CN204402598U - Join the double reheat supercharging steam turbine thermodynamic system of backpressure small turbine - Google Patents
Join the double reheat supercharging steam turbine thermodynamic system of backpressure small turbine Download PDFInfo
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- CN204402598U CN204402598U CN201520018504.6U CN201520018504U CN204402598U CN 204402598 U CN204402598 U CN 204402598U CN 201520018504 U CN201520018504 U CN 201520018504U CN 204402598 U CN204402598 U CN 204402598U
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Abstract
The utility model discloses a kind of double reheat supercharging steam turbine thermodynamic system of joining backpressure small turbine.Double reheat supercharging steam turbine thermodynamic system comprises: high parameter Turbo-generator Set, comprises ultra-high pressure cylinder and the first generator; Low parameter Turbo-generator Set, comprises high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator; Backpressure small turbine system, comprises backpressure small turbine and driven device; And heat regenerative system, comprise the first high-pressure heater, oxygen-eliminating device and low-pressure heater and for the vapour condenser of thermodynamic cycle, condensate pump and feed water pump group.Vapor communication before backpressure small turbine steam inlet pipe and double reheat supercharging steam turbine system reheating, utilizes the steam before double reheat supercharging steam turbine system reheating as vapour source, and after backpressure small turbine acting, steam discharge heat supply or steam discharge backheat are to thermodynamic system.Thermodynamic system of the present utility model can reduce energy consumption, reduces cost, improves efficiency of thermal cycle simultaneously.
Description
Technical field
The utility model relates to double reheat supercharging steam turbine thermodynamic system, is specifically related to the double reheat supercharging steam turbine thermodynamic system of joining backpressure small turbine in steam power plant.
Background technique
Existing thermal power generation unit, can be divided into subcritical, overcritical and ultra supercritical according to steam inlet condition from low to high.Steam inlet condition is higher, and the generating thermal efficiency is higher.
20th century 80, the nineties are built, so far still at long playing thermal power generation unit, limit by its construction year generation technique, the Turbo-generator Set of many employings subcritical (canonical parameter 16.7MPa, 538 DEG C) low parameter, net coal consumption rate is about 320g/kW.h.In recent years the new thermal power generation unit built, the Turbo-generator Set of many employings overcritical (canonical parameter 24.2MPa, 566 DEG C), ultra supercritical (canonical parameter 25 ~ 28MPa, 600 DEG C) high parameter, supercritical unit net coal consumption rate is about 305g/kW.h, and extra-supercritical unit net coal consumption rate is about 290g/kW.h.
In order to improve the subcritical efficiency waiting low parameter thermal power generation unit, prior art proposes the preposition steam turbine technology of a kind of double reheat, and the heat flow diagrams of the prior art is see accompanying drawing 1-3.
Fig. 1 is double reheat supercharging steam turbine thermodynamic system, to low parameter steam turbine, before series connection set up ultra-high pressure cylinder, by improving fired power generating unit main vapour parameter, and adopting double reheat, reaching the object improving overall efficiency of thermal cycle.
Fig. 2 increases one-level more the drawing gas and corresponding high-pressure heater of high pressure on the basis of Fig. 1, provides further and improves overall efficiency of thermal cycle.
Fig. 3 increases back pressure to draw gas cylinder on the basis of Fig. 2, improves the generating thermal efficiency further, reduces net coal consumption rate, and many times increase unit outputs simultaneously.
Draw gas cylinder (BEST) and ultra-high pressure cylinder of back pressure can be a point cylinder, also can be conjunction cylinder.
Final stage hyperbaric heating vapour source can from ultra-high pressure cylinder steam discharge/draw gas, and also can to draw gas cylinder from back pressure.
Feed-water pump can arrange the high feedwater main pump of lift, also can arrange the low feedwater main pump of lift and feed water booster pump.
In the heat regenerative system of prior art 1 and 2 (being respectively Fig. 1 and Fig. 2), the steam of high-pressure heater, oxygen-eliminating device, low-pressure heater, feed water pump steam turbine is provided by original the drawing gas of low parameter steam turbine.
In the heat regenerative system of prior art 3 (Fig. 3), the steam of high-pressure heater, oxygen-eliminating device is provided by the back pressure cylinder that draws gas.
But station service power consumption rate is higher in prior art, during steam discharge heat supply, restriction loss is large, affects efficiency of thermal cycle.Therefore, can station service power consumption rate be reduced in the urgent need to one, reduce restriction loss, improve the thermodynamic system of efficiency of thermal cycle.
Model utility content
The utility model is for the above-mentioned situation of existing thermodynamic system, on the basis of existing double reheat supercharging steam turbine thermodynamic system, configuration backpressure small turbine, extracting high-temperature high pressure steam in thermodynamic system, after backpressure small turbine acting, steam discharge heat supply or steam discharge backheat are to thermodynamic system, and backpressure small turbine can be used for driving all kinds of pumping unit.Be to reduce station service power consumption rate the order of technical solutions of the utility model, during steam discharge heat supply steam discharge parameter and heat user desired parameters comparatively close, heat supply restriction loss can be reduced; Simultaneously when during backpressure small turbine vapour source is from the thermodynamic system before high-pressure cylinder, can unit output be improved, every heat supply 100t/h, unit output can be increased and be about 7MW.Further reduction net coal consumption rate, increases return on investment.
For achieving the above object, the utility model provides a kind of double reheat supercharging steam turbine thermodynamic system of joining backpressure small turbine, and described thermodynamic system comprises:
(1) high parameter Turbo-generator Set, comprises ultra-high pressure cylinder and the first generator;
(2) low parameter Turbo-generator Set, this low parameter Turbo-generator Set is connected with described high parameter Turbo-generator Set, comprises high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator;
(3) backpressure small turbine system, comprises backpressure small turbine and driven device;
(4) backheat and circulation system, this backheat and circulation system are connected with low parameter Turbo-generator Set with described high parameter Turbo-generator Set, and are provided with (i) for the first high-pressure heater of backheat, oxygen-eliminating device and low-pressure heater and (ii) for the vapour condenser of thermodynamic cycle, condensate pump and feed water pump group.
In another preference, the steam inlet pipe of described backpressure small turbine is connected with the exhaust steam pipe of any one appropriate device being selected from lower group: low-temperature reheater, reheater, ultra-high pressure cylinder and high-pressure cylinder.
In another preference, described high parameter Turbo-generator Set is also provided with back pressure and draws gas cylinder, and the described back pressure cylinder admission end that draws gas is connected with the steam output end of described ultra-high pressure cylinder.
In another preference, draw gas draw gas (1,2,3,4) of cylinder of described back pressure directly enter heat regenerative system, for heated feed water or water of condensation.
In another preference, described ultra-high pressure cylinder and back pressure draw gas cylinder close cylinder.
In another preference, between the first high-pressure heater and described ultra-high pressure cylinder, be provided with economizer and superheater successively.
In another preference, the steam outlet pipe of the first high-pressure heater is connected with the steam inlet pipe of economizer.
In another preference, between the first high-pressure heater and economizer, be also provided with the second high-pressure heater.
In another preference, the steam inlet pipe of the second high-pressure heater is connected with the steam outlet pipe of ultra-high pressure cylinder.
In another preference, described feed water pump group comprises feedwater main pump.
In another preference, described feed water pump group comprises feedwater main pump and feed water booster pump.
In another preference, between described high-pressure cylinder and intermediate pressure cylinder, be provided with the second reheater.
In another preference, the steam inlet pipe of the second reheater is connected with the steam outlet pipe of high-pressure cylinder, and the steam outlet pipe of the second reheater is connected with the steam inlet pipe of intermediate pressure cylinder.
In another preference, the exhaust steam pipe of described backpressure small turbine is connected with heat user pipeline.
In another preference, described backpressure small turbine and driven device pass through coupling of shaft system.
In another preference, described driven device is pumping unit.
In another preference, described driven device is driven by backpressure small turbine.
In another preference, between described ultra-high pressure cylinder and high-pressure cylinder, be also provided with the first reheater.
In another preference, the steam inlet pipe of the first reheater is connected with the steam outlet pipe of ultra-high pressure cylinder and the steam outlet pipe of the first reheater is connected with the steam inlet pipe of high-pressure cylinder.
In another preference, the steam inlet pipe of described backpressure small turbine is between ultra-high pressure cylinder and the first reheater.
In another preference, described high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator are coaxially arranged.
In another preference, described condensate pump, low-pressure heater, oxygen-eliminating device, feed water pump group and high-pressure heater are coaxially arranged.
Accompanying drawing explanation
Fig. 1-3 is flow charts of the double reheat supercharging steam turbine thermodynamic system of prior art.
Fig. 4 is the double reheat supercharging steam turbine thermodynamic system flow chart of joining backpressure small turbine shown in the utility model embodiment 1.
Fig. 5 is the double reheat supercharging steam turbine thermodynamic system flow chart of joining backpressure small turbine shown in the utility model embodiment 2.Wherein, the thermal source of newly-increased high-pressure heater is from ultra-high pressure cylinder.
Fig. 6 is the double reheat supercharging steam turbine thermodynamic system flow chart of joining backpressure small turbine shown in the utility model embodiment 3.Wherein, draw gas cylinder and ultra-high pressure cylinder of back pressure divides cylinder.
Embodiment
Below with reference to accompanying drawing, preferred embodiment of the present utility model is described in detail, understands the purpose of this utility model, feature and advantage so that clearer.It should be understood that embodiment shown in the drawings is not the restriction to the utility model scope, and the connotation just in order to technical solutions of the utility model are described.
Term
Back pressure type small turbine: steam discharge is called condensed steam type steam turbine to the steam turbine of the vacuum vapour condenser lower than large vapour pressure, steam discharge is called back-pressure turbine to higher than the piping of large vapour pressure or the steam turbine of heat exchanger.In the utility model, " back pressure turbine ", " back pressure type small turbine ", " the little machine of back pressure " are same statement, all refer to that steam discharge arrives the steam turbine higher than atmospheric piping or heat exchanger.
Steam discharge heat supply: high temperature and high pressure steam through backpressure small turbine acting after steam discharge parameter and heat user desired parameters comparatively close, for heat supply.
Steam discharge backheat: high temperature and high pressure steam is after backpressure small turbine acting, and steam discharge is back to thermodynamic system.
Cylinder: the through-flow constituent element of steam turbine, usual pressing force is divided into: ultra-high pressure cylinder, high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder.
Reheating: the steam having done part merit in steam turbine is drawn and again heats, then lead back steam turbine and continue acting.This mode is called reheating.By rational reheating, can exhaust steam moisture be reduced, improve efficiency of thermal cycle.
Supercharging: to low parameter steam turbine, the cylinder of high parameter of connecting above, to improve overall efficiency of thermal cycle, lifting unit generated output.
Draw gas: extract steam out from the intergrade before turbine discharge.
Embodiment 1
Fig. 4 illustrates the double reheat supercharging steam turbine thermodynamic system flow chart of joining backpressure small turbine in the utility model embodiment 1.As shown in the figure, system flow is as follows:
Ultra-high pressure cylinder is entered by boiler superheater high parameter main steam out, acting rear portion steam discharge enters reheater 1 and heats, single reheat steam after intensification enters high-pressure cylinder and continues acting, the steam discharge of high-pressure cylinder enters boiler reheater 2 and heats, double reheat steam after intensification enters intermediate pressure cylinder, intermediate pressure cylinder steam discharge after acting enters low pressure (LP) cylinder and continues acting, and the low pressure (LP) cylinder steam discharge after acting enters vapour condenser, and cooling becomes water of condensation.Steam is extracted out, as the vapour source of high-pressure heater, oxygen-eliminating device, low-pressure heater in many places from front to back from the centre of high-pressure cylinder, intermediate pressure cylinder and low pressure (LP) cylinder.
A part of steam discharge of ultra-high pressure cylinder enters backpressure small turbine, and after backpressure small turbine acting, steam discharge heat supply or steam discharge backheat are to thermodynamic system.The vapour source of backpressure small turbine can be any suitable location in heat regenerative system according to heat user parameter or backheat parameter and driven device power, as: hot arc/cold section, secondary hot arc/cold section, low-temperature reheater outlet, each cylinder extraction opening etc.Backpressure small turbine can be used for driving all kinds of pumping unit.
Vapour condenser water of condensation is out boosted through condensate pump, enters low-pressure heater heating, enters oxygen-eliminating device heating subsequently and deoxygenation.Oxygen-eliminating device feedwater out, through feed water pump group (usually by small turbine drive) boosting, enters high-pressure heater heating, finally enters boiler economizer, carry out thermodynamic cycle.
Compared with the prior art shown in accompanying drawing 1, join the double reheat supercharging steam turbine thermodynamic system of backpressure small turbine: add backpressure small turbine, drive all kinds of pumping unit, reduce station service power consumption rate; When steam discharge heat supply, reduce the restriction loss that direct heating brings; The discharge capacity of ultra-high pressure cylinder increases, and the increase of exerting oneself of corresponding generator 1, therefore improves raising efficiency of thermal cycle.
Embodiment 2
Fig. 5 illustrates the double reheat supercharging steam turbine thermodynamic system flow chart of joining backpressure small turbine in the utility model embodiment 2.
The technological scheme of the utility model embodiment 2 is similar to embodiment 1 system flow, and difference is: newly-increased one of final stage highly adds, and it draws gas to draw from ultra-high pressure cylinder steam discharge and connects, and the discharge capacity of ultra-high pressure cylinder increases, the increase of exerting oneself of corresponding generator 1.
Embodiment 3
Fig. 6 illustrates the double reheat supercharging steam turbine thermodynamic system flow chart of joining backpressure small turbine in the utility model embodiment 3.
The technological scheme of the utility model embodiment 3 is similar to embodiment 2 system flow, difference is: embodiment 3 increases back pressure and to draw gas cylinder (BEST) on the basis of embodiment 2, the further raising generating thermal efficiency, reduction net coal consumption rate, many times increase unit outputs simultaneously.
Effect
The utility model is on the basis of existing double reheat supercharging steam turbine thermodynamic system, configuration backpressure small turbine, extracting high-temperature high pressure steam in thermodynamic system, after backpressure small turbine acting, steam discharge heat supply or steam discharge backheat are to thermodynamic system, and backpressure small turbine can be used for driving all kinds of pumping unit.Be order reduce station service power consumption rate, during steam discharge heat supply, steam discharge parameter and heat user desired parameters comparatively close, heat supply restriction loss can be reduced.Simultaneously when during backpressure small turbine vapour source is from the thermodynamic system before high-pressure cylinder, can unit output be improved, every heat supply 100t/h, unit output can be increased and be about 7MW.Further reduction net coal consumption rate, increases return on investment.
Below described preferred embodiment of the present utility model in detail, but it will be appreciated that, after having read above-mentioned instruction content of the present utility model, those skilled in the art can make various changes or modifications the utility model.These equivalent form of values fall within the application's appended claims limited range equally.
Description of reference numerals:
A1: high-pressure cylinder
A2: intermediate pressure cylinder
A3: low pressure (LP) cylinder
A4: ultra-high pressure cylinder
B1: vapour condenser
B2: condensate pump
B3: low-pressure heater (multistage)
B4: oxygen-eliminating device
B5: feed water pump group
B6: high-pressure heater (multistage)
C1: reheater 1
C2: reheater 2
D1: economizer
D2: superheater
D3: newly-increased high-pressure heater
H1: small turbine
H2: driven device
G1: generator 1
G2: generator 2
Claims (9)
1. join a double reheat supercharging steam turbine thermodynamic system for backpressure small turbine, it is characterized in that, described thermodynamic system comprises:
(1) high parameter Turbo-generator Set, comprises ultra-high pressure cylinder and the first generator;
(2) low parameter Turbo-generator Set, this low parameter Turbo-generator Set is connected with described high parameter Turbo-generator Set, comprises high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator;
(3) backpressure small turbine system, comprises backpressure small turbine and driven device;
(4) backheat and circulation system, this backheat and circulation system are connected with low parameter Turbo-generator Set with described high parameter Turbo-generator Set, and are provided with for the first high-pressure heater of backheat, oxygen-eliminating device and low-pressure heater and for the vapour condenser of thermodynamic cycle, condensate pump and feed water pump group.
2. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, the steam inlet pipe of described backpressure small turbine is connected with the exhaust steam pipe of the device being selected from lower group: low-temperature reheater, reheater, ultra-high pressure cylinder and high-pressure cylinder.
3. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, the exhaust steam pipe of described backpressure small turbine is connected with heat user pipeline.
4. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, described backpressure small turbine and driven device pass through coupling of shaft system.
5. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, described driven device is driven by backpressure small turbine.
6. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, is characterized in that, be also provided with the first reheater between described ultra-high pressure cylinder and high-pressure cylinder.
7. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, the steam inlet pipe of described backpressure small turbine is between ultra-high pressure cylinder and the first reheater.
8. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, described high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator are coaxially arranged.
9. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, it is characterized in that, described condensate pump, low-pressure heater, oxygen-eliminating device, feed water pump group and high-pressure heater are coaxially arranged.
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| CN104948244A (en) * | 2015-06-29 | 2015-09-30 | 华北电力大学（保定） | Supercritical thermal power generation system constructed through subcritical thermal power generation system |
| CN105042666A (en) * | 2015-06-26 | 2015-11-11 | 中国能源建设集团广东省电力设计研究院有限公司 | Wide-load heat supply energy saving system of back pressure type small turbine driving induced draft fan |
| CN106247312A (en) * | 2016-08-30 | 2016-12-21 | 山东电力工程咨询院有限公司 | A kind of extra-supercritical unit double reheat two-shipper backheat thermodynamic system without deaerator |
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| CN108104887A (en) * | 2017-12-07 | 2018-06-01 | 中国神华能源股份有限公司 | The therrmodynamic system of double reheat |
| CN108643980A (en) * | 2018-04-17 | 2018-10-12 | 章礼道 | Ultra-high pressure cylinder and high intermediate pressure cylinder carry the double reheat power generation sets of additional backheat grade |
| CN109505672A (en) * | 2018-11-23 | 2019-03-22 | 中国大唐集团科学技术研究院有限公司火力发电技术研究院 | Two-shipper backheat electricity generation system and its increase power output method |
| CN111005775A (en) * | 2019-12-19 | 2020-04-14 | 大唐郓城发电有限公司 | 630 ℃ double reheating unit thermodynamic system |
| CN112282877A (en) * | 2020-09-27 | 2021-01-29 | 山东电力工程咨询院有限公司 | Industrial steam extraction system of double reheating unit and operation method thereof |
| CN114458404A (en) * | 2021-12-24 | 2022-05-10 | 华能秦煤瑞金发电有限责任公司 | Double-reheat steam turbine system with double back pressure machines distributed |
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| CN105042666A (en) * | 2015-06-26 | 2015-11-11 | 中国能源建设集团广东省电力设计研究院有限公司 | Wide-load heat supply energy saving system of back pressure type small turbine driving induced draft fan |
| CN104948244A (en) * | 2015-06-29 | 2015-09-30 | 华北电力大学（保定） | Supercritical thermal power generation system constructed through subcritical thermal power generation system |
| CN106247312A (en) * | 2016-08-30 | 2016-12-21 | 山东电力工程咨询院有限公司 | A kind of extra-supercritical unit double reheat two-shipper backheat thermodynamic system without deaerator |
| CN106382620A (en) * | 2016-08-30 | 2017-02-08 | 山东电力工程咨询院有限公司 | Low-pressure water supply system for steam extraction and backheating of power station unit |
| CN108104887A (en) * | 2017-12-07 | 2018-06-01 | 中国神华能源股份有限公司 | The therrmodynamic system of double reheat |
| CN108104887B (en) * | 2017-12-07 | 2020-10-16 | 中国神华能源股份有限公司 | Thermodynamic system with double reheating |
| CN108643980A (en) * | 2018-04-17 | 2018-10-12 | 章礼道 | Ultra-high pressure cylinder and high intermediate pressure cylinder carry the double reheat power generation sets of additional backheat grade |
| CN108643980B (en) * | 2018-04-17 | 2022-09-13 | 章礼道 | Ultrahigh pressure cylinder and high and medium pressure cylinder both have secondary reheating unit of additional reheat level |
| CN109505672A (en) * | 2018-11-23 | 2019-03-22 | 中国大唐集团科学技术研究院有限公司火力发电技术研究院 | Two-shipper backheat electricity generation system and its increase power output method |
| CN111005775A (en) * | 2019-12-19 | 2020-04-14 | 大唐郓城发电有限公司 | 630 ℃ double reheating unit thermodynamic system |
| CN112282877A (en) * | 2020-09-27 | 2021-01-29 | 山东电力工程咨询院有限公司 | Industrial steam extraction system of double reheating unit and operation method thereof |
| CN114458404A (en) * | 2021-12-24 | 2022-05-10 | 华能秦煤瑞金发电有限责任公司 | Double-reheat steam turbine system with double back pressure machines distributed |
| CN114458404B (en) * | 2021-12-24 | 2023-10-31 | 华能秦煤瑞金发电有限责任公司 | Double-reheat steam turbine system with double backpressure machines distributed |
| CN114810250A (en) * | 2022-04-14 | 2022-07-29 | 重庆赛迪热工环保工程技术有限公司 | Power generation thermodynamic system for reducing heat loss of steam turbine exhaust |
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