Heating turbines with a capacity of 40-100 MW

Cogeneration turbines with a capacity of 40-100 MW for initial steam parameters of 130 kgf / cm 2, 565 ° C are designed as a single series, united by common basic solutions, design unity and wide unification of units and parts.

Turbine T-50-130 with two heating steam extractions at 3000 rpm, rated power 50 MW. Further rated power the turbine was increased to 55 MW while improving the turbine economy guarantee.

The T-50-130 turbine is a two-cylinder and has a single-flow exhaust. All extractions, regenerative and heating, together with the exhaust pipe are located in one cylinder low pressure... In the cylinder high pressure steam expands to the pressure of the upper regenerative extraction (about 34 kgf / cm 2), in the low pressure cylinder - to the pressure of the lower heating extraction

For the T-50-130 turbine, the optimal was the use of a two-crown control wheel with a limited isentropic difference and the implementation of the first group of stages with a small diameter. The high pressure cylinder of all turbines has 9 stages - regulating and 8 pressure stages.

Subsequent stages located in a medium or low pressure cylinder have a higher volumetric steam flow and are made with large diameters.

All stages of the turbines of the series have aerodynamically developed profiles; for the regulating stage of the high-pressure pump, blading of the Moscow Power Engineering Institute with radial profiling of the nozzle and working grids is adopted.

The swabbing of the CVD and CSD is performed with radial and axial tendrils, which made it possible to reduce the clearances in the flow path.

The high-pressure cylinder is made counter-flowing relative to the medium-pressure cylinder, which made it possible to use one thrust bearing and a rigid coupling while maintaining relatively small axial clearances in the flow path of both the HPC and the HPC (or LPG for 50 MW turbines).

The implementation of cogeneration turbines with one thrust bearing was facilitated by the balancing of the main part of the axial force within each individual rotor and the transfer of the remaining limited force to the bearing operating in both directions, achieved in the turbines. In cogeneration turbines, in contrast to condensing turbines, axial forces are determined not only by the steam flow rate, but also by the pressures in the steam extraction chambers. Significant changes in the efforts along the flow path take place in turbines with two heating extractions when the outside air temperature changes. Since the steam consumption remains unchanged in this case, this change in axial force can hardly be compensated for by the dummy and is completely transferred to the thrust bearing. Factory-performed study of variable turbine operation and bifurcation

practice report

6. Turbine T-50-130

Single-shaft steam turbineТ-50-130 with a rated power of 50 MW at 3000 rpm with condensation and two heating steam extractions is designed to drive a generator alternating current, type TVF 60-2 with a capacity of 50 MW with hydrogen cooling. The turbine put into operation is controlled from the control and monitoring board.

The turbine is designed to operate with live steam parameters of 130 atm, 565 C 0, measured before the check valve. The nominal temperature of the cooling water at the inlet to the condenser is 20 ° C 0.

The turbine has two heating outlets, an upper and a lower one, intended for stepwise heating of heating water in boilers. Heating of feed water is carried out sequentially in the refrigerators of the main ejector and the ejector for suction of steam from the seals with a stuffing box heater, four LPH and three HPH. LPH # 1 and # 2 are fed with steam from heating extractions, and the other five - from unregulated extractions after 9, 11, 14, 17, 19 stages.

"right"> Table

Gas turbine unit of TA type by "Rustom & Hornsby" with a capacity of 1000 kW

A gas turbine (turbine from the Latin turbo vortex, rotation) is a continuous-action heat engine, in the blade apparatus of which the energy of compressed and heated gas is converted into mechanical work on the shaft. Consists of a rotor (blades ...

Study of the heat supply system at the Ufa combined heat and power plant

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The history of the industrial steam turbine began with the invention of the milk separator by the Swedish engineer Carl - Gustav - Patrick de Laval. The designed apparatus required a drive with a large number revolutions. The inventor knew ...

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The gas turbine was an engine that combined beneficial features steam turbines (transfer of energy to the rotating shaft directly ...

Equipment design of the power unit of the Rostov NPP

Purpose The K-1000-60 / 1500-2 turbine of the KhTGZ production association is steam, condensing, four-cylinder (block diagram "HPC + three low pressure cylinders"), without controlled steam extractions ...

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The purpose of the boiler and turbine shop

NPP design with a capacity of 2000 MW

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Project of the first stage of BGRES-2 using the K-800-240-5 turbine and the PP-2650-255 boiler unit

The OK-18PU-800 (K-17-15P) drive turbine, single-cylinder, unified, condensing, with eight pressure stages, is designed to operate with a variable speed with variable initial steam parameters ...

27. Pressure at the outlet of the compressor station: 28. Gas flow through the HP turbine: 29. The work done by the gas in the HP turbine: 30. Gas temperature behind the HP turbine:, where 31. The efficiency of the HP turbine is set: 32. The degree of pressure reduction in the turbine VD: 33 ...

High pressure compressor calculation

34. Gas flow through the low-pressure turbine: We have a temperature of more than 1200K, so we choose GVoilND according to dependence 35. Gas work performed in the LP turbine: 36. The efficiency of the low-pressure turbine is set: 37. The degree of pressure reduction in the LP turbine: 38 ...

Stationary cogeneration steam turbine PT turbine -135 / 165-130 / 15 s condensing device and regulated production and two heating steam extractions with a rated power of 135 MW ...

Device and technical specifications equipment of OOO LUKOIL-Volgogradenergo Volzhskaya CHP

Single-shaft steam turbine T 100 / 120-130 with a rated power of 100 MW at 3000 rpm. With condensation and two heating steam extractions, it is intended for direct drive of an alternator ...

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Condensing turbine with controlled steam extraction for production and heating without reheating, two-cylinder, single-flow, with a capacity of 65 MW ...

Russian Federation

Standard characteristics of condensers of turbines T-50-130 TMZ, PT-60-130 / 13 and PT-80 / 100-130 / 13 LMZ

When compiling the "Normative characteristics", the following basic designations were adopted:

Steam consumption in the condenser (steam load of the condenser), t / h;

Standard steam pressure in the condenser, kgf / cm *;

Actual steam pressure in the condenser, kgf / cm;

Cooling water temperature at the condenser inlet, ° С;

Cooling water temperature at the outlet of the condenser, ° С;

Saturation temperature corresponding to the vapor pressure in the condenser, ° С;

Condenser hydraulic resistance (pressure drop of cooling water in the condenser), mm of water column;

Standard temperature head of the condenser, ° С;

Actual temperature head of the condenser, ° С;

Heating of cooling water in the condenser, ° С;

Rated design flow rate of cooling water into the condenser, m / h;

Cooling water consumption in the condenser, m / h;

Full condenser cooling surface, m;

Condenser cooling surface with built-in condenser bundle disconnected by water, m.

The regulatory characteristics include the following main dependencies:

1) the temperature head of the condenser (° C) from the steam flow rate into the condenser (steam load of the condenser) and the initial temperature of the cooling water at the nominal flow rate of the cooling water:

2) steam pressure in the condenser (kgf / cm) from the steam flow into the condenser and the initial temperature of the cooling water at the nominal flow rate of the cooling water:

3) the temperature head of the condenser (° C) from the steam flow into the condenser and the initial temperature of the cooling water at a cooling water flow rate of 0.6-0.7 nominal:

4) steam pressure in the condenser (kgf / cm) from the steam flow into the condenser and the initial temperature of the cooling water at a cooling water flow rate of 0.6-0.7 - nominal:

5) the temperature head of the condenser (° C) from the steam flow into the condenser and the initial temperature of the cooling water at the cooling water flow rate of 0.44-0.5 nominal;

6) steam pressure in the condenser (kgf / cm) from the steam flow into the condenser and the initial temperature of the cooling water at the cooling water flow rate of 0.44-0.5 nominal:

7) the hydraulic resistance of the condenser (the pressure drop of the cooling water in the condenser) from the flow rate of the cooling water when the condenser cooling surface is clean;

8) corrections to the turbine power for the deviation of the exhaust steam pressure.

Turbines T-50-130 TMZ and PT-80 / 100-130 / 13 LMZ are equipped with condensers, in which about 15% of the cooling surface can be used to heat make-up or return network water (built-in bundles). The possibility of cooling the built-in beams with circulating water is provided. Therefore, in the "Standard characteristics" for turbines of the T-50-130 TMZ and PT-80 / 100-130 / 13 LMZ types, dependencies according to clauses 1-6 are also given for capacitors with disconnected built-in beams (with a cooling surface reduced by about 15% condensers) at a cooling water flow rate of 0.6-0.7 and 0.44-0.5.

For the PT-80 / 100-130 / 13 LMZ turbine, the characteristics of the condenser with the built-in beam switched off at a cooling water flow rate of 0.78 nominal are also given.

3. OPERATING CONTROL OF THE OPERATION OF THE CONDENSING UNIT AND THE STATE OF THE CONDENSER

The main criteria for evaluating the operation of a condensing unit, characterizing the state of the equipment, at a given steam load of the condenser, are the vapor pressure in the condenser and the temperature head of the condenser corresponding to these conditions.

Operational control over the operation of the condensing unit and the condition of the condenser is carried out by comparing the actual steam pressure in the condenser measured under operating conditions with the standard steam pressure in the condenser determined for the same conditions (the same steam load of the condenser, flow rate and temperature of the cooling water) condenser head with standard.

Comparative analysis of measurement data and standard performance indicators of the unit allows you to detect changes in the operation of the condensing unit and establish their probable causes.

A feature of turbines with controlled steam extraction is their long-term operation, with low steam consumption to the condenser. In the mode with heating extractions, the control of the temperature head in the condenser does not give a reliable answer about the degree of condenser contamination. Therefore, it is advisable to monitor the operation of the condensing unit at a steam flow rate into the condenser of at least 50% and with the condensate recirculation turned off; this will increase the accuracy of determining the steam pressure and temperature difference of the condenser.

In addition to these basic values, for operational control and for analyzing the operation of the condensing unit, it is necessary to reliably determine also a number of other parameters on which the exhaust steam pressure and temperature head depend, namely: the temperature of the entering and leaving water, the steam load of the condenser, the flow rate of cooling water. and etc.

Influence of air suction in air removal devices operating within performance characteristics, on and insignificantly, while the deterioration of the air density and the increase in air suction, exceeding the operating capacity of the ejectors, have a significant effect on the operation of the condensing unit.

Therefore, control over the air density of the vacuum system of turbine plants and maintaining air suction at the level of PTE standards is one of the main tasks during operation. condensing units.

The proposed standard characteristics are constructed for the values ​​of air suction that do not exceed the PTE standards.

Below are the main parameters that need to be measured during operational monitoring of the condition of the capacitor, and some recommendations for organizing measurements and methods for determining the main controlled quantities.

3.1. Exhaust steam pressure

In order to obtain representative data on the exhaust steam pressure in the condenser under operating conditions, the measurement should be made at the points indicated in the Rating for each type of condenser.

Exhaust steam pressure should be measured with liquid mercury devices with an accuracy of at least 1 mm Hg. (single-glass cup vacuum gauges, barovakummetrichesky tubes).

When determining the pressure in the condenser, it is necessary to introduce appropriate corrections to the readings of the devices: for the temperature of the column of mercury, for the scale, for capillarity (for single-glass devices).

The pressure in the condenser (kgf / cm) when measuring vacuum is determined by the formula

Where is barometric pressure (as amended), mm Hg;

Vacuum, determined by a vacuum gauge (with corrections), mm Hg

The pressure in the condenser (kgf / cm) when measured with a vacuum tube is determined as

Where is the pressure in the condenser, determined by the device, mm Hg.

The barometric pressure must be measured with a mercury inspector barometer with the introduction of all the corrections required according to the instrument's passport. It is also allowed to use the data of the nearest meteorological station, taking into account the difference in the heights of the location of the objects.

When measuring the pressure of the exhaust steam, the laying of impulse lines and the installation of devices must be carried out in compliance with the following rules for installing devices under vacuum:

• inner diameter impulse tubes must be at least 10-12 mm;
• impulse lines must have a total slope towards the capacitor of at least 1:10;
• the tightness of the impulse lines must be checked by pressure testing with water;
• it is prohibited to apply locking devices having oil seals and threaded connections;
• measuring devices to impulse lines should be connected with thick-walled vacuum rubber.

3.2. Temperature head

Temperature head (° C) is defined as the difference between the saturation temperature of the exhaust steam and the temperature of the cooling water leaving the condenser

In this case, the saturation temperature is determined by the measured pressure of the exhaust steam in the condenser.

Control over the operation of condensing units of cogeneration turbines should be carried out in the condensation mode of the turbine with the pressure regulator turned off in the production and cogeneration extraction.

The steam load (steam flow into the condenser) is determined by the pressure in the chamber of one of the extractions, the value of which is the control value.

Steam consumption (t / h) into the condenser in condensing mode is:

Where is the consumption coefficient, numerical value which is given in the technical data of the condenser for each type of turbine;

Steam pressure in the control stage (selection chamber), kgf / cm.

If it is necessary to monitor the operation of the condenser in the cogeneration mode of the turbine, the steam consumption is determined approximately by calculation by the steam consumption in one of the intermediate stages of the turbine and the steam consumption in the cogeneration extraction and for the regenerative low-pressure heaters.

For the T-50-130 TMZ turbine, the steam consumption (t / h) into the condenser in the heating mode is:

• with one-stage heating of heating water

• with two-stage heating of heating water

Where and - steam consumption, respectively, through the 23rd (with one-stage) and 21st (with two-stage heating of the heating system) stages, t / h;

Network water consumption, m / h;

; - heating of network water, respectively, in horizontal and vertical network heaters, ° С; is defined as the temperature difference of the heating water after and before the corresponding heater.

The steam flow through the 23rd stage is determined according to Fig. I-15, b, depending on the flow of live steam to the turbine and the steam pressure in the lower heating extraction.

The steam flow through the 21st stage is determined according to Fig. I-15, a, depending on the flow of live steam to the turbine and the steam pressure in the upper heating extraction.

For turbines of the PT type, the steam consumption (t / h) into the condenser in the heating mode is:

• for turbines PT-60-130 / 13 LMZ

• for turbines PT-80 / 100-130 / 13 LMZ

Where is the steam consumption at the outlet of the CSD, t / h. Determined according to Fig. II-9 depending on the steam pressure in the cogeneration bleed and in the V bleed (for turbines PT-60-130 / 13) and according to Fig. III-17 depending on the steam pressure in the cogeneration bleed and in the IV bleed ( for turbines PT-80 / 100-130 / 13);

Water heating in network heaters, ° С. It is determined by the difference in temperature of the supply water after and before the heaters.

The pressure taken as the reference pressure must be measured with spring-loaded instruments of accuracy class 0.6, periodically and carefully checked. To determine the true value of the pressure in the control stages, it is necessary to enter the appropriate corrections to the readings of the device (for the height of installation of the devices, correction according to the passport, etc.).

The flow rates of live steam for the turbine and network water required to determine the flow rate of steam into the condenser are measured by standard flow meters with the introduction of corrections for the deviation of the operating parameters of the medium from the calculated ones.

The temperature of the network water is measured by mercury laboratory thermometers with a graduation value of 0.1 ° C.

3.4. Cooling water temperature

The temperature of the cooling water entering the condenser is measured at one point on each pressure line. The condenser leaving water temperature must be measured at least three points in one cross section each drain conduit at a distance of 5-6 m from the outlet flange of the condenser and be determined as the average according to the thermometer readings at all points.

The temperature of the cooling water should be measured with mercury laboratory thermometers with a graduation of 0.1 ° C, installed in thermometric wells with a length of at least 300 mm.

3.5. Hydraulic resistance

The control over the contamination of the tube plates and condenser tubes is carried out by the hydraulic resistance of the condenser through the cooling water, for which the pressure difference between the discharge and drain pipes of the condensers is measured with a mercury two-glass U-shaped differential pressure gauge, installed at a mark below the pressure measurement points. The impulse lines from the discharge and drain connections of the condensers must be filled with water.

The hydraulic resistance (mm of water column) of the condenser is determined by the formula

Where is the difference measured by the device (corrected for the temperature of the column of mercury), mm Hg.

When measuring the hydraulic resistance, the flow rate of cooling water into the condenser is simultaneously determined for the possibility of comparison with the hydraulic resistance according to the Standard Specifications.

3.6. Cooling water consumption

The flow rate of cooling water to the condenser is determined by the thermal balance of the condenser or by direct measurement with segmental diaphragms installed on the pressure supply lines. Cooling water flow rate (m / h) based on the thermal balance of the condenser is determined by the formula

Where is the difference between the heat content of the exhaust steam and condensate, kcal / kg;

Heat capacity of cooling water, kcal / kg · ° С, equal to 1;

Density of water, kg / m, equal to 1.

When compiling the Standard characteristics, it was taken equal to 535 or 550 kcal / kg, depending on the operating mode of the turbine.

3.7. Air density of the vacuum system

The air density of the vacuum system is controlled by the amount of air at the exhaust of the steam jet ejector.

4. ESTIMATION OF REDUCTION OF POWER OF THE TURBO UNIT DURING OPERATION WITH REDUCED COMPARED TO REGULATORY VACUUM

The deviation of the pressure in the steam turbine condenser from the normative one leads, at a given heat consumption to the turbine unit, to a decrease in the power developed by the turbine.

The change in power when the absolute pressure in the turbine condenser differs from its standard value is determined from the experimentally obtained correction curves. The correction graphs included in this Capacitor Ratings show the change in wattage for different meanings steam flow rate in the LPH turbine. For this mode of the turbine unit, the value of the change in power is determined and according to the corresponding curve is removed when the pressure in the condenser changes from to.

This value of the change in power and serves as the basis for determining the excess specific consumption heat or specific fuel consumption set at a given load for the turbine.

For turbines T-50-130 TMZ, PT-60-130 / 13 and PT-80 / 100-130 / 13 LMZ, the steam consumption in the LMP to determine the underdevelopment of the turbine power due to an increase in the pressure in the condenser can be taken equal to the steam consumption in capacitor.

I. NORMATIVE CHARACTERISTICS OF THE K2-3000-2 CONDENSER OF THE T-50-130 TMZ TURBINE

1. Technical data of the condenser

Cooling surface area:

without built-in beam
Tube diameter:
outer
interior
Number of tubes
Number of strokes water
Number of threads
Air removal device - two steam jet ejectors EP-3-2

• in condensing mode - according to the steam pressure in the IV extraction:

2.3. The difference in the heat content of the exhaust steam and condensate () is taken:

Figure I-1. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

7000 m / h; = 3000 m

Figure I-2. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

5000 m / h; = 3000 m

Figure I-3. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

3500 m / h; = 3000 m

Figure I-4. Absolute pressure versus steam flow into the condenser and cooling water temperature:

7000 m / h; = 3000 m

Figure I-5. Dependence of the absolute pressure on the steam flow into the condenser and the temperature of the cooling water:

5000 m / h; = 3000 m

Figure I-6. Absolute pressure versus steam flow into the condenser and cooling water temperature:

3500 m / h; = 3000 m

Figure I-7. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

7000 m / h; = 2555 m

Figure I-8. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

5000 m / h; = 2555 m

Figure I-9. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

3500 m / h; = 2555 m

Figure I-10. Absolute pressure versus steam flow into the condenser and cooling water temperature:

7000 m / h; = 2555 m

Figure I-11. Absolute pressure versus steam flow into the condenser and cooling water temperature:

5000 m / h; = 2555 m

Figure I-12. Absolute pressure versus steam flow into the condenser and cooling water temperature:

3500 m / h; = 2555 m

Figure I-13. The dependence of the hydraulic resistance on the flow rate of cooling water into the condenser:

1 - full surface of the capacitor; 2 - with the built-in beam turned off

Figure I-14. Correction to the power of the turbine T-50-130 TMZ for the deviation of the steam pressure in the condenser (according to the "Typical energy characteristics of the turbine unit T-50-130 TMZ". Moscow: SPO Soyuztekhenergo, 1979)

Fig. L-15. Dependence of steam flow through the T-50-130 TMZ turbine on live steam flow and pressure in the upper heating outlet (with two-stage heating of heating water) and pressure in the lower heating outlet (with single-stage heating of heating water):

a - steam consumption through the 21st stage; b - steam consumption through the 23rd stage

II. NORMATIVE CHARACTERISTIC OF THE CAPACITOR 60KTSS OF THE TURBINE PT-60-130 / 13 LMZ

1. Technical data

Total cooling surface area
Rated steam flow to the condenser
Estimated amount of cooling water
Active length of condenser tubes Tube diameter:
outer
interior
Number of tubes
Number of water strokes
Number of threads

Air removal device - two steam jet ejectors EP-3-700

2. Guidelines for determining some parameters of the condensing unit

2.1. The exhaust steam pressure in the condenser is determined as an average value over two measurements.

The location of the points for measuring the vapor pressure in the neck of the condenser is shown in the diagram. The pressure measuring points are located in a horizontal plane, passing 1 m above the plane of the condenser connection with the adapter pipe.

2.2. Determine the steam consumption in the condenser:

• in the condensation mode - according to the vapor pressure in the V extraction;

• in heating mode - in accordance with the instructions in Section 3.

2.3. The difference between the heat content of the exhaust steam and condensate () is taken:

• for condensation mode 535 kcal / kg;
• for the heating regime 550 kcal / kg.

Figure II-1. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

Figure II-2. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

Figure II-3. Dependence of the temperature head on the steam flow into the condenser and the temperature of the cooling water:

Figure II-4. Absolute pressure versus steam flow into the condenser and cooling water temperature:

Figure II-5. Dependence of the absolute pressure on the steam flow into the condenser and the temperature of the cooling water:

Figure II-6. Dependence of the absolute pressure on the steam flow into the condenser and the temperature of the cooling water.

Ministry of General and Vocational Education

Russian Federation

Novosibirsk State Technical University

Department of Thermal and Power Plants

COURSE PROJECT

on the topic: Calculation of the thermal scheme of a power unit based on a heating turbine T - 50/60 - 130.

Faculty: FEN

Group: ET Z - 91u

Completed:

Student - Schmidt A.I.

Checked:

Teacher - Borodikhin I.V.

Protection mark:

Novosibirsk city

2003 year

Introduction ……………………………………………………………………… .... 2

1. Construction of graphs of thermal loads …………………………………… .2

2. Determination of the parameters of the design block diagram …………………………… 3

3. Determination of the parameters of the drains of the heaters of the regeneration system and the parameters of steam in the extraction ……………………………………………………… ..5

4. Determination of steam consumption …………………………………………………… 7

5. Determination of steam consumption of unregulated extractions ……………………… 8

6. Determination of underproduction rates ……………………………… ... 11

7. Actual steam consumption for the turbine …………………………………… ... 11

8. Selection of the steam generator ……………………………… ... ……………………… ..12

9. Electricity consumption for own needs ……………………………… .12

10. Determination of technical and economic indicators ………………………… ..14

Conclusion ………………………………………………………………………… .15

Used literature ……………………………………………………… 15

Appendix: Fig. 1 - Heat load graph

fig. 2 - Thermal circuit block

P, S - Diagram of water and steam

Introduction.

This paper presents the calculation of the body scheme of the power unit (based on the heating turbine T - 50/60 - 130 TMZ and the boiler unit E - 420 - 140 TM

(TP - 81), which can be located at the TPP in the city of Irkutsk. Design a thermal power plant in Novosibirsk. The main fuel is Nazarovskiy brown coal. Turbine power 50 MW, initial pressure 13 MPa and superheated steam temperature 565 C 0, without reheating t P.V. = 230 С 0, Р К = 5 KPa, and tzh = 0.6. Binding to this city, located in the Siberian region, determines the choice of fuel from the nearest coal basin (Nazarovo coal basin), as well as the choice of the estimated ambient temperature.

The basic thermal diagram indicating the parameters of steam and water and the values ​​of energy indicators obtained as a result of its calculation determine the level of technical perfection of the power unit and power plants, as well as, to a large extent, their economic indicators. PTS is the main technological scheme of the projected power plant, which allows for the given energy loads to determine the consumption of steam and water in all parts of the installation, its energy indicators. On the basis of the PTS, technical characteristics are determined and thermal equipment is selected, a detailed (detailed) thermal diagram of power units and the power plant as a whole is developed.

In the course of the work, the graphs of heat loads are plotted, the process is plotted in the hS-diagram, the network heaters and the regeneration system are calculated, as well as the main technical and economic indicators are calculated.

1. Construction of graphs of thermal loads.

Heat load graphs are presented in the form of nomograms (Fig. 1):

a. the graph of the change in the heat load, the dependence of the heat load of the turbine Q T, MW on the ambient temperature t vz, C 0;

b. temperature graph of high-quality regulation of electricity supply - the dependence of the temperatures of the direct and return network water t ps, t oss, C 0 on t bz, C 0;

c. annual heat load schedule - dependence of the turbine heat load Q t, MW on the number of operating hours during the heating period t, h / year;

d. the graph of the duration of the air temperature standing t vz, C 0 in the annual context.

The maximum thermal power of 1 unit, which is provided by "T" by the extraction of the turbine, MW, according to the turbine passport is 80 MW. Maximum thermal power of the unit, which is also provided by the peak hot water boiler, MW

, (1.1)

Where a CHP is the coefficient of district heating, a CHP = 0.6

MW

Heat load (power) of hot water supply, MW, is estimated by the formula:

MW

The most typical temperatures for the graph of changes in heat load (Fig. 1a) and the temperature graph of quality control:

t vz = + 8C 0 - air temperature corresponding to the beginning and end of the heating season:

t = + 18C 0 - design temperature at which a state of thermal equilibrium occurs.

t vz = -40C 0 - design air temperature for Krasnoyarsk.

In the graphs shown in Fig. 1d and 1c, the heating period t does not exceed 5500 h / year.

bar. The pressure drop in the T-selection is equal to: bar, after the pressure drop is equal to: P T1 = 2.99 bar is equal to C 0, underheating dt = 5C 0. The maximum possible heating water temperature С 0

Cogeneration steam turbine T-50 / 60-130 is designed to drive an electric generator and has two heating extractions for supplying heat for heating. Like other turbines with a capacity of 30-60 MW, it is intended for installation at thermal power plants in medium and small towns. The pressure in both the heating and industrial extraction is maintained by rotary control diaphragms installed in the LPC.

The turbine is designed to operate at the following ratings:

· Superheated steam pressure - 3.41 MPa;

Superheated steam temperature - 396 ° С;

· Rated power of the turbine - 50 MW.

Subsequence technological process the working fluid is as follows: steam generated in the boiler is directed through steam lines to the high-pressure cylinder of the turbine, having worked at all stages of the HPC, it enters the LPC and then enters the condenser. In the condenser, the exhaust steam is condensed due to the heat given to the cooling water, which has its own circulation circuit (circulating water), then, with the help of condensate pumps, the main condensate is sent to the regeneration system. This system includes 4 HDPE, 3 LDPE and a deaerator. The regeneration system is designed to heat the feed water at the boiler inlet to a certain temperature. This temperature has a fixed value and is indicated in the turbine passport.

The schematic thermal diagram is one of the main schemes of the power plant. Such a diagram gives an idea of ​​the type of power plant and the principle of its operation, revealing the essence of the technological process of power generation, and also characterizes the technical equipment and thermal efficiency of the plant. It is necessary for calculating the heat and energy balances of the installation.

This diagram shows 7 extractions, two of which are also cogeneration ones, i.e. are intended for heating of heating water. Drains from the heaters are discharged either to the previous heater, or by means of drain pumps to the mixing point. After the main condensate has passed 4 LPH, it enters the deaerator. The main value of which is not to heat the water, but to purify it from oxygen, which causes corrosion of pipeline metals, screen tubes, pipes of superheaters and other equipment.

Basic elements and legend:

K- (capacitor)

KU - boiler plant

HPC - high pressure cylinder

LPC - low pressure cylinder

EG - electric generator

OE - ejector cooler

PS - network heater

PVK - peak hot water boiler

TP - heat consumer

KN - condensate pump

DN - drainage pump

PN - feed pump

HDPE - high pressure heater

LDPE - low pressure heater

D - deaerator

Scheme. 1 Thermal diagram of the turbine T50 / 60-130

Table 1.1. Nominal values ​​of the main parameters of the turbine

Table 1.2. Steam parameters in the extraction chamber

Heater	Steam parameters in the extraction chamber	The amount of extracted steam, kgf / s
Pressure, MPa	Temperature, ° С
PVD7	3,41		3,02
PVD6	2,177		4,11
PVD5	1,28		1,69
Deaerator	1,28		1,16
PND4	0,529		2,3
PNDZ	0,272		2,97
PND2	0,0981	-	0,97
PND1	0,04	-	0,055