CN1605717A - Super-supercritical air cooling steam turbine - Google Patents
Super-supercritical air cooling steam turbine Download PDFInfo
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- CN1605717A CN1605717A CN 200310107845 CN200310107845A CN1605717A CN 1605717 A CN1605717 A CN 1605717A CN 200310107845 CN200310107845 CN 200310107845 CN 200310107845 A CN200310107845 A CN 200310107845A CN 1605717 A CN1605717 A CN 1605717A
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Abstract
The super-supercritical air-cooled steam turbine suitable for use in thermal power plant in unwatered area consists of super-supercritical wet cooled steam turbine high pressure cylinder, super-supercritical wet cooled steam turbine medium pressure cylinder and two low pressure cylinders. It features the two air cooled low pressure cylinders, the connection with low pressure cylinder bearing seat between the super-supercritical wet cooled steam turbine medium pressure cylinder and the air cooled low pressure cylinders and between the two air cooled low pressure cylinders, and the same structure of the high pressure cylinder and medium pressure cylinder in the super-supercritical air-cooled steam turbine and the high pressure cylinder and medium pressure cylinder in the super-supercritical wet cooled steam turbine. The two low pressure cylinders have improved structure and the present invention has air cooled exhaust. The present invention has low heat loss rate, high heat efficiency and low water consumption.
Description
Technical field
The present invention relates to a kind of ultra supercritical air cooling turbine, be applicable to the thermal power plant, water-deficient area, belong to power generating equipment steam turbine technology field.
Background technique
Some country in Asia and Africa and the northwest and the North China of China all belong to rich coal or rich oil but the problem that the thermal power plant faces lack of water is built in the area of lack of water or arid.The water globe resource reduces day by day, and industry and the life water usage but grow with each passing day.China's water resources safety problem is severe day by day, per capita water resources quantity be equivalent to the world per capita quantity 1/4th, and mix extremely unbalancedly at the region branch, in Shanxi of northern China, rich coal area such as Shaanxi, Inner Mongol, Xinjiang, Gansu, water resources extremely lacks.In more than 600 city of China, there is the insufficient water problem in more than 400 city, and wherein more serious lack of water city reaches 110, and National urban lack of water total amount is 60 billion cubic meters.Shortage of water resources has become one of factor that influences China's economic development.The thermal power plant is the industrial water rich and influential family, and water consumption accounts for more than 20% of industrial water.Along with the development and national economy power industry develops rapidly, big capacity thermal power plant constantly increases, and the thermal power plant is subjected to the contradiction of water resources restriction more and more outstanding.Build the thermal power plant both at home and abroad in the water-deficient area and adopt subcritical air cooling turbine, be called for short air cooling turbine.The low pressure steam discharge of subcritical air cooling turbine adopts direct air cooling system or indirect air cooling system cooling, and its water usage only is that water-saving result is remarkable with 1/4th of power wet cooling gas turbine water usage.The air cooling turbine that adopts at present is subcritical air cooling turbine both at home and abroad, and the steam turbine steam inlet condition is subcritical parameter, and main steam pressure is 16.67MPa, and the scope of main steam and reheat steam temperature is about 538 ℃ to 540 ℃.The advantage of subcritical air cooling turbine is to be applied to the water-deficient area, and the major defect of subcritical air cooling turbine is that system's heat consumption rate height, generatine set heat efficiency are low.
The steam inlet condition of ultra supercritical wet cooling gas turbine is a ultra supercritical parameter, and the scope of main steam pressure is 25.0MPa to 32.0MPa, and the scope of main steam and reheat steam temperature is 580 ℃ to 720 ℃.The characteristics of ultra supercritical wet cooling gas turbine are good economy performance, compare with the subcritical air cooling turbine with power, and the major advantage of ultra supercritical wet cooling gas turbine is that heat consumption rate is low, the generatine set heat efficiency height.The heat consumption rate of ultra supercritical wet cooling gas turbine is than low 4 to 8 percentage points approximately of subcritical air cooling turbines, the subcritical Air-cooled Unit of the thermal efficiency ratio of the clammy unit of ultra supercritical is high approximately 4 to 8 percentage points, thermal efficiency height than overcritical clammy unit, as shown in Figure 1, be ultra supercritical wet cooling gas turbine low pressure (LP) cylinder structural representation, mainly be made up of low pressure cylinder, low-pressure shaft, bearing support, stator blade, moving vane, steam discharge diffuser pipe, its structural feature is:
1. the altitude range of the final stage moving blade 11 of ultra supercritical wet cooling gas turbine low pressure cylinder is between 800mm to 1300mm;
2. the height of two low pressure cylinders of ultra supercritical wet cooling gas turbine 9,10 is 6000mm-9500mm, and length is 6000mm-9000mmm;
3. the bearing support 12 of low pressure (LP) cylinder adopts seat cylinder formula bearing support in the low pressure (LP) cylinder the inside usually, and center line of shafting will oscilaltion causes bearing load to be redistributed with the variation of low pressure (LP) cylinder exhaust temperature, influence axle system stability;
4. the length overall of the steam discharge diffuser pipe 13 of ultra supercritical wet cooling gas turbine low pressure (LP) cylinder is 1900mm-3000mm, and the guide ring outlet diameter Φ of steam discharge diffuser pipe is 4500mm-6000mm, the initial angle of flare α of the outer wall of steam discharge diffuser pipe
2It is 15 °-25 °.
The low pressure steam discharge of ultra supercritical wet cooling gas turbine adopts the circulating water wet condenser cooling of unifying, and its major defect is that water usage is big, can't use in the water-deficient area.
Summary of the invention
The purpose of this invention is to provide and a kind ofly can be applied to the water-deficient area, water usage is little, and heat consumption rate is low, the ultra supercritical air cooling turbine that generatine set heat efficiency is high.
In order to achieve the above object, technological scheme of the present invention provides a kind of ultra supercritical air cooling turbine, form by ultra supercritical wet cooling gas turbine high-pressure cylinder, ultra supercritical wet cooling gas turbine intermediate pressure cylinder and two low pressure (LP) cylinders, its main feature is, described two low pressure (LP) cylinders are the air cooling turbine low pressure (LP) cylinder, between overcritical wet cooling gas turbine intermediate pressure cylinder and the air cooling turbine low pressure (LP) cylinder, connected by the floor model bearing support between two air cooling turbine low pressure (LP) cylinders.
The final stage moving blade height of described two air cooling turbine low pressure (LP) cylinders foreshortens to 500mm-700mm;
The cylinder height H of described two air cooling turbine low pressure (LP) cylinders is reduced to 4500mm-7500mm, and axial length L is reduced to 4500mm-7500mm;
Described low pressure (LP) cylinder bearing support is the floor model bearing block structure in the outside of two low pressure (LP) cylinders;
The length overall L of the steam discharge diffuser pipe of described two air cooling turbine low pressure (LP) cylinders
1Shorten to 700mm-2000mm, the guide ring outlet diameter Φ of steam discharge diffuser pipe is reduced to 4000mm-5000mm, the initial angle of flare α of the outer wall of steam discharge diffuser pipe
2Expand as 20 °-35 °.
The 1st grade blade leaf plateau blade and blade of described two air cooling turbine low pressure (LP) cylinders is high 1.1 times to 1.25 times.
The invention provides a kind of ultra supercritical air cooling turbine, this steam turbine adopts the ultra supercritical steam inlet condition, the scope of main steam pressure is 25.0MPa to 32.0MPa, the scope of main steam and reheat steam temperature is 580 ℃ to 720 ℃, and promptly the high-pressure cylinder of ultra supercritical air cooling turbine is identical with the high-pressure cylinder and the intermediate pressure cylinder structure of ultra supercritical wet cooling gas turbine with intermediate pressure cylinder.Two low pressure (LP) cylinders of ultra supercritical air cooling turbine improve the low pressure steam discharge cooling that makes this steam turbine from structure and adopt direct air cooling system or indirect air cooling system, it is low to make the ultra supercritical air cooling turbine both have a heat consumption rate of ultra supercritical wet cooling gas turbine, the advantage that generatine set heat efficiency is high, it is few to have subcritical air cooling turbine water consumption again, can be applied to the advantage of water-deficient area.
With compare with power ultra supercritical wet cooling gas turbine, the final stage moving blade height of two air cooling turbine low pressure (LP) cylinders shortens, the low pressure leaving area of ultra supercritical air cooling turbine is about 50% to 70% of ultra supercritical wet cooling gas turbine leaving area, to be suitable for the back pressure height of ultra supercritical air cooling turbine.Because ultra supercritical air cooling turbine low pressure leaving area is little, ultra supercritical air cooling turbine low pressure exhaust casing should adopt the good structure of aeroperformance, the loss coefficient ξ of low pressure exhaust casing
n＜1.
Ultra supercritical air cooling turbine final stage adopts relatively shorter moving vane, is in order to adapt to Air-cooled Unit back pressure height, characteristics that volume flow is little.The design back pressure of ultra supercritical air cooling turbine is higher approximately 1 times to 2 times than ultra supercritical wet cooling gas turbine; The high back pressure of ultra supercritical wet cooling gas turbine is generally high approximately 1 times than the design back pressure, and the high back pressure of ultra supercritical air cooling turbine is generally high approximately 3 times than designing back pressure.Wet-bulb temperature is depended in the back pressure variation of ultra supercritical wet cooling gas turbine, and the back pressure of ultra supercritical air cooling turbine depends on atmosphere dry-bulb temperature.The atmospheric temperature day and night temperature is big, so ultra supercritical air cooling turbine back pressure changes frequently.The ultra supercritical air cooling turbine adopts relatively shorter exhaust stage blade, under the big condition of back pressure height, back pressure excursion, has higher stage load, and separation of flow zone is little, and requires to flow and do not block.The ultra supercritical air cooling turbine adopts relatively shorter final stage moving blade, can improve the rigidity of moving vane, helps reducing the dynamic stress peak value of blade.
The load carrying exhaust temperature of ultra supercritical air cooling turbine equals the saturation temperature of turbine back pressure correspondence.Because ultra supercritical air cooling turbine back pressure height and back pressure vary within wide limits, then ultra supercritical air cooling turbine low pressure exhaust temperature height and vary within wide limits.The center line of ultra supercritical air cooling turbine low pressure (LP) cylinder will change with low pressure (LP) cylinder steam discharge temperature to be raised or reduces.So the ultra supercritical air cooling turbine should adopt the floor model bearing block structure, the low pressure (LP) cylinder bearing support directly is supported on the basis that reinforced concrete casts, center line of shafting does not change with the low pressure exhaust temperature, the bearing load distribution does not also change with the low pressure exhaust temperature, guarantees ultra supercritical air-cooled steam turbine arbor system stability.
Because ultra supercritical air cooling turbine low pressure (LP) cylinder adopts the floor model bearing support, moved on to the outside of turbine low pressure cylinder by original bearing support in turbine low pressure cylinder, cause the length overall of the steam discharge diffuser pipe of turbine low pressure cylinder to shorten, but the length overall of the steam discharge diffuser pipe of turbine low pressure cylinder shortens, and can make low pressure (LP) cylinder steam discharge aeroperformance variation.By the guide ring outlet diameter of change steam discharge diffuser pipe and the initial angle of flare α of outer wall of steam discharge diffuser pipe
2The steam discharge loss of turbine low pressure cylinder is reduced, remedy the shortcoming of the relative distance shortening of low pressure exhaust casing, reach low pressure exhaust casing aeroperformance purpose preferably.
Because the raising of main steam and reheat steam temperature, ultra supercritical air cooling turbine low pressure rotor admission position operating temperature raises.Supercritical turbine low pressure rotor the 1st grade blade blade profile root adopts negative degree of reaction structure, is in order to reduce the operating temperature at low pressure rotor admission position.Blade profile root at the 1st grade of moving vane of low pressure, negative degree of reaction makes the pressure height of pressure ratio stator blade blade profile root steam output side of moving vane root steam output side, makes the steam of having done merit and having reduced the moving vane outlet of temperature flow to the stator blade outlet through moving vane blade profile root and vertical tree type blade root bottom gap.The reverse flow of this steam flow makes the wheel rim of low pressure rotor and low pressure rotor admission high temperature position obtain cooling.After moving vane blade profile root adopted negative degree of reaction, the leaf height of the 1st grade of moving vane increased to some extent, and it highly is high 1.1 times to 1.25 times of the moving vane leaf that do not adopt the negative degree of reaction of blade profile root.
Advantage of the present invention is that heat consumption rate is low, the generatine set heat efficiency height, and its water usage only is with 1/4th of power ultra supercritical wet cooling gas turbine, can use in the water-deficient area.
Description of drawings
Fig. 1 is a ultra supercritical wet cooling gas turbine low pressure (LP) cylinder structural representation;
Fig. 2 is a ultra supercritical air cooling turbine structural representation;
Fig. 3 is a ultra supercritical air cooling turbine low pressure (LP) cylinder structural representation;
Fig. 4 is a ultra supercritical air cooling turbine low pressure (LP) cylinder final stage diffuser pipe structural representation;
Embodiment
Embodiment:
With 600MW ultra supercritical air cooling turbine is example, main steam pressure 25MPa, 600 ℃ of main steam temperatures, 600 ℃ of reheat steam temperatures, design back pressure 16kPa.
As shown in Figure 2, be ultra supercritical air cooling turbine structural representation, be made up of ultra supercritical wet cooling gas turbine high-pressure cylinder 1, ultra supercritical wet cooling gas turbine intermediate pressure cylinder 2, air cooling turbine low pressure (LP) cylinder 3 and air cooling turbine low pressure (LP) cylinder 4, low pressure (LP) cylinder 3 and low pressure (LP) cylinder 4 adopt the floor model bearing support.
As shown in Figure 3, be ultra supercritical air cooling turbine low pressure (LP) cylinder structural representation, the height of the 1st grade of moving vane 8 of low pressure is 201mm, and the height of exhaust stage blade 5 is 664.99mm; The cylinder height H of air cooling turbine low pressure (LP) cylinder 3 and air cooling turbine low pressure (LP) cylinder 4 is 5400mm, and axial length L is 5400mm; Low pressure (LP) cylinder adopts the floor model bearing support.
As shown in Figure 4, be ultra supercritical air cooling turbine low pressure (LP) cylinder final stage diffuser pipe structural representation, the length overall L of the steam discharge diffuser pipe 7 of air cooling turbine low pressure (LP) cylinder 3 and air cooling turbine low pressure (LP) cylinder 4
1Be 1077.1mm, the guide ring outlet diameter Φ of steam discharge diffuser pipe 7 is 4500mm, final stage exhaust annulus area 4.44 * 4m
2The initial angle of flare α of the outer wall of steam discharge diffuser pipe 7
2It is 25 °; The length overall L of steam discharge diffuser pipe 7
1With the ratio of the height of exhaust stage blade 5 be 1.620, diffuser pipe loss coefficient ξ
n=0.995, ξ
n＜1 has reached optimal design.
Claims (6)
1. ultra supercritical air cooling turbine, form by ultra supercritical wet cooling gas turbine high-pressure cylinder (1), ultra supercritical wet cooling gas turbine intermediate pressure cylinder (2) and two low pressure (LP) cylinders, it is characterized in that, described low pressure (LP) cylinder is air cooling turbine low pressure (LP) cylinder (3) and air cooling turbine low pressure (LP) cylinder (4), between overcritical wet cooling gas turbine intermediate pressure cylinder (2) and the air cooling turbine low pressure (LP) cylinder (3), connected by floor model bearing support (6) between air cooling turbine low pressure (LP) cylinder (3) and the air cooling turbine low pressure (LP) cylinder (4).
2. ultra supercritical air cooling turbine according to claim 1 is characterized in that, the final stage moving blade (5) of described air cooling turbine low pressure (LP) cylinder (3) and air cooling turbine low pressure (LP) cylinder (4) highly foreshortens to 500mm-700mm.
3. ultra supercritical air cooling turbine according to claim 1, it is characterized in that, the cylinder height H of described air cooling turbine low pressure (LP) cylinder (3) and air cooling turbine low pressure (LP) cylinder (4) is reduced to 4500mm-7500mm, and axial length L is reduced to 4500mm-7500mm.
4. ultra supercritical air cooling turbine according to claim 1 is characterized in that, described low pressure (LP) cylinder bearing support (6) is the floor model bearing block structure in the outside of air cooling turbine low pressure (LP) cylinder (3) and air cooling turbine low pressure (LP) cylinder (4).
5. a kind of ultra supercritical air cooling turbine according to claim 1 is characterized in that, the length overall L of the steam discharge diffuser pipe (7) of described air cooling turbine low pressure (LP) cylinder (3) and air cooling turbine low pressure (LP) cylinder (4)
1Shorten to 700mm-2000mm, the guide ring outlet diameter Φ of steam discharge diffuser pipe (7) is reduced to 4000mm-5000mm, the initial angle of flare α of the outer wall of steam discharge diffuser pipe (7)
2Expand as 20-35 °.
6. a kind of ultra supercritical air cooling turbine according to claim 1 is characterized in that, the leaf height of the 1st grade blade (8) of described air cooling turbine low pressure (LP) cylinder (3) and air cooling turbine low pressure (LP) cylinder (4) is high 1.1 times to 1.25 times of former blade and blade.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101078452A CN100357570C (en) | 2003-10-10 | 2003-10-10 | Super-supercritical air cooling steam turbine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101078452A CN100357570C (en) | 2003-10-10 | 2003-10-10 | Super-supercritical air cooling steam turbine |
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| CN1605717A true CN1605717A (en) | 2005-04-13 |
| CN100357570C CN100357570C (en) | 2007-12-26 |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102383879A (en) * | 2011-10-28 | 2012-03-21 | 上海电气电站设备有限公司 | Steam turbine structure |
| CN102392699A (en) * | 2011-10-28 | 2012-03-28 | 上海电气电站设备有限公司 | Steam turbine operation method |
| CN102720546A (en) * | 2012-07-02 | 2012-10-10 | 上海汽轮机厂有限公司 | Ultra-supercritical 1300MW grade steam turbine |
| CN108204252A (en) * | 2016-12-20 | 2018-06-26 | 上海电气电站设备有限公司 | The cylinder of steam turbine |
| CN109902426A (en) * | 2019-03-12 | 2019-06-18 | 上海发电设备成套设计研究院有限责任公司 | Air-cooled type high-parameter steam turbine high intermediate pressure cylinder performance and structure design and monitoring method |
| CN109915217A (en) * | 2019-02-02 | 2019-06-21 | 上海发电设备成套设计研究院有限责任公司 | The overall structure and overall performance of air-cooled type high-parameter steam turbine design monitoring method |
| CN109960852A (en) * | 2019-02-22 | 2019-07-02 | 上海发电设备成套设计研究院有限责任公司 | The structure and performance design and monitoring method of air-cooled type high-parameter steam turbine low pressure (LP) cylinder |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB845202A (en) * | 1955-11-29 | 1960-08-17 | Gen Electric | Improvements in and relating to combined gas and steam turbine plants |
| WO1986005234A1 (en) * | 1985-03-15 | 1986-09-12 | Tch Thermo-Consulting-Heidelberg Gmbh | A combined steam-gas turbine installation |
| FR2698659B1 (en) * | 1992-12-02 | 1995-01-13 | Stein Industrie | Heat recovery process in particular for combined cycles apparatus for implementing the process and installation for heat recovery for combined cycle. |
| CN2530042Y (en) * | 2002-04-05 | 2003-01-08 | 东方汽轮机厂 | Direct air cooling turbine steam exhauster for power station |
-
2003
- 2003-10-10 CN CNB2003101078452A patent/CN100357570C/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102383879A (en) * | 2011-10-28 | 2012-03-21 | 上海电气电站设备有限公司 | Steam turbine structure |
| CN102392699A (en) * | 2011-10-28 | 2012-03-28 | 上海电气电站设备有限公司 | Steam turbine operation method |
| CN102392699B (en) * | 2011-10-28 | 2015-03-25 | 上海电气电站设备有限公司 | Steam turbine operation method |
| CN102383879B (en) * | 2011-10-28 | 2015-03-25 | 上海电气电站设备有限公司 | Steam turbine structure |
| CN102720546A (en) * | 2012-07-02 | 2012-10-10 | 上海汽轮机厂有限公司 | Ultra-supercritical 1300MW grade steam turbine |
| CN108204252B (en) * | 2016-12-20 | 2020-04-17 | 上海电气电站设备有限公司 | Cylinder for steam turbine |
| CN108204252A (en) * | 2016-12-20 | 2018-06-26 | 上海电气电站设备有限公司 | The cylinder of steam turbine |
| CN109915217A (en) * | 2019-02-02 | 2019-06-21 | 上海发电设备成套设计研究院有限责任公司 | The overall structure and overall performance of air-cooled type high-parameter steam turbine design monitoring method |
| CN109915217B (en) * | 2019-02-02 | 2020-06-16 | 上海发电设备成套设计研究院有限责任公司 | Overall structure and overall performance design monitoring method of air-cooled high-parameter steam turbine |
| CN109960852A (en) * | 2019-02-22 | 2019-07-02 | 上海发电设备成套设计研究院有限责任公司 | The structure and performance design and monitoring method of air-cooled type high-parameter steam turbine low pressure (LP) cylinder |
| CN109960852B (en) * | 2019-02-22 | 2020-06-16 | 上海发电设备成套设计研究院有限责任公司 | Structure and performance design and monitoring method for low pressure cylinder of air-cooled high-parameter steam turbine |
| CN109902426A (en) * | 2019-03-12 | 2019-06-18 | 上海发电设备成套设计研究院有限责任公司 | Air-cooled type high-parameter steam turbine high intermediate pressure cylinder performance and structure design and monitoring method |
| CN109902426B (en) * | 2019-03-12 | 2020-05-15 | 上海发电设备成套设计研究院有限责任公司 | Performance and structure design and monitoring method for high-medium pressure cylinder of air-cooled high-parameter steam turbine |
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| CN100357570C (en) | 2007-12-26 |
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