Ministry of Education and Science of the Russian Federation
Branch of the federal state budgetary educational institution higher vocational education
National Research University Moscow Power Engineering Institute in Volzhsky
Department of Industrial Thermal Power Engineering
On industrial training practice
At LLC "LUKOIL - Volgogradenergo" Volzhskaya CHPP
Student of VF MPEI (TU) group TES-09
Naumov Vladislav Sergeevich
Head of practice:
from the enterprise: Shidlovsky S.N.
from the institute: Zakozhurnikova G.P.
Volzhsky, 2012
Introduction
.Safety regulations 2.Thermal diagram
.Turbine PT-135/165-130/15 .Turbine T-100/120-130 .Turbine PT-65/75-130/13 .Turbine T-50-130 .Capacitors .Circulating water system .Heaters low pressure
.Heaters high pressure
.Deaerators .Reducing cooling units .Turbine oil supply system .Thermal power plant heating plant .Feed pumps Conclusion Bibliography Introduction:
LLC "LUKOIL - Volgogradenergo" Volzhskaya CHPP is the most powerful thermal station in the region. Volzhskaya CHPP-1 is an energy enterprise in Volzhsky. Construction of the Volzhskaya CHPP-1 began in May 1959<#"justify">Auxiliary equipment includes: feed pumps, HDPE, HDPE, condensers, deaerators, network heaters or boilers. 1. Safety regulations
All personnel must be provided with special clothing, safety shoes and by individual means protection in accordance with the nature of the work performed and is obliged to use them during work Personnel must work in work clothes that are fastened with all buttons. There should be no fluttering parts on clothing that could be caught by moving (rotating) parts of the mechanisms. Rolling up the sleeves of workwear and tucking the tops of boots is prohibited. All production personnel must be practically trained in the techniques of releasing a person under voltage from the action. electric current and providing him with first aid, as well as methods of providing first aid to victims in other accidents. At each enterprise, safe routes through the territory of the enterprise to the place of work and evacuation plans in case of fire or emergency must be developed and brought to the attention of all personnel. Persons unrelated to the maintenance of the equipment located there are prohibited from being on the territory of the power plant and in the production premises of the enterprise without accompanying persons. All passages and passages, entrances and exits are as inside production premises and structures, and outside on the adjacent territory must be illuminated, free and safe for the movement of pedestrians and vehicles. Obstructing passages and passages or using them for storing goods is prohibited. Interfloor ceilings, floors, channels, and pits must be maintained in good repair. All openings in the floor must be fenced. Covers and edges of hatches of wells, chambers and pits, as well as channel covers must be made of corrugated iron, flush with the floor or ground and securely fastened. 2. Thermal circuit
3. Turbine PT -135/165-130/15
Stationary steam heating turbine type Turbine PT -135/165-130/15 with a condensing device and adjustable production and two heating steam extractions with a nominal power of 135 MW, designed for direct drive of a turbogenerator with a rotor speed of 3000 rpm. And supply of steam and heat for production and heating needs. The turbine is designed to operate with the following basic parameters: .Live steam pressure before the automatic stop valve is 130 ata; 2.Fresh steam temperature before the automatic stop valve 555C; .The calculated temperature of the cooling water at the condenser inlet is 20C; .Cooling water consumption - 12400 m3/hour. The maximum steam consumption at nominal parameters is 760t/h. The turbine is equipped with a regenerative device for heating the feedwater and must operate in conjunction with a condensing unit. The turbine has an adjustable production steam extraction with a nominal pressure of 15 ata and two adjustable heating steam extractions - upper and lower, intended for heating network water in the network heaters of the turbine unit and additional water in station heat exchangers. . 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 extractions, steam is designed to directly drive the generator alternating current, type TVF-100-2 with a power of 100 MW with hydrogen cooling. The turbine is designed to operate with fresh steam parameters of 130 atm and a temperature of 565C, measured before the stop valve. The nominal temperature of the cooling water at the condenser inlet 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 of heating steam extraction. 5. Turbine PT -65/75-130/13
Condensing turbine with controlled steam extraction for production and district heating without reheating, two-cylinder, single-flow, 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 °C, -steam pressure in production extraction 10-18 kgf/cm 2,
-steam pressure in district heating extraction 0.6-1.5 kgf/cm 2,
-nominal steam pressure in the condenser 0.04 kgf/cm 2.
The maximum steam flow per 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 regenerative turbine installation consists of four low pressure heaters, deaerator 6 kgf/cm 2and three high-pressure heaters. Part of the cooling water after the condenser is taken to water treatment plant. The T-50-130 single-shaft steam turbine 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, type TVF 60-2, with a power of 50 MW and hydrogen cooling. A turbine that is put into operation is controlled from the monitoring and control panel. The turbine is designed to work with fresh steam parameters of 130 ata, 565 C 0, measured in front of the stop valve. Nominal temperature of cooling water at the condenser inlet is 20 C 0.
The turbine has two heating outlets, upper and lower, designed for stepwise heating of network water in boilers. Heating of the feed water is carried out sequentially in the refrigerators of the main ejector and the ejector for suctioning steam from the seals with a stuffing box heater, four HDPE and three HDPE. HDPE 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 stages. . Capacitors
The main purpose of the condensing device is to condense the turbine exhaust steam and provide optimal pressure steam behind the turbine under nominal operating conditions. In addition to maintaining the exhaust steam pressure at the level required for economical operation of the turbine unit, it ensures that the exhaust steam condensate is maintained and its quality is appropriate PTE requirements and absence of subcooling relative to the saturation temperature in the condenser. St. No. Type before and after re-marking Condenser type Estimated amount of cooling water, t/h Nominal steam flow per condenser, t/ h 50-130 R-44-1154dismantling5Т-50-130 Т-48-115К2-3000-270001406Т-100-130 Т-97-115КГ2-6200-1160002707Т-100-130 Т-97-115КГ2-6200-116000270 8PT-135- 130-13 PT-135-115-13K-600012400340 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 cooling water flow, m 3/h 8000 Number of cooling water strokes, pcs. 2 Number of cooling water flows, pcs. 2 Condenser weight without water, t. 60.3 Weight of the condenser with filled water space, t 92.3 Mass of the condenser with filled vapor space during hydrotesting, t 150.3 The pipe cleanliness factor adopted in the thermal calculation of the condenser is 0.9 Cooling water pressure, MPa (kgf/cm 2) 0,2(2,0)
. Circulating water supply system (1st stage)
The circulating water supply is intended to supply cooling water to the turbine condenser, generator gas coolers, turbine unit oil coolers, etc. The circulating water supply includes: circulation pumps type 32D-19 (2-TG-1, 2-TG-2, 2-TG-5); spray cooling towers No. 1 and No. 2; pipelines, shut-off and control valves. Circulation pumps supply circulation water from the suction manifolds through circulation pipelines into the cooling tubes of the turbine condenser. Circulating water condenses the exhaust steam entering the condenser after the turbine LPC. The water heated in the condenser enters the drain circulation manifolds, from where it is supplied to the nozzles of the cooling towers. Technical characteristics of the circulator pump type 32D-19: Productivity, m3/h 5600 Pressure, MPa (m. water column) 0.2(20) Permissible suction height (m. water column) 7.5 Rotation speed, rpm 585 Electric motor power, kW 320 The pump housing is made of cast iron with a horizontal connector. The pump shaft is steel. The shaft is sealed where it exits the housing using stuffing box seals. Pressure water is supplied to the seal to remove friction heat. The supports are ball bearings. Cooling towers: Technical and economic characteristics of the spray cooling tower: Irrigation area - 1280 m 2
Estimated water flow - 9200 m 3/ h Maneuverability - 0-9200 m Temperature difference - 8 C 0
Spraying devices - evolute nozzles designed by VNIIG 2050 pcs. Water pressure in front of the nozzle - 4 mm.water column. Water supply height - 8.6 m Air inlet window height - 3.5 m Exhaust tower height - 49.5 m Pool diameter - 40 m Cooling tower height - 49.5 m Pool volume - 2135.2 m 3
. Low pressure heaters of turbine No. 1
The system of low and high pressure heaters is designed to increase the thermodynamic efficiency of the cycle by heating the main condensate and feed water with turbine extraction steam. The low pressure heater system includes the following equipment: three series-connected low-pressure surface heaters type PN -200-16-7-1; two drain pumps PND-2 type Ks-50-110-2; Low pressure heater device Low-pressure heaters are structurally a cylindrical apparatus of vertical design with an upper location of the water distribution chamber, four passages through the main condensate. Technical characteristics of HDPE 2,3 and 4 types PN-20016-7-1M. Heating surface - 200 m 2
Maximum pressure in a pipe system - 1.56(16) MPa (kgf/cm 2)
Maximum pressure in the housing - 0.68(0.7) MPa (kgf/cm 2)
Maximum steam temperature - 240 C 0
Test hydraulic pressure in the pipe system is 2.1 (21.4) MPa (kgf/cm 2)
Test hydraulic pressure in the housing - 0.95 (9.7) MPa (kgf/cm 2)
Nominal water consumption - 350 t/h Hydraulic resistance of the pipe system - 0.68(7) MPa(kgf/cm 2) 10. High pressure heaters
HPHs are designed for regenerative heating of feedwater due to cooling and condensation of steam from turbine extractions. The high pressure heater system includes the following equipment: three high-pressure heaters connected in series, type PV 375-23-2.5-1, PV 375-23-3.5-1 and PV 375-23-5.0-1 pipelines, shut-off and control valves. High-pressure heaters are a welded apparatus of a vertical type. The main components of the heater are the body and the coil pipe system. The body consists of an upper removable part welded from a cylindrical shell, a stamped bottom and flange, and a lower non-light part. Basic factory data . Deaerators
Purpose of the deaerator installation: Air dissolved in the condenser, feed and additional water, contains aggressive gases that cause corrosion of equipment and pipelines of a power plant. A deaeration unit is designed to carry out deaeration of water in the cycle of a steam power plant. In addition, it serves to heat the feed water in the regeneration circuit of the turbine unit and create a constant reserve of feed water to compensate for the imbalance between the water flow to the boiler and to the deaerator. Characteristics Deaerator No. 4, 6, 7, 8, 9 of feed water No. 3, 5, 13 of chemically desalted water No. 11, 12, 14, 15 of feed water Type of head Chipboard-400 DS-300 Chipboard-500 Number of heads 121 Head capacity, t/h 400 300 500 Tank capacity, m 3100100100Working pressure, kgf/cm 261.26 Water temperature in the storage tank, C 0158104158
Deaeration column DP-400 is vertical, jet-drip type, having closed chamber mixing and five holey plates with a pitch between them of 765mm. Deaeration of water is carried out by fragmenting the stream in the holes of five plates. Fittings are inserted into the housing for supplying heating steam and deaerated water, and for removing steam. Productivity - 400 t/h Working pressure - 6 kgf/cm 2
Operating temperature - 158 C 0
Permissible temperature vessel walls - 164 C 0
Working environment- water, steam Test hydraulic pressure - 9 kgf/cm 2
Permissible increase in pressure during operation of safety valves - 7.25 kgf/cm 2
Deaeration column DP-500 is vertical, film type with a random packing. The separation of water into films is carried out using omega-shaped nozzles with holes. Steam also passing through these nozzles and having large area resistance and sufficient duration of contact with water. Fittings are inserted into the column body for supplying heating steam and deaerated water. Specifications :
Productivity - 500 t/h Working pressure - 7 kgf/cm 2
Operating temperature - 164 C 0
Hydraulic pressure - 10 kgf/cm 2
Permissible temperature of the vessel walls - 172 C 0
Working medium - steam, water Nozzle layer height - 500 mm Dry weight - 9660 kg Battery tankdesigned to create a constant reserve of feed water and provide power to boilers for a certain time. Safety valveis a shut-off device that opens when the pressure rises above the permissible value and closes when the pressure drops above the nominal value. The safety valve is installed together with the pulse valve. . Reducing cooling units
Reduction-cooling units are designed to reduce the pressure and temperature of steam to the limits set by consumers. They serve for: reservation of production and heat supply turbines; reservation and supply of steam to own consumers (deaerator, ejectors, boiler heaters, LDPE, etc.); rational use of steam when lighting boilers. The steam pressure is regulated by changing the opening value of the installation's throttle valve, and the temperature by changing the amount of cooling water injected into the steam. No. Installation typePerformanceParametersbeforeafterP 1, kgf/cm 2T 1, WITH 0R 2, kgf/cm 2T 2, WITH 01RROU No. 1 140/14150140530142302RROU No. 7 140/14150140530142303ROU 21/14 TG-3 (2 pcs)10021395142304ROU 14/2.5 (3 pcs)30142302.51955ROU-11,12,14 250140530142306ROU-1325014053020270 13. Turbine oil cooling system
The turbine oil system is designed to provide oil (Tp-22, Tp-22S) to both the turbine and generator bearing lubrication system and the control system. The main elements of the oil system of the T-100/120-130 turbine are: oil tank with a capacity of 26 m 3with an ejector group and oil coolers built into it; main oil pump centrifugal type, mounted on the turbine shaft; starting oil pump 8MS7x7 with a capacity of 300 m 3/ h; reserve oil pump 5 with a capacity of 150 m 3/ h; emergency oil pump 4 with a capacity of 108 m 3/ h; system of pressure and drain oil pipelines; control and measuring instruments. The system is made with a centrifugal type main oil pump installed on the turbine shaft, which drops oil into the system with a pressure of 14 kgf/cm during turbine operation. 2.
Technical characteristics of oil lubrication pumps: Name of indicators Reserve pump Emergency pump Pump type 5 Dw 4 Dv Capacity, m 3/ h150108 Pressure, mm. water Art. 2822 Rotation speed, rpm 1450 1450 Electric motor type A2-71-4P-62 Electric motor power, kW 2214 Voltage, V 380 220 . Thermal power plant heating plant
The turbine heating unit is designed to heat network water supplied by network pumps to network heaters. Heating of the network water is carried out using the heat of the turbine extraction steam. The heating installation of the T-100/120-130 turbine consists of the following elements: network horizontal heater (PSG-1) type PSG-2300-2-8-1; network horizontal heater (PSG-2) type PSG-2300-3-8-2; three condensate pumps type KSV-320-160; booster pumps type 20NDS; network pumps type SE-2500-180 and SE-1250-140; pipelines for supplying steam to network heaters; network water pipelines, heating steam condensate pipelines of heaters, suction pipelines of non-condensing gases from heaters to the condenser; shut-off and control valves, drainage systems and emptying of pipelines and equipment; automatic level control systems for network heaters; control and measuring instruments, technological protections, interlocks, alarms. Parameter name CharacteristicsPSG-2300-2-8-1PSG-2300-3-8-2Water space: working pressure, kgf/cm288Outlet temperature,С0125125Water flow, m3/h3500-45003500-4500Hydraulic resistance (at 70С0), mm.water. Art. 6.86.8 Volume, l2200023000 Steam space: working pressure, kgf/cm234.5 Steam temperature, С0250300 Steam consumption, t/h185185 Condensate consumption, t/h185185 Housing volume, l3000031000 Condensate collector volume, l43003400 Tube bundle Heat transfer surface, m223002300Number of strokes44Number of tubes49994999Tube diameter,mm24/2224/22Tube length , mm62806280 Technical characteristics of the network pump SE-2500-180: Parameter name Characteristics Capacity, m3/h2500 Pressure, m180 Allowable cavitation reserve, m28 Working pressure at the inlet, kgf/cm210 Pumped water temperature, C0120 Pump efficiency, %84 Pump power, kW 1460 Water consumption for cooling the seal and bearings, m3/ h3 Electric motor type 2АЗМ- 1600 Electric motor power, kW 1600 Voltage, V 6000 Rotation speed, rpm3000 Rice. Heating plant diagram . Feed pumps
Feed pumps PE-500-180, PE-580-185-3, which are part of the thermal circuit of the Volzhskaya CHPP-1, are designed to supply water to the boiler units of the power plant. Feed pumps PE-500-180, PE-580-185-3 are included in one group of pumps that have the same type of unified design main nodes. Feed pumps PE-500-180 and PE-580-185-3 - centrifugal, horizontal, double-casing, sectional type with 10 pressure levels. Main structural elements The pump consists of: housing, rotor, ring seals, bearings, axial force relief system, coupling. Main characteristics of the pump PE-500-180: Capacity, m3/h500Pressure, m1975Admissible cavitation reserve, m15Feed water temperature, C0160Pressure in the discharge pipe, kgf/cm2186.7Pump operating interval, m3/h130-500Rotation speed, rpm2985Power consumption, kW3180Pump efficiency, %78.2Flow oil, m3/h2 .8Condensate consumption, m3/h3Condensate consumption process water, m3/h107.5 Main characteristics of the pump PE-580-18: Capacity, m3/h580 Pressure, m2030 Allowable cavitation reserve, m15 Feed water temperature, C0165 Pressure at pump inlet, kgf/cm27 Pressure at pump outlet, kgf/cm210 Pressure in discharge pipe, kgf/cm2230 Rotation speed, rpm 2982 Power consumption, kW 3590 Pump efficiency a, %81 Operating time to failure, h8000 Recirculation flow, m3/h130 Conclusion
In the process of passing industrial practice at the Volzhskaya CHPP I got acquainted with the main and additional equipment CHP. I studied the passport data, operating diagram and technical characteristics of the turbines of CHPP-1: turbine PT-135/165-130/15, turbine T-100/120-130, turbine PT-65/75-130/13, turbine T-50 -130. I also got acquainted with the passport data and technical characteristics of the auxiliary equipment: condenser 65 KTSST-5, circulating water supply system, high-pressure pumps and low-pressure pumps, cooling towers, high-pressure deaerators, reduction-cooling units, turbine oil supply system, feed pumps. In my report I described the appointments, design features, technical characteristics of the main and auxiliary equipment of the turbine shop of the thermal power plant. Bibliography:
1.Description of turbine type T-50-130. 2.Description of turbine type T-100/120-130 .Description of turbine type PT-135/165-130/15 .Description of turbine type PT-65/75-130/13 .Instructions for the design and maintenance of deaerators .Instructions for the design and maintenance of low pressure heaters .Instructions for the design and maintenance of high pressure heaters .Instructions for the design and maintenance of the oil supply system of a thermal power plant .Instructions for the design and maintenance of feed pumps .Instructions for the design and maintenance of capacitors .Instructions for the design and maintenance of reduction-cooling units
Cogeneration turbines with a capacity of 40-100 MW
Cogeneration turbines with a capacity of 40-100 MW for initial steam parameters of 130 kgf/cm2, 565ºС are designed as a single series, united by common basic solutions, unity of design and broad unification of components and parts.
Turbine T-50-130 with two heating steam extractions at 3000 rpm, rated power 50 MW. Subsequently, the rated power of the turbine was increased to 55 MW while simultaneously improving the turbine's efficiency guarantee.
The T-50-130 turbine is made of two cylinders and has a single-flow exhaust. All extractions, regenerative and heating, together with the exhaust pipe are placed in one low-pressure cylinder. In the high-pressure cylinder, steam expands to the pressure of the upper regenerative extraction (about 34 kgf/cm2), in the low-pressure cylinder - to the pressure of the lower heating extraction
For the T-50-130 turbine, it was optimal to use a two-crown control wheel with a limited isentropic difference and perform the first group of stages with a small diameter. The high pressure cylinder of all turbines has 9 stages - control and 8 pressure stages.
Subsequent stages located in a medium or low pressure cylinder have a higher volumetric flow rate of steam and are made with larger diameters.
All stages of the turbines of the series have aerodynamically developed profiles; for the control stage of the high-pressure engine, blades from the Moscow Energy Institute with radial profiling of the nozzle and working grids were adopted.
Blading of the CVP and CSD is performed with radial and axial tendrils, which made it possible to reduce the gaps in the flow part.
The high-pressure cylinder is made counter-flow 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 part of both the HPC and the LPC (or the LPC for 50 MW turbines).
The implementation of heating turbines with one thrust bearing was facilitated by the balancing of the main part of the axial force achieved in the turbines within each individual rotor and the transfer of the remaining, limited in magnitude, force to the bearing operating in both directions. In heating turbines, unlike 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 forces along the flow path take place in turbines with two heating extractions when the outside air temperature changes. Since the steam consumption remains unchanged, this change in the axial force practically cannot be compensated by the dummis and is completely transferred to the thrust bearing. Factory-performed study of alternating turbine operation, as well as bifurcation
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 extractions, the steam is designed to directly drive an alternating current generator, type TVF-100-2 with a power of 100 MW and hydrogen cooling.
The turbine is designed to operate with fresh steam parameters of 130 atm and a temperature of 565C, measured before the stop valve.
The nominal temperature of the cooling water at the condenser inlet 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 of heating steam extraction.
Turbine PT -65/75-130/13
Condensing turbine with controlled steam extraction for production and district heating without reheating, two-cylinder, single-flow, 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 is 555 °C,
Steam pressure in production extraction is 10-18 kgf/cm 2,
Steam pressure in district heating extraction is 0.6-1.5 kgf/cm2,
The nominal steam pressure in the condenser is 0.04 kgf/cm2.
The maximum steam consumption per turbine is 400 t/h, the maximum steam extraction for production is 250 t/h, the maximum amount of heat released with hot water is 90 Gcal/h.
The regenerative turbine installation 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 T-50-130 single-shaft steam turbine 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, type TVF 60-2, with a power of 50 MW and hydrogen cooling. A turbine that is put into operation is controlled from the monitoring and control panel.
The turbine is designed to operate with fresh steam parameters of 130 ata, 565 C 0, measured before the stop valve. The nominal temperature of the cooling water at the condenser inlet is 20 C 0.
The turbine has two heating outlets, upper and lower, designed for stepwise heating of network water in boilers. Heating of the feed water is carried out sequentially in the refrigerators of the main ejector and the ejector for suctioning steam from the seals with a stuffing box heater, four HDPE and three HDPE. HDPE 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 stages.
Capacitors
The main purpose of the condensing device is to condense the exhaust steam of the turbine and ensure optimal steam pressure behind the turbine under nominal operating conditions.
In addition to maintaining the exhaust steam pressure at the level required for economical operation of the turbine unit, it ensures that the exhaust steam condensate is maintained and its quality meets the requirements of the PTE and the absence of overcooling in relation to the saturation temperature in the condenser.
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Type before and after relabeling |
Capacitor type |
Estimated amount of cooling water, t/h |
Nominal steam consumption per 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
Inner and outer diameter, mm 23/25
Length of condenser pipes, mm 7000
Pipe material - copper-nickel alloy MNZh5-1
Nominal cooling water flow, m 3 /h 8000
Number of cooling water strokes, pcs. 2
Number of cooling water flows, pcs. 2
Condenser weight without water, t. 60.3
Weight of the condenser with filled water space, t 92.3
Mass of the condenser with filled vapor space during hydrotesting, t 150.3
The pipe cleanliness factor adopted in the thermal calculation of the condenser is 0.9
Cooling water pressure, MPa (kgf/cm2) 0.2(2.0)
T-50-130 TMZ
TYPICAL
ENERGY CHARACTERISTICS
TURBO UNIT
T-50-130 TMZ
SERVICE OF EXCELLENCE AND INFORMATION SOYUZTEKHENERGO
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 the typical characteristics data with the TMZ warranty data
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Index |
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Heat transferred to the consumer Q t, Gcal/h |
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Turbine operating mode |
Condensation |
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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Cooling water temperature at the condenser inlet t in 1, °C |
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Cooling water flow W, m 3 /h |
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Specific steam consumption d, kg/(kW? h) |
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Typical data |
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Fresh steam pressure P o, kgf/cm 2 |
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Fresh steam temperature t o , °C |
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Pressure in regulated extraction P, kgf/cm 2 |
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Generator efficiency h, % |
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Temperature of feed water downstream of HPH No. 7 t p.v., °C |
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Temperature of network water at the inlet to the PSG heater t 2, °C |
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Exhaust steam pressure P 2, kgf/cm 2 |
t in 1 = 20 °C, W = 7000 m 3 / h |
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Specific steam consumption d e, kg/(kW? h) |
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Amendment to specific steam consumption for deviation of standard characteristics from warranty conditions |
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for deviation of exhaust steam pressure Dd e, kg/(kWh) |
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for deviation of feed water temperature Dd e, kg/(kW? h) |
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for temperature deviation of return network water Dd e, kg/(kW? h) |
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Total correction to specific steam consumption Dd e, kg/(kW? h) |
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Specific steam consumption under warranty conditions dne, kg/(kW? h) |
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Deviation of specific steam consumption from the guarantee ad e, % |
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Average deviation ad e, % |
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* Extraction pressure regulator is switched off. |
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PRINCIPAL THERMAL DIAGRAM 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 EXTRACTION CHAMBERS UNDER 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 EXTRACTION CHAMBERS UNDER HEATING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM PRESSURE IN EXTRACTION CHAMBERS UNDER HEATING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT TEMPERATURE AND ENTHALPY OF FEEDWATER BEYOND HIGH PRESSURE HEATERS |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CONDENSATE TEMPERATURE BEYOND HDPE No. 4 WITH TWO- AND THREE-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION FOR HIGH PRESSURE HEATERS AND DEARATOR |
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 LEAKS THROUGH THE FIRST COMPARTMENTS OF THE HPC, LPC SHAFT SEALS, STEAM SUPPLY TO THE END SEALS |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT EXTRACTIONS OF STEAM FROM SEALS INTO I, IV EXTRACTIONS, INTO THE STILLING HEATER AND COOLER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION THROUGH THE 21ST STAGE WITH TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION THROUGH THE 23rd STAGE WITH SINGLE-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM CONSUMPTION IN LPG IN CONDENSING MODE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT STEAM FLOW IN THE LPG 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 HEATING OF NETWORK WATER |
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 ELECTRICITY PRODUCTION FROM THERMAL 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 CONSUMPTION OF FRESH STEAM AND HEAT IN CONDENSING MODE WITH PRESSURE REGULATOR DISABLED |
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 HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT SPECIFIC GROSS HEAT CONSUMPTION FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT SPECIFIC HEAT CONSUMPTION FOR THREE-STAGE HEATING OF NETWORK WATER AND ELECTROMECHANICAL EFFICIENCY OF THE TURBO UNIT |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT TEMPERATURE DIFFERENCE |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT RELATIVE UNDERHEATING OF NETWORK WATER IN PSG AND PSV |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT ENTHALPY OF STEAM IN THE UPPER HEATING CHAMBER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT INTERMEDIATE COMPARTMENT HEAT DROP USED |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT HEAT USE IN THE NETWORK WATER HEATER (PSW) |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT CHARACTERISTICS OF CONDENSER K2-3000-2 |
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 MODE DIAGRAM FOR SINGLE-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT MODE DIAGRAM FOR SINGLE-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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Given: Q t = 60 Gcal/h; N t = 34 MW; R tn = 1.0 kgf/cm 2.
Determine: D about t/h.
Definition. On the diagram we find the given point A (Q t = 60 Gcal/h; N t = 34 MW). From point A, parallel to the inclined straight line, we go to the line set pressure(R tn = 1.0 kgf/cm 2). From the resulting point B we go in a straight line to the line of the given pressure (P tn = 1.0 kgf/cm2) of the right quadrant. From the resulting point B we lower the perpendicular to the flow axis. Point G corresponds to the determined fresh steam flow.
Given: Q t = 75 Gcal/h; R tn = 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 = 75 Gcal/h; P t = 0.5 kgf/cm 2). From point D we go in a straight line to the power axis. Point E corresponds to the determined power. Then we go in a straight line to the line P tn = 0.5 kgf/cm 2 of the right quadrant. From point G we lower the perpendicular to the flow axis. The resulting point 3 corresponds to the determined fresh steam flow.
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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 FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT DIAGRAM OF MODES FOR TWO-STAGE HEATING OF NETWORK WATER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
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Asked by: Q T= 81 Gcal/h; N t = 57.2 MW; P TV= 1.4 kgf/cm2. 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= 1.4 kgf/cm 2). From the obtained point B we go in a straight line to the line of the given pressure ( P T in= 1.4 kgf/cm 2) left quadrant. From the resulting point B we lower the perpendicular to the flow axis. Point G corresponds to the determined fresh steam flow. |
Asked by: Q T= 73 Gcal/h; P T in= 0.8 kgf/cm2. Determine: N t MW; D 0 t/h Definition. Finding the given point D (QT= 73 Gcal/h; P T in = 0.8 kgf/cm 2) From point D we go in a straight line 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 left quadrant. From the resulting point Ж we lower the perpendicular to the flow axis. The resulting point 3 corresponds to the determined fresh steam flow. |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT |
Type T-50-130 TMZ |
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b) Deviation of fresh steam pressure from the nominal V)
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT AMENDMENTS TO FRESH STEAM CONSUMPTION IN 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 fresh steam temperature from the nominal b) Deviation of fresh steam pressure from the nominal V) Deviation of feed water flow from the nominal
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT AMENDMENTS TO SPECIFIC HEAT CONSUMPTION IN CONDENSING MODE |
Type T-50-130 TMZ |
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d) For underheating of feed water in high-pressure heaters 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 POWER FOR EXHAUST STEAM PRESSURE IN THE CONDENSER |
Type T-50-130 TMZ |
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TYPICAL ENERGY CHARACTERISTICS OF A TURBO UNIT ADJUSTMENTS TO POWER WHEN WORKING WITH HEATING COIL EXHAUSTS |
Type T-50-130 TMZ |
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Given: Q t = 81 Gcal/h; N t = 57.2 MW; R TV = 1.4 kgf/cm 2.
Determine: D about 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 = 1.4 kgf/cm 2). From the resulting point B we go in a straight line to the line of the given pressure (P TV = 1.4 kgf/cm2) of the left quadrant. From the resulting point B we lower the perpendicular to the flow axis. Point G corresponds to the determined fresh steam flow.
Given: Q t = 73 Gcal/h; R TV = 0.8 kgf/cm 2.
Determine: N t MW; D about t/h.
Definition. We find the given point D (Q t = 73 Gcal/h; P t = 0.8 kgf/cm 2). From point D we go in a straight line to the power axis. Point E corresponds to the determined power. Then we go in a straight line to the line P TV = 0.8 kgf/cm 2 of the left quadrant. From the resulting point Ж we lower the perpendicular to the flow axis. The resulting point 3 corresponds to the determined fresh steam flow.
APPLICATION
1. The typical energy characteristics of the T-50-130 TMZ turbine unit are compiled on the basis of thermal tests of two turbines (carried out by Yuzhtekhenergo at the Leningradskaya CHPP-14 and Sibtekhenergo at the Ust-Kamenogorskaya CHPP) and reflects the average efficiency of a turbine unit that has undergone a major overhaul, operating according to the factory design thermal scheme (graph T-1) and under the following conditions accepted as nominal:
The pressure and temperature of fresh steam in front of the turbine stop valves are, respectively, 130 kgf/cm2 * and 555 °C;
* Absolute pressure is given in the text and graphs.
The maximum permissible fresh steam consumption is 265 t/h;
The maximum permissible steam flow through the switchable compartment and low-pressure pump is 165 and 140 t/h, respectively; the limit values of steam flow through certain compartments correspond to the technical specifications of TU 24-2-319-71;
Exhaust steam pressure:
a) for the characteristics of the condensation mode with constant pressure and the characteristics of work with selections for two- and one-stage heating of network water - 0.05 kgf/cm 2 ;
b) to characterize the condensation regime at a constant flow rate and temperature of cooling water in accordance with the thermal characteristics 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 operating mode 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 enabled; steam from selection III or II is supplied to the deaerator at 6 kgf/cm 2 (when the steam pressure in chamber III of selection decreases to 7 kgf/cm 2 steam is supplied to the deaerator from selection II);
The feedwater flow rate is equal to the fresh steam flow rate;
The temperature of the feed water and the main turbine condensate behind the heaters corresponds to the dependencies shown in graphs T-6 and T-7;
The increase in enthalpy of feed water in the feed pump is 7 kcal/kg;
The efficiency of the electric generator corresponds to the warranty data of the Elektrosila plant;
The pressure control range in the upper heating selection is 0.6 - 2.5 kgf/cm 2, and in the lower one - 0.5 - 2.0 kgf/cm 2;
Heating of network water in the heating plant is 47 °C.
The test data underlying this energy characteristic was processed using the “Tables of Thermophysical Properties of Water and Water Steam” (Publishing House of Standards, 1969).
The condensate from the heating steam of the high-pressure heaters is drained in cascade into HPH No. 5, and from it is fed into the deaerator 6 kgf/cm2. When the steam pressure in selection chamber III is below 9 kgf/cm 2, the heating steam condensate from HPH No. 5 is sent to HPH 4. Moreover, if the steam pressure in selection chamber II is above 9 kgf/cm2, the heating steam condensate from HPH No. 6 is sent in the deaerator 6 kgf/cm2.
The condensate of the heating steam of the low-pressure heaters is drained in cascade into the HDPE No. 2, from which it is supplied by drain pumps to the main condensate line behind the HDPE No. 2. The heating steam condensate from the HDPE No. 1 is drained into the condenser.
The upper and lower heating water heaters are connected to turbine outlets VI and VII, respectively. The condensate of the heating steam from the upper heating water heater is supplied to the main condensate line behind the HDPE No. 2, and from the lower one - into the main condensate line behind the HDPE No. I.
2. The turbine unit, along with the turbine, includes the following equipment:
Generator type TV-60-2 from the Elektrosila plant with hydrogen cooling;
Four low-pressure heaters: HDPE No. 1 and HDPE No. 2, type PN-100-16-9, HDPE No. 3 and HDPE No. 4, type PN-130-16-9;
Three high-pressure heaters: PVD No. 5 type PV-350-230-21M, PVD No. 6 type PV-350-230-36M, PVD 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 starting one (one main ejector is constantly in operation);
Two network water heaters (upper and lower) PSS-1300-3-8-1;
Two condensate pumps 8KsD-6?3 driven by electric motors with a power of 100 kW (one pump is constantly in operation, the other is in reserve);
Three condensate pumps of network water heaters 8KsD-5?3 driven by electric motors with a power 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 terminals, are analytically expressed by the following equations:
At constant steam pressure in the condenser P 2 = 0.05 kgf/cm 2 (graph T-22, b)
Q o = 10.3 + 1.985N t + 0.195 (N t - 45.44) Gcal/h; (1)
D o = 10.8 + 3.368 N t + 0.715 (N t - 45.44) t/h; (2)
At constant flow (W = 7000 m 3 / h) and temperature (t in 1 = 20 ° C) of cooling water (graph T-22, a):
Q o = 10.0 + 1.987 N t + 0.376 (N t - 45.3) Gcal/h; (3)
D o = 8.0 + 3.439 N t + 0.827 (N t - 45.3) t/h. (4)
The consumption of heat and fresh steam for the power specified under operating conditions is determined from the above dependencies with the subsequent introduction of the necessary corrections (graphs T-41, T-42, T-43); these amendments take into account deviations of 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 a turbine unit under power plant conditions.
The corrections are calculated for the condition of maintaining constant power at the generator terminals. 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 district heating extraction, the turbine unit can operate with one-, two- and three-stage heating of network water. The corresponding typical mode diagrams are shown in 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 of use.
Typical mode diagrams allow you to directly determine for the adopted initial conditions(N t, Q t, P t) steam flow to the turbine.
Graphs T-33 (a - d) and T-34 (a - j) show regime diagrams expressing the dependence D o = f (N t, Q t) at certain pressure values in regulated extractions.
It should be noted that mode diagrams for one- and two-stage heating of network water, expressing the dependence D o = f(N t, Q t, P t) (graphs T-33A and T-34A), are less accurate due to certain assumptions, adopted during their construction. These mode diagrams can be recommended for use in approximate calculations. When using them, it should be borne in mind that the diagrams do not clearly indicate the boundaries defining all possible modes (according to the maximum steam flow rates through the corresponding sections of the turbine flow path and the maximum pressures in the upper and lower extractions).
For more precise definition values of steam flow to the turbine for a given thermal and electrical load and steam pressure in a controlled extraction, as well as determining the zone of permissible operating modes, one should use the mode diagrams presented in graphs T-33 (a - d) and T-34 (a - j) .
Specific heat consumption for electricity production for the corresponding operating modes should be determined directly from 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 constructed based on the results of special calculations using the characteristics of the turbine flow section and heating plant and do not contain inaccuracies that appear when constructing regime diagrams. Calculation of specific heat consumption for electricity generation using mode diagrams gives a less accurate result.
To determine the specific heat consumption for the production of electricity, as well as the steam consumption per turbine according to graphs T-33 (a - d) and T-34 (a - j) at pressures in regulated extractions, for which graphs are not directly given, the method should be used interpolation.
For operating mode with three-stage heating of heating water specific consumption heat for electricity production should be determined according to schedule T-25, which is calculated according to the following relationship:
q t = 860 (1 + ) + kcal/(kWh), (5)
where Q pr - constant other heat losses, for 50 MW turbines, taken equal to 0.61 Gcal/h, according to the “Instructions and methodological instructions on standardization of specific fuel consumption at thermal power plants" (BTI ORGRES, 1966).
The T-44 graphs show corrections to the power at the generator terminals when the operating conditions of the turbine unit deviate from the nominal ones. If the exhaust steam pressure in the condenser deviates from the nominal value, the power correction is determined using the vacuum correction grid (graph T-43).
The signs of the corrections correspond to the transition from the conditions for constructing the regime diagram to operational conditions.
If there are two or more deviations of the operating conditions of the turbine unit from the nominal ones, the corrections are algebraically summed up.
Corrections to power for fresh steam parameters and return water temperature correspond to the factory calculation data.
In order to maintain a constant amount of heat supplied to the consumer (Q t = 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 flow into the extraction due to a change in the enthalpy of steam in the controlled extraction. This amendment is determined by the following dependencies:
When working according to an electrical schedule and a constant steam flow to the turbine:
D = -0.1 Q t (P o - ) kW; (6)
D = +0.1 Q t (t o - ) kW; (7)
When working according to the heat schedule:
D = +0.343 Q t (P o - ) kW; (8)
D = -0.357 Q t (t o - ) kW; (9)
D = +0.14 Q t (P o - ) kg/h; (10)
D = -0.14 Q t (t o - ) kg/h. (eleven)
The enthalpy of steam in the chambers of controlled heating extraction is determined according to graphs T-28 and T-29.
The temperature pressure of the network water heaters is taken according to the calculated TMZ data and is determined by the relative underheating according to schedule T-37.
When determining the heat utilization 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 pressure is assumed to be 6 °C.
The electric power developed in the heating cycle due to the release of heat from regulated extractions is determined from the expression
N tf = W tf? Q t MW, (12)
where W tf - specific electricity production for the heating cycle under the corresponding operating modes of the turbine unit is determined according to schedule T-21.
The electrical power developed by the condensation cycle is determined as the difference
N kn = N t - N tf MW. (13)
5. The methodology for determining the specific heat consumption for electricity generation for various operating modes of a turbine unit when the specified conditions deviate from the nominal ones is explained by the following examples.
Example 1. Condensing mode with pressure regulator disabled.
Given: N t = 40 MW, P o = 125 kgf/cm 2 , t o = 550 °C, P 2 = 0.06 kgf/cm 2 ; thermal diagram - calculated.
It is required to determine the fresh steam consumption and gross specific heat consumption under given conditions (Nt = 40 MW).
In table 1 shows the calculation sequence.
Example 2. Operating mode with controlled steam extraction for two- and one-stage heating of network water.
A. Operating mode according to thermal schedule
Given: Q t = 60 Gcal/h; R TV = 1.0 kgf/cm 2; P o = 125 kgf/cm 2 ; t o = 545 °C; t 2 = 55 °C; heating of network water - two-stage; thermal diagram - calculated; other conditions are nominal.
It is required to determine the power at the generator terminals, fresh steam consumption and gross specific heat consumption under given conditions (Q t = 60 Gcal/h).
In table 2 shows the calculation sequence.
The operating mode for single-stage heating of network water is calculated in a similar way.
Table 1
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Index |
Designation |
Dimension |
Determination method |
Received value |
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Fresh steam consumption per turbine at nominal conditions |
Graph T-22 or equation (2) |
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Heat consumption per turbine at nominal conditions |
Graph 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 |
