Description of the condensing unit of boilers tgm 84. Hello student. Estimated heat balance and fuel consumption

The typical energy characteristic of the TGM-96B boiler reflects the technically achievable efficiency of the boiler. A typical energy characteristic can serve as the basis for compiling the standard characteristics of TGM-96B boilers when burning fuel oil.

MINISTRY OF ENERGY AND ELECTRIFICATION OF THE USSR

MAIN TECHNICAL DEPARTMENT FOR OPERATION
ENERGY SYSTEMS

TYPICAL ENERGY DATA
OF THE TGM-96B BOILER FOR FUEL FUEL COMBUSTION

Moscow 1981

This Typical Energy Characteristic was developed by Soyuztekhenergo (engineer G.I. GUTSALO)

The typical energy characteristic of the TGM-96B boiler was compiled on the basis of thermal tests conducted by Soyuztekhenergo at the Riga CHPP-2 and Sredaztekhenergo at the CHPP-GAZ, and reflects the technically achievable efficiency of the boiler.

A typical energy characteristic can serve as the basis for compiling the standard characteristics of TGM-96B boilers when burning fuel oil.

Appendix

. BRIEF DESCRIPTION OF THE BOILER INSTALLATION EQUIPMENT

1.1 . Boiler TGM-96B of the Taganrog Boiler Plant - gas-oil with natural circulation and U-shaped layout, designed to work with turbines T -100/120-130-3 and PT-60-130/13. The main design parameters of the boiler when operating on fuel oil are given in Table. .

According to the TKZ, the minimum allowable load of the boiler according to the circulation condition is 40% of the nominal one.

1.2 . The combustion chamber has a prismatic shape and in plan is a rectangle with dimensions of 6080 × 14700 mm. The volume of the combustion chamber is 1635 m 3 . The thermal stress of the furnace volume is 214 kW/m 3 , or 184 10 3 kcal/(m 3 h). Evaporative screens and a radiation wall superheater (RNS) are placed in the combustion chamber. In the upper part of the furnace in the rotary chamber there is a screen superheater (SHPP). In the lowering convective shaft, two packages of a convective superheater (CSH) and a water economizer (WE) are located in series along the gas flow.

1.3 . The steam path of the boiler consists of two independent flows with steam transfer between the sides of the boiler. The temperature of the superheated steam is controlled by injection of its own condensate.

1.4 . On the front wall of the combustion chamber there are four double-flow oil-gas burners HF TsKB-VTI. The burners are installed in two tiers at elevations of -7250 and 11300 mm with an elevation angle of 10° to the horizon.

For burning fuel oil, steam-mechanical nozzles "Titan" are provided with a nominal capacity of 8.4 t / h at a fuel oil pressure of 3.5 MPa (35 kgf / cm 2). The steam pressure for blowing off and spraying fuel oil is recommended by the plant to be 0.6 MPa (6 kgf/cm2). Steam consumption per nozzle is 240 kg/h.

1.5 . The boiler plant is equipped with:

Two draft fans VDN-16-P with a capacity of 259 10 3 m 3 / h with a margin of 10%, a pressure of 39.8 MPa (398.0 kgf / m 2) with a margin of 20%, a power of 500/250 kW and a rotation speed of 741 /594 rpm each machine;

Two smoke exhausters DN-24 × 2-0.62 GM with a capacity of 10% margin 415 10 3 m 3 / h, pressure with a margin of 20% 21.6 MPa (216.0 kgf / m 2), power 800/400 kW and a speed of 743/595 rpm of each machine.

1.6. To clean the convective heating surfaces from ash deposits, the project provides for a shot plant, for cleaning the RAH - water washing and blowing with steam from a drum with a decrease in pressure in the throttling plant. The duration of blowing one RAH 50 min.

. TYPICAL ENERGY CHARACTERISTICS OF THE TGM-96B BOILER

2.1 . Typical energy characteristic of the TGM-96B boiler ( rice. , , ) was compiled on the basis of the results of thermal tests of boilers at Riga CHPP-2 and CHPP GAZ in accordance with the instructive materials and methodological guidelines for standardizing the technical and economic indicators of boilers. The characteristic reflects the average efficiency of a new boiler operating with turbines T -100/120-130/3 and PT-60-130/13 under the following conditions taken as initial.

2.1.1 . The fuel balance of power plants burning liquid fuels is dominated by high-sulphur fuel oil M 100. Therefore, the characteristic is drawn up for fuel oil M 100 ( GOST 10585-75) with characteristics: A P = 0.14%, W P = 1.5%, S P = 3.5%, (9500 kcal/kg). All necessary calculations are made for the working mass of fuel oil

2.1.2 . The temperature of the fuel oil in front of the nozzles is assumed to be 120 ° C( t t= 120 °С) based on fuel oil viscosity conditions M 100, equal to 2.5 ° VU, according to § 5.41 PTE.

2.1.3 . The average annual temperature of cold air (t x .c.) at the inlet to the blower fan is taken equal to 10 ° C , since TGM-96B boilers are mainly located in climatic regions (Moscow, Riga, Gorky, Chisinau) with an average annual air temperature close to this temperature.

2.1.4 . The air temperature at the inlet to the air heater (t vp) is taken equal to 70 ° C and constant when the boiler load changes, in accordance with § 17.25 PTE.

2.1.5 . For power plants with cross connections, the feed water temperature (t a.c.) in front of the boiler is taken as calculated (230 °C) and constant when the boiler load changes.

2.1.6 . The specific net heat consumption for the turbine plant is assumed to be 1750 kcal/(kWh), according to thermal tests.

2.1.7 . The heat flow coefficient is assumed to vary with the boiler load from 98.5% at rated load to 97.5% at a load of 0.6D number.

2.2 . The calculation of the standard characteristic was carried out in accordance with the instructions of the “Thermal calculation of boiler units (normative method)”, (M.: Energia, 1973).

2.2.1 . The gross efficiency of the boiler and the heat loss with flue gases were calculated in accordance with the methodology described in the book by Ya.L. Pekker "Heat engineering calculations based on the reduced characteristics of the fuel" (M.: Energia, 1977).

where

here

α uh = α "ve + Δ α tr

α uh- coefficient of excess air in the exhaust gases;

Δ α tr- suction cups in the gas path of the boiler;

T uh- flue gas temperature behind the smoke exhauster.

The calculation takes into account the flue gas temperatures measured in the boiler thermal tests and reduced to the conditions for constructing a standard characteristic (input parameterst x in, t "kf, t a.c.).

2.2.2 . Excess air coefficient at the mode point (behind the water economizer)α "ve taken equal to 1.04 at rated load and changing to 1.1 at 50% load according to thermal tests.

The reduction of the calculated (1.13) excess air coefficient downstream of the water economizer to the one adopted in the standard characteristic (1.04) is achieved by the correct maintenance of the combustion mode according to the regime map of the boiler, compliance with the PTE requirements regarding air suction into the furnace and into the gas path and selection of a set of nozzles .

2.2.3 . Air suction into the gas path of the boiler at rated load is taken equal to 25%. With a change in load, air suction is determined by the formula

2.2.4 . Heat losses from chemical incompleteness of fuel combustion (q 3 ) are taken equal to zero, since during the tests of the boiler with excess air, accepted in the Typical energy characteristic, they were absent.

2.2.5 . Heat loss from mechanical incompleteness of fuel combustion (q 4 ) are taken equal to zero according to the "Regulations on the harmonization of the regulatory characteristics of equipment and estimated specific fuel consumption" (M.: STsNTI ORGRES, 1975).

2.2.6 . Heat loss to the environment (q 5 ) were not determined during the tests. They are calculated in accordance with the "Method of testing boiler plants" (M.: Energia, 1970) according to the formula

2.2.7 . The specific power consumption for the feed electric pump PE-580-185-2 was calculated using the characteristics of the pump adopted from the specifications TU-26-06-899-74.

2.2.8 . The specific power consumption for draft and blast is calculated from the power consumption for the drive of draft fans and smoke exhausters, measured during thermal tests and reduced to the conditions (Δ α tr= 25%), adopted in the preparation of the regulatory characteristics.

It has been established that at a sufficient density of the gas path (Δ α ≤ 30%) smoke exhausters provide the rated load of the boiler at low speed, but without any reserve.

Blow fans at low speed ensure normal operation of the boiler up to loads of 450 t/h.

2.2.9 . The total electric power of the mechanisms of the boiler plant includes the power of electric drives: electric feed pump, smoke exhausters, fans, regenerative air heaters (Fig. ). The power of the electric motor of the regenerative air heater is taken according to the passport data. The power of the electric motors of smoke exhausters, fans and the electric feed pump was determined during the thermal tests of the boiler.

2.2.10 . The specific heat consumption for air heating in a calorific unit is calculated taking into account air heating in fans.

2.2.11 . The specific heat consumption for auxiliary needs of the boiler plant includes heat losses in heaters, the efficiency of which is assumed to be 98%; for steam blowing of RAH and heat loss with steam blowing of the boiler.

The heat consumption for steam blowing of RAH was calculated by the formula

Q obd = G obd · i obd · τ obd 10 -3 MW (Gcal/h)

where G obd= 75 kg/min in accordance with the "Standards for the consumption of steam and condensate for auxiliary needs of power units 300, 200, 150 MW" (M.: STSNTI ORGRES, 1974);

i obd = i us. pair= 2598 kJ/kg (kcal/kg)

τ obd= 200 min (4 devices with a blowing time of 50 min when switched on during the day).

The heat consumption with the boiler blowdown was calculated by the formula

Q prod = G prod · i k.v10 -3 MW (Gcal/h)

where G prod = PD nom 10 2 kg/h

P = 0.5%

i k.v- enthalpy of boiler water;

2.2.12 . The procedure for conducting tests and the choice of measuring instruments used in the tests were determined by the "Method of testing boiler plants" (M .: Energia, 1970).

. AMENDMENTS TO REGULATIONS

3.1 . In order to bring the main normative indicators of the boiler operation to the changed conditions of its operation within the permissible deviation limits of the parameter values, amendments are given in the form of graphs and numerical values. Amendments toq 2 in the form of graphs are shown in fig. , . Corrections to flue gas temperature are shown in fig. . In addition to the above, corrections are given for the change in the temperature of heating fuel oil supplied to the boiler, and for the change in the temperature of the feed water.

MINISTRY OF ENERGY AND ELECTRIFICATION OF THE USSR

MAIN TECHNICAL DEPARTMENT FOR OPERATION
ENERGY SYSTEMS

TYPICAL ENERGY DATA
OF THE TGM-96B BOILER FOR FUEL FUEL COMBUSTION

Moscow 1981

This Typical Energy Characteristic was developed by Soyuztekhenergo (engineer G.I. GUTSALO)

A typical energy characteristic can serve as the basis for compiling the standard characteristics of TGM-96B boilers when burning fuel oil.

Appendix

. BRIEF DESCRIPTION OF THE BOILER INSTALLATION EQUIPMENT

According to the TKZ, the minimum allowable load of the boiler according to the circulation condition is 40% of the nominal one.

1.5 . The boiler plant is equipped with:

. TYPICAL ENERGY CHARACTERISTICS OF THE TGM-96B BOILER

2.1.1 . The fuel balance of power plants burning liquid fuels is dominated by high-sulphur fuel oil M 100. Therefore, the characteristic is drawn up for fuel oil M 100 (GOST 10585-75 ) with characteristics: A P = 0.14%, W P = 1.5%, S P = 3.5%, (9500 kcal/kg). All necessary calculations are made for the working mass of fuel oil

2.1.2 . The temperature of the fuel oil in front of the nozzles is assumed to be 120 ° C( t t= 120 °С) based on fuel oil viscosity conditions M 100, equal to 2.5 ° VU, according to § 5.41 PTE.

2.1.4 . The air temperature at the inlet to the air heater (t vp) is taken equal to 70 ° C and constant when the boiler load changes, in accordance with § 17.25 PTE.

2.1.5 . For power plants with cross connections, the feed water temperature (t a.c.) in front of the boiler is taken as calculated (230 °C) and constant when the boiler load changes.

2.1.6 . The specific net heat consumption for the turbine plant is assumed to be 1750 kcal/(kWh), according to thermal tests.

2.1.7 . The heat flow coefficient is assumed to vary with the boiler load from 98.5% at rated load to 97.5% at a load of 0.6D number.

2.2 . The calculation of the standard characteristic was carried out in accordance with the instructions of the “Thermal calculation of boiler units (normative method)”, (M.: Energia, 1973).

where

here

α uh = α "ve + Δ α tr

α uh- coefficient of excess air in the exhaust gases;

Δ α tr- suction cups in the gas path of the boiler;

T uh- flue gas temperature behind the smoke exhauster.

2.2.2 . Excess air coefficient at the mode point (behind the water economizer)α "ve taken equal to 1.04 at rated load and changing to 1.1 at 50% load according to thermal tests.

2.2.3 . Air suction into the gas path of the boiler at rated load is taken equal to 25%. With a change in load, air suction is determined by the formula

2.2.7 . The specific power consumption for the feed electric pump PE-580-185-2 was calculated using the characteristics of the pump adopted from the specifications TU-26-06-899-74.

It has been established that at a sufficient density of the gas path (Δ α ≤ 30%) smoke exhausters provide the rated load of the boiler at low speed, but without any reserve.

Blow fans at low speed ensure normal operation of the boiler up to loads of 450 t/h.

2.2.10 . The specific heat consumption for air heating in a calorific unit is calculated taking into account air heating in fans.

The heat consumption for steam blowing of RAH was calculated by the formula

Q obd = G obd · i obd · τ obd 10 -3 MW (Gcal/h)

where G obd= 75 kg/min in accordance with the "Standards for the consumption of steam and condensate for auxiliary needs of power units 300, 200, 150 MW" (M.: STSNTI ORGRES, 1974);

i obd = i us. pair= 2598 kJ/kg (kcal/kg)

τ obd= 200 min (4 devices with a blowing time of 50 min when switched on during the day).

The heat consumption with the boiler blowdown was calculated by the formula

Q prod = G prod · i k.v10 -3 MW (Gcal/h)

where G prod = PD nom 10 2 kg/h

P = 0.5%

i k.v- enthalpy of boiler water;

2.2.12 . The procedure for conducting tests and the choice of measuring instruments used in the tests were determined by the "Method of testing boiler plants" (M .: Energia, 1970).

. AMENDMENTS TO REGULATIONS

3.1.1 . The correction for the change in the temperature of the fuel oil supplied to the boiler is calculated from the effect of the change To Q on the q 2 by formula

Description of the object.

Full name:“Automated training course “Operation of the TGM-96B boiler unit when burning fuel oil and natural gas”.

Symbol:

Year of issue: 2007.

The automated training course for the operation of the TGM-96B boiler unit was developed to train operational personnel servicing boiler plants of this type and is a means of training, pre-examination preparation and examination testing of CHP personnel.

AUK is compiled on the basis of regulatory and technical documentation used in the operation of TGM-96B boilers. It contains textual and graphical material for interactive study and testing of students.

This AUC describes the design and technological characteristics of the main and auxiliary equipment of TGM-96B boilers, namely: a combustion chamber, a drum, a superheater, a convection shaft, a power unit, draft devices, steam and water temperature control, etc.

Starting, normal, emergency and shutdown modes of operation of the boiler plant are considered, as well as the main reliability criteria for heating and cooling down steam pipelines, screens and other elements of the boiler.

The system of automatic control of the boiler, the system of protections, interlocks and alarms are considered.

The procedure for admission to inspection, testing, repair of equipment, safety rules and explosion and fire safety have been determined.

The composition of the AUC:

Automated training course (ATC) is a software tool designed for initial training and subsequent testing of knowledge of the personnel of power plants and electrical networks. First of all, for the training of operational and operational-repair personnel.

The basis of AUC is the current production and job descriptions, regulatory materials, data from equipment manufacturers.

AUC includes:

section of general theoretical information;
a section that deals with the design and operation of a particular type of equipment;
student self-examination section;
examiner block.

In addition to texts, AUC contains the necessary graphic material (diagrams, drawings, photographs).

Information content of AUK.

The text material is based on the operating instructions for the TGM-96 boiler unit, factory instructions, other regulatory and technical materials and includes the following sections:

1. Brief description of the design of the TGM-96 boiler unit.
1.1. Main settings.
1.2. Boiler layout.
1.3. Furnace chamber.
1.3.1. General information.
1.3.2. Placement of heating surfaces in the furnace.
1.4. Burner device.
1.4.1. General information.
1.4.2. Specifications of the burner.
1.4.3. Oil nozzles.
1.5. Drum and separation device.
1.5.1. General information.
1.5.2. Intradrum device.
1.6. Superheater.
1.6.1. General information.
1.6.2. Radiation superheater.
1.6.3. Ceiling superheater.
1.6.4. Shielded steam heater.
1.6.5. Convective superheater.
1.6.6. Scheme of steam movement.
1.7. A device for controlling the temperature of superheated steam.
1.7.1. condensation plant.
1.7.2. injection devices.
1.7.3. Scheme of supply of condensate and feed water.
1.8. Water economizer.
1.8.1. General information.
1.8.2. Suspended part of the economizer.
1.8.3. Wall economizer panels.
1.8.4. convective economizer.
1.9. Air heater.
1.10. Boiler frame.
1.11. Boiler lining.
1.12. Cleaning of heating surfaces.
1.13. Thrust installation.
2. Extract from the thermal calculation.
2.1. The main characteristics of the boiler.
2.2. Excess air coefficients.
2.3. Thermal balance and characteristics of the furnace.
2.4. The temperature of the combustion products.
2.5. steam temperatures.
2.6. Water temperatures.
2.7. Air temperatures.
2.8. Condensate consumption for injection.
2.9. boiler resistance.
3. Preparing the boiler for cold start.
3.1. Inspection and testing of equipment.
3.2. Preparation of lighting schemes.
3.2.1. Assembling circuits for warming up a reduced power unit and injections.
3.2.2. Assembly of schemes for steam pipelines and a superheater.
3.2.3. Assembly of the gas-air path.
3.2.4. Preparation of gas pipelines of the boiler.
3.2.5. Assembly of fuel oil pipelines within the boiler.
3.3. Filling the boiler with water.
3.3.1. General provisions.
3.3.2. Operations before filling.
3.3.3. Operations after filling.
4. Kindling the boiler.
4.1. A common part.
4.2. Kindling on gas from a cold state.
4.2.1. Furnace ventilation.
4.2.2. Filling the pipeline with gas.
4.2.3. Checking the gas pipeline and fittings within the boiler for tightness.
4.2.4. Ignition of the first burner.
4.2.5. Ignition of the second and subsequent burners.
4.2.6. Purging of water-indicating columns.
4.2.7. Boiler firing schedule.
4.2.8. Purging the bottom points of the screens.
4.2.9. Temperature regime of a radiant superheater during kindling.
4.2.10. Temperature regime of the water economizer during kindling.
4.2.11. Inclusion of the boiler in the main.
4.2.12. Raising the load to nominal.
4.3. Boiler kindling from a hot state.
4.4. Fire-up of the boiler using the boiler water recirculation scheme.
5. Maintenance of the boiler and equipment during operation.
5.1. General provisions.
5.1.1. The main tasks of the operating personnel.
5.1.2. Boiler steam output regulation.
5.2. Boiler service.
5.2.1. Observations during the operation of the boiler.
5.2.2. Boiler power.
5.2.3. Superheated steam temperature control.
5.2.4. Combustion control.
5.2.5. Boiler purge.
5.2.6. Oil boiler operation.
6. Switching from one type of fuel to another.
6.1. Switching from natural gas to fuel oil.
6.1.1. Transfer of the burner from gas combustion to fuel oil from the main control room.
6.1.2. Transfer of the burner from fuel oil to natural gas on site.
6.2. Switching from fuel oil to natural gas.
6.2.1. Transfer of the heater from fuel oil combustion to natural gas from the main control room.
6.2.2. Transfer of the burner from fuel oil to natural gas on site.
6.3. Co-firing of natural gas and fuel oil.
7. Stop the boiler.
7.1. General provisions.
7.2. Stop the boiler in reserve.
7.2.1. Actions of personnel during shutdown.
7.2.2. Testing of safety valves.
7.2.3. Actions of personnel after shutdown.
7.3. Boiler shutdown with cooldown.
7.4. Boiler emergency stop.
7.4.1. Cases of emergency shutdown of the boiler by protection or personnel.
7.4.2. Cases of emergency shutdown of the boiler by order of the chief engineer.
7.4.3. Remote shutdown of the boiler.
8. Emergencies and the procedure for their elimination.
8.1. General provisions.
8.1.1. A common part.
8.1.2. Responsibilities of the personnel on duty in case of an accident.
8.1.3. Personnel actions during an accident.
8.2. Load shedding.
8.3. Station load shedding with loss of auxiliary needs.
8.4. Lowering of the water level.
8.4.1. Signs of downgrading and actions of personnel.
8.4.2. Actions of the personnel after the liquidation of the accident.
8.5. Rising water level.
8.5.1. Signs and actions of personnel.
8.5.2. Actions of personnel in case of failure of the protection.
8.6. Failure of all water-indicating devices.
8.7. Screen pipe rupture.
8.8. Rupture of the superheater pipe.
8.9. Rupture of the water economizer pipe.
8.10. Detection of cracks in pipelines and steam fittings of the boiler.
8.11. Increasing pressure in the drum over 170 atm and failure of safety valves.
8.12. Stopping the gas supply.
8.13. Reducing the oil pressure behind the control valve.
8.14. Shutdown of both smoke exhausters.
8.15. Turn off both blowers.
8.16. Disable all RVPs.
8.17. Ignition of deposits in air heaters.
8.18. Explosion in the furnace or gas ducts of the boiler.
8.19. Breakage of the torch, unstable combustion mode, pulsation in the furnace.
8.20. Throwing water into the superheater.
8.21. Rupture of the main fuel oil pipeline.
8.22. Rupture or fire on fuel oil pipelines within the boiler.
8.23. Gap or fire on the main gas pipelines.
8.24. Gap or fire on gas pipelines within the boiler.
8.25. Decreasing the outdoor air temperature below the calculated one.
9. Boiler automation.
9.1. General provisions.
9.2. Level regulator.
9.3. combustion regulator.
9.4. Superheated steam temperature controller.
9.5. Continuous purge regulator.
9.6. Water Phosphating Regulator.
10. Thermal protection of the boiler.
10.1. General provisions.
10.2. Boiler overfeeding protection.
10.3. Level-down protection.
10.4. Protection when turning off smoke exhausters or blowers.
10.5. Protection when all RVPs are turned off.
10.6. Emergency stop of the boiler with a button.
10.7. Fuel pressure drop protection.
10.8. Gas pressure increase protection.
10.9. Operation of the fuel switch.
10.10. Flame extinguishing protection in the furnace.
10.11. Protection for increasing the temperature of superheated steam behind the boiler.
11. Technological protection and alarm settings.
11.1. Process alarm settings.
11.2. Technological protection settings.
12. Impulse-safety devices of the boiler.
12.1. General provisions.
12.2. IPU operation.
13. Safety and fire prevention measures.
13.1. A common part.
13.2. Safety regulations.
13.3. Safety measures when taking the boiler out for repair.
13.4. Safety and fire safety requirements.
13.4.1. General information.
13.4.2. Safety requirements.
13.4.3. Safety requirements for the operation of the boiler on fuel oil substitutes.
13.4.4. fire safety requirements.

14. Graphic material in this AUK is presented as part of 17 figures and diagrams:
14.1. The layout of the boiler TGM-96B.
14.2. Under the combustion chamber.
14.3. Screen pipe attachment point.
14.4. The layout of the burners.
14.5. Burner device.
14.6. Intradrum device.
14.7. condensation plant.
14.8. Scheme of a reduced power unit and boiler injections.
14.9. Desuperheater.
14.10. Assembling a circuit for warming up a reduced power unit.
14.11. Scheme of kindling the boiler (steam path).
14.12. Scheme of gas-air ducts of the boiler.
14.13. Scheme of gas pipelines within the boiler.
14.14. Scheme of fuel oil pipelines within the boiler.
14.15. Furnace ventilation.
14.16. Filling the pipeline with gas.
14.17. Checking the gas pipeline for tightness.

Knowledge check

After studying the textual and graphic material, the student can launch a program of self-testing knowledge. The program is a test that checks the degree of assimilation of the material of the instruction. In case of an erroneous answer, the operator is shown an error message and a quote from the text of the instruction containing the correct answer. The total number of questions in this course is 396.

Exam

After completing the training course and self-control of knowledge, the student takes an examination test. It includes 10 questions automatically selected at random from among the questions provided for self-test. During the exam, the examinee is asked to answer these questions without prompts and the opportunity to refer to the textbook. No error messages are displayed until the end of testing. After the end of the exam, the student receives a protocol that contains the proposed questions, the answers chosen by the examiner and comments on erroneous answers. The exam grade is set automatically. The test protocol is stored on the hard drive of the computer. It is possible to print it on a printer.

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Federal Agency for Education

State educational institution

higher professional education

"Ural State Technical University - UPI

Name of the first President of Russia B.N. Yeltsin" -

branch in Sredneuralsk

SPECIALTY: 140101

GROUP: TPP -441

COURSE PROJECT

THERMAL CALCULATION OF THE BOILER UNIT TGM - 96

ON THE DISCIPLINE “Boiler plants of thermal power plants”

Teacher

Svalova Nina Pavlovna

Kashurin Anton Vadimovich

Sredneuralsk

1.Assignment for a course project

2. Brief description and parameters of the TGM-96 boiler

3. Excess air coefficients, volumes and enthalpies of combustion products

4. Thermal calculation of the boiler unit:

4.1 Heat balance and fuel calculation

4.2 Regenerative air heater

a. cold part

b. hot part

4.4 Exit screens

4.4 Entrance screens

Bibliography

1. Assignment for a course project

For the calculation, a drum boiler unit TGM - 96 was adopted.

Job input

Boiler parameters TGM - 96

Boiler steam capacity - 485 t/h

The pressure of superheated steam at the outlet of the boiler is 140 kgf / cm 2

Superheated steam temperature - 560 єС

Working pressure in the boiler drum - 156 kgf / cm 2

Feed water temperature at the inlet to the boiler - 230ºС

Feed water pressure at the inlet to the boiler - 200 kgf / cm 2

The temperature of cold air at the inlet to the RVP is 30ºС

2 . Description of the thermal scheme

The boiler feed water is turbine condensate. Which is heated by a condensate pump sequentially through the main ejectors, the seals ejector, stuffing box heater, LPH-1, LPH-2, LPH-3 and LPH-4 to a temperature of 140-150 ° C and is fed into deaerators 6 atm. In deaerators, the gases dissolved in the condensate are separated (deaeration) and additionally heated to a temperature of approximately 160-170°C. Then the condensate from the deaerators is fed by gravity to the suction of the feed pumps, after which the pressure rises to 180-200 kgf/cm² and the feed water through HPH-5, HPH-6, and HPH-7 heated to a temperature of 225-235°C is fed to a reduced boiler power supply. Behind the boiler power regulator, the pressure drops to 165 kgf / cm² and is fed into the water economizer.

Feed water through 4 chambers D 219x26 mm enters hanging pipes D 42x4.5 mm st. Outlet chambers of suspended pipes are located inside the flue, suspended on 16 pipes D 108x11 mm st. At the same time, flows are transferred from one side to the other. The panels are made of pipes D28x3.5 mm, Art. 20 and screen the side walls and the turning chamber.

Water flows in two parallel streams through the top and bottom panels and is directed to the inlet chambers of the convective economizer.

The convective economizer consists of upper and lower packages, the lower part is made in the form of coils from pipes with a diameter of 28x3.5 mm Art. 20, arranged in a checkerboard pattern with a pitch of 80x56 mm. It consists of 2 parts located in the right and left gas ducts. Each part consists of 4 blocks (2 upper and 2 lower). The movement of water and flue gases in a convective economizer is countercurrent. When running on gas, the economizer has a 15% boil. The separation of the steam generated in the economizer (the economizer has a 15% boiling point when operating on gas) takes place in a special steam separator box with a labyrinth hydraulic seal. Through an opening in the box, a constant amount of feed water, regardless of the load, is supplied together with steam into the volume of the drum under the washing shields. Discharge of water from flushing shields is carried out using drain boxes.

The steam-water mixture from the screens through the steam pipes enters the distribution boxes, and then into the vertical separation cyclones, where the primary separation takes place. In the clean compartment, 32 double and 7 single cyclones are installed, in the salt compartment 8 - 4 on each side. Boxes are installed under all cyclones to prevent steam from cyclones from entering the downcomers. The water separated in the cyclones flows down into the water volume of the drum, and the steam, together with a certain amount of moisture, rises up, passing by the reflective cover of the cyclone, enters the washing device, which consists of horizontal perforated shields, to which 50% of the feed water is supplied. Steam, passing through the layer of the washing device, gives it the main amount of silicon salts contained in it. After the flushing device, the steam passes through the louvered separator and is additionally cleaned from moisture droplets, and then through the perforated ceiling shield, which equalizes the velocity field in the steam space of the drum, it enters the superheater.

All separation elements are collapsible and fastened with wedges, which are welded to the separation parts.

The average water level in the drum is 50 mm below the middle of the average gauge glass and 200 mm below the geometric center of the drum. The upper allowable level is +100mm, the lower allowable level is 175 mm on the gauge glass.

To heat the drum body during kindling and cool down when the boiler is stopped, a special device according to the UTE project is mounted in it. Steam is supplied to this device from a nearby operating boiler.

Saturated steam from the drum with a temperature of 343°C enters 6 panels of the radiative superheater and is heated to a temperature of 430°C, after which it is heated to 460-470°C in 6 panels of the ceiling superheater.

In the first desuperheater, the steam temperature is reduced to 360-380°C. Before the first desuperheaters, the steam flow is divided into two flows, and after them, to equalize the temperature sweep, the left steam flow is transferred to the right side, and the right one to the left. After the transfer, each steam flow enters 5 inlet cold screens, followed by 5 outlet cold screens. In these screens, steam moves in countercurrent. Further, the steam enters 5 hot inlet screens in a cocurrent flow, followed by 5 hot outlet screens. Cold screens are located on the sides of the boiler, hot - in the center. The steam temperature level in the screens is 520-530оС.

Further, through 12 steam bypass pipes D 159x18 mm st. If the temperature rises above the specified value, the second injection starts. Further along the bypass pipeline D 325x50 st. 12X1MF enters the output package of the checkpoint, where the temperature increase is 10-15oC. After it, the steam enters the gearbox output manifold, which passes into the main steam pipeline towards the front of the boiler, and 2 main working safety valves are mounted in the rear section.

To remove the salts dissolved in the boiler water, continuous blowing is carried out from the boiler drum; To remove sludge from the lower collectors of the screens, periodic purge of the lower points is carried out. To prevent the formation of calcium scale in the boiler, phosphate the boiler water.

The amount of phosphate introduced is regulated by the senior engineer on the instructions of the shift supervisor of the chemical workshop. To bind free oxygen and form a passivating (protective) film on the inner surfaces of the boiler pipes, dosing hydrazine into the feed water, maintaining its excess of 20-60 µg/kg. Dosing of hydrazine into the feed water is carried out by the personnel of the turbine department on the instructions of the shift supervisor of the chemical shop.

For utilization of heat from continuous blowdown of boilers P och. 2 continuous blowdown expanders connected in series are installed.

Expander 1 tbsp. has a volume of 5000 l and is designed for a pressure of 8 atm with a temperature of 170 ° C, the vapor is directed to the heating steam collector of 6 atm, the separator through the condensate trap into the expander П och.

Expander R st. has a volume of 7500 l and is designed for a pressure of 1.5 atm with an ambient temperature of 127 ° C, the flash steam is directed to the NDU and connected in parallel to the flash steam of the drain expanders and the reduced steam pipeline of the ignition ROU. The dilator separator is directed through an 8 m high water seal into the sewerage system. Submission of drainage expanders P st. in the scheme is prohibited! For emergency drain from boilers P och. and purging the lower points of these boilers, 2 parallel-connected expanders with a volume of 7500 liters each and a design pressure of 1.5 atm are installed in the KTC-1. The flash steam from each expander of periodic blowdown through pipelines with a diameter of 700 mm without shutoff valves is directed to the atmosphere and brought to the roof of the boiler shop. The separation of the steam generated in the economizer (the economizer has a 15% boiling point when operating on gas) takes place in a special steam separator box with a labyrinth hydraulic seal. Through an opening in the box, a constant amount of feed water, regardless of the load, is supplied together with steam into the volume of the drum under the washing shields. Discharge of water from flushing shields is carried out using drain boxes

3 . Excess air coefficients, volumes and enthalpiescombustion products

Estimated characteristic of gaseous fuel (Table II)

Excess air coefficients for gas ducts:

The coefficient of excess air at the outlet of the furnace:

t = 1.0 + ? t \u003d 1.0 + 0.05 \u003d 1.05

?Coefficient of excess air behind the checkpoint:

PPC \u003d t + ? KPP \u003d 1.05 + 0.03 \u003d 1.08

Excess air coefficient for CE:

VE \u003d checkpoint + ? VE \u003d 1.08 + 0.02 \u003d 1.10

Excess air coefficient behind RAH:

RVP \u003d VE + ? RVP \u003d 1.10 + 0.2 \u003d 1.30

Characteristics of combustion products

Calculated value	Dimension	V°=9,5 2	V° H2O= 2 , 10	V° N2 = 7 , 6 0	V RO2=1, 04	V°g=10, 73
		G A Z O C O D S
		Firebox				Wow. gases
Excess air coefficient, ? ?
Excess air ratio, average? Wed
V H2O = V° H2O +0.0161* (?-1)* V°
V G \u003d V RO2 + V ° N2 + V H2O + (? -1) * V °
r RO2 \u003d V RO2 / V G
r H2O \u003d V H2O / V G
rn=rRO2 +rH2O

Theoretical amount of air

V ° \u003d 0.0476 (0.5CO + 0.575H 2 O + 1.5H 2 S + U (m + n / 4) C m H n - O P)

Theoretical volume of nitrogen

Theoretical volume of water vapor

Volume of triatomic gases

Enthalpies of combustion products (J - table).

J°g, kcal/nmі

J°v, kcal/nmі

J=J°g+(?-1)*J°v, kcal/nmі

Firebox

Outgoing gases

1, 09

1,2 0

1,3 0

4.Warmnew calculation of the boiler unit

4.1 Heat balance and fuel calculation

Calculated value	Designation	The size-ness	Formula or justification	Calculation
Thermal balance
Available heat of the fuel
Flue gas temperature
Enthalpy			By J-??table
Cold air temperature
Enthalpy			By J-??table
Heat loss:
From mechanical failure
from chemical injury			Table 4
with flue gases			(Jux-?ux*J°xv)/Q p p	(533-1,3090,3)100/8550=4,9
into the environment
The amount of heat loss
Boiler unit efficiency (gross)
Superheated steam flow
Superheated steam pressure behind the boiler unit
Superheated steam temperature behind the boiler unit
Enthalpy			According to the table XXVI(N.m.p.221)
Feed water pressure
Feed water temperature
Enthalpy			According to the table XXVII (N.m.p.222)
Purge water consumption				0,0150010 3 =5,0*10 3
Purge water temperature			t n at R b \u003d 156 kgf / cm 2
Enthalpy of blowdown water	ipr.v = i? KIP		According to the table XX1II (N.M.p.205)
Calculated value	Designation	Dimension	Formula or justification	Calculation

4.2 Regeinerative air heater

Calculated value	Designation	Dimension	Formula or justification	Calculation
Rotor diameter			According to design data
Number of air heaters per housing			According to design data
Number of sectors			According to design data	24 (13 gas, 9 air and 2 separation)
Fractions of the surface washed by gases and air

cold part
Equivalent Diameter			p.42 (Normal)
Sheet thickness			According to design data (smooth corrugated sheet)
			0.785Din 2 hgCr	0,7855,4 2 0,5420,80,81*3=26,98
			0.785Din 2 hvCr	0,7855,4 2 0,3750,80,81*3=18,7
Stuffing height			According to design data
Heating surface			According to design data
Inlet air temperature
Inlet air enthalpy			By J-? table
The ratio of air flow at the outlet of the cold part to the theoretical
Air suction
Outlet air temperature (intermediate)			Accepted provisionally
Outlet air enthalpy			By J-? table
			(in"hh+??hh) (J°pr-J°hv)	(1,15+0,1)*(201,67 -90,3)=139
Outlet gas temperature
Calculated value	Designation	Dimension	Formula or justification	Calculation
Enthalpy of gases at the outlet			According to J-? table
Enthalpy of gases at the inlet			Jux + Qb / c -?? xh * J ° xv	533+139 / 0,998-0,1*90,3=663
Inlet gas temperature			By J-? table
Average gas temperature
Average air temperature
Average temperature difference
Average wall temperature			(хг?ср+хвtср)/ (хг+хв)	(0,542140+0,37549)/(0,542+0,375)= 109
Average velocity of gases			(ВрVг(?av+273))/	(3704712,6747(140+273))/(293600273)=6,9
Average air speed			(Вр * Vє * (in "xh + xh / 2) * (tav + 273)) /	(370479,52(1,15+0,1)(49+273))/ (3600273*20,07)=7,3
		kcal / (m 2 * h * * hail)	Nomogram 18 SnSfSy*?n	0,91,241,0*28,3=31,6
		kcal / (m 2 * h * * hail)	Nomogram 18 SnS"fSy*?n	0,91,161,0*29,5=30,8
Utilization factor
Heat transfer coefficient		kcal / (m 2 * h * * hail)		0,85/(1/(0,54231,6)+1/(0,37530,8))=5,86
Thermal absorption of the cold part (according to the heat transfer equation)				5,86975091/37047=140
Thermal perception ratio				(140/ 139)*100=100,7

Calculated value	Designation	Dimension	Formula or justification	Calculation
hot part
Equivalent Diameter			p.42 (Normal)
Sheet thickness			According to design data
Clear area for gases and air			0.785Din 2 hgCrCl*n	0,7855,4 2 0,5420,8970,89*3=29,7
			0.785Din 2 hvKrKl*n	0,7855,4 2 0,3750,8970,89*3=20,6
Stuffing height			According to design data
Heating surface			According to design data
Air inlet temperature (intermediate)			Adopted in advance (in the cold part)
Inlet air enthalpy			By J-? table
Air suction
The ratio of air flow rates at the outlet of the hot part to the theoretical
Outlet air temperature			Accepted provisionally
Outlet air enthalpy			By J-? table
Heat absorption of the step (according to balance)			(v "gch +?? gch / 2) * * (J ° gv-J ° pr)	(1,15+0,1)*(806- 201,67)=755
Outlet gas temperature			From the cold part
Enthalpy of gases at the outlet			According to J-? table
Enthalpy of gases at the inlet			J?hch + Qb / c-??gch *	663+755/0,998-0,1*201,67=1400
Inlet gas temperature			By J-? table
Average gas temperature			(?"vp + ??xh) / 2	(330 + 159)/2=245
Average air temperature
Average temperature difference
Average wall temperature			(хг?ср+хвtср)	(0,542245+0,375164)/(0,542+0,375)=212
Average velocity of gases			(ВрVг(?av+273))	(3704712,7(245 +273)/29,73600273 =8,3
Calculated value	Designation	Dimension	Formula or justification	Calculation
Average air speed			(Вр * Vє * (in "vp + ?? hch (tav+273))/(3600273 Fv)	(370479,52(1,15+0,1)(164+273)/ /360020,6*273=9,5
Heat transfer coefficient from gases to the wall		kcal / (m 2 * h * * hail)	Nomogram 18 SnSfSy*?n	1,61,01,07*32,5=54,5
Heat transfer coefficient from wall to air		kcal / (m 2 * h * * hail)	Nomogram 18 SnS"fSy*?n	1,60,971,0*36,5=56,6
Utilization factor
Heat transfer coefficient		kcal / (m 2 * h * * hail)	o / (1/ (хг?гк) + 1/(хв?вк))	0,85/ (1/(0,54259,5)+1/0,37558,2))=9,6
Heat absorption of the hot part (according to the heat transfer equation)				9,63645081/37047=765
Thermal perception ratio				765/755*100=101,3
The values of Qt and Qb differ by less than 2%.

vp=330°С tdv=260°С

Jvp=1400 kcal/nm 3 Jgv=806 kcal/nm 3

hch=159°С tpr=67°С

Јhh \u003d 663 kcal / nm 3

Jpr \u003d 201.67 kcal / nm 3

ux=120°С txv=30°С

Јhv \u003d 90.3 kcal / nm 3

Jux \u003d 533 kcal / nm 3

4.3 Firebox

Calculated value	Designation	Dimension	Formula or justification	Calculation
Diameter and thickness of screen pipes			According to design data
			According to design data
The total surface of the walls of the furnace part			According to design data
The volume of the furnace part			According to design data
				3,6*1635/1022=5,76
The coefficient of excess air in the furnace
Air suction in the boiler furnace
hot air temperature			From the calculation of the air heater
Hot air enthalpy			By J-? table
The heat introduced by the air into the furnace			(?t-??t)* J°gw + +??t*J°hv	(1,05-0,05)806+0,0590,3= 811,0
Useful heat dissipation in the furnace			Q p p * (100-q 3) / 100 + Qv	(8550*(100-0,5)/100)+811 =9318
Theoretical combustion temperature			By J-? table
Relative position of the temperature maximum along the furnace height			xt \u003d xg \u003d hg / Ht
Coefficient			page 16 0.54 - 0.2*xt	0,54 - 0,2*0,143=0,511
			Accepted provisionally
			By J-? table
Average total heat capacity of combustion products		kcal/(nmі*deg)	(Qt- J?t)*(1+Chr)	(9318 -5 018 )*(1+0,1) (2084-1200) =5,35
Work		m*kgf/cm²		1,00,27985,35=1,5
Coefficient of attenuation of rays by triatomic gases		1/ (m ** kgf / / cm 2)	Nomogram 3
Optical thickness				0,380,27981,0*5,35=0,57
Calculated value	Designation	Dimension	Formula or justification	Calculation
Torch blackness			Nomogram 2
Thermal efficiency coefficient of smooth tube screens			shekr=x*f shek \u003d w at x \u003d 1 according to the table. 6-2
The degree of blackness of the combustion chamber			Nomogram 6
The temperature of the gases at the outlet of the furnace			Ta / [M * ((4.9 * 10 -8 * * shekr * Fst * at * Tai) / (ts * Вр*Vср)) 0.6 +1]-273	(2084+273)/-273=1238
Enthalpy of gases at the furnace outlet			By J-? table
The amount of heat received in the furnace				0,998*(9318-5197)=4113
Average heat load of the radiant-receiving heating surface			Vr*Q t l/Nl	37047*4113/ 903=168742
Thermal stress of the furnace volume			Vr*Q r n / Vt	37047*8550/1635=193732

4.4 Hotwirma

Calculated value	convoy- nache- nie	Dimension	Formula or justification	Calculation
Pipe diameter and thickness			According to the drawing
			According to the drawing
Number of screens			According to the drawing
Average step between screens			According to the drawing
Longitudinal pitch			According to the drawing
Relative pitch
Relative pitch
Screen heating surface			According to design data
Additional heating surface in the area of hot screens			According to the drawing	6,65*14,7/2= 48,9
Entrance window surface			According to the drawing	(2,5+5,38)*14,7=113,5
			Нin*(НшI/(НшI+HdopI))	113,5*624/(624+48,9)=105,3
			H in - H lshI
Clearance for gases			According to design data
Clear area for steam			According to design data
Effective thickness of the radiating layer			1.8 / (1/ A+1/ B+1/ C)
Inlet gas temperature			From the calculation of the furnace
Enthalpy			By J-? table
Coefficient
Coefficient
	kcal / (m 2 h)	c * w c * q l	0,61,35168742=136681
Radiant heat received by the plane of the inlet section of the hot screens			(q lsh * H in) / (Vr / 2)	(136681113,5)/ 370470,5=838


Calculated value	Designation	Dimension	Formula or justification	Calculation
The temperature of the gases at the outlet of the screens I and ?? steps			Accepted provisionally
			By J-? table
Average temperature of gases in hot screens				(1238+1100)/2=1069
Work		m*kgf/cm²		1,00,27980,892=0,25
			Nomogram 3
Optical thickness				1,110,27981,0*0,892=0,28
			Nomogram 2
			v ((th/S1)I+1)th/S1
			(Q l in? (1-a)?? C w) / in + + (4.9 * 10 -8 a * Zl.out * T cf 4 * op) / Vr * 0.5	(838 (1-0,245)0,065)/0,6+(4,910 -8 0,245(89,8)(1069+273) 4 0,7)/ 370470,5)= 201
Heat received by radiation from the furnace with screens of the 1st stage	Q LSHI + additional		Q l in - Q l out
			Q t l - Q l in
			(Qscreen?Vr) / D	(3912*37047)/490000=296
The amount of radiant heat received from the firebox by the screens			QlshI + extra* Nlsh I / (Nlsh I + Nl add I)	637*89,8/(89,8+23,7)= 504
			Q lsh I + add * H l add I / (N lsh I + N l add I)	637*23,7/(89,8+23,7)= 133
				0,998*(5197-3650)= 1544
Including:
actual screen			Accepted provisionally
additional surfaces			Accepted provisionally
			Accepted provisionally
enthalpy is there
Calculated value	Designation	Dimension	Formula or justification	Calculation
			(Qbsh + Qlsh) * Vr	(1092 + 27 2 ,0 )* 3 7047 *0,5
Enthalpy of steam at the outlet				747,8 +68,1=815,9
The temperature is there			Table XXV
Average steam temperature				(440+536)/2= 488
temperature difference
Average velocity of gases
				520,9850,6*1,0=30,7
Pollution factor		m 2 h deg/ /kcal
				488+(0,0(1063+275)33460/624)=
				2200,2450,985=53,1
Utilization factor
Heat transfer coefficient from gases to the wall				((30,73,140,042/20,04750,98)+53,1) *0,85= 76,6
Heat transfer coefficient				76,6/ (1+ (1+504/1480)0,076,6)=76,6
			k? НшI ??t / Вр*0.5	76,6624581/37047*0,5=1499
Thermal perception ratio			(Qtsh / Qbsh)??100	(1499/1480)*100=101,3
			Accepted provisionally
			k? NdopI ? (?avg?-t)/Br	76,648,9(1069-410)/37047=66,7
Thermal perception ratio	Q t add / Q b add		(Q t add / Q b add)?? 100	(66,7/64)*100=104,2

ValuesQtsh andQ

aQt additional andQ

4.4 Coldwirma

Calculated value	Designation	Dimension	Formula or justification	Calculation
Pipe diameter and thickness			According to the drawing
Number of pipes connected in parallel			According to the drawing
Number of screens			According to the drawing
Average step between screens			According to the drawing
Longitudinal pitch			According to the drawing
Relative pitch
Relative pitch
Screen heating surface			According to design data
Additional heating surface in the screen area			According to the drawing	(14,7/26,65)+(26,65*4,64)=110,6
Entrance window surface			According to the drawing	(2,5+3,5)*14,7=87,9
Radiation-receiving screen surface			Нin*(НшI/(НшI+HdopI))	87,9*624/(624+110,6)=74,7
Additional radiation receiving surface			H in - H lshI
Clearance for gases			According to design data
Clear area for steam			According to design data
Effective thickness of the radiating layer			1.8 / (1/ A+1/ B+1/ C)	1,8/(1/5,28+1/0,7+1/2,495)=0,892
The temperature of the gases at the outlet of the cold			Based on hot
Enthalpy			By J-? table
Coefficient
Coefficient
	kcal / (m 2 h)	c * w c * q l	0,61,35168742=136681
Radiant heat received by the plane of the entrance section of the screens			(q lsh * H in) / (Vr * 0.5)	(13668187,9)/ 370470,5=648,6
Correction factor for taking into account radiation to the beam behind the screens

Calculated value	Designation	Dimension	Formula or justification	Calculation
Temperature of gases at the inlet to cold screens			Based on hot
The enthalpy of gases at the outlet of the screens at the assumed temperature			J-table
The average temperature of the gases in the screens? Art.				(1238+900)/2=1069
Work		m*kgf/cm²		1,00,27980,892=0,25
Beam attenuation coefficient: by triatomic gases			Nomogram 3
Optical thickness				1,110,27981,0*0,892=0,28
Degree of blackness of gases in screens			Nomogram 2
Slope coefficient from the input to the output section of the screens			v ((1/S 1)І+1)-1/S 1	v((5.4/0.7)І+1) -5.4/0.7=0.065
Heat radiation from the furnace to the entrance screens			(Ql in? (1-a)?? tssh) / in + (4.9 * 10 -8 аZl.out(Тср) 4 op) / Вр	(648,6 (1-0,245)0,065)/0,6+(4,910 -8 0,245(80,3)(1069+273)4 0,7)/ 370470,5)= 171,2
Heat received by radiation from the furnace with cold screens			Ql in - Ql out	648,6 -171,2= 477,4
Heat absorption of combustion screens			Qtl - Ql in	4113 -171,2=3942
The increase in the enthalpy of the medium in screens			(Qscreen?Vr) / D	(3942*37047)/490000=298
The amount of radiant heat taken from the furnace by the entrance screens			QlshI + extra* Nlsh I / (Nlsh I + Nl add I)	477,4*74,7/(74,7+13,2)= 406,0
The same with additional surfaces			Qlsh I + add * Nl add I / (NlshI + Nl add I)	477,4*13,2/(74,7+13,2)= 71,7
Heat absorption of first stage screens and additional surfaces according to balance			c * (Ј "-Ј "")	0,998*(5197-3650)=1544

Calculated value	Designation	Dimension	Formula or justification	Calculation
Including:
actual screen			Accepted provisionally
additional surfaces			Accepted provisionally
Steam temperature at the outlet of the inlet screens			Based on weekends
enthalpy is there			According to table XXVI
Steam enthalpy increase in screens			(Qbsh + Qlsh) * Vr	((1440+406,0)* 37047) / ((490*10 3)=69,8
Steam enthalpy at the inlet to the inlet screens				747,8 - 69,8 = 678,0
Steam temperature at the entrance to the screen			According to table XXVI (P=150kgf/cm2)
Average steam temperature
temperature difference				1069 - 405=664,0
Average velocity of gases			In r? V g? (?av+273) / 3600 * 273* Fg	3704711,2237(1069+273)/(360027374,8 =7,6
Convection heat transfer coefficient				52,00,9850,6*1,0=30,7
Pollution factor		m 2 h deg/ /kcal
The temperature of the outer surface of the contaminants			t cf + (e? (Q bsh + Q lsh) * Vr / NshI)	405+(0,0(600+89,8)33460/624)=
Radiant heat transfer coefficient				2100,2450,96=49,4
Utilization factor
Heat transfer coefficient from gases to the wall			(? k? pd / (2S 2 ? x)+ ? l)?? ?	((30,73,140,042/20,04750,98)+49,4) *0,85= 63,4
Heat transfer coefficient			1 / (1+ (1+ Q ls / Q bs)?? ??? ? 1)	63,4/(1+ (1+89,8/1440)0,065,5)=63,4
Heat absorption of screens according to the heat transfer equation			k? НшI ??t / Вр	63,4624664/37047*0,5=1418
Thermal perception ratio			(Qtsh / Qbsh)??100	(1418/1420)*100=99,9
Average steam temperature in additional surfaces			Accepted provisionally
Calculated value	Designation	Dimension	Formula or justification	Calculation
Heat absorption of additional surfaces according to the heat transfer equation			k? NdopI ? (?avg?-t)/Br	63,4110,6(1069-360)/37047=134,2
Thermal perception ratio	Q t add / Q b add		(Q t add / Q b add)?? 100	(134,2/124)*100=108,2

ValuesQtsh andQbsh differ by no more than 2%,

aQt additional andQb additional - less than 10%, which is acceptable.

Bibliography

Thermal calculation of boiler units. normative method. Moscow: Energy, 1973, 295 p.

Rivkin S.L., Alexandrov A.A. Tables of thermodynamic properties of water and steam. Moscow: Energy, 1975

Fadyushina M.P. Thermal calculation of boiler units: Guidelines for the implementation of the course project in the discipline "Boiler plants and steam generators" for full-time students of the specialty 0305 - Thermal power plants. Sverdlovsk: UPI im. Kirova, 1988, 38 p.

Fadyushina M.P. Thermal calculation of boiler units. Guidelines for the implementation of the course project in the discipline "Boiler installations and steam generators". Sverdlovsk, 1988, 46 p.

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INFLUENCE OF STEAM LOAD OF RADIATION PROPERTIES OF THE TORCH IN THE BOILER FIRE CHAMBER

Mikhail Taimarov

dr. sci. tech., professor of the Kazan state energetic university,

Rais Sungatullin

high teacher of the Kazan state energetic university,

Russia, Republic of Tatarstan, Kazan

ANNOTATION

In this paper, we consider the heat flow from the flare during the combustion of natural gas in the TGM-84A boiler (station No. 4) of the Nizhnekamsk CHP-1 (NkCHP-1) for various operating conditions in order to determine the conditions under which the lining of the rear screen is the least susceptible to thermal destruction.

ABSTRACT

In this operation the heat flux from a torch in case of combustion of natural gas in the boiler TGM-84A (station No. 4) of Nizhnekamsk TETc-1 (NkTETs-1) for different regime conditions for the purpose of determination of conditions under which the brickwork envelope of the back screen is least subject to thermal corrupting is considered.

Keywords: steam boilers, heat flows, air swirling parameters.

keywords: boilers, heat fluxes, air twisting parameters.

Introduction.

The TGM-84A boiler is a widely used gas-oil boiler with relatively small dimensions. Its combustion chamber is divided by a two-light screen. The lower part of each side screen passes into a slightly inclined hearth screen, the lower collectors of which are attached to the collectors of the two-light screen and move together with thermal deformations during the firing and shutdown of the boiler. The inclined pipes of the hearth are protected from flare radiation by a layer of refractory bricks and chromite mass. The presence of a two-light screen provides intensive cooling of flue gases.

In the upper part of the furnace, the pipes of the rear screen are bent into the combustion chamber, forming a threshold with a projection of 1400 mm. This ensures the washing of the screens and their protection from direct radiation of the torch. Ten pipes of each panel are straight, do not have a protrusion into the furnace and are load-bearing. Screens are located above the threshold, which are part of the superheater and are designed to cool the combustion products and superheat the steam. The presence of a two-light screen, according to the designers' intention, should provide more intensive cooling of the flue gases than in the gas-oil boiler TGM-96B, which is similar in performance. However, the area of the heating screen surface has a significant margin, which is practically higher than that required for the nominal operation of the boiler.

The basic model TGM-84 was repeatedly reconstructed, as a result of which, as indicated above, the model TGM-84A (with 4 burners) appeared, and then TGM-84B. (6 burners). Boilers of the first modification TGM-84 were equipped with 18 oil-gas burners placed in three rows on the front wall of the combustion chamber. Currently, either four or six higher capacity burners are being installed.

The combustion chamber of the TGM-84A boiler is equipped with four KhF-TsKB-VTI-TKZ gas-oil burners with a unit capacity of 79 MW, installed in two tiers in a row with peaks on the front wall. Burners of the lower tier (2 pcs.) are installed at the level of 7200 mm, the upper tier (2 pcs.) - at the level of 10200 mm. Burners are designed for separate combustion of gas and fuel oil. The performance of the burner on gas 5200 nm 3 /hour. Kindling of the boiler on steam-mechanical nozzles. To control the temperature of the superheated steam, 3 stages of injection of its own condensate are installed.

The HF-TsKB-VTI-TKZ burner is a vortex dual-flow hot air burner and consists of a body, 2 sections of an axial (central) swirler and the 1st section of a tangential (peripheral) air swirler, a central installation pipe for an oil burner and an igniter, gas-distributing pipes . The main design (design) technical characteristics of the KhF-TsKB-VTI-TKZ burner are given in Table. one.

Table 1.

Basic design (design) specificationsburners HF-TsKB-VTI-TKZ:

Gas pressure, kPa
Gas consumption per burner, nm 3 / h
Thermal power of the burner, MW
Gas path resistance at rated load, mm w.c. Art.
Air path resistance at rated load, mm w.c. Art.
Overall dimensions, mm	3452x3770x3080
Total outlet section of the hot air channel, m 2
Total outlet section of gas pipes, m 2

Characteristics of air twist directions in HF-TsKB-VTI-TKZ burners are shown in fig. 1. The scheme of the twisting mechanism is shown in fig. 2. The layout of the gas outlet pipes in the burners is shown in fig. 3.

Figure 1. Scheme of burner numbering, air swirling in the burners and the location of the KhF-TsKB-VTI-TKZ burners on the front wall of the furnace of boilers TGM-84A No. 4.5 NkCHP-1

Figure 2. Scheme of the mechanism for the implementation of air twist in the burners KhF-TsKB-VTI-TKZ of boilers TGM-84A NkCHP-1

The hot air box in the burner is divided into two streams. An axial swirler is installed in the inner channel, and an adjustable tangential swirler is installed in the peripheral tangential channel.

Figure 3. Diagram of the location of the gas outlet pipes in burners KhF-TsLB-VTI-TKZ of boilers TGM-84A NkCHP-1

During the experiments, Urengoy gas was burned with a calorific value of 8015 kcal/m 3 . The technique of experimental research is based on the use of a non-contact method for measuring the incident heat fluxes from the torch. In experiments, the value of the heat flux incident from the torch on the screens q The drop was measured with a laboratory-calibrated radiometer.

Measurements of non-luminous combustion products in boiler furnaces were carried out in a non-contact way using a radiation pyrometer of the RAPIR type, which showed the radiation temperature. The error in measuring the actual temperature of non-luminous products at their exit from the furnace at 1100°C by the radiation method for calibrating RK-15 with a lens material made of quartz is estimated to be ± 1.36%.

In general, the expression for the local value of the heat flux incident from the torch on the screens q drop can be represented as a function of the real flame temperature T f in the combustion chamber and the emissivity of the torch α f, according to the Stefan-Boltzmann law:

q pad = 5.67 ´ 10 -8 α f T f 4, W / m 2,

where: T f is the temperature of the combustion products in the torch, K. The brightness degree of emissivity of the torch α λf = 0.8 is taken according to the recommendations.

The graph of the dependence on the influence of the steam load on the radiation properties of the flame is shown in Fig. 4. Measurements were taken at a height of 5.5 m through hatches No. 1 and No. 2 of the left side screen. It can be seen from the graph that with an increase in the steam load of the boiler, there is a very strong increase in the values of the falling heat fluxes from the torch in the area of the rear screen. When measuring through a hatch located closer to the front wall, there is also an increase in the values falling from the torch onto the heat flow screens with increasing load. However, in comparison with the heat fluxes at the rear screen, in terms of absolute value, the heat fluxes in the area of the front screen for heavy loads are on average 2 ... 2.5 times lower.

Figure 4. Incident heat flux distribution q pad according to the depth of the furnace, depending on the steam capacity D to according to measurements through hatches 1, 2 1st tier at the level of 5.5 m along the left wall of the furnace for boiler TGM-84A No. 4 NkCHP-1 at maximum air twist in the position of the blades in burners Z (the distance between hatches 1 and 2 is 6.0 m with a total depth of the furnace 7.4 m):

On fig. Figure 5 shows the graphs of the distribution of the incident heat flux q fall along the depth of the furnace, depending on the steam capacity D k, according to measurements through hatches No. 6 and No. 7 of the 2nd tier at an elevation of 9.9 m along the left wall of the furnace for the TGM-84A boiler No. 4 NKTES at maximum twist of air in the position of the blades in the burners 3 in comparison with the resulting heat flows according to measurements through hatches No. 1 and No. 2 of the first tier.

Figure 5. Incident heat flux distribution q pad according to the depth of the furnace, depending on the steam capacity D to according to measurements through hatches No. 6 and No. 7 of the 2nd tier at elev. 9.9 m along the left wall of the furnace for the TGM-84A boiler No. 4 of NKTEC at maximum air twist in the position of the blades in the burners H in comparison with the resulting heat flows according to measurements through hatches No. 1 and No. 2 of the first tier (distance between hatches 6 and 7 equals 5.5 m with a total furnace depth of 7.4 m):

Designations for the position of air swirlers in burners, adopted in this work:

Z - maximum twist, O - no twist, air goes without twist.

The index c is the central twist, the index p is the peripheral main twist.

The absence of an index means the same position of the blades for the central and peripheral twists (either both twists in the O position or both twists in the Z position).

From fig. 5 it can be seen that the highest values of heat flows from the torch to the screen heating surfaces take place, according to measurements through hatch No. 6 of the second tier, closest to the back wall of the furnace at around 9.9 m. At the mark of 9.9 m, according to measurements through hatch No. 6, growth heat fluxes from the torch occur at a rate of 2 kW/m2 for every 10 t/h increase in steam load, while for burner No. kW / m 2 for every 10 t / h increase in steam load.

The growth of heat fluxes falling from the torch to the rear screen, according to measurements through hatch No. 1 at the level of 5.5 m of the first tier, with an increase in the load of the TGM-84A boiler No. an increase in heat fluxes near the rear screen at around 9.9 m.

The maximum density of thermal radiation from the torch to the rear screen, as measured through hatch No. 6 at the level of 9.9 m, even at the maximum steam output of the TGM-84A boiler No. ) is on average 23% higher compared to the value of the radiation density from the torch at the rear screen at the level of 5.5 m, according to measurements through hatch No. 1.

The resulting heat flux obtained from measurements at the level of 9.9 m through hatch No. 7 of the second tier (closest to the front screen), with an increase in the steam load of the TGM-84A boiler No. air twist in the burners (position of the twist blades H) for every 10 t / h increases by 2 kW / m 2, i.e., as in the above case, according to measurements through hatch No. 6 closest to the rear screen at around 9.9 m.

The increase in the values of the falling heat fluxes, according to measurements through hatch No. 7 of the second tier at the level of 9.9 m, occurs with an increase in the steam load of the TGM-84A boiler No. 4 of the NCTPP from 230 t/h to 420 t/h for every 10 t/h at a rate of 4 .7 kW / m 2, i.e. 2.35 times slower in comparison with the growth of heat fluxes falling from the torch, according to measurements through hatch No. 2 at around 5.5 m.

Measurements of heat fluxes falling from the torch through hatch No. 7 at the level of 9.9 m at values of the boiler steam load of 420 t/h practically coincide with the values obtained during measurements through hatch No. 2 at the level of 5.5 m for conditions of maximum air swirl in the burners (position of the twisting blades H) of the TGM-84A boiler No. 4 of the NKTES.

Findings.

1. The influence of changes in the axial (central) twist of air in the burners on the value of heat flows from the torch, in comparison with the change in the tangential twist of air in the burners, is small and is more noticeable at the level of 5.5 m along section 2.

2. The highest measured flows occurred in the absence of tangential (peripheral) air twist in the burners and amounted to 362.7 kW / m 2, measured through hatch No. 6 at the level of 9.9 m at a load of 400 t / h. The values of heat fluxes from the torch in the range of 360 ... 400 kW/m 2 are dangerous when the furnace is operated with the direct throw of the torch onto the furnace wall from the firing side due to the gradual destruction of the inner lining.

Bibliography:

Garrison T.R. Radiation pyrometry. – M.: Mir, 1964, 248 p.
Gordov A.N. Fundamentals of pyrometry - M .: Metallurgy, 1964. 471 p.
Taimarov M.A. Laboratory workshop on the course "Boiler plants and steam generators". Textbook Kazan, KSEU 2002, 144 p.
Taimarov M.A. Study of the efficiency of energy facilities. - Kazan: Kazan. state energy un-t, 2011. 110 p.
Taimarov M.A. Practical training at the CHP. - Kazan: Kazan. state energy un-t, 2003., 90 p.
Thermal receivers of radiation. Proceedings of the 1st All-Union Symposium. Kyiv, Naukova Dumka, 1967. 310 p.
Shubin E.P., Livin B.I. Design of heat treatment plants for thermal power plants and boiler houses - M .: Energia, 1980. 494 p.
Trasition Metal Pyrite Dichaicogenides: High-Pressure Synthesis and Correlation of Properties / T.A. Bither, R.I. Bouchard, W.H. Cloud et al. // Inorg. Chem. - 1968. - V. 7. - P. 2208–2220.

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