CN102140938B - Double-cylinder coaxial combined cycle heat supply gas turbine - Google Patents
Double-cylinder coaxial combined cycle heat supply gas turbine Download PDFInfo
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Abstract
The invention discloses a double-cylinder coaxial combined cycle heat supply gas turbine. The double-cylinder coaxial combined cycle heat supply gas turbine comprises a high pressure module and a low pressure module which are distributed coaxially; a high and medium pressure rotor is arranged in the high pressure module; a low pressure rotor is arranged in the low pressure module; one end of the high and medium pressure rotor close to a medium pressure cylinder is connected with a motor; one end of the high and medium pressure rotor close to a high pressure cylinder is coaxially connected with an intermediate shaft; the other end of the intermediate shaft is connected with the low pressure rotor through an autosynchronous clutch; and the high pressure module and the low pressure module are communicated through a low pressure communication pipe which is provided with a low pressure valve bank. The gas turbine can realize the on-line paralleling or disconnection of the high and medium pressure module and the low pressure module, is suitable for single backpressure running of the high pressure module, steam extraction and condensation running of the high pressure module and the low pressure module and steam condensation running of the high pressure module and the low pressure module, and can improve the energy utilization rate to the maximum extent according requirements; and the running mode of the gas turbine is very flexible.
Description
Technical field
The present invention relates to cogeneration turbine technology, disclose a kind of double-cylinder coaxial combined cycle heat supply steam turbine, particularly a kind of cogeneration turbine applicable to the condensing operation of winter back pressure operation, summer.
Background technique
Steam turbine is one of crucial power equipment in power plant construction, is the energy conversion device that thermal power transfer is become to mechanical energy and then convert electric energy to.The high temperature being produced by boiler, high pressure steam, through steam turbine, heat energy and pressure potential are converted to the mechanical energy of steam turbine, drive turbine rotor output shaft work, this mechanical energy passes to generator by rotating shaft of steam turbine, thereby converts mechanical energy to electric energy, therefore, steam turbine is often called as source motivation: " source of light ".
Gas-steam Combined Cycle is one of attainable most effective thermodynamic cycle at present, it is using gas turbine as preposition turbine, by the exhaust heat boiler of heating system, reclaimed the exhaust heat of combustion gas turbine, and produce some grades of steams, again steam is introduced to steam turbine, make combustion gas turbine and steam turbine all export shaft work, drive generator to change out electric energy.For the steam turbine of above-mentioned combined cycle, be generally known as combination circulation steam turbine, current most effective combination circulation steam turbine is three to press heat integration turbine cycle again, and the vapor pressure producing divides high pressure, middle pressure, low pressure third gear.This kind of combined cycle is the most effective New Equipments that energy-conserving and environment-protective require that meets, and has very large development prospect." one-to-one " combined cycle refers to that a combustion gas turbine and an exhaust heat boiler drive a steam turbine set." two drag one " combined cycle refers to that two combustion gas turbines and two exhaust heat boilers drive a steam turbine set." two drag one " combined cycle, because the raising of steam turbine capacity advantage aspect energy-conservation is more outstanding, therefore, the application of " two drag one " combined cycle will become more extensive.
Cogeneration condensing steam turbine refers to that when steam turbine drives generator to electrical network transmission of electric energy, extracting a part of steam out again in the suitable through-flow position of steam turbine enters heat supply network heat supply, another part steam continues to expand in turbine runner and drives rotor of output shaft axle merit, steam discharge level pressure constant temperature heat release condense into water in vapour condenser, finally, then enter in the middle of thermodynamic cycle.Cogeneration back pressure turbine just refers to that steam is after through-flow acting output shaft work, steam is all introduced to a kind of steam turbine of heat supply network heat supply, because back pressure turbine does not arrange vapour condenser, the heat release loss without cold junction, becomes the highest steam turbine of current heat utilization rate.The angle of utilizing from heat energy: straight condensing turbine, cogeneration condensing steam turbine, cogeneration back pressure turbine three's the utilization ratio to heat energy is from low to high.
Yet although cogeneration turbine has higher heat utilization rate, it also exists drawback: working conditions change is generally larger, and the optimum design operating mode of steam turbine generally only has one, when unit operation off-design operating mode, the efficiency of unit will decline.For example, in Chinese northern territory, need to carry out heating general winter, and at this moment cogeneration turbine will be followed the principle of electricity determining by heat, to heat supply network input heat energy, and to summer, northern territory is general does not just need heating to draw gas, at this moment steam turbine does not need again to have drawn gas to have entered pure condensed steam working condition running state, in order to meet the operation demand of this operating mode, low-pressure section is through-flow needs to arrange longer blade, and longer blade is in the winter time in operating mode, there is the problem of inefficiency, this is a difficult problem to cogeneration turbine, because the optimum point of efficiency only has one, generally when design, can consider to select the latter as design conditions, because the time of general Winter heat supply is about a season, and generally will there be three seasons the time of condensing operation.But the problem of bringing be like this in the winter time during operating mode because steam turbine low-pressure flow efficiency is too low, the utilization of the energy has been produced to inevitable waste.
If can allow steam turbine move in back pressure mode in the winter time, the utilization ratio by the raising of maximum possible to heat energy; And move in pure condensed steam mode in summer, using this operating mode as optimum design conditions, make the internal efficiency of steam turbine reach the highest, so just can solve an above-mentioned difficult problem, reach the object that the energy is used in maximum saving.
Summary of the invention
For above-mentioned the deficiencies in the prior art, the technical problem to be solved in the present invention be to provide a kind of can winter the steam turbine of back pressure operation, condensing operation in summer.
For solving the problems of the technologies described above, the present invention adopts following technological scheme:
A kind of double-cylinder coaxial combined cycle heat supply steam turbine, it comprises a high-pressure modular and a low-voltage module, described high-pressure modular, low-voltage module is coaxially arranged, in described high-pressure modular, be provided with high pressure rotor, in described low-voltage module, be provided with low pressure rotor, described high-pressure modular adopts high pressure cylinder combined structure, counter spreading put, it can be divided into high-pressure cylinder and intermediate pressure cylinder in logic, described high-pressure cylinder following current is arranged, described intermediate pressure cylinder counter-flow arrangement, described high pressure rotor connects with generator near one end of intermediate pressure cylinder, one end of described high pressure rotor coaxially connects with a jack shaft, the other end of described jack shaft connects with described low pressure rotor by a self-synchronizing clutch, between described high-pressure modular and described low-voltage module, pass through mesolow unicom pipeline UNICOM, described mesolow unicom pipeline is provided with low pressure valve group, described high-pressure modular also with a heat supply extraction line UNICOM, described heat supply extraction line is provided with extraction control valve.
Preferably, senior middle school's pressing cylinder of described high-pressure modular adopts double shell structure, comprise High-and-medium Pressure Outer Casing and high pressure inner casing, described high pressure rotor is positioned at described high pressure inner casing, the low pressure (LP) cylinder of described low-voltage module is double shell structure, comprise lp outer casing and low-pressure internal cylinder, described low pressure rotor is positioned at described low-pressure internal cylinder.
Preferably, described high pressure inner casing adopts whole interior cylinder structure.
Preferably, described high-pressure modular is provided with high pressure main stop valve, high pressure speed governing steam valve, middle pressure reheating main steam valve and middle pressure speed governing steam valve, described high pressure main stop valve, high pressure speed governing steam valve is fixed on the first valve casing, described the first valve casing connects with described High-and-medium Pressure Outer Casing by flange, described high pressure main stop valve, high pressure speed governing steam valve and described high-pressure cylinder UNICOM, described middle pressure reheating main steam valve, middle pressure speed governing steam valve is fixed on the second valve casing, described the second valve casing connects with described High-and-medium Pressure Outer Casing by flange, described middle pressure reheating main steam valve, middle pressure speed governing steam valve and described intermediate pressure cylinder UNICOM.
Preferably, described the first valve casing, the second valve casing is respectively equipped with below constant force supporting frame.
Preferably, the rear and front end of described high pressure rotor adopts respectively high pressure fore bearing and high pressure rear bearing to support, and the rear and front end of described low pressure rotor adopts respectively low pressure fore bearing and low pressure rear bearing to support, and described jack shaft adopts a stable bearing to support.
Preferably, described high pressure rotor connects with generator by a coupling near one end of intermediate pressure cylinder, and described high pressure rotor connects with jack shaft by a synchronous coupling near one end of high-pressure cylinder.
Preferably, the free end of described low pressure rotor is provided with jiggering motor.
Preferably, described low pressure valve group comprises low pressure main stop valve, low pressure speed governing steam valve and low voltage starting steam valve.
Preferably, described mesolow unicom pipeline also with a combined cycle low pressure steam supply pipe UNICOM, described combined cycle low pressure steam supply pipe is provided with the low pressure filling valve group of regulating and controlling low pressure filling throttle flow.
Technique scheme has following beneficial effect: the high pressure rotor of this double-cylinder coaxial combined cycle heat supply steam turbine connects by self-synchronizing clutch with low pressure rotor, like this when the rotating speed of low pressure rotor is during higher than the rotating speed of high pressure rotor, low pressure rotor and high pressure rotor mesh by self-synchronizing clutch, when the rotating speed of low pressure rotor is during lower than the rotating speed of high pressure rotor, self-synchronizing clutch is thrown off low pressure rotor and high pressure rotor, this steam turbine can be realized online " and car " or " off-the-line " of high pressure module and low-voltage module like this, so this steam turbine operation mode is very flexible, it is applicable to the independent back pressure operation of high-pressure modular, high-pressure modular and the operation of low-voltage module steam extraction and condensing formula, high-pressure modular and the operation of low-voltage module condensed steam type, can select as required the corresponding method of operation, thereby improve to the full extent the utilization ratio of the energy.
Above-mentioned explanation is only the general introduction of technical solution of the present invention, in order to better understand technological means of the present invention, and can be implemented according to the content of specification, below with preferred embodiment of the present invention and coordinate accompanying drawing to be described in detail as follows.The specific embodiment of the present invention is provided in detail by following examples and accompanying drawing thereof.
Accompanying drawing explanation
Fig. 1 is the sectional view of the embodiment of the present invention.
Fig. 2 is the plan view of the embodiment of the present invention.
Fig. 3 is the side view of the embodiment of the present invention.
Embodiment
Below in conjunction with accompanying drawing, preferred embodiment of the present invention is described in detail.
As shown in Figure 1, this double-cylinder coaxial combined cycle heat supply steam turbine comprises high-pressure modular 1 and low-voltage module 2, described in high-pressure modular 1, high-pressure modular 1 adopts high pressure cylinder combined structure, counter spreading put, it can be divided into high-pressure cylinder 11 and intermediate pressure cylinder 12 in logic, high-pressure cylinder 11 following currents are arranged, intermediate pressure cylinder 12 counter-flow arrangement.Senior middle school's pressing cylinder 13 of high-pressure modular 1 is double shell structure, High-and-medium Pressure Outer Casing 131 and high pressure inner casing 132, consists of, and high pressure rotor 14 is positioned at high pressure inner casing 132.High pressure rotor 14 adopts two fulcrum support modes, by high pressure fore bearing 17 and high pressure rear bearing 16, supported respectively, high pressure fore bearing 17 is arranged in front-end bearing pedestal 18, high pressure rear bearing 16 is arranged in bottom bracket 15, high pressure rear bearing 16 adopts radial thrusts to combine formation, and usings this absolute dead point as high pressure module 1.
High pressure inner casing 132 adopts whole interior cylinder structure, this structure can reduce leakage losses as much as possible, to improve unit efficiency, adopt in addition the interior cylinder technology of this integral body can reduce operating temperature and the working pressure of High-and-medium Pressure Outer Casing 131, and then can reduce the materials'use grade of High-and-medium Pressure Outer Casing 131, can also reduce the wall thickness of outer shell, thereby reach the object that reduces manufacture cost simultaneously.Through-flow 20 of high-pressure modular 1 inside is that what to adopt is the efficient through-flow structure of the through-flow technology platform exploitation of integral body based on advanced, and the first stage stator blades 21 in intermediate pressure cylinder 12 is tilting, so also effectively improves the efficiency of this steam turbine.
As shown in Figure 2, on high-pressure modular 1, be also provided with high pressure main stop valve 37, high pressure speed governing steam valve 38, middle pressure reheating main steam valve 43 and middle pressure speed governing steam valve 44.High pressure main stop valve 37, high pressure speed governing steam valve 38 are fixed on the first valve casing 39, the first valve casing 39 connects with High-and-medium Pressure Outer Casing 131 by flange, high pressure main stop valve 37, high pressure speed governing steam valve 38 and high-pressure cylinder 11 UNICOMs, high pressure main stop valve 37, high pressure speed governing steam valve 38 are used for controlling the steam flow that enters high-pressure cylinder 11.Middle pressure reheating main steam valve 43, middle pressure speed governing steam valve 44 are fixed on the second valve casing 45, the second valve casing 45 connects with High-and-medium Pressure Outer Casing 131 by flange, middle pressure reheating main steam valve 43, middle pressure speed governing steam valve 44 and intermediate pressure cylinder 12 UNICOMs, middle pressure reheating main steam valve 43, middle pressure speed governing steam valve 44 are used for controlling the flow that enters intermediate pressure cylinder 12.The admission structure of above-mentioned intermediate pressure cylinder 12, high-pressure cylinder 11 does not adopt the structural type of steam guiding tube road steam supply, and has adopted a kind of efficiently without steam guiding tube tangential admission technology, can effectively improve the efficiency of admission.The below that the below of the second valve casing 45 is provided with a constant force supporting frame 46, the first valve casing 39 is provided with a constant force supporting frame 47, (as shown in Figure 3) adopt constant force supporting frame 46,47 respectively the first valve casing 39, the second valve casing 45 to be supported on separately and to be conducive to piping arrangement, improved the safe running performance of steam turbine set simultaneously.
Again as shown in Figure 1, low-voltage module 2 comprises low pressure (LP) cylinder 22 and low pressure rotor 23.Low pressure (LP) cylinder 22 adopts double shell structure, the outer shell 34 of low pressure (LP) cylinder 22 adopts On-site Welding Technology, be beneficial to transportation, the inner casing 35 of low pressure (LP) cylinder 22 adopts the form of landing, and through-flow 36 in low pressure (LP) cylinder 22 adopts the efficient through-flow structure of the through-flow technology platform exploitation of advanced integral body and adopt double-current layout pattern.Low pressure rotor 23 adopts two fulcrum supports, two ends are supported by low pressure fore bearing 24 and low pressure rear bearing 26 respectively, low pressure fore bearing 24 is arranged in bottom bracket 25, low pressure rear bearing 26 is arranged in rear bearing block 27, the thrust-bearing 28 of low pressure rotor arranges in low pressure rear bearing block 27, and the dead point of low pressure rotor 23 and low-pressure internal cylinder 22 is all arranged on steam turbine end.The free end of low pressure rotor 23 also arranges a hydraulic turning gear motor 29, and hydraulic turning gear motor 29 can carry out jiggering or high-pressure modular 1 and low-voltage module 2 are carried out to jiggering simultaneously low-voltage module 2 when needed.
This double-cylinder coaxial combined cycle heat supply steam turbine is set up and is different from conventional steam turbine set at the cloth of module, the high pressure rotor 14 of this steam turbine connects with generator by a coupling near one end 19 of intermediate pressure cylinder 12, therefore order of placement during this steam turbine power generation is followed successively by generator, intermediate pressure cylinder, high-pressure cylinder and low pressure (LP) cylinder, and conventional steam turbine is arranged and is generally: the setting type of high-pressure cylinder, intermediate pressure cylinder, low pressure (LP) cylinder, generator.In other words, the layout of this unit is preposition by generator, makes " online " off-the-line low pressure (LP) cylinder module become possibility.High-pressure cylinder and intermediate pressure cylinder are counter arranges to be on the one hand the layout that is conducive to unit dead point, on the other hand, to be conducive to the layout of mesolow unicom pipeline 3.High pressure rotor 14, low pressure rotor 23 coaxially arrange, and jointly drive the advantage of a generator to be, can reduce the space that unit takies factory building, save the cost of investment of founding the factory.
The object that jack shaft 4 is set between high pressure rotor 14, low pressure rotor 23 is, at self-synchronizing clutch 5 places, stable bearing 41 is set, thereby make self-synchronizing clutch 5 can be good at realizing " from centering ", be conducive to the automatic engagement/disengagement of self-synchronizing clutch 5, be conducive to the safe operation of unit.Self-synchronizing clutch 5 can also play the effect of compensation differential expansion in unit running process.
Again as shown in Figure 1, 2, High-and-medium Pressure Outer Casing 131 tops are by a mesolow unicom pipeline 3 and low pressure (LP) cylinder 22 UNICOMs, mesolow unicom pipeline 3 is provided with the low pressure valve group that regulates low pressure (LP) cylinder admission, this low pressure valve group comprises low pressure main stop valve 31, low pressure speed governing steam valve 32 and low voltage starting steam valve 33, this low pressure valve group can enter by control the steam flow of low pressure (LP) cylinder, thereby realizes the control to low pressure (LP) cylinder module.High-and-medium Pressure Outer Casing 131 bottoms also with a heat supply extraction line UNICOM (not shown), heat supply extraction line is provided with extraction control valve, heat supply extraction line for when needs heat to heat supply network delivering vapor.As shown in Figure 3, mesolow unicom pipeline 3 also with combined cycle low pressure steam supply pipe 48 UNICOMs, combined cycle low pressure steam supply pipe 48 is provided with the low pressure filling valve group 49 of regulating and controlling low pressure filling throttle flow, and combined cycle low pressure steam supply pipe 48 connects with the low pressure steam pipe of exhaust heat boiler.
During this double-cylinder coaxial combined cycle heat supply steam turbine work, can regulate as required the steam valve on each pipeline, this steam turbine is moved under various operating modes.
At the non-heating period of summer condition, this steam turbine can adopt pure condensed steam formula operating mode, can close the extraction control valve on heat supply extraction line, open low pressure valve group and low pressure filling valve group 49 on mesolow unicom pipeline 3 simultaneously, the steam that intermediate pressure cylinder is discharged like this and the low pressure steam of exhaust heat boiler can flow in low pressure (LP) cylinder 22, make low pressure rotor 23 High Rotation Speeds in low pressure (LP) cylinder 22, when being not less than high pressure rotor 14, can realize low pressure rotor 23 rotating speeds high pressure module 1 and low-voltage module 2 " and car ", steam turbine operating mode now can be made as to declared working condition/optimum operating condition, now this steam turbine is the same with conventional machine unit has a higher internal efficiency.
And operating mode spike heating period in the winter time, this steam turbine can adopt back pressure type operating mode, can open the extraction control valve on heat supply extraction line, close low pressure valve group and low pressure filling valve group 49 on mesolow unicom pipeline 3 simultaneously, steam can all enter heat supply network by bypass and carries out heat supply like this, and do not have steam to enter in low pressure (LP) cylinder 22, low pressure rotor 23 rotating speeds lower than with high pressure rotor 14, high pressure module 1 and low-voltage module 2 off-the-lines, this steam turbine is just worked under back pressure operating mode like this, the independent back pressure type operation of high pressure module 1 drives generator generating, cold end loss when at this moment this steam turbine does not have conventional steam turbine condensing formula operation.Therefore, back pressure type operation has the highest efficiency of energy utilization.
The non-spike heating period of operating mode in the winter time, this steam turbine can adopt steam extraction and condensing formula operating mode, can control accordingly the amount of opening of above-mentioned each steam valve of pipeline, adjustment enters the steam flow of heat supply network and low pressure (LP) cylinder, realize the adjustable steam extraction of heat supply network, also can make steam turbine work under higher efficiency simultaneously.
This steam turbine operation mode is extremely flexible, can realize the online off-the-line of low-voltage module/and car, by control, enter into the steam flow of low pressure (LP) cylinder, can realize the operation of high pressure module back pressure operating mode, high pressure module and the operation of low-voltage module steam extraction and condensing formula, high pressure module and three kinds of operating modes of low-voltage module pure condensed steam formula operation, so, can select as required corresponding operating mode, thereby effectively improve the utilization ratio of the energy, there is good economic benefit.
Economic benefit is apparent that the heat supply of north of china in winter steam turbine the most, with the power 300MW of unit, calculates, and getting non-heat supply and be 7 months, normal heat supply phase and be 3 months, high (point) peak heat supply phase is 2 months; 0.4 yuan/KWh of rate for incorporation into the power network, caloric value is by 29 yuan/GJ.Calculating shows 1,600 ten thousand yuan of annual saving energies.Remove 1,000 ten thousand yuan of the manufacture cost value addeds of this steam turbine, this steam turbine also has 6,000,000 yuan of bonus every year.This double-cylinder coaxial combined cycle heat supply steam turbine is a kind of Novel steam turbine equipment of inventing under Gas-steam Combined Cycle and cogeneration double environmental protection theory, the utilization ratio that it improves the energy is to the full extent a kind of efficient energy saving heating combination circulation steam turbine.
The double-cylinder coaxial combined cycle the heat supply steam turbine above embodiment of the present invention being provided is described in detail; for one of ordinary skill in the art; thought according to the embodiment of the present invention; all can change to some extent in specific embodiments and applications; therefore this description is only used in the embodiment of the present invention is described; should not be construed as limitation of the present invention, all any changes of making according to design philosophy of the present invention are all within protection scope of the present invention.
Claims (10)
1. a double-cylinder coaxial combined cycle heat supply steam turbine, it is characterized in that: it comprises a high-pressure modular and a low-voltage module, described high-pressure modular, low-voltage module is coaxially arranged, in described high-pressure modular, be provided with high pressure rotor, in described low-voltage module, be provided with low pressure rotor, described high-pressure modular adopts high pressure cylinder combined structure, counter spreading put, it can be divided into high-pressure cylinder and intermediate pressure cylinder in logic, described high-pressure cylinder following current is arranged, described intermediate pressure cylinder counter-flow arrangement, described high pressure rotor connects with generator near one end of intermediate pressure cylinder, described high pressure rotor coaxially connects with a jack shaft near one end of high-pressure cylinder, the other end of described jack shaft connects with described low pressure rotor by a self-synchronizing clutch, between described high-pressure modular and described low-voltage module, pass through mesolow unicom pipeline UNICOM, described mesolow unicom pipeline is provided with low pressure valve group, described high-pressure modular also with a heat supply extraction line UNICOM, described heat supply extraction line is provided with extraction control valve.
2. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 1, it is characterized in that: senior middle school's pressing cylinder of described high-pressure modular adopts double shell structure, comprise High-and-medium Pressure Outer Casing and high pressure inner casing, described high pressure rotor is positioned at described high pressure inner casing, the low pressure (LP) cylinder of described low-voltage module is double shell structure, comprise lp outer casing and low-pressure internal cylinder, described low pressure rotor is positioned at described low-pressure internal cylinder.
3. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 2, is characterized in that: described high pressure inner casing adopts whole interior cylinder structure.
4. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 2, it is characterized in that: described high-pressure modular is provided with high pressure main stop valve, high pressure speed governing steam valve, middle pressure reheating main steam valve and middle pressure speed governing steam valve, described high pressure main stop valve, high pressure speed governing steam valve is fixed on the first valve casing, described the first valve casing connects with described High-and-medium Pressure Outer Casing by flange, described high pressure main stop valve, high pressure speed governing steam valve and described high-pressure cylinder UNICOM, described middle pressure reheating main steam valve, middle pressure speed governing steam valve is fixed on the second valve casing, described the second valve casing connects with described High-and-medium Pressure Outer Casing by flange, described middle pressure reheating main steam valve, middle pressure speed governing steam valve and described intermediate pressure cylinder UNICOM.
5. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 4, is characterized in that: below described the first valve casing, the second valve casing, be respectively equipped with constant force supporting frame.
6. according to the double-cylinder coaxial combined cycle heat supply steam turbine described in claim 1, it is characterized in that: the rear and front end of described high pressure rotor adopts respectively high pressure fore bearing and high pressure rear bearing to support, the rear and front end of described low pressure rotor adopts respectively low pressure fore bearing and low pressure rear bearing to support, and described jack shaft adopts a stable bearing to support.
7. according to the double-cylinder coaxial combined cycle heat supply steam turbine described in claim 1, it is characterized in that: described high pressure rotor connects with generator by a coupling near one end of intermediate pressure cylinder, described high pressure rotor connects with jack shaft by a synchronous coupling near one end of high-pressure cylinder.
8. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 1, is characterized in that: the free end of described low pressure rotor is provided with jiggering motor.
9. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 1, is characterized in that: described low pressure valve group comprises low pressure main stop valve, low pressure speed governing steam valve and low voltage starting steam valve.
10. double-cylinder coaxial combined cycle heat supply steam turbine according to claim 1, it is characterized in that: described mesolow unicom pipeline also with a combined cycle low pressure steam supply pipe UNICOM, described combined cycle low pressure steam supply pipe is provided with the low pressure filling valve group of regulating and controlling low pressure filling throttle flow.
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| CN102140938A (en) | 2011-08-03 |
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