CN110656991B - Injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance - Google Patents
Injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance Download PDFInfo
- Publication number
- CN110656991B CN110656991B CN201911073326.6A CN201911073326A CN110656991B CN 110656991 B CN110656991 B CN 110656991B CN 201911073326 A CN201911073326 A CN 201911073326A CN 110656991 B CN110656991 B CN 110656991B
- Authority
- CN
- China
- Prior art keywords
- steam
- pressure
- pressure cylinder
- inlet
- medium
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000009826 distribution Methods 0.000 title claims abstract description 59
- 238000002347 injection Methods 0.000 title claims abstract description 26
- 239000007924 injection Substances 0.000 title claims abstract description 26
- 230000008878 coupling Effects 0.000 title abstract description 6
- 238000010168 coupling process Methods 0.000 title abstract description 6
- 238000005859 coupling reaction Methods 0.000 title abstract description 6
- 238000000605 extraction Methods 0.000 claims abstract description 33
- 238000000034 method Methods 0.000 claims abstract description 32
- 238000010248 power generation Methods 0.000 claims abstract description 28
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 12
- 230000001105 regulatory effect Effects 0.000 claims description 13
- 230000007246 mechanism Effects 0.000 claims description 9
- 230000008569 process Effects 0.000 claims description 9
- 238000006467 substitution reaction Methods 0.000 claims description 4
- 238000004458 analytical method Methods 0.000 claims description 3
- 230000008859 change Effects 0.000 claims description 3
- 102220078862 rs77460377 Human genes 0.000 claims description 2
- 102220030750 rs7987664 Human genes 0.000 claims description 2
- 238000004064 recycling Methods 0.000 claims 3
- 102220107940 rs11464 Human genes 0.000 claims 1
- 238000010438 heat treatment Methods 0.000 abstract description 10
- 238000007599 discharging Methods 0.000 abstract 2
- 239000007789 gas Substances 0.000 description 28
- 238000004080 punching Methods 0.000 description 6
- 238000001816 cooling Methods 0.000 description 5
- 230000009466 transformation Effects 0.000 description 5
- 230000005611 electricity Effects 0.000 description 4
- 239000002918 waste heat Substances 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005485 electric heating Methods 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000003546 flue gas Substances 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000005622 photoelectricity Effects 0.000 description 1
- 239000002994 raw material Substances 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
- 239000000779 smoke Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
An injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance belongs to the technical field of cogeneration and central heating. To the problem that the current thermal power of the thermal power plant needs to increase the power generation load simultaneously when the current thermal power is involved, a decoupling injection device is arranged, wherein a high-pressure driving steam inlet of a gas distribution injector is connected with a new steam pipe, a low-pressure steam inlet is connected with a high-pressure cylinder steam discharging cold re-pipe, a medium-pressure steam discharging outlet is connected with a boiler reheater inlet, a steam outlet is arranged on the boiler reheater outlet hot re-pipe to extract required high-pressure steam, an external steam supplying outlet is not arranged on the cold re-pipe, and all high-pressure steam is sent out after being compressed by the injector, and the system control method comprises the following steps: the external steam extraction amount of the heat re-pipe is equal to the sum of the driving steam amount and the temperature-increasing water amount of the distribution ejector; the steam inlet quantity of the high-pressure cylinder and the steam inlet quantity of the low-pressure cylinder are changed in an approximately equal proportion; and according to the safe decoupling model and the decision and demand curves thereof, adjusting the optimal injection ratio of the ejector, and realizing stepless adjustment of complete thermal decoupling.
Description
Technical Field
The invention relates to an injection distribution thermal decoupling mode based on axial thrust balance and reheat balance, and belongs to the technical field of cogeneration and central heating.
Background
Under the background of current industrial development and structure adjustment, the current situation of serious surplus in the production of Chinese electric power causes a large amount of electricity discarding situations of wind power, photoelectricity and the like, so that a large-scale thermal generator set is required to participate in peak shaving. The cogeneration system usually adopts a running mode of heat fixed electricity or electricity fixed heat due to the inherent characteristics of heat and electricity, so that the national energy agency and the like take out various policy measures to promote the thermoelectric decoupling, the deep peak shaving and the flexibility transformation of the thermal power generation, the main power unit requiring the flexibility transformation mainly comprises 300MW level 880, 600MW level 481 and 1361 total power unit, the capacity of the total assembly machine is about 7 hundred million kilowatts, and the total transformation investment is estimated to reach the grade of billions in recent years.
At present, heating and steam extraction of a main heat supply unit in China are generally carried out by exhausting a medium-pressure cylinder, and when the heat supply capacity is maximum, the electric load rate is generally about 80 percent and is larger than the load rate, and the heat supply capacity is suddenly reduced due to the limitation of the evaporation capacity of a boiler; when the electric heating load is smaller than the preset value, the flow rate of the steam turbine is reduced, and the steam extraction flow rate is also reduced, so that the electric heating load is mutually related and restrained. The main tasks and essence of the current thermal decoupling are: on the premise of meeting the great increase of heat supply requirements, the power generation load rate is greatly reduced. The complete thermal decoupling scheme must solve the following six basic problems: firstly, the problem of overheat of a reheater caused by overheat of a boiler and unbalance of reheat steam flow is solved; secondly, the problem of rotor thrust balance of the turbo generator set is solved; thirdly, the problem of safe and stable operation; fourthly, the problem of running economy; fifthly, how to realize a large-scale problem; and sixthly, the investment is saved. The first two problems, which are the most central, are the technological preconditions that any technical solution is established.
Based on the above analysis, the existing thermal decoupling schemes and their main problems are summarized as follows: the heat storage scheme and the electric boiler scheme have large occupied area and investment scale, and cannot be completely and deeply decoupled; the low-pressure cylinder zero-output transformation comprises an optical axis scheme, and a scheme of directly reducing or closing the steam inlet of the low-pressure cylinder and additionally introducing a small amount of cooling steam to cool the final stage and the steam outlet, so that the influence on the increase of heat supply is not great; the high-low side joint steam distribution scheme has the problems that the recent pressure of the reheater is greatly reduced due to the great reduction of the steam inlet amount of a steam turbine at the low power generation load rate, so that the volume flow is greatly increased, the through-flow capacity and the heat exchange amount of the reheater are greatly reduced, the flue gas temperature of the reheater is difficult to effectively reduce, and the reheater and the subsequent heating surfaces thereof are overtemperature and damaged; the perforation and steam extraction of the cylinder, the heating of low vacuum circulating water and the like can not effectively reduce the power generation load rate; the main steam is directly used for punching and extracting steam, or a cold section pipeline (cold re) of a reheater at a steam discharge outlet of a high-pressure cylinder is used for punching and extracting steam, or a hot section (hot re) of the reheater outlet is used for punching and extracting steam, so that the power generation load rate can be greatly reduced, but a series of safety problems such as overheating of the reheater, overrun of the axial thrust of a steam turbine and the like are necessarily caused when the steam extraction amount is large.
The complete thermoelectric decoupling scheme can be realized by adopting an injection type steam pressure matching technology and an injection type heat pump exhaust steam waste heat recovery technology, wherein the following pre-developed patent technical achievements provide a technical basis for realizing comprehensive thermal decoupling by adopting an injection gas distribution technology, and the method comprises the following steps: multichannel water vapor ejectors (patent number: 200820188000.9, inventor: zhu Jianwen, etc.); a joint ejector (application number: 201410416461.7, inventor: zhu Jianwen, etc.); a multi-effect cascade jet heat pump and a high pressure ratio vacuum pump (patent number: 201120510397.0, inventor: zhang Maoyong, etc.); waste steam waste heat recovery cogeneration system based on multi-effect cascade jet type heat exchange (patent number: 201110407567.7, inventor: zhang Maoyong, etc.); a low vacuum injection type heat pump combined super-large temperature difference heat supply network waste heat heating system (patent number: 201320570436.5, inventor: zhang Maoyong, etc.).
Disclosure of Invention
The invention aims at solving the inherent problems in the deep thermal electrolytic coupling, adopts a gas distribution ejector and a gas supply ejector, and steplessly adjusts the high-pressure steam and the low-pressure steam flow of the ejector according to a proportion, thereby realizing the cooling heat exchange balance of a reheater and the axial thrust balance of a steam turbine, fundamentally ensuring the safe operation of a machine furnace and realizing the thermal electrolytic coupling to the greatest extent.
The working mechanism and the technical path according to the invention are briefly described below. The essence of solving the first problem is that the problems of too low inlet steam flow of the reheater, too small cooling heat requirement, smoke Wen Chaowen and overtemperature of the reheater and the heating surface after the reheater are prevented; the essence of solving the second problem is that the reduction of the power generation load rate necessarily requires the reduction of the steam inflow of the steam turbine, but if the steam inflow of the high-pressure cylinder and the medium-pressure cylinder is unbalanced in amplitude, the axial thrust imbalance is caused, the thrust bearing range is exceeded, and the safety problem of the steam turbine is caused. Therefore, the two problems of directly punching holes on the main steam pipeline, the cold re-heating pipeline and the hot re-heating pipeline are not necessarily solved, a gas distribution ejector is adopted to extract part of new steam as driving steam, the cold re-heating steam is ejected, the exhaust pressure is increased, the specific volume and the volume flow are reduced, and when the new steam is sent to the boiler reheater for reheating, the mass flow can be ensured to meet the requirement of cooling heat exchange quantity, and the overtemperature problem of the reheater is avoided. The steam after hot re-extraction is sent to the medium pressure cylinder, the steam inlet flow of the medium pressure cylinder and the steam inlet flow of the high pressure cylinder are regulated in proportion, and the steam can be carried out through a gas distribution ejector and a related regulating valve, so that the axial thrust of the steam turbine is always in a balanced state. The system control method comprises the following steps: the external steam extraction amount of the hot re-pipeline is equal to the sum of the hot water addition and subtraction flow of the driving steam amount of the distribution ejector; the steam inlet quantity of the high-pressure cylinder and the steam inlet quantity of the low-pressure cylinder are changed in an approximately equal proportion; the optimal injection ratio of the injector is adjusted accordingly, and the stepless adjustment of complete thermal electrolytic coupling is realized.
The specific description of the invention is as follows: the system comprises boiler superheated steam, a reheater, a high-pressure cylinder of a steam turbine, a medium-pressure cylinder, a low-pressure cylinder, a generator, a decoupling injection device and a connecting pipeline, wherein the decoupling injection device comprises a gas distribution injector 20, a high-pressure driving steam inlet 21 of the gas distribution injector 20 is connected with a main steam pipe 9 between an outlet of a superheater 3 of a boiler 1 and an inlet of a high-pressure cylinder 4, a low-pressure steam inlet 22 of the gas distribution injector 20 is connected with a steam outlet of the high-pressure cylinder 4 through a cold re-pipe 12, a medium-pressure steam outlet 23 of the gas distribution injector 20 is connected with an inlet of the reheater 2 of the boiler 1 through a gas distribution attemperator 24 and a gas distribution check valve 25, and a steam outlet of the reheater 2 is connected with a steam inlet of the medium-pressure cylinder 5 through a hot re-pipe 13 and is also communicated with a high-pressure steam user Y1 through a high-pressure attemperator 27.
The cold return pipe 12 is provided with a cold return check valve 26, the inlet and outlet of which are respectively connected with the low pressure steam inlet 22 and the medium pressure steam outlet 23 of the distribution ejector 20.
The cold return pipe 12 is not provided with an external supply steam extraction port.
The main steam pipe 9 is not provided with an external steam supply and extraction port.
The injection gas distribution thermal decoupling mode based on axial thrust balance and reheat balance has the following working method and scheduling control method.
I. When the external steam supply demand of the hot re-pipe (13) is 0, the actuating mechanism of the high-pressure driving steam inlet (21) is closed, and the steam flow of the cold re-check valve (26) is larger than zero;
When the external steam supply demand of the hot re-pipe (13) is greater than 0, an actuating mechanism of a high-pressure driving steam inlet (21) is opened, the opening of the actuating mechanism is increased along with the external steam supply, steam of the cold re-pipe (12) enters a low-pressure steam inlet (22), and if the power generation load demand is kept unchanged, the steam inlet of the high-pressure cylinder (4) and the steam inlet of the medium-pressure cylinder (5) are kept unchanged, and the steam flow of the cold re-check valve (26) is zero at the moment;
When the power generation load demand changes, the steam inlet of the high pressure cylinder (4) and the steam inlet of the medium pressure cylinder (5) are simultaneously adjusted, and the two steam inlet are maintained to be adjusted in an approximately equal proportion so as to ensure the axial thrust balance of the turbine, and if the external steam supply demand of the heat re-pipe (13) is maintained unchanged, the new steam quantity of the superheater (3) is also maintained unchanged, and if the external steam supply demand is changed, the new steam quantity of the superheater (3) is also changed, wherein the quantity is determined according to the following relation: external steam demand = new steam quantity + reduced temperature water quantity;
and iv, when only the high-pressure steam extraction quantity is regulated, the safe decoupling model and the decision method are as follows:
The safe decoupling base model is as follows: the variable symbols are defined as follows: g2 boiler superheater new steam quantity; g3 reheater steam inlet; g41 high-pressure cylinder steam inlet quantity; g42 high pressure cylinder exhaust; g10 high side total steam volume; g11 high bypass flow; the G21 gas distribution ejector drives the steam quantity; g22 gas distribution ejector low pressure gas inlet quantity; medium-pressure exhaust gas quantity of G23 gas distribution ejector; g24 air distribution ejector is matched with the temperature-reducing water quantity; g51 medium pressure cylinder steam inlet amount; g61, steam inlet amount of a medium-pressure cylinder; GY1 heat is supplied to the outside for steam extraction; GY2 medium-pressure external steam extraction quantity; w0 is the power generation load of the turbine unit, MW; w4, W5 and W6 are respectively the power generation loads of the high, medium and low pressure cylinders, MW; only the high-pressure steam supply GY1 is considered temporarily, and the external steam supply and extraction quantity of the medium-pressure cylinder and the low-pressure cylinder is not considered; GY1 and W0 are two external independent variables, wherein W0=W4+W5+W6, the generated energy W6 of the low pressure cylinder is taken as an input variable of the model, and the sum W45=W4+W5=W0-W6 of the generated energy of the high pressure cylinder and the generated energy of the medium pressure cylinder can be taken as the independent variable instead of W0 during analysis of the model; the high-pressure cylinder is provided with the ratio of the exhaust steam quantity to the inlet steam quantity under the safe operation condition as R4=G42/G41 because of the in-plant process air extraction such as high-addition steam and the like; based on the axial thrust balance of the steam turbine, setting the flow ratio of the medium pressure cylinder to the high pressure cylinder to be unchanged, namely, R54=G51/G41 is unchanged, and then G5=G4×R54; the matched water reducing amount G24 of the air distribution ejector can be considered to be changed in proportion to the medium-pressure exhaust amount G23 of the air distribution ejector, further is changed in proportion to the steam inlet amount G3 of the reheater, and is set as G24=k×G3, wherein k is a coefficient;
And (II) a decision curve of the steam inlet quantity of the high-pressure cylinder: g41 =f4 (W45), where function F4 depends on turbine characteristics;
And (III) a decision curve of the steam inlet quantity of the medium pressure cylinder: g51 =f4 (W45) R54;
(IV) a demand curve of the steam inlet quantity of the reheater: g2 =f4 (W45) r54+gy1;
(V) decision curve of superheater fresh steam quantity: g3 = (F4 (W45) × (r54+r4-1) +gy1)/(1+k);
the scheduling and decision process of the thermocouple operation is as follows:
i) If the power generation load W0 and the substitution variable W45 are unchanged and the heat re-supply steam extraction GY1 is changed, adjusting G3 only according to a decision curve of the new steam quantity of the superheater and adjusting G2 according to a demand curve of the steam inlet quantity of the reheater;
ii) if the heat re-external steam supply GY1 is unchanged and the power generation load W0 is changed, under the condition that the power generation load W6 of the low pressure cylinder is changed by itself, the load demand of W45 is changed correspondingly, G3 is adjusted according to the decision curve of the new steam quantity of the superheater, G41 is adjusted according to the decision curve of the steam inlet quantity of the high pressure cylinder, the steam inlet quantity G51 of the medium pressure cylinder is adjusted correspondingly and approximately in the same proportion, and then the steam inlet quantity G2 of the reheater is adjusted;
iii) If two external variables W0 and GY1 change at the same time, the adjustment is still performed with reference to the step in decision method (B) described above;
And v. when not only the high-pressure steam extraction quantity is regulated, but also the steam extraction quantity of the medium-pressure cylinder is regulated, the external variable of the medium-pressure external steam supply GY2 and a model equation thereof are added on the basis of the safe decoupling model, but the core decision and the demand curve related to the fundamental safety problem of the machine furnace still follow the curve and the scheduling and decision process in the iv.
The air distribution ejector 20 adopts a stepless adjustment joint adjustment structure.
The exhaust port of the medium pressure cylinder 5 is communicated with the low pressure steam user Y2 in addition to the steam inlet of the low pressure cylinder 6 through an inlet butterfly valve 8.
The decoupling ejector device further comprises a steam supply ejector 30, a steam supply high-pressure driving steam inlet 31 of the steam supply ejector 30 is connected with an external steam supply outlet of the heat re-pipe 13 and a steam supply pipeline of the high-pressure steam user Y1, a steam supply low-pressure steam inlet 32 of the steam supply ejector 30 is connected with a steam discharge outlet of the medium-pressure cylinder 5 and a gas supply pipeline of the low-pressure steam user Y2, and a steam supply medium-pressure steam discharge outlet 33 of the steam supply ejector 30 is communicated with the medium-pressure steam user Y3 through a steam supply desuperheater 34.
The steam supply ejector 20 adopts a stepless adjustment joint adjustment structure.
The detailed derivation process of the safe decoupling model for adjusting only the high-pressure steam extraction is as follows.
Since W4 is a function of G41 under certain operating conditions, taken as w4=f4 (G41), and similarly W5 is a function of G51, w5=f0 (G51) =f0 (G41×r54) =f1 (G41) is obtained by variable substitution, and the sum of the power generation amounts of the high-pressure cylinder and the medium-pressure cylinder w45=w4+w5=f4 (G41) +f1 (G41) =f45 (G41) is taken as the inverse function: g41 =f4 (W45), which is the decision curve of the cylinder intake.
G51 The decision curve of the intake of the medium pressure cylinder is defined as g41×r54=f4 (W45) ×r54.
G2 The required curve of the reheater intake is defined as g51+gy1=f4 (W45) r54+gy1.
According to the topological relation G2 and G3, i.e. G41 and G42, G41 is defined as the difference between G41 and G42, and G24 is subtracted, then g3-g2=g41-g42-g24=g41 (1-R4) -k is defined as G3= (G2-g41 (1-R4))/(1+k) = (f4 (W45) ×r54+gy1-f4 (W45)/(1-R4))/(1+k) = (f4 (W45) ×r54+r4-1) +gy1)/(1+k), which is the decision curve of the new steam amount of the superheater.
Thus, the main decision and demand variables G2, G3, G41, G51 can be expressed as functions of the external independent variable high-pressure external steam supply GY1 and the internal independent variable W45 (for replacing the external independent variable complete machine power generation load W0), and are called high-pressure thermocouple safety decision curves.
Similarly, a high-medium pressure thermocouple safety decision curve can be further deduced when the medium pressure cylinder has external steam supply requirements; and, furthermore, a full-state thermal decoupling safety decision curve for simultaneously recovering the exhaust steam waste heat of the low-pressure cylinder to heat can be further deduced, which is not repeated.
In view of the fact that in an actual boiler system, the allowable variation range of a certain range exists in actual operation in view of the intake amount of the reheater, the parameters thereof, the proportional relation between the intake amount of the reheater and the new steam amount, and the like, the allowable variation range is considered to be safe as long as the allowable variation range does not exceed the allowable variation range, depending on specific technical characteristics of the boiler. Likewise, in practical turbo generator set systems, the axial stress of the turbine is also affected by a number of factors, which are related to the specific technical characteristics of the turbine, and the method for balancing the axial thrust of the turbine includes that the high-pressure cylinder and the medium-pressure cylinder are reversely arranged to balance the thrust with each other; the double-side outflow of the low-pressure cylinder realizes self-balancing stress; the impeller is provided with a balance hole axial thrust; the two ends of the high-pressure shaft seal are subjected to reverse pressure difference; setting a balance piston; and finally, the thrust bearing (thrust bush) bears the residual thrust difference and is used for balancing the axial thrust of the rotor, so as to establish the expansion dead point of the rotor and ensure that the axial gap between the moving and static parts is within the design range. In principle, it is therefore considered safe if the ratio of the intake flows of the high and medium pressure cylinders does not exceed the safe operating range of the above-described axial thrust balancing measures. Therefore, the safety decision curve of the thermocouple and the adjustment value thereof during operation scheduling are safe as long as the safety decision curve does not exceed the allowable variation range, and the functional relationship between the parameters, such as w4=f4 (G41), the specific allowable variation range of the parameters, the specific limiting conditions and requirements thereof and the like, are also provided by corresponding host equipment manufacturers, and a more specific thermocouple scheduling and execution work plan are formulated by a cogeneration operation manager according to specific conditions and specific requirements of the thermocouple.
The invention has the technical effects and advantages that: by adopting the injection type technical principle, the gas distribution injector is utilized to proportionally adjust the gas inlet quantity of the high-pressure cylinder and the medium-pressure cylinder so as to ensure the axial thrust balance of the steam turbine, and the through-flow capacity of the reheater and the cooling heat exchange quantity of the reheater are improved so as to ensure the heat exchange balance, thereby realizing the safe operation of the machine furnace efficiently and stably; the thermoelectric safety decoupling model is creatively established, a decision and a demand curve of safety decoupling are given, and a working method of safety decoupling is guided according to the decision and the demand curve; the thermoelectric ratio is greatly adjusted, and the thermoelectric decoupling is fundamentally realized; the automatic steam pipeline, cold re-punching and hot re-punching and steam extraction are not needed, so that the serious safety problem of the steam turbine is avoided; the system is simple and reliable, the occupied space is small, and the reconstruction workload is small; the system cost is reduced by 30-70% compared with the conventional decoupling mode; no extra energy consumption and raw material consumption, small operation and maintenance requirements and low operation cost.
Drawings
Fig. 1 and 2 are schematic diagrams of the system of the present invention.
The component numbers and names in fig. 1 and 2 are as follows.
Boiler 1, reheater 2, superheater 3, high pressure cylinder 4, intermediate pressure cylinder 5, low pressure cylinder 6, generator 7, inlet butterfly valve 8, main steam pipe 9, high bypass pipe 10, high bypass regulating valve 11, cold return pipe 12, hot return pipe 13, intermediate pressure cylinder inlet valve 14, high pressure cylinder inlet valve 15, distribution ejector 20, high pressure drive steam inlet 21, low pressure steam inlet 22, intermediate pressure steam outlet 23, distribution desuperheater 24, distribution check valve 25, cold return check valve 26, high pressure desuperheater 27, steam supply ejector 30, steam supply high pressure drive steam inlet 31, steam supply low pressure steam inlet 32, steam supply intermediate pressure steam outlet 33, steam supply desuperheater 34, steam supply regulating valve 35, boiler feed water G, high pressure steam user Y1, low pressure steam user Y2, medium pressure steam user Y3.
Detailed Description
Fig. 1, 2 are schematic diagrams and embodiments of the system of the present invention.
Specific example 1 of the present invention is as follows.
The system comprises boiler superheated steam, a reheater, a high-pressure cylinder of a steam turbine, a medium-pressure cylinder, a low-pressure cylinder, a generator, a decoupling injection device and a connecting pipeline, wherein the decoupling injection device comprises a gas distribution injector 20, a high-pressure driving steam inlet 21 of the gas distribution injector 20 is connected with a main steam pipe 9 between an outlet of a superheater 3 of a boiler 1 and an inlet of a high-pressure cylinder 4, a low-pressure steam inlet 22 of the gas distribution injector 20 is connected with a steam outlet of the high-pressure cylinder 4 through a cold re-pipe 12, a medium-pressure steam outlet 23 of the gas distribution injector 20 is connected with an inlet of the reheater 2 of the boiler 1 through a gas distribution attemperator 24 and a gas distribution check valve 25, and a steam outlet of the reheater 2 is connected with a steam inlet of the medium-pressure cylinder 5 through a hot re-pipe 13 and is also communicated with a high-pressure steam user Y1 through a high-pressure attemperator 27.
The cold return pipe 12 is provided with a cold return check valve 26, the inlet and outlet of which are respectively connected with the low pressure steam inlet 22 and the medium pressure steam outlet 23 of the distribution ejector 20.
The cold return pipe 12 is not provided with an external supply steam extraction port.
The main steam pipe 9 is not provided with an external steam supply and extraction port.
The injection gas distribution thermal decoupling mode based on axial thrust balance and reheat balance and the operation control method of the system thereof are as follows.
I. when the external steam supply demand of the hot re-pipe 13 is 0, the actuator of the high-pressure driving steam inlet 21 is closed, and the steam flow of the cold re-check valve 26 is larger than zero.
When the demand of the external steam supply of the hot re-pipe 13 is greater than 0, the actuating mechanism of the high-pressure driving steam inlet 21 is opened, the opening of the actuating mechanism increases with the external steam supply, the steam of the cold re-pipe 12 enters the low-pressure steam inlet 22, and if the power generation load demand is kept unchanged, the steam inlet of the high-pressure cylinder 4 and the steam inlet of the medium-pressure cylinder 5 are kept unchanged, and at the moment, the steam flow of the cold re-check valve 26 is zero.
When the power generation load demand changes, the steam inlet of the high pressure cylinder 4 and the steam inlet of the medium pressure cylinder 5 are simultaneously adjusted, and the two steam inlet are maintained to be adjusted in an approximately equal proportion so as to ensure the axial thrust balance of the turbine, and if the external steam supply demand of the heat re-pipe 13 is kept unchanged, the new steam quantity of the superheater 3 is also kept unchanged, and if the external steam supply demand is changed, the new steam quantity of the superheater 3 is also changed, wherein the quantity is determined according to the following relation: external steam demand = new steam quantity + reduced temperature water quantity.
And iv, when only the high-pressure steam extraction quantity is regulated, the safe decoupling model and the decision method are as follows:
Decision curve of high pressure cylinder steam inlet: g41 =f4 (W45), where function F4 depends on turbine characteristics;
And (II) a decision curve of the steam inlet quantity of the medium pressure cylinder: g51 =f4 (W45) R54;
(III) a demand curve of reheater steam admission: g2 =f4 (W45) r54+gy1;
decision curve of superheater fresh steam quantity: g3 = (F4 (W45) × (r54+r4-1) +gy1)/(1+k);
And (V) the scheduling and decision process of the thermoelectric decoupling operation is as follows:
i) If the power generation load W0 and the substitution variable W45 are unchanged and the heat re-supply steam extraction GY1 is changed, adjusting G3 only according to a decision curve of the new steam quantity of the superheater and adjusting G2 according to a demand curve of the steam inlet quantity of the reheater;
ii) if the heat re-external steam supply GY1 is unchanged and the power generation load W0 is changed, under the condition that the power generation load W6 of the low pressure cylinder is changed by itself, the load demand of W45 is changed correspondingly, G3 is adjusted according to the decision curve of the new steam quantity of the superheater, G41 is adjusted according to the decision curve of the steam inlet quantity of the high pressure cylinder, the steam inlet quantity G51 of the medium pressure cylinder is adjusted correspondingly and approximately in the same proportion, and then the steam inlet quantity G2 of the reheater is adjusted;
iii) If two external variables W0 and GY1 change at the same time, the adjustment is still performed with reference to the step in decision method (B) described above;
And v. when not only the high-pressure steam extraction quantity is regulated, but also the steam extraction quantity of the medium-pressure cylinder is regulated, the external variable of the medium-pressure external steam supply GY2 and a model equation thereof are added on the basis of the safe decoupling model, but the core decision and the demand curve related to the fundamental safety problem of the machine furnace still follow the curve and the scheduling and decision process.
The air distribution ejector 20 adopts a stepless adjustment joint adjustment structure.
The exhaust port of the medium pressure cylinder 5 is communicated with the low pressure steam user Y2 in addition to the steam inlet of the low pressure cylinder 6 through an inlet butterfly valve 8.
The embodiment 1 is suitable for the places with steam users and only one or two high and low pressure steam specifications; if there are more pressure rated steam users, the design modification can be made as described in example 2 below.
Specific example 2 of the present invention is as follows.
The decoupling ejector device of the embodiment further comprises a steam supply ejector 30 on the basis of embodiment 1, wherein a steam supply high-pressure driving steam inlet 31 of the steam supply ejector 30 is connected with an external steam supply outlet of the heat re-pipe 13 and a steam supply pipeline of the high-pressure steam user Y1, a steam supply low-pressure steam inlet 32 of the steam supply ejector 30 is connected with a steam discharge outlet of the medium-pressure cylinder 5 and a gas supply pipeline of the low-pressure steam user Y2, and a steam supply medium-pressure steam discharge outlet 33 of the steam supply ejector 30 is communicated with the medium-pressure steam user Y3 through a steam supply desuperheater 34. The steam supply ejector 20 adopts a stepless adjustment joint adjustment structure.
It should be noted that, the present invention provides innovative and precise technical principles, technical methods and system for implementing thermoelectric deep decoupling and flexible transformation, and provides theoretical basis for precise adjustment, and specific implementation method how to implement the above-mentioned objects, and according to this general solution, there may be different specific implementation measures and specific implementation devices with different structures, where the above-mentioned specific implementation is only one or several, and any other similar simple variant implementation, for example, different injector structures are adopted; adding or subtracting a plurality of pipeline connection schemes; or in a manner that would occur to one of ordinary skill in the art, etc., are within the scope of the present invention.
Claims (5)
1. The injection distribution thermal decoupling method based on axial thrust balance and reheat balance comprises a boiler superheater, a reheater, a turbine high-pressure cylinder, a middle-pressure cylinder, a low-pressure cylinder, a generator, a decoupling injection device and a connecting pipeline, and is characterized in that: the decoupling injection device comprises a gas distribution injector (20), a high-pressure driving steam inlet (21) of the gas distribution injector (20) is connected with a main steam pipe (9) between an outlet of a superheater (3) of the boiler (1) and an inlet of a high-pressure cylinder (4), a low-pressure steam inlet (22) of the gas distribution injector (20) is connected with a steam outlet of the high-pressure cylinder (4) through a cold re-pipe (12), a medium-pressure steam outlet (23) of the gas distribution injector (20) is connected with an inlet of a reheater (2) of the boiler (1) through a gas distribution attemperator (24) and a gas distribution check valve (25), and a steam outlet of the reheater (2) is connected with a steam inlet of the medium-pressure cylinder (5) through a high-pressure attemperator (27) and is also communicated with a high-pressure steam user (Y1); the cold recycling pipe (12) is provided with a cold recycling check valve (26), and the inlet and the outlet of the cold recycling check valve are respectively connected with a low-pressure steam inlet (22) and a medium-pressure steam outlet (23) of the air distribution ejector (20); the working method and the scheduling control method are as follows:
i. When the external steam supply demand of the hot re-pipe (13) is 0, the actuating mechanism of the high-pressure driving steam inlet (21) is closed, and the steam flow of the cold re-check valve (26) is larger than zero;
When the external steam supply demand of the hot re-pipe (13) is greater than 0, an actuating mechanism of a high-pressure driving steam inlet (21) is opened, the opening of the actuating mechanism is increased along with the external steam supply, steam of the cold re-pipe (12) enters a low-pressure steam inlet (22), and if the power generation load demand is kept unchanged, the steam inlet of the high-pressure cylinder (4) and the steam inlet of the medium-pressure cylinder (5) are kept unchanged, and the steam flow of the cold re-check valve (26) is zero at the moment;
When the power generation load demand changes, the steam inlet of the high pressure cylinder (4) and the steam inlet of the medium pressure cylinder (5) are simultaneously adjusted, and the two steam inlet are maintained to be adjusted in an approximately equal proportion so as to ensure the axial thrust balance of the turbine, and if the external steam supply demand of the heat re-pipe (13) is maintained unchanged, the new steam quantity of the superheater (3) is also maintained unchanged, and if the external steam supply demand is changed, the new steam quantity of the superheater (3) is also changed, wherein the quantity is determined according to the following relation: external steam demand = new steam quantity + reduced temperature water quantity;
and iv, when only the high-pressure steam extraction quantity is regulated, the safe decoupling model and the decision method are as follows:
the safe decoupling base model is as follows: the variable symbols are defined as follows: g2 boiler superheater new steam quantity; g3 reheater steam inlet; g41 high-pressure cylinder steam inlet quantity; g42 high pressure cylinder exhaust; g10 high side total steam volume; g11 high bypass flow; the G21 gas distribution ejector drives the steam quantity; g22 gas distribution ejector low pressure gas inlet quantity; medium-pressure exhaust gas quantity of G23 gas distribution ejector; g24 air distribution ejector is matched with the temperature-reducing water quantity; g51 medium pressure cylinder steam inlet amount; g61, steam inlet amount of a medium-pressure cylinder; GY1 heat is supplied to the outside for steam extraction; GY2 medium-pressure external steam extraction quantity; w0 is the power generation load of the turbine unit, MW; w4, W5 and W6 are respectively the power generation loads of the high, medium and low pressure cylinders, MW; only the high-pressure steam supply GY1 is considered temporarily, and the external steam supply and extraction quantity of the medium-pressure cylinder and the low-pressure cylinder is not considered; GY1 and W0 are two external independent variables, wherein W0=W4+W5+W6, the generated energy W6 of the low pressure cylinder is taken as an input variable of the model, and the sum W45=W4+W5=W0-W6 of the generated energy of the high pressure cylinder and the generated energy of the medium pressure cylinder can be taken as the independent variable instead of W0 during analysis of the model; the high-pressure cylinder is provided with the ratio of the exhaust steam quantity to the inlet steam quantity under the safe operation condition as R4=G42/G41 because of the in-plant process air extraction such as high-addition steam and the like; based on the axial thrust balance of the steam turbine, setting the flow ratio of the medium pressure cylinder to the high pressure cylinder to be unchanged, namely, R54=G51/G41 is unchanged, and then G51=G41×R54; the matched water reducing amount G24 of the air distribution ejector can be considered to be changed in proportion to the medium-pressure exhaust amount G23 of the air distribution ejector, further is changed in proportion to the steam inlet amount G3 of the reheater, and is set as G24=k×G3, wherein k is a coefficient;
And (II) a decision curve of the steam inlet quantity of the high-pressure cylinder: g41 =f4 (W45), where function F4 depends on turbine characteristics;
And (III) a decision curve of the steam inlet quantity of the medium pressure cylinder: g51 =f4 (W45) R54;
(IV) a demand curve of the steam inlet quantity of the reheater: g2 =f4 (W45) r54+gy1;
(V) decision curve of superheater fresh steam quantity: g3 = (F4 (W45) × (r54+r4-1) +gy1)/(1+k);
the scheduling and decision process of the thermocouple operation is as follows:
i) If the power generation load W0 and the substitution variable W45 are unchanged and the heat re-supply steam extraction GY1 is changed, adjusting G3 only according to a decision curve of the new steam quantity of the superheater and adjusting G2 according to a demand curve of the steam inlet quantity of the reheater;
ii) if the heat re-external steam supply GY1 is unchanged and the power generation load W0 is changed, under the condition that the power generation load W6 of the low pressure cylinder is changed by itself, the load demand of W45 is changed correspondingly, G3 is adjusted according to the decision curve of the new steam quantity of the superheater, G41 is adjusted according to the decision curve of the steam inlet quantity of the high pressure cylinder, the steam inlet quantity G51 of the medium pressure cylinder is adjusted correspondingly and approximately in the same proportion, and then the steam inlet quantity G2 of the reheater is adjusted;
iii) If two external variables W0 and GY1 change at the same time, the adjustment is still performed with reference to the step in decision method (B) described above;
And v. when not only the high-pressure steam extraction quantity is regulated, but also the steam extraction quantity of the medium-pressure cylinder is regulated, the external variable of the medium-pressure external steam supply GY2 and a model equation thereof are added on the basis of the safe decoupling model, but the core decision and the demand curve related to the fundamental safety problem of the machine furnace still follow the curve and the scheduling and decision process in the iv.
2. The injection distribution thermal decoupling method based on axial thrust balance and reheat balance as claimed in claim 1, wherein the distribution injector (20) adopts a stepless adjustment joint adjustment structure.
3. The injection distribution thermal decoupling method based on axial thrust balance and reheat balance as claimed in claim 1, wherein the exhaust port of the medium pressure cylinder (5) is connected with the steam inlet of the low pressure cylinder (6) through an inlet butterfly valve (8) and is also communicated with a low pressure steam user (Y2).
4. The injection distribution thermal decoupling method based on axial thrust balance and reheat balance as claimed in claim 3, wherein the decoupling injection device further comprises a steam supply injector (30), a steam supply high-pressure driving steam inlet (31) of the steam supply injector (30) is connected with an external steam supply outlet of the thermal reheat pipe (13) and a steam supply pipeline of the high-pressure steam user (Y1), a steam supply low-pressure steam inlet (32) of the steam supply injector (30) is connected with a steam outlet of the medium-pressure cylinder (5) and a gas supply pipeline of the low-pressure steam user (Y2), and a steam supply medium-pressure steam outlet (33) of the steam supply injector (30) is connected with the medium-pressure steam user (Y3) through a steam supply attemperator (34).
5. The injection distribution thermal decoupling method based on axial thrust balance and reheat balance as claimed in claim 4, wherein said steam supply injector (30) adopts a stepless regulation joint regulation structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911073326.6A CN110656991B (en) | 2019-11-05 | 2019-11-05 | Injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911073326.6A CN110656991B (en) | 2019-11-05 | 2019-11-05 | Injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110656991A CN110656991A (en) | 2020-01-07 |
| CN110656991B true CN110656991B (en) | 2024-06-18 |
Family
ID=69042971
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911073326.6A Active CN110656991B (en) | 2019-11-05 | 2019-11-05 | Injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110656991B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111396155B (en) * | 2020-03-24 | 2024-04-19 | 清华大学 | Injection self-balancing type high-pressure steam supply full-load thermal decoupling method with medium-pressure valve being regulated |
| CN112050190A (en) * | 2020-09-09 | 2020-12-08 | 太原理工大学 | Thermoelectric peak regulation method for coal-fired unit |
| CN113914950B (en) * | 2021-10-13 | 2023-04-28 | 西安热工研究院有限公司 | Ultra-supercritical double-reheat multi-extraction steam turbine set and thermal decoupling control method |
| CN115853608A (en) * | 2022-12-12 | 2023-03-28 | 东方电气集团东方汽轮机有限公司 | Steam turbine middle-connection door parameter adjusting heat supply system and method for improving steam flow of steam turbine middle-connection door parameter adjusting heat supply system |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN210858830U (en) * | 2019-11-05 | 2020-06-26 | 清华大学 | Injection gas distribution depth thermoelectric decoupling system based on axial thrust balance |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201244454Y (en) * | 2008-08-20 | 2009-05-27 | 青岛高远热能动力设备有限公司 | Multichannel water vapour injector |
| JP5727951B2 (en) * | 2011-04-20 | 2015-06-03 | 新日鐵住金株式会社 | Steam supply system and method for controlling steam supply system |
| CN102996191B (en) * | 2012-12-26 | 2015-05-27 | 北京国电蓝天节能科技开发有限公司 | Double-extraction adjustable heating system of thermal power generating unit |
| CN107956517B (en) * | 2017-10-24 | 2023-07-25 | 联合瑞升（北京）科技有限公司 | Thermodynamic system and method for deep thermal decoupling |
| CN207583442U (en) * | 2017-10-24 | 2018-07-06 | 联合瑞升（北京）科技有限公司 | A kind of therrmodynamic system for the decoupling of depth thermoelectricity |
| CN109578094A (en) * | 2018-10-07 | 2019-04-05 | 联合瑞升（北京）科技有限公司 | A kind of increasing steam turbine system for the decoupling of heat supply steam supply depth thermoelectricity |
-
2019
- 2019-11-05 CN CN201911073326.6A patent/CN110656991B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN210858830U (en) * | 2019-11-05 | 2020-06-26 | 清华大学 | Injection gas distribution depth thermoelectric decoupling system based on axial thrust balance |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110656991A (en) | 2020-01-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110701663B (en) | Injection type heat pump exhaust steam recovery heat supply mode and system based on complete thermal electrolytic coupling | |
| CN110656991B (en) | Injection distribution thermal electrolytic coupling mode based on axial thrust balance and reheat balance | |
| CN105673101B (en) | A kind of steam turbine and therrmodynamic system with depth peak regulating function | |
| CN110792482A (en) | Control system and method for ultra-supercritical secondary reheating unit to participate in primary frequency modulation of power grid | |
| CN105201564A (en) | Main-steam-flow-based steam turbine sliding pressure optimization control method | |
| CN109638861B (en) | Control method and control system model for supercritical unit to participate in primary frequency modulation | |
| CN210858830U (en) | Injection gas distribution depth thermoelectric decoupling system based on axial thrust balance | |
| CN111255530A (en) | Thermal power generating unit load adjusting system and method assisted by butterfly valve with low-pressure cylinder | |
| CN210801355U (en) | Thermoelectric decoupling system based on multistage injection type gas distribution and heat pump exhaust steam recovery | |
| CN112523822A (en) | Wide-load medium-pressure heating mode based on parameter adjustment of medium-adjustment door | |
| CN113107623A (en) | Device and method for improving heat supply steam extraction parameters during low-load operation of double-low-pressure-cylinder steam turbine | |
| CN210509309U (en) | Steam complementary energy utilization coupling steam extraction heat supply system for thermoelectric unit electric power peak regulation | |
| CN111206970B (en) | Peak regulating system utilizing steam jet and steam extractor in thermal power plant and control method | |
| CN212296519U (en) | Variable-parameter multi-element cascade thermoelectric decoupling system of thermal power heat supply unit | |
| CN110735677A (en) | natural gas compressor station gas turbine-steam turbine combined cycle control system | |
| CN114439559B (en) | Heat supply method for switching condensing type and high back pressure of steam turbine generator set | |
| CN214660397U (en) | Device for improving heat supply steam extraction parameters during low-load operation of double-low-pressure-cylinder steam turbine | |
| CN113374539B (en) | Steam inlet control system of double-cylinder double-pressure waste heat generating set and steam supplementing control method thereof | |
| CN112031883B (en) | Two-stage adjusting system suitable for middle adjusting valve participating in adjusting and lifting industrial steam supply parameters | |
| CN212027896U (en) | High-pressure injection type thermoelectric decoupling heat supply system | |
| CN114233403A (en) | High-efficient turbo electric power generation system of degree of depth peak regulation that split-axis was arranged | |
| CN110056402B (en) | Steam complementary energy utilization coupling steam extraction heat supply system and adjusting method | |
| CN111828115A (en) | High-low pressure cutting cylinder thermoelectric decoupling mode and system based on exhaust steam built-in group spraying injection | |
| CN214464455U (en) | Depth peak regulation system based on thermodynamic system coupling among units | |
| CN111396155B (en) | Injection self-balancing type high-pressure steam supply full-load thermal decoupling method with medium-pressure valve being regulated |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |