CN117892034A - Calculation method, device, equipment and medium for heat supply coal consumption of cogeneration unit - Google Patents
Calculation method, device, equipment and medium for heat supply coal consumption of cogeneration unit Download PDFInfo
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Abstract
The invention discloses a calculation method, a device, equipment and a medium for heat supply coal consumption of a cogeneration unit, wherein the method comprises the following steps: acquiring data of the steam turbine generator unit under a pure condensation working condition, and calculating to obtain heat consumption of a steam turbine under the pure condensation working condition of the steam turbine generator unit; acquiring heat supply working condition data of the steam turbine generator unit under different unit heat supply modes, and calculating to obtain heat consumption of a steam turbine under the heat supply working conditions of the steam turbine generator unit, wherein the heat supply working conditions correspond to the different unit heat supply modes; according to the heat consumption of the turbine under the pure condensation working condition and the heat consumption of the turbine under the heat supply working condition, the heat supply heat of the turbine generator set under different heat supply modes of the turbine generator set and the heat consumption variable quantity of the turbine caused by heat supply are calculated, and then the real coal consumption of unit heat supply of the turbine generator set under different heat supply modes of the turbine generator set is calculated. The invention can reflect the difference of heat supply coal consumption of heat supply steam with different qualities.
Description
Technical Field
The invention relates to the technical field of cogeneration of coal-fired power plants, in particular to a calculation method, a device, equipment and a medium for heat supply coal consumption of a cogeneration unit.
Background
With the speed increase and slow down of the social electricity demand and the large-scale development of renewable energy sources, the utilization time of thermal power is gradually reduced year by year, the power grid function of the coal-fired thermal power unit is gradually changed from a main body to the power regulation type, the operation pressure of coal-fired power generation enterprises is huge, and the long-term survival problem cannot be solved by simply relying on power generation. The heat-engine plant gradually operates thought, the original power generation is mainly used, the industries of resident heat supply, industrial steam supply and the like are used as auxiliary materials, the power generation is changed into the auxiliary materials, the emerging services of resident heat supply, industrial steam supply and the like are greatly developed, the profit field is expanded, and the long-term competitiveness of enterprises is maintained.
For a coal-fired cogeneration thermal power unit, the heat supply cost is an important economic index of enterprise production and operation, calculates the heat supply cost of different quality steam, and has important values for heat supply income accounting, heat supply transformation mode selection, heat supply operation optimization, external heat price negotiation and other works.
The heat supply cost consists of heat supply coal cost, heat supply water consumption cost, equipment depreciation cost, manpower resource cost and the like. Wherein, the heat supply coal cost accounts for more than 60 percent of the heat supply cost, and the heat supply coal cost is directly related to the heat supply coal consumption. In the prior art, when the power plant calculates the heating coal, an apportionment method of 'benefit power return' is generally adopted according to the standard of DL/T904 'calculation method of technical economic index of thermal power plant', and the heating coal consumption obtained by the calculation method is only related to the boiler efficiency and the pipeline efficiency, but not related to the quality of the supplied steam. The method greatly reduces the power generation coal consumption of the unit, but the calculated fuel coal consumption of each stage of heat supply is the same, and the real situation of each stage of heat supply can not be well reflected.
Disclosure of Invention
The invention provides a calculation method, a device, equipment and a medium for heat supply coal consumption of a cogeneration unit, which are used for solving the technical problem that the calculated heat supply fuel coal consumption of each stage is the same and cannot well reflect the real situation of heat supply of each stage in the prior art.
In order to solve the technical problems, the embodiment of the invention provides a method for calculating heat supply coal consumption of a cogeneration unit, which comprises the following steps:
acquiring pure condensation working condition data obtained by carrying out a pure condensation working condition thermodynamic performance test on a steam turbine generator unit under the operation electric load of a certain unit;
according to the pure condensation working condition data, calculating to obtain the heat consumption of the turbine under the pure condensation working condition of the turbine generator set;
acquiring heat supply condition data obtained by performing heat supply condition thermal performance tests on a steam turbine generator unit under different heat supply modes of the steam turbine generator unit, the same running electric load of the steam turbine generator unit and a certain heat supply flow; wherein, the unit heat supply mode includes: steam turbine main steam extraction heat supply, cold and hot re-extraction heat supply and middle-exhaust steam extraction heat supply;
according to the heat supply working condition data, calculating to obtain heat consumption and heat supply quantity of a heat supply working condition steam turbine corresponding to different heat supply modes of the steam turbine generator unit under the heat supply working condition;
according to the heat consumption of the turbine under the pure condensation working condition and the heat consumption of the turbine under the heat supply working condition, calculating to obtain the heat consumption variable quantity of the turbine caused by heat supply of the turbine generator unit under different unit heat supply modes;
and calculating to obtain the actual heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes according to the heat consumption variable quantity of the steam turbine and the heat supply heat.
Preferably, the pure condensation condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder and the temperature flow of the feed water pressure;
the heating condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply extraction pressure and the temperature flow of the heat supply drainage pressure.
As a preferred scheme, the heat consumption of a turbine generator set under the pure condensation working condition under the operation electric load of a certain set and the heat consumption of a turbine generator set under the heating working condition under the same operation electric load of the set are calculated through the following formulas:
Qsr＝W ms ×(h ms -h fw )+(W hr -W rh )×(h hr -h cr )+W rh ×(h hr -h rh )；
wherein Qsr is the heat consumption of a turbine under the pure condensation condition of a turbine generator set under the running electric load of a certain unit or the heat consumption of a turbine under the heating condition of the same unit, W ms Is the main steam flow, h ms Is the enthalpy of main steam, h fw For final feed enthalpy, W hr For hot reheat steam flow, W rh For reheat steam desuperheating water flow, h hr Enthalpy of hot reheat steam, h cr For cold reheat steam enthalpy, h rh The enthalpy of the desuperheating water for reheat steam.
As a preferred scheme, the heat supply quantity of the steam turbine generator unit under the heat supply working condition is calculated through the following formula:
Q gr ＝W gr ×(h gr -h ss )；
wherein W is gr For supplying heat steam flow, h gr To heat vapor enthalpy, h ss For supplying heat and hydrophobic enthalpy.
As a preferred scheme, the turbine heat consumption variable quantity of the steam turbine generator unit caused by heat supply under the same unit operation electric load is calculated by the following formula:
ΔQ sr ＝Q srg -Q src 。
as a preferred scheme, the true heat supply coal consumption of the steam turbine generator unit is calculated through the following formula:
wherein B is bc Is pureFuel consumption of condensing working condition unit, B bg For the consumption of coal by the heat supply working condition unit, Q gr For heat supply, eta gl For boiler efficiency, eta gd Is pipeline efficiency.
On the basis of the above embodiment, another embodiment of the present invention provides a device for calculating heat supply coal consumption of a cogeneration unit, including: the system comprises a pure condensation working condition data acquisition module, a pure condensation working condition heat consumption calculation module, a heat supply working condition data acquisition module, a heat supply working condition heat consumption acquisition module, a turbine heat consumption variation calculation module and a real heat supply coal consumption calculation module;
the pure condensation working condition data acquisition module is used for acquiring pure condensation working condition data obtained by carrying out a pure condensation working condition thermal performance test on the steam turbine generator unit under the operation electric load of a certain unit;
the pure condensing condition heat consumption calculation module is used for calculating and obtaining the heat consumption of the pure condensing condition steam turbine of the steam turbine generator unit under the pure condensing condition according to the pure condensing condition data;
the heat supply working condition data acquisition module acquires heat supply working condition data obtained by performing heat supply working condition thermal performance tests on the steam turbine generator unit under different unit heat supply modes, the same unit operation electric load and a certain heat supply flow; wherein, the unit heat supply mode includes: steam turbine main steam extraction heat supply, cold and hot re-extraction heat supply and middle-exhaust steam extraction heat supply;
the heat supply working condition heat consumption acquisition module is used for calculating and obtaining heat consumption and heat supply heat of a heat supply working condition steam turbine corresponding to different heat supply modes of the steam turbine generator unit under the heat supply working condition according to the heat supply working condition data;
the turbine heat consumption variable quantity calculating module is used for calculating the turbine heat consumption variable quantity of the steam turbine generator unit caused by heat supply under different unit heat supply modes according to the heat consumption of the turbine under the pure condensation working condition and the heat consumption of the turbine under the heat supply working condition;
the real heat supply coal consumption calculation module is used for calculating the real heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes according to the heat consumption variable quantity of the steam turbine and the heat supply heat.
Preferably, the pure condensation condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder and the temperature flow of the feed water pressure;
the heating condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply extraction pressure and the temperature flow of the heat supply drainage pressure.
On the basis of the embodiment, the invention further provides electronic equipment, which comprises a processor, a memory and a computer program stored in the memory and configured to be executed by the processor, wherein the computer program is executed by the processor to realize the method for calculating the heat supply coal consumption of the cogeneration unit.
On the basis of the embodiment, the invention further provides a storage medium, which comprises a stored computer program, wherein the equipment where the storage medium is controlled to execute the method for calculating the heat supply coal consumption of the cogeneration unit according to the embodiment of the invention when the computer program runs.
Compared with the prior art, the embodiment of the invention has the following beneficial effects:
based on pure condensation working condition data obtained by a pure condensation working condition thermodynamic performance test of the steam turbine generator unit under a certain operation electric load, the heat consumption of a pure condensation working condition steam turbine of the steam turbine generator unit under the pure condensation working condition is calculated; based on heat supply working condition data obtained by heat supply working condition thermal performance tests of the steam turbine generator unit under different heat supply modes of the steam turbine generator unit, the same running electric load of the steam turbine generator unit and a certain heat supply flow, heat consumption and heat supply quantity of heat supply working condition turbines corresponding to the different heat supply modes of the steam turbine generator unit are calculated; then, according to the total heat consumption of the turbine under the pure condensation working condition and the total heat consumption of the turbine under the heat supply working condition, calculating to obtain the heat consumption variable quantity of the turbine caused by heat supply of the turbine generator unit under different unit heat supply modes; and finally, according to the heat consumption variable quantity and the heat supply quantity of the steam turbine, calculating to obtain the real heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes.
The invention overcomes the defect that the current general calculation method for the heat supply coal consumption index of the coal-fired unit cannot react to the difference of heat supply steam with different qualities. Because the difference of the heat supply steam with different qualities is related to different unit heat supply modes, the real heat supply coal consumption can be quantitatively evaluated from three dimensions of the unit heat supply mode, the heat supply flow and the unit operation electric load by the related data of the turbine pure condensation and heat supply working condition thermodynamic performance test, the difference of the different heat supply modes is reflected, the difference of the heat supply steam with different qualities is reflected, and the method has guiding significance for the work of coal-fired cogeneration unit heat price negotiation, heat supply operation mode optimization, heat supply transformation scheme selection and the like of power plant personnel.
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Fig. 1 is a schematic flow chart of a method for calculating heat supply coal consumption of a cogeneration unit according to an embodiment of the invention;
fig. 2 is a schematic structural diagram of a computing device for heat supply coal consumption of a cogeneration unit according to an embodiment of the invention.
Detailed Description
For the purposes of making the objects, technical solutions and advantages of the present application more apparent, the technical solutions in the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application, and it is apparent that the described embodiments are some, but not all, embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art based on the embodiments herein without making any inventive effort, are intended to be within the scope of the present application.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application; the terms "comprising" and "having" and any variations thereof in the description and claims of the present application and in the description of the figures above are intended to cover non-exclusive inclusions.
In the description of the embodiments of the present application, the technical terms "first," "second," etc. are used merely to distinguish between different objects and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated, a particular order or a primary or secondary relationship. In the description of the embodiments of the present application, the meaning of "plurality" is two or more unless explicitly defined otherwise.
Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of the present application. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. Those of skill in the art will explicitly and implicitly appreciate that the embodiments described herein may be combined with other embodiments.
In the description of the embodiments of the present application, the term "and/or" is merely an association relationship describing an association object, which means that three relationships may exist, for example, a and/or B may mean: a exists alone, A and B exist together, and B exists alone. In addition, the character "/" herein generally indicates that the front and rear associated objects are an "or" relationship.
In the description of the embodiments of the present application, the term "plurality" refers to two or more (including two), and similarly, "plural sets" refers to two or more (including two), and "plural sheets" refers to two or more (including two).
In the description of the embodiments of the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured" and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally formed; or may be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the embodiments of the present application will be understood by those of ordinary skill in the art according to the specific circumstances.
Example 1
Referring to fig. 1, a flow chart of a method for calculating heat supply coal consumption of a cogeneration unit according to an embodiment of the invention includes the following specific steps:
s1, acquiring pure condensation condition data obtained by a pure condensation condition thermodynamic performance test of a steam turbine generator unit under the operation electric load of a certain unit;
s2, calculating to obtain the heat consumption of the turbine in the pure condensation working condition of the turbine generator unit under the pure condensation working condition according to the pure condensation working condition data;
s3, acquiring heat supply condition data obtained by heat supply condition thermal performance tests of the steam turbine generator unit under different heat supply modes of the steam turbine generator unit, the same unit operation electric load and a certain heat supply flow; wherein, the unit heat supply mode includes: steam turbine main steam extraction heat supply, cold and hot re-extraction heat supply and middle-exhaust steam extraction heat supply;
preferably, the pure condensation condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder and the temperature flow of the feed water pressure; the heating condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply extraction pressure and the temperature flow of the heat supply drainage pressure.
S4, calculating to obtain heat consumption and heat supply quantity of the heat supply working condition turbines corresponding to different heat supply modes of the steam turbine generator unit under the heat supply working condition according to the heat supply working condition data;
preferably, the heat consumption of the turbine generator set under the pure condensation working condition under the operation electric load of a certain set and the heat consumption of the turbine generator set under the heating working condition under the same operation electric load of the set are calculated by the following formulas:
Qsr＝W ms ×(h ms -h fw )+(W hr -W rh )×(h hr -h cr )+W rh ×(h hr -h rh )；
wherein Qsr is the heat consumption of a turbine under the pure condensing condition of a turbine generator set under the operation electric load of a certain unit or the heat consumption of a turbine under the heating condition of the same unit, W ms Is the main steam flow, h ms Is the enthalpy of main steam, h fw For final feed enthalpy, W hr For hot reheat steam flow, W rh For reheat steam desuperheating water flow, h hr Enthalpy of hot reheat steam, h cr For cold reheat steam enthalpy, h rh The enthalpy of the desuperheating water for reheat steam.
Preferably, the heat supply quantity of the steam turbine generator unit under the heat supply working condition is calculated through the following formula:
Q gr ＝W gr ×(h gr -h ss )；
wherein W is gr For supplying heat steam flow, h gr To heat vapor enthalpy, h ss For supplying heat and hydrophobic enthalpy.
S5, calculating to obtain the heat consumption variable quantity of the steam turbine caused by heat supply of the steam turbine generator unit in different unit heat supply modes according to the heat consumption of the steam turbine under the pure condensation working condition and the heat consumption of the steam turbine under the heat supply working condition;
preferably, the turbine heat consumption variable quantity of the steam turbine generator unit caused by heat supply under the same unit operation electric load is calculated by the following formula:
ΔQ sr ＝Q srg -Q src 。
s6, calculating to obtain the actual heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes according to the steam turbine heat consumption variable quantity and the heat supply heat.
Preferably, the true heat supply coal consumption of the steam turbine generator unit is calculated by the following formula:
wherein B is bc B is the fuel consumption of the unit under the pure condensation working condition bg For the consumption of coal by the heat supply working condition unit, Q gr For heat supply, eta gl For boiler efficiency, eta gd Is pipeline efficiency.
In the prior art, when a power plant calculates heating coal, a power plant usually adopts an allocation method of 'benefit power return' according to the standard of DL/T904 'technical economic index calculation method of a thermal power plant', wherein the 'benefit power return' method is formulated based on a first law of thermodynamics and is a legal allocation method of China, and the method is adopted in GB35574 'energy consumption limit of a cogeneration unit product' and DL/T904 'technical economic index calculation method of the thermal power plant'. The essence is that the heat consumed by heat supply and power generation is distributed according to the proportion of the total heat consumption of the steam turbine. The heat supply coal consumption calculation formula given in DL/T904-2015 "method for calculating technical economic index of thermal Power plant" is as follows:
wherein B is b For the total standard coal consumption, alpha is the heating ratio, i.e. the heating quantity ΣQ gr And total heat consumption Σq sr Ratio of the two components.
According to the two above formulas of the DLT904 standard, the heat supply coal consumption is only related to the boiler efficiency and the pipeline efficiency (the standard coal heating value is 29307.6 kJ/kg). The calculation shows that for a large-scale heat supply unit, the heat supply coal consumption is generally 37-40 kg/GJ. And the heat supply coal cost of the coal-fired cogeneration unit is equal to the heat supply coal consumption multiplied by the standard coal price. Therefore, the heat method is simple and convenient to calculate, but the cost of heat supply and coal burning of steam extraction of the turbines with different pressure grades is the same, and the economical difference of different quality steam cannot be reflected.
Therefore, we begin to adopt the apportionment mode of 'benefit heat returning', the 'benefit heat returning' method, in short, distributes the benefits of cogeneration to heat supply, the unit generates electricity with unchanged coal consumption, and the heat supply economy is finally embodied in the real heat supply coal consumption of different heat supply modes.
Considering that the current thermal power unit load rate is low, unit heat supply generally does not influence load scheduling. Assume that the unit has a certain electric load P under the pure condensing condition g The lower fuel consumption is B bc The method comprises the steps of carrying out a first treatment on the surface of the After the heat supply of the unit, the electric load is also P g And the heat supply is Q gr When the total consumption of the fire coal is B bg . According to the idea of 'benefit to return heat', the heat supply quantity Q gr The corresponding fuel consumption is B bg -B bc 。
According to the allocation idea of 'benefit heat recovery', the following two calculation methods exist:
(1) "actual enthalpy drop method": the actual enthalpy drop method is to distribute the total coal consumption according to the ratio of the actual enthalpy drop deficiency of the steam extraction of the steam turbine and the total actual enthalpy drop of the steam inlet, in short, the benefits of cogeneration are distributed to heat supply, the coal consumption of the unit power generation is unchanged, and the heat supply economy is finally embodied in the heat supply coal consumption of different heat supply modes. The method can accurately reflect the heat supply essence of different extraction steam, but the calculation process is complex and difficult to master.
(2) Positive balance coal consumption statistics: and (5) counting the fire coal quantity fed into the furnace under the same electric load pure condensation and heat supply working conditions by adopting a positive balance method. However, the weighing accuracy of the coal amount is insufficient, and the heat value of the coal is unstable, so that the method has larger error and is less adopted.
In summary, in order to solve the above problems, the present invention provides a new method for calculating the heat supply coal consumption of a co-production unit, which includes the steps of firstly analyzing factors affecting the real heat supply coal consumption of the unit: the influence of the unit heating mode on the real heat supply coal consumption of the unit is most direct, and the change of the unit operation electric load and the heat supply flow rate can possibly lead the unit to introduce a middle regulating valve, a seat cylinder valve, a rotary partition plate, a middle-row butterfly valve and other heat supply regulating means for maintaining the heat supply parameters, thereby leading the heat supply coal consumption to change, and the test research and calculation of the real heat supply coal consumption can be carried out from the three dimensions (the unit heating mode, the unit operation electric load and the heat supply flow rate).
Firstly, performing a turbine pure condensing thermal performance test under a normal running load of a unit, recording data such as main reheat steam pressure temperature, extraction steam pressure temperature of each section of a high-pressure cylinder, water supply pressure temperature and flow rate and the like, and calculating to obtain the total heat consumption of the turbine (namely main and reheat steam heat absorption). And (3) keeping the electric load of the unit unchanged, slowly inputting a certain section of heat supply and steam extraction of the unit, regulating the heat supply pressure, temperature and flow to normal operation values, after the heat supply parameters are stable, performing a heat supply working condition thermodynamic performance test of the steam turbine, recording data such as the pressure temperature of the main reheat steam, the steam extraction pressure temperature of each section of the high-pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply and steam extraction pressure, the temperature flow of the heat supply and drainage steam extraction pressure, and calculating to obtain the total heat consumption and the external heat supply of the steam turbine. And comparing the heat obtained from the boiler under the heating working condition and the pure condensing working condition to obtain real heating coal consumption, and calculating the real heating cost by the real heating coal consumption and the standard coal price, so that the real heating coal consumption is used in daily work of a power plant.
The invention overcomes the defect that the current general calculation method for the heat supply coal consumption index of the coal-fired unit cannot reflect the economic difference of heat supply steam with different qualities. By performing thermal performance tests of pure condensation and heat supply working conditions, real heat supply coal consumption can be quantitatively evaluated from three dimensions of a heat supply mode, heat supply flow and unit load, and heat supply economy of different heat supply modes is reflected. The method has guiding significance for the work of negotiating the heat price of the coal-fired cogeneration unit, optimizing the heat supply operation mode, selecting the heat supply transformation scheme and the like for power plant personnel, and comprises the following specific implementation steps:
for an engine unit, the real heat supply coal consumption is mainly influenced by a heat supply mode, unit load and heat supply quantity, and the method performs tests and calculation from the three dimensions:
in step S1, taking a certain unit heating mode as a research object, firstly selecting a certain unit operation electric load, carrying out a pure condensing condition thermodynamic performance test on a turbo generator unit, and recording pure condensing condition data such as main reheat steam pressure temperature, extraction steam pressure temperature of each section of a high-pressure cylinder, water supply pressure temperature flow and the like.
In step S2, according to the pure condensation working condition data, the heat consumption of the pure condensation working condition steam turbine corresponding to the heat supply mode of the steam turbine generator unit is calculated and obtained under the pure condensation working condition.
In step S3, the operation electric load of the unit is kept unchanged, a certain section of heat supply and steam extraction of the unit is slowly input, the heat supply pressure, the temperature and the flow are regulated to normal operation values, after the heat supply parameters are stable, a heat supply working condition thermodynamic performance test of the steam turbine is carried out, and heat supply working condition data such as the pressure temperature of main reheat steam, the steam extraction pressure temperature of each section of the high-pressure cylinder, the flow of water supply pressure and temperature of heat supply steam extraction pressure and flow of heat supply drainage steam extraction pressure and the like are recorded.
In step S4, according to the heat supply working condition data, calculating to obtain heat consumption and heat supply quantity of a heat supply working condition turbine corresponding to the heat supply mode of the steam turbine generator unit under the heat supply working condition;
the heat consumption of a turbine in a pure condensation working condition under a certain unit operation electric load of the turbine generator unit and the heat consumption of a turbine in a heat supply working condition under the same unit operation electric load of the turbine generator unit are calculated through the following formulas (the heat consumption calculation formulas of the turbine in the pure condensation working condition and the heat supply working condition are the same, and the heat absorption of main steam and the heat absorption of reheat steam are respectively):
Qsr＝W ms ×(h ms -h fw )+(W hr -W rh )×(h hr -h cr )+W rh ×(h hr -h rh )；
wherein W is ms Is the main steam flow, t/h (measured by a flowmeter); h is a ms kJ/kg (calculated from main steam pressure, temperature) for main steam enthalpy; h is a fw For final enthalpy of feed water, kJ/kg (calculated by pressure, temperature), W hr Is the hot reheat steam flow, t/h (calculated by the main steam flow and a high pressure cylinder steam extraction flow meter), W rh For reheat steam desuperheating water flow, t/h (measured by flowmeter), h hr For the enthalpy of the hot reheat steam, kJ/kg (calculated by pressure, temperature), h cr For cold reheat steam enthalpy, kJ/kg (calculated by pressure, temperature), h rh kJ/kg (calculated by pressure, temperature) for reheat steam desuperheating enthalpy;
the heat supply quantity of the steam turbine generator unit under the heat supply working condition is calculated through the following formula:
Q gr ＝W gr ×(h gr -h ss )；
wherein W is gr For supplying heat steam flow, h gr To heat vapor enthalpy, h ss For supplying heat and hydrophobic enthalpy.
In step S5, according to the total heat consumption of the turbine under the pure condensation condition and the total heat consumption of the turbine under the heat supply condition, the heat consumption variable quantity of the turbine caused by heat supply of the turbine generator unit in different heat supply modes of the turbine generator unit is calculated and obtained:
ΔQ sr ＝Q srg -Q src
wherein Q is src The total heat consumption of the steam turbine is the pure condensation working condition, and MJ/h; q (Q) srg The total heat consumption of the steam turbine under the heating working condition is MJ/h.
In step S6, according to the heat consumption variable quantity of the steam turbine and the heat supply quantity, calculating to obtain the actual heat supply coal consumption of the steam turbine generator unit in different unit heat supply modes:
wherein B is bc The fuel consumption of the unit under the pure condensation working condition is kg/s, B bg For the consumption of coal combustion of a heat supply working condition unit, kg/s and Q gr For supplying heat in this heating mode, GW (by calculating heat supply steam flow, heat supply steam enthalpy and drain or water supplementing enthalpy), η gl For boiler efficiency,% (obtained by performing boiler efficiency tests or based on plant statistics), η gd For pipe efficiency,% (typically 99%).
After the test and calculation are carried out on the real heat supply coal consumption of a certain unit heat supply mode, the unit operation electric load can be kept unchanged, the unit heat supply mode and heat supply flow are changed, and the test and calculation are carried out again, so that the real heat supply coal consumption of different heat supply modes under the unit operation electric load and heat supply flow can be obtained. But only the actual heating coal consumption of one heating mode should be tested and calculated at a time.
The unit running electric load and the heat supply flow generally take the average unit load and the average heat supply quantity within a certain period of time, and can also be selected according to the requirements of power plant personnel.
The purpose of the thermal performance test of the steam turbine is to determine the operating parameters and economy of the steam turbine under a certain operating condition, and in a specific embodiment, the thermal performance test of the steam turbine under the pure condensation and heat supply conditions is taken as an example for a certain plant to perform the following description.
1 purpose of test
1.1 under the operating conditions specified by a manufacturing plant, under the 230MW load pure condensing working condition, main economic indexes of the turbo generator set are measured: high and medium pressure cylinder efficiency, heat rate and the like of the steam turbine;
1.2, keeping the 230MW electric load unchanged, and measuring main economic indexes of the steam turbine generator unit under the heating working condition (2.5 MPa 100 t/h): high and medium pressure cylinder efficiency, heat rate and the like of the steam turbine;
1.3, keeping the 230MW electric load unchanged, and measuring main economic indexes of the steam turbine generator unit under the heating working condition (1.5 MPa 100 t/h): high and medium pressure cylinder efficiency, heat rate and the like of the steam turbine.
2 test standard and basis
2.1 test criteria:
2.1.1 American society of mechanical Engineers "turbine Performance test protocol" (ASME PTC 6-2004);
2.1.2 national institutes of standardization of the chinese national institutes of standardization "turbine thermal performance acceptance test procedure part 2: method B-Wide accuracy test of turbines of various types and capacities (GB/T8117.2-2008).
2.2 test basis:
2.2.1 steam turbine plant, steam turbine thermodynamic characteristics calculation book;
2.2.2 havingParameter Water and Water vapor Property parameter handbook (1997 Industrial IFC formula calculation);
2.2.3 design, manufacturing technology documentation, materials, and related contracts.
3 test point and measuring method
The instruments and meters used in the test are checked to be qualified by legal metering departments.
3.1 Main condensate flow measurement: the main condensate flow is measured by adopting a throat pressure-taking long-neck flow nozzle which accords with ASME PTC6-2004 standard and has high precision and low beta value. The flow measurement pipe section is arranged on a horizontal condensate pipeline between a #5 low pressure adding outlet and an deaerator inlet, and flow differential pressure is measured by two groups of pressure taking holes which form 180 degrees with each other by using a 0.05-level ROSEMOUNT differential pressure transmitter;
3.2 measurement of generator power: the electric power of the generator outlet and the variable power of the high factory obtain site DCS data;
3.3 temperature measurement: measuring by using a 0.1-grade ROSEMUNT temperature transmitter and an industrial grade I thermocouple;
3.4 measurement of pressure and auxiliary flow: pressures below 1MPa were measured using a 0.075 grade rossemount pressure transmitter and pressures above 1MPa were measured using a 0.1 grade rossemount pressure transmitter. The superheater and reheater de-temperature water flow takes on-site DCS data. The gate rod steam leakage flow and the shaft seal steam leakage flow adopt design values;
3.5 water level measurement: the water level of the deaerator water tank and the water level of the condenser are measured by using a liquid level transmitter;
3.6 System leakage measurement: during the test, the visible leakage flow which cannot be isolated in the unit system is measured by a tester on site by using a measuring cylinder and a stopwatch;
3.7 test data acquisition and sampling frequency: the main flow differential pressure, the auxiliary flow differential pressure, the pressure and the temperature are measured and recorded by an IMP distributed data acquisition system, the data are acquired every 2 seconds, and the average value of the data is recorded every 30 seconds.
4 test method and test conditions
4.1 test method:
4.1.1, installing test points and a data acquisition system, and debugging the data acquisition system;
4.1.2 checking the isolation condition of the system;
4.1.3, adjusting the operation parameters to enable the operation parameters to meet the requirements of the test outline;
and 4.1.4 the unit operation system is regulated to be stable for half an hour according to the requirement, and then a test can be carried out, wherein the test working condition lasts for 1 hour.
4.2 plant conditions:
4.2.1 the main and auxiliary equipment is normally put into operation, and the equipment and the system have no abnormal leakage;
4.2.2 the turbine speed regulating system works normally and the vacuum tightness is qualified.
4.3 operating conditions: the test thermodynamic system operates and remains stable in accordance with the thermodynamic cycle specified by the design thermal equilibrium diagram.
4.3.1 the high and low pressure heater and deaerator are operated according to the design operation mode, and the dewatering is normally operated according to the design mode;
4.3.2, reducing the steam parameters and the up-and-down fluctuation of the water level of each water storage container as much as possible;
4.3.3, adding no or as little reheater desuperheating water as possible, if desuperheating water is needed, keeping the desuperheating water constant in the test duration;
the hydrogen pressure and the hydrogen purity of a hydrogen cooling system of the 4.3.4 generator are adjusted to rated values, hydrogen supplementing is stopped during a test period, and water supplementing is stopped in an internal cooling water tank;
4.3.5 feeding coal in advance, wherein the auxiliary machine normally operates during the test, keeps stable, and does not perform start-stop operation so as to ensure stable combustion during the test, and the operation parameters reach the requirements;
4.3.6, the pressure of each monitoring section does not exceed the design maximum value in the unit test, the main operation parameters meet the requirements of the following table 1, and the deviation of the two sides of the reheat steam temperature does not exceed 5 ℃;
table 1 main operating parameters meet requirement 4.4 test conditions: as shown in table 2 below:
table 2 summary table of test conditions of the unit
The running parameters of the unit can be acquired by additionally installing or utilizing the original pressure, temperature, flow and other instruments of the unit, and the economical efficiency data can be calculated according to the running parameters.
Example two
Referring to fig. 2, a schematic structural diagram of a computing device for heat supply and coal consumption of a cogeneration unit according to an embodiment of the invention is shown, where the device includes: the system comprises a pure condensation working condition data acquisition module, a pure condensation working condition heat consumption calculation module, a heat supply working condition data acquisition module, a heat supply working condition heat consumption acquisition module, a turbine heat consumption variation calculation module and a real heat supply coal consumption calculation module;
the pure condensation working condition data acquisition module is used for acquiring pure condensation working condition data obtained by carrying out a pure condensation working condition thermal performance test on the steam turbine generator unit under the operation electric load of a certain unit;
the pure condensing condition heat consumption calculation module is used for calculating and obtaining the heat consumption of the pure condensing condition steam turbine of the steam turbine generator unit under the pure condensing condition according to the pure condensing condition data;
the heat supply working condition data acquisition module acquires heat supply working condition data obtained by performing heat supply working condition thermal performance tests on the steam turbine generator unit under different unit heat supply modes, the same unit operation electric load and a certain heat supply flow; wherein, the unit heat supply mode includes: steam turbine main steam extraction heat supply, cold and hot re-extraction heat supply and middle-exhaust steam extraction heat supply;
the heat supply working condition heat consumption acquisition module is used for calculating and obtaining heat consumption and heat supply heat of a heat supply working condition steam turbine corresponding to different heat supply modes of the steam turbine generator unit under the heat supply working condition according to the heat supply working condition data;
the turbine heat consumption variable quantity calculating module is used for calculating the turbine heat consumption variable quantity of the steam turbine generator unit caused by heat supply under different unit heat supply modes according to the heat consumption of the turbine under the pure condensation working condition and the heat consumption of the turbine under the heat supply working condition;
the real heat supply coal consumption calculation module is used for calculating the real heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes according to the heat consumption variable quantity of the steam turbine and the heat supply heat.
Preferably, the pure condensation condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder and the temperature flow of the feed water pressure;
the heating condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply extraction pressure and the temperature flow of the heat supply drainage pressure.
It should be noted that the above-described apparatus embodiments are merely illustrative, and the units described as separate units may or may not be physically separate, and units shown as units may or may not be physical units, may be located in one place, or may be distributed over a plurality of network units. Some or all of the modules may be selected according to actual needs to achieve the purpose of the solution of this embodiment. In addition, in the drawings of the embodiment of the device provided by the invention, the connection relation between the modules represents that the modules have communication connection, and can be specifically implemented as one or more communication buses or signal lines. Those of ordinary skill in the art will understand and implement the present invention without undue burden.
It will be clearly understood by those skilled in the art that, for convenience and brevity, the specific working process of the apparatus described above may refer to the corresponding process in the foregoing method embodiment, which is not described herein again.
Example III
Correspondingly, the embodiment of the invention provides electronic equipment, which comprises a processor, a memory and a computer program stored in the memory and configured to be executed by the processor, wherein the computer program is executed by the processor to realize the method for calculating the heat supply coal consumption of the cogeneration unit.
The electronic equipment can be a desktop computer, a notebook computer, a palm computer, a cloud server and other computing equipment. The device may include, but is not limited to, a processor, a memory.
The processor may be a central processing unit (Central Processing Unit, CPU), other general purpose processors, digital signal processors (Digital Signal Processor, DSP), application specific integrated circuits (Application Specific Integrated Circuit, ASIC), off-the-shelf programmable gate arrays (Field-Programmable Gate Array, FPGA) or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, or the like. A general purpose processor may be a microprocessor or the processor may be any conventional processor or the like that is a control center of the device, connecting the various parts of the overall device using various interfaces and lines.
Example IV
Correspondingly, the embodiment of the invention provides a storage medium which comprises a stored computer program, wherein equipment where the storage medium is controlled to execute the calculation method of the heat supply coal consumption of the cogeneration unit according to the embodiment of the invention when the computer program runs.
The memory may be used to store the computer program, and the processor may implement various functions of the device by running or executing the computer program stored in the memory, and invoking data stored in the memory. The memory may mainly include a storage program area and a storage data area, wherein the storage program area may store an operating system, an application program required for at least one function, and the like; the storage data area may store data created according to the use of the cellular phone, etc. In addition, the memory may include high-speed random access memory, and may also include non-volatile memory, such as a hard disk, memory, plug-in hard disk, smart Media Card (SMC), secure Digital (SD) Card, flash Card (Flash Card), at least one disk storage device, flash memory device, or other volatile solid-state storage device.
The storage medium is a computer readable storage medium, and the computer program is stored in the computer readable storage medium, and when executed by a processor, the computer program can implement the steps of the above-mentioned method embodiments. Wherein the computer program comprises computer program code which may be in source code form, object code form, executable file or some intermediate form etc. The computer readable medium may include: any entity or device capable of carrying the computer program code, a recording medium, a U disk, a removable hard disk, a magnetic disk, an optical disk, a computer Memory, a Read-Only Memory (ROM), a random access Memory (RAM, random Access Memory), an electrical carrier signal, a telecommunications signal, a software distribution medium, and so forth. It should be noted that the computer readable medium contains content that can be appropriately scaled according to the requirements of jurisdictions in which such content is subject to legislation and patent practice, such as in certain jurisdictions in which such content is subject to legislation and patent practice, the computer readable medium does not include electrical carrier signals and telecommunication signals.
While the foregoing is directed to the preferred embodiments of the present invention, it will be appreciated by those skilled in the art that changes and modifications may be made without departing from the principles of the invention, such changes and modifications are also intended to be within the scope of the invention.
Claims (10)
1. The calculation method of the heat supply coal consumption of the cogeneration unit is characterized by comprising the following steps of:
acquiring pure condensation working condition data obtained by carrying out a pure condensation working condition thermodynamic performance test on a steam turbine generator unit under the operation electric load of a certain unit;
according to the pure condensation working condition data, calculating to obtain the heat consumption of the turbine under the pure condensation working condition of the turbine generator set;
acquiring heat supply condition data obtained by performing heat supply condition thermal performance tests on a steam turbine generator unit under different heat supply modes of the steam turbine generator unit, the same running electric load of the steam turbine generator unit and a certain heat supply flow; wherein, the unit heat supply mode includes: steam turbine main steam extraction heat supply, cold and hot re-extraction heat supply and middle-exhaust steam extraction heat supply;
according to the heat supply working condition data, calculating to obtain heat consumption and heat supply quantity of a heat supply working condition steam turbine corresponding to different heat supply modes of the steam turbine generator unit under the heat supply working condition;
according to the heat consumption of the turbine under the pure condensation working condition and the heat consumption of the turbine under the heat supply working condition, calculating to obtain the heat consumption variable quantity of the turbine caused by heat supply of the turbine generator unit under different unit heat supply modes;
and calculating to obtain the actual heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes according to the heat consumption variable quantity of the steam turbine and the heat supply heat.
2. The method for calculating heat supply coal consumption of a cogeneration unit according to claim 1, wherein the pure condensation condition data comprises: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder and the temperature flow of the feed water pressure;
the heating condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply extraction pressure and the temperature flow of the heat supply drainage pressure.
3. The method for calculating heat supply coal consumption of a cogeneration unit according to claim 1, wherein the heat consumption of a turbine in a pure condensation condition under a certain unit operation electric load of the turbo generator unit and the heat consumption of the turbine in a heat supply condition under the same unit operation electric load of the turbo generator unit are calculated by the following formula:
Qsr＝W ms ×(h ms -h fw )+(W hr -W rh )×(h hr -h cr )+W rh ×(h hr -h rh )；
wherein Qsr is the heat consumption of a turbine under the pure condensation condition of a turbine generator set under the running electric load of a certain unit or the heat consumption of a turbine under the heating condition of the same unit, W ms Is the main steam flow, h ms Is the enthalpy of main steam, h fw For final feed enthalpy, W hr For hot reheat steam flow, W rh For reheat steam desuperheating water flow, h rh Enthalpy of hot reheat steam, h cr For cold reheat steam enthalpy, h rh The enthalpy of the desuperheating water for reheat steam.
4. The method for calculating the heat supply coal consumption of the cogeneration unit according to claim 3, wherein the heat supply quantity of the steam turbine generator unit under the heat supply working condition is calculated by the following formula:
Q gr ＝W gr ×(h gr -h ss )；
wherein W is gr For supplying heat steam flow, h gr To heat vapor enthalpy, h ss For supplying heat and hydrophobic enthalpy.
5. The method for calculating the heat supply coal consumption of the cogeneration unit according to claim 4, wherein the heat consumption variable quantity of the steam turbine caused by heat supply of the steam turbine generator unit under the same unit operation electric load is calculated by the following formula:
ΔQ sr ＝Q srg -Q src 。
6. the method for calculating the heat supply coal consumption of the cogeneration unit according to claim 5, wherein the actual heat supply coal consumption of the turbo generator unit is calculated by the following formula:
wherein B is bc B is the fuel consumption of the unit under the pure condensation working condition bg For the consumption of coal by the heat supply working condition unit, Q gr For heat supply, eta gl For boiler efficiency, eta gd Is pipeline efficiency.
7. The utility model provides a computing device of cogeneration unit heat supply coal consumption which characterized in that includes: the system comprises a pure condensation working condition data acquisition module, a pure condensation working condition heat consumption calculation module, a heat supply working condition data acquisition module, a heat supply working condition heat consumption acquisition module, a turbine heat consumption variation calculation module and a real heat supply coal consumption calculation module;
the pure condensation working condition data acquisition module is used for acquiring pure condensation working condition data obtained by carrying out a pure condensation working condition thermal performance test on the steam turbine generator unit under the operation electric load of a certain unit;
the pure condensing condition heat consumption calculation module is used for calculating and obtaining the heat consumption of the pure condensing condition steam turbine of the steam turbine generator unit under the pure condensing condition according to the pure condensing condition data;
the heat supply working condition data acquisition module acquires heat supply working condition data obtained by performing heat supply working condition thermal performance tests on the steam turbine generator unit under different unit heat supply modes, the same unit operation electric load and a certain heat supply flow; wherein, the unit heat supply mode includes: steam turbine main steam extraction heat supply, cold and hot re-extraction heat supply and middle-exhaust steam extraction heat supply;
the heat supply working condition heat consumption acquisition module is used for calculating and obtaining heat consumption and heat supply heat of a heat supply working condition steam turbine corresponding to different heat supply modes of the steam turbine generator unit under the heat supply working condition according to the heat supply working condition data;
the turbine heat consumption variable quantity calculating module is used for calculating the turbine heat consumption variable quantity of the steam turbine generator unit caused by heat supply under different unit heat supply modes according to the heat consumption of the turbine under the pure condensation working condition and the heat consumption of the turbine under the heat supply working condition;
the real heat supply coal consumption calculation module is used for calculating the real heat supply coal consumption of the steam turbine generator unit under different unit heat supply modes according to the heat consumption variable quantity of the steam turbine and the heat supply heat.
8. The cogeneration unit heating coal consumption calculation device of claim 7, wherein the pure condensation condition data comprises: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder and the temperature flow of the feed water pressure;
the heating condition data includes: the pressure temperature of the main reheat steam, the extraction pressure temperature of each section of the high pressure cylinder, the temperature flow of the water supply pressure, the temperature flow of the heat supply extraction pressure and the temperature flow of the heat supply drainage pressure.
9. An electronic device comprising a processor, a memory and a computer program stored in the memory and configured to be executed by the processor, the processor implementing the method of calculating the heat supply coal consumption of a cogeneration unit according to any one of claims 1 to 6 when executing the computer program.
10. A storage medium comprising a stored computer program, wherein the computer program, when run, controls a device in which the storage medium is located to perform the method for calculating the heat supply coal consumption of a cogeneration unit according to any one of claims 1 to 6.
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