CN104405457A - Energy cascade utilization system of back pressure turbine heating - Google Patents
Energy cascade utilization system of back pressure turbine heating Download PDFInfo
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- CN104405457A CN104405457A CN201410701906.6A CN201410701906A CN104405457A CN 104405457 A CN104405457 A CN 104405457A CN 201410701906 A CN201410701906 A CN 201410701906A CN 104405457 A CN104405457 A CN 104405457A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
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Abstract
The invention provides an energy cascade utilization system of back pressure turbine heating, the energy cascade utilization system of back pressure turbine heating is driven by the coal-fired power generation set turbine steam extraction and comprises a small turbine and a small electric generator, the small turbine and the small electric generator are connected together through a coupling joint, the steam inlet of the small turbine is connected with the steam inlet pipe, the steam inlet pipe is provided with a steam inlet adjusting valve, the inlet end of the steam inlet pipe is respectively connected with the main steam pipe and the high pressure extraction steam pipe of the main turbine, the steam exhaust port of the small turbine is connected with the industrial steam device, the small electric generator is connected with the station service system of the power plant through the power transmission line, the energy cascade utilization system of back pressure turbine heating further comprises an adjusting system, the adjusting system is composed of the single pump hydraulic governor and the corrugated tube valve type voltage regulator, the single pump hydraulic governor and the corrugated tube valve type voltage regulator are connected in a parallel mode for controlling the back pressure turbine for running according to thermal load or electrical load mode.
Description
Technical field
The present invention relates to a kind of energy gradient utilization system of back pressure turbine heat supply, adopt unit main steam turbine to draw gas and drive back pressure type small turbine generator set, the energy cascade utilization device system of small steam turbine exhaust steam heat supply, belong to coal-fired power generator set field.
Background technique
Current cogeneration units majority adopts main steam turbine extraction for heat supply, and part back pressure type unit adopts the heat supply of main steam turbine steam discharge.The pressure that main steam turbine draws gas, temperature parameter, usually all higher than heat user demand, supply the heat user such as factory steam or municipal administration heating after needing to turn down parameter by temperature-decreased pressure reducer.Desuperheat pressurizer causes main steam turbine to draw gas the loss of energy, affects cogeneration units generating efficiency.Pressure, the temperature of back pressure type unit main steam turbine steam discharge are all lower, usually can not meet the parameter requirements of factory steam, can only for municipal administration heating.
The structure of traditional back pressure steam turbines belongs to prior art, such as in document CN201110196Y, disclose a kind of back pressure turbine, comprise cylinder 7, front-end bearing pedestal 2, rear bearing block 10, be supported on front-end bearing pedestal 2, chassis 21 on the downside of rear bearing block 10, front-end bearing pedestal 2 is provided with speed regulator 1, the bearing 3 of support rotor 11 is installed in front-end bearing pedestal 2, bearing 4, front-end bearing pedestal 2 is provided with thermometer 5, Curtis wheel blade 8 in cylinder 7 is arranged on rotor 11, packing 9 is provided with between cylinder 7 and rotor 11, cylinder 7 body is provided with exhaust steam pipe 6, the rotor 11 of rear bearing block 10 side is provided with coupling 12, nozzle sets 19 is installed bottom the vaporium of cylinder 7 and turns to guide vane ring 20, front-end bearing pedestal 2, the distance at rear bearing block 10 impeller blade 8 center in the side of cylinder 7 and cylinder 7 is 361.5cm, the internal diameter of impeller blade 8 is 130cm, external diameter is 400cm, before and after cylinder 7, the exhaust steam pipe 6 of both sides is 291.5cm with the distance at impeller blade 8 center, the front end of cylinder 7 is provided with main stop valve 13, emergency governor, overspeed governor 16, servo valve connecting rod 18, emergency governor, overspeed governor connecting rod 17 is provided with between emergency governor, overspeed governor 16 and main stop valve 13, the downside of main stop valve 13 is provided with steam valve mounting 14, the initial steam pressure of this steam turbine is 2.5Mpa, throttle (steam) temperature 350 DEG C, exhaust steam pressure is 0.4Mpa, power range is 75KW, rated speed is 3000rpm/min, tripping operation rotating speed is 3320rpm/min.This back pressure turbine can meet the requirement of user to product power accurately, has saved the energy
Document CN201301734U also discloses a kind of back pressure turbine, eliminates former unit 4 ~ 13 stage pressure level, retains wherein 4, 8 ~ 12 pressure level impellers, as counterweight block, arrange midsplit type shutoff volute and back pressure steam-expelling port at middle cylinder, do corresponding transformation simultaneously to set auxiliary machinery part, and improved back pressure turbine back pressure turbine, by front bearing box, thrust radial journal bearing, high pressure steam room, front cylinder, dual row governing stage, 2nd stage pressure level, 3rd level pressure level, middle cylinder, midsplit type shutoff volute, counterweight block, exhaust casing, rear bearing block forms, and thrust radial journal bearing is positioned at front bearing box, and front bearing box is connected with front cylinder according to structure with high pressure steam room, and the rotor between front cylinder and middle cylinder is designed with dual row governing stage, 2nd stage pressure level, 3rd level pressure level, rear bearing block is positioned at exhaust casing, arranges midsplit type shutoff volute at middle cylinder, back pressure steam-expelling port and counterweight block, and counterweight block be former condensing steam turbine the 4th, the impeller of 8 ~ 12 pressure levels.Cylinder after the built-in back pressure of midsplit type shutoff volute, gusset and built-in packing composition, reduces steam steam discharge volume, and tail wind loss reduces greatly, and unit efficiency improves; Special Profile Design ensures that spiral case intensity is run under various bad working environments condition to meet steam turbine, ensures the requirement of back pressure exhaust steam pressure simultaneously.The single-cylinder structure of three sections of compositions before, during and after condensed steam type 12MW through-flow structure of steam turbine before transformation adopts, flow passage component is made up of 1 dual row governing stage and 12 pressure levels, and front cylinder high pressure steam room configures 6 50-60 servo valves; Fore bearing is that thrust supports joint bearing, rear radial journal bearing is elliptic bearing.Improved back pressure turbine is through-flow, and structure comprises: (1) transforms turbine rotor, retain former velocity-compounded stage and two pressure levels, pressure level blades all after removing 4 ~ 13 grades, impeller remain and use as balancing weight, and front steam seal changes Φ 300 into reduce unit end thrust by Φ 445mm.(2) before and after, cylinder is not changed, and middle cylinder carries out transforming to install horizontal midsplit type shutoff volute additional, and sets up new rear shaft seal at volute place, arranges back pressure steam-expelling port; Former exhaust casing still retains the support unit to be used as No. 2 bearings.(3) by the servo valve of former six latus rectums (φ 50 ~ 60) mm, the servo valve of six φ 70mm is replaced with to increase admission ability.(4) improved forward and backward bearing centre distance is constant, constant with the Placement of generator.Thus ensure that former steam turbine-generatot set foundation design size is constant.Regulating system: former regulating system is constant, increases back pressure exhaust steam pressure protective gear.Thermodynamic system: (1) back pressure turbine is identical with the design conditions of condensing steam turbine or close, the parameter of main vapour and water supply system, part backheat device systems (comprising high-pressure heater, higher-pressure deaerator etc.) all changes not quite, therefore continues to retain and use.(2) gland heater with 2 Fans (1 open 1 standby) is newly set, for setting up the air system of back pressure machine, to receive the air-discharging of a bar, gland packing leakage and heater.(3) vapour condenser is abandoned, and rubber ball cleaning, water jet air suction system are abandoned, and circulation is stopped transport, and (the boost cycle cooling water system of accessory is gone in reservation.(4) hydrophobic pipeline does corresponding change, retains former hydrophobic expansion tank.(5) increase back pressure exhaust line, back pressure pipeline is set up check valve, safety valve.(6) sealing system transformation, the front steam seal diameter before transformation is 445mm, and wherein front steam seal first grade leaks vapour to high-pressure heater, and second gear leaks vapour to surge tank, and third gear leaks vapour to gland heater.After transforming, front steam seal diameter is 300mm, and reducing packing diameter is that guarantee transforms the end thrust of rear unit in the reasonable scope.Wherein front steam seal first grade leaks vapour to high-pressure heater (remaining unchanged with before transformation), and second gear leaks vapour to the gland heater newly increased, and because back pressure machine Steam loss is comparatively large, former unit surge tank can not meet the large requirement of Steam loss.Third gear leaks vapour still to gland heater (remaining unchanged with before transformation).Built-in packing first grade leaks vapour to the gland heater newly increased, and second gear leaks to former gland heater.The former rear packing of unit remains unchanged.Condensing steam turbine is transform as back pressure type steam turbine machine technology for improving unit efficiency, reducing coal consumption, make same type units after transformation, again be able to utilization and provide effective way; Do not do in guarantee unit external structure and change, only flow passage component is transformed.Which provide one with low cost, low input to obtain the effective ways of high benefit.
Traditional main steam turbine extraction for heat supply and back pressure type unit adopt the heat supply of main steam turbine steam discharge reasonable all not to the utilization of the energy of steam, temperature-decreased pressure reducer is needed to turn down steam parameter, cause energy waste, pressure, the temperature of steam discharge are too low, the parameter requirements of factory steam cannot be met, can only for municipal administration heating.
Summary of the invention
In order to solve above technical problem, the present invention proposes a kind of energy gradient utilization system of back pressure turbine heat supply, adopts Thermal generation unit extracted steam from turbine to drive, designing with steam pressure, temperature, flow according to heat user.The main steam of unit or the high pressure extraction of main steam turbine control the generating of flow rear driving small turbine generator set through electric control valve, and the steam discharge of small turbine meets the pressure of factory steam, temperature, traffic demand, directly supplies factory steam.Small turbine generator set generate electricity and can access the station service electrical system of power plant, for the subsidiary engine equipment of drive train.
According to a first aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, comprise small steam turbine and small generator, connected by coupling between small steam turbine and small generator, the steam inlet of small steam turbine is communicated with steam inlet pipe, steam inlet pipe is provided with admission modulating valve, steam inlet pipe entry end is communicated with the high pressure extraction pipe of main steam turbine respectively with main steam pipe, the steam-expelling port of small steam turbine is communicated with factory steam equipment, and small generator is connected with the station service electrical system of power plant by electric transmission line.
According to a second aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, is characterized in that, described back pressure turbine is driven by Thermal generation unit extracted steam from turbine.
According to a third aspect of the invention we, the energy gradient utilization system of back pressure turbine heat supply of the present invention, it is characterized in that, also comprise regulating system, this regulating system is formed by being with single pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor, and described band list pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor are arranged in parallel.
Because back pressure turbine takes into account generating and heat supply (namely to factory steam equipment steam supply), regulating system needs adjusting rotary speed and back pressure two parameters.Have corresponding relation between generated energy and heating load, displacement and the throttle flow of back pressure turbine have corresponding relation.If the steam supplying amount that factory steam equipment needs increases, just need the throttle flow increasing steam turbine, such generated energy will increase accordingly.Heating load depend on maximum generating watt to greatest extent, that is the method for operation of back pressure turbine will regulate according to heat load (i.e. the steam consumption of factory steam equipment needs), now the admission modulating valve of back pressure turbine controls by corrugated tube list sliding valve style pressure governor, the steam consumption needed due to factory steam equipment is often change, need to ensure that the exhaust pressure of back pressure turbine stablizes the needs that could meet within the specific limits with vapour, pressure governor must be adopted to keep the method for operation of heat load, under the effect of pressure governor, the steam consumption that steam turbine throttle flow needs with factory steam equipment and changing, the power that generator sends also changes thereupon, steam consumption increases, just increased by the steam flow of steam turbine, the generated output of generator also increases, otherwise steam consumption reduces, just reduced by the steam flow of steam turbine, the generated output of generator also reduces.In this case, the electric energy that generator sends at all cannot with the needs of user to balance, usually should be connected to the grid operation, allow the rotating speed of unit and synchronized, because the frequency of electrical network is maintained jointly by unit in net, more stable comparatively speaking, now the rotating speed of back pressure turbine need not adjust, and the main task of regulating system maintains stablizing of exhaust pressure.
If need to run by electric load mode, pressure governor is for exit status, steam turbine is run under speed regulator controls, the electric load of guarantee station service electrical system and the throttle flow of steam turbine are to balance, guarantee that rotating speed is at rating number, but can not ensure that the air displacement of steam turbine and the desired steam consumption of heat user balance each other.
According to a forth aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, is characterized in that, described band list pump hydraulic speed governor comprises Speed sensing mechanism, transfer mechanism and the institution of distributing gas; Described pressure governor is pressure sensitive mechanism, receives the change pulse of back pressure, and then regulates according to the change of back pressure the steam flow entering steam turbine.
According to a fifth aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, it is characterized in that, described Speed sensing mechanism is hydraulic type, be made up of radial bore pump, oil gun and pressure transducer, the change of rotating speed is converted to the change of outlet oil pressure by radial bore pump, and the guiding valve of pilot pressure transducer is subjected to displacement, and changes pulse oil pressure; Radial bore pump is directly driven by turbine spindle, and oil gun is to the import fuel feeding of radial bore hole pump, and when steam turbine rotates, radial bore pump impeller rotation generation centrifugal force makes fluid pressure raise.
According to a sixth aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, is characterized in that, square being directly proportional of the oil pressure increment of described radial bore pump and rotating speed.
According to a seventh aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, is characterized in that, described oil gun comprises nozzle, diffuser pipe and mixing chamber; When the high pressure oil of radial bore pump penetrates from nozzle at high speeds, the oil stream of mixing chamber penetrates from diffuser pipe with high pressure oil under ejector action, the formation low pressure area simultaneously in mixing chamber, thus oil is supplied the import of radial bore pump.
According to an eighth aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, is characterized in that, the oil pressure variable signal of radial bore pump is transformed into the displacement of guiding valve by described pressure transducer, and handles transfer mechanism thus.
According to a ninth aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, it is characterized in that, the described institution of distributing gas comprises admission modulating valve driving mechanism, regulates for driving admission modulating valve the steam flow entering steam turbine.
According to the tenth aspect of the invention, the energy gradient utilization system of back pressure turbine heat supply of the present invention, it is characterized in that, the variable signal of described transfer mechanism receiving belt list pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor also amplifies, and then handle the admission modulating valve driving mechanism of the institution of distributing gas, regulate for driving admission modulating valve the steam flow entering steam turbine.
Accompanying drawing explanation
Fig. 1 is the overall schematic of the energy gradient utilization system of the back pressure turbine heat supply described in the application.
Embodiment
As shown in Figure 1, the energy gradient utilization system of back pressure turbine heat supply of the present invention, comprise small steam turbine 2 and small generator 4, connected by coupling 3 between small steam turbine and small generator, the steam inlet of small steam turbine is communicated with steam inlet pipe, steam inlet pipe is provided with admission modulating valve 1, steam inlet pipe entry end is communicated with the high pressure extraction pipe of main steam turbine respectively with main steam pipe, the steam-expelling port of small steam turbine is communicated with factory steam equipment, and small generator is connected with the station service electrical system of power plant by electric transmission line.Small steam turbine 2 is back pressure turbine.
The high pressure extraction of main steam or main steam turbine via small steam turbine admission modulating valve 1 control flow laggard enter small steam turbine 2.The steam discharge supply factory steam of small steam turbine 2.Small steam turbine 2 drives small generator 4 to generate electricity by coupling 3, generate electricity and can access the station service electrical system of power plant.
Described back pressure turbine is driven by Thermal generation unit extracted steam from turbine.
The energy gradient utilization system of described back pressure turbine heat supply also comprises regulating system, this regulating system is formed by being with single pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor, and described band list pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor are arranged in parallel.
Because back pressure turbine takes into account generating and heat supply (namely to factory steam equipment steam supply), regulating system needs adjusting rotary speed and back pressure two parameters.Have corresponding relation between generated energy and heating load, displacement and the throttle flow of back pressure turbine have corresponding relation.If the steam supplying amount that factory steam equipment needs increases, just need the throttle flow increasing steam turbine, such generated energy will increase accordingly.Heating load depend on maximum generating watt to greatest extent, that is back pressure turbine the method for operation otherwise regulate according to heat load (i.e. factory steam equipment need steam consumption), now the admission modulating valve of back pressure turbine controls by corrugated tube list sliding valve style pressure governor, the steam consumption needed due to factory steam equipment is often change, need to ensure that the exhaust pressure of back pressure turbine stablizes the needs that could meet within the specific limits with vapour, pressure governor must be adopted to keep the method for operation of heat load, under the effect of pressure governor, the steam consumption that steam turbine throttle flow needs with factory steam equipment and changing, the power that generator sends also changes thereupon, steam consumption increases, just increased by the steam flow of steam turbine, the generated output of generator also increases, otherwise steam consumption reduces, just reduced by the steam flow of steam turbine, the generated output of generator also reduces.In this case, the electric energy that generator sends at all cannot with the needs of user to balance, usually should be connected to the grid operation, allow the rotating speed of unit and synchronized, because the frequency of electrical network is maintained jointly by unit in net, more stable comparatively speaking, now the rotating speed of back pressure turbine need not adjust, and the main task of regulating system maintains stablizing of exhaust pressure.
If need to run by electric load mode, pressure governor is for exit status, steam turbine is run under speed regulator controls, the electric load of guarantee station service electrical system and the throttle flow of steam turbine are to balance, guarantee that rotating speed is at rating number, but can not ensure that the air displacement of steam turbine and the desired steam consumption of heat user balance each other.
Described band list pump hydraulic speed governor comprises Speed sensing mechanism, transfer mechanism and the institution of distributing gas; The described institution of distributing gas comprises admission modulating valve driving mechanism, regulates for driving admission modulating valve the steam flow entering steam turbine.Described pressure governor is pressure sensitive mechanism, receives the change pulse of back pressure, and then regulates according to the change of back pressure the steam flow entering steam turbine.Pressure governor is primarily of corrugated tube, guiding valve, Compress Spring, pressure governor handwheel and eccentric wheel composition, when heat load increases, back pressure declines, and corrugated tube extends downwards, and thimble band movable pulley moves down, when guiding valve moves down, drive the admission modulating valve driving mechanism of the institution of distributing gas, make admission modulating valve open greatly, increase the throttle flow entering steam turbine; When heat load reduces, working procedure is contrary to the above.
Described Speed sensing mechanism is hydraulic type, is made up of radial bore pump, oil gun and pressure transducer, and the change of rotating speed is converted to the change of outlet oil pressure by radial bore pump, and the guiding valve of pilot pressure transducer is subjected to displacement, and changes pulse oil pressure; Radial bore pump is directly driven by turbine spindle, and oil gun is to the import fuel feeding of radial bore hole pump, and when steam turbine rotates, radial bore pump impeller rotation generation centrifugal force makes fluid pressure raise.Square being directly proportional of the oil pressure increment of described radial bore pump and rotating speed.The working principle of radial bore pump is when external load reduces or increase, namely the rotating speed of steam turbine leaves stabilized (steady-state) speed and rises or decline, due to square being directly proportional of oil pressure increment and rotating speed of radial bore pump, the Speed sensing element of this characteristic as speed control system of this pump therefore can be utilized.
Described oil gun comprises nozzle, diffuser pipe and mixing chamber; When the high pressure oil of radial bore pump penetrates from nozzle at high speeds, the oil stream of mixing chamber penetrates from diffuser pipe with high pressure oil under ejector action, the formation low pressure area simultaneously in mixing chamber, thus oil is supplied the import of radial bore pump.
The oil pressure variable signal of radial bore pump is transformed into the displacement of guiding valve by described pressure transducer, and handles transfer mechanism thus.The variable signal of described transfer mechanism receiving belt list pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor also amplifies, and then handles the admission modulating valve driving mechanism of the institution of distributing gas, for regulating the steam flow entering steam turbine.
Systems approach of the present invention is illustrated with reference to exemplary process figure and explains.Based on description above, additional variants and modifications is apparent for those of ordinary skills, and within the protection domain all falling into the application, and protection scope of the present invention is determined by appended claim.
Claims (10)
1. the energy gradient utilization system of a back pressure turbine heat supply, it is characterized in that, comprise small steam turbine and small generator, connected by coupling between small steam turbine and small generator, the steam inlet of small steam turbine is communicated with steam inlet pipe, steam inlet pipe is provided with admission modulating valve, steam inlet pipe entry end is communicated with the high pressure extraction pipe of main steam turbine respectively with main steam pipe, the steam-expelling port of small steam turbine is communicated with factory steam equipment, and small generator is connected with the station service electrical system of power plant by electric transmission line.
2. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 1, it is characterized in that, described back pressure turbine is driven by Thermal generation unit extracted steam from turbine.
3. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 2, it is characterized in that, also comprise regulating system, this regulating system is formed by being with single pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor, and described band list pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor are arranged in parallel.
4. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 3, it is characterized in that, described band list pump hydraulic speed governor comprises Speed sensing mechanism, transfer mechanism and the institution of distributing gas; Described pressure governor is pressure sensitive mechanism, receives the change pulse of back pressure, and then regulates according to the change of back pressure the steam flow entering steam turbine.
5. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 4, it is characterized in that, described Speed sensing mechanism is hydraulic type, be made up of radial bore pump, oil gun and pressure transducer, the change of rotating speed is converted to the change of outlet oil pressure by radial bore pump, the guiding valve of pilot pressure transducer is subjected to displacement, and changes pulse oil pressure; Radial bore pump is directly driven by turbine spindle, and oil gun is to the import fuel feeding of radial bore hole pump, and when steam turbine rotates, radial bore pump impeller rotation generation centrifugal force makes fluid pressure raise.
6. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 5, is characterized in that, square being directly proportional of the oil pressure increment of described radial bore pump and rotating speed.
7. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 6, it is characterized in that, described oil gun comprises nozzle, diffuser pipe and mixing chamber; When the high pressure oil of radial bore pump penetrates from nozzle at high speeds, the oil stream of mixing chamber penetrates from diffuser pipe with high pressure oil under ejector action, the formation low pressure area simultaneously in mixing chamber, thus oil is supplied the import of radial bore pump.
8. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 5, it is characterized in that, the oil pressure variable signal of radial bore pump is transformed into the displacement of guiding valve by described pressure transducer, and handles transfer mechanism thus.
9. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 8, it is characterized in that, the described institution of distributing gas comprises admission modulating valve driving mechanism, regulates for driving admission modulating valve the steam flow entering steam turbine.
10. the energy gradient utilization system of back pressure turbine heat supply as claimed in claim 9, it is characterized in that, the variable signal of described transfer mechanism receiving belt list pump hydraulic speed governor and corrugated tube list sliding valve style pressure governor also amplifies, and then handle the admission modulating valve driving mechanism of the institution of distributing gas, regulate for driving admission modulating valve the steam flow entering steam turbine.
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| CN201410701906.6A CN104405457B (en) | 2014-11-28 | 2014-11-28 | A kind of energy gradient utilization system of back pressure turbine heat supply |
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| CN201410701906.6A CN104405457B (en) | 2014-11-28 | 2014-11-28 | A kind of energy gradient utilization system of back pressure turbine heat supply |
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| CN104405457A true CN104405457A (en) | 2015-03-11 |
| CN104405457B CN104405457B (en) | 2015-07-29 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108539881A (en) * | 2018-05-24 | 2018-09-14 | 江苏金通灵流体机械科技股份有限公司 | A kind of Turbo-generator Set device that more quality steams are provided |
| CN112523824A (en) * | 2020-11-23 | 2021-03-19 | 国能(泉州)热电有限公司 | Heat supply system and heat supply method |
| CN112610290A (en) * | 2020-12-10 | 2021-04-06 | 宜昌华直能源开发有限公司 | Automatic putting-in method of temperature and pressure reducer |
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| CN204238990U (en) * | 2014-11-28 | 2015-04-01 | 中国华能集团公司 | A kind of energy gradient utilization system of back pressure turbine heat supply |
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| CN2396184Y (en) * | 1999-09-03 | 2000-09-13 | 中国长江动力公司(集团) | Below 50 MW condensing steam turbine for power supplying and heating |
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| CN112523824A (en) * | 2020-11-23 | 2021-03-19 | 国能(泉州)热电有限公司 | Heat supply system and heat supply method |
| CN112610290A (en) * | 2020-12-10 | 2021-04-06 | 宜昌华直能源开发有限公司 | Automatic putting-in method of temperature and pressure reducer |
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| CN104405457B (en) | 2015-07-29 |
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