CN111379604A - Multistage heat supply back pressure type steam turbine, thermodynamic system and heat supply method thereof - Google Patents
Multistage heat supply back pressure type steam turbine, thermodynamic system and heat supply method thereof Download PDFInfo
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- 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
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
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- 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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/10—Heating, e.g. warming-up before starting
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
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- 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
- F01K13/02—Controlling, e.g. stopping or starting
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- 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
- F01K7/34—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 of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/38—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 of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D3/00—Hot-water central heating systems
- F24D3/10—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system
- F24D3/1058—Feed-line arrangements, e.g. providing for heat-accumulator tanks, expansion tanks ; Hydraulic components of a central heating system disposition of pipes and pipe connections
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Abstract
The invention discloses a multistage heat supply back pressure turbine, a thermodynamic system and a heat supply method thereof, belonging to the field of cogeneration equipment, and comprising a back pressure turbine body, a steam inlet end and a steam outlet end, wherein at least one steam extraction regulating device is arranged in a through flow between the steam inlet end and the steam outlet end; heat supply steam extraction ports at all levels are respectively arranged between the steam extraction regulating device and the steam inlet end and between two adjacent steam extraction regulating devices, and the steam exhaust end is used as a final-stage heat supply steam extraction port; the steam flow and pressure of the corresponding heat supply steam extraction port are adjusted through each steam extraction adjusting device, so that multi-stage heat supply steam with different parameters is provided at the same time; all levels of heat supply steam are respectively extracted according to requirements after expanding and acting in the backpressure machine, more reasonable parameter matching can be realized, and the energy gradient utilization is more sufficient; after the multistage heat supply back pressure turbine and the variable heat regeneration system matched with the multistage heat supply back pressure turbine are adopted, the multistage heat supply back pressure turbine can still continuously run when the final stage heat supply load at the steam exhaust end does not exist.
Description
Technical Field
The invention belongs to the field of cogeneration equipment, and particularly relates to a multistage heat supply back pressure steam turbine, a thermodynamic system and a heat supply method thereof, which are suitable for industrial heat supply and heating heat supply comprehensive energy-saving projects in a park, more typically projects with high-parameter industrial heat load and heating heat load at the same time, and one back press of the type can realize the operation with industrial and heating heat load in a heating season; the non-heating season only carries industrial heat load to continuously operate, the problem that the traditional back pressure machine needs to be stopped because the heat load at the steam exhaust end can not be absorbed after being cut off is solved, the application of the back pressure machine is expanded, the equipment utilization rate is greatly improved, and the engineering investment is saved.
Background
The cogeneration turbine can effectively realize the cascade utilization of energy, and is one of the most effective technologies for energy conservation and emission reduction. The back pressure turbine has no energy loss and better economical efficiency, is beneficial to realizing environmental protection targets such as carbon dioxide emission reduction and the like, and is vigorously advocated and developed in China at present. Seventeenth article of the ' cogeneration management method ' (energy agency ' 2016,617) issued by the national energy agency clearly shows that, for cities with less than 50 ten thousand of residents in urban areas, a heating type cogeneration project adopts a backpressure cogeneration unit with a single machine of 5 ten thousand kilowatts and less in principle; eighteenth note that, for cities with 50 ten thousand or more of the urban population, the back pressure cogeneration units of 5 ten thousand kilowatts or more are preferentially adopted in the heating type cogeneration project. The energy development ' thirteen-five ' planning ' proposes ' implementation of multi-energy complementary integration optimization engineering ', promotes comprehensive cascade utilization and transformation of energy in energy utilization areas such as the existing industrial park, popularizes and applies an energy supply mode of ' coupling integration and complementary utilization of energy production of heat, electricity, cold, gas and the like ', and enhances recovery and comprehensive utilization of energy resources such as waste heat and excess pressure, industrial byproducts, household garbage and the like.
When the final-stage heat supply requirement of a steam exhaust end is discontinuous, a back pressure machine cannot continuously operate in the conventional back pressure steam turbine with two or more stages of different heat supply parameters; to address such problems, several different types of back pressure turbines are conventionally configured to meet the requirements of various operating conditions.
The existing back pressure steam turbine mainly comprises two main types of industrial heat supply and heating heat supply, the steam exhaust pressure needs to be determined according to different heat supply parameters in unit model selection design, and the design and application of the back pressure machine are limited by engineering conditions. The extraction condensing type cogeneration unit has low thermoelectric ratio and limited thermoelectric decoupling capacity, so that the operation flexibility is limited. The further development of cogeneration turbines is mainly limited by the following aspects:
(1) the exhaust steam of the heating back pressure turbine is communicated to a heating heat supply network, and the steam turbine can only operate in heating seasons, so that the equipment utilization rate is low due to non-heating season shutdown. The heating time of the places such as northeast three provinces and Xinjiang with longer heating period in China is about 5-6 months, the heating seasons in other areas are about 3-4 months, the project investment recovery period is longer due to low equipment utilization rate, and the further popularization of the heating back pressure turbine is influenced to a certain extent. Industrial heating back pressure turbines have found many applications in areas where heat consumers are mature. However, when planning and raising many industrial parks, most steam-consuming enterprises are willing to invest in construction only when the cogeneration units are required to have heat supply capacity. The back pressure turbine can only operate when the heat supply network meets a certain load requirement; if the hot user is not in fact, there is a great risk that the equipment is idle after being built. The steam enterprises and the investment suppliers of the cogeneration project want to minimize the risk, and the difficulty in supply and demand connection causes the slow development of the back pressure turbine. Most of the existing back pressure type steam turbine units are self-provided forms of enterprises, the investment enthusiasm of professional power enterprises is still not fully mobilized, and the integrated energy supply engineering of newly built terminals in newly added functional areas such as industrial parks is not facilitated.
(2) Although the operation of the extraction condensing type cogeneration unit is not limited by seasons, the heat and power ratio is low, the heat supply amount is limited by the unit load (the heat and power decoupling range is small), and the power generation share of renewable energy sources such as wind energy and the like is occupied when the unit operates at a higher load in a heating season, which is not consistent with the energy development direction of the country. Taking the 'heating area in the northwest of China' as an example, the proportion of the traditional large-scale extraction condensing unit is too large, so that the large-scale 'wind abandoning' condition occurs in the heating season. The problem of thermoelectric decoupling is solved to a certain extent by the flexibility modification (low-pressure cylinder zero-power modification) of the existing pumping and condensing unit, but the low-pressure last-stage movable blade has larger running risks such as water erosion and the like, and the safety and reliability of the low-pressure last-stage movable blade also need to pass long-term running inspection; and a certain amount of cooling steam is still discharged to the condenser, so that cold end loss exists. The extraction condenser is changed into high back pressure heat supply of the low-pressure double rotors, and the generated energy loss exists during the rotor replacement.
(3) The conventional heating back pressure turbine does not have the operation capacity in non-heating seasons (the extraction condensing unit or the condensing unit is not suitable for high back pressure heating). If a high industrial heat supply parameter is designed as an exhaust parameter of the back pressure turbine, heat supply steam (or heating steam) with a low parameter needs to be obtained outside the back pressure turbine through temperature reduction and pressure reduction, or has a large heat exchange temperature difference with a heating heat network, so that great efficiency loss is caused, and the primary purpose of energy gradient utilization is not met. The engineering usually adopts a plurality of back pressure turbines with different steam discharge parameters to be matched and used, and the investment of equipment, factory buildings and the like is higher.
(4) At present, an automatic synchronous clutch is arranged between a medium-pressure module and a low-pressure module of a partial combined cycle cogeneration turbine, and the automatic synchronous clutch is generally called as a condensing-extracting-back turbine. The condensing-extracting-back steam turbine is automatically and synchronously engaged with a clutch in a non-heating season, and a low-pressure module is put into operation and operates in a pure condensing mode; the automatic synchronous clutch is disengaged under the maximum heat supply working condition in the heating season, and the automatic synchronous clutch operates in a backpressure mode. Although the running mode of the unit is flexible, the length of the unit is increased due to the additional arrangement of the automatic synchronous clutch, and the equipment cost is higher; and there is a cold end loss for most of the run.
Disclosure of Invention
In view of the above, in order to solve the above problems in the prior art, the present invention provides a multi-stage heat supply back pressure turbine, a thermodynamic system and a heat supply method thereof, so as to provide multi-stage heat supply with different parameters at the same time, and when there is no back pressure machine to exhaust steam and supply heat, the unit can still operate continuously; and each level of heat supply steam is respectively extracted according to requirements after expanding and acting in the back pressure machine, so that more efficient and more reasonable parameter matching can be realized.
The technical scheme adopted by the invention is as follows: a multi-stage heat supply back pressure steam turbine comprises a back pressure steam turbine body, and a steam inlet end and a steam outlet end which are arranged on the back pressure steam turbine body, wherein at least one steam extraction regulating device is arranged in a through-flow stage between the steam inlet end and the steam outlet end; the heat supply steam extraction of each stage of heat supply steam extraction port is sequentially extracted after expanding and acting in the back pressure type steam turbine body, and the external pressure reduction mode is not adopted to meet the engineering requirement.
Furthermore, each stage of heat supply steam extraction port is set as an industrial heat supply steam extraction port, and the last stage heat supply steam extraction port is set as a heating heat supply steam extraction port, so that the problem that the heating back pressing machine cannot operate in non-heating seasons can be solved, the heating back pressing machine can be used as the heating back pressing machine temporarily when no load is required by industrial heat users, equipment is prevented from being idle, engineering risks are reduced, and the requirements of energy production coupling integration and complementary utilization proposed by ' thirteen-five ' planning of energy development ' are met. The final stage heat supply steam extraction port can also be set as a low-parameter industrial steam extraction port, and when steam supply is discontinuous, continuous operation of the unit is not influenced.
The invention also provides a multistage heat supply back pressure turbine thermodynamic system, which comprises a variable heat regenerative system and the multistage heat supply back pressure turbine, wherein the cooling flow required by the flow of the last stages of the multistage heat supply back pressure turbine is absorbed by the variable heat regenerative system; the variable heat regenerative system comprises at least one stage of heater, and each stage of heater is connected with a multi-stage heat supply back pressure turbine through a heat return pipeline. After any stage of heat supply in the thermodynamic system is cut off, particularly after the last stage of heat supply load (such as the heating load of a steam exhaust end direct supply heat network of the back pressure turbine) is cut off, the cooling flow required by the flow of the last stages can be completely absorbed by the variable heat recovery system, and the thrust of the set and the load distribution of the heat recovery heaters of each stage are adjusted through the variable heat recovery system, so that the back pressure turbine can continuously and safely operate. Taking a back press with high-parameter industrial heat load and heating load as an example, an industrial steam extraction port in front of the steam extraction regulating device provides high-parameter industrial steam extraction, and a final-stage heat supply steam extraction port at a steam exhaust end provides heating steam. The back press takes the rated industrial heat load and heating load in the heating season as the design working condition; and after the heating load is cut off in non-heating seasons, the unit operates under sliding pressure, the steam extraction regulating device participates in the regulation of the industrial steam extraction flow and pressure, the variable regenerative system regulates the thrust of the unit and the load distribution of regenerative heaters at all stages, and the cooling flow required by the last stages is consumed. The problem that the back pressure machine with the heating function cannot operate in non-heating seasons can be solved, the back pressure machine can be used as the back pressure machine for heating temporarily during the period of no-load demand of industrial heat users, equipment is prevented from being idle, engineering risks are reduced, and the requirements of energy production coupling integration and complementary utilization proposed by ' thirteen-five ' planning of energy development ' can be met.
Furthermore, the heater is set as one stage, the heater is connected with the steam exhaust end of the multistage heat supply back pressure turbine through a heat return pipeline, a regulating valve is arranged on the heat return pipeline, the regulating valve is used for controlling the pressure at the steam exhaust end not to be reduced too much, and the heat return steam extraction quantity of two adjacent stages and the temperature rise of the heater are changed through the change of the throttling degree of the regulating valve. The load of the final heater is reduced, the pressure of the steam exhaust end is increased, the adjacent regenerative steam extraction amount is increased, the flow pressure at the corresponding steam extraction point is reduced, and therefore the thrust adjusting effect is achieved.
Further, when the heaters are set to be two-stage or more than two-stage, each stage of heaters are respectively connected to the multistage heat supply back pressure turbine through a back heating pipeline, and the heaters are connected in series through a water supply pipeline, and whether a regulating valve is arranged on each back heating pipeline is determined according to the magnitude of change of back heating steam extraction flow of each stage of the multistage heat supply back pressure turbine under variable working conditions. The same-stage heater can adopt a single-body design, and also can adopt a parallel arrangement of two or more heaters. Controlling the flow of the regenerative steam through regulating valves on the regenerative pipelines; or individual heaters may be cut out of two or more heaters connected in parallel to change the heat exchange area, thereby adjusting the heater load. Through the regulation of the load of the heaters, the temperature rise distribution of the adjacent heaters is adjusted, the main through-flow of the back pressure turbine is regulated, and the through-flow pressure at each regenerative steam extraction point is controlled, so that the axial thrust of the multistage heat supply back pressure turbine is regulated, and the safe and continuous operation of the unit is ensured.
The invention also provides a heat supply method of the multistage heat supply back pressure turbine thermodynamic system, the heat supply method is applied to the multistage heat supply back pressure turbine thermodynamic system, and the heat supply method comprises the following steps:
controlling the steam inlet amount and the total heat supply amount of the unit through a main steam regulating valve of the multistage heat supply back pressure steam turbine;
the steam pressure and the flow of each stage of heat supply steam extraction port are adjusted by changing the opening degree of each steam extraction adjusting device so as to provide steam supply with different multi-stage parameters;
each stage of heat supply steam extraction port is extracted after expansion work is performed in the multi-stage heat supply back pressure steam turbine, high-efficiency parameter matching is achieved, and an external decompression mode is not adopted to meet engineering requirements; the exhaust end of the multi-stage heat supply back pressure turbine is used as a final stage heat supply steam extraction port and provides low-parameter industrial steam extraction or heating steam extraction for the outside.
The invention has the beneficial effects that:
1. by adopting the multistage heat supply back pressure turbine, the thermodynamic system and the heat supply method thereof, the back pressure turbine and the corresponding thermodynamic system are newly designed, the heat supply requirements of multistage different parameters can be met simultaneously, and the back pressure turbine can still continuously operate when no final stage heat supply load of a steam exhaust end exists; and can set up the steam extraction regulating device on the corresponding through-flow stage, so as to make the single back pressure turbine can meet the requirement of the multistage heat supply, does not need to set up the external pressure relief device, can realize the high-efficient cascade utilization of energy; the whole scheme has the characteristics of high operation efficiency, high equipment utilization rate and the like, can effectively solve the problems of short operation time and low investment return rate of the heating back pressure turbine particularly for areas with industrial heat supply and heating heat supply at the same time, and is favorable for propelling clean heating work.
2. The multistage heat supply back pressure turbine, the thermodynamic system and the heat supply method thereof disclosed by the invention meet the national energy development requirements, widen the popularization and application range of the back pressure turbine, meet the guidance thought of implementing multi-energy complementary integration optimization engineering provided in the energy development 'thirteen-five' plan, and are suitable for implementing terminal integrated energy supply engineering in newly added functional areas such as newly built industrial parks. Compared with the scheme that a plurality of traditional back pressure turbines are matched to meet the heat supply requirements of different parameters, the investment of equipment, plants and other projects is greatly reduced, and the investment risk is correspondingly reduced.
Drawings
Fig. 1 is a schematic system structure diagram of a multistage heat supply back pressure turbine thermodynamic system provided by the invention in an embodiment 1;
FIG. 2 is a schematic diagram of the system structure of the multi-stage heating back pressure turbine thermodynamic system provided by the invention in the embodiment 2;
the reference numerals are explained below:
1-back pressure turbine, 2-steam extraction regulating device, 3-regulating valve I, 4-regulating valve II, 5-low pressure heater I, 6-low pressure heater II, 7-deaerator, 8-primary high pressure heater, 9-secondary high pressure heater, 10-regulating valve III, 11-low pressure heater III.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
In the description of the embodiments of the present invention, it should be noted that the indication of the orientation or the positional relationship is based on the orientation or the positional relationship shown in the drawings, or the orientation or the positional relationship which is usually placed when the product of the present invention is used, or the orientation or the positional relationship which is usually understood by those skilled in the art, or the orientation or the positional relationship which is usually placed when the product of the present invention is used, and is only for the convenience of describing the present invention and simplifying the description, but does not indicate or imply that the indicated device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore, cannot be understood as limiting the present invention. Furthermore, the terms "first" and "second" are used merely to distinguish one description from another, and are not to be construed as indicating or implying relative importance.
In the description of the embodiments of the present invention, it should be further noted that the terms "disposed" and "connected" are to be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected, unless explicitly stated or limited otherwise; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases by those skilled in the art; the drawings in the embodiments are used for clearly and completely describing the technical scheme in the embodiments of the invention, and obviously, the described embodiments are a part of the embodiments of the invention, but not all of the embodiments. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Example 1
At present, when the final stage heat supply is discontinuous, the unit can not continuously operate. In order to solve the problems, a plurality of different back pressure machines are required to be configured, and in the embodiment, a multistage heat supply back pressure turbine and a thermodynamic system thereof are provided, the design scheme does not simply use high-parameter heat supply as the basis of steam exhaust design parameters of the back pressure turbine, and the heat supply requirements of each stage are met by traditional methods such as temperature reduction, pressure reduction and the like outside a unit; but each stage of heat supply steam is respectively extracted according to requirements after expanding and acting in the back pressure machine, more efficient and more reasonable parameter matching can be realized, and the unit can still operate when the final stage heat supply load is discontinuous.
In this embodiment, as shown in fig. 1, a two-stage heat supply back pressure turbine for high-parameter industrial heat supply and heating heat supply and a thermodynamic system thereof are taken as an example, and the two-stage heat supply back pressure turbine includes a multi-stage heat supply back pressure turbine and a variable heat regeneration system, the multi-stage heat supply back pressure turbine includes a back pressure turbine body, and a steam inlet end and a steam outlet end which are arranged on the back pressure turbine body, the steam from a boiler is communicated through the steam inlet end, the steam outlet end is taken as a steam extraction port for low-parameter heating heat supply, the heating heat supply parameter is taken as a design basis for the steam outlet parameter of the back pressure turbine, and a steam extraction adjusting device is arranged in a through-flow between the steam inlet end and the. Preferably, the steam extraction adjustment device may be a rotary diaphragm or a cylinder valve, etc., but is not limited to the above examples. A primary heat supply steam extraction port is arranged between the steam extraction regulating device and the steam inlet end and is used as a high-parameter industrial heat supply steam extraction port, and the steam pressure and the flow of the primary heat supply steam extraction port are regulated through the steam extraction regulating device; the exhaust end of the back pressure turbine is used as the final stage heat supply steam extraction port. In the embodiment, the high-parameter industrial heating and low-parameter heating machine types are taken as examples, so that industrial and heating steam extraction is simultaneously provided for the outside in the heating season; when the device is operated in a non-heating season, the heat supply load of a heating heat supply steam extraction port is cut off, a main steam regulating valve is turned down or the device is operated under sliding pressure, the main steam quantity is reduced, a built-in industrial steam extraction regulating device is in a minimum opening degree, and the steam flow from an industrial steam extraction point to a steam exhaust end only needs to be larger than the minimum cooling flow required by last stages of blades; the partial flow enters the heat recovery system through the steam exhaust end for recycling, and because the required water replenishing amount is large during industrial heat supply, the tail blade of the back pressure turbine is short, the required cooling flow is relatively small, and the steam at the steam exhaust end is completely absorbed by the variable heat recovery system. The unit can ensure safe and continuous operation, no cold source loss and high system heat efficiency.
The through-flow capacity between the steam inlet end of the back pressure turbine and the steam extraction regulating device is designed as follows: the through-flow capacity is the sum of system losses such as industrial heat supply flow of a first-stage heat supply steam extraction port, heating heat supply flow of a last-stage heat supply steam extraction port, steam consumption of a regenerative system, shaft seal steam leakage and the like and design allowance. The design margin is typically taken to be 3% -5% of the rated calculated flow.
The through-flow capacity between the exhaust end of the back pressure turbine and the steam extraction regulating device is designed as follows: the through-flow capacity should be the sum of the final stage heat supply steam extraction port heat supply flow, the heater flow and the design allowance, and the design allowance is usually 3% -5% of the rated calculated flow.
In the multi-stage heat supply back pressure steam turbine, the movable and fixed blade molded lines of each flow stage are designed by selecting the design with good working condition adaptability and insensitive attack angle; the strength of the cylinder, the valve shell and the through-flow components at all levels is designed according to the working conditions of the highest working temperature and the maximum pressure difference; so that the multistage heat supply back pressure type steam turbine can meet the safe operation requirements of rated working conditions and various variable working conditions.
In order to ensure that the multistage heat supply back pressure type steam turbine can safely and efficiently operate under various variable working conditions, the steam extraction amount of a regenerative system, the unit thrust and the like are in allowable ranges, a variable regenerative system is configured. The variable heat regenerative system has the essential and design points that: the temperature rise requirement of each stage of heater is met, and the regenerative secondary steam extraction quantity which has large influence on the axial thrust of the unit and the through-flow pressure of the corresponding steam extraction port are controlled within a reasonable range so as to ensure that the thrust of the rotor is within an allowable range under various working conditions.
As shown in fig. 1, the variable regenerative system is provided with two low-pressure heaters connected in parallel, wherein the two low-pressure heaters are respectively a low-pressure heater i and a low-pressure heater ii, and the low-pressure heater i is designed according to the last-stage heat supply cutting working condition; and the low-pressure heater II is designed according to the increased load under the working condition of simultaneously carrying two-stage steam extraction and heat supply, and the allowance is considered according to the design specification. And the low-pressure heater I and the low-pressure heater II are respectively connected to a last-stage steam extraction port of the multistage heat supply back pressure turbine through heat return pipelines, and each heat return pipeline is respectively provided with a regulating valve I and a regulating valve II. When the unit is removed at the last stage of heat load, namely the load of a heating heat supply steam extraction port is removed, the flow of main steam and the flow of return water are correspondingly reduced, and the return water can still be heated to the required temperature after the low-pressure heater II is removed; the two regulating valves are matched for use, and the loads of the low-pressure heater I and the low-pressure heater II can be regulated to meet the requirements of other variable working conditions. According to the thrust of the unit and the load change condition of each stage of heater during variable working condition operation, the low-pressure heater at the steam exhaust end is not limited to be designed into a parallel connection mode, and an adjusting valve is not limited to be added on a heat return pipeline at the steam exhaust end, and whether the adjusting valve is arranged on the corresponding heat return pipeline or not is determined according to the change of the heat return steam extraction flow during variable working conditions.
The variable regenerative system also comprises a regenerative heater of other grades such as a deaerator. The deaerator through steam conduit with multistage heat supply back pressure turbine is connected, low pressure feed water line and deaerator are connected to the low pressure feed water heater, get into the deaerator after passing through low pressure feed water heater heating with the moisturizing and the return water of back pressure turbine. The deaerator reduces the oxygen content in the water to an allowable content in a heating mode; the other end of the deaerator is connected in series with a first-stage high-pressure heater and a second-stage high-pressure heater through a water supply pipeline, and the first-stage high-pressure heater and the second-stage high-pressure heater are respectively connected with the multistage heat supply back pressure steam turbine through steam pipelines. The first-stage high-pressure heater and the second-stage high-pressure heater are connected in series with the deaerator, the drainage of each stage of high-pressure heater automatically flows to the deaerator step by step, and the low-pressure heater I and the low-pressure heater II which are connected in parallel, the deaerator, the first-stage high-pressure heater and the second-stage high-pressure heater are connected in series to form the multi-stage heater.
The heat supply method of the multistage heat supply back pressure turbine thermodynamic system comprises the following steps:
taking two-stage heat supply requirements of industrial heat supply and heating heat supply as an example, arranging a steam extraction regulating device in the through flow of the back pressure turbine according to the steam extraction parameter requirement; the steam extraction regulating device is a cylinder valve or a rotary clapboard and the like, and if the steam extraction is carried out under 2.0MPa in the industry, the cylinder valve is arranged at the middle pressure section; if the industrial steam extraction is 1.0MPa, a rotary clapboard is arranged at the middle pressure section. A high-parameter industrial heat supply steam extraction port is arranged between the steam extraction adjusting device and the steam inlet end, and the steam exhaust end is used as a low-parameter final-stage heat supply steam extraction port; the steam inlet amount and the total heat supply amount are controlled by the main steam regulating valve, and the steam pressure and the flow demand of the first-stage heat supply steam extraction port are met by regulating the opening degree of the steam extraction regulating device.
When the heat supply method is actually used, in order to improve the economical efficiency of the unit operation in the heating season and the non-heating season, the initial parameter (such as subcritical 16.67MPa/535 ℃ and above) of the steam inlet end can be properly improved. When the steam inlet pressure is increased and the temperature of the industrial extraction steam is unreasonably matched with the required pressure, the unit can consider to select the single reheating or properly adjust the matching of the temperature and the pressure (such as 12.7MPa/565 ℃) so as to meet the requirements of extraction steam temperature and pressure of each stage.
Taking a certain engineering requirement as an example: the non-reheating back pressure steam turbine has the following steam admission parameters in the rated heat supply working condition in the heating season: 12.7MPa/565 ℃, the industrial extraction pressure is 1.0MPa, the flow rate is 250t/h, the heating steam pressure is 0.4MPa, and the flow rate is 350 t/h; the non-heating season sliding pressure operation is carried out, the initial parameter is reduced to 6.0MPa/485 ℃, the rotary clapboard is closed to the minimum opening, the industrial extraction pressure is ensured to be 1.0MPa, the flow is 250t/h, the flow required by the final-stage low-pressure heater is about 60t/h, the minimum safety flow required by the final-stage moving blade is met, the flow can be recycled by the final-stage low-pressure heater, and the back pressure steam turbine can be safely operated in the non-heating season completely.
Taking a steam turbine with reheating back pressure as an example, the steam inlet parameters of rated heat supply working conditions in a heating season are as follows: 16.7MPa/538 ℃/538 ℃, the industrial extraction pressure is 1.0MPa, the flow rate is 250t/h, the heating steam pressure is 0.4MPa, and the flow rate is 250 t/h; the non-heating season sliding pressure operation is carried out, the initial parameter is reduced to 11.0MPa/530 ℃/520 ℃, the rotary partition plate is closed to the minimum opening, the industrial extraction pressure is ensured to be 1.0MPa, the flow is 250t/h, the flow required by the final-stage low-pressure heater is about 70t/h, the cooling flow required by the final leaves is met, and the non-heating season safety operation can be completely carried out.
In practical application, parameters and through-flow capacity are reasonably selected according to specific requirements of an industrial park, and all equipment (parts) in the multistage heat supply back pressure turbine thermodynamic system check strength according to the highest parameters, so that the aims of simultaneously providing multistage parameters with different heat loads and continuously and safely operating the multistage heat supply back pressure turbine after final-stage heat supply is cut off can be completely fulfilled.
Example 2
As shown in fig. 2, the variable regenerative system configured in embodiment 1 can also be designed in the following manner: the variable regenerative system comprises a low-pressure heater III, the low-pressure heater III is connected with a last-stage steam extraction port of the multi-stage heat supply back-pressure steam turbine through a heat return pipeline, a regulating valve III is arranged on the regenerative pipeline to control the pressure at a steam exhaust end not to be excessively reduced, and the regenerative steam extraction quantity of two adjacent stages and the temperature rise of the heater are regulated through the throttle degree change of the regulating valve III. The load of the low-pressure heater III is reduced, the pressure of the steam exhaust end is increased, the adjacent regenerative steam extraction amount is increased, the flow pressure at the corresponding steam extraction point is reduced, and therefore the thrust adjusting effect is achieved. After any stage of heat supply is cut off, especially the last stage of heat supply load (such as the heating load of a back pressure turbine exhaust direct supply heat network) is cut off, the cooling flow required by the through flow of the last stages can be completely absorbed by the variable heat recovery system, and the back pressure turbine can continuously and safely operate.
Taking the back pressure turbine with one-stage high-parameter industrial heat load and heating load as an example, the thermodynamic system thereofAs shown in figure 2, the rated inlet flow of the back pressure type steam turbine in the heating season is set to be Q01Inlet pressure of P01The industrial extraction pressure is PWorker's toolThe through flow rate after the industrial steam extraction regulating device is Q02The steam extraction amount and the pressing force of each stage of heater and deaerator are Q from high to low in sequenceb1、Qb2、Qb3、Qb4And the heating load is QMiningThe industrial extraction steam is QWorker's tool. When the factors such as shaft seal steam leakage loss and the like are not considered, the simple relation among the flow rates is expressed as follows:
Q01＝Q02+Qworker's tool+Qb1
Q02＝QMining+Qb2+Qb3+Qb4
Under variable working conditions, the inlet flow of the back pressure turbine is Q1Inlet pressure of P1The rear through-flow of the steam extraction regulating device is Q2The back flow pressure of the steam extraction adjusting device is P2And the heating load is QMining. Heater extraction Q before extraction regulating deviceb1And industrial extraction steam quantity QWorker's toolThe ratio of the two is mu1The steam extraction amount of the three heaters behind the steam extraction adjusting device and the heating heat supply amount Q under each working conditionMiningAre respectively mu2、μ3、μ4. The through-flow after the steam extraction regulating device is as follows:
Q1＝Qmining×(1+μ2+μ3+μ4)+QWorker's tool×(1+μ1)
According to the frieger formula, one can obtain:
when P is presentWorker's tool＜＜P1Then, the above equation becomes:
operating mode of last-stage heat supply removal at steam exhaust endDuring operation, as industrial heat supply usually has no backwater, the system needs a large amount of water supplement, and the cooling flow required by the last-stage moving blade of the back pressure turbine is less than the backheating steam extraction quantity Qb4At the moment, the exhaust steam of the back pressure turbine is consumed by the variable heat regeneration system, so that the back pressure turbine has the precondition that the back pressure turbine can operate under all working conditions.
In the variable regenerative systems of embodiments 1 and 2, the final low-pressure heater can be replaced by an atmospheric deaerator, and details thereof are not repeated.
The invention is not limited to the above alternative embodiments, and any other various forms of products can be obtained by anyone in the light of the present invention, but any changes in shape or structure thereof, which fall within the scope of the present invention as defined in the claims, fall within the scope of the present invention.
Claims (6)
1. The utility model provides a multistage heat supply back pressure steam turbine, includes back pressure steam turbine body and locates steam inlet end and the steam extraction end on this back pressure steam turbine body, its characterized in that be equipped with at least one steam extraction adjusting device in the through-flow rank between steam inlet end and the steam extraction end, be provided with heat supply steam extraction openings at different levels and use the steam extraction end as the last stage heat supply steam extraction opening between steam extraction adjusting device and the steam inlet end, between two adjacent steam extraction adjusting device respectively to steam pressure and the flow that corresponds heat supply steam extraction opening are adjusted through each steam extraction adjusting device.
2. The multi-stage heating back pressure turbine according to claim 1, wherein each stage heating steam extraction is provided as an industrial heating steam extraction, and the last stage heating steam extraction is provided as a heating steam extraction or a low-parameter industrial heating steam extraction.
3. A multistage heat supply back pressure turbine thermodynamic system comprising a variable regenerative system and a multistage heat supply back pressure turbine according to any one of claims 1 to 2, the cooling flow required for the through flow of the last stages of the multistage heat supply back pressure turbine being taken up by the variable regenerative system; the variable heat regenerative system comprises at least one stage of heater, and each stage of heater is connected with the multi-stage heat supply back pressure turbine through a heat return pipeline.
4. The thermodynamic system as claimed in claim 3, wherein when the heater is set to one stage, the heater is connected to the exhaust end of the backpressure turbine via a heat return line with a regulating valve.
5. The thermodynamic system of claim 3, wherein when the heaters are set to two or more stages, each stage of heater is connected to the multistage heat supply backpressure turbine through a regenerative pipeline and is connected in series through a water supply pipeline, and whether a regulating valve is arranged on each regenerative pipeline is determined according to the magnitude of the change of the flow rate of regenerative steam extraction of each stage when the multistage heat supply backpressure turbine operates under variable working conditions.
6. A heating method of a multistage heat supply back pressure turbine thermal system, which is applied to the multistage heat supply back pressure turbine thermal system according to any one of claims 3 to 5, the heating method comprising:
controlling the steam inlet amount and the total heat supply amount of the unit through a main steam regulating valve of the multistage heat supply back pressure steam turbine;
the steam pressure and the flow of each stage of heat supply steam extraction port are adjusted by changing the opening of each steam extraction adjusting device;
each stage of heat supply extraction steam is extracted after expansion work is done in the multi-stage heat supply back pressure steam turbine; the exhaust end of the multi-stage heat supply back pressure turbine is used as a final stage heat supply steam extraction port and provides heating steam extraction or low-parameter industrial steam extraction for the outside.
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