Stairs. Entry group. Materials. Doors. Locks. Design » Siding Thermal calculation (on the example of a secondary school). Heating system of a school, kindergarten, educational institutions - organization and reconstruction with all approvals Design of heating for schools

Thermal calculation (on the example of a secondary school). Heating system of a school, kindergarten, educational institutions - organization and reconstruction with all approvals Design of heating for schools

Introduction

a common part

Object characteristic

Determination of the number of heat consumers. Graph of the annual heat consumption

System and circuit diagram of heat supply

Calculation of the thermal scheme of the boiler house

Selection of boiler room equipment

Selection and placement of the main and auxiliary equipment

Thermal calculation of the boiler unit

Aerodynamic calculation of the heat duct

Special part.

2. Development of a block system of heaters.

2.1 Baseline water supply

2.2 Selecting a water treatment plan

2.3 Calculation of the equipment of the water heating plant

2.4 Network installation calculation

3. Technical and economic part

3.1 Initial data

3.2 Calculation of the contractual cost of construction and installation works

3.3 Determination of annual operating costs

3.4 Determining the annual economic effect

Installation of sectional water heaters

5. Automation

Automatic regulation and thermal control of the boiler unit KE-25-14s

6. Labor protection in construction

6.1 Labor protection during the installation of power and technological equipment in the boiler room

6.2 Analysis and prevention of potential hazards

6.3 Sling calculation

7. Organization, planning and construction management

7.1 Installing the boilers

7.2 Conditions for commencement of work

7.3 Production costing of labor and wages

7.4 Calculation of schedule parameters

7.5 Organization of the building plan

7.6 Calculation of technical and economic indicators

8. Organization of operation and energy saving

List of used literature

Introduction.

In our difficult time, with a sick crisis economy, the construction of new industrial facilities is fraught with great difficulties, if construction is possible at all. But at any time, in any economic situation, there are a number of industries without the development of which normal functioning is impossible. National economy, it is impossible to provide the necessary sanitary and hygienic conditions for the population. Such industries include energy, which provides comfortable living conditions for the population both at home and at work.

Recent studies have shown the economic feasibility of maintaining a significant share of the participation of large heating boiler plants in covering the total consumption of thermal energy.

Along with large industrial, production and heating boiler houses with a capacity of hundreds of tons of steam per hour or hundreds of MW of heat load, a large number of boiler units up to 1 MW and operating on almost all types of fuel have been installed.

However, fuel is the biggest problem. For liquid and gaseous fuels, consumers often do not have enough money to pay. Therefore, it is necessary to use local resources.

In this graduation project, the reconstruction of the production and heating boiler plant of the RSC Energia plant is being developed, which uses locally mined coal as fuel. In the future, it is planned to transfer boiler units to burning gas from the degassing of gas emissions from the mine, which is located on the territory of the processing plant. The existing boiler house has two KE‑25‑14 steam boilers, which served to supply steam to the enterprises of the RSC Energia plant, and hot water boilers TVG-8 (2 boilers) for heating, ventilation and hot water supply of administrative buildings and a residential village.

Due to the reduction in coal production, the production capacity of the coal mining enterprise decreased, which led to a reduction in the need for steam. This caused the reconstruction of the boiler house, which consists in the use of steam boilers KE-25 not only for production purposes, but also for the production of hot water for heating, ventilation and hot water supply in special heat exchangers.

1. GENERAL

1.1. OBJECT CHARACTERISTICS

The designed boiler house is located on the territory of the RSC Energia plant

The layout, placement of buildings and structures on the industrial site of the processing plant are made in accordance with the requirements of SNiP.

The area of the industrial site within the boundaries of the fences is 12.66 hectares, the building area is 52194 m 2 .

The transport network of the construction area is represented by public railways and local roads.

The terrain is flat, with slight rises, loam prevails in the soil.

The source of water supply is the filtration station and the Seversky Donets-Donbass canal. Duplication of the water conduit is provided.

1.3. Determination of the number of heat consumers. Graph of the annual heat consumption.

Estimated heat consumption by industrial enterprises is determined by the specific norms of heat consumption per unit of output or per one heat carrier (water, steam) operating by type. Heat costs for heating, ventilation and technological needs are shown in Table 1.2. thermal loads.

The annual graph of heat consumption is built depending on the duration of standing outside temperatures, which is reflected in table 1.2. this graduation project.

The maximum ordinate of the annual heat consumption graph corresponds to the heat consumption at an outside air temperature of –23 С.

The area bounded by the curve and the ordinates gives the total heat consumption for the heating period, and the rectangle on the right side of the graph shows the heat consumption for hot water supply in summer.

Based on the data in table 1.2. we calculate the heat costs for consumers for 4 modes: maximum winter (t r. o. = -23C;); at the average outdoor temperature for the heating period; at an outside air temperature of +8C; during the summer period.

We carry out the calculation in table 1.3. according to the formulas:

Heat load for heating and ventilation, MW

Q OB \u003d Q R OV * (t ext -t n) / (t ext -t r.o.)

Heat load on hot water supply in summer, MW

Q L GV \u003d Q R GV * (t g -t chl) / (t g -t xs) * 

where: Q P OV - calculated winter thermal load for heating and ventilation at the calculated outdoor temperature for the design of the heating system. We accept according to the table. 1.2.

t VN - internal air temperature in the heated room, t VN = 18С

Q R GW - calculated winter heat load on hot water supply (Table 1.2);

t n - current outdoor temperature, ° С;

t r.o. - calculated heating temperature of the outside air,

t g - hot water temperature in the hot water supply system, t g \u003d 65 ° С

t chl, t xs - cold water temperature in summer and winter, t xl =15°C, t xs =5°C;

 - correction factor for the summer period, =0.85

Table 1.2

Thermal loads

Type of thermal	Heat load consumption, MW		Characteristic
Loads			coolant
1.Heating and ventilation			Water 150/70 С Steam Р=1.4 MPa
2.Hot water supply		By calculation
3.Technological needs			Steam Р=1.44MPa

Table 1.3.

Calculation of annual thermal loads

Type of load	Designation	Heat load value at MW temperature
		t r.o \u003d -23 С	t cf r.p. \u003d -1.8С
Heating and ventilation
Hot water supply

Technology

According to Table. 1.1. and 1.3. we build a graph of the annual costs of the heat load, presented in Fig. 1.1.

1.4. HEAT SUPPLY SYSTEM AND PRINCIPAL DIAGRAM

The source of heat supply is the reconstructed boiler house of the mine. The heat carrier is steam and superheated water. Drinking water used only for hot water systems. For technological needs, steam P = 0.6 MPa is used. For the preparation of superheated water with a temperature of 150-70С, a network installation is provided, for the preparation of water with t=65°С - a hot water supply installation.

The heating system is closed. Due to the lack of direct water intake and a slight leakage of the coolant through the leaky connections of pipes and equipment, closed systems are characterized by a high constancy in the quantity and quality of the network water circulating in it.

In closed water heating systems, water from heating networks is used only as a heating medium for heating tap water in surface-type heaters, which then enters the local hot water supply system. In open water heating systems, hot water to the taps of the local hot water supply system comes directly from the heating networks.

On the industrial site, heat supply pipelines are laid along bridges and galleries and partially in impassable flume channels of the Kl type. Pipelines are laid with a compensation device due to the angles of turns of the route and U-shaped compensators.

Pipelines are made of steel electric-welded pipes with thermal insulation device.

Sheet 1 of the graphic part of the graduation project shows the general layout of the industrial site with the distribution of heat networks to consumer objects.

1.5. CALCULATION OF THE THERMAL SCHEME OF THE BOILER ROOM

The principal thermal diagram characterizes the essence of the main technological process of energy conversion and the use of the heat of the working fluid in the installation. It is a conditional graphic representation of the main and auxiliary equipment, united by pipeline lines of the working fluid in accordance with the sequence of its movement in the installation.

The main purpose of calculating the thermal scheme of the boiler house is:

Determination of the total heat loads, consisting of external loads and heat consumption for own needs, and the distribution of these loads between the hot water and steam parts of the boiler house to justify the choice of the main equipment;

Determination of all heat and mass flows required to select auxiliary equipment and determine the diameters of pipelines and fittings;

Determination of initial data for further technical and economic calculations (annual heat generation, annual fuel consumption, etc.).

The calculation of the thermal scheme allows you to determine the total heat output of the boiler plant for several modes of operation.

The thermal scheme of the boiler house is shown on sheet 2 of the graphic part of the graduation project.

The initial data for calculating the thermal scheme of the boiler house are given in Table 1.4, and the calculation of the thermal scheme itself is given in Table 1.5.

Table 1.4

Initial data for calculating the thermal scheme of a heating and production boiler house with steam boilers KE-25-14s for a closed heating system.

	Name	Design modes		Note
pos. Exodus. data		Maximum winter	At the outside air temperature at the break point of the temperature graph

	Outside temperature
	Air temperature inside heated buildings
	Maximum temperature of direct heating water
	Minimum temperature of direct heating water at the break point of the temperature curve
	Maximum return water temperature
	Temperature of deaerated water after deaerator
	Enthalpy of deaerated water			From tables saturated steam and water at a pressure of 1.2MPa
	Temperature raw water at the entrance to the boiler room
	Raw water temperature before chemical water treatment
	Specific volume of water in the heat and water supply system, tons per 1 MW of total heat supply for heating, ventilation and hot water supply			For industrial enterprises
	Parameters of steam generated by boilers (before reduction plant)
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 1.4 MPa
	Steam parameters after reduction plant:
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 0.7 MPa
	Parameters of the steam generated in the continuous production separator:
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 0.17 MPa
	Parameters of steam entering the vapor cooler from the deaerator:
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 0.12 MPa
	Condenser parameters after the vapor cooler:
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 0.12 MPa
	Parameters of blowdown water at the inlet to the continuous blowdown separator:
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 1.4 MPa
	Blowdown water parameters at the outlet of the continuous blowdown separator:
	Pressure			From tables nasy-
	Temperature			puppy steam and
	Enthalpy			water at a pressure of 0.17 MPa
	Blowdown water temperature after blowdown water cooling
	Condensate temperature from the block of network water heaters			accepted
	Condensate temperature after the raw water steam heater			accepted
	Enthalpy of condensate after steam-water heater of raw water			From tables of saturated steam and water at a pressure of 0.7 MPa
	Temperature of condensate returned from production
	Continuous purge amount			Accepted from the calculation of chemical water treatment
	Specific losses of steam with steam from the feed water deaerator in t per 1 t of deaerated water
	Coefficient of auxiliary needs of chemical water treatment
	Steam loss coefficient			accepted
	Estimated heat supply from the boiler house for heating and ventilation
	Estimated heat supply for hot water supply for the day of the highest water consumption
	Heat supply to industrial consumers in the form of steam
	Return of condensate from industrial consumers (80%)

Table 1.5

Calculation of the thermal scheme of a heating and production boiler house with steam boilers KE-25-14s for a closed heat supply system.

	Name		Estimated	Design modes
pos. Exodus. data				Maximum winter	At the average temperature of the coldest period	At the outside air temperature at the break point of the network water temperature graph.
	Outside air temperature at the break point of the heating water temperature curve		t vn -0.354 (t vn - t r.o.)			18-0,354* *(18+24)= =3,486
	The coefficient of reduction of heat consumption for heating and ventilation, depending on the outdoor temperature		(t vn - t "n) / (t vn - t p.o)		(18-(-10))/(18-(-23))=0,67	(18-0,486)/ /(18-(-24))= =0,354


	Estimated heat supply for heating and ventilation		Q max s *K s		15,86*0,67= 10,62
	The value of the coefficient K ov to the power of 0.8
	The temperature of the direct network water at the outlet of the boiler room		18+64.5* K 0.8 ov +64.5K ov		18+64,50,73+67,50,67= 110,3
	Return water temperature
	Total heat supply for heating, ventilation and hot water supply in winter modes		Q ov + Q cf gv
	Estimated consumption of network water in winter modes		Q ov + gv * 10 3 / (t 1 -t 2) * C
	Heat supply for hot water supply in summer mode


	Estimated network water consumption in summer mode		Q l gv * 10 3 / (t 1 -t 2) * C
	The volume of network water in the water supply system		q sys *Q d max
	Consumption of make-up water to replenish leaks in the heating network		0.005G sys 1/3.60
	Amount of return network water	G net.	G set - G ut
	Return network water temperature in front of network pumps		t 2 G set. arr + TG ut / G set
	Steam consumption for network water heaters		G set (t 1 -t 3) / (i 2 /4.19-t kb) 0.98
	Amount of condensate from network water heaters





	Steam load on the boiler house, minus the steam consumption for deaeration and for heating raw water, softened to feed the boilers, and without taking into account intra-boiler losses		D consumption + D b + D maz	4,98+7,14= 12,12	4,98+9,13= 14,11	4,98+2,93= 7,91	0,53+0,43= 0,96
	Amount of condensate from network water heaters and production		G b + G cons	7,19+3,98= 11,12	9,13+3,98= 13,11	2,93+3,98= 6,91	0,43+0,42= 0,85

				0,148*0,6= 0,089	0,148*0,70= 0,104	0,148*0,39= 0,060	0,148*0,05= 0,007




	Amount of blowdown water at the outlet of the continuous blowdown separator		G "pr - D pr	0,6-0,089= 0,511	0,70-0,104= 0,596	0,32-0,060= 0,33	0,05-0,007= 0,043
	Boiler steam losses			0,021212 0,24	0,02*14,11= 0,28	0,02*7,91= 0,16	0,02*0,96= 0,02
			D + G pr + P ut
	Evaporation from the deaerator			0,002*13,44= 0,027	0,002*15,53= 0,03	0,002*9,02= 0,018	0,002*2,07= 0,004
	The amount of softened water entering the deaerator		(D cont -G cont) + + G "pr + D sweat + D ex + G ut
			To s.n. tail *G tail
			G St * (T 3 -T 1) * C / (i 2 -i 6) * 0.98
	The amount of condensate from the raw water heaters entering the deaerator

	The total weight of flows entering the deaerator (except for heating steam)		G to + G tail + G s + D pr -D vy
	The share of condensate from network water heaters and from production in the total weight of flows entering the deaerator


	Steam consumption for feed water deaerator and raw water heating			0,75+0,13= 0,88	0,82+0,13= 0,95	0,56+0,12= 0,88	0,15+0,024= 0,179
			D+(D g + D s)	12,12+0,88= 13,00	14,11+0,9= 15,06	7,91+0,68= 8,59	0,96+0,179= 1,13
	Boiler steam losses		D "* (K pot / (1-K pot))


	Amount of blowdown water entering the continuous blowdown separator
	The amount of steam at the outlet of the continuous blowdown separator		G pr * (i 7 * 0.98-i 8) / (i 3 -i 8)
	The amount of blowdown water at the outlet of their continuous blowdown separator
	The amount of water to feed the boilers		D sum + G pr
	The amount of water leaving the deaerator		G pit + G ut
	Evaporation from the deaerator
	The amount of softened water entering the deaerator		(D cont -G cont) -G "pr + D sweat + D ex + G ut


	The amount of raw water entering the chemical water treatment		K s.n. tail *G tail
	Steam consumption for heating raw water		G s. in. (T 3 -T 1) C / (i 2 -i 8) * 0.98
	The amount of condensate entering the deaerator from raw water heaters
	The total weight of flows entering the deaerator (except for heating steam)		G k + G tail + G c + D pr -D vy
	Share of condensate from heaters			11,12/13,90= 0,797	13,11/16,04= 0,82
	Specific steam consumption per deaerator
	Absolute steam flow to the deaerator
	Steam consumption for deaeration of feed water and heating of raw water

	Steam load on the boiler house without taking into account intra-boiler losses			12,12+0,87= 12,9	14,11+0,87= 15,07	7,91+0,67= 8,58	0,96+0,17= 1,13

	Percentage of steam consumption for auxiliary needs of the boiler house (deaeration raw water heating)		(D g + D s) / D sum * 100
	Number of operating boilers		D sum / D to nom
	Percentage of loading of operating steam boilers		D sum / D to nom * N k.r. * *100%
	The amount of water passed in addition to the network water heaters (through the jumper between the pipelines of the direct and return network water)		G set *(t max 1 -t 1)/ /(t max 1 -t 3)



	The amount of water passed through the network water heaters		G set - G set.p.		94,13-40,22= 53,91	66,56-49,52= 17,04	9,20-7,03= 2,17
	The temperature of the network water at the inlet to the steam-water heaters		/ (i 2 - t k. b. s.)
	Soft water temperature at the outlet of the blowdown water cooler		T 3 + G "pr / G tail * (i 8 / c --t pr)
	The temperature of softened water entering the deaerator from the steam cooler		T 4 + D issue / G tail * (i 4 -i 5) / c

Calculation of the thermal scheme.

The principal thermal diagram indicates the main equipment (boilers, pumps, deaerators, heaters) and the main pipelines.

1. Description of the thermal scheme.

Saturated steam from boilers with a working pressure of P = 0.8 MPa enters the common steam line of the boiler room, from which part of the steam is taken to the equipment installed in the boiler room, namely: to the network water heater; hot water heater; deaerator. The other part of the steam is directed to the production needs of the enterprise.

Condensate from the production consumer returns by gravity, in the amount of 30% at a temperature of 80 ° C, to the condensate collector and then is sent to the hot water tank by a condensate pump.

The heating of network water, as well as heating of hot water, is carried out by steam in two heaters connected in series, while the heaters operate without steam traps, the exhaust condensate is sent to the deaerator.

The deaerator also receives chemically purified water from the HVO, which makes up for the loss of condensate.

The raw water pump sends water from the city water supply to the HVO and to the hot water tank.

Deaerated water with a temperature of about 104 ° C is pumped into the economizers by a feed pump and then enters the boilers.

Make-up water for the heating system is taken by the make-up pump from the hot water tank.

The main purpose of calculating the thermal scheme is:

determination of total heat loads, consisting of external loads and steam consumption for own needs,

determination of all heat and mass flows necessary for the selection of equipment,

determination of initial data for further technical and economic calculations (annual production of heat, fuel, etc.).

The calculation of the thermal scheme allows you to determine the total steam output of the boiler plant in several modes of operation. The calculation is made for 3 characteristic modes:

maximum winter

the coldest month

2. Initial data for calculating the thermal scheme.

Physical quantity	Designation	Rationale	The value of the value for the characteristic modes of operation of the boiler house.
Physical quantity	Designation	Rationale	Maximum - winter	The coldest month	summer
Heat consumption for production needs, Gcal/h.
Heat consumption for heating and ventilation needs, Gcal/h.
Water consumption for hot water supply, t/h.
Hot water temperature, o C		SNiP 2.04.07-86.
Estimated outdoor temperature for the city of Yakutsk, o C:
– when calculating the heating system:
– when calculating the ventilation system:
Condensate return by industrial consumer, %
Enthalpy of saturated steam with a pressure of 0.8 MPa, Gcal/t.		Water vapor table
Boiler water enthalpy, Gcal/t.
Enthalpy of feed water, Gcal/t.
Condensate enthalpy at t= 80 o C, Gcal/t.
Enthalpy of condensate with “flying” steam, Gcal/t.
Temperature of condensate returned from production, o C
Raw water temperature, o С
Periodic purge, %
Water loss in closed system heat supply, %
Steam consumption for auxiliary needs of the boiler house, %
Steam losses in the boiler house and at the consumer, %
Raw water consumption coefficient for own needs of HVO.

What do you get when ordering a heating system for children's and educational institutions in the company "Integra Engineering"

Heating system of a school, kindergarten, college, university: a range of services of our company

project development internal system heating of educational institutions;
thermal and hydraulic calculation boiler school, kindergarten, university;
reconstruction and modernization of the heating system;
mounting internal networks and heating equipment;
selection and boiler installation heating systems for children's and educational institutions;
calculation, selection and installation underfloor heating systems;
maintenance and repair heating and boiler equipment;
harmonization with supervisory authorities.

For educational institutions in areas with an estimated outside air temperature of -40 ° C and below, it is allowed to use water with additives that prevent it from freezing (no harmful substances of the 1st and 2nd hazard classes according to GOST 12.1.005 should be used as additives), and in the buildings of preschool institutions it is not allowed to use a coolant with additives harmful substances 1-4th hazard classes.

Design and installation of autonomous boiler houses and heating systems in schools, preschool and educational institutions

The heating system of schools, kindergartens and other children's and educational institutions (universities, vocational schools, colleges) in cities is connected to central system heating and hot, which is powered by a city thermal power plant or its own boiler house. In rural areas, an autonomous scheme is used, located in special room own boiler room. In the case of a gasified area, the boiler operates from natural gas, in small school and preschool institutions boilers are used low power operating on solid or liquid fuels or electricity.

When designing an internal heating system, microclimatic standards for air temperature in classrooms, school classes, canteens, gyms, swimming pools and other premises should be taken into account. Various by technical purpose building zones should have their own heating networks with water and heat meters.

For heating sports halls, along with the water system, air system heating, combined with forced ventilation and operating from the same boiler room. A device for water floor heating may be present in locker rooms, bathrooms, showers, pools and other rooms, if any. On the entrance groups thermal curtains are installed in large educational institutions.

The heating system of a kindergarten, school, educational institution - a list of works on the organization and reconstruction of the heating system:

identification of need when creating a project or sketch diagram heat supply;
choice ways and places installation of pipelines;
selection equipment and materials appropriate quality;
thermal and hydraulic calculation of the boiler room, definition of technology and its verification for the requirements of SNiP;
the possibility of increasing productivity, connection additional equipment (if needed);
load calculation and performance of the heating system as a whole and in terms of the area of heated premises;
during the reconstruction of the object - site preparation, foundation and walls for subsequent installation;
defecting sections of the building heating system;
calculation of terms and costs works and equipment, coordination of estimates;
supply of equipment and execution of works on time at a pre-agreed cost estimate.

For heating appliances and pipelines in kindergartens, stairwells and lobbies must be provided protective fences and thermal insulation pipelines.

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Introduction

1. Calculation of heating, ventilation and hot water supply of a school for 90 students

1.1 a brief description of schools

1.2 Determination of heat loss through the outer fences of the garage

1.3 Calculation of the heating surface area and selection heating appliances central heating systems

1.4 Calculation of school air exchange

1.5 Selection of heaters

1.6 Calculation of heat consumption for hot water supply of the school

2. Calculation of heating and ventilation of other objects according to the given scheme No. 1 with centralized and local heat supply

2.1 Calculation of heat consumption for heating and ventilation according to the aggregated standards for residential and public facilities

2.2 Calculation of heat consumption for hot water supply for residential and public buildings

3.Construction of the annual schedule of heat load and selection of boilers

3.1 Building an annual heat load graph

3.2 Choice of heat transfer medium

3.3 Boiler selection

3.4 Construction of an annual schedule for regulating the supply of a thermal boiler house

Bibliography

Introduction

The agro-industrial complex is an energy-intensive branch of the national economy. A large number of energy is spent on heating industrial, residential and public buildings, creating an artificial microclimate in livestock buildings and structures of protective soil, drying of agricultural products, production, obtaining artificial cold and for many other purposes. Therefore, the energy supply of agribusiness enterprises includes a wide range of tasks related to the production, transmission and use of thermal and electrical energy using traditional and non-traditional energy sources.

This course project proposes a variant of integrated energy supply locality:

for a given scheme of agro-industrial complex objects, an analysis of the need for thermal energy, electricity, gas and cold water;

Calculation of loads of heating, ventilation and hot water supply;

determined required power boiler room, which could meet the needs of the economy in heat;

Boilers are selected.

calculation of gas consumption,

1. Calculation of heating, ventilation and hot water supply of a school for 90 students

1 . 1 Brief hacharacteristics of the school

Dimensions 43.350x12x2.7.

The volume of the room V = 1709.34 m 3.

External longitudinal walls - load-bearing, are made of facing and finishing, thickened bricks of the KP-U100 / 25 brand according to GOST 530-95 on a cement-sand mortar M 50, 250 and 120 mm thick and 140 mm of insulation - expanded polystyrene between them.

Internal walls - are made of hollow, thickened ceramic brick brand KP-U100/15 according to GOST 530-95, on solution M50.

Partitions - are made of brick KP-U75/15 according to GOST 530-95, on mortar M 50.

Roof - roofing material (3 layers), cement-sand screed 20mm, expanded polystyrene 40mm, roofing material in 1 layer, cement-sand screed 20mm and reinforced concrete slab;

Floors - concrete M300 and soil compacted with crushed stone.

The windows are double with paired wooden binding, the size of the windows is 2940x3000 (22 pcs) and 1800x1760 (4 pcs).

Exterior wooden single doors 1770x2300 (6 pcs)

Design parameters of outdoor air tn = - 25 0 С.

Estimated winter outdoor air temperature tn.a. = - 16 0 С.

Estimated temperature of the internal air tv = 16 0 С.

The humidity zone of the area is normal dry.

Barometric pressure 99.3 kPa.

1.2 School air exchange calculation

The learning process takes place in the school. It is characterized by a long stay of a large number of students. There are no harmful emissions. The air shift coefficient for the school will be 0.95…2.

where Q is air exchange, m?/h; Vp - room volume, m?; K - the frequency of air exchange is accepted = 1.

Fig.1. Room dimensions.

Room volume:

V \u003d 1709.34 m 3.

Q \u003d 1 1709.34 \u003d 1709.34 m 3 / h.

In the room we arrange general ventilation combined with heating. natural exhaust ventilation we arrange in the form of exhaust shafts, the cross-sectional area F of the exhaust shafts is found by the formula: F \u003d Q / (3600 ? n k.vn) . , having previously determined the air speed in the exhaust shaft with a height h = 2.7 m

n k.vn. = = 1.23 m/s

F \u003d 1709.34 / (3600 1.23) \u003d 0.38 m?

Number of exhaust shafts

n vsh \u003d F / 0.04 \u003d 0.38 / 0.04 \u003d 9.5? ten

We accept 10 exhaust shafts 2 m high with a living section of 0.04 m? (with dimensions 200 x 200 mm).

1.3 Determination of heat losses through the external enclosures of the room

Heat losses through the internal enclosures of the premises are not taken into account, because the temperature difference in the shared rooms does not exceed 5 0 C. We determine the resistance to heat transfer of enclosing structures. Heat transfer resistance outer wall(Fig. 1) we find by the formula, using the data in Table. 1 knowing that thermal resistance heat perception inner surface fences Rv \u003d 0.115 m 2 0 C / W

where Rв - thermal resistance to heat absorption of the inner surface of the fence, m?·?С / W; - the sum of the thermal resistances of the thermal conductivity of individual layers m - layered fence thickness di (m), made of materials with thermal conductivity li, W / (m ? C), the values of l are given in Table 1; Rn - thermal resistance to heat transfer outer surface fencing Rn \u003d 0.043 m 2 0 C / W (for external walls and non-attic floors).

Fig.1 Structure of wall materials.

Table 1 Thermal conductivity and width of wall materials.

Heat transfer resistance of outer wall:

R 01 \u003d m? ? C / W.

2) Heat transfer resistance of windows Ro.ok \u003d 0.34 m 2 0 C / W (we find from the table on p. 8)

Heat transfer resistance of external doors and gates 0.215 m 2 0 C / W (we find from the table on p. 8)

3) Heat transfer resistance of the ceiling for a non-attic floor (Rv \u003d 0.115 m 2 0 C / W, Rn \u003d 0.043 m 2 0 C / W).

Calculation of heat losses through floors:

Fig.2 ceiling structure.

Table 2 Thermal conductivity and width of floor materials

Ceiling heat transfer resistance

m 2 0 C / W.

4) Heat losses through the floors are calculated by zones - strips 2 m wide, parallel to the outer walls (Fig. 3).

Areas of floor zones minus basement area:

F1 \u003d 43 2 + 28 2 \u003d 142 m 2

F1 \u003d 12 2 + 12 2 \u003d 48 m 2,

F2 \u003d 43 2 + 28 2 \u003d 148 m 2

F2 \u003d 12 2 + 12 2 \u003d 48 m 2,

F3 \u003d 43 2 + 28 2 \u003d 142 m 2

F3 \u003d 6 0.5 + 12 2 \u003d 27 m 2

Areas of basement floor zones:

F1 \u003d 15 2 + 15 2 \u003d 60 m 2

F1 \u003d 6 2 + 6 2 \u003d 24 m 2,

F2 \u003d 15 2 + 15 2 \u003d 60 m 2

F2 \u003d 6 2 \u003d 12 m 2

F1 \u003d 15 2 + 15 2 \u003d 60 m 2

Floors located directly on the ground are considered non-insulated if they consist of several layers of materials, the thermal conductivity of each of which is l? 1.16 W / (m 2 0 C). Floors are considered to be insulated, the insulation layer of which has l<1,16 Вт/м 2 0 С.

Heat transfer resistance (m 2 0 C / W) for each zone is determined as for non-insulated floors, because thermal conductivity of each layer l? 1.16 W / m 2 0 C. So, heat transfer resistance Ro \u003d Rn.p. for the first zone is 2.15, for the second - 4.3, for the third - 8.6, the rest - 14.2 m 2 0 C / W.

5) Total area of window openings:

Fok \u003d 2.94 3 22 + 1.8 1.76 6 \u003d 213 m 2.

Total area of external doorways:

Fdv \u003d 1.77 2.3 6 \u003d 34.43 m 2.

The area of the outer wall minus window and door openings:

Fn.s. \u003d 42.85 2.7 + 29.5 2.7 + 11.5 2.7 + 14.5 2.7 + 3 2.7 + 8.5 2.7 - 213-34.43 \u003d 62 m 2 .

Basement wall area:

Fn.s.p =14.5 2.7+5.5 2.7-4.1=50

6) Ceiling area:

Fpot \u003d 42.85 12 + 3 8.5 \u003d 539.7 m 2,

where F is the area of \u200b\u200bthe fence (m?), Which is calculated with an accuracy of 0.1 m? (the linear dimensions of the enclosing structures are determined with an accuracy of 0.1 m, observing the measurement rules); tv and tn - design temperatures of indoor and outdoor air, ? С (app. 1 ... 3); R 0 - total resistance to heat transfer, m 2 0 C / W; n - coefficient depending on the position of the outer surface of the fence in relation to the outside air, we will take the values of the coefficient n \u003d 1 (for external walls, non-attic coverings, attic floors with steel, tiled or asbestos-cement roofing along a sparse crate, floors on the ground)

Heat loss through external walls:

Fns = 601.1 W.

Heat loss through the outer walls of the basement:

Fn.s.p = 130.1W.

Fn.s. =F n.s. + F n.s.p. \u003d 601.1 + 130.1 \u003d 731.2 W.

Heat loss through windows:

Fok \u003d 25685 W.

Heat loss through doorways:

Fdv \u003d 6565.72 W.

Heat loss through the ceiling:

Fpot = = 13093.3 W.

Heat loss through the floor:

Fpol \u003d 6240.5 W.

Heat loss through the basement floor:

Fpol.p = 100 W.

F floor \u003d F floor. + Ф pol.p. \u003d 6240.5 + 100 \u003d 6340.5 W.

Additional heat losses through external vertical and inclined (vertical projection) walls, doors and windows depend on various factors. The values of Fdob are calculated as a percentage of the main heat losses. Additional heat loss through the outer wall and windows facing north, east, northwest and northeast is 10%, southeast and west - 5%.

Additional losses for infiltration of outdoor air for industrial buildings are taken in the amount of 30% of the main losses through all fences:

Finf \u003d 0.3 (Fn.s. + Focal. + Fpot. + Fdv + Fpol.) \u003d 0.3 (731.2 + 25685 + 13093.3 + 6565.72 + 6340.5) \u003d 15724, 7 W

Thus, the total heat loss is determined by the formula:

Fogr = 78698.3 W.

1.4 Calculation of the heating surface area and selectionheating devices of central heating systems

The most common and versatile heating devices in use are cast-iron radiators. They are installed in residential, public and various industrial buildings. We use steel pipes as heating devices in industrial premises.

Let us first determine the heat flow from the pipelines of the heating system. The heat flux given off to the room by openly laid non-insulated pipelines is determined by formula 3:

Ftr = Ftr ktr (tfr - tv) s,

where Ftr = p? d l is the area of the outer surface of the pipe, m?; d and l - outer diameter and length of the pipeline, m (diameters of main pipelines are usually 25 ... 50 mm, risers 20 ... 32 mm, connections to heating devices 15 ... 20 mm); ktr - heat transfer coefficient of the pipe W / (m 2 0 С) is determined according to table 4 depending on the temperature difference and the type of coolant in the pipeline, ?С; h - coefficient equal to the supply line located under the ceiling, 0.25, for vertical risers - 0.5, for the return line located above the floor - 0.75, for connections to the heating device - 1.0

Supply pipeline:

Diameter-50mm:

F1 50mm = 3.14 73.4 0.05 = 11.52 m?;

Diameter 32mm:

F1 32mm = 3.14 35.4 0.032 = 3.56 m?;

Diameter-25mm:

F1 25mm = 3.14 14.45 0.025 = 1.45 m?;

Diameter-20:

F1 20mm = 3.14 32.1 0.02 = 2.02 m?;

Return pipeline:

Diameter-25mm:

F2 25mm = 3.14 73.4 0.025 = 5.76 m?;

Diameter-40mm:

F2 40mm = 3.14 35.4 0.04 = 4.45 m?;

Diameter-50mm:

F2 50mm = 3.14 46.55 0.05 = 7.31 m?;

The heat transfer coefficient of pipes for the average difference between the water temperature in the device and the air temperature in the room (95 + 70) / 2 - 15 \u003d 67.5 ° С is taken equal to 9.2 W / (m? ° С). in accordance with the data in table 4 .

Direct heat pipe:

Ф p1.50mm \u003d 11.52 9.2 (95 - 16) 1 \u003d 8478.72 W;

Ф p1.32mm \u003d 3.56 9.2 (95 - 16) 1 \u003d 2620.16 W;

Ф p1.25mm \u003d 1.45 9.2 (95 - 16) 1 \u003d 1067.2 W;

Ф p1.20mm \u003d 2.02 9.2 (95 - 16) 1 \u003d 1486.72 W;

Return heat pipe:

Ф p2.25mm \u003d 5.76 9.2 (70 - 16) 1 \u003d 2914.56 W;

Ф p2.40mm \u003d 4.45 9.2 (70 - 16) 1 \u003d 2251.7 W;

Ф p2.50mm \u003d 7.31 9.2 (70 - 16) 1 \u003d 3698.86 W;

Total heat flow from all pipelines:

F tr \u003d 8478.72 + 2620.16 + 1067.16 + 1486.72 + 2914.56 + 2251.17 + 3698.86 \u003d 22517.65 W

The required heating surface area (m?) of devices is approximately determined by formula 4:

where Fogr-Ftr - heat transfer of heating devices, W; Фfr - heat transfer of open pipelines located in the same room with heating devices, W;

kpr - heat transfer coefficient of the device, W / (m 2 0 С). for water heating tpr \u003d (tg + tо) / 2; tg and tо - design temperature of hot and chilled water in the device; for steam heating low pressure take tpr = 100 ?С, in high-pressure systems tpr is equal to the steam temperature in front of the device at its corresponding pressure; tv - design air temperature in the room, ?С; in 1 - correction factor, taking into account the installation method of the heater. With free installation against a wall or in a niche with a depth of 130 mm in 1 = 1; in other cases, values in 1 are taken based on the following data: a) the device is installed against a wall without a niche and is covered with a board in the form of a shelf with a distance between the board and the heater of 40 ... 100 mm; coefficient in 1 \u003d 1.05 ... 1.02; b) the device is installed in a wall niche with a depth of more than 130 mm with a distance between the board and the heater of 40 ... 100 mm, the coefficient in 1 = 1.11 ... 1.06; c) the device is installed in a wall without a niche and closed with a wooden cabinet with slots in the top board and in the front wall near the floor with a distance between the board and the heater equal to 150, 180, 220 and 260 mm, the coefficient of 1, respectively, is 1.25; 1.19; 1.13 and 1.12; in 1 - correction factor in 2 - correction factor that takes into account the cooling of water in pipelines. With open laying of water heating pipelines and with steam heating in 2 \u003d 1. for a hidden laying pipeline, with pump circulation in 2 \u003d 1.04 (single-pipe systems) and in 2 \u003d 1.05 (two-pipe systems with top wiring); in natural circulation, due to an increase in the cooling of water in pipelines, the values \u200b\u200bof 2 should be multiplied by a factor of 1.04.

The required number of sections of cast-iron radiators for the calculated room is determined by the formula:

n = Fpr / fsection,

where fsection is the heating surface area of one section, m? (Table 2).

n = 96 / 0.31 = 309.

The resulting value of n is approximate. If necessary, it is divided into several devices and, by introducing a correction factor of 3, taking into account the change in the average heat transfer coefficient of the device depending on the number of sections in it, they find the number of sections accepted for installation in each heating device:

nset \u003d n in 3;

nset = 309 1.05 = 325.

We install 27 radiators in 12 sections.

heating water supply school ventilation

1.5 Selection of heaters

Heaters are used as heating devices to increase the temperature of the air supplied to the room.

The selection of heaters is determined in the following order:

1. Determine the heat flux (W) going to heat the air:

Fv \u003d 0.278 Q? With? c (tv - tn), (10)

where Q is the volumetric air flow, m?/h; с - air density at temperature tк, kg/m?; ср = 1 kJ/(kg ?С) - specific isobaric heat capacity of air; tk - air temperature after the heater, ?С; tn - initial temperature of the air entering the heater, ?С

Air Density:

c \u003d 346 / (273 + 18) 99.3 / 99.3 \u003d 1.19;

Fv \u003d 0.278 1709.34 1.19 1 (16- (-16)) \u003d 18095.48 W.

Estimated mass air velocity is 4-12 kg/s m?.

3. Then, according to Table 7, we select the model and number of the air heater with an open air area close to the calculated one. With a parallel (along the air) installation of several heaters, their total area of \u200b\u200bthe live section is taken into account. We choose 1 K4PP No. 2 with an air area of 0.115 m? and a heating surface area of 12.7 m?

4. For the selected heater, calculate the actual mass air velocity

5. After that, according to the graph (Fig. 10) for the accepted heater model, we find the heat transfer coefficient k depending on the type of coolant, its speed, and the value of ns. According to the schedule, the heat transfer coefficient k \u003d 16 W / (m 2 0 C)

6. Determine the actual heat flux (W) transferred by the calorific unit to the heated air:

Фк = k F (t?avg - tav),

where k is the heat transfer coefficient, W / (m 2 0 С); F - heating surface area of the air heater, m?; t?av - average temperature of the coolant, ?С, for the coolant - steam - t?av = 95?С; tav - the average temperature of the heated air t?av = (tk + tn) / 2

Fk \u003d 16 12.7 (95 - (16-16) / 2) \u003d 46451 2 \u003d 92902 W.

2 plate heaters KZPP No. 7 provide a heat flow of 92902 W, and the required one is 83789.85 W. Therefore, heat transfer is fully ensured.

The heat transfer margin is = 6%.

1.6 Calculation of heat consumption for hot water supply of the school

The school needs hot water for sanitary needs. The school with 90 seats consumes 5 liters of hot water per day. Total: 50 liters. Therefore, we place 2 risers with a water flow of 60 l / h each (that is, a total of 120 l / h). Taking into account the fact that on average hot water for sanitary needs is used for about 7 hours during the day, we find the amount of hot water - 840 l / day. 0.35 m³/h is consumed per hour at school

Then the heat flow to the water supply will be

FGV. \u003d 0.278 0.35 983 4.19 (55 - 5) \u003d 20038 W

The number of shower cabins for the school is 2. The hourly consumption of hot water by one cabin is Q = 250 l / h, we assume that on average the shower works 2 hours a day.

Then the total consumption of hot water: Q \u003d 3 2 250 10 -3 \u003d 1m 3

FGV. \u003d 0.278 1 983 4.19 (55 - 5) \u003d 57250 W.

F \u003d 20038 + 57250 \u003d 77288 W.

2. Calculation of heat load for district heating

2.1 Rcalculation of heat consumption for heating and ventilation according toconsolidated standards

The maximum heat flow (W) consumed for heating residential and public buildings of the village, included in the district heating system, can be determined by aggregated indicators depending on the living area using the following formulas:

Photograph = c? F,

Photo.l.=0.25 Photo.l., (19)

where c is an aggregated indicator of the maximum specific heat flux consumed for heating 1 m? living space, W/m?. The values \u200b\u200bof are determined depending on the calculated winter temperature of the outside air according to the schedule (Fig. 62); F - living area, m?.

1. For thirteen 16 apartment buildings with an area of 720 m 2 we get:

Photograph \u003d 13 170 720 \u003d 1591200 W.

2. For eleven 8-apartment buildings with an area of 360 m 2 we get:

Photograph \u003d 8 170 360 \u003d 489600 watts.

3. For honey. points with dimensions 6x6x2.4 we get:

Photototal=0.25 170 6 6=1530 W;

4. For an office with dimensions of 6x12 m:

Photo common = 0.25 170 6 12 = 3060 W,

For individual residential, public and industrial buildings, the maximum heat flows (W) consumed for heating and air heating in the supply ventilation system are approximately determined by the formulas:

Phot \u003d qot Vn (tv - tn) a,

Fv \u003d qv Vn (tv - tn.v.),

where q from and q in - specific heating and ventilation characteristics of the building, W / (m 3 0 C), taken according to Table 20; V n - the volume of the building according to the outer measurement without the basement, m 3, is taken according to standard designs or is determined by multiplying its length by its width and height from the planning mark of the earth to the top of the eaves; t in = average design air temperature, typical for most rooms of the building, 0 С; t n \u003d calculated winter temperature of the outside air, - 25 0 С; t N.V. - calculated winter ventilation temperature of the outside air, - 16 0 С; a is a correction factor that takes into account the impact on the specific thermal characteristic of local climatic conditions at tn=25 0 С a = 1.05

Ph = 0.7 18 36 4.2 (10 - (- 25)) 1.05 = 5000.91W,

Fv.tot.=0.4 5000.91=2000 W.

Brigade house:

Phot \u003d 0.5 1944 (18 - (- 25)) 1.05 \u003d 5511.2 W,

School workshop:

Phot \u003d 0.6 1814.4 (15 - (- 25)) 1.05 \u003d 47981.8 W,

Fv \u003d 0.2 1814.4 (15 - (- 16)) \u003d 11249.28 W,

2.2 RCalculation of heat consumption for hot water supply forresidential and public buildings

The average heat flow (W) consumed during the heating period for hot water supply of buildings is found by the formula:

F = q yr. · n f,

Depending on the rate of water consumption at a temperature of 55 0 C, the aggregated indicator of the average heat flux (W) spent on hot water supply of one person will be equal to: is 407 watts.

For 16 apartment buildings with 60 residents, the heat flow for hot water supply will be: \u003d 407 60 \u003d 24420 W,

for thirteen such houses - F g.v. \u003d 24420 13 \u003d 317460 W.

Heat consumption for hot water supply of eight 16-apartment buildings with 60 inhabitants in summer

F g.w.l. = 0.65 F g.w. = 0.65 317460 = 206349 W

For 8 apartment buildings with 30 residents, the heat flow for hot water supply will be:

F \u003d 407 30 \u003d 12210 W,

for eleven such houses - F g.v. \u003d 12210 11 \u003d 97680 W.

Heat consumption for hot water supply of eleven 8-apartment buildings with 30 inhabitants in summer

F g.w.l. = 0.65 F g.w. \u003d 0.65 97680 \u003d 63492 W.

Then the heat flow to the water supply of the office will be:

FGV. = 0.278 0.833 983 4.19 (55 - 5) = 47690 W

Heat consumption for office hot water supply in summer:

F g.w.l. = 0.65 F g.w. = 0.65 47690 = 31000 W

Heat flow for water supply honey. point will be:

FGV. = 0.278 0.23 983 4.19 (55 - 5) = 13167 W

Heat consumption for hot water supply honey. points in summer:

F g.w.l. = 0.65 F g.w. = 0.65 13167 = 8559 W

In the workshops, hot water is also needed for sanitary needs.

The workshop accommodates 2 risers with a water flow of 30 l/h each (i.e. a total of 60 l/h). Considering that, on average, hot water for sanitary needs is used for about 3 hours during the day, we find the amount of hot water - 180 l / day

FGV. \u003d 0.278 0.68 983 4.19 (55 - 5) \u003d 38930 W

The flow of heat consumed for hot water supply of the school workshop in the summer:

Fgw.l \u003d 38930 0.65 \u003d 25304.5 W

Summary table of heat flows

Estimated heat fluxes, W
	Name	Heating	Ventilation	Technical needs

	School for 90 students
	16 sq. house
	Honey. paragraph
	8 apartment building
	school workshop

F total \u003d F from + F to + F g.v. \u003d 2147318 + 13243 + 737078 \u003d 2897638 W.

3. Building an annual chartthermal load and selection of boilers

3.1 Building an annual heat load graph

The annual consumption for all types of heat consumption can be calculated using analytical formulas, but it is more convenient to determine it graphically from the annual heat load schedule, which is also necessary to establish the operating modes of the boiler house throughout the year. Such a schedule is built depending on the duration of various temperatures in a given area, which is determined by Appendix 3.

On fig. 3 shows the annual load schedule of the boiler house serving the residential area of the village and a group of industrial buildings. The graph is built as follows. On the right side, along the abscissa axis, the duration of the boiler house operation in hours is plotted, on the left side - the outside air temperature; heat consumption is plotted along the y-axis.

First, a graph is plotted for changing the heat consumption for heating residential and public buildings, depending on the outside temperature. To do this, the total maximum heat flow spent on heating these buildings is plotted on the y-axis, and the found point is connected by a straight line to the point corresponding to the outdoor air temperature, which is equal to the average design temperature of residential buildings; public and industrial buildings tv = 18 °C. Since the beginning of the heating season is taken at a temperature of 8 °C, line 1 of the graph up to this temperature is shown as a dotted line.

The heat consumption for heating and ventilation of public buildings in the function tn is an inclined straight line 3 from tv = 18 °C to the calculated ventilation temperature tn.v. for this climatic region. At lower temperatures, room air is mixed with the supply air, i.e. recirculation occurs, and the heat consumption remains unchanged (the graph runs parallel to the x-axis). In a similar way, graphs of heat consumption for heating and ventilation of various industrial buildings are built. The average temperature of industrial buildings tv = 16 °C. The figure shows the total heat consumption for heating and ventilation for this group of objects (lines 2 and 4 starting from a temperature of 16 °C). Heat consumption for hot water supply and technological needs does not depend on tn. The general graph for these heat losses is shown by straight line 5.

The total graph of heat consumption depending on the outdoor air temperature is shown by a broken line 6 (the break point corresponds to tn.a.), cutting off on the y-axis a segment equal to the maximum heat flow consumed for all types of consumption (?Fot + ?Fv + ?Fg. in. + ?Ft) at the calculated outdoor temperature tn.

Adding the total load received 2.9W.

To the right of the abscissa axis, for each outdoor temperature, the number of hours of the heating season (on a cumulative total) is plotted, during which the temperature was kept equal to or lower than that for which the construction is being made (Appendix 3). And through these points draw vertical lines. Further, ordinates are projected onto these lines from the total heat consumption graph, corresponding to the maximum heat consumption at the same outdoor temperatures. The obtained points are connected by a smooth curve 7, which is a graph of the heat load for the heating period.

The area bounded by the coordinate axes, curve 7 and horizontal line 8, showing the total summer load, expresses the annual heat consumption (GJ / year):

Qyear = 3.6 10 -6 F m Q m n ,

where F is the area of the annual heat load schedule, mm?; m Q and m n are the scales of heat consumption and the operating time of the boiler house, W/mm and h/mm, respectively.

Qyear = 3.6 10 -6 9871.74 23548 47.8 = 40001.67J/year

Of which the share of the heating period is 31681.32 J / year, which is 79.2%, for the summer 6589.72 J / year, which is 20.8%.

3.2 The choice of coolant

We use water as a heat carrier. So how is the thermal design load Fr? 2.9 MW, which is less than the condition (Fr? 5.8 MW), it is allowed to use water with a temperature of 105 ° C in the supply line, and the water temperature in the return pipeline is assumed to be 70 ° C. At the same time, we take into account that the temperature drop in the consumer's network can reach up to 10%.

The use of superheated water as a heat carrier gives greater savings in pipe metal due to a decrease in their diameter, reduces the energy consumption of network pumps, since the total amount of water circulating in the system is reduced.

Since for some consumers steam is required for technical purposes, additional heat exchangers must be installed at consumers.

3.3 Boiler selection

Heating and industrial boilers, depending on the type of boilers installed in them, can be water-heating, steam or combined - with steam and hot-water boilers.

The choice of conventional cast-iron boilers with a low-temperature coolant simplifies and reduces the cost of local energy supply. For heat supply, we accept three Tula-3 cast-iron water boilers with a thermal power of 779 kW each with gas fuel with the following characteristics:

Estimated power Fr = 2128 kW

Installed power Fu = 2337 kW

Heating surface area - 40.6 m?

Number of sections - 26

Dimensions 2249×2300×2361 mm

Maximum temperature heating water - 115?

Efficiency when working on gas c.a. = 0.8

When operating in steam mode, excess steam pressure - 68.7 kPa

When operating in steam mode, the power is reduced by 4 - 7%

3.4 Construction of an annual schedule for regulating the supply of a thermal boiler house

Due to the fact that the heat load of consumers varies depending on the outdoor temperature, the mode of operation of the ventilation and air conditioning system, the flow of water for hot water supply and technological needs, economical modes of heat generation in the boiler house should be provided by central regulation of heat supply.

In water heating networks, high-quality regulation of heat supply is used, carried out by changing the temperature of the coolant at a constant flow rate.

The graphs of water temperatures in the heating network are tp = f (tn, ?С), tо = f (tн, ?С). Having built a graph according to the method given in the work for tn = 95? С; to = 70 °С for heating (it is taken into account that the temperature of the heat carrier in the hot water supply network should not fall below 70 °С), tpv = 90 °С; tov = 55 ? С - for ventilation, we determine the ranges of change in the temperature of the coolant in the heating and ventilation networks. On the abscissa axis, the values of the outside temperature are plotted, on the ordinate axis - the temperature of the network water. The origin of coordinates coincides with the calculated internal temperature for residential and public buildings (18 °C) and the coolant temperature, also equal to 18 °C. At the intersection of perpendiculars restored to the coordinate axes at points corresponding to temperatures tp = 95 ° C, tn = -25 ° C, point A is found, and by drawing a horizontal straight line from the return water temperature of 70 ° C, point B. Connecting points A and In with the origin of coordinates, we get a graph of the change in the temperature of the direct and return water in the heating network, depending on the outdoor temperature. In the presence of a hot water supply load, the temperature of the coolant in the supply line of an open type network should not fall below 70 ° C, therefore the temperature graph for the supply water has a break point C, to the left of which f p \u003d const. The supply of heat for heating at a constant temperature is regulated by changing the flow rate of the coolant. Minimum temperature return water is determined if a vertical line is drawn through point C until it intersects with the return water graph. The projection of the point D on the y-axis shows the smallest value of pho. The perpendicular, reconstructed from the point corresponding to the calculated outdoor temperature (-16 ? C), intersects lines AC and BD at points E and F, showing the maximum temperatures of the supply and return water for ventilation systems. That is, the temperatures are 91 ?С and 47 ?С, respectively, which remain unchanged in the range from tn.v and tn (lines EK and FL). In this range of outdoor temperatures, ventilation units operate with recirculation, the degree of which is regulated so that the temperature of the air entering the heaters remains constant.

The graph of water temperatures in the heating network is shown in Fig.4.

Fig.4. Graph of water temperatures in the heating network.

Bibliography

1. Efendiev A.M. Design of energy supply for agro-industrial complex enterprises. Toolkit. Saratov 2009.

2. Zakharov A.A. Workshop on the use of heat in agriculture. Second edition, revised and enlarged. Moscow Agropromizdat 1985.

3. Zakharov A.A. The use of heat in agriculture. Moscow Kolos 1980.

4. Kiryushatov A.I. Thermal power plants for agricultural production. Saratov 1989.

5. SNiP 2.10.02-84 Buildings and premises for storage and processing of agricultural products.

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INTRODUCTION

1.1 General information about the building
1.2 Climatological data

2.6 About the VALTEC program

3.3 Initial data

4.1.2 Installing radiators
4.1.3 Installation of shut-off valves and control devices

5. AUTOMATION OF THE HEAT POINT

5.1 General provisions and requirements for the automation system
5.2 Metrological assurance

5.2.1 Locations for measuring instruments
5.2.2 Types and specifications of pressure gauges
5.2.3 Types and specifications of thermometers

5.3 Radiator thermostats
5.4 Heat consumption metering unit

5.4.1 General requirements for the metering unit and metering devices
5.4.2 Characteristics and principle of operation of the heat meter "Logic"

5.5 Dispatch and control system structure

6. TECHNICAL AND ECONOMIC SECTION

6.1 The problem of choosing a heating system in Russia
6.2 Main steps in choosing a heating system
7. LIFE SAFETY
7.1 Occupational safety measures

7.1.1 Piping installation safety
7.1.2 Safety when installing heating systems
7.1.3 Safety regulations for the maintenance of heating substations

7.2 List of environmental protection measures

CONCLUSION
LIST OF USED SOURCES
APPENDIX 1 Thermal engineering calculations
APPENDIX 2 Calculation of heat losses
APPENDIX 3 Calculation of heating devices
APPENDIX 4 Hydraulic calculation of the heating system
APPENDIX 5. Selection of plate heat exchanger
APPENDIX 6. SONO 1500 CT DANFOSS technical data
APPENDIX 7. Technical characteristics of the heat calculator "Logic SPT943.1"
APPENDIX 8. Technical data of the electronic controller ECL Comfort 210
APPENDIX 9. Specification of the equipment of the heat substation

INTRODUCTION

Energy consumption in Russia, as well as throughout the world, is steadily increasing, and, above all, to provide heat to the engineering systems of buildings and structures. It is known that more than one third of all fossil fuel produced in our country is spent on heat supply to civil and industrial buildings.

The main heat costs for household needs in buildings (heating, ventilation, air conditioning, hot water supply) are heating costs. This is due to the operating conditions of buildings during the heating season in most of Russia. At this time, heat losses through the external enclosing structures significantly exceed internal heat releases (from people, lighting fixtures, equipment). Therefore, in order to maintain a normal microclimate and temperature conditions in residential and public buildings, it is necessary to equip them with heating installations and systems.

Thus, heating is called artificial, with the help of a special installation or system, heating the premises of a building to compensate for heat losses and maintain temperature parameters in them at a level determined by the conditions of thermal comfort for people in the room.

The last decade has also seen a steady increase in the cost of all fuels. This is due both to the transition to the conditions of a market economy, and to the complication of fuel extraction during the development of deep deposits in certain regions of Russia. In this regard, it is becoming increasingly important to solve the problems of energy saving by increasing the heat resistance of the building's external building envelope, and saving the consumption of thermal energy at different times and under different environmental conditions by regulating with the help of automatic devices.

Important in modern conditions is the task of instrumental accounting of actually consumed thermal energy. This issue is fundamental in the relationship between the energy supply organization and the consumer. And the more efficiently it is solved within the framework of a single building heat supply system, the more expedient and noticeable is the efficiency of applying energy saving measures.

Summarizing the above, we can say that a modern building heat supply system, and especially a public or administrative building, must meet the following requirements:

Ensuring the required thermal conditions in the room. Moreover, the absence of both underheating and excess of air temperature in the room is important, since both facts lead to a lack of comfort. This, in turn, can lead to reduced productivity and poor health for people arriving on the premises;

The ability to regulate the parameters of the heat supply system and, as a result, the temperature parameters inside the premises, depending on the desires of consumers, the time and characteristics of the office building and the outdoor temperature;

Maximum independence from the parameters of the heat carrier in district heating networks and district heating modes;

Accurate accounting of actually consumed heat for the needs of heat supply, ventilation and hot water supply.

The purpose of this graduation project is the design of the heating system of the school building, located at the address: Vologda region, with. Koskovo, Kichmengsko-Gorodetsky district.

The school building is two-story with axial dimensions 49.5x42.0, floor height 3.6 m.

On the first floor of the building there are classrooms, sanitary facilities, an electrical room, a dining room, a gym, a medical worker's office, a director's office, a workshop, a cloakroom, a hall and corridors.

On the second floor there is an assembly hall, a teacher's room, a library, labor rooms for girls, classrooms, a dignity. nodes, laboratory, recreation.

The structural scheme of the building is a supporting metal frame of columns and roof trusses with sheathing with Petropanel wall sandwich panels 120 mm thick and galvanized sheet along metal girders.

Heat supply is centralized from the boiler house. Connection point: one-pipe overground heating system. The connection of the heating system is provided according to the dependent scheme. The temperature of the heat carrier in the system is 95-70 0 С. The temperature of the water in the heating system is 80-60 0 С.

1. ARCHITECTURAL AND DESIGN SECTION

1.1 General information about the building

The projected school building is located in the village of Koskovo, Kichmengsko-Gorodets district, Vologda region. The architectural solution of the facade of the building is dictated by the existing building, taking into account new technologies, using modern finishing materials. The planning decision of the building was made on the basis of the design assignment and the requirements of regulatory documents.

On the ground floor there are: a hall, a wardrobe, a director's office, a medical worker's office, classes of the 1st level of education, a combined workshop, toilets for men and women, as well as a separate one for groups with limited mobility, recreation, a dining room, a gym, locker rooms and showers, an electrical panel room.

There is a ramp for access to the first floor.

On the second floor there are: laboratory rooms, high school students' offices, recreation, a library, a teacher's room, an assembly hall with rooms for decorations, toilets for men and women, as well as a separate one for groups with limited mobility.

Number of students - 150 people, including:

Primary school - 40 people;

Secondary school - 110 people.

Teachers - 18 people.

Canteen workers - 6 people.

Administration - 3 people.

Other specialists - 3 people.

Service staff - 3 people.

1.2 Climatological data

Construction area - the village of Koskovo, Kichmengsko-Gorodetsky district, Vologda region. We accept climatic characteristics in accordance with the nearest settlement - the city of Nikolsk.

The land plot provided for capital construction is located in meteorological and climatic conditions:

Outside air temperature of the coldest five-day period with a probability of 0.92 - t n \u003d - 34 0 C

The temperature of the coldest day with a probability of 0.92

Average temperature of the period with average daily air temperature<8 0 C (средняя температура отопительного периода) t от = - 4,9 0 С .

Duration of the period with an average daily outdoor temperature<8 0 С (продолжительность отопительного периода) z от = 236 сут.

Normative high-speed wind pressure - 23kgf / m²

The design temperature of the indoor air is taken depending on the functional purpose of each room of the building in accordance with the requirements.

By determining the operating conditions of enclosing structures, depending on the humidity regime of the premises and humidity zones. Accordingly, we accept the operating conditions of external enclosing structures as "B".

1.3 Space-planning and structural solutions of the building

1.3.1 Space-planning elements of the building

The school building is two-story with axial dimensions 42.0x49.5, floor height 3.6m.

There is a heating unit in the basement.

On the first floor of the building there are classrooms, a canteen, a gym, corridors and recreation, a medical worker's office, and toilets.

On the second floor there are classrooms, laboratory rooms, a library, a teacher's room, and an assembly hall.

Space-planning solutions are given in Table 1.1.

Table 1.1

Space-planning solutions of the building

The name of indicators	unit of measurement	Indicators
Number of floors
Basement Height
1st floor height
Height 2 floors
The total area of the building, including:

Structural volume of the building, including
underground part Aboveground part
Built-up area

1.3.2 Information about the building structures of the building

Structural scheme of the building: load-bearing metal frame of columns and roof trusses.

Foundations: the project adopted monolithic reinforced concrete columnar foundations for the building columns. The foundations are made of concrete class. B15, W4, F75. Under the foundations, concrete preparation is provided t = 100 mm from concrete class. B15 performed on compacted sand preparation t = 100 mm from coarse sand.

In the decoration of premises related to the dining room, the following are used:

Walls: grouting and plaster, bottom and top of walls painted with water-dispersion moisture-resistant paint, ceramic tiles;

Floors: porcelain tiles.

In the decoration of premises related to the gym, the following are used:

Walls: grouting;