working condition, the amount of overflowing steam and thrust of the back pressure turbine do not need to be monitored additionally, the number of parameters and variables is reduced, and operation and regulation are more convenient.
As a preferred technical scheme, the back pressure turbine heat recovery system further comprises a low-pressure heater i connected with the water supply power device and the auxiliary device respectively, and the low-pressure heater i is further connected to the small turbine through a heat recovery pipeline; and the low-pressure heater I is connected with a bypass regulating valve in parallel to regulate the regenerative steam dosage of the low-pressure heater I. After the small steam turbine is provided with the low-pressure heater I, the through-flow capacity of the small steam turbine is increased, so that the through-flow efficiency of the small steam turbine is improved; the proportion of the regenerative steam extracted from the small steam turbine to the through flow is large, and the power of the small steam turbine can be changed in a large range by changing the flow of the water side of the low-pressure heater carried by the small steam turbine, so that the effect of improving the load regulation capacity is strong.
Preferably, the back pressure turbine is a reheat back pressure turbine.
As a preferred technical solution, the reheating back pressure turbine includes a high pressure module and a medium pressure module; the high-voltage module and the medium-voltage module are respectively connected with the auxiliary device; the small steam turbine is connected to the medium-pressure module through a heat recovery steam pipeline; the heat recovery system also comprises a low-pressure heater I connected with the auxiliary device and a low-pressure heater II connected with the low-pressure heater I, and the other end of the low-pressure heater II is connected with the water supply power device; the low-pressure heater I and the low-pressure heater II are also connected to the small steam turbine through a heat return pipeline; and the low-pressure heater I and the low-pressure heater II are connected with a bypass regulating valve in parallel, and the quantity of regenerative steam of the low-pressure heater I and the low-pressure heater II is regulated. This scheme changes back pressure steam turbine into the reheat type because this scheme can only take the biggest benefit in high-power reheat type back of the body press system, more laminating in-service use.
As a preferred technical scheme, the water supply power device comprises a water supply pump and a water delivery pump, the steam turbine drives the water supply pump, so that the service power can be reduced, the external power supply quantity can be increased, the online power quantity can be increased, and the economic benefit of a power plant can be increased.
According to a preferable technical scheme, the condenser is an injection type condenser. The jet condenser is also called as a mixed condenser, and a nozzle of the jet condenser sprays the supplemented water of a system to form a water film to directly contact with the exhaust steam of the small turbine for heat exchange.
As a preferred technical scheme, the heat recovery system is provided with an auxiliary steam source, and the auxiliary steam source is connected to the steam inlet end of the condenser; and the auxiliary steam source is taken from the exhaust steam of the back pressure turbine and/or the service steam. In the process of starting and stopping the unit and changing working conditions, when the steam discharged by the small steam turbine does not meet the steam quantity required by system water supplement and backwater deoxidization, steam is supplied to the condenser through the auxiliary steam source.
As a preferable technical scheme, a regulating valve is arranged on a pipeline of the auxiliary steam source. The thermodynamic balance and the oxygen removal effect of the unit during starting, stopping and variable working condition running are ensured, and the backpressure of the small steam turbine is stabilized within an allowable range.
Preferably, the inlet of the small turbine is connected to the exhaust end or the through flow interstage of the back pressure turbine.
The invention also provides a design method for thermodynamic equilibrium of the regenerative system, which comprises the following steps:
s1, presetting the backpressure of a small turbine as Pkt to obtain the effluent enthalpy of the condenser, and calculating the steam quantity A required by deoxygenation and boiling according to the heat balance of the condenser by combining the inlet enthalpy and the inlet flow of the condenser;
s2, obtaining enthalpy drop of the small steam turbine according to the steam inlet pressure temperature and the backpressure of the small steam turbine, and calculating by combining the power of a feed pump to obtain the steam inlet amount B required by the small steam turbine;
s3, iteratively solving the backpressure Pkt of the small steam turbine to enable the A and the B to be equal, comparing whether the difference value of the A and the B is within an allowable range, if the difference value is not within the allowable range and the A is larger than the B, reducing the preset backpressure Pkt, and repeatedly executing steps S1 and S2; if the difference is not within the allowable range and the flow rate a is less than the flow rate B, Pkt is increased, and steps S1 and S2 are repeatedly performed.
S4, judging whether the difference value between the backpressure Pkt obtained after iteration and the preset backpressure Pkt is within an allowable range, if the difference value is not within the allowable range and the Pkt is greater than the Pkt, moving the steam inlet of the small steam turbine forward, increasing the inlet pressure and the inlet temperature of the small steam turbine, and repeatedly executing the step S1; if the difference is not within the allowable range and Pkt is less than Pkt, the steam inlet of the small steam turbine is moved backward, the pressure and temperature at the inlet of the small steam turbine are reduced, and step S1 is repeatedly performed.
The invention also provides another design method for thermodynamic equilibrium of the heat recovery system, which comprises the following steps:
s1, setting the backpressure Pkt of the small turbine to obtain the effluent enthalpy of the condenser, and calculating the steam quantity A required by deoxygenation and boiling according to the heat balance of the condenser by combining the inlet enthalpy and the inlet flow of the condenser;
s2, calculating to obtain the enthalpy drop of the small steam turbine according to the steam inlet pressure, temperature and back pressure of the small steam turbine, and calculating to obtain the power B of the small steam turbine by combining the steam quantity A;
s3, comparing whether the difference value between the power B of the small steam turbine and the power of the water feeding pump is within an allowable range, if the difference value is not within the allowable range and the power B of the small steam turbine is greater than the power of the water feeding pump, moving the steam inlet of the small steam turbine backwards, reducing the pressure and the temperature of the inlet of the small steam turbine, and repeatedly executing the step S2; if the difference value is not in the allowable range and the power B of the small steam turbine is less than the power of the feed pump, the steam inlet of the small steam turbine is moved forward, the pressure temperature of the inlet of the small steam turbine is increased, or a regenerative steam extraction stage is additionally arranged between the through flow stages of the small steam turbine, and the step S2 is repeatedly executed.
The invention has the beneficial effects that: the small steam turbine exhaust steam is completely used for heating water replenishing and water returning, the heat exchange temperature difference is reduced, cold end loss is avoided, system efficiency is improved, and overlarge problem caused by heating water replenishing of heat supply exhaust steam with higher parameters of an active back pressure steam turbine can be solved
And (4) loss. And compared with the technical scheme that a plurality of lower-pressure through flow stages are added behind the last-stage steam extraction point of the back pressure turbine, when the unit is started and stopped and operates under variable working conditions, the scheme does not need to additionally monitor the overflow steam quantity and the thrust of the back pressure turbine, the number of the parameter variable quantities is reduced, and the operation regulation is more convenient. In addition, the power and flow balance of the small steam turbine are independently controlled by the regulating system of the small steam turbine; in the case of a back-pressure turbine,the steam consumption of the small steam turbine is only the heat load regulated by an external system, and the operation control difficulty of the back pressure steam turbine is not increased. The system adopts two-stage thermal power deoxidization for back pressure type steam turbine set steam-water system deoxidization effect that the moisturizing volume is great is better, and equipment security can improve. In addition, after the small steam turbine is provided with the low-pressure heater, the through-flow capacity of the small steam turbine is increased, so that the through-flow efficiency of the small steam turbine is improved; the proportion of the regenerative steam extracted from the small steam turbine in the through-flow of the regenerative steam is large, the power of the small steam turbine can be changed in a large range by changing the flow of the water side of the low-pressure heater carried by the small steam turbine, and the effect of improving the load and adjusting the energy is strong. With the continuous improvement of the parameters and the capacity of the back pressure turbine, the thermodynamic system designed by the scheme can obtain better economic benefits and meet the development trend and the technical requirements of the industry.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained based on these drawings without paying creative efforts.
FIG. 1 is a schematic view of a back pressure turbine regenerative system according to a first embodiment;
FIG. 2 is a schematic view of a back pressure turbine regenerative system according to a second embodiment;
FIG. 3 is a schematic view of a reheating system of a reheating back pressure turbine according to a third embodiment;
the system comprises a 1-back pressure turbine, a 2-high pressure heater I, a 3-high pressure heater II, a 4-high pressure deaerator, a 5-small turbine, a 6-water feeding pump, a 7-water conveying pump, an 8-condenser, a 9-shaft seal cooler, a 10-regulating valve, an 11-low pressure heater I, a 12-bypass regulating valve, a 13-low pressure heater II, a 14-medium pressure module and a 15-high pressure module.
Detailed Description
The technical solutions of the present invention are further described in detail below with reference to the accompanying drawings, but the scope of the present invention is not limited to the following.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the embodiments of the present invention will be described in detail and completely with reference to the accompanying drawings, and it is to be understood that the described embodiments are a part of the embodiments of the present invention, but not all of the embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.
As shown in the attached drawing, the back pressure turbine heat recovery system with the small turbine is provided. Compared with the traditional back pressure type steam turbine heat regeneration system, the technical scheme of the embodiment is that the inventor finds that the traditional back pressure type steam turbine is generally simpler through deep exploration, and the efficiency is not high because a steam exhaust decompression mode is generally adopted to heat the system for water supplement; or a plurality of through-flow stages with lower pressure are added behind the last-stage steam extraction point of the back pressure steam turbine, although the temperature difference between the water replenishing of the system and the heating steam is reduced, the complexity of the operation adjustment of the system is increased, and the flexible adjustment and the safe operation of the heat supply load are not facilitated; or a small steam turbine is arranged and a steam feed pump is adopted, but the discharged steam of the small steam turbine is mainly cooled by circulating water, and certain cold end loss is still unavoidable. Based on the above, the inventor makes an improvement on the basis of the traditional back pressure turbine heat recovery system, designs the back pressure turbine heat recovery system with the small turbine as shown in the attached drawing, designs the back pressure turbine and the small turbine thereof in a cooperative manner, configures an injection type condenser for the small turbine, and the condenser is also used as a contact type heat exchanger for system water supplement heating and primary deoxidization, and uses the exhaust steam of the small turbine to heat the system water supplement and the return water, thereby improving the system thermal efficiency. See the following examples for specific embodiments:
example one
As shown in fig. 1, the above mentioned back pressure turbine regenerative system at least includes a back pressure turbine 1, an auxiliary device, a water supply power device, a small steam turbine 5, and a condenser. The auxiliary device is connected with the back pressure turbine 1 and used for heating and deoxidizing the water supplement and return water of the heat recovery system, and the water supply power device provides power for the water supplement and return water of the system so as to enable the water supplement and return water to circularly flow in the heat recovery system; the small turbine 5 is connected with the back pressure turbine 1 and can drive the water supply power device, and the condenser 8 is connected with the small turbine 5; it should be noted that the condenser 8 is used as the primary deoxidizing and heating equipment for the water supplement and the water return of the whole heat recovery system, besides the exhaust steam condensing equipment of the small steam turbine 5, the exhaust steam of the small steam turbine 5 is used as the steam source of the condenser 8 for deoxidizing and heating the water supplement and the water return of the system.
The 5 steam extraction of little steam turbine of this embodiment all are used for heating moisturizing and return water, and the heat transfer difference in temperature reduces and does not have the cold end loss, and system efficiency can promote. In addition, the power and flow balance of the small steam turbine 5 are independently controlled by the adjusting system of the small steam turbine 5; in the back pressure turbine 1, the amount of steam used by the small steam turbine 5 is only a thermal load regulated by an external system, and the difficulty in controlling the operation of the back pressure turbine 1 is not increased.
In order to facilitate understanding and implementation of the present embodiment, the features of the auxiliary device, the water supply power device, and the like mentioned above are specifically illustrated, but it should be noted that the illustrated examples do not limit technical features of the present embodiment, and those skilled in the art may undoubtedly know that other examples with the same effect still belong to the protection scope of the present embodiment, and the present embodiment is not listed here.
Specifically, the above-mentioned water supply power device comprises a water supply pump 6 and a water delivery pump 7, and the small steam engine 5 drives the water supply pump 6. The auxiliary device comprises a high-pressure heater I2, a high-pressure heater II 3, a high-pressure deaerator 4, a shaft seal cooler 9 and a boiler.
As can be seen from fig. 1, the connection relationship between the components is specifically as follows: the high-pressure heater I2 and the high-pressure heater II 3 are connected to the back pressure turbine 1 through a regenerative steam pipeline, and the steam inlets of the high-pressure deaerator 4 and the small steam turbine 5 are connected to the steam exhaust end of the back pressure turbine 1. The steam inlet of the condenser 8 is connected to the steam exhaust end of the small steam turbine 5. The condenser 8 is used as a steam discharging and condensing device of the small steam turbine 5, and is also used as a primary deoxidizing and heating device for water replenishing and returning of the whole thermodynamic system. The heat recovery system is also provided with an auxiliary steam source which is connected to the steam inlet end of the condenser 8; the auxiliary steam source is taken from the exhaust steam and/or the service steam of the back pressure steam turbine 1. And, the pipeline of the auxiliary steam source is provided with a regulating valve 10. The condenser 8 is a jet condenser, and preferably, the condenser 8 operates in a constant pressure mode.
In practical use, the connection position of the steam inlet of the small steam turbine 5 can be adjusted according to the thermodynamic balance calculation requirement of the regenerative system, and the steam inlet of the small steam turbine can be connected to the exhaust end or the through-flow stage of the back pressure steam turbine 1.
When the system is in specific operation, water supplementing and returning pass through a shaft seal cooler 9, then enter a condenser 8 for heating and preliminary deoxidization, then are sent to a high-pressure deoxidization device 4 for further deoxidization and heating through a water delivery pump 7, are sent into a high-pressure heater II 3 and a high-pressure heater I2 for heating in sequence through a water supply pump 6 after deoxidization again, and are sent into a boiler after water supply and heating to generate main steam with rated parameters. The main steam enters the back pressure steam turbine 1 to do work and provides regenerative steam for the high-pressure heater I2, the high-pressure heater II 3 and the high-pressure deaerator 4; the exhaust steam of the back pressure turbine 1 is supplied to a heat consumer through a heat network and provides steam to the small steam turbine 5. The exhaust steam of the small steam turbine 5 is used as a steam source of the condenser 8 and is used for primary deoxygenation and heating of system water supplement and return water. Enough water storage space is reserved in the high-pressure deaerator 4 and the condenser 8 and used for increasing the dynamic balance capacity of the system.
The design pressure of the condenser 8 is adjusted, so that the power and the flow of the feed pump 6 can meet the requirements of the system at the same time. When the thermodynamic scheme is designed, because the exhaust steam of the small steam turbine 5 is used for water supplement and water return of a heating system, the exhaust steam pressure of the small steam turbine 5 is divided by the pressure loss of a pipeline, namely the pressure of the condenser 8, when the miscellaneous items such as shaft seal main pipe overflow entering the condenser 8 are ignored, the steam consumption of the condenser 8, namely the exhaust steam consumption of the small steam turbine 5, and the thermodynamic equilibrium calculation needs to be solved by the following formula:
qt-small steam turbine steam quantity
Nt-small steam turbine power
Steam quantity for Qd-condenser deoxygenation and heating
Delta Ht-actual enthalpy drop of small steam turbine
Ht' -exhaust enthalpy of small steam turbine
Hw-system water replenishing and backwater flow enthalpy value
Hw-enthalpy value of outlet water of condenser
Qw-system water replenishing and water returning flow
Qw' -condenser water flow
The method comprises the following specific implementation steps: the back pressure turbine 1 needs to supply 694.1t/h of steam with pressure of 0.9MPa.a and temperature of 176 ℃ to the outside, and all exhausted steam of the small turbine 5 with 100% capacity enters the jet condenser 8 for water supplement and return of a heating system. The technical scheme (parameters) of the back pressure turbine 1 and the small turbine 5 are as follows:
therefore, the design is carried out by combining specific heat supply requirements, and the content of the scheme can be completely realized.
To sum up, the 5 steam exhausts of little steam turbine of this scheme are all used for heating moisturizing and backwater, and the heat transfer difference in temperature reduces and do not have the cold junction loss, and system efficiency can promote, can solve the too big moisturizing of active service back pressure steam turbine 1 because of the heat supply steam exhaust that adopts higher parameter heats the moisturizing and brings
And (4) loss. In addition, the scheme does not need to carry out additional monitoring on the overflowing steam quantity and the thrust of the back pressure turbine 1 when the unit is started and stopped and operates under variable working conditions, the parameter regulating quantity is reduced, and the operation regulation is more convenient. In addition, the power and flow balance of the small steam turbine 5 are independently controlled by the adjusting system of the small steam turbine 5; in the back pressure turbine 1, the amount of steam used by the small steam turbine 5 is only a thermal load regulated by an external system, and the difficulty in controlling the operation of the back pressure turbine 1 is not increased. The system adopts two-stage thermal power deoxidization for 1 group of soda system of back pressure turbine that the moisturizing volume is great deoxidization effect is better, and equipment security can improve. With the continuous improvement of the parameters and the capacity of the back pressure turbine 1, the regenerative system designed by the scheme can obtain better economic benefits and meet the development trend and the technical requirements of the industry.
Example two
When the power and the flow of the small turbine 5 do not meet the requirements of the system, and the design pressure of the condenser 8 is unreasonable, so that the equipment cost is increased, the operation is difficult or the system efficiency is reduced, the scheme of the embodiment can be adopted for optimization. The embodiment is a further improvement of the first embodiment, and the main improvement is that the back pressure turbine 1 heat recovery system further comprises a low-pressure heater i 11 respectively connected with the water supply power device and the auxiliary device, and the low-pressure heater i 11 is further connected to the small turbine 5 through a heat recovery pipeline; and the low-pressure heater I11 is connected with a bypass regulating valve 12 in parallel, and the quantity of the regenerative steam of the low-pressure heater I11 is regulated by bypassing partial water side flow of the low-pressure heater I11.
As shown in fig. 2, for example, a low-pressure heater i 11 is connected to the water delivery pump 7 and the high-pressure deoxygenator 4, and the low-pressure heater i 11 is also connected to the small steam engine 5 through a regenerative pipeline.
The connection relationship among the components in the figure is specifically as follows: the high-pressure heater I2 and the high-pressure heater II 3 are connected to the back pressure turbine 1 through a backheating steam pipeline, a steam inlet of the small steam turbine 5 is connected to a certain through flow stage of the back pressure turbine 1, and then the high-pressure deaerator 4 is connected to a steam exhaust end of the back pressure turbine 1. The heat recovery system is also provided with an auxiliary steam source, and the auxiliary steam source is connected to the steam inlet end of the condenser 8; the auxiliary steam source is taken from the back pressure type steam turbine 1 to exhaust steam and/or service steam. And, the pipeline of the auxiliary steam source is provided with a regulating valve 10. The steam inlet of the condenser 8 is connected to the steam exhaust end of the small steam turbine 5, the low-pressure heater I11 is connected to the rear of a certain through flow stage of the small steam turbine 5 through a regenerative pipeline, and a bypass adjusting valve 12 are arranged on the water side of the low-pressure heater I11 and used for adjusting the regenerative steam consumption of the low-pressure heater I11.
When the system is in specific operation, water supplement and return water enter the condenser 8 for heating and preliminary deoxidization after passing through the shaft seal cooler 9, then are conveyed to the low-pressure heater I11 for heating through the water conveying pump 7, then flow through the high-pressure deoxidization device 4 for further deoxidization, are conveyed into the high-pressure heater II 3 and the high-pressure heater I2 for heating in sequence through the water feeding pump 6 after being heated, and are conveyed into the boiler to generate main steam with rated parameters after being heated. The main steam enters the back pressure steam turbine 1 to do work, provides regenerative steam for the high pressure heater I2 and the high pressure heater II 3, and provides steam for the small steam turbine 5. The exhaust steam of the back pressure turbine 1 is supplied to a heat consumer through a heat supply network and supplies steam to the high pressure deaerator 4. The steam extracted from the through-flow stage of the small steam turbine 5 is supplied to the low-pressure heater I11, and the exhaust steam of the low-pressure heater is used as a steam source of the condenser 8 and is used for deoxidizing and heating water for system water supplement and return water. Compared with the scheme of the first embodiment, after the steam inlet of the small steam turbine 5 is connected to a certain through-flow stage of the back pressure steam turbine 1 with higher pressure and temperature, the enthalpy difference of inlet steam and exhaust steam of the small steam turbine 5 is increased, and if the exhaust steam flow of the small steam turbine 5 is unchanged, the power is increased along with the change of the enthalpy difference; assuming that the power required by the small steam turbine 5 is not changed, the flow rate of inlet steam and outlet steam is reduced. When the through-flow interstage extraction steam of the small steam turbine 5 is supplied to the low-pressure heater I11, and the steam discharge amount of the small steam turbine 5 required by the steam condenser 8 is not changed, the steam flow between the steam inlet of the small steam turbine 5 and the steam outlet of the low-pressure heater I11 is increased, and the power of the small steam turbine 5 is increased along with the increase of the steam flow. If the power of the small steam turbine 5 is too large during the calculation of the thermodynamic scheme and the exhaust steam quantity does not meet the requirement of the condenser 8, a low-pressure heater is not needed, and the steam inlet of the small steam turbine 5 is moved to the exhaust steam end. The matching of the power and the flow of the small turbine 5 can be changed by adjusting the design pressure of the condenser 8, so that the thermodynamic balance of the system is met. A bypass regulating valve 12 is provided for improving the regulation of the transient power of the small steam turbine 5. When the instantaneous power of the small steam turbine 5 needs to be increased, the bypass regulating valve 12 is opened to be large, system water supplement and return water flow to the high-pressure deaerator 4 through a bypass, the required regenerative steam extraction amount of the low-pressure heater I11 is reduced, and the power of the small steam turbine 5 is increased in a short time; and vice versa.
Besides the effect of the first embodiment, the scheme of the embodiment has the advantages that the through-flow capacity of the small steam turbine 5 is correspondingly increased after the small steam turbine 5 is provided with the low-pressure heater I11, so that the through-flow efficiency of the small steam turbine 5 is improved; the proportion of the regenerative steam extracted from the small steam turbine 5 in the through-flow is large, the power of the small steam turbine 5 can be changed in a large range by changing the water side flow of the low-pressure heater I11, and the effect of improving the load regulation capacity is strong. With the continuous improvement of the parameters and the capacity of the back pressure turbine 1, the regenerative system designed by the scheme can obtain better economic benefits and meet the development trend and the technical requirements of the industry.
EXAMPLE III
The third embodiment is a further improvement of the first embodiment, and as shown in fig. 3, the main improvement is that the back pressure turbine 1 is a reheat back pressure turbine 1. The reheating steam turbine is characterized in that steam which is used for completing work of a high pressure cylinder of the steam turbine is sent back to a boiler reheater to be heated to a temperature close to the temperature of new steam, and then the steam is returned to a medium-low pressure cylinder of the steam turbine to continue to do work. The steam adopts intermediate reheating, thereby not only reducing the exhaust steam humidity of the steam turbine, but also improving the working conditions of the last stage of blades of the steam turbine and improving the relative internal efficiency of the steam turbine. The difference of the reheating back pressure turbine and the non-reheating back pressure turbine is that the temperature and the pressure of steam after passing through a reheater are changed, the reheating back pressure turbine is suitable for special requirements of partial petrochemical industry and coal chemical industry on steam parameters, and is suitable for projects with multi-stage heat supply requirements.
The above-mentioned reheat back pressure turbine 1 comprises a high pressure module 15 and an intermediate pressure module 14; the high-voltage module 15 and the medium-voltage module 14 are respectively connected with the auxiliary device; the small steam turbine 5 is connected to the intermediate-pressure module 14 through a heat recovery steam pipeline; the heat recovery system also comprises a low-pressure heater I11 connected with the auxiliary device and a low-pressure heater II 13 connected with the low-pressure heater I11, and the other end of the low-pressure heater II 13 is connected with the water supply power device; the low-pressure heater I11 and the low-pressure heater II 13 are also connected to the small steam turbine 5 through a regenerative pipeline; and the low-pressure heater I11 and the low-pressure heater II 13 are connected with a bypass regulating valve 12 in parallel, and the quantity of the regenerative steam of the low-pressure heater I11 and the low-pressure heater II 13 is regulated.
Referring to fig. 3, the above-mentioned water supply power device comprises a water supply pump 6 and a water delivery pump 7, wherein the small steam engine 5 drives the water supply pump 6. The auxiliary device comprises a high-pressure heater I2, a high-pressure heater II 3, a high-pressure deaerator 4, a shaft seal cooler 9 and a boiler.
The high-pressure heater I2 is connected to the high-pressure module 15 through a regenerative steam pipeline, and the high-pressure heater II 3, the high-pressure deaerator 4 and the small steam turbine 5 are connected to the medium-pressure module 14 through regenerative steam pipelines. The steam inlet of the condenser 8 is connected to the steam exhaust end of the small steam turbine 5, and the low-pressure heater I11 and the low-pressure heater II 13 are connected to the rear of a certain flow stage of the small steam turbine 5 through a heat return pipeline. And bypass adjusting valves 12 are arranged on the water sides of the low-pressure heater I11 and the low-pressure heater II 13 and are used for adjusting the quantity of regenerative steam of the low-pressure heater I11 and the low-pressure heater II 13. When the system is in operation, the water supplement and the backwater enter the condenser 8 for heating and preliminary deoxygenation after passing through the shaft seal cooler 9, are sent to the low-pressure heater I11 and the low-pressure heater II 13 for heating step by step through the water delivery pump 7, then flow through the high-pressure deoxygenator 4 for further deoxygenation and heating, are sent to the high-pressure heater II 3 and the high-pressure heater I2 for heating in sequence through the water supply pump 6, and are sent to the boiler for generating main steam with rated parameters after being heated. The main steam enters the high-pressure module 15 to do work and provides regenerative steam for the high-pressure heater I2. After being reheated by the boiler, the exhaust steam of the high-pressure module 15 of the back-pressure turbine 1 enters the medium-pressure module 14 of the back-pressure turbine 1 to do work, provides regenerative steam for the high-pressure heater II 3 and the high-pressure deaerator 4, provides steam for the small steam turbine 5, and the exhaust steam of the medium-pressure module 14 serves as an auxiliary steam source of the condenser 8 and supplies steam to heat users through the heat supply network 2. The through-flow interstage steam extraction of the small steam turbine 5 supplies a low-pressure heater I11 and a low-pressure heater II 13, and the exhaust steam of the small steam turbine is used as a steam source of the condenser 8 and is used for system water supplement and backwater deoxidization heating. The method for adjusting the power and the flow of the small steam turbine 5 and the method for using the bypass adjusting valve 12 and the adjusting valve 10 are the same as those described in the second embodiment.
The scheme of this embodiment has the effect in the second embodiment, adopts high-power reheat type backpressure machine, and it can play more big benefit in the system, more fits practical use.
Example four
The present embodiment provides a method for designing a thermodynamic balance of a regenerative system, where the method includes the regenerative system described in embodiment 1, and includes the following steps:
s1, presetting the backpressure of a small turbine as Pkt to obtain the effluent enthalpy of the condenser, and calculating the steam quantity A required by deoxygenation and boiling according to the heat balance of the condenser by combining the inlet enthalpy and the inlet flow of the condenser;
s2, obtaining enthalpy drop of the small steam turbine according to the steam inlet pressure temperature and the backpressure of the small steam turbine, and calculating by combining the power of a feed pump to obtain the steam inlet amount B required by the small steam turbine;
s3, iteratively solving the backpressure of the small steam turbine to obtain Pkt, enabling A and B to be equal, comparing whether the difference value of A and B is within an allowable range, if the difference value is not within the allowable range and A is larger than B, reducing the preset backpressure Pkt, and repeatedly executing steps S1 and S2; if the difference is not within the allowable range and A is smaller than B, increasing Pkt and repeatedly executing the steps S1 and S2;
s4, judging whether the difference value between the backpressure Pkt obtained after iteration and the preset backpressure Pkt is within an allowable range, if the difference value is not within the allowable range and the Pkt is greater than the Pkt, moving the steam inlet of the small steam turbine forward, increasing the inlet pressure and the inlet temperature of the small steam turbine, and repeatedly executing the step S1; if the difference is not within the allowable range and Pkt is less than Pkt, the steam inlet of the small steam turbine is moved backward, the pressure and temperature at the inlet of the small steam turbine are reduced, and step S1 is repeatedly performed. The design pressure of the condenser is increased due to the overhigh back pressure of the small steam turbine, so that the cost is increased, and the unsafe operation and the poorer economical efficiency are caused due to the overlow back pressure of the small steam turbine.
By using the heat recovery system and the design method in the embodiment, the same effect as that of embodiment 1, 2 or 3 can be achieved, and the description is not repeated here.
EXAMPLE five
The present embodiment provides another design method for thermodynamic equilibrium of a regenerative system, where the method includes the regenerative system described in embodiment 1, and the first calculation method includes the following steps:
s1, setting the backpressure Pkt of the small turbine to obtain the effluent enthalpy of the condenser, and calculating the steam quantity A required by deoxygenation and boiling according to the heat balance of the condenser by combining the inlet enthalpy and the inlet flow of the condenser;
s2, calculating to obtain the enthalpy drop of the small steam turbine according to the steam inlet pressure, temperature and back pressure of the small steam turbine, and calculating to obtain the power B of the small steam turbine by combining the steam quantity A;
s3, comparing whether the difference value between the power B of the small steam turbine and the power of the water feeding pump is within an allowable range, if the difference value is not within the allowable range and the power B of the small steam turbine is greater than the power of the water feeding pump, moving the steam inlet of the small steam turbine backwards, reducing the pressure and the temperature of the inlet of the small steam turbine, and repeatedly executing the step S2; if the difference value is not in the allowable range and the power B of the small steam turbine is less than the power of the feed pump, the steam inlet of the small steam turbine is moved forward, the pressure temperature of the inlet of the small steam turbine is increased, or a regenerative steam extraction stage is additionally arranged between the through flow stages of the small steam turbine, and the step S2 is repeatedly executed.
The power increased by adding the regenerative extraction steam can be used for supplementing the deficiency of the power of the small steam turbine. It should be noted that, when the difference between the small steam turbine power B and the feed water pump power is within the allowable range, the loss in the power transmission process is ignored, the numerical value of the allowable range may be set by a technician according to an actual situation, and when the numerical value of the allowable range is smaller, it may be understood that the difference between the small steam turbine power B and the feed water pump power is not large.
By using the heat recovery system and the design method in the embodiment, the same effect as that of embodiment 1, 2 or 3 can be achieved, and the description is not repeated here.
While preferred embodiments of the present invention have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, it is intended that the appended claims be interpreted as including preferred embodiments and all such alterations and modifications as fall within the scope of the invention. The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, it should be noted that any modifications, equivalents and improvements made within the spirit and principle of the present invention should be included in the scope of the present invention.
Claims (10)
1. The utility model provides a back pressure turbine system of heating back with little steam turbine, this system of heating back includes back pressure turbine at least, with what back pressure turbine was connected is used for give the moisturizing of system of heating back and the auxiliary device of return water heating, deoxidization, for system's moisturizing and return water provide power make it be in the circulating flow's among the system of heating back feedwater power device, its characterized in that: the heat recovery system also comprises a small turbine connected with the back pressure turbine and used for driving the water supply power device, and a condenser connected with the small turbine; and the exhaust steam of the small steam turbine is used as a steam source of the condenser and is used for deoxidizing and heating water supply and return water of the system.
2. The system of claim 1, wherein the heat recovery system comprises: the back pressure turbine heat regeneration system also comprises a low-pressure heater I which is respectively connected with the water supply power device and the auxiliary device, and the low-pressure heater I is also connected to the small turbine through a heat regeneration pipeline;
and the low-pressure heater I is connected with a bypass regulating valve in parallel to regulate the regenerative steam dosage of the low-pressure heater I.
3. The system of claim 1, wherein the heat recovery system comprises: the back pressure turbine is a reheating back pressure turbine.
4. A back pressure turbine recuperator system with small turbine as in claim 3, wherein: the reheating back pressure turbine comprises a high-pressure module and a medium-pressure module; the high-voltage module and the medium-voltage module are respectively connected with the auxiliary device; the small steam turbine is connected to the medium-pressure module through a regenerative steam pipeline;
the heat regenerative system also comprises a low-pressure heater I connected with the auxiliary device and a low-pressure heater II connected with the low-pressure heater I, and the other end of the low-pressure heater II is connected with the water supply power device; the low-pressure heater I and the low-pressure heater II are also connected to the small steam turbine through a heat return pipeline;
and the low-pressure heater I and the low-pressure heater II are connected with a bypass regulating valve in parallel, and the quantity of regenerative steam of the low-pressure heater I and the low-pressure heater II is regulated.
5. The back pressure turbine regenerative system with a small steam turbine according to any one of claims 1 to 4, wherein: the water supply power device comprises a water supply pump and a water delivery pump, and the small steam engine drives the water supply pump.
6. The back pressure turbine regenerative system with a small steam turbine according to any one of claims 1 to 4, wherein: the condenser is an injection type condenser.
7. The back pressure turbine regenerative system with a small steam turbine according to any one of claims 1 to 4, wherein: the heat recovery system is provided with an auxiliary steam source, and the auxiliary steam source is connected to the steam inlet end of the condenser; the pipeline of the auxiliary steam source is provided with an adjusting valve;
and the auxiliary steam source is taken from the exhaust steam of the back pressure turbine and/or the service steam.
8. A back pressure turbine regenerative system with small turbines according to claims 1-4 characterized by: and the steam inlet of the small steam turbine is connected to the steam exhaust end or the through flow interstage of the back pressure steam turbine.
9. A method of thermodynamic equilibrium design, characterized in that it comprises a regenerative system according to any of claims 1 to 4, comprising the following steps:
s1, presetting the backpressure of a small turbine as Pkt to obtain the effluent enthalpy of the condenser, and calculating the steam quantity A required by deoxygenation and boiling according to the heat balance of the condenser by combining the inlet enthalpy and the inlet flow of the condenser;
s2, obtaining enthalpy drop of the small steam turbine according to the steam inlet pressure temperature and the backpressure of the small steam turbine, and calculating by combining the power of a feed pump to obtain the steam inlet amount B required by the small steam turbine;
s3, iteratively solving the backpressure Pkt of the small steam turbine to enable the A and the B to be equal, comparing whether the difference value of the A and the B is within an allowable range, if the difference value is not within the allowable range and the A is larger than the B, reducing the preset backpressure Pkt, and repeatedly executing the steps S1 and S2; if the difference is not within the allowable range and A is smaller than B, increasing Pkt and repeatedly executing the steps S1 and S2;
s4, judging whether the difference value between the backpressure Pkt obtained after iteration and the preset backpressure Pkt is within an allowable range, if the difference value is not within the allowable range and the Pkt is greater than the Pkt, moving the steam inlet of the small steam turbine forward, increasing the inlet pressure and the temperature of the small steam turbine, and repeatedly executing the step S1; if the difference is not within the allowable range and Pkt is less than Pkt, the steam inlet of the small steam turbine is moved backward, the pressure and temperature at the inlet of the small steam turbine are reduced, and step S1 is repeatedly performed.
10. A method of thermodynamic equilibrium design, characterized in that it comprises a regenerative system according to any of claims 1 to 4, comprising the following steps:
s1, setting the backpressure Pkt of the small turbine to obtain the effluent enthalpy of the condenser, and calculating the steam quantity A required by deoxygenation and boiling according to the heat balance of the condenser by combining the inlet enthalpy and the inlet flow of the condenser;
s2, calculating to obtain the enthalpy drop of the small steam turbine according to the steam inlet pressure temperature and the backpressure of the small steam turbine, and calculating to obtain the power B of the small steam turbine by combining the steam quantity A;
s3, comparing whether the difference value between the power B of the small steam turbine and the power of the water feeding pump is within an allowable range, if the difference value is not within the allowable range and the power B of the small steam turbine is greater than the power of the water feeding pump, moving the steam inlet of the small steam turbine backwards, reducing the pressure and the temperature of the inlet of the small steam turbine, and repeatedly executing the step S2; if the difference value is not in the allowable range and the power B of the small steam turbine is smaller than the power of the feed pump, the steam inlet of the small steam turbine is moved forward, the pressure temperature of the inlet of the small steam turbine is increased, or regenerative steam extraction is additionally arranged between through flow stages of the small steam turbine, and the step S2 is repeatedly executed.
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