Russian FederationRD
Regulatory characteristics of turbine condensers T-50-130 TMZ, PT-60-130/13 and PT-80/100-130/13 LMZ
When compiling the "Regulatory Characteristics", the following main designations were adopted:
Steam consumption in the condenser (steam load of the condenser), t/h;
Standard steam pressure in the condenser, kgf/cm*;
Actual vapor pressure in the condenser, kgf/cm;
Cooling water temperature at the condenser inlet, °С;
Cooling water temperature at the condenser outlet, °С;
Saturation temperature corresponding to the vapor pressure in the condenser, °С;
Hydraulic resistance of the condenser (pressure drop of the cooling water in the condenser), mm water column;
Normative temperature head of the condenser, °С;
Actual temperature difference of the condenser, °С;
Heating of cooling water in the condenser, °С;
Rated design flow of cooling water to the condenser, m/h;
Consumption of cooling water in the condenser, m/h;
Total condenser cooling surface, m;
Condenser cooling surface with the built-in condenser bundle disconnected from the water, m
Regulatory characteristics include the following main dependencies:
1) temperature difference of the condenser (°C) from the steam flow into the condenser (condenser steam load) and the initial temperature of the cooling water at the nominal flow rate of the cooling water:
2) vapor 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) temperature difference 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 3) 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) temperature difference 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 0.44-0.5 nominal;
6) vapor 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 0.44-0.5 nominal:
7) hydraulic resistance of the condenser (cooling water pressure drop in the condenser) from the cooling water flow rate with an operationally clean condenser cooling surface;
8) corrections to the power of the turbine for the deviation of the pressure of the exhaust steam.
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 "Regulatory characteristics" for turbines of the T-50-130 TMZ and PT-80 / 100-130 / 13 LMZ type, the dependencies according to paragraphs 1-6 are also given for condensers with disabled built-in bundles (with a cooling surface reduced by about 15% condensers) at cooling water flow rates 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 turned off at a cooling water flow rate of 0.78 nominal are also given.
3. OPERATIONAL CONTROL OVER THE OPERATION OF THE CONDENSING UNIT AND THE CONDITION OF THE CONDENSER
The main criteria for evaluating the operation of a condensing unit, which characterize the state of the equipment, for a given condenser steam load, are the vapor pressure in the condenser and the temperature difference of the condenser that meets these conditions.
Operational control over the operation of the condensing unit and the state 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), as well as comparing the actual temperature head of the condenser with standard.
Comparative analysis of measurement data and normative indicators of the plant operation allows detecting changes in the operation of the condensing unit and establishing the probable causes of them.
A feature of turbines with controlled steam extraction is their long-term operation, with low steam flow rates to the condenser. In the mode with heat extractions, monitoring the temperature difference in the condenser does not give a reliable answer about the degree of contamination of the condenser. Therefore, it is advisable to monitor the operation of the condensing unit with steam flow rates to the condenser of at least 50% and with the condensate recirculation turned off; this will increase the accuracy of determining the vapor pressure and temperature difference of the condenser.
In addition to these basic quantities, for operational control and for analyzing the operation of a condensing unit, it is also necessary to reliably determine a number of other parameters that affect the exhaust steam pressure and temperature difference, namely: the temperature of the inlet and outlet water, the steam load of the condenser, the flow rate of the cooling water and etc.
The influence of air suction in air-removing devices operating within the operating characteristics is on and insignificant, while the deterioration of air density and the increase in air suction, exceeding the operating performance of the ejectors, have a significant impact on the operation of the condensing unit.
Therefore, air density control vacuum system turbine plants and maintaining air suction at the level of PTE standards is one of the main tasks in the operation condensing units.
The proposed Normative characteristics are built for air suction values that do not exceed the norms of PTE.
Below are the main parameters that must be measured during the operational control of the state of the capacitor, and some recommendations for organizing measurements and methods for determining the main controlled quantities.
3.1. Exhaust steam pressure
To obtain representative data on the pressure of the exhaust steam in the condenser under operating conditions, the measurement should be made at the points specified in the Standard characteristics for each type of condenser.
The pressure of the exhaust steam must be measured by liquid mercury instruments with an accuracy of at least 1 mm Hg. (single-glass cup vacuum gauges, barovacuummetric tubes).
When determining the pressure in the condenser, it is necessary to introduce appropriate corrections to the instrument readings: for the temperature of the mercury column, for the scale, for capillarity (for single-glass instruments).
The pressure in the condenser (kgf / cm) when measuring vacuum is determined by the formula
Where - barometric pressure (as amended), mm Hg;
Depression determined by a vacuum gauge (with amendments), mm Hg.
The pressure in the condenser (kgf/cm) when measured with a barvacuum tube is defined as
Where is the pressure in the condenser, determined by the device, mm Hg.
Barometric pressure must be measured with a mercury inspector's barometer with the introduction of all the necessary amendments according to the instrument's passport. It is also allowed to use the data of the nearest weather station, taking into account the difference in the heights of the objects.
When measuring the exhaust steam pressure, 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:
- the inner diameter of the impulse tubes must be at least 10-12 mm;
- impulse lines must have a general slope towards the condenser of at least 1:10;
- the tightness of the impulse lines must be checked by pressure testing with water;
- it is forbidden to use locking devices with glands and threaded connections;
- measuring devices must be connected to the impulse lines using thick-walled vacuum rubber.
3.2. temperature difference
The temperature difference (°C) is defined as the difference between the saturation temperature of the exhaust steam and the temperature of the cooling water at the condenser outlet
In this case, the saturation temperature is determined from the measured exhaust steam pressure in the condenser.
Control over the operation of condensing units of heating turbines should be carried out in the condensing mode of the turbine with the pressure regulator turned off in the production and heating extractions.
Steam load (steam flow to the condenser) is determined by the pressure in the chamber of one of the selections, the value of which is a control one.
The steam flow rate (t/h) to the condenser in the condensing mode is:
Where is the cost factor, 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 heating mode of the turbine, the steam flow rate is determined approximately by calculation from the steam flow rates to one of the intermediate stages of the turbine and the steam flow rates to the heat extraction and to low-pressure regenerative heaters.
For the T-50-130 TMZ turbine, the steam flow rate (t/h) to the condenser in the heating mode is:
- with single-stage heating of network water
- with two-stage heating of network water
Where and - steam flow rates, respectively, through the 23rd (with a single-stage) and 21st (with a two-stage heating of network water) 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 between the network 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 fresh steam flow 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 fresh steam flow to the turbine and the steam pressure in the upper heating extraction.
For turbines of the PT type, the steam flow rate (t/h) to 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. It is determined according to Fig. II-9 depending on the steam pressure in the heating extraction and in the V selection (for turbines PT-60-130 / 13) and according to Fig. III-17 depending on the steam pressure in the heating extraction and in the IV selection ( for turbines PT-80/100-130/13);
Water heating in network heaters, °С. It is determined by the temperature difference of the network water after and before the heaters.
The pressure taken as the control pressure must be measured with spring instruments of accuracy class 0.6, periodically and carefully checked. For determining true value pressure in the control stages to the readings of the device, it is necessary to introduce appropriate corrections (for the height of the installation of devices, amendment according to the passport, etc.).
The flow rates of live steam to the turbine and heating water required to determine the flow rate of steam to the condenser are measured by standard flow meters with the introduction of corrections for the deviation of the working parameters of the medium from the calculated ones.
The temperature of the network water is measured by mercury laboratory thermometers with a division value of 0.1 °C.
3.4. Cooling water temperature
The temperature of the cooling water at the condenser inlet is measured at one point on each penstock. The water temperature at the outlet of the condenser should be measured at least at three points in one cross-section of each drain conduit at a distance of 5-6 m from the outlet flange of the condenser and be determined as an average according to thermometer readings at all points.
The temperature of the cooling water must be measured with mercury laboratory thermometers with a division value of 0.1 °C, installed in thermometric sleeves with a length of at least 300 mm.
3.5. Hydraulic resistance
Control over contamination of tube sheets and tubes of the condenser is carried out by the hydraulic resistance of the condenser to the cooling water, for which the pressure drop between the pressure and drain pipes of the condensers is measured with a mercury double-glass U-shaped differential pressure gauge installed at a mark below the pressure measurement points. Impulse lines from pressure and drain pipes 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 (adjusted for the temperature of the mercury column), mm Hg.
When measuring the hydraulic resistance, the flow rate of the cooling water to the condenser is simultaneously determined for the possibility of comparison with the hydraulic resistance according to the Normative characteristics.
3.6. Cooling water consumption
The flow rate of cooling water to the condenser is determined by heat balance condenser or by direct measurement with segment diaphragms installed on pressure supply conduits. Cooling water consumption (m/h) according to the heat balance of the condenser is determined by the formula
Where is the difference in the heat content of the exhaust steam and condensate, kcal / kg;
Heat capacity of cooling water, kcal/kg °C, equal to 1;
Density of water, kg/m, equal to 1.
When compiling the Normative characteristics, it was taken equal to 535 or 550 kcal/kg, depending on the turbine operation mode.
3.7. Air density 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. EVALUATION OF THE POWER REDUCTION OF A TURBO PLANT DURING OPERATION WITH A VACUUM REDUCED IN COMPARED WITH THE RATED VACUUM
The deviation of the pressure in the condenser of the steam turbine from the norm leads to a decrease in the power developed by the turbine at a given heat consumption for the turbine plant.
The change in power when the absolute pressure in the turbine condenser differs from its standard value is determined from the correction curves obtained experimentally. The correction graphs included in this Capacitor Specifications show the change in power for different meanings steam flow rate in the turbine LPR. For this mode of the turbine unit, the value of the change in power is determined and taken from the corresponding curve when the pressure in the condenser changes from to .
This value of the power change serves as the basis for determining the excess of the specific heat consumption or specific fuel consumption established at a given load for the turbine.
For the T-50-130 TMZ, PT-60-130/13 and PT-80/100-130/13 LMZ turbines, the steam flow rate in the LPR to determine the underproduction of turbine power due to pressure increase in the condenser can be taken equal to the steam flow rate in capacitor.
I. NORMATIVE CHARACTERISTICS OF THE K2-3000-2 CONDENSER OF THE T-50-130 TMZ TURBINE
1. Capacitor technical data
Cooling surface area:
without built-in beam | |
Tube diameter: | |
outer | |
interior | |
Number of tubes | |
Number of water strokes | |
Number of threads | |
Air removal device - two steam jet ejectors EP-3-2 |
- in the condensing mode - according to the vapor pressure in the IV selection:
2.3. The difference between the heat content of the exhaust steam and condensate () is taken:
Fig.I-1. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
7000 m/h; =3000 m
Fig.I-2. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
5000 m/h; =3000 m
Fig.I-3. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
3500 m/h; =3000 m
Fig.I-4. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
7000 m/h; =3000 m
Fig.I-5. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
5000 m/h; =3000 m
Fig. I-6. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
3500 m/h; =3000 m
Fig.I-7. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
7000 m/h; =2555 m
Fig. I-8. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
5000 m/h; =2555 m
Fig.I-9. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
3500 m/h; =2555 m
Fig. I-10. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
7000 m/h; =2555 m
Fig. I-11. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
5000 m/h; =2555 m
Fig. I-12. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
3500 m/h; =2555 m
Fig. I-13. Dependence of hydraulic resistance on the flow rate of cooling water to the condenser:
1 - full surface condenser; 2 - with disabled built-in beam
Fig. I-14. Correction to the power of the T-50-130 TMZ turbine for the deviation of the steam pressure in the condenser (according to the "Typical energy characteristics of the turbine unit T-50-130 TMZ" . M .: SPO Soyuztekhenergo, 1979)
Fig.l-15. Dependence of the steam flow rate through the T-50-130 TMZ turbine on the flow rate of live steam and the pressure in the upper heating extraction (with two-stage heating of heating water) and the pressure in the lower heating extraction (with one-stage heating of heating water):
a - steam consumption through the 21st stage; b - steam consumption through the 23rd stage
II. NORMATIVE CHARACTERISTICS OF THE 60KTSS TURBINE PT-60-130/13 LMZ CONDENSER
1. Technical data
Total cooling surface area | |
Nominal 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 the average of two measurements.
The location of the steam pressure measurement points in the condenser neck is shown in the diagram. The pressure measuring points are located in horizontal plane, passing 1 m above the plane of connection of the condenser with the transition pipe.
2.2. Determine the steam flow in the condenser:
- in the condensing mode - according to the vapor pressure in the V selection;
- in heating mode - in accordance with the instructions of 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 heating mode 550 kcal/kg.
Fig.II-1. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
Fig.II-2. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
Fig.II-3. The dependence of the temperature difference on the steam flow to the condenser and the temperature of the cooling water:
Fig.II-4. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
Fig.II-5. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature:
Fig.II-6. Dependence of absolute pressure on steam flow to the condenser and cooling water temperature.
T-50-130 TMZ
TYPICAL
ENERGY CHARACTERISTICS
TURBO UNIT
T-50-130 TMZ
SOYUZTEKHENERGO SERVICE OF BEST EXPERIENCE AND INFORMATION
MOSCOW 1979
MAIN FACTORY DATA OF THE TURBO UNIT
(TU 24-2-319-71)
* Taking into account the heat of the steam entering the condenser.
Comparison of the results of typical characteristic data with TMZ warranty data
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Index |
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Heat given to the consumer Q t, Gcal/h |
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Turbine operating mode |
Condensing |
single stage |
two stage |
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TMZ data |
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Fresh steam temperature tо, °С |
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Generator efficiency h, % |
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The temperature of the cooling water at the inlet to the condenser t in 1, ° С |
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Cooling water consumption W, m 3 / h |
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Specific steam consumption d, kg/(kWh) |
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Typical characteristic data |
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Fresh steam pressure P o, kgf / cm 2 |
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Live steam temperature t o , °С |
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Pressure in the controlled selection P, kgf / cm 2 |
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Generator efficiency h, % |
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Temperature feed water for HPH No. 7 t p.v, °С |
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Temperature of network water at the inlet to the PSG heater t 2 , °С |
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Exhaust steam pressure Р 2, kgf / cm 2 |
t in 1 \u003d 20 ° С, W \u003d 7000 m 3 / h |
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Specific steam consumption d e, kg/(kWh) |
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Correction to the specific steam consumption for the deviation of the conditions of the typical characteristic from the warranty |
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on the deviation of the pressure of the exhaust steam Dd e, kg / (kWh) |
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for feed water temperature deviation Dd e, kg/(kWh) |
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on the temperature deviation of the return network water Dd e, kg / (kWh) |
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Total correction to the specific steam consumption Dd e, kg/(kWh) |
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Specific steam consumption under warranty conditions d n e, kg/(kWh) |
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Deviation of the specific steam consumption from the warranty ad e, % |
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Average deviation ad e, % |
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* Extraction pressure regulator off. |
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THERMAL SCHEME OF A TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM DISTRIBUTION DIAGRAM |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM PRESSURE IN THE SAMPLING CHAMBER UNDER THE CONDENSATION MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM PRESSURE IN SAMPLING CHAMBERS UNDER HEATING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM PRESSURE IN SAMPLING CHAMBERS UNDER HEATING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT TEMPERATURE AND ENTHALPY OF FEED WATER AFTER HIGH PRESSURE HEATERS |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CONDENSATE TEMPERATURE FOR HDPE No. 4 WITH TWO- AND THREE-STAGE MAINS WATER HEATING |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION FOR HIGH PRESSURE HEATER AND DEAERATOR |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION FOR LOW PRESSURE HEATER No. 4 |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION FOR LOW PRESSURE HEATER No. 3 |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM LEAKAGE THROUGH THE FIRST COMPARTMENTS OF SHAFT SEALS HPC, LPC, STEAM SUPPLY TO END SEALS |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM EXTRACTS FROM SEALS IN I, IV OUTLETS, INTO TUBE HEATER AND COOLER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION THROUGH STAGE 21 WITH TWO-STAGE MAINS WATER HEATING |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION THROUGH STAGE 23 WITH SINGLE-STAGE MAINS WATER HEATING |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION IN LPH IN CONDENSING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION IN LPH THROUGH A CLOSED DIAPHRAGM |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT INTERNAL CAPACITY OF COMPARTMENTS 1 - 21 |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT INTERNAL POWER OF COMPARTMENTS 1 - 23 WITH SINGLE-STAGE MAINS WATER HEATING |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT INTERMEDIATE COMPARTMENT POWER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT SPECIFIC POWER GENERATION ON HEAT CONSUMPTION |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT TOTAL LOSSES OF TURBINE AND GENERATOR |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT FRESH STEAM AND HEAT CONSUMPTION IN CONDENSING MODE WITH PRESSURE REGULATOR OFF |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS. TURBO UNIT SPECIFIC GROSS HEAT CONSUMPTION FOR SINGLE-STAGE HEATING OF WATER NETWORKS |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT SPECIFIC GROSS HEAT CONSUMPTION FOR TWO-STAGE MAINS WATER HEATING |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT SPECIFIC GROSS HEAT CONSUMPTION FOR TWO-STAGE MAINS WATER HEATING |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT SPECIFIC HEAT CONSUMPTION FOR THREE-STAGE MAINS WATER HEATING AND ELECTROMECHANICAL EFFICIENCY OF THE TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT TEMPERATURE DIFFERENT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT RELATIVE UNDERHEATING OF MAINS WATER IN PSG AND PSV |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM ENTHALPY IN THE CHAMBER OF THE UPPER HEAT EXHAUST |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT USED HEAT DROP OF INTERMEDIATE COMPARTMENT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT HEAT USE IN THE NETWORK WATER HEATER (PSV) |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CHARACTERISTICS OF THE K2-3000-2 CAPACITOR |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH SINGLE-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH SINGLE-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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Given: Q t \u003d 60 Gcal / h; N t = 34 MW; P tn \u003d 1.0 kgf / cm 2.
Determine: D about t / h.
Definition. On the diagram we find given point A (Q t \u003d 60 Gcal / h; N t \u003d 34 MW). From point A parallel to the inclined straight line we go to the line set pressure(P tn \u003d 1.0 kgf / cm 2). From the obtained point B in a straight line we go to the line of the given pressure (P tn \u003d 1.0 kgf / cm 2) of the right quadrant. From the obtained point B we lower the perpendicular to the axis of costs. Point G corresponds to the determined consumption of live steam.
Given: Q t \u003d 75 Gcal / h; P tn \u003d 0.5 kgf / cm 2.
Determine: N t MW; D about t/h.
Definition. On the diagram we find the given point D (Q t \u003d 75 Gcal / h; P tn \u003d 0.5 kgf / cm 2). From point D in a straight line we go to the power axis. Point E corresponds to the determined power. Then we go in a straight line to the line P tn \u003d 0.5 kgf / cm 2 of the right quadrant. From the point W we lower the perpendicular to the axis of costs. The obtained point Z corresponds to the determined consumption of fresh steam.
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES WITH TWO-STAGE HEATING OF MAINS WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
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Given: Q T= 81 Gcal/h; N t = 57.2 MW; P TV\u003d 1.4 kgf / cm 2. Define: D0 t/h Definition. On the diagram we find the given point A ( Q t = 81 Gcal/h; N t = 57.2 MW). From point A parallel to the inclined straight line we go to the line of the given pressure ( P TV\u003d 1.4 kgf / cm 2). From the received point B in a straight line we go to the line of the given pressure ( P T in\u003d 1.4 kgf / cm 2) of the left quadrant. From the obtained point B we lower the perpendicular to the axis of costs. Point G corresponds to the determined consumption of live steam. |
Given: Q T= 73 Gcal/h; P T in\u003d 0.8 kgf / cm 2. Determine: N t MW; D 0 t/h Definition. Finding a given point D (Q T= 73 Gcal/h; P T in = 0.8 kgf / cm 2) From point D in a straight line we go to the power axis. Point E corresponds to the determined power. Further in a straight line we go to the line P T in = 0.8 kgf / cm 2 of the left quadrant. From the obtained point W we lower the perpendicular to the axis of costs. The obtained point Z corresponds to the determined consumption of fresh steam. |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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b) On the deviation of the pressure of live steam from the nominal V)
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CORRECTIONS FOR FRESH STEAM FLOW UNDER CONDENSING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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a) On the deviation of the temperature of live steam from the nominal b) On the deviation of the pressure of live steam from the nominal V) On the deviation of the feed water flow from the nominal
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CORRECTIONS TO SPECIFIC HEAT CONSUMPTION UNDER CONDENSING MODE |
Type T-50-130 TMZ |
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d) For undercooling of feed water in heaters high pressure e) To change the heating of water in the feed pump f) To turn off a group of high-pressure heaters
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CORRECTION TO THE POWER FOR THE PRESSURE OF THE EXHAUST STEAM IN THE CONDENSER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CORRECTIONS TO THE POWER WHEN WORKING WITH HEATING OUTPUTS |
Type T-50-130 TMZ |
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Given: Q t \u003d 81 Gcal / h; N t = 57.2 MW; R TV \u003d 1.4 kgf / cm 2.
Determine: D about t / h.
Definition. On the diagram we find the given point A (Q t \u003d 81 Gcal / h; N t \u003d 57.2 MW). From point A, parallel to the inclined straight line, we go to the line of a given pressure (P TV \u003d 1.4 kgf / cm 2). From the point B obtained, we go in a straight line to the line of the given pressure (P tv \u003d 1.4 kgf / cm 2) of the left quadrant. From the obtained point B we lower the perpendicular to the axis of costs. Point G corresponds to the determined consumption of live steam.
Given: Q t \u003d 73 Gcal / h; R TV \u003d 0.8 kgf / cm 2.
Determine: N t MW; D about t/h.
Definition. We find the given point D (Q t \u003d 73 Gcal / h; P TV \u003d 0.8 kgf / cm 2). From point D in a straight line we go to the power axis. Point E corresponds to the determined power. Then we go in a straight line to the line P tv \u003d 0.8 kgf / cm 2 of the left quadrant. From the obtained point W we lower the perpendicular to the axis of costs. The obtained point Z corresponds to the determined consumption of fresh steam.
APPLICATION
1. The typical energy characteristic of the turbine unit T-50-130 TMZ was compiled on the basis of thermal tests of two turbines (carried out by Yuzhtekhenergo at the Leningradskaya CHPP-14 and Sibtechenergo at the Ust-Kamenogorsk CHPP) and reflects the average efficiency of the turbine unit that has been overhauled and operates according to the factory design thermal scheme (chart T-1) and under the following conditions, taken as nominal:
Pressure and temperature of fresh steam in front of the turbine stop valves - respectively - 130 kgf / cm 2 * and 555 ° C;
* Absolute pressures are given in the text and graphs.
The maximum allowable consumption of live steam is 265 t/h;
The maximum allowable steam flow rates through the switchable compartment and low pressure pump are 165 and 140 t/h, respectively; limit values of steam flow rates through certain compartments comply with the specifications of TU 24-2-319-71;
Exhaust steam pressure:
a) to characterize the condensation mode with constant pressure and performance characteristics with selections for two- and one-stage heating of network water - 0.05 kgf / cm 2;
b) to characterize the condensation mode at a constant flow rate and temperature of the cooling water in accordance with the thermal characteristic of the K-2-3000-2 condenser at W = 7000 m 3 / h and t in 1 = 20 ° C - (graph T-31);
c) for the mode of operation with steam extraction with three-stage heating of network water - in accordance with schedule T-38;
The high and low pressure regeneration system is fully included; steam is supplied to the deaerator of 6 kgf/cm 2 from selections III or II (when the steam pressure in the selection chamber III drops to 7 kgf/cm 2, steam is supplied to the deaerator from selection II);
The feed water flow rate is equal to the live steam flow rate;
The temperature of the feed water and main condensate of the turbine downstream of the heaters corresponds to the dependencies shown in graphs T-6 and T-7;
The increase in the enthalpy of feed water in the feed pump - 7 kcal/kg;
The efficiency of the electric generator corresponds to the warranty data of the Electrosila plant;
The range of pressure regulation in the upper heating selection - 0.6 - 2.5 kgf / cm 2, and in the lower - 0.5 - 2.0 kgf / cm 2;
Heating of network water in the heating plant - 47 °С.
The test data underlying this energy characteristic were processed using the “Tables of Thermophysical Properties of Water and Steam” (Publishing House of Standards, 1969).
The condensate of the heating steam of the high-pressure heaters is cascaded into HPH No. 5, and from it is fed into the deaerator 6 kgf/cm 2 . When the steam pressure in the selection chamber III is below 9 kgf/cm 2, the heating steam condensate from HPH No. 5 is sent to HPH 4. In this case, if the steam pressure in the selection chamber II is higher than 9 kgf/cm 2, the heating steam condensate from HPH No. 6 is sent into the deaerator 6 kgf / cm 2.
Heating steam condensate from low-pressure heaters is cascaded into LPH No. 2, from which it is fed by drain pumps to the main condensate line behind LPH No. 2. Heating steam condensate from LPH No. 1 is drained into the condenser.
The upper and lower network water heaters are connected to the VI and VII turbine outlets, respectively. The heating steam condensate of the upper heating water heater is supplied to the main condensate line downstream of LPH No. 2, and the lower one is fed into the main condensate line downstream of LPH No. I.
2. The composition of the turbine unit, along with the turbine, includes the following equipment:
Generator type TV-60-2 of the Electrosila plant with hydrogen cooling;
Four low pressure heaters: HDPE No. 1 and HDPE No. 2 of type PN-100-16-9, HDPE No. 3 and HDPE No. 4 of type PN-130-16-9;
Three high pressure heaters: HPH No. 5 type PV-350-230-21M, HPH No. 6 type PV-350-230-36M, HPH No. 7 type PV-350-230-50M;
Surface two-way capacitor K2-3000-2;
Two main three-stage ejectors EP-3-600-4A and one starter (one main ejector is constantly in operation);
Two network water heaters (upper and lower) PSS-1300-3-8-1;
Two 8KsD-6?3 condensate pumps driven by electric motors with a capacity of 100 kW each (one pump is constantly in operation, the other is in reserve);
Three condensate pumps for network water heaters 8KsD-5?3 driven by electric motors with a capacity of 100 kW each (two pumps are in operation, one is in reserve).
3. In the condensing mode of operation with the pressure regulator turned off, the total gross heat consumption and fresh steam consumption, depending on the power at the generator outputs, are analytically expressed by the following equations:
At a constant vapor pressure in the condenser P 2 \u003d 0.05 kgf / cm 2 (graph T-22, b)
Q o \u003d 10.3 + 1.985N t + 0.195 (N t - 45.44) Gcal / h; (1)
D o \u003d 10.8 + 3.368 N t + 0.715 (N t - 45.44) t / h; (2)
At a constant flow rate (W = 7000 m 3 / h) and temperature (t in 1 = 20 ° C) of cooling water (graph T-22, a):
Q o \u003d 10.0 + 1.987 N t + 0.376 (N t - 45.3) Gcal / h; (3)
D o \u003d 8.0 + 3.439 N t + 0.827 (N t - 45.3) t / h. (4)
The heat and live steam consumption for the power specified in the operating conditions are determined according to the above dependencies with the subsequent introduction of the necessary amendments (graphs T-41, T-42, T-43); these corrections take into account deviations in operating conditions from nominal (from characteristic conditions).
The system of correction curves practically covers the entire range of possible deviations of the operating conditions of the turbine unit from the nominal ones. This makes it possible to analyze the operation of the turbine unit in a power plant.
The corrections are calculated for the condition of maintaining a constant power at the generator outputs. If there are two or more deviations from the nominal operating conditions of the turbogenerator, the corrections are algebraically summed up.
4. In the mode with heat extractions, the turbine unit can operate with one-, two- and three-stage heating of network water. The corresponding typical mode diagrams are shown on the graphs T-33 (a - d), T-33A, T-34 (a - j), T-34A and T-37.
The diagrams indicate the conditions for their construction and the rules for using them.
Typical mode diagrams allow you to directly determine for the accepted initial conditions (N t, Q t, P t) the steam flow to the turbine.
Graphs T-33 (a - d) and T-34 (a - k) show diagrams of regimes expressing the dependence D o \u003d f (N t, Q t) at certain pressure values in controlled selections.
It should be noted that the diagrams of regimes for one- and two-stage heating of network water, expressing the dependence D о \u003d f (N t, Q t, P t) (graphs T-33A and T-34A), are less accurate due to certain assumptions, taken during their construction. These mode diagrams can be recommended for use when indicative calculations. When using them, it should be borne in mind that the diagrams do not clearly indicate the boundaries that define all possible modes(according to the limiting steam flow rates through the corresponding compartments of the turbine flow path and limiting pressures in the upper and lower extractions).
For a more accurate determination of the value of steam flow to the turbine for a given thermal and electrical load and steam pressure in controlled extraction, as well as to determine the zone of permissible operating modes, use the mode diagrams presented in graphs T-33 (a - d) and T-34 ( a - k).
The specific heat consumption for the production of electricity for the corresponding operating modes should be determined directly from the graphs T-23 (a - d) - for single-stage heating of network water and T-24 (a - j) - for two-stage heating of network water.
These graphs are built based on the results of special calculations using the characteristics of the sections of the flow path of the turbine and the heat and power plant and do not contain inaccuracies that appear when plotting regime diagrams. The calculation of specific heat consumption for electricity generation using regime diagrams gives a less accurate result.
To determine the specific heat consumption for the production of electricity, as well as the steam consumption for the turbine according to the graphs T-33 (a - d) and T-34 (a - j) at pressures in controlled extractions, for which graphs are not directly given, the method should be used interpolation.
For operating mode with three-stage heating of network water specific consumption heat for electricity generation should be determined according to the T-25 schedule, which is calculated according to the following relationship:
q t \u003d 860 (1 + ) + kcal / (kWh), (5)
where Q pr - constant other heat losses, for turbines 50 MW, taken equal to 0.61 Gcal / h, according to the "Instructions and guidelines on the regulation of specific fuel consumption at thermal power plants (BTI ORGRES, 1966).
Graphs T-44 show corrections to the power at the generator outputs when the operating conditions of the turbine unit deviate from the nominal ones. When the pressure of the exhaust steam in the condenser deviates from the nominal value, the correction to the power is determined by the grid of corrections for vacuum (graph T-43).
The signs of the corrections correspond to the transition from the conditions for constructing the regime diagram to operational ones.
If there are two or more deviations from the nominal operating conditions of the turbine unit, the corrections are algebraically summed up.
Corrections to the power for the parameters of live steam and the temperature of the return network water correspond to the data of the factory calculation.
In order to maintain a constant amount of heat supplied to the consumer (Qt = const), when the parameters of fresh steam change, it is necessary to make an additional correction to the power, taking into account the change in steam consumption in the extraction due to a change in the enthalpy of steam in the controlled extraction. This correction is determined by the following dependencies:
When operating according to the electrical schedule and a constant steam flow to the turbine:
D \u003d -0.1 Q t (P o - ) kW; (6)
D \u003d +0.1 Q t (t about -) kW; (7)
When working according to the thermal schedule:
D \u003d +0.343 Q t (P o - ) kW; (8)
D \u003d -0.357 Q t (t about - ) kW; (9)
D \u003d +0.14 Q t (P o - ) kg / h; (10)
D \u003d -0.14 Q t (t about -) kg / h. (eleven)
The enthalpy of steam in the chambers of controlled heat extraction is determined according to the graphs T-28 and T-29.
The temperature head of the network water heaters is taken according to the calculated data of the TMZ and is determined by the relative undercooling according to the T-37 schedule.
When determining the heat use of network water heaters, the subcooling of the heating steam condensate is assumed to be 20 °C.
When determining the amount of heat perceived by the built-in beam (for three-stage heating of network water), the temperature difference is assumed to be 6 °C.
The electric power developed according to the heating cycle due to the release of heat from controlled extractions is determined from the expression
N tf = W tf? Q t MW, (12)
where W tf - specific generation of electricity for the heating cycle under the appropriate operating modes of the turbine unit is determined according to schedule T-21.
The electrical power developed by the condensation cycle is defined as the difference
N kn \u003d N t - N tf MW. (13)
5. Methodology for determining the specific heat consumption for electricity generation for different modes operation of the turbine unit when the specified conditions deviate from the nominal ones is explained by the following examples.
Example 1: Condensing mode with the pressure regulator switched off.
Given: N t \u003d 40 MW, P o \u003d 125 kgf / cm 2, t o \u003d 550 ° C, P 2 \u003d 0.06 kgf / cm 2; thermal scheme - calculated.
It is required to determine the consumption of live steam and the gross specific heat consumption under given conditions (N t = 40 MW).
In table. 1 shows the calculation sequence.
Example 2. Operating mode with controlled steam extractions with two- and one-stage heating of network water.
A. Operating mode according to the thermal schedule
Given: Q t \u003d 60 Gcal / h; R tv \u003d 1.0 kgf / cm 2; R o \u003d 125 kgf / cm 2; t o \u003d 545 ° С; t 2 \u003d 55 ° С; heating of network water - two-stage; thermal scheme - calculated; other conditions are nominal.
It is required to determine the power at the generator outputs, the fresh steam consumption and the gross specific heat consumption under the given conditions (Qt = 60 Gcal/h).
In table. 2 shows the calculation sequence.
The operating mode for single-stage heating of network water is calculated similarly.
Table 1
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Index |
Designation |
Dimension |
Definition method |
Received value |
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Fresh steam flow rate per turbine at nominal conditions |
Schedule T-22 or Equation (2) |
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Turbine heat consumption at nominal conditions |
Schedule T-22 or Equation (1) |
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Specific heat consumption at nominal conditions |
kcal/(kWh) |
Schedule T-22 or Q o / N t |
Heating plant steam turbine T-50/60-130 is designed to drive an electric generator and has two heat extraction outlets for distributing heat for heating. Like other turbines with a capacity of 30-60 MW, it is intended for installation at thermal power plants of medium and small cities. The pressure in both heating and production extraction is maintained by regulating rotary diaphragms installed in the LPC.
The turbine is designed to operate at the following nominal parameters:
superheated steam pressure – 3.41 MPa;
temperature of superheated steam - 396°C;
· rated power of the turbine - 50 MW.
Subsequence technological process The working fluid is as follows: the steam generated in the boiler is sent through the steam pipelines to the high-pressure cylinder of the turbine, having worked out 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 off to the cooling water, which has its own circulation circuit (circulating water), then, using condensate pumps, the main condensate is sent to the regeneration system. This system includes 4 HDPE, 3 HPH and a deaerator. The regeneration system is designed to heat the feed water at the boiler inlet to certain temperature. This temperature has a fixed value and is indicated in the turbine passport.
The thermal circuit diagram is one of the basic diagrams of a power plant. Such a scheme gives an idea of the type of power plant and the principle of its operation, revealing the essence of the technological process of energy generation, and also characterizes the technical equipment and thermal efficiency of the plant. It is necessary to calculate the heat and energy balances of the installation.
This diagram shows 7 extractions, two of which are also heat extraction, i.e. are intended for heating of network water. The drains from the heaters are discharged either to the previous heater or with the help of drainage pumps to the mixing point. After the main condensate has passed 4 LPHs, it enters the deaerator. The main significance of which is not to heat the water, but to purify it from oxygen, which causes corrosion of pipeline metals, screen pipes, pipes of superheaters and other equipment.
Basic elements and conventions:
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 scheme turbines Т50/60-130
Table 1.1. Nominal values of the main parameters of the turbine
Table 1.2. Steam parameters in the selection chamber
| Heater | Steam parameters in the selection chamber | Amount of selected 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 | |
| HDPE4 | 0,529 | 2,3 | |
| PNDZ | 0,272 | 2,97 | |
| PND2 | 0,0981 | - | 0,97 |
| PND1 | 0,04 | - | 0,055 |
Turbine T -100/120-130
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 designed for direct generator drive alternating current, type TVF-100-2 with a capacity of 100 MW with hydrogen cooling.
The turbine is designed to operate with fresh steam parameters of 130 ata and a temperature of 565C, measured in front of the stop valve.
The nominal temperature of the cooling water at the inlet to the condenser is 20C.
The turbine has two heating outlets: upper and lower, designed for stepwise heating of network water in boilers.
The turbine can take a load of up to 120 MW at certain values heating steam extractions.
Turbine PT -65/75-130/13
Condensing turbine with controlled steam extraction for production and district heating without reheating, two-cylinder, single-flow, with a capacity of 65 MW.
The turbine is designed to operate with the following steam parameters:
Pressure in front of the turbine 130 kgf / cm 2,
Steam temperature in front of the turbine 555 °С,
Steam pressure in the production selection 10-18 kgf / cm 2,
Steam pressure in heating extraction 0.6-1.5 kgf / cm 2,
Nominal steam pressure in the condenser 0.04 kgf/cm 2 .
The maximum steam consumption for the turbine is 400 t/h, the maximum steam extraction for production is 250 t/h, the maximum amount of heat released from hot water- 90 Gcal/h.
The turbine regenerative plant consists of four low-pressure heaters, a 6 kgf/cm2 deaerator, and three high-pressure heaters. Part of the cooling water after the condenser is taken to the water treatment plant.
Turbine T-50-130
The single-shaft steam turbine T-50-130 with a rated power of 50 MW at 3000 rpm with condensation and two heating steam extractions is designed to drive an alternating current generator of the TVF 60-2 type with a power of 50 MW with hydrogen cooling. The turbine put into operation is controlled from the control panel.
The turbine is designed to operate with fresh steam parameters of 130 ata, 565 C 0 measured in front of the stop valve. The nominal temperature of the cooling water at the inlet to the condenser is 20 С 0 .
The turbine has two heating outlets, upper and lower, designed for stepwise heating of network water in boilers. The feed water is heated sequentially in the refrigerators of the main ejector and the steam suction ejector from the seals with a stuffing box heater, four HDPE and three HPH. HPH No. 1 and No. 2 are fed with steam from heating extractions, and the remaining five - from unregulated extractions after 9, 11, 14, 17, 19 steps.
Capacitors
Main purpose condensation device is the condensation of the exhaust steam of the turbine and the provision of optimal steam pressure behind the turbine under nominal operating conditions.
In addition to maintaining the pressure of the exhaust steam at the level required for the economical operation of the turbine plant, it ensures the maintenance of the exhaust steam condensate and its quality in accordance with the requirements of the PTE and the absence of subcooling in relation to the saturation temperature in the condenser.
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Type before and after marking |
Capacitor type |
Estimated amount of cooling water, t/h |
Nominal steam consumption for the condenser, t/h |
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dismantling |
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Technical data of the capacitor 65KTsST:
Heat transfer surface, m 3 3000
Number of cooling pipes, pcs. 5470
Internal and outside diameter, mm 23/25
Length of condenser pipes, mm 7000
Pipe material - copper-nickel alloy MNZh5-1
Nominal consumption of cooling water, m 3 / h 8000
Number of cooling water passes, pcs. 2
Number of cooling water flows, pcs. 2
Mass of the condenser without water, t. 60.3
Mass of the condenser with filled water space, t 92.3
Mass of the condenser with filled vapor space during hydrotesting, t 150.3
The coefficient of cleanliness of the pipes, adopted in the thermal calculation of the condenser 0.9
Cooling water pressure, MPa (kgf/cm2) 0.2(2.0)
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