CN103806966A - Double-reheat supercharged steam turbine thermal system - Google Patents
Double-reheat supercharged steam turbine thermal system Download PDFInfo
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- CN103806966A CN103806966A CN201410096005.9A CN201410096005A CN103806966A CN 103806966 A CN103806966 A CN 103806966A CN 201410096005 A CN201410096005 A CN 201410096005A CN 103806966 A CN103806966 A CN 103806966A
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Abstract
The invention discloses a double-reheat supercharged steam turbine thermal system which is characterized in that a high parameter steam turbine generating set is provided with a back pressure steam extraction cylinder; the back pressure steam extraction cylinder and an ultrahigh pressure cylinder are set into a split or combined structure; a regeneration and double-reheat thermal cycle system is provided with a second high pressure heater for regeneration; steam extraction of the second high pressure heater is led from steam exhaust of the back pressure steam extraction cylinder. The double-reheat supercharged steam turbine thermal system disclosed by the invention further improves thermal efficiency of electricity generation, reduces power supply coal consumption, and obviously increases the unit output.
Description
Technical field
The present invention relates to a kind of double reheat supercharging steam turbine thermodynamic system, especially relate to a kind of draw gas double reheat supercharging steam turbine thermodynamic system of cylinder of back pressure that has.
Background technique
According to steam inlet condition from low to high, thermal power generation unit can be divided into subcritical, overcritical and ultra supercritical.Steam inlet condition is higher, and the generating thermal efficiency is higher.
To the thermal power generation unit that 20th century 80, the nineties build, grown working time so far, be subject to it to build age technical limitations, adopt the Turbo-generator Set of subcritical (canonical parameter 16.7MPa, 538 ℃) low parameter, the about 320g/kW.h of net coal consumption rate more.In recent years the new thermal power generation unit of building, the Turbo-generator Set that adopt overcritical (canonical parameter 24.2MPa, 566 ℃), ultra supercritical (canonical parameter 25～28MPa, 600 ℃) high parameter more, the about 305g/kW.h of supercritical unit net coal consumption rate, the about 290g/kW.h of ultra supercritical unit net coal consumption rate.
Now move the steam turbine of thermal power generation unit, conventionally formed by high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder.The initial steam pressure of subcritical (16.7MPa, 538 ℃) low parameter steam turbine is low compared with the initial steam pressure of ultra supercritical (25～28MPa, 600 ℃) high parameter steam turbine, the about 30g/kW.h of corresponding difference of coal consumption of power supply.
In order to improve this subcritical efficiency that waits low parameter thermal power generation unit, a kind of preposition steam turbine technology has been proposed both at home and abroad, the double reheat heat flow diagrams of the prior art is referring to accompanying drawing 1, for to low parameter steam turbine, set up the preposition cylinder of high parameter, by improving the main vapour parameter of fired power generating unit, reach the object that improves overall efficiency of thermal cycle.
Double reheat supercharging steam turbine thermodynamic system in Fig. 1 comprises: high parameter steam turbine generator set, and this high parameter steam turbine generator set has ultra-high pressure cylinder C4 and the first generator G1; Low parameter steam turbine generator set, this low parameter steam turbine generator set is connected with described high parameter steam turbine generator set and has high-pressure cylinder C3, intermediate pressure cylinder C2, low pressure (LP) cylinder C1 and the second generator G2; And backheat and double reheat circulation system, this backheat and double reheat circulation system are connected with described low parameter steam turbine generator set with described high parameter steam turbine generator set and have the first high-pressure heater H2, oxygen-eliminating device A4, low-pressure heater H1 and condensate pump A3, the feed water pump group A5 for thermodynamic cycle for backheat.The steam of the first high-pressure heater H2, oxygen-eliminating device A4, low-pressure heater H1, feed water pump group A5 is provided by original the drawing gas of low parameter steam turbine.
The prior art is to subcritical low parameter fired power generating unit, as set up the preposition cylinder of ultra supercritical high parameter, and adopt double reheat, net coal consumption rate can be reduced to the i.e. about 15g/kW.h of nearly 4%(), increase the about 20%(of unit output simultaneously common 300MW unit is 60MW, is 120MW to common 600MW unit).
Prior art shown in Fig. 2 is to increase by 1 grade of more drawing gas and corresponding high-pressure heater of high pressure on the basis of prior art shown in Figure 1, further provides and improves overall efficiency of thermal cycle.
But, because subcritical low parameter Transformation of Unit is ultra supercritical high pressure high temperature turbosets, the boiler that need to more renew, increase preposition cylinder, change the main auxiliary machine equipment such as heater, feed water pump, Overall Reconstruction construction investment is very high, every 300MW unit investment approximately needs 600,000,000, and every 600MW unit investment approximately needs 1,200,000,000, causes investment yield lower, only approximately 5%～6%(is that payback period is 15～17 years), economic aspect does not possess feasibility.The popularization therefore prior art is not applied always.
Therefore,, in order to make this technology become economically feasible, need to provide a kind of new pay off period double reheat supercharging faster steam turbine thermodynamic system.
Summary of the invention
A first aspect of the present invention provides a kind of double reheat supercharging steam turbine thermodynamic system, comprising:
High parameter steam turbine generator set, this high parameter steam turbine generator set has ultra-high pressure cylinder and the first generator;
Low parameter steam turbine generator set, this low parameter steam turbine generator set is connected and has high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator with described high parameter steam turbine generator set; And
Backheat and double reheat circulation system, this backheat and double reheat circulation system are connected with described low parameter steam turbine generator set with described high parameter steam turbine generator set and have the first high-pressure heater, oxygen-eliminating device, low-pressure heater and condensate pump, the feed water pump group for thermodynamic cycle for backheat
This double reheat supercharging steam turbine thermodynamic system is characterised in that,
Described high parameter steam turbine generator set also has the back pressure cylinder that draws gas, and draw gas cylinder and described ultra-high pressure cylinder of this back pressure is set to point cylinder or closes cylinder,
Described backheat and double reheat circulation system also have the second high-pressure heater for backheat, and drawing gas of this second high-pressure heater drawn and connect from the draw gas steam discharge of cylinder of described back pressure.
In another preference, the drawing gas not from draw gas cylinder but draw and connect from the steam discharge of described ultra-high pressure cylinder of described back pressure of described the second high-pressure heater.
In another preference, described backheat and double reheat circulation system also have the feed water booster pump for thermodynamic cycle, and this feed water booster pump is located at the ingress of described the second high-pressure heater.
In another preference, described feed water booster pump is not located at described the second inlet of high pressure heater place but is located at the outlet port of described feed water pump group.
In another preference, described feed water pump group comprises feedwater main pump and pre feedwater pump, and this feedwater main pump is driven by the described back pressure cylinder that draws gas, and draw gas cylinder and described ultra-high pressure cylinder of described back pressure is set to a point cylinder.
In another preference, described feed water booster pump is by the described back pressure cylinder Driven by Coaxial of drawing gas, and draws gas and between cylinder, is provided with timing gear roller box in described feed water booster pump and described back pressure.
In another preference, described feed water pump group comprises feedwater main pump and pre feedwater pump, and this feedwater main pump is by the described back pressure cylinder Driven by Coaxial of drawing gas, and draws gas and between cylinder, is provided with timing gear roller box in described feedwater main pump and described back pressure.
The present invention is directed to existing double reheat supercharging steam turbine thermodynamic system, the configuration back pressure cylinder that draws gas, its object is further to improve the generating thermal efficiency, reduce net coal consumption rate, many times increase unit output simultaneously, thereby increase return on investment, make technology become economically feasible, for extensive use creates conditions.
Accompanying drawing explanation
Fig. 1 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in prior art is shown.
Fig. 2 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in another kind of prior art is shown.
Fig. 3 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 1 is shown.
Fig. 4 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 2 is shown.
Fig. 5 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 3 is shown.
Fig. 6 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 4 is shown.
Fig. 7 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 5 is shown.
Fig. 8 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 6 is shown.
Fig. 9 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 7 is shown.
Embodiment
Terminological interpretation
Back pressure type: steam discharge is called condensed steam type steam turbine to the steam turbine of subatmospheric vacuum vapour condenser, steam discharge is to being called back-pressure turbine higher than the steam turbine of atmospheric piping or heat exchanger.
Draw gas: in the middle of from steam turbine steam discharge, extract steam out.
Cylinder: the through-flow constituent element of steam turbine, pressing force is divided into conventionally: ultra-high pressure cylinder, high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder.As everyone knows, in steam turbine field, liquid or gas pressure are called low pressure at 0.1MPa～1.6MPa, and 1.6MPa～10MPa is called middle pressure, and 10～22.12MPa is called high pressure, and 22.12MPa is called ultrahigh pressure above.In this article, the meaning of " ultrahigh pressure " in above-mentioned ultra-high pressure cylinder, high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder, " high pressure ", " middle pressure ", " low pressure " is identical therewith.
Supercharging: to low parameter steam turbine, the cylinder of the high parameter of connecting above, to improve overall efficiency of thermal cycle, lifting unit generated output.
Below in conjunction with specific embodiment, further set forth the present invention.Should be understood that following examples are only not used in and limit the scope of the invention for the present invention is described.
Embodiment 1
Fig. 3 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 1 is shown.Compared to Figure 1 can find out, in the double reheat supercharging steam turbine thermodynamic system shown in Fig. 1, increase in prior art unexistent back pressure draw gas cylinder BEST and the second high-pressure heater H3.As shown in the figure, in this double reheat supercharging steam turbine thermodynamic system, there is reheater A0 and A1, vapour condenser A2, condensate pump A3, oxygen-eliminating device A4, feed water pump group A5, economizer A6, superheater A7, back pressure draw gas cylinder BEST, low pressure (LP) cylinder C1, intermediate pressure cylinder C2, high-pressure cylinder C3, ultra-high pressure cylinder C4 the first generator G1, the second generator G2, low-pressure heater H1, the first high-pressure heater H2 and the second high-pressure heater H3.Wherein, ultra-high pressure cylinder C4 and the first generator G1 etc. have formed high parameter steam turbine generator set, high-pressure cylinder C3, intermediate pressure cylinder C2, low pressure (LP) cylinder C1 and the second generator G2 etc. have formed low parameter steam turbine generator set, low parameter steam turbine generator set is connected with described high parameter steam turbine generator set, for the first high-pressure heater H2 of backheat, oxygen-eliminating device A4, low-pressure heater H1 and for the condensate pump A3 of thermodynamic cycle, feed water pump group A5 etc. has formed backheat and double reheat circulation system, backheat and double reheat circulation system are connected with described low parameter steam turbine generator set with described high parameter steam turbine generator set.Low-pressure heater H1 and the first high-pressure heater H2 can be multistage heaters.
In Fig. 3, the flow process of system is as follows:
Enter ultra-high pressure cylinder C4 by the high parameter main steam out of the superheater A7 in boiler, acting rear portion steam discharge enters reheater A0 heating, single reheat steam after intensification enters high-pressure cylinder C3 and continues acting, the steam discharge of high-pressure cylinder C3 enters the reheater A1 heating in boiler, double reheat steam after intensification enters intermediate pressure cylinder C2, intermediate pressure cylinder C2 steam discharge after acting enters low pressure (LP) cylinder C1 and continues acting, and the low pressure (LP) cylinder C1 steam discharge after acting enters vapour condenser A2, the cooling water of condensation that becomes.From the centre of intermediate pressure cylinder C2 and low pressure (LP) cylinder C1, many places are extracted steam (intermediate pressure cylinder: draw gas for No. 5, low pressure (LP) cylinder: 6, draw gas for 7, No. 8) out from front to back, as the vapour source of low-pressure heater H1.
A part of steam discharge of ultra-high pressure cylinder C4 enters the back pressure cylinder BEST that draws gas, extract steam (drawing gas for 1,2,3, No. 4) out in many places from front to back from the draw gas centre of cylinder BEST of back pressure, as the vapour source of little steam turbine and the part low-pressure heater H1 of the second high-pressure heater H3, the first high-pressure heater H2, oxygen-eliminating device A4, feed water pump group A5.
Boost through condensate pump A3 from vapour condenser A2 water of condensation out, enter low-pressure heater H1 heating, enter subsequently oxygen-eliminating device A4 heating deoxygenation.Oxygen-eliminating device A4 feedwater process feed water pump group A5(is out conventionally by small turbine drive) boost, enter the first high-pressure heater H2 heating, finally enter the economizer A6 in boiler, carry out thermodynamic cycle.
Compared with showing the accompanying drawing 1 of prior art, the double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 1 has been equipped with the back pressure cylinder BEST that draws gas, and due to this back pressure cylinder BEST that draws gas, exerting oneself of corresponding the first generator G1 obtained increase.In addition, the discharge capacity increase of ultra-high pressure cylinder C4 also makes exerting oneself of corresponding the first generator G1 obtain increase.And the minimizing of drawing gas of high-pressure cylinder C3, intermediate pressure cylinder C2 makes exerting oneself of corresponding the second generator G2 obtain increase.In addition, the back pressure cylinder BEST that draws gas can provide than No. 1 in high-pressure cylinder C4 more the drawing gas for No. 0 of high pressure of drawing gas, and to newly increase a second high-pressure heater H3, has improved the feed temperature that enters economizer A6, thereby has improved efficiency of thermal cycle.
Fig. 4 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 2 is shown.
Embodiments of the invention 2 are similar to embodiment 1, difference is: the drawing gas of the second newly-increased high-pressure heater H3 changes into from the draw gas steam discharge of cylinder BEST of back pressure draws and connect, the draw gas discharge capacity of cylinder BEST of ultra-high pressure cylinder C4 and back pressure increases, corresponding, the increase of exerting oneself of the first generator G1.
Fig. 5 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 3 is shown.
Embodiments of the invention 3 are similar to embodiment 2, and difference is: set up a feed water booster pump A8 in the ingress of Xin Zeng the second high-pressure heater H3.Thus, in the time that the low parameter unit to old is transformed, can change feed water pump group and drive little machine or motor, need not change original multistage high-pressure heater, can significantly reduce engineering cost.
Fig. 6 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 4 is shown.
Embodiments of the invention 4 are similar to embodiment 3, and difference is: feed water booster pump A8 is located at the outlet port of feed water pump group A5.Compared with Fig. 4, the temperature of the ingress of feed water booster pump A8 is lower, and technical difficulty is low, and operational reliability is high.
Fig. 7 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 5 is shown.
Embodiments of the invention 5 are similar to embodiment 4, and difference is: feed water pump group A5 is made up of feed water main pump B1 and pre feedwater pump B2, and pre feedwater pump B2 is generally electronic, and feedwater main pump B1 is generally small turbine drive.The feedwater main pump B1 that comprises feed water booster pump A8 function is provided in the technological scheme in Fig. 7, and feedwater main pump B1 lift equals the lift sum of original lift and feed water booster pump, feedwater main pump B1 is changed by the back pressure cylinder BEST that draws gas simultaneously and drives.Back pressure in this embodiment cylinder BEST that draws gas is different from other all embodiments, and due to coaxial with ultra-high pressure cylinder C4, therefore draw gas cylinder BEST and ultra-high pressure cylinder C4 of back pressure can only be made as a point cylinder, closes cylinder and can not be made as.Compared with technological scheme in Fig. 6, without feed water booster pump motor, station service power consumption rate is relatively low.Accompanying drawing 7 newly increases the heating steam adding from ultra-high pressure cylinder steam discharge, also can be as accompanying drawing 6 from back pressure the drawing gas of cylinder of drawing gas.
Fig. 8 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 6 is shown.
Embodiments of the invention 6 are similar to embodiment 3, difference is: feed water booster pump A8 is by the cylinder BEST Driven by Coaxial of drawing gas of the back pressure in high parameter Turbo-generator Set, feed water booster pump A8 and back pressure are drawn gas timing gear roller box A9 are set between cylinder BEST, when normal operation, the rotating speed of high parameter Turbo-generator Set is that power frequency is determined rotating speed, the rotating speed of feed water booster pump A8 regulates by timing gear roller box A9, meets the needs of changing speed and regulating pressure.Compared with technological scheme in Fig. 4, station service power consumption rate is relatively low.
Fig. 9 is the structural drawing that double reheat supercharging steam turbine thermodynamic system in the embodiment of the present invention 7 is shown.
Embodiments of the invention 7 are similar to embodiment 4, and difference is: feed water pump group A5 is made up of feed water main pump B1 and pre feedwater pump B2, and pre feedwater pump B2 is generally electronic, and feedwater main pump B1 is generally small turbine drive.The feedwater main pump B1 that comprises feed water booster pump A8 function is provided in the technological scheme in Fig. 9, feedwater main pump B1 lift equals the lift sum of original lift and feed water booster pump, simultaneously, feedwater main pump B1 is by the cylinder BEST Driven by Coaxial of drawing gas of the back pressure in high parameter Turbo-generator Set, between feedwater main pump B1 and high parameter Turbo-generator Set, timing gear roller box A9 is set, when normal operation, the rotating speed of high parameter Turbo-generator Set is that power frequency is determined rotating speed, the rotating speed of feedwater main pump B1 regulates by timing gear roller box A9, meets the needs of changing speed and regulating pressure.Compared with technological scheme in Fig. 5, without feed water booster pump motor, station service power consumption rate is relatively low.
Effect
The low parameter fired power generating unit transformation that technological scheme of the present invention can be used for having moved, also can be used for newly-built high pressure high temperature turbosets.For example, for typical 300MW Subcritical Units, adopt the present invention to join the draw gas double reheat supercharging steam turbine thermodynamic system of cylinder of back pressure, can reduce the about 20g/kW.h of net coal consumption rate, increase 150MW exert oneself (being more than 2.5 times of existing scheme), investment yield approximately 16%, pay off period approximately 6 years; For typical 600MW Subcritical Units, adopt the present invention to join the draw gas double reheat supercharging steam turbine thermodynamic system of cylinder of back pressure, can reduce the about 20g/kW.h of net coal consumption rate, increase 300MW exert oneself (being more than 2.5 times of existing scheme), investment yield approximately 16%, pay off period approximately 6 years.In thering is good energy-saving and environmental protection social benefit, there is good economic feasibility.
In addition should be understood that those skilled in the art can make various changes or modifications the present invention after having read above-mentioned instruction content of the present invention, these equivalent form of values fall within the application's appended claims limited range equally.
Description of reference numerals
A0, A1: reheater
A2: vapour condenser
A3: condensate pump
A4: oxygen-eliminating device
A5: feed water pump group
A6: economizer
A7: superheater
A8: feed water booster pump
A9: timing gear roller box
B1: feedwater main pump
B2: pre feedwater pump
BEST: the back pressure cylinder that draws gas
C1: low pressure (LP) cylinder
C2: intermediate pressure cylinder
C3: high-pressure cylinder
C4: ultra-high pressure cylinder
G1: the first generator
G2: the second generator
H1: low-pressure heater
H2: the first high-pressure heater
H3: the second high-pressure heater
Claims (7)
1. a double reheat supercharging steam turbine thermodynamic system, comprising:
High parameter steam turbine generator set, this high parameter steam turbine generator set has ultra-high pressure cylinder and the first generator;
Low parameter steam turbine generator set, this low parameter steam turbine generator set is connected and has high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder and the second generator with described high parameter steam turbine generator set; And
Backheat and double reheat circulation system, this backheat and double reheat circulation system are connected with described low parameter steam turbine generator set with described high parameter steam turbine generator set and have the first high-pressure heater, oxygen-eliminating device, low-pressure heater and condensate pump, the feed water pump group for thermodynamic cycle for backheat
This double reheat supercharging steam turbine thermodynamic system is characterised in that,
Described high parameter steam turbine generator set also has the back pressure cylinder that draws gas, and draw gas cylinder and described ultra-high pressure cylinder of this back pressure is set to point cylinder or closes cylinder,
Described backheat and double reheat circulation system also have the second high-pressure heater for backheat, and drawing gas of this second high-pressure heater drawn and connect from the draw gas steam discharge of cylinder of described back pressure.
2. double reheat supercharging steam turbine thermodynamic system as claimed in claim 1, is characterized in that,
Drawing gas not from draw gas cylinder but draw and connect from the steam discharge of described ultra-high pressure cylinder of described back pressure of described the second high-pressure heater.
3. double reheat supercharging steam turbine thermodynamic system as claimed in claim 2, is characterized in that,
Described backheat and double reheat circulation system also have the feed water booster pump for thermodynamic cycle, and this feed water booster pump is located at the ingress of described the second high-pressure heater.
4. double reheat supercharging steam turbine thermodynamic system as claimed in claim 3, is characterized in that,
Described feed water booster pump is not located at described the second inlet of high pressure heater place but is located at the outlet port of described feed water pump group.
5. double reheat supercharging steam turbine thermodynamic system as claimed in claim 2, is characterized in that,
Described feed water pump group comprises feedwater main pump and pre feedwater pump, and this feedwater main pump is driven by the described back pressure cylinder that draws gas, and draw gas cylinder and described ultra-high pressure cylinder of described back pressure is set to a point cylinder.
6. double reheat supercharging steam turbine thermodynamic system as claimed in claim 3, is characterized in that,
Described feed water booster pump is by the described back pressure cylinder Driven by Coaxial of drawing gas, and draws gas and between cylinder, is provided with timing gear roller box in described feed water booster pump and described back pressure.
7. double reheat supercharging steam turbine thermodynamic system as claimed in claim 2, is characterized in that,
Described feed water pump group comprises feedwater main pump and pre feedwater pump, and this feedwater main pump is by the described back pressure cylinder Driven by Coaxial of drawing gas, and draws gas and between cylinder, is provided with timing gear roller box in described feedwater main pump and described back pressure.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822373A (en) * | 2015-01-08 | 2016-08-03 | 国电浙江北仑第发电有限公司 | Pressure-boosting main machine coaxial driving water feeding pump system comprising backpressure steam extraction small steam turbine |
| CN109615271A (en) * | 2018-12-29 | 2019-04-12 | 国电南京电力试验研究有限公司 | A kind of accurate power consumption analysis method of the more loads of Double reheat steam turbine |
| CN110566298A (en) * | 2019-09-30 | 2019-12-13 | 大唐郓城发电有限公司 | Method for optimizing regenerative cycle efficiency |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2955429A (en) * | 1957-07-16 | 1960-10-11 | Gen Electric | Double reheat compound turbine powerplant |
| US20070137204A1 (en) * | 2003-02-07 | 2007-06-21 | Elsam Engineering A/S | Steam turbine system |
| CN101638998A (en) * | 2009-09-07 | 2010-02-03 | 上海电力学院 | Front-end double pressure heat absorbing and heat returning circulating thermal system for thermal generator set |
| CN102678207A (en) * | 2011-03-18 | 2012-09-19 | 中国电力工程顾问集团华东电力设计院 | Thermodynamic system with twice reheating |
| CN103485848A (en) * | 2013-09-30 | 2014-01-01 | 中国电力工程顾问集团华东电力设计院 | Backpressure steam extraction small turbine thermal system which is coaxial with single reheating main turbine |
-
2014
- 2014-03-14 CN CN201410096005.9A patent/CN103806966B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2955429A (en) * | 1957-07-16 | 1960-10-11 | Gen Electric | Double reheat compound turbine powerplant |
| US20070137204A1 (en) * | 2003-02-07 | 2007-06-21 | Elsam Engineering A/S | Steam turbine system |
| CN101638998A (en) * | 2009-09-07 | 2010-02-03 | 上海电力学院 | Front-end double pressure heat absorbing and heat returning circulating thermal system for thermal generator set |
| CN102678207A (en) * | 2011-03-18 | 2012-09-19 | 中国电力工程顾问集团华东电力设计院 | Thermodynamic system with twice reheating |
| CN103485848A (en) * | 2013-09-30 | 2014-01-01 | 中国电力工程顾问集团华东电力设计院 | Backpressure steam extraction small turbine thermal system which is coaxial with single reheating main turbine |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822373A (en) * | 2015-01-08 | 2016-08-03 | 国电浙江北仑第发电有限公司 | Pressure-boosting main machine coaxial driving water feeding pump system comprising backpressure steam extraction small steam turbine |
| CN109615271A (en) * | 2018-12-29 | 2019-04-12 | 国电南京电力试验研究有限公司 | A kind of accurate power consumption analysis method of the more loads of Double reheat steam turbine |
| CN109615271B (en) * | 2018-12-29 | 2021-11-12 | 国能南京电力试验研究有限公司 | Multi-load accurate consumption difference analysis method for secondary reheating steam turbine |
| CN110566298A (en) * | 2019-09-30 | 2019-12-13 | 大唐郓城发电有限公司 | Method for optimizing regenerative cycle efficiency |
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| CN103806966B (en) | 2016-01-13 |
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