Ministry of Energy and Electrification of the USSR
Main technical service management
Energy Systems
Typical energy characteristic
TGM-96B boiler when burning fuel oil
Moscow 1981.
This typical energy characteristic was developed by Soyucehenergo (Inzh. G.I. Gutsalo)
The standard energy characteristics of the TGM-96B boiler was prepared on the basis of thermal tests conducted by the Soyucenergo at the Riga CHP-2 and the Mediaztehenergo on CHP gas, and reflects the technically achievable cost of the boiler.
A typical energy characteristic can serve as a basis for compiling the regulatory characteristics of TGM-96B boilers when combing fuel oil.
1.1 . Copper TGM-96B Taganrog Boiler Plant - gas-gas with natural circulation and P-shaped layout, designed to work with turbinesT. -100 / 120-130-3 and PT-60-130 / 13. The main calculated parameters of the boiler when working on fuel oil are shown in Table. .
According to TKZ, the minimum allowable load of the boiler under the circulation condition is 40% nominal.
1.2 . The furnace chamber has a prismatic form and in the plan is a rectangle with dimensions of 6080 × 14700 mm. The volume of the furnace chamber is 1635 m 3. The thermal voltage of the flue volume is 214 kW / m 3, or 184 · 10 3 kcal / (m 3 · h). Evapory screens are placed in the furnace chamber and on the front wall Radiation Wall Steam Steaver (RNP). In the upper part of the furnace in the rotary chamber there is a wide steamer (SPP). In the lowered convective mine, two packages of the convective steamer (CAT) and a water economizer (VE) are located consistently along the gases.
1.3 . The steam path of the boiler consists of two independent streams with a pair of crossing between the side of the boiler. The temperature of the superheated steam is regulated by the injection of its own condensate.
1.4 . On the front wall of the furnace chamber there are four two-flow gas-tank burners HF CKB-WTI. The burners are installed in two tiers on -7250 and 11300 mm with an angle of lifting to the horizon 10 °.
For the combustion of the fuel oil, ferry mechanical nozzles "titanium" with a nominal capacity of 8.4 t / h at a pressure of the fuel oil 3.5 MPa (35 kgf / cm 2). Pressure pressure on purge and sprayed fuel oil is recommended by a 0.6 MPa plant (6 kgf / cm 2). The steam consumption on the nozzle is 240 kg / h.
1.5 . The boiler installation is equipped with:
Two blowing fans of VDN-16-P capacity with a reserve of 10% 259 · 10 3 m 3 / h, pressure with a reserve of 20% 39.8 MPa (398.0 kgf / m 2), 500/250 kW and rotation frequency 741 / 594 rpm of each machine;
Two smokers of DN-24 × 2-0.62 GM with a reserve with a reserve of 10% 415 · 10 3 m 3 / h, pressure with a reserve of 20% 21.6 MPa (216.0 kgf / m 2), with a capacity of 800/400 kW and rotation frequency of 743/595 rpm of each machine.
1.6 . For the cleaning of convective surfaces of heating from sediments of ash, the project is provided for a fractional installation, for cleaning RVP - water washing and blasting with a ferry from a drum with a decrease in pressure in the throttling unit. The duration of the blowing of one RVP 50 min.
2.1 . Typical energy characteristics of the TGM-96B boiler ( fig. , , ) Compiled on the basis of the results of thermal testing of boilers of the Riga CHP-2 and CHP gas in accordance with the instrumental materials and methodological instructions on the normalization of the feasibility of boilers. Characteristic reflects the average economy of the new boiler working with turbinesT. -100 / 120-130 / 3 and PT-60-130 / 13 at the following conditions adopted for the initial one below.
2.1.1
. In the fuel balance of power plants, burning liquid fuel, most of the fancy fuel oilM. 100. Therefore, the characteristic is composed of fuel oil.M 100 (GOST 10585-75 ) With characteristics:A p \u003d 0.14%, w p \u003d 1.5%, s p \u003d 3.5%, 
(9500 kcal / kg). All necessary calculations are made on the working mass of fuel oil.
2.1.2 . The temperature of the fuel oil in front of the nozzles is taken 120 °C ( t TL \u003d 120 ° C) based on the viscosity of fuel oilM. 100, equal to 2.5 ° W, according to § 5.41 PTE.
2.1.3 . The average annual temperature of cold air (t x.) At the entrance to the blowing fan is taken equal to 10 °C. Since mainly TGM-96B boilers are located in climatic areas (Moscow, Riga, Gorky, Chisinau) with an average annual air temperature close to this temperature.
2.1.4 . Air temperature at the entrance to the air heater (t VP) adopted equal to 70 °C. and constant when changing the load of the boiler, according to § 17.25 of the PTE.
2.1.5 . For power plants with transverse ties temperature nutrient water (t P.V.) Before the boiler is made calculated (230 ° C) and constant when the boiler load changes.
2.1.6 . The specific heat consumption of the net on the turbine installation is adopted 1750 kcal / (kWh), according to thermal tests.
2.1.7 . Coefficient heat flux Accepted varying with a load of the boiler from 98.5% at a rated load to 97.5% with a load of 0.6D Nom..
2.2 . The calculation of the regulatory characteristic was carried out in accordance with the instructions of the "thermal calculation of boiler aggregates (regulatory method)", (M.: Energy, 1973).
2.2.1 . The efficiency of the gross boiler and heat loss with outgoing gases is calculated in accordance with the method described in the book Ya.L. Pecker " Heat engineering calculations According to the above characteristics of fuel "(M.: Energy, 1977).
where
here
α Wow = α " VE. + Δ α Tr.
α Wow - the excess air coefficient in the outgoing gases;
Δ α Tr. - the gazes in the gas path of the boiler;
So uh - The temperature of the outgoing gases behind the smoke.
The calculation of the temperature of the outgoing gases, measured in the experiments of thermal testing of the boiler and the regulatory conditions given to the conditions for constructing the regulatory characteristics (input parameters
t X B., t "kf, t P.V.).2.2.2 . Outlet air coefficient of an airpoint (for a water economizer)α " VE. It is accepted equal to 1.04 on the rated load and varying to 1.1 by 50% load according to thermal tests.
The decrease in the calculated (1.13) coefficient of an excess of air for a water economizer to adopted in the regulatory characteristic (1.04) is achieved properly conducting the flue regime according to the boiler's regime map, compliance with the PTE requirements for air supplies in the furnace and the gas tract and the selection of the nozzles set .
2.2.3 . Air shocks in the gas path of the boiler on the rated load are taken equal to 25%. With a change in the load of the air supplies are determined by the formula
2.2.4 . Heat losses from chemical non-fuel combustion (q. 3 ) Accepted zero, since during the testing of the boiler in excess airs adopted in a typical energy characteristic, they were absent.
2.2.5 . Heat loss from mechanical fuel combustion (q. 4 ) Adopted equal zero in accordance with the "Regulations on the coordination of the regulatory characteristics of the equipment and the estimated specific costs of fuel" (M.: SNTTI OrGRES, 1975).
2.2.6 . Heat losses in the environment (q. 5 ) When testing were not determined. They are calculated in accordance with the "method of testing boiler installations" (M.: Energy, 1970) by the formula
2.2.7 . The specific consumption of electricity to the nutritious electric pump PE-580-185-2 was calculated using the characteristic of the pump accepted from technical Conditions Tu-26-06-899-74.
2.2.8 . The specific consumption of electricity on the thrust and blowing is calculated by electricity costs on the drive of blowing fans and the smoke, measured when conducting thermal tests and reduced to the conditions (Δ α Tr. \u003d 25%) adopted when drawing up the regulatory characteristics.
It has been established that with a sufficient density of the gas tract (Δ α ≤ 30%) The smokers provide a nominal load of the boiler at a low speed frequency, but without any stock.
Blowing fans on a low speed of rotation provide the normal operation of the boiler to loads 450 t / h.
2.2.9 . The total electrical power of the mechanisms of the boiler installation includes electric drive power: nutritional electric pump, smoke, fans, regenerative air heaters (Fig. ). The power of the electric motor of the regenerative air heater is accepted according to passport data. The power of electric motors of the smoke, fans and the nutritional electric pump is determined during the heat tests of the boiler.
2.2.10 . Specific heat consumption for air heating in the caloric installation is calculated with the heating of air in the fans.
2.2.11 . IN specific consumption Heat on the own needs of the boiler room installation includes heat losses in the COOD, the efficiency of which is taken by 98%; on steam blowing RVP and heat loss with vapor purge boiler.
Heat consumption for steam blowing RVP was calculated by the formula
Q hp = G PBD · i found · τ OBD · 10 -3. MW. (Gkal / Ch)
where G PBD \u003d 75 kg / min in accordance with the "Current standards of steam and condensate for their own needs of the power units 300, 200, 150 MW" (M.: SNTTI OrGRES, 1974);
i found = i. couple \u003d 2598 kJ / kg (kcal / kg)
τ OBD \u003d 200 min (4 apparatus with a rejoice duration of 50 min when turned on within 24 hours).
Heat consumption with the blowing of the boiler was calculated by the formula
Q Prod. = G Prod · i K.V. · 10 -3. MW. (Gkal / Ch)
where G Prod = PD Nome.10 2 kg / ch
P \u003d 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 tests were determined by the "method of testing boiler installations" (M.: Energy, 1970).
3.1 . To bring the basic regulatory indicators of the boiler to the changed conditions of its operation within the permissible limits of deviation of the parameter values, amendments in the form of graphs and digital values \u200b\u200bare given. Amendments K.q. 2 In the form of graphs, shown in Fig. , . Amendments to the temperature of the outgoing gases are shown in Fig. . In addition to those listed, amendments are presented to change the heating temperature of the fuel oil supplied to the boiler, and to change the temperature of the nutrient water.
3.1.1 . The amendment to change the temperature of the fuel oil supplied to the boiler is designed to influence the change TO Q.on the q. 2 by formula
Deciphering TGM - 84 - Taganrog gas-fledged boiler 1984 release.
The TGM-84 boiler is designed according to the P-shaped layout and consists of a flue chamber that is a rising gas duct, and a lower convective mine separated by two gas strokes.
The transitional horizontal gas duct between the furnace and the convective shaft is practically absent. In the top of the furnace and the rotary chamber there is a wide steamer. In a convective mine, divided into two gas strokes, placed consistently (along flue gases) Horizontal steamer and water economizer. The water economizer is a rotary chamber with anti-arriving bunkers.
Two included parallel regenerative air heater installed behind the convective shaft.
The furnace chamber has a conventional prismatic shape with dimensions between the axes of the pipes 6016 14080 mm and is divided into two half-blowing watercourse. The side and rear walls of the furnace chamber are shielded by evaporative pipes with a diameter of 60 6 mm (steel 20) in 64mm increments. The side screens in the lower part have the rods to the middle, at the bottom of the angle of 15 to the horizontal, and form "cold under.
The two-minute screen also consists of pipes with a diameter of 60 6 mm in 64mm increments and has windows formed by pipe wiring, to equalize the pressure in half-over. The on-screen system with the help of the thrust is suspended to the metal structures of the ceiling overlap and has the ability to freely drop down when thermal expansion.
The ceiling of the furnace chamber is made horizontal and shielded ceiling steamer pipes.
The furnace chamber is equipped with 18th fuel oil burnerswhich are located on the front wall in three tiers.
A drum is installed on the boiler internal diameter of 1800mm. The length of the cylindrical part is 16200 mm. In the boiler of the boiler, separation and flushing of a pair of nutrient water are organized.
The TGM-84 boiler operator in the nature of the heat perception of radiation-convective and consists of the three following main parts: radiation, shirm (or semiradiation) and convective.
The radiation unit consists of a wall and ceiling steamer.
Semiradiative steamer from 60 unified Shirm.
The convective horizontal type steamer consists of two parts placed in two risks of the lowered mine over a water economizer.
On the front wall of the heat chamber, a wall-mounted steamper washed, made in the form of six transportable blocks of pipes with a diameter of 42x5.5 mm (art. 12x1mf).
The ceiling superheater inlet camera consists of two welded collectors forming a common chamber one on each half-gun. The output chamber of the ceiling superheater is one and consists of six collectors' welded.
The input and output chamber of the wiring superheater is located one above the other and made of pipes with a diameter of 133x13 mm.
The convective steamer is made by Z - the figurative scheme, i.e. Couple comes from the front wall side. Each package consists of 4-axis coils.
The device for regulating the overheating temperature of the steam includes: condensation set and injection vaporoolels. Injecting steam detergents are installed in front of the screening steamers in the wiring dissection and in the dissection of the convective steamer. When the boiler is running on gas, all the steamers work, when working on fuel oil - only installed in the dissection of the convective steamer.
The steel coating of a water economizer consists of two parts placed in the left and right roshodes of the sink convective shaft.
Each part of the economizer consists of 4 packages in height. In each package, two blocks, in each block 56 or 54 of the four-day coil from the pipes with a diameter of 25x3.5 mm (Steel20). Snakes are located in parallel to the front of the boiler in a checkerboard with a step of 80mm. Economizer collectors are outwarded to the convective shaft.
On the boiler there are two regenerative rotating aircraft heater RVP-54. The air heater is carried out and is a rotating rotor, enclosed inside the fixed body. The rotation of the rotor is carried out by an electric motor with a gearbox with a speed of 3 rpm. The decrease in the cold air supplies into the air heater and air flows from the air side to the gas is achieved by installing radial and peripheral seals.
The boiler frame consists of metal columns associated with horizontal beams, farms and disclosures and serves to perceive loads from the weight of the drum, the surfaces of heating, irrigation, service platforms, gas-producing and other elements of the boiler. The frame is made welded from profile rental and sheet steel.
To clean the surfaces of the convective steamer and water economizer, a shot blasting unit is used, in which the kinetic energy is used freely falling crushing, with a size of 3-5 mm. Gas pulse cleaning can also be used.
Compiler: M.V. Kalmykov UDC 621.1 Design and operation of the Boiler TGM-84: Method. Decree / Samar. State tehn un-t; Cost. M.V. Kalmykov. Samara, 2006. 12 s. Considered mains specifications, layout and description of the design of the TGM-84 boiler and the principle of its work. The drawings of the layout of the boiler unit with auxiliary equipment are given, general view Boiler and its nodes. A diagram of the steaming path of the boiler and the description of its work is presented. Methodical instructions are designed for students of the specialty 140101 "Heat electric stations". Il. 4. Bibliogr.: 3 Names. Printed by the decision of the editorial-publishing council SamgTa 0 The main characteristics of the boiler unit Boiler aggregates TGM-84 are designed to obtain steam high pressure When burning gaseous fuel or fuel oil and are designed for the following parameters: Rated steam output ..................................................................................................................... Working For main vapor latch ................ The temperature of the superheated pair .............................................. The temperature of the nutrient water ............................................. The temperature of hot air a) when burning fuel oil ................................................ b) when burning gas .................................................... 420 t / h 155 Ata 140 Ata 550 ° C 230 ° C 268 ° C 238 ° C Boiler unit TGM-84 vertically water-tube, single-backed, puppy layout, with natural circulation. It consists of a flue chamber, which is the ascending gas duct and the lowered convective shaft (Fig. 1). The cooler is divided by a two-switch screen. The lower part of each side screen goes into a slightly inclined sublict screen, the lower collectors of which are attached to the reservoirs of the two-fold screen and are jointly moved with heat deformations during extracts and boiler stops. The presence of a two-fold screen provides more intensive cooling of the fuel gases. Accordingly, the thermal voltage of the flue volume of this boiler was chosen significantly higher than in dust aggregates, but lower than in other sizes of gas-contained boilers. This was facilitated by the working conditions of the pipes of the two-shield, which perceive the greatest amount of heat. In the upper part of the furnace and in the rotary chamber there is a semi-radiative wide steamer. In a convective mine, a horizontal convective steamer and a water economizer are placed. The water economizer has a camera with adopted shotgun bunkers. Two inclied parallel regenerative air heater rotating type RVP-54 are installed after a convective mine. The boiler is equipped with two blowing fans of type VDN-26-11 and two D-21 smoke. The boiler was repeatedly subjected to reconstruction, as a result of which the model TGM-84A appeared, and then TGM-84B. In particular, unified scrolls were introduced and a more uniform distribution of steam between the pipes was achieved. A transverse pitch of pipes was increased in horizontal packages of the convective part of the steam-1 of the superheater, thereby decreased the likelihood of its pollution of fasonry. 2 0 p and s. 1. Longitudinal and transverse sections of the gas-gas boiler TGM-84: 1 - heat chamber; 2 - burners; 3 - drum; 4 - shirma; 5 - convective steamer; 6 - condensation installation; 7 - Economyzer; 11 - shotgun; 12 - Remote separation cyclone The boilers of the first modification of TGM-84 were equipped with 18 gas-gas burners placed in three rows on the front wall of the fiber chamber. Currently establish either four or six burners greater performance, which simplifies the maintenance and repair of boilers. The burner devices The furnace chamber is equipped with 6 gas-gas burners installed in two tiers (in the form of 2 triangles in a row, vertices up, on the front wall). The burners of the lower tier are set at a mark of 7200 mm, the upper tier at a mark of 10200 mm. The burners are designed for separate burning of gas and fuel oil, vortex, single-threaded with central gas distribution. The extreme burners of the lower tier are unfolded towards the axis of the semi-powder by 12 degrees. To improve the mixing of fuel with air, the burners have guides, passing that the air is spinning. On the axis of burners on the boilers, fuel oil nozzles with a mechanical spray, the length of the fuel oil nozzle is 2700 mm. The design of the furnace and layout of the burner should provide a steady combustion process, its control, and also exclude the possibility of forming poorly ventilated zones. Gas burners must work steadily, without separation and sprinkle of the torch in the heat load range of the boiler. Applied to bolers gas-burners Must be certified and to have passports of factory producers. The coaching chamber The prismatic chamber is divided into two half-windows. The volume of the furnace chamber is 1557 m3, the heat voltage of the flue volume is 177,000 kcal / m3 ּ hour. The side and rear walls of the chamber are shielded by evaporative pipes with a diameter of 60 × 6 mm in 64 mm increments. The side screens in the lower part have slopes to the middle of the furnace with a slope of 15 degrees to the horizontal and form under. In order to avoid the bundle of a steam mixture in a slightly blocker to horizontal pipes, the portions of the side screens forming under, coated with chamoten brick and chromite mass. The on-screen system with the help of the thrust is suspended to the metal structures of the ceiling overlap and has the ability to freely drop down when thermal expansion. Pipes of evaporative screens were welded with each other with a rod of D-10 mm with an interval at a height of 4-5 mm. To improve the aerodynamics of the top of the furnace chamber and protect the rear screen cameras from radiation, the rear screen pipes in the upper part form a protrusion into the firebox with a departure of 1.4 m. The protrusion is formed by 70% of the rear screen pipes. 3 In order to reduce the influence of uneven heating on circulation, all screens are partitioned. Two-minute and two side screens have three circulation circuits, rear - six. TGM-84 boilers operate on a two-stage evaporation scheme. The first step of evaporation (pure compartment) includes drums, rear panels, two-sweat screens, 1st and 2nd from the front of the side screens panel. The second stage of evaporation (salt compartment) includes 4 remote cyclones (two on each side) and third on the front of the side screens panel. To six lower rear screen cameras, water from the drum is supplied by 18 water pipes, three to each collector. Each of the 6 panels includes 35 on-screen pipes . The upper ends of the pipes are connected to the cameras, of which the steam mixture comes through 18 pipes into the drum. The two-shield screen has windows formed by laying pipes to equalize the pressure in the half-gun. To the three lower chambers of the two-fold screen, water from the drum comes through 12 water pipes (4 pipes per collector). The extreme panels have 32 on-screen pipes, medium - 29 pipes. The upper ends of the pipes are connected to the three top cameras, of which the steam mixture of 18 pipes is sent to the drum. To the four front bottom collectors of the side screens, water comes from the drum over 8 water pipes. Each of these panels contains on the 31st screen tube. The upper ends of the on-screen pipes are connected to 4-chambers, of which the steam mixture falls into the drum along 12 pipes. The lower chambers of salt compartments are powered by 4 remote cyclones in 4 water pipes (from each cyclone on one pipe). Packs of salt compartments contain 31 on-screen pipes. The upper ends of the on-screen pipes are connected to the chambers, of which the steam-cutting mixture of 8 pipes enters 4 remote cyclones. The drum and the separation device of the drum has an inner diameter of 1.8 m, length of 18 m. All the drums are made of sheet steel 16 Gnm (manganese-nickemolybdenum steel), the thickness of the wall is 115 mm. The weight of the drum is about 96600 kg. The boiler drum is designed to create a natural circulation of water in the boiler, cleaning and separating the steam obtained in the on-screen pipes. The drum was organized separation of a steaming mixture of the 1st stage of evaporation (separation of the 2nd evaporation stage was performed on boilers in 4 out-of-wear cyclones), flushing of the entire steam is carried out by feed water, followed by the capture of moisture from steam. The entire drum is a pure compartment. A steaming mixture from the upper collectors (except for collectors of salt compartments) enters the drum on both sides and enters a special sinking box, from which it is sent to cyclones, where the initial separation of steam from water occurs. In the borants of the boilers, 92 cyclone was installed - 46 left and 46 right. 4 At the exit of steam from cyclones, horizontal plate separators are installed, steam, passing them, enters the barbaste-washing device. Here, under the flushing device of the pure compartment, pairs of remote cyclones were tested, inside which the separation of the steam mixture is also organized. Couple, having passed a barbages and flushing device, enters a holey sheet, where the steam separation and the leveling of the flow occurs simultaneously. Passing a hole leaf, couples 32 steaming pipes are allocated to the input chambers of the wall-mounted steam steamper and 8-pipes to the condensate installation. P and s. 2. Two-stage evaporation scheme with remote cyclones: 1 - drum; 2 - remote cyclone; 3 - lower collector of the circulation circuit; 4 - steam generating pipes; 5 - sink pipes; 6 - supply of nutrient water; 7 - removal of purge water; 8 - water supply tube from drum in cyclone; 9 - par pilot tube from cyclone in the drum; 10 - a steaming pipe from the unit on a barbage-washing device is fed about 50% of the nutrient water, and the rest of it through the distribution collector merges into the drum under the water level. The average water level in the drum is 200 mm below its geometric axis. Permissible level fluctuations in the drum of 75 mm. For the alignment of the saline in salt compartments of the boilers, two waterproof pipes are made, so the right cyclone nourishes the left bottom collector of the salt compartment, and the left nourishes right. 5 The design of the surface of the heating surface of the steamer is placed in a float chamber, a horizontal gas duct and a sink mine. The steamer scheme is made of two-way with repeated stirring and a steam transfer along the width of the boiler, which makes it possible to align thermal sprinkle for individual coins. By the nature of the heat perception, the steamer is conditionally divided into two parts: radiation and convective. The radiation part includes a wall-mounted steamer (NPP), the first series of ShirM (SPP) and a portion of the ceiling steamer (PPP), shielding the ceiling of the coaming chamber. By convective - the second series of shirm, part of the ceiling steamer and convective steamer (PPC). Radiation Wall-mounted NPP Pipe Steamer Shielded Front Wall of the Floor Camera. The NPP consists of six panels, two of them have 48, and the remaining 49 pipes, the step between the pipes is 46 mm. In each panel 22 pipes are lowered, the rest of the lifting. Input and output collectors are located in a non-heated zone above the heat chamber, intermediate collectors - in a non-heated zone below the heat chamber. The upper chambers with the help of thrust are suspended with the ceiling overlap metal structures. The fastening of pipes is carried out in 4 tiers in height and allows vertical movement of panels. Ceiling superheater The ceiling steamer is located above the furnace and horizontal gas duct, consists of 394 pipes placed in 35 mm increments and connected input and output collectors. Shirm Steam-Steel Warmer Steamer consists of two rows of vertical shutters (30 shirm in each row) located in the upper part of the heat chamber and the swivel gas duct. Step between shirms 455 mm. Shirma consists of 23 coils of the same length and two collectors (input and output), installed horizontally in a non-heated zone. Convective steamer Convective horizontal type steamer, consists of the left and right parts located in the gas duct of the hydrocarbon mine over a water economizer. Each party in turn is divided into two straight-flow steps. 6 Steam path of the boiler The saturated pairs of the boiler of the boiler on 12 steamed pipes enters the upper collectors of the NPP, of which 6 panels are moving down and enters 6 bottom collectors, after which it rises up extreme pipes 6 panels to the top Collectors, of which on 12-reheated pipes are sent to the input collectors of the ceiling steamer. Next, steam across the entire width of the boiler moves along the ceiling pipes and enters the output collectors of the steamer, located at the rear wall of the convective gas plant. From these collectors, steam is divided into two streams and is sent to the chambers of the steamers of stage I, and then in the chambers of the extreme shots (7 left and 7 right), passing which both streams of steam fall into intermediate steamers of stage II, left and right. In steamers I and II, steam steam are transferred from the left side to the right and, on the contrary, in order to reduce thermal reassembly caused by gas bumps. Coming out of the intermediate vaporochlastors of the II injection, the pairs enters the medium-sized collectors (8 left and 8 right), passing which is sent to the PPC input chambers. Between the upper and lower parts of the gearbox, steamers of stage III are installed. Next, overheated steam on steam pipeline is sent to turbines. P and s. 3. Boiler steamer scheme: 1 - boiler drum; 2 - radiation two-way radiation tube panel (left conditionally shown upper collectors, and on the right - lower); 3 - ceiling panel; 4-lady pairoker; 5 - water injection location in pairs; 6 - extreme screens; 7 - average screen; 8 - convective packages; 9 - Couple out of boiler 7 Condensate installation and injection steamers To obtain your own condensate on the boiler, 2 condensate installations are installed (one on each side) located on the ceiling overlap of the boiler over the convective part. They consist of 2 distributing collectors, 4 capacitors and condensate collectors. Each condenser consists of a chamber D426 × 36 mm. The cooling surfaces of the capacitors are formed by pipes welded to the tubular board, which is divided into two parts and forms a drainage and water supply chamber. A saturated pair of boiler drum on 8 pipes is sent to four distributing collectors. Each collector pairs are allocated to two capacitors of pipes of 6 tubes to each condenser. The condensation of a saturated steam coming from the boiler borax is made by cooling it with nutrient water. Nutrient water after a suspended system is fed to the water-powered chamber, passes through the tubes of capacitors and goes into the drainage of the chamber and further to the water economizer. A saturated steam received from the drum fills the steam space between the pipes, comes into contact with them and condenses. The resulting condensate on the 3rd tubes from each condenser enters two collections, from there through regulators is supplied to the pairochholders I, II, III of the left and right injections. Condensate injection occurs at the expense of the head of the spelling out of the difference in the Venturi tube and the pressure drop in the steam path of the steamer from the drum to the injection site. Condensate is injected into the cavity of the tube "Venturi" through 24 holes with a diameter of 6 mm, located around the circle in a narrow place of the pipe. The Venturi tube at full load on the boiler reduces the pair pressure by increasing its speed at the injection site by 4 kgf / cm2. The maximum capacity of one capacitor at 100% load and calculated parameters of steam and nutrient water is 17.1 t / h. Water economizer steel coating water economizer consists of 2 parts placed respectively in the left and right side of the sink shaft. Each part of the economizer consists of 4 blocks: lower, 2 medium and top. In height between blocks made openings. Water economizer consists of 110 packages of coils located in parallel to the front of the boiler. The coils in the blocks are located in a checkerboard with a step of 30 mm and 80 mm. Medium and upper blocks are installed on the beams located in the gas duct. To protect against the gas medium, these beams are covered with insulation protected by metal sheets with a thickness of 3 mm from the effects of the shot blasting. Lower blocks with racks suspended to beams. Racks allow removing the package of coils during repair. 8 The inlet and output chambers of the water economizer are located outside the gas ducts and brackets attached to the boiler frame. Cooling the beams of a water economizer (the temperature of the beams during trails and during operation should not be more than 250 ° C) due to the supply of cold air from the head of blowing fans, with air discharge into suction box of blowing fans. The air heater in the boiler room was installed two regenerative air heater RVP-54. The RVP-54 regenerative air heater is a countercurrent heat exchange unit consisting of a rotator rotor concluded inside a fixed body (Fig. 4). The rotor consists of a shell with a diameter of 5590 mm and a height of 2250 mm made from sheet steel with a thickness of 10 mm and a hub with a diameter of 600 mm, as well as connecting the hub with a shell of radial ribs separating the rotor on 24 sectors. Each sector is divided by vertical sheets on P and C. 4. Constructive diagram of regenerative air heater: 1 - box; 2 - drum; 3 - body; 4 - packing; 5 - shaft; 6 - Bearing; 7 - seal; 8 - electric motor three parts. They are stacked by the sections of the heating sheets. In the height of the section are installed in two rows. The upper row is a hot part of the rotor, made of distinguishing and corrugated sheets, 0.7 mm thick. The lower series of sections is a cold part of the rotor and is made of distinguishing direct sheets, 1.2 mm thick. The cold part is more susceptible to corrosion and can be easily replaced. Inside the hub of the rotor passes a hollow tree, having a flange on the bottom, which relies the rotor, the hub is attached to the flange with studs. RVP has two covers - the upper and lower, they have sealing plates. 9 The heat exchange process is carried out by heating the rotor packing in the gas stream and its cooling in the air flow. The sequential movement of the heated gas flow to the air is carried out due to the rotation of the rotor with a frequency of 2 turns per minute. At each moment of time, from 24 sectors of the rotor 13 sectors included in the gas tract, 9 sectors - in the air tract, two sectors are turned off and overlapped with sealing plates. In the air heater, the principle of counterflow is carried out: the air is entered from the outlet side and is removed from the part side of the gases. The air heater is designed for heating air from 30 to 280 ° C when the gases are cooling from 331 ° C to 151 ° C when working on fuel oil. The advantage of regenerative air heaters is their compactness and a small mass, the main disadvantage is a significant air punch from the air side into the gas (regulatory air suppression 0.2-0.25). The frame of the boiler The boiler frame consists of steel columns associated with horizontal beams, farms and disconsets, and serves to perceive loads from the weight of the drum, all surfaces of heating, condensate installation, irrigation, insulation and maintenance sites. The frame of the boiler is made by welded from profile rental and sheet steel. The columns of the frame are attached to the underground reinforced concrete foundation of the boiler, the base (shoe) columns are poured with concrete. Cutting Camera icing consists of refractory concrete, collateral plates and sealing magnesiac coating. Claiming thickness 260 mm. It is installed in the form of shields that are attached to the boiler frame. Ceiling icon consists of panels, 280 mm thick, freely lying on the pipes of the steamer. The structure of the panels: a layer of refractory concrete with a thickness of 50 mm, a layer of thermal insulation concrete with a thickness of 85 mm, three layers of constructing plates, a total thickness of 125 mm and a layer of sealing magnesial coating, a thickness of 20 mm applied to a metal grid. The irrigation of the rotary chamber and the convective mines are attached on the shields, which in turn are attached to the boiler frame. The overall thickness of the rotary chamber is 380 mm: refractory concrete - 80 mm, thermal insulation concrete - 135 mm and four layers of context plates of 40 mm. The convection of the convective steamer consists of one layer of thermal insulation concrete with a thickness of 155 mm, a layer of refractory concrete - 80 mm and four layers of collateral plates - 165 mm. Between the plates is a layer of suspended mass10 ticks 2 ÷ 2.5 mm thick. The watelling of the water economizer with a thickness of 260 mm, consists of refractory and thermal insulating concrete and three layers of collateral plates. Safety measures The operation of boiler aggregates should be made in accordance with the applicable "Devices of the device and safe operation Steam and hot water boilers, approved by Rostekhnadzor and "technical requirements for explosion safety of boiler plants working on fuel oil and natural gas", as well as operating "safety regulations for maintenance of power plants of power plants". Bibliographic list 1. Instructions for the operation of the energy boiler TGM-84 CHP VAZ. 2. Maclar M.V. Modern boiler aggregates TKZ. M.: Energia, 1978. 3. Kovalev A.P., Leleev N.S., Vilensky T.V. Steam generators: Tutorial for universities. M.: Energoatomizdat, 1985. 11 Design and work of the Boiler TGM-84 Compiler Kalmykov Maxim Vitalevich Editor N.V. In the e p and n and n and technical editor of G.N. W and H L to about and signed in print 06/20/06. Format 60 × 84 1/12. Offset paper. Print offset. Usl.l. 1.39. Sl.Kr.-Ott. 1.39. Ud. l. 1.25 Circulation 100. S. - 171. ____________________________________________________________________________________________________________________________________ State educational institution of higher vocational education "Samara State Technical University" 432100. Samara, ul. Young Guard, 244. Main Corps 12
0Course project
Task for the course project ...........................................................................
2.1. The composition of the fuel .........................................................................
2.2. Calculation of volumes and enthalpium products of combustion ..............................
2.3. Estimated thermal balance and fuel consumption ..................................
2.4. Calculation of the furnace chamber .................................................................................
2.5. Calculation of boiler steamers ................................................ ..
2.5.1 Calculation of a wall-mounted steamer ............................... .......
2.5.2. Calculation of the ceiling superheater ........................ .. ..........
2.5.3. Calculation of the wired steamer .....................................
2.5.4. Calculation of the convective steamer ..................... .. ..........
2.6. Conclusion ......................................................................................... ..
The task
It is necessary to produce calibration thermal calculation of the TGM-84 of the E420-140-565 brand.
In the calibration thermal calculation according to the adopted design and the size of the boiler for the specified load and the type of fuel, the water temperatures, steam, air and gases are determined at the boundaries between the individual heating surfaces, the efficiency, fuel consumption, consumption and velocity of steam, air and flue gases.
Calculation Calculation is made to assess the indicators of the cost-effectiveness and reliability of the boiler when working on a given fuel, identifying the necessary reconstructive activities, the choice of auxiliary equipment and the preparation of the source materials for the calculations: aerodynamic, hydraulic, metal temperature, pipe strength, the intensities of the hydraulic wear of pipes, corrosion, etc. .
Initial data:
1. The foundation of the TGM-84 steam boiler and the basic parameters.
Boiler units of the TGM-84 series are designed to obtain a high pressure steam when combing fuel oil or natural gas.
All TGM-84 series boilers have a P-shaped layout and consist of a flue chamber, which is a rising gas duct, and a lower convective mine, connected in the upper part with a horizontal gas duct.
Evapory screens and radiation wall steam steampers are placed in the furnace chamber. In the upper part of the furnace (and in some modifications of the boiler and in the horizontal gas duct) there is a wide steamer. In a convective mine, a convective (in the course of gases) contains a convective steamer and a water economizer. A convective mine after a convective superheater is divided into two gas strokes, each of which is one stream of water economizer. For a water economizer, the gas duct makes a turn at the bottom of which bins for ash and fractions are installed. Regenerative rotating air heaters are installed behind a convective mine outside the boiler house.
1.1. Floor chamber.
The furnace chamber has a prismatic shape and in terms of rectangle size: 6016x14080 mm. The side and rear walls of the furnace chamber of all types of boilers are shielded by evaporative pipes with a diameter of 60x6 mm in a step of 64 mm made of steel 20. The radiation steamer is placed on the front wall, the design of which is described below. The two-minute screen divides the filling chamber into two semi-furnaces. The double-screen screen consists of three panels and is formed by pipes with a diameter of 60x6 mm (steel 20). The first panel consists of twenty-six pipes with a pitch between pipes 64 mm; The second panel is from twenty-eight pipes with a step between pipes 64 mm; The third panel is from twenty nine pipes, the step between the pipes is 64 mm. The input and output reservoirs of the two-windscreen are made of pipes with a diameter of 273x32 mm (Steel20). The two-minute screen with the help of the thrust is suspended with the ceiling overlap metal structures and has the ability to move at a temperature expansion. In order to align the pressure on half-blowing in a two-fold screen, there are windows formed by pipe wiring.
Side and rear screens are made structurally identical for all types of TGM-84 boilers. The side screens at the bottom form the cold funnels with a slope of 15 0 to the horizontal. With the fir side, the pipe pipes are closed with a layer of chamotte brick and a layer of chromite mass. In the upper and lower parts of the heat chamber, side and rear screens are connected to collectors with a diameter of 219x26 mm and 219x30 mm, respectively. The upper rear screen collectors are made of pipes with a diameter of 219x30 mm, the bottom of the pipes with a diameter of 219x26 mm. Screen collector material - steel 20. Submission of water to collectors of screens is carried out by pipes with a diameter of 159x15 mm and 133x13 mm. The cutting machine washed with pipes with a diameter of 133x13 mm. Pipes of screens are attached to the beams of the boiler frame to prevent the brass in the furnace. The side screens and two-fold screen have four fastener tiers, the rear screen panels are three tiers. The suspension of the panels of the fiber screens is carried out using the thrust and allows vertical movement of pipes.
Pasteing of pipes in the panels is carried out by welded rods with a diameter of 12 mm, a length of 80 mm, the material - steel 3kp.
In order to reduce the effect of uneven heating on circulation all the screens of the heat chamber are partitioned: Pipes with collectors are made in the form of a panel, each of which is a separate circulation circuit. In total, there are fifteen panels in the furnace: the rear screen has six panels, two-time and each side screen three panels. Each rear screen panel consists of thirty-five evaporative pipes, three water-powered and three drainage pipes. Each side screens panel consists of thirty-one evaporative pipes.
In the upper part of the heat chamber, there is a protrusion (in the depth of the furnace), formed by the rear screen pipes, which contributes to the best wash with smoke gases of the wiring part of the steamer.
1.2. Umbrane devices.
1 - Digit order; 2 - the box of cyclone; 3 - blunt box; 4 - cyclone; 5 - pallet; 6 - emergency plum pipe; 7 - the phosphating manifold; 8 - collector of steam heating; 9 - leaf hole ceiling; 10 - nutritious pipe; 11 - sheet of barber.
On this boiler, TGM-84 uses a two-stage evaporation scheme. The drum is a pure compartment and is the first step of evaporation. The drum has an inner diameter of 1600 mm and made of steel 16GNM. The wall thickness of the drum is 89 mm. The length of the cylindrical part of the drum is 16200 mm, the total length of the drum is 17990 mm.
The second stage of evaporation is remote cyclones.
A steamwatering mixture of steam pipes enters the boiler drum - into the distribution boxes of cyclones. In cyclones, a pair of water is separated. Water from cyclones merges into pallets, and the separated pa vapor enters the flushing device.
Washing steam is carried out in a layer of nutrient water, which is supported on a hole sheet. Couple passes through the holes in the hole sheet and barbatches through a layer of nutrient water, freeing from the salts.
Distributing boxes are located above the washing device and have in their lower part of the water drain.
The average water level in the drum is below the geometric axis by 200 mm. On waterproof devices, this level is accepted for zero. The highest and lower levels are respectively lower and higher from the average to 75 m. To prevent the copper of the boiler in the drum, an emergency drain pipe is installed, which allows you to drop an excessive amount of water, but not greater than the average level.
For processing boiler water with phosphates, a pipe is installed in the lower part of the drum, through which phosphates are introduced into the drum.
At the bottom of the drum there are two collectors of steam heating of the drum. In modern steam boilers They are used only for accelerated drum dropping when the boiler is stopped. Maintaining the relationship between the body temperature of the Top-Ben Body is achieved by regime measures.
1.3. Superheater.
The surfaces of the superheater on all boilers are placed in a fire chamber, a horizontal gas duct and a convective mine. By the nature of the heat-perception, the steamer is divided into two parts: radiation and convective.
The radiation part includes a radiation-wall superheater (NPP), the first stage of the Shirm and part of the ceiling steamer, located above the heat chamber.
The convective part belongs to the part of the wide superheater (which does not receive directly radiation from the furnace), the ceiling superheater and the convective steamer.
The steamer scheme is made of two-way with repeated stirring of steam inside each thread and a steam transfer along the width of the boiler.
Schematic diagram of steps.
1.3.1. Radiation steamer.
On the boilers of the TGM-84 series, the pipes of the radiation operator shields the front wall of the flue chamber from a mark of 2000 mm to 24600 mm and consist of six panels, each of which is an independent circuit. Pipes panels have a diameter of 42x5 mm, made of steel 12x1mf, installed in a step of 46 mm.
In each panel, twenty-two pipes are lowered, the rest are lifting. All panel collectors are located outside the heated zone. Upper collectors with the help of thrust are suspended with ceiling overlap metal structures. The fastening of pipes in the panels is carried out by distinguishing placas and welded rods. In the panels of the radiation superheater, there are wiring for the installation of burners and layout under the lazium and luch-glades.
1.3.2. Ceiling steamer.
The ceiling steamer is located above the heat chamber, horizontal gas duct and convective shaft. The ceiling on all boilers made of pipes with a diameter of 32x4 mm in the amount of three hundred ninety-four pipes placed in 35 mm increments. The mounting of the ceiling pipes is made as follows: rectangular strips are welded in one end to the pipes of the ceiling steamer, to others - to special beams, which are suspended with the help of the ceiling overlap. The length of the ceiling pipes has eight rows of fasteners.
1.3.3. Shirm Steamer (SPP).
On the boilers of the TGM-84 series, two types of vertical shirms are installed. Screenshots U-shaped with coils of different lengths and unified shirms with coils of the same length. Shirms are installed in the top of the furnace and in the output windows of the furnace.
On fuel oil boilers, U-shaped shirms are installed in one or two rows. Unified shirms in two rows are installed on gas-gas boilers.
Inside each U-shaped screen - forty-one serpentine, which are installed in 35 mm increments, in each of the series eighteen shirm, between shirms step 455 mm.
The step between coils inside the unified Shirm 40 mm, in each of the series it is set to thirty-wide shirms, each twenty-three coils. The remantization of coils in Shirma is carried out using a comb and clamps, in some structures - welded rods.
The Suspension of the wiring steamer is carried out to the ceiling metal structures using the collectors welded to the ears. In the case when the collectors are located one over the other, the lower collector is suspended to the top, and then in turn to the ceiling overlap.
1.3.4. Convective steamer (PPC).
Convective Steamer Scheme (PPC).
On TGM-84 boilers, the convective horizontal type steamer is located at the beginning of the convective shaft. The steamer is performed by two-way and each stream is located symmetrically relative to the axis of the boiler.
The suspension of the packets of the front level of the steamer is made on the suspended pipes of the convective mine.
The weekend (second) stage is located first in a convective mine along the gas ducts. The coils of this step are also made of pipes with a diameter of 38x6 mm (steel 12x1mf) with the same steps. Input collectors with a diameter of 219x30 mm, the output with a diameter of 325x50 mm (steel 12x1mf).
Fastening and disconnection of analogously to the input level.
In some variants of boilers, steamers differ from the input and output collectors described above and steps in the packages of coils.
1.4. Water economizer
Water economizer is located in a convective mine, which is divided into two gas strokes. Each of the streams of the water economizer is located in the corresponding gas duct, forming two parallel independent flow.
In the height of each sheather, the water economizer is divided into four parts, between which there are 665mm highs with a height of 665mm (on some boilers are a height of 655mm) for the production of repair work.
The economizer is made of pipes with a diameter of 25x3,3mm (steel 20), and the input and output collectors are made with a diameter of 219x20mm (steel 20).
Packages of the water economizer are made of 110 double mining coils. Packages are located in a checkerboard with a transverse step S 1 \u003d 80mm and a longitudinal step S 2 \u003d 35mm.
Water economizer coils are located in parallel to the front of the boiler, and the collectors are located outside the gas plant on the side walls of the convective shaft.
Distanceing coils in packages carried out with the help of five rows of racks, whose curly cheats cover a coil from two sides.
The upper part of the water economizer is based on three beams located inside the gas and air cooled. The next part (the second in the gas) is suspended to the above-mentioned cooled beams with the help of distortional racks. Fastening and suspension of the lower two parts of the water economizer is identical to the first two.
Cooled beams are made of rolled and coated with thermal protection concrete. From above, concrete is covered with a metal sheet that protects the beams from fraud.
The first in the course of the movement of the flue gases of coils have metal lining of steel3 to protect against wear by the fraction.
The input and output collectors of the water economizer have 4 movable supports to compensate for temperature movements.
Movement of the medium in a water economizer - countercurrent.
1.5. Regenerative air heater.
For heating air, the boiler unit has two regenerative rotating aircraft heater RRV-54.
RVP design: typical, frameless, the air heater is installed on a special reinforced concrete pedestal of a frame type, and all the auxiliary nodes are attached on the air itself.
The weight of the rotor is transmitted through the thrust spherical bearing mounted in the lower support, on the carrier beam, in four supports on the foundation.
The air heater is rotating on the vertical shaft of the rotor with a diameter of 5400 mm and a height of 2250 mm prisonered inside the fixed body. Vertical partitions divide the rotor into 24 sectors. Each remote partition sector is divided into 3 compartments, in which the packets of heating steel sheets are stacked. Heating sheets collected in packets are laid in two tiers in the height of the rotor. Upper Yar The first in the course of gases is the "hot part" of the rotor, the lower - "cold part".
The "hot part" with a height of 1200 mm is made of distainer corrugated sheets with a thickness of 0.7 mm. The overall surface of the "hot part" of two devices is 17896 m2. The cold part with a height of 600 mm is made of distainer corrugated sheets with a thickness of 1.3 mm. The overall surface of the heating of the cold part of the heating of 7733 m2.
The gaps between the remote partitions of the rotor and packing packages are filled with separate sheets of additional packing.
Gases and air enter the rotor and are discharged from it by boxes based on the special frame and connected to the lower caps of the air heater. The covers together with the casing form the air heater housing.
The housing of the bottom cover relies on the supports installed on the foundation and the bearing of the bottom support. The vertical cover consists of 8 sections, of which 4 are carriers.
Rotation of the rotor is carried out by an electric motor with a gearbox through the lap engagement. Rotation speed - 2 rpm.
Rotor packing packages alternately pass the gas tract, warming up from flue gases, and an air tract giving a battery airflow. At each moment of time, 13 sectors of 24 are included in the gas tract, and 9 sectors - in the air and 2 sectors are covered with sealing plates and disconnected from work.
To prevent air supplements (dense separation of gas and air flow) there are radial, peripheral and central seals. Radial seals consist of horizontal steel strips fixed on radial partitions of the rotor - radial moving plates. Each plate is fixed on the upper and lower caps with three adjusting bolts. The adjustment of the gaps in the seals is carried out by the rise and lowering the plates.
The peruperial seals consist of rotor flanges, stuffed during installation, and movable cast iron pads. Pads together with guides are fixed on the top and bottom cover of the RVP case. Adjusting the pads is carried out by special adjustment bolts.
Internal shaft seals are similar to the peripheral seals. External seals of the shaft of the seal type.
Live cross section for gases: a) in the "cold part" - 7.72 m2.
b) in the "hot part" - 19.4 m2.
Live cross section for air passage: a) in the "hot part" - 13.4 m2.
b) in the "cold part" - 12.2 m2.
1.6. Cleaning the heating surfaces.
For cleaning the surfaces of heating and hydrochda, shot writing is used.
With a shot blasting method of cleaning the surfaces of heating, a cast-iron fraction of a round shape of 3-5 mm is used.
For normal operation, the contour of the shot writing in the bunker should be about 500 kg of fraction.
When the air ejector is turned on, the necessary air velocity is created for lifting the fraction through the pneumatic tube to the top of the convective mine in the shotgun. From the shotgun, the exhaust air is discharged into the atmosphere, and fraction through the conical flaying, the intermediate bunker with a wire mesh and through the fraci separator, the fraci flows in flow.
In leaks, the flow rate of the fraction is slowed down using inclined shelves, after which the fraction falls on spherical spreaders.
Passing through the cleaned surfaces, which spent the shot collected in the bunker, at the output of which the air separator is installed. The separator serves to separate the ash from the flow of the fraction and to maintain the bins in the purity of the bunker by air entering the gas duct through the separator.
The ash particles, pickled, air, are returned to the zone of active flue gases and are carried out beyond the convective shaft. The fraction cleaned from the ash is passed through the separator flasher and through the wire mesh of the bunker. From the bunker, the fraction is again served in the pneumatic transport pipe.
For cleaning the convective mine, 5 contours of 10 leaks are installed.
The amount of fraction passed through the flow of purification pipes increases with an increase in the initial degree of the beam contamination. Therefore, during the operation of the installation, it is necessary to strive for a decrease in the intervals between the purification, which allows relatively small portions of the fraction to maintain the surface in its pure state and, therefore, during the operation of the aggregates for the entire company have the minimum values \u200b\u200bof pollution coefficients.
To create discharge in the ejector, air from the discharge plant with a pressure of 0.8-1.0 ATI and a temperature of 30-60 o C were used.
2.1. Fuel composition.
2.2. Calculation of volumes and enthalpy of air and combustion products.
Calculations of air and combustion products are presented in Table 1.
Calculation of enthalpy:
where - enthalpy 1 m 3 air, KJ / kg.
This enthalpy can also be found along the XVI table.
where, - enthalpy 1 m 3 of trochatomic gases, theoretical volume of nitrogen, theoretical volume of water vapor.
We find this enthalpy for the whole range of temperatures and the obtained values \u200b\u200bare in a table 2.
where is an excess air coefficient, and is located on the XVII and XX tables
This enthalpy is found for the entire temperature range and the obtained values \u200b\u200bare in Table 2.
2.3. Estimated thermal balance and fuel consumption.
2.3.1. Calculation of heat loss.
The total amount of heat entered into the boiler unit is called the warmth and denoted. Heat, which left the boiler unit is the sum of useful warmth and heat loss associated with technological process Development of steam or hot water. Consequently, the heat balance of the boiler has the form: \u003d Q 1 + Q 2 + Q 3 + Q 4 + Q 5 + Q 6,
where - located heat, kj / m 3.
Q 1 - useful heat contained in a pair, KJ / kg.
Q 2 - Warm loss with exhaust gases, KJ / kg.
Q 3 - the loss of heat from the chemical incompleteness of combustion, KJ / kg.
Q 4 - the loss of heat from the mechanical incompleteness of combustion, KJ / kg.
Q 5 - Warm loss from outdoor cooling, KJ / kg.
Q 6 - the loss of heat from the physical heat contained in the removable slag, plus the losses for cooling panels and beams not included in the circulation circuit of the boiler, KJ / kg.
The heat balance of the boiler is compiled in relation to the steady heat regime, and the loss of heat is expressed as a percentage of disposable warmth:
The calculation of the heat loss is shown in Table 3.
Notes to Table 3:
H Wow - the enthalpy of the outgoing gases is determined by table 2.
2.3.2. Calculation of efficiency and fuel consumption.
The efficiency of the steam boiler is called the ratio of useful heat to the warmth. Not all useful heat generated by the unit is sent to the consumer. If the efficiency is determined by the warmth developed - it is called gross if the heat released is net.
The calculation of the efficiency and fuel consumption is shown in Table 3.
Table 1.
|
The calculated value |
Mostoz-outpound |
Dimension |
Calculation or justification |
|||
|
Theoretical number necessary for complete fuel combustion. |
0,0476(0,5*0+0,5*0++1,5*0+(1+4/4)*98,2+ +(2+6/4)*0,4+(3+8/4)*0,1+ +(4+10/4)*0,1+(5+12/4)*0,0+(6+14/4)*0,0)*0,005-0) |
|||||
|
Theoretical nitrogen volume |
0.79 · 9,725 + 0,01 · 1 |
|||||
|
trehatomic |
*98,2+2*0,4+3*0,1+4* *0,1+5*0,0+6*0,0) |
|||||
|
Theoretical volume water |
0,01(0+0+2*98,2+3*0,0,4+3*0,1+5*0,1+6*0,0+7*0++0,124*0)+0,0161* |
|||||
|
Volume water |
2,14+0,0161(1,05- |
|||||
|
The volume of smoke |
2,148+ (1.05-1) · 9,47 |
|||||
|
Volumetric lobes Trehatomic |
r RO 2, R H 2 O |
|||||
|
Dry gas density at N.U. |
||||||
|
Mass of combustion products |
G g \u003d 0,7684 + (0/1000) + 1.306 · 1.05 · 9,47 |
Table 2.
|
The surface of heating |
Temperature after heating surface, 0 s |
H 0 B, KJ / M 3 |
H 0 g, kj / m 3 |
H b HOW, KJ / M 3 |
|
|
Top Camera a T \u003d 1.05 + 0.07 \u003d 1.12 |
|||||
|
Shirm steamer, a SPE \u003d 1,12 + 0 \u003d 1.12 |
|||||
|
Convective steamer, a KPE \u003d 1,12 + 0.03 \u003d 1.15 |
|||||
|
Water economizer a EK \u003d 1.15 + 0.02 \u003d 1.17 |
|||||
|
Air heater a VP \u003d 1.17 + 0.15 + 0.15 \u003d 1.47 |
Table 3.
|
The calculated value |
Mostoz-outpound |
Dimension |
Calculation or justification |
Result |
|
|
Enthalpy theoretical volume of cold air at a temperature of 30 0 s |
I 0 Kh.V. \u003d 1,32145 · 30 · 9,47 |
||||
|
Entalpy of the outgoing gases |
Accepted at a temperature of 150 0 s |
Take on table 2 |
|||
|
Loss of heat from mechanical non-payment of combustion |
When burning gas loss from mechanical incompleteness of combustion |
||||
|
Placed heat per 1 kg. Fuels in |
|||||
|
Warm loss with outgoing gases |
q 2 \u003d [(2902,71-1,47 * 375.42) * |
||||
|
Warm loss from outdoor cooling |
Determine in fig. 5.1. |
||||
|
Warm loss from chemical non-payment of combustion |
Determine Table XX |
||||
|
KPD gross PO |
h br \u003d 100 - (Q 2 + Q 3 + Q 4 + Q 5) |
h br \u003d 100 - (6,6 + 0.07 + 0 + 0.4) |
|||
|
Fuel consumption by (5-06) and (5-19) |
In pg \u003d (/) · 100 |
||||
|
Estimated fuel consumption of software (4-01) |
In p \u003d 9,14 * (1-0 / 100) |
2.4. Thermal calculation of the heat chamber.
2.4.1 Determination of the geometric characteristics of the furnace.
When designing and operating boiler installations, the sealing device calculation is most often performed. During the calibration calculation of the furnaces according to the drawings, it is necessary to determine: the volume of the heat chamber, the degree of its shielding, the surface area of \u200b\u200bthe walls and the area of \u200b\u200bthe emission surfaces of heating, as well as the design characteristics of the pipes of the screens (pipe diameter, the distance between the pipe axes).
The calculation of the geometrical characteristics is given in Tables 4 and 5.
Table 4.
|
The calculated value |
Mostoz-outpound |
Dimension |
Calculation or justification |
Result |
|
Front-line area |
19,3*14, 2-4*(3,14* *1 2 /4) |
|||
|
Square side wall |
6,136*25,7-1,9*3,1- (0,5*1,4*1,7+0,5*1,4*1,2)-2(3,14*1 2 /4) |
|||
|
Back Wall area |
2(0,5*7,04*2,1)+ |
|||
|
Square of a two-shield |
2*(6,136*20,8-(0,5*1,4 *1,7+0,5*1,4*1,2)- |
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|
Outlet window Fires |
||||
|
Burner |
||||
|
Fire width |
according to constructive data |
|||
|
Active volume of the heat chamber |
Table 5.
|
Name of the surface |
by nomographer |
|||||
|
Front wall |
||||||
|
Side Walls |
||||||
|
Two wave screen |
||||||
|
Rear Wall |
||||||
|
Gas window |
||||||
|
Square shielded walls (excluding burners) |
||||||
2.4.2. Calculation of firebox.
Table 6.
|
The calculated value |
Mostoz-outpound |
Dimension |
Formula |
Calculation or justification |
Result |
|
The temperature of combustion products at the outlet of the furnace |
According to the design of the boiler. |
Previously accepted depending on the combed fuel |
|||
|
Enhaulpia products of combustion |
Accepted on Table. 2. |
||||
|
Useful heat dissipation in the firebox (6-28) |
35590 · (100-0.07-0) / (100-0) |
||||
|
Degree of shielding software (6-29) |
H ray / f st |
||||
|
Film screenshot coefficient |
Accepted according to Table 6.3. |
depending on the burned fuel |
|||
|
The thermal efficiency coefficient of screens (6-31) |
|||||
|
Effective thickness of the emitted layer by |
|||||
|
The coefficient of weakening rays of trothy gas gases (6-13) |
|
The attenuation coefficient of rays with large particles (6-14) |
1.2 / (1 + 1,12 2) · (2.99) 0.4 · (1.6 · 920 / 1000-0.5) |
||||
|
The coefficient characterizing the share of flopping volume filled with a luminous part of the torch |
Accepted on page 38. |
Depending on the proportion of the separation volume: |
|||
|
The absorption coefficient of the coaming environment of software (6-17) |
1,175 + 0.1 · 0,894 |
||||
|
Criterion of absorbing ability (criterion of buger) software (6-12) |
1,264 · 0.1 · 5.08 |
||||
|
Effective value of the bug criterion |
1,6LN ((1,4 · 0.642 2 +0,642 +2) / (1.4 · 0.642 2 -0.642 +2)) |
||||
|
The charlasticity parameter of the fuel gases by |
11,11*(1+0)/(7,49+1,0) |
||||
|
Fuel consumption of tier burner |
|
The level of the location of the torch axes in Yarusa software (6-10) |
(2 · 2.28 · 5.2 + 2 · 2.28 · 9.2) / (2 · 2.28 · 2) |
||||
|
Relative level of burner by (6-11) |
x g \u003d h g / h t |
||||
|
Coefficient (for gas-airing floors with a wall burner) |
Take on page 40 |
||||
|
Parameter software (6-26a) |
0,40(1-0,4∙0,371) |
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|
The coefficient of conservation of heat by |
|||||
|
Theoretical (adiabatic) combustion temperature |
Accepted equal to 2000 0 s |
||||
|
The average total heat capacity of combustion products on page 41 |
The temperature at the outlet of the furnace is chosen correctly and the error was (920-911.85) * 100% / 920 \u003d 0.885%
2.5. Calculation of boiler steamers.
The convective surfaces of the heating of steam boilers play an important role in the process of obtaining steam, as well as the use of heat of combustion products, leaving the flue chamber. The effectiveness of the operation of convective surfaces of heating depends on the intensity of heat transfer of heat combustion products.
Combustion products transfer the heat of the outer surface of the pipe by convection and radiation. Through the wall of the pipe, heat is transmitted with thermal conductivity, and from the inner surface to a pair of convection.
Scheme of the steam of steam on boiler top steampersites:
Wallpapers, located on the front wall of the heat chamber, and occupies the entire surface of the front wall.
The ceiling superheater, located on the ceiling, passing through the fiberboard, shirm steamers and the upper part of the convective shaft.
The first series of shirmers, located in the rotary chamber.
The second series of shirm steamers, located in a swivel chamber after the first next.
Convective steamer with serial-mixed current and injecting vapor cooler, installed by the Korissechka, installed in the convective mine of the boiler.
After the gearbox pairs enters the steam collector and goes beyond the boiler unit.
Geometrical characteristics of steps
Table 7.
2.5.1. Calculation of a wall-mounted superheater.
Wall-mounted PP is located in the furnace, with its calculation, the heat perception will be determined as part of heat, given by products of combustion of the NPP surface with respect to the other surfaces of the furnace.
The calculation of the NPP is presented in Table No. 8
2.5.2. Calculation of the ceiling steamer.
Considering the fact that the PPP is located both in the furnace chamber and in the convective part, but perceived heat in the convective part after the SPP and under the brackets are very small in relation to the heat-perceived heat supply in the furnace in the furnace (about 10% and 30%, respectively (from the technical manual on the boiler TGM-84. The calculation of the PPP is carried out in Table No. 9.
2.5.3. Calculation of the shirm steamer.
The calculation of the SPP is carried out in Table No. 10.
2.5.4. Calculation of the convective steamer.
The calculation of the CAT is carried out in Table No. 11.
Table 8.
|
The calculated value |
Mostoz-outpound |
Dimension |
Formula |
Calculation or justification |
Result |
|
Surface area heating |
From table 4. |
From table 4. |
|||
|
Lighting surface of wall pp |
From table 5. |
From table 5. |
|||
|
Heat, perceived by the NPP |
0,74∙(35760/1098,08)∙268,21 |
||||
|
The increase in enthalpy couple in the NPP |
6416,54∙8,88/116,67 |
||||
|
Entalpy couple before NPP |
Enthalpy of dry saturated steam at a pressure of 155 Ata (15.5 MPa) |
||||
|
Enthalpy couple in front of the ceiling steamer |
I "PPP \u003d I" + DI NPP |
||||
|
Steam temperature in front of the ceiling steamer |
From tables of thermodynamic properties of water and superheated steam |
The temperature of the superheated steam at a pressure of 155 Ata and enthalpy 3085,88CH / kg (15.5 MPa) |
The temperature after NPP is taken equal to the temperature of combustion products at the outlet of the furnace \u003d 911.85 0 C.
Table 9.
|
The calculated value |
Mostoz-outpound |
Dimension |
Formula |
Calculation or justification |
Result |
|
Surface surface of heating 1st PPP |
|||||
|
Emipable Surface PPP-1 |
H L PPP \u003d F ∙ x. |
||||
|
Heat, perceived PPP-1 |
0,74(35760/1098,08)∙50,61 |
||||
|
The increase in enthalpy couple in PPP-1 |
1224,275∙9,14/116,67 |
||||
|
Entalpy couple after PPP-1 |
I`` PPP -2 \u003d I`` PPP + DI NPP |
||||
|
The increase in enthalpy vapor in the PPP under the bracket |
About 30% of Di PPP |
||||
|
The increase in enthalpy couple in the PPP for the bracket |
It is accepted pre-on regulatory methods for calculating the boiler TGM-84 |
About 10% of Di PPP |
|||
|
Enthapia Couple Before SPP |
I`` PPP -2 + DI PPP -2 + DI PPP-3 |
3178,03+27,64+9,21 |
|||
|
Steam temperature in front of the screen steamer |
From tables of thermodynamic properties of water and superheated steam |
The temperature of the superheated pair at a pressure of 155 Ata and enthalpy 3239.84CH / kg (15.5 MPa) |
Table10.
|
The calculated value |
Mostoz-outpound |
Dimension |
Formula |
Calculation or justification |
Result |
|
Surface area heating |
∙ d ∙ l ∙ z 1 ∙ z 2 |
3,14∙0,033∙3∙30∙46 |
|||
|
Live cross section area for the passage of combustion products for (7-31) |
3,76∙14,2-30∙3∙0,033 |
||||
|
Temperature of combustion products after the brass |
Pre-evaluate the final temperature |
||||
|
Enthalpy of combustion products before the SPP |
Accepted on Table. 2: |
||||
|
Enthalpy of combustion products after the brass |
Accepted on Table. 2. |
||||
|
Enthalpy of the air suctioned in the convective surface, at T B \u003d 30 0 s |
Accepted on Table. 3. |
||||
|
0,996(17714,56-16873,59+0) |
|||||
|
The heat transfer coefficient |
W / (m 2 × k) |
Determine the nomogram 7 |
|||
|
Amendment for the number of pipes in the course of combustion products software (7-42) |
With the transverse wash the corridor beams |
||||
|
Amendment on the layout of a beam |
Determine the nomogram 7 |
With the transverse wash the corridor beams |
|||
|
Determine the nomogram 7 |
With the transverse wash the corridor beams |
||||
|
The coefficient of heat-giving convection from p / s to the surface of the nipper (formula in nomogram 7) |
W / (m 2 × k) |
75∙1,0∙0,75∙1,01 |
|||
|
Total optical thickness of software (7-66) |
(k g R p + k evil m) ps |
(1,202∙0,2831 +0) 0,1∙0,628 |
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|
The thickness of the emitting layer for the wiring surfaces by |
|||||
|
The heat transfer coefficient |
W / (m 2 × k) |
Determine the nomogram - |
|
Coefficient |
Determine the nomogram - |
||||
|
Heat transfer coefficient for disadvantaged flow |
W / (m 2 × k) |
Distribution coefficient height heat height See Table 8-4 |
|||
|
The heat obtained from the heat dissipation of the heating surface, adjacent to the output need window firebox |
|||||
|
Preliminary enthalpy couple at the exit of the bracket by (7-02) and (7-03) |
|||||
|
Pre-temperature steam at the outlet of the brass |
Temp-RA overheated pair with pressure. 150 Ata |
||||
|
Coefficient of use |
Choose in fig. 7-13 |
||||
|
W / (m 2 × k) |
|
Coefficient of thermal efficiency Shirm |
Determine from Table 7-5 |
||||
|
Coefficient of heat transfer software (7-15V) |
W / (m 2 × k) |
||||
|
The actual temperature of combustion products after the brass |
Since q b and q t differ on (837,61 -780,62)*100% / 837,61 the calculation of the surface is not specified |
||||
|
Consumption of the steelectricel on page 80 |
0.4 \u003d 0.4 (0.05 ... 0.07) D |
||||
|
Medium enthalpy couple in the tract |
0,5(3285,78+3085,88) |
||||
|
Enhatpia of water used for injection in steam |
From the tables of thermodynamic properties of water and superheated steam at 230 ° C |
Table 11.
|
The calculated value |
Mostoz-outpound |
Dimension |
Formula |
Calculation or justification |
Result |
|
Surface area heating |
3,14∙0,036∙6,3∙32∙74 |
||||
|
Live cross section for the passage of combustion products |
|||||
|
Temperature of combustion products after convective PP |
Pre-adopted 2 values |
By the design of the boiler unit |
|||
|
Enhaulpia combustion products before gear |
Accepted on Table. 2: |
||||
|
Enhaulpia combustion products after gearbox |
Accepted on Table. 2. |
||||
|
Heat, given to combustion products by |
0,996(17257,06-12399+0,03∙373,51) 0,996(17257,06-16317+0,03∙373,51) |
||||
|
The average speed of combustion products by |
|||||
|
The heat transfer coefficient |
W / (m 2 × k) |
Determine the nomogram 8 |
With the transverse wash the corridor beams |
||
|
Amendment for the number of pipes in the course of combustion products |
Determine the nomogram 8 |
With the transverse wash the corridor beams |
|||
|
Amendment on the layout of a beam |
Determine the nomogram 8 |
With the transverse wash the corridor beams |
|||
|
Coefficient taking into account the impact of changes in the physical flow parameters |
Determine the nomogram 8 |
With the transverse wash the corridor beams |
|||
|
Coefficient of heat transfer convection from p / s to the heating surface |
W / (m 2 × k) |
75∙1∙1,02∙1,04 82∙1∙1,02∙1,04 |
|||
|
Polluted wall temperature (7-70) |
|||||
|
Coefficient of use |
We accept on instructions on |
For complex washed beams |
|||
|
The total heat transfer coefficient by |
W / (m 2 × k) |
0,85∙ (77,73+0) 0,85∙ (86,13+0) |
|||
|
The coefficient of thermal efficiency |
Determine the table. 7-5 |
||||
|
Coefficient of heat transfer by |
W / (m 2 × k) |
||||
|
Preliminary enthalpy couple at the exit from the checkpoint by (7-02) and (7-03) |
|||||
|
Pre-temperature steam after gearbox |
From the tables of thermodynamic properties of overheated steam |
Temp-RA overheated pair with pressure. 140 Ata |
|||
|
Temperature pressure software (7-74) |
|||||
|
The amount of heat perceived by the heating surface of the software (7-01) |
50,11 ∙1686,38∙211,38/(9,14∙10 3) 55,73∙1686,38∙421,56/(9,14 ∙10 3) |
||||
|
Active Heat Perceived in PPC |
We accept on schedule 1 |
||||
|
The actual temperature of the combustion products after the CAT |
We accept on schedule 1 |
The schedule is built by QB and QT values \u200b\u200bfor two temperatures. |
|||
|
The increase in enthalpy couple in the checkpoint |
3070∙9,14 /116,67 |
||||
|
Entalpy couple after gearbox |
I`` KPP + DI PPC |
||||
|
Couple temperature after gearbox |
From tables of thermodynamic properties of water and superheated steam |
The temperature of the superheated steam at a pressure of 140 Ata and enthalpy 3465.67 kJ / kg |
Calculation Results:
Q p p \u003d 35590 kJ / kg - disposed of heat.
Q l \u003d φ · (q m - i't) \u003d 0.996 · (35565.08 - 17714,56) \u003d 17779,118 kJ / kg.
Q K \u003d 2011.55 kJ / kg - Heat-perception of the SPP.
Q PE \u003d 3070 KJ / kg - gearmosphere of the checkpoint.
The heat-perception of the NPP and the PPP is taken into account in Q L, since the NPP and the PPP are in the firebox of the boiler. That is, q NPP and Q RPP are included in Q l.
2.6 Conclusion
I made a calibration calculation of the TGM-84 boiler.
In the calibration of the heat calculation on the adopted design and the size of the boiler for the given load and the type of fuel, the water temperature, steam, air and gases on the boundaries between the individual heating surfaces, the efficiency, fuel consumption, consumption and steam velocity, air and flue gases are determined.
Tweet calculation is made to evaluate indicators of the economy and reliability of the boiler when working on a given fuel, identifying the necessary reconstructive measures, the choice of auxiliary equipment and the preparation of the starting materials for settlements: aerodynamic, hydraulic, metal temperature, pipe strength, the intensity of the ash volunteer aboutsa tub, corrosion, etc.
3. The list of literature used
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Typical energy characteristics of the TGM-96B boiler reflects the technically achievable efficiency of the boiler. A typical energy characteristic can serve as a basis for compiling the regulatory characteristics of TGM-96B boilers when combing fuel oil.
Ministry of Energy and Electrification of the USSR
Main technical service management
Energy Systems
Typical energy characteristic
TGM-96B boiler when burning fuel oil
Moscow 1981.
This typical energy characteristic was developed by Soyucehenergo (Inzh. G.I. Gutsalo)
The standard energy characteristics of the TGM-96B boiler was prepared on the basis of thermal tests conducted by the Soyucenergo at the Riga CHP-2 and the Mediaztehenergo on CHP gas, and reflects the technically achievable cost of the boiler.
A typical energy characteristic can serve as a basis for compiling the regulatory characteristics of TGM-96B boilers when combing fuel oil.
1.1 . Copper TGM-96B Taganrog Boiler Plant - gas-gas with natural circulation and P-shaped layout, designed to work with turbinesT. -100 / 120-130-3 and PT-60-130 / 13. The main calculated parameters of the boiler when working on fuel oil are shown in Table. .
According to TKZ, the minimum allowable load of the boiler under the circulation condition is 40% nominal.
1.2 . The furnace chamber has a prismatic form and in the plan is a rectangle with dimensions of 6080 × 14700 mm. The volume of the furnace chamber is 1635 m 3. The thermal voltage of the flue volume is 214 kW / m 3, or 184 · 10 3 kcal / (m 3 · h). Evapory screens are placed in the furnace chamber and on the front wall Radiation Wall Steam Steaver (RNP). In the upper part of the furnace in the rotary chamber there is a wide steamer (SPP). In the lowered convective mine, two packages of the convective steamer (CAT) and a water economizer (VE) are located consistently along the gases.
1.3 . The steam path of the boiler consists of two independent streams with a pair of crossing between the side of the boiler. The temperature of the superheated steam is regulated by the injection of its own condensate.
1.4 . On the front wall of the furnace chamber there are four two-flow gas-tank burners HF CKB-WTI. The burners are installed in two tiers on -7250 and 11300 mm with an angle of lifting to the horizon 10 °.
For the combustion of the fuel oil, ferry mechanical nozzles "titanium" with a nominal capacity of 8.4 t / h at a pressure of the fuel oil 3.5 MPa (35 kgf / cm 2). Pressure pressure on purge and sprayed fuel oil is recommended by a 0.6 MPa plant (6 kgf / cm 2). The steam consumption on the nozzle is 240 kg / h.
1.5 . The boiler installation is equipped with:
Two blowing fans of VDN-16-P capacity with a reserve of 10% 259 · 10 3 m 3 / h, pressure with a reserve of 20% 39.8 MPa (398.0 kgf / m 2), 500/250 kW and rotation frequency 741 / 594 rpm of each machine;
Two smokers of DN-24 × 2-0.62 GM with a reserve with a reserve of 10% 415 · 10 3 m 3 / h, pressure with a reserve of 20% 21.6 MPa (216.0 kgf / m 2), with a capacity of 800/400 kW and rotation frequency of 743/595 rpm of each machine.
1.6 . For the cleaning of convective surfaces of heating from sediments of ash, the project is provided for a fractional installation, for cleaning RVP - water washing and blasting with a ferry from a drum with a decrease in pressure in the throttling unit. The duration of the blowing of one RVP 50 min.
2.1 . Typical energy characteristics of the TGM-96B boiler ( fig. , , ) Compiled on the basis of the results of thermal testing of boilers of the Riga CHP-2 and CHP gas in accordance with the instrumental materials and methodological instructions on the normalization of the feasibility of boilers. Characteristic reflects the average economy of the new boiler working with turbinesT. -100 / 120-130 / 3 and PT-60-130 / 13 at the following conditions adopted for the initial one below.
2.1.1
. In the fuel balance of power plants, burning liquid fuel, most of the fancy fuel oilM. 100. Therefore, the characteristic is composed of fuel oil.M 100 ( GOST 10585-75) With characteristics:A p \u003d 0.14%, w p \u003d 1.5%, s p \u003d 3.5%, 
(9500 kcal / kg). All necessary calculations are made on the working mass of fuel oil.
2.1.2 . The temperature of the fuel oil in front of the nozzles is taken 120 °C ( t TL \u003d 120 ° C) based on the viscosity of fuel oilM. 100, equal to 2.5 ° W, according to § 5.41 PTE.
2.1.3 . The average annual temperature of cold air (t x.) At the entrance to the blowing fan is taken equal to 10 °C. Since mainly TGM-96B boilers are located in climatic areas (Moscow, Riga, Gorky, Chisinau) with an average annual air temperature close to this temperature.
2.1.4 . Air temperature at the entrance to the air heater (t VP) adopted equal to 70 °C. and constant when changing the load of the boiler, according to § 17.25 of the PTE.
2.1.5 . For power plants with transverse bonds, the temperature of the nutrient water (t P.V.) Before the boiler is made calculated (230 ° C) and constant when the boiler load changes.
2.1.6 . The specific heat consumption of the net on the turbine installation is adopted 1750 kcal / (kWh), according to thermal tests.
2.1.7 . The heat flux coefficient is accepted by changing the load of the boiler from 98.5% at a rated load to 97.5% with a load of 0.6D Nom..
2.2 . The calculation of the regulatory characteristic was carried out in accordance with the instructions of the "thermal calculation of boiler aggregates (regulatory method)", (M.: Energy, 1973).
2.2.1 . The efficiency of the gross boiler and heat loss with outgoing gases is calculated in accordance with the method described in the book Ya.L. Pecker "Heat engineering calculations for the above fuel characteristics" (M.: Energy, 1977).
where
here
α Wow = α " VE. + Δ α Tr.
α Wow - the excess air coefficient in the outgoing gases;
Δ α Tr. - the gazes in the gas path of the boiler;
So uh - The temperature of the outgoing gases behind the smoke.
The calculation of the temperature of the outgoing gases, measured in the experiments of thermal testing of the boiler and the regulatory conditions given to the conditions for constructing the regulatory characteristics (input parameterst X B., t "kf, t P.V.).
2.2.2 . Outlet air coefficient of an airpoint (for a water economizer)α " VE. It is accepted equal to 1.04 on the rated load and varying to 1.1 by 50% load according to thermal tests.
The decrease in the calculated (1.13) coefficient of an excess of air for a water economizer to adopted in the regulatory characteristic (1.04) is achieved properly conducting the flue regime according to the boiler's regime map, compliance with the PTE requirements for air supplies in the furnace and the gas tract and the selection of the nozzles set .
2.2.3 . Air shocks in the gas path of the boiler on the rated load are taken equal to 25%. With a change in the load of the air supplies are determined by the formula
2.2.4 . Heat losses from chemical non-fuel combustion (q. 3 ) Accepted zero, since during the testing of the boiler in excess airs adopted in a typical energy characteristic, they were absent.
2.2.5 . Heat loss from mechanical fuel combustion (q. 4 ) Adopted equal zero in accordance with the "Regulations on the coordination of the regulatory characteristics of the equipment and the estimated specific costs of fuel" (M.: SNTTI OrGRES, 1975).
2.2.6 . Heat losses in the environment (q. 5 ) When testing were not determined. They are calculated in accordance with the "method of testing boiler installations" (M.: Energy, 1970) by the formula
2.2.7 . The specific consumption of electricity to the nutritional electric pump PE-580-185-2 was calculated using the characteristic of the pump adopted from the technical conditions of Tu-26-06-899-74.
2.2.8 . The specific consumption of electricity on the thrust and blowing is calculated by electricity costs on the drive of blowing fans and the smoke, measured when conducting thermal tests and reduced to the conditions (Δ α Tr. \u003d 25%) adopted when drawing up the regulatory characteristics.
It has been established that with a sufficient density of the gas tract (Δ α ≤ 30%) The smokers provide a nominal load of the boiler at a low speed frequency, but without any stock.
Blowing fans on a low speed of rotation provide the normal operation of the boiler to loads 450 t / h.
2.2.9 . The total electrical power of the mechanisms of the boiler installation includes electric drive power: nutritional electric pump, smoke, fans, regenerative air heaters (Fig. ). The power of the electric motor of the regenerative air heater is accepted according to passport data. The power of electric motors of the smoke, fans and the nutritional electric pump is determined during the heat tests of the boiler.
2.2.10 . Specific heat consumption for air heating in the caloric installation is calculated with the heating of air in the fans.
2.2.11 . To the specific heat consumption for the own needs of the boiler installation, heat losses in the carriers, the efficiency of which are taken by 98%; On the steam blow of the RVP and the loss of heat with the steam blowing of the boiler.
Heat consumption for steam blowing RVP was calculated by the formula
Q hp = G PBD · i found · τ OBD · 10 -3. MW. (Gkal / Ch)
where G PBD \u003d 75 kg / min in accordance with the "Current standards of steam and condensate for their own needs of the power units 300, 200, 150 MW" (M.: SNTTI OrGRES, 1974);
i found = i. couple \u003d 2598 kJ / kg (kcal / kg)
τ OBD \u003d 200 min (4 apparatus with a rejoice duration of 50 min when turned on within 24 hours).
Heat consumption with the blowing of the boiler was calculated by the formula
Q Prod. = G Prod · i K.V. · 10 -3. MW. (Gkal / Ch)
where G Prod = PD Nome.10 2 kg / ch
P \u003d 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 tests were determined by the "method of testing boiler installations" (M.: Energy, 1970).
3.1 . To bring the basic regulatory indicators of the boiler to the changed conditions of its operation within the permissible limits of deviation of the parameter values, amendments in the form of graphs and digital values \u200b\u200bare given. Amendments K.q. 2 In the form of graphs, shown in Fig. , . Amendments to the temperature of the outgoing gases are shown in Fig. . In addition to those listed, amendments are presented to change the heating temperature of the fuel oil supplied to the boiler, and to change the temperature of the nutrient water.
