The first ten discs of the rotor low pressure forged together with the shaft, the other three disks are mounted.

The HP and LPC rotors are connected rigidly with the help of flanges forged integrally with the rotors. The rotors of the LPC and the TVF-120-2 type generator are connected by a rigid coupling.

The steam distribution of the turbine is nozzle. Fresh steam is supplied to a free-standing nozzle box, in which an automatic shutter is located, from where steam flows through bypass pipes to the turbine control valves.

Upon leaving the HPC, part of the steam goes to controlled production extraction, the rest goes to the LPC.

Heating extractions are carried out from the corresponding LPC chambers.

The turbine fixing point is located on the turbine frame on the generator side, and the unit expands towards the front bearing.

To reduce the warm-up time and improve start-up conditions, steam heating of flanges and studs and live steam supply to the HPC front seal are provided.

The turbine is equipped with a barring device that rotates the shafting of the unit with a frequency of 0.0067.

The turbine blade apparatus is designed and configured to operate at a mains frequency of 50 Hz, which corresponds to a rotor rotation of 50. long work turbines at a network frequency of 49 to 50.5 Hz.

The height of the foundation of the turbine unit from the floor level of the condensation room to the floor level of the engine room is 8 m.

2.1 Description of the principle thermal diagram of the turbine PT–80/100–130/13

The condensing device includes a condensing group, an air-removing device, condensate and circulation pumps, ejector circulation system, water filters, pipelines with the necessary fittings.

The condenser group consists of a single condenser with a built-in beam common surface cooling area of ​​3000 m² and is designed to condense the steam entering it, create a vacuum in the turbine exhaust pipe and store condensate, as well as to use the heat of the steam entering the condenser in operating modes according to the heat schedule to heat make-up water in the built-in bundle.

The condenser has a special chamber built into the steam part, in which the HDPE section No. 1 is installed. The rest of the PND are installed by a separate group.

The regenerative plant is designed for heating feed water steam taken from unregulated turbine extractions, and has four stages of HDPE, three stages of HPH and a deaerator. All heaters are surface type.

HPH No. 5,6 and 7 - vertical design with built-in desuperheaters and drain coolers. HPH are supplied with group protection, consisting of automatic exhaust and check valves at the inlet and outlet of water, an automatic valve with an electromagnet, a pipeline for starting and switching off heaters.

HPH and HDPE (except HDPE No. 1) are equipped with control valves for condensate removal, controlled by electronic regulators.

The heating steam condensate drain from the heaters is cascaded. Condensate is pumped out from HDPE No. 2 by a drain pump.

The installation for heating network water includes two network heaters, condensate and network pumps. Each heater is a horizontal steam-to-water heat exchanger with a heat exchange surface of 1300 m², which is formed by straight brass tubes flared on both sides in tube sheets.

3 Choice auxiliary equipment thermal scheme of the station

3.1 Equipment supplied with the turbine

Because condenser, main ejector, low and high pressure are delivered to the designed station together with the turbine, then the following are used for installation at the station:

a) Condenser type 80-KTsST-1 in the amount of three pieces, one for each turbine;

b) The main ejector type EP-3-700-1 in the amount of six pieces, two for each turbine;

c) Low-pressure heaters of the type PN-130-16-10-II (PND No. 2) and PN-200-16-4-I (PND No. 3,4);

d) High-pressure heaters of the type PV-450-230-25 (PVD No. 1), PV-450-230-35 (PVD No. 2) and PV-450-230-50 (PVD No. 3).

The characteristics of the above equipment are summarized in tables 2, 3, 4, 5.

Table 2 - capacitor characteristics

Table 3 - characteristics of the main condenser ejector

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annotation

In this term paper the calculation of the basic thermal scheme of the power plant based on the cogeneration steam turbine

PT-80/100-130/13 at temperature environment, the system of regenerative heating and network heaters, as well as the indicators of thermal efficiency of the turbine plant and power unit are calculated.

The appendix shows a schematic thermal diagram based on the PT-80/100-130/13 turbine plant, a graph of temperatures of network water and a heating load, h-s diagram of steam expansion in the turbine, a diagram of modes of the PT-80/100-130/13 turbine plant, a general view of the heater high pressure PV-350-230-50, specification general view PV-350-230-50, longitudinal section of the turbine plant PT-80/100-130/13, specification of the general view of the auxiliary equipment included in the TPP scheme.

The work is composed on 45 sheets and includes 6 tables and 17 illustrations. 5 literary sources were used in the work.

• Introduction
• Review of scientific and technical literature (Technologies for the generation of electrical and thermal energy)
• 1. Description of the principal thermal diagram of the PT-80/100-130/13 turbine plant
• 2. Calculation of the principal thermal diagram of the PT-80/100-130/13 turbine plant in the increased load mode
• 2.1 Initial data for calculation
• 2.2
• 2.3 Calculation of the parameters of the steam expansion process in the turbine compartments inh- Sdiagram
• 2.4
• 2.5
• 2.6
• 2.6.1 Network heating installation (boiler)
• 2.6.2 High pressure regenerative heaters and feed plant (pump)
• 2.6.3 Feed water deaerator
• 2.6.4 Heater raw water
• 2.6.5
• 2.6.6 Deaerator additional water
• 2.6.7
• 2.6.8 Capacitor
• 2.7
• 2.8 Energy balance of the turbine unit PT-80/100-130/13
• 2.9
• 2.10
• Conclusion
• Bibliography
• Introduction
• For large plants of all industries with high heat consumption, the optimal system of energy supply is from a district or industrial CHP.
• The process of generating electricity at CHP plants is characterized by increased thermal efficiency and higher energy performance compared to condensing power plants. This is explained by the fact that the waste heat of the turbine, which is diverted to a cold source (a heat receiver from an external consumer), is used in it.
• In the work, the calculation of the basic thermal scheme of the power plant on the basis of the production cogeneration turbine PT-80/100-130/13 operating in the design mode at outdoor temperature air.
• The task of calculating the thermal scheme is to determine the parameters, flow rates and directions of the flow of the working fluid in units and assemblies, as well as the total steam consumption, electric power and indicators of thermal efficiency of the station.
• 1. Description of the principal thermal diagram of the turbine plant PT-80/100-130/13

The 80 MW electric power unit consists of an E-320/140 high-pressure drum boiler, a PT-80/100-130/13 turbine, a generator and auxiliary equipment.

The power unit has seven selections. It is possible to carry out two-stage heating of network water in the turbine plant. There is a main and peak boiler, as well as a PVC, which turns on if the boilers cannot provide the required heating of the network water.

Fresh steam from the boiler with a pressure of 12.8 MPa and a temperature of 555 0 It enters the turbine HPC and, after exhausting, is sent to the turbine HPC, and then to the HPC. Having worked out, the steam flows from the LPC to the condenser.

The power unit for regeneration has three high-pressure heaters (HPH) and four low-pressure heaters (LPH). The heaters are numbered from the tail of the turbine unit. The condensate of the heating steam HPH-7 is cascaded into HPH-6, into HPH-5 and then into the deaerator (6 atm). Condensate drain from LPH4, LPH3 and LPH2 is also carried out in cascade in LPH1. Then, from the LPH1, the condensate of the heating steam is sent to the CM1 (see PRT2).

The main condensate and feed water are heated sequentially in PE, SH and PS, in four low-pressure heaters (LPH), in a 0.6 MPa deaerator and in three high-pressure heaters (HPV). Steam is supplied to these heaters from three adjustable and four unregulated turbine steam extractions.

The unit for heating water in the heating network has a boiler plant, consisting of a lower (PSG-1) and an upper (PSG-2) network heaters, fed respectively with steam from the 6th and 7th selections, and PVK. Condensate from the upper and lower network heaters is supplied by drain pumps to mixers SM1 between LPH1 and LPH2 and SM2 between heaters LPH2 and LPH3.

The feed water heating temperature lies within (235-247) 0 С and depends on the initial pressure of fresh steam, the amount of subheating in HPH7.

The first steam extraction (from HPC) is used to heat feed water in HPH-7, the second steam extraction (from HPC) - to HPH-6, the third (from HPC) - to HPH-5, D6ata, for production; the fourth (from CSD) - in LPH-4, the fifth (from CSD) - in LPH-3, the sixth (from CSD) - in LPH-2, deaerator (1.2 atm), in PSG2, in PSV; the seventh (from CND) - in PND-1 and PSG1.

To make up for losses, the scheme provides for the intake of raw water. Raw water is heated in the raw water heater (RWS) to a temperature of 35 o C, then, after chemical treatment, it enters the deaerator 1.2 ata. To ensure heating and deaeration of additional water, the heat of steam from the sixth extraction is used.

Steam from the sealing rods in the amount of D pcs = 0.003D 0 goes to the deaerator (6 atm). Steam from the extreme seal chambers is directed to the SH, from the middle seal chambers to the PS.

Boiler blowdown - two-stage. Steam from the expander of the 1st stage goes to the deaerator (6 atm), from the expander of the 2nd stage to the deaerator (1.2 atm). Water from the expander of the 2nd stage is supplied to the network water main, to partially replenish network losses.

Figure 1. Schematic diagram of a thermal power plant based on TU PT-80/100-130/13

2. Calculation of the principle thermal diagram of a turbine plantFri-80/100-130/13 in high load mode

Calculation of the basic thermal scheme of the turbine plant is based on the given steam flow rate for the turbine. As a result of the calculation, determine:

? electrical power of the turbine unit - W e;

? energy performance of the turbine plant and CHP as a whole:

b. coefficient useful action CHP for the production of electricity;

in. efficiency factor of CHPP for the production and supply of heat for heating;

d. specific consumption of reference fuel for electricity generation;

e. Specific consumption of reference fuel for the production and supply of thermal energy.

2.1 Initial data for calculation

Live steam pressure -

Fresh steam temperature -

Pressure in the condenser - P to = 0.00226 MPa

Parameters of steam production selection:

steam consumption -

giving - ,

reverse - .

Fresh steam consumption for the turbine -

The efficiency values ​​of the thermal circuit elements are given in Table 2.1.

Table 2.1. Efficiency factor of thermal circuit elements

Thermal circuit element	Efficiency
	Designation	Meaning
Extender continuous purge
Lower network heater
Upper network heater
Regenerative heating system:
Feed pump
Feed water deaerator
Purge cooler
Purified water heater
Condensate water deaerator
Faucets
Seal heater
Seal ejector
Pipelines
Generator

2.2 Calculation of pressures in turbine extractions

Thermal load The CHPP is determined by the needs of the production consumer of steam and the supply of heat to an external consumer for heating, ventilation and hot water supply.

To calculate the characteristics of the thermal efficiency of a CHP plant with an industrial heat and power turbine in an increased load mode (below -5ºС), it is necessary to determine the steam pressure in the turbine bleeds. This pressure is set based on the requirements of the industrial consumer and the temperature schedule of the network water.

In this course work, a constant steam extraction for the technological (industrial) needs of an external consumer is adopted, which is equal to the pressure, which corresponds to the nominal operation of the turbine, therefore, the pressure in the unregulated turbine extractions No. 1 and No. 2 is:

The steam parameters in the turbine extractions at nominal mode are known from its main parameters. specifications.

It is necessary to determine the actual (i.e. for a given mode) pressure value in the heat extraction. To do this, the following sequence of actions is performed:

1. According to the given value and the selected (given) temperature graph of the heating network, we determine the temperature of the network water behind the network heaters at a given outdoor temperature t NAR

t Sun = t O.S + b CHP ( t P.S - t O.S)

t BC \u003d 55.6 + 0.6 (106.5 - 55.6) \u003d 86.14 0 C

2. According to the accepted value of water undercooling and and value t BC we find the saturation temperature in the network heater:

= t sun + and

86.14 + 4.3 \u003d 90.44 0 С

Then, according to the saturation tables for water and steam, we determine the steam pressure in the network heater R BC = 0.07136 MPa.

3. The heat load on the lower network heater reaches 60% of the total load on the boiler room

t NS = t O.S + 0.6 ( t V.S - t O.S)

t NS \u003d 55.6 + 0.6 (86.14 - 55.6) \u003d 73.924 0 C

According to the saturation tables for water and steam, we determine the steam pressure in the network heater R H C \u003d 0.04411 MPa.

4. We determine the steam pressure in the cogeneration (regulated) extractions No. 6, No. 7 of the turbine, taking into account the accepted pressure losses through pipelines:

where losses in pipelines and control systems of the turbine are accepted:; ;

5. According to the steam pressure value ( R 6 ) in the heating extraction No. 6 of the turbine, we specify the steam pressure in the unregulated turbine extractions between the industrial extraction No. 3 and the controlled heating extraction No. 6 (according to the Flugel-Stodola equation):

where D 0 , D, R 60 , R 6 - steam flow rate and pressure in the turbine extraction in the nominal and calculated mode, respectively.

2.3 Calculation of parameterssteam expansion process in the turbine compartments inh- Sdiagram

According to the method described below and the values ​​of pressures in the extractions found in the previous paragraph, we construct a diagram of the process of steam expansion in the flow path of the turbine at t bunk=- 15 є FROM.

Intersection point on h, s- isobar diagram with isotherm determines the enthalpy of fresh steam (point 0 ).

The loss of live steam pressure in the stop and control valves and the start-up vapor path with valves fully open is approximately 3%. Therefore, the steam pressure in front of the first stage of the turbine is:

On the h, s- the diagram shows the point of intersection of the isobar with the level of enthalpy of fresh steam (point 0 /).

To calculate the steam parameters at the outlet of each turbine compartment, we have the values ​​of the internal relative efficiency of the compartments.

Table 2.2. Internal relative efficiency of the turbine by compartments

From the obtained point (point 0 /) a line is drawn vertically downward (along the isentrope) to the intersection with the pressure isobar in selection No. 3. The enthalpy of the intersection point is equal to.

The enthalpy of steam in the chamber of the third regenerative selection in the real expansion process is equal to:

Similar to h,s- the diagram contains points corresponding to the state of steam in the chamber of the sixth and seventh selections.

After constructing the steam expansion process in h, S- the diagram shows isobars of unregulated extractions for regenerative heaters R 1 , R 2 ,R 4 ,R 5 and the enthalpies of steam in these extractions are established.

built on h,s- in the diagram, the points are connected by a line, which reflects the process of steam expansion in the flow path of the turbine. The graph of the steam expansion process is shown in Figure A.1. (Appendix A).

According to the built h,s- the diagram determines the temperature of the steam in the corresponding selection of the turbine by the values ​​of its pressure and enthalpy. All parameters are given in table 2.3.

2.4 Calculation of thermodynamic parameters in heaters

The pressure in regenerative heaters is less than the pressure in the extraction chambers by the amount of pressure loss due to the hydraulic resistance of the extraction pipelines, safety and stop valves.

1. We calculate the pressure of saturated water vapor in regenerative heaters. The pressure losses in the pipeline from the turbine extraction to the corresponding heater are taken equal to:

The pressure of saturated water vapor in the feed and condensate water deaerators is known from their technical specifications and is equal to, respectively,

2. According to the table of properties of water and steam in the saturation state, according to the saturation pressures found, we determine the temperatures and enthalpies of the heating steam condensate.

3. We accept undercooling of water:

In high pressure regenerative heaters - 2єFROM

In low pressure regenerative heaters - 5єFROM,

In deaerators - 0є FROM ,

therefore, the water temperature at the outlet of these heaters is:

, є FROM

4. The water pressure downstream of the respective heaters is determined hydraulic resistance tract and operating mode of pumps. The values ​​of these pressures are accepted and are given in Table 2.3.

5. According to the tables for water and superheated steam, we determine the enthalpy of water after the heaters (by the values ​​and):

6. Water heating in the heater is defined as the difference between the enthalpies of water at the inlet and outlet of the heater:

, kJ/kg;

kJ/kg;

kJ/kg;

kJ/kg;

kJ/kg

kJ/kg;

kJ/kg;

kJ/kg;

kJ/kg,

where is the enthalpy of the condensate at the outlet of the seal heater. In this work, this value is taken equal to.

7. The heat given off by the heating steam to the water in the heater:

2.5 Steam and water parameters in the turbine plant

For the convenience of further calculation, the parameters of steam and water in the turbine plant, calculated above, are summarized in Table 2.3.

Data on steam and water parameters in drain coolers are given in Table 2.4.

Table 2.3. Steam and water parameters in the turbine plant

p, MPa

t, 0 FROM

h, kJ/kg

p", MPa

t" H, 0 FROM

h B H, kJ/kg

0 FROM

p B, MPa

t P, 0 FROM

h B P, kJ/kg

kJ/kg

Table 2.4. Steam and water parameters in drain coolers

2.6 Determination of steam and condensate flow rates in the elements of the thermal scheme

The calculation is performed in the following order:

1. Steam flow to the turbine in the design mode.

2. Steam leaks through seals

Accept, then

4. Feed water consumption per boiler (including blowdown)

where is the amount of boiler water going into the continuous blowdown

D etc=(b etc/100)·D pg=(1.5/100) 131.15=1.968kg/s

5. Steam outlet from purge expander

where is the proportion of steam released from the blowdown water in the continuous blowdown expander

6.Blowdown water outlet from expander

7. Consumption of additional water from the chemical water treatment plant (CWT)

where is the condensate return coefficient from

production consumers, we accept;

Calculation of steam flow rates in regenerative and network heaters in the deaerator and condenser, as well as condensate flow rates through heaters and mixers is based on the equations of material and heat balances.

Balance equations are compiled sequentially for each element of the thermal scheme.

The first stage in the calculation of the thermal scheme of a turbine plant is the preparation of thermal balances for network heaters and the determination of steam flow rates for each of them based on the given thermal load of the turbine and the temperature graph. After that, heat balances of high pressure regenerative heaters, deaerators and low pressure heaters are compiled.

2.6.1 Network heating installation (boiler room)

Table 2.5. Steam and water parameters in a network heating plant

Index	Bottom heater	Top heater
Heating steam Selection pressure P, MPa
Pressure in the heater Р?, MPa
Steam temperature t, ºС
Heat output qns, qvs, kJ/kg
Heating steam condensate Saturation temperature tn, єС
Enthalpy at saturation h?, kJ/kg
Network water Underheating in the heater Ins, Ivs, єС
Inlet temperature tс, tns, єС
Inlet enthalpy, kJ/kg
Outlet temperature tns, tvs, єС
Output enthalpy, kJ/kg
Heating in the heater fns, fvs, kJ/kg

The installation parameters are defined in the following sequence.

1. Consumption of network water for the calculated mode

2.Heat balance of the lower network heater

Heating steam flow to the lower network heater

from Table 2.1.

3.Heat balance of the upper network heater

Heating steam flow to the upper network heater

Regenerative high temperature heaters pressure and feed plant (pump)

LDPE 7

The equation heat balance PVD7

Heating steam consumption for PVD7

LDPE 6

Heat balance equation for HPH6

Heating steam consumption for PVD6

heat removed from the drainage OD2

Feed pump (PN)

Pressure after PN

Pressure in the pump in PN

Pressure drop

The specific volume of water in PN v PN - determined from the tables by value

R Mon.

Feed pump efficiency

Water heating in Mon

Enthalpy after PN

Where - from table 2.3;

HPH5 heat balance equation

Heating steam consumption for PVD5

2.6.3 Feed water deaerator

The steam flow rate from the seals of the valve stems in the DPV is accepted

Steam enthalpy from valve stem seals

(at P = 12,9 MPa and t=556 0 FROM) :

Evaporation from the deaerator:

D issue=0,02 D PV=0.02

The share of steam (in fractions of the vapor from the deaerator going to the PE, the seals of the middle and end seal chambers

Deaerator material balance equation:

.

Deaerator heat balance equation

After substituting into this equation the expression D CD we get:

Heating steam consumption from the third turbine extraction to the DPV

hence the consumption of heating steam from the turbine extraction No. 3 to the DPV:

D D = 4.529.

Condensate flow at the deaerator inlet:

D KD \u003d 111.82 - 4.529 \u003d 107.288.

2.6.4 Raw water heater

Drainage enthalpy h PSV=140

.

2.6.5 Two Stage Purge Expander

2nd stage: expansion of water boiling at 6 atm in quantity

up to a pressure of 1 atm.

= + (-)

sent to the atmospheric deaerator.

2.6.6 Additional water deaerator

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Equation of the material balance of the return condensate deaerator and additional water DKV.

D KV = + D P.O.V + D OK + D OV;

Consumption of chemically treated water:

D OB = ( D P - D OK) + + D UT.

Thermal balance of the blowdown water cooler

material turbine condensate

where q OP = h h heat supplied to the additional water in the OP.

q OP \u003d 670.5- 160 \u003d 510.5 kJ / kg,

where: h enthalpy of blowdown water at the outlet of the OP.

We accept the return of condensate from industrial heat consumers?k = 0.5 (50%), then:

D OK = ?k* D P = 0.5 51.89 = 25.694 kg / s;

D RH = (51.89 - 25.694) + 1.145 + 0.65 = 27.493 kg/s.

The additional water heating in the OP is determined from the OP heat balance equation:

= 27.493 from here:

= 21.162 kJ/kg.

After the blowdown cooler (BP), the additional water enters the chemical water treatment, and then to the chemically treated water heater.

Thermal balance of the POV chemically purified water heater:

where q 6 - the amount of heat transferred in the heater by steam from turbine extraction No. 6;

water heating in POV. Accept h RH = 140 kJ/kg, then

.

The steam flow rate for SOW is determined from the heat balance of the chemically treated water heater:

D POV 2175.34 = 27.493 230.4 from where D POV = 2.897 kg / s.

In this way,

D KV = D

Heat balance equation for chemically treated water deaerator:

D h 6 + D POV h+ D OK h+ D OV hD HF h

D 2566,944+ 2,897 391,6+ 25,694 376,77 + 27,493 370,4= (D+ 56,084) * 391,6

From here D\u003d 0.761 kg / s - heating steam consumption at the DKV and extraction No. 6 of the turbine.

The flow of condensate at the outlet of the DKV:

D KV \u003d 0.761 + 56.084 \u003d 56.846 kg / s.

2.6.7 Low pressure regenerative heaters

HDPE 4

Heat balance equation for HDPE4

.

Heating steam consumption for LPH4

,

where

HDPE and mixerCM2

Combined heat balance equation:

where is the condensate flow at the LPH2 outlet:

D K6 = D KD - D HF -D Sun - D PSV = 107,288 -56,846 - 8,937 - 2,897 = 38,609

substitute D K2 into the combined heat balance equation:

D\u003d 0.544 kg / s - heating steam consumption at LPH3 from selection No. 5

turbines.

PND2, mixer CM1, PND1

Temperature for PS:

1 material equation and 2 heat balance equations are compiled:

1.

2.

3.

substitute into equation 2

We get:

kg/s;

D P6 = 1,253 kg/s;

D P7 = 2,758 kg/s.

2.6.8 Capacitor

Capacitor Material Balance Equation

.

2.7 Checking the material balance calculation

Checking the correctness of taking into account in the calculations of all flows of the thermal scheme is carried out by comparing the material balances for steam and condensate in the turbine condenser.

Exhaust steam flow to condenser:

,

where is the steam flow rate from the turbine extraction chamber with the number.

Steam flow rates from extractions are given in Table 2.6.

Table 2.6. Steam consumption by turbine extraction

Selection No.	Designation	Steam consumption, kg/s
	D 1 =D P1
	D 2 =D P2
	D 3 =D P3+D D+D P
	D 4 =D P4
	D 5 = D NS + D P5
	D 6 =D P6+D sun++D PSV
	D 7 =D P7+D HC

Total steam flow from turbine extractions

Steam flow to the condenser after the turbine:

Steam and condensate balance error

Since the error in the balance of steam and condensate does not exceed the permissible value, therefore, all flows of the thermal scheme are taken into account correctly.

2.8 Energy balance of the turbine unit Fri- 80/100-130/13

Let us determine the power of the turbine compartments and its total power:

N i=

where N i OTS - power of the turbine compartment, N i UTS = D i UTS H i UTS,

H i UTS = H i UTS - H i +1 HTS - heat drop in the compartment, kJ/kg,

D i OTS - passage of steam through the compartment, kg/s.

compartment 0-1:

D 01 UTS = D 0 = 130,5 kg/s,

H 01 UTS = H 0 UTS - H 1 UTS = 34 8 7 - 3233,4 = 253,6 kJ/kg,

N 01 UTS = 130,5 . 253,6 = 33,095 MVt.

- compartment 1-2:

D 12 UTS = D 01 -D 1 = 130,5 - 8,631 = 121,869 kg/s,

H 12 UTS = H 1 UTS - H 2 UTS = 3233,4 - 3118,2 = 11 5,2 kJ/kg,

N 12 UTS = 121,869 . 11 5,2 = 14,039 MVt.

- compartment 2-3:

D 23 UTS = D 12 -D 2 = 121,869 - 8,929 = 112,94 kg/s,

H 23 UTS = H 2 UTS - H 3 UTS = 3118,2 - 2981,4 = 136,8 kJ/kg,

N 23 UTS = 112,94 . 136,8 = 15,45 MVt.

- compartment 3-4:

D 34 UTS = D 23 -D 3 = 112,94 - 61,166 = 51,774 kg/s,

H 34 UTS = H 3 UTS - H 4 UTS = 2981,4 - 2790,384 = 191,016 kJ/kg,

N 34 UTS = 51,774 . 191,016 = 9,889 MVt.

- compartment 4-5:

D 45 UTS = D 34 -D 4 = 51,774 - 8,358 = 43,416 kg/s,

H 45 UTS = H 4 UTS - H 5 UTS = 2790,384 - 2608,104 = 182,28 kJ/kg,

N 45 UTS = 43,416 . 182,28 = 7,913 MVt.

- compartment 5-6:

D 56 UTS = D 45 -D 5 = 43,416 - 9,481 = 33, 935 kg/s,

H 56 UTS = H 5 UTS - H 6 UTS = 2608,104 - 2566,944 = 41,16 kJ/kg,

N 45 UTS = 33, 935 . 41,16 = 1,397 MVt.

- compartment 6-7:

D 67 UTS = D 56 -D 6 = 33, 935 - 13,848 = 20,087 kg/s,

H 67 UTS = H 6 UTS - H 7 UTS = 2566,944 - 2502,392 = 64,552 kJ/kg,

N 67 UTS = 20,087 . 66,525 = 1, 297 MVt.

- compartment 7-K:

D 7k UTS = D 67 -D 7 = 20,087 - 13,699 = 6,388 kg/s,

H 7k UTS = H 7 UTS - H to UTS = 2502,392 - 2442,933 = 59,459 kJ/kg,

N 7k UTS = 6,388 . 59,459 = 0,38 MVt.

3.5.1 Total power of turbine compartments

3.5.2 The electrical power of the turbine set is determined by the formula:

N E = N i

where is the mechanical and electrical efficiency of the generator,

N E \u003d 83.46. 0.99. 0.98=80.97MW.

2.9 Turbine thermal efficiency indicators

Total heat consumption for the turbine plant

, MW

.

2. Heat consumption for heating

,

where h T- coefficient taking into account heat losses in the heating system.

3. Total heat consumption for industrial consumers

,

.

4. Total heat consumption for external consumers

, MW

.

5. Heat consumption for the turbine plant for the production of electricity

,

6. Efficiency of the turbine plant for the production of electricity (excluding own consumption of electricity)

,

.

7. Specific heat consumption for electricity generation

,

2.10 Energy indicators of CHP

Fresh steam parameters at the outlet of the steam generator.

- pressure P PG = 12.9 MPa;

- Gross steam generator efficiency from SG = 0.92;

- temperature t SG = 556 о С;

- h PG = 3488 kJ / kg at the specified R PG and t PG.

Efficiency of the steam generator, taken from the characteristics of the boiler E-320/140

.

1. Thermal load of the steam generator set

, MW

2. Efficiency of pipelines (heat transport)

,

.

3. Efficiency of CHP for the production of electricity

,

.

4. Efficiency of the CHPP for the production and supply of heat for heating, taking into account the PVC

,

.

PVC at t H=- 15 0 FROM works,

5. Specific consumption of reference fuel for electricity generation

,

.

6. Specific consumption of reference fuel for the production and supply of thermal energy

,

.

7. Fuel heat consumption per station

,

.

8. Total efficiency of the power unit (gross)

,

9. Specific heat consumption per CHP power unit

,

.

10. Efficiency of the power unit (net)

,

.

where E S.N - own specific consumption of electricity, E S.N = 0.03.

11. Specific consumption of reference fuel "net"

,

.

12. Reference fuel consumption

kg/s

13. Consumption of reference fuel for the generation of heat supplied to external consumers

kg/s

14. Reference fuel consumption for electricity generation

V E U \u003d V U -V T U \u003d 13.214-8.757 \u003d 4.457 kg / s

Conclusion

As a result of the calculation of the thermal scheme of the power plant based on the production heat-and-power turbine PT-80/100-130/13, operating in the increased load mode at ambient temperature, the following values ​​of the main parameters characterizing the power plant of this type were obtained:

Steam consumption in turbine extractions

Heating steam consumption for network heaters

Heat output for heating by a turbine plant

Q T= 72.22MW;

Heat output from a turbine plant to industrial consumers

Q P= 141.36 MW;

Total consumption heat for external consumers

Q TP= 231.58 MW;

Power at generator terminals

N uh=80.97 MW;

CHP efficiency for electricity generation

Efficiency of CHPP for the production and supply of heat for heating

Specific fuel consumption for electricity generation

b E At= 162.27g/kw/h

Specific fuel consumption for the production and supply of thermal energy

b T At= 40.427 kg/GJ

Gross total CHP efficiency

Total efficiency of CHP "net"

Specific reference fuel consumption per station "net"

Bibliography

1. Ryzhkin V.Ya. Thermal power plants: Textbook for universities - 2nd ed., Revised. - M.: Energy, 1976.-447p.

2. Alexandrov A.A., Grigoriev B.A. Tables of thermophysical properties of water and steam: a Handbook. - M.: Ed. MPEI, 1999. - 168s.

3. Poleshchuk I.Z. Drawing up and calculation of basic thermal schemes of thermal power station. Guidelines to the course project on the discipline "TPP and NPP", / Ufa State. aviation tech.un - t. - Ufa, 2003.

4. Standard of the enterprise (STP UGATU 002-98). Requirements for the construction, presentation, design.-Ufa.: 1998.

5. Boyko E.A. Steam-tube power plants at TPPs: Help Guide- CPI KSTU, 2006. -152s

6. . Thermal and nuclear power plants: Handbook / Under the general editorship. corresponding member RAS A.V. Klimenko and V.M. Zorin. - 3rd ed. - M.: Izd MPEI, 2003. - 648s.: ill. - (Heat power engineering and heat engineering; Book 3).

7. . Thermal and nuclear turbines power stations: Textbook for universities / Ed. A.G, Kostyuk, V.V. Frolova. - 2nd ed., revised. and additional - M.: Izd MPEI, 2001. - 488 p.

8. Calculation of thermal schemes of steam turbine plants: Educational electronic edition / Poleshchuk I.Z. - GOU VPO UGATU, 2005.

Conventions power plants, equipment and their elements (includingtext, figures, indexes)

D - feed water deaerator;

DN - drainage pump;

K - condenser, boiler;

KN - condensate pump;

OE - drainage cooler;

PrTS - basic thermal diagram;

PVD, HDPE - regenerative heater (high, low pressure);

PVK - peak hot water boiler;

SG - steam generator;

PE - superheater (primary);

PN - feed pump;

PS - stuffing box heater;

PSG - horizontal network heater;

PSV - raw water heater;

PT - steam turbine; heating turbine with industrial and heating steam extraction;

PHOV - chemically purified water heater;

PE - ejector cooler;

P - expander;

CHPP - combined heat and power plant;

CM - mixer;

СХ - stuffing box cooler;

HPC - high pressure cylinder;

LPC - low pressure cylinder;

EG - electric generator;

Annex A

Annex B

Mode diagram PT-80/100

Annex B

Heating schedules for quality regulation of the releaseheat according to the average daily outdoor temperature

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	Task for course project	3
1.	Initial reference data	4
2.	Calculation of the boiler plant	6
3.	Construction of the steam expansion process in the turbine	8
4.	Steam and feed water balance	9
5.	Determination of parameters of steam, feed water and condensate by PTS elements	11
6.	Compilation and solution of heat balance equations for sections and elements of PTS	15
7.	Energy power equation and its solution	23
8.	Calculation check	24
9.	Definition of energy indicators	25
10.	Choice of accessories	26
	Bibliography	27

Assignment for a course project
Student: Onuchin D.M..

Project theme: Calculation of the thermal scheme of PTU PT-80/100-130/13
Project Data

P 0 \u003d 130 kg / cm 2;

;

;

Q t \u003d 220 MW;

;

.

Pressure in unregulated withdrawals - from reference data.

Preparation of additional water - from the atmospheric deaerator "D-1.2".
The volume of the settlement part

1. 
   Design calculation of PTU in the SI system for rated power.
2. 
   Determination of energy indicators of the work of vocational schools.
3. 
   The choice of auxiliary equipment for vocational schools.

1. Initial reference data
The main indicators of the turbine PT-80/100-130.

Table 1.

Parameter	Value	Dimension
Rated power	80	MW
Max Power	100	MW
Initial pressure	23,5	MPa
Initial temperature	540	FROM
Pressure at the outlet of the HPC	4,07	MPa
The temperature at the outlet of the HPC	300	FROM
Superheated steam temperature	540	FROM
Cooling water consumption	28000	m 3 / h
Cooling water temperature	20	FROM
Condenser pressure	0,0044	MPa

The turbine has 8 unregulated steam extractions designed to heat feed water in the low pressure heaters, deaerator, high pressure heaters and to power the drive turbine of the main feed pump. The exhaust steam from the turbo drive is returned to the turbine.
Table 2.

	Selection	Pressure, MPa	Temperature, 0 C
I	LDPE №7	4,41	420
II	PVD №6	2,55	348
III	PND №5	1,27	265
	Deaerator	1,27	265
IV	PND №4	0,39	160
V	PND №3	0,0981	-
VI	PND №2	0,033	-
VII	PND №1	0,003	-

The turbine has two heating steam extractions, upper and lower, designed for one and two-stage heating of network water. Heating extractions have the following pressure regulation limits:

Upper 0.5-2.5 kg / cm 2;

Lower 0.3-1 kg/cm 2 .

2. Calculation of the boiler plant

WB - upper boiler;

NB - lower boiler;

Obr - reverse network water.

D WB, D NB - steam flow to the upper and lower boilers, respectively.

temperature graph: t pr / t o br \u003d 130 / 70 C;

T pr \u003d 130 0 C (403 K);

T arr \u003d 70 0 C (343 K).

Determination of steam parameters in heating extractions

We accept uniform heating on the VSP and NSP;

We accept the value of underheating in network heaters
.

We accept pressure losses in pipelines
.

The pressure of the upper and lower extractions from the turbine for VSP and LSP:

bar;

bar.
h WB =418.77 kJ/kg

h NB \u003d 355.82 kJ / kg

D WB (h 5 - h WB /) \u003d K W SV (h WB - h NB) →

→ D WB =1.01∙870.18(418.77-355.82)/(2552.5-448.76)=26.3 kg/s

D NB h 6 + D WB h WB / + K W SV h ​​OBR \u003d KW SV h ​​NB + (D WB +D NB) h NB / →

→ D NB \u003d / (2492-384.88) \u003d 25.34 kg / s

D WB + D NB \u003d D B \u003d 26.3 + 25.34 \u003d 51.64 kg / s

3. Construction of the steam expansion process in the turbine
Let us take the pressure loss in the steam distribution devices of the cylinders:

;

;

;

In this case, the pressure at the inlet to the cylinders (behind the control valves) will be:

The process in the h,s-diagram is shown in fig. 2.

4. Balance of steam and feed water.

• 
  We assume that the end seals (D KU) and the steam ejectors (D EP) receive steam of higher potential.
• 
  The spent steam from the end seals and from the ejectors is directed to the stuffing box heater. We accept heating of condensate in it:

• 
  The spent steam in the ejector coolers is directed to the ejector heater (EP). Heating in it:

• 
  We accept the steam flow to the turbine (D) as a known value.
• 
  Intra-station losses of the working fluid: D UT =0.02D.
• 
  Steam consumption for end seals will be 0.5%: D KU = 0.005D.
• 
  Steam consumption for the main ejectors will be 0.3%: D EJ = 0.003D.

Then:

• 
  Steam consumption from the boiler will be:

D K \u003d D + D UT + D KU + D EJ \u003d (1 + 0.02 + 0.005 + 0.003) D \u003d 1.028D

• 
  Because drum boiler, it is necessary to take into account the blowdown of the boiler.

The purge is 1.5%, i.e.

D prod \u003d 0.015D \u003d 1.03D K \u003d 0.0154D.

• 
  The amount of feed water supplied to the boiler:

D PV \u003d D K + D prod \u003d 1.0434D

• 
  Amount of additional water:

D ext \u003d D ut + (1-K pr) D pr + D v.r.

Condensate losses for production:

(1-K pr) D pr \u003d (1-0.6) ∙ 75 \u003d 30 kg / s.

The pressure in the boiler drum is approximately 20% higher than the fresh steam pressure at the turbine (due to hydraulic losses), i.e.

P q.v. =1.2P 0 =1.2∙12.8=15.36 MPa →
kJ/kg.

The pressure in the continuous blowdown expander (CRP) is about 10% higher than in the deaerator (D-6), i.e.

P RNP \u003d 1.1P d \u003d 1.1 ∙ 5.88 \u003d 6.5 bar →

→
kJ/kg;

kJ/kg;

kJ/kg;

D P.R. \u003d β ∙ D prod \u003d 0.438 0.0154D \u003d 0.0067D;

D V.R. \u003d (1-β) D prod \u003d (1-0.438) 0.0154D \u003d 0.00865D.
D ext \u003d D ut + (1-K pr) D pr + D v.r. =0.02D+30+0.00865D=0.02865D+30.

We determine the consumption of network water through network heaters:

We accept leaks in the heat supply system of 1% of the amount of circulating water.

Thus, the required performance of chem. water treatment:

5. Determination of parameters of steam, feed water and condensate by PTS elements.
We accept the pressure loss in the steam pipelines from the turbine to the heaters of the regenerative system in the amount of:

I selection	PVD-7	4%
II selection	PVD-6	5%
III selection	PVD-5	6%
IV selection	PVD-4	7%
V selection	PND-3	8%
VI selection	PND-2	9%
VII selection	PND-1	10%

The determination of the parameters depends on the design of the heaters ( see fig. 3). In the calculated scheme, all HDPE and LDPE are surface.

In the course of the main condensate and feed water from the condenser to the boiler, we determine the parameters we need.

5.1. We neglect the increase in enthalpy in the condensate pump. Then the parameters of the condensate before the EP:

0.04 bar
29°С,
121.41 kJ/kg.

5.2. We take the heating of the main condensate in the ejector heater equal to 5°C.

34 °С; kJ/kg.

5.3. The water heating in the stuffing box heater (SH) is assumed to be 5°С.

39 °С,
kJ/kg.

5.4. PND-1 - disabled.

It feeds on steam from the VI selection.

69.12 °С,
289.31 kJ / kg \u003d h d2 (drainage from HDPE-2).

°С,
4.19∙64.12=268.66kJ/kg

It feeds on steam from the V selection.

Heating steam pressure in the heater body:

96.7 °С,
405.21 kJ/kg;

Water parameters behind the heater:

°С,
4.19∙91.7=384.22 kJ/kg.

We preliminarily set the temperature increase due to the mixing of flows in front of LPH-3 by
, i.e. we have:

It feeds on steam from the IV selection.

Heating steam pressure in the heater body:

140.12°С,
589.4 kJ/kg;

Water parameters behind the heater:

°С,
4.19∙135.12=516.15 kJ/kg.

Parameters of the heating medium in the drain cooler:

5.8. Feed water deaerator.

Feed water deaerator operates at constant steam pressure in the casing

R D-6 \u003d 5.88 bar → t D-6 H \u003d 158 ˚C, h ’D-6 \u003d 667 kJ / kg, h ”D-6 \u003d 2755.54 kJ / kg,

5.9. Feed pump.

Let's take the pump efficiency
0,72.

Discharge pressure: MPa. °C, and the parameters of the heating medium in the drain cooler:
Steam parameters in the steam cooler:

°C;
2833.36 kJ/kg.

We set the heating in OP-7 equal to 17.5 ° С. Then the temperature of the water behind the HPH-7 is equal to °С, and the parameters of the heating medium in the drain cooler are:

°C;
1032.9 kJ/kg.

Feed water pressure after HPH-7 is:

Water parameters behind the heater itself.

3.3.4 Steam turbine plant PT-80/100-130/13

Heating steam turbine PT-80/100-130/13 with industrial and heating steam extraction is designed for direct drive electric generator TVF-120-2 with a rotation speed of 50 rpm and heat supply for the needs of production and heating.

Power, MW

nominal 80

maximum 100

Rated steam parameters

pressure, MPa 12.8

temperature, 0 С 555

Consumption of extracted steam for production needs, t/h

nominal 185

maximum 300

upper 0.049-0.245

lower 0.029-0.098

Production selection pressure 1.28

Water temperature, 0 C

nutritional 249

cooling 20

Cooling water consumption, t/h 8000

The turbine has the following adjustable steam extractions:

production with an absolute pressure of (1.275 ± 0.29) MPa and two heating selections - the upper one with an absolute pressure in the range of 0.049-0.245 MPa and the lower one with a pressure in the range of 0.029-0.098 MPa. The heating extraction pressure is regulated by means of one control diaphragm installed in the upper heating extraction chamber. Adjustable pressure in heating extractions it is supported: in the upper extraction - when both heating extractions are switched on, in the lower extraction - when one lower heating extraction is switched on. Network water through the network heaters of the lower and upper stages of heating must be passed sequentially and in equal quantities. The flow of water passing through the network heaters must be controlled.

The turbine is a single-shaft two-cylinder unit. The HPC flow path has a single-row control stage and 16 pressure stages.

The flow part of the LPC consists of three parts:

the first (up to the upper heating outlet) has a control stage and 7 pressure stages,

the second (between the heating taps) two pressure stages,

the third - the control stage and two pressure stages.

The high pressure rotor is one-piece forged. The first ten disks of the low-pressure rotor are forged integrally with the shaft, the remaining three disks are mounted.

Steam distribution of the turbine - nozzle. At the exit from the HPC, part of the steam goes to controlled production extraction, the rest goes to the LPC. Heating extractions are carried out from the corresponding LPC chambers.

To reduce the warm-up time and improve start-up conditions, steam heating of flanges and studs and live steam supply to the HPC front seal are provided.

The turbine is equipped with a barring device that rotates the shafting of the turbine unit at a frequency of 3.4 rpm.

The turbine blade apparatus is designed to operate at a mains frequency of 50 Hz, which corresponds to a turbine rotor speed of 50 rpm (3000 rpm). Long-term operation of the turbine is allowed with a frequency deviation in the network of 49.0-50.5 Hz.

3.3.5 Steam turbine plant Р-50/60-130/13-2

The R-50/60-130/13-2 counterpressure steam turbine is designed to drive the TVF-63-2 electric generator with a rotation speed of 50 s -1 and to release steam for production needs.

The nominal values ​​of the main parameters of the turbine are given below:

Power, MW

Rated 52.7

Maximum 60

Initial steam parameters

Pressure, MPa 12.8

Temperature, o C 555

Pressure in the exhaust pipe, MPa 1.3

The turbine has two unregulated steam extractions intended for heating feed water in high pressure heaters.

Turbine design:

The turbine is a single-cylinder unit with a single-crown control stage and 16 pressure stages. All rotor discs are forged integrally with the shaft. Steam distribution of the turbine with bypass. Fresh steam is supplied to a free-standing steam box, in which the automatic shutter valve is located, from where steam is supplied through bypass pipes to four control valves.

The turbine blade apparatus is designed to operate at a frequency of 3000 rpm. Long-term operation of the turbine is allowed with a frequency deviation in the network of 49.0-50.5 Hz

The turbo unit is equipped protective devices for joint shutdown of the HPH with simultaneous activation of the bypass line by giving a signal. Atmospheric diaphragm valves installed on the exhaust pipes and opening when the pressure in the pipes rises to 0.12 MPa.

3.3.6 Steam turbine plant T-110/120-130/13

Heating steam turbine T-110/120-130/13 with heating steam extraction is designed for direct drive of electric generator TVF-120-2 with a rotation speed of 50 rpm and heat supply for heating needs.

The nominal values ​​of the main parameters of the turbine are given below.

Power, MW

nominal 110

maximum 120

Rated steam parameters

pressure, MPa 12.8

temperature, 0 С 555

nominal 732

maximum 770

Limits of steam pressure change in controlled heating extraction, MPa

upper 0.059-0.245

lower 0.049-0.196

Water temperature, 0 C

nutritional 232

cooling 20

Cooling water consumption, t/h 16000

Vapor pressure in the condenser, kPa 5.6

The turbine has two heating extractions - lower and upper, designed for stepwise heating of network water. In case of stepwise heating of network water with steam from two heating extractions, the control maintains the set temperature of network water downstream of the upper network heater. When heating network water with one lower heating extraction, the temperature of network water is maintained behind the lower network heater.

Pressure in adjustable heating extractions can vary within the following limits:

in the upper 0.059 - 0.245 MPa with two heating extractions turned on,

at the bottom 0.049 - 0.196 MPa with the top heating off.

Turbine T-110/120-130/13 is a single-shaft unit consisting of three cylinders: high pressure cylinder, low pressure cylinder, low pressure cylinder.

The HPC is single-flow, has a two-row control stage and 8 pressure stages. The high-pressure rotor is one-piece forged.

TsSD - also single-flow, has 14 steps of pressure. The first 8 disks of the medium pressure rotor are forged integrally with the shaft, the remaining 6 are mounted. The guide vane of the first stage of the TsSD is installed in the housing, the remaining diaphragms are installed in holders.

LPC - double-flow, has two stages in each stream of left and right rotation (one control and one pressure stage). The length of the working blade of the last stage is 550 mm, the average diameter of the impeller of this stage is 1915 mm. The low pressure rotor has 4 mounted discs.

In order to facilitate the start-up of the turbine from a hot state and increase its maneuverability during operation under load, the temperature of the steam supplied to the penultimate chamber of the HPC front seal is increased by mixing hot steam from the control valve stems or from the main steam pipeline. From the last compartments of the seals, the vapor-air mixture is sucked off by the suction ejector from the seals.

To reduce the heating time and improve the conditions for starting the turbine, steam heating of the HPC flanges and studs is provided.

The turbine blade apparatus is designed to operate at a mains frequency of 50 Hz, which corresponds to a turbine rotor speed of 50 rpm (3000 rpm).

Long-term operation of the turbine is allowed with a frequency deviation in the network of 49.0-50.5 Hz. In emergency situations for the system, short-term operation of the turbine is allowed at a network frequency below 49 Hz, but not below 46.5 Hz (the time is specified in the technical specifications).

Information about the work "Modernization of the Almaty CHPP-2 by changing water chemistry make-up water treatment systems to increase the temperature of network water up to 140-145 C"

Cogeneration steam turbine PT-80 / 100-130 / 13 of the production association for turbine construction "Leningrad Metal Works" (NOG LMZ) with industrial and heating steam extraction with a rated power of 80 MW, a maximum of 100 MW with an initial steam pressure of 12.8 MPa is designed for direct drive electric generator TVF-120-2 with a rotation frequency of 50 Hz and heat supply for the needs of production and heating.

When ordering a turbine, as well as in other documentation, where it should be designated "Steam turbine 1GG-80/100-130/13 TU 108-948-80".

Turbine PT-80/100-130/13 complies with the requirements of GOST 3618-85, GOST 24278-85 and GOST 26948-86.

The turbine has the following adjustable steam extractions: a production one with an absolute pressure of (1.275 ± 0.29) MPa and two heating extractions: an upper one with an absolute pressure in the range of 0.049-0.245 MPa and a lower one with a pressure in the range of 0.029-0.098 MPa.

The heating extraction pressure is regulated by means of one control diaphragm installed in the upper heating extraction chamber. Regulated pressure in the heating extractions is maintained: in the upper extraction - when both heating extractions are switched on, in the lower extraction - when one lower heating extraction is switched on. Network water through the network heaters of the lower and upper stages of heating is passed sequentially and in the same amount. The flow of water passing through the network heaters is controlled.

Nominal values ​​of the main parameters of the turbine PT-80/100-130/13

Parameter	PT-8O/100-130/13
1. Power, MW
nominal	80
maximum	100
2. Initial steam parameters:
pressure, MPa	12.8
temperature. °C	555
284 (78.88)
4. Consumption of selected steam for production. needs, t/h
nominal	185
maximum	300
5. Production selection pressure, MPa	1.28
6. Max Flow live steam, t/h	470
7. Limits of steam pressure change in adjustable heating steam extractions, MPa
at the top	0.049-0.245
in the bottom	0.029-0.098
8. Water temperature, °С
nutritional	249
cooling	20
9. Cooling water consumption, t/h	8000
10. Steam pressure in the condenser, kPa	2.84

With nominal parameters of fresh steam, cooling water flow rate of 8000 m3/h, cooling water temperature of 20 °C, fully activated regeneration, the amount of condensate heated in the HPH equal to 100% of the steam flow through the turbine, when the turbine unit is operating with a deaerator of 0.59 MPa, with stepped heating of network water, at full use bandwidth turbine and the minimum passage of steam into the condenser, the following extraction values ​​can be taken:

— nominal values ​​of regulated extractions at a power of 80 MW;

- production selection - 185 t / h at an absolute pressure of 1.275 MPa;

- total heating extraction - 285 GJ / h (132 t / h) at absolute pressures: in the upper extraction - 0.088 MPa and in the lower extraction - 0.034 MPa;

- the maximum value of production selection at an absolute pressure in the selection chamber of 1.275 MPa is 300 t / h. With this value of production extraction and the absence of heating extractions, the turbine power is -70 MW. With a rated power of 80 MW and no heating extraction, the maximum production extraction will be -250 t/h;

— the maximum total value of heating extractions is 420 GJ/h (200 t/h); with this value of heating extractions and the absence of industrial extraction, the turbine power is about 75 MW; with a rated power of 80 MW and no industrial extraction, the maximum heating extraction will be about 250 GJ/h (-120 t/h).

— the maximum power of the turbine with production and heating extraction off, at a cooling water flow rate of 8000 m3/h at a temperature of 20 °C, with fully switched on regeneration, will be 80 MW. The maximum power of the turbine is 100 MW. obtained with certain combinations of production and heating extractions, depends on the magnitude of the extractions and is determined by the mode aperture.

It is possible to operate the turbine plant with the passage of make-up and network water through the built-in bundle

When the condenser is cooled by network water, the turbine can operate according to the heat schedule. Maximum thermal power of the built-in beam is -130 GJ/h while maintaining the temperature in the exhaust part no higher than 80 °C.

Long-term operation of the turbine with rated power is allowed with the following deviations of the main parameters from the nominal:

• with a simultaneous change in any combination of the initial parameters of live steam - pressure from 12.25 to 13.23 MPa and temperature from 545 to 560 ° C; at the same time, the temperature of the cooling water should not exceed 20 °C;
• when the temperature of the cooling water at the condenser inlet rises to 33 °C and the flow rate of the cooling water is 8000 m3/h, if the initial parameters of the live steam are not lower than the nominal ones;
• while reducing the values ​​of industrial and heating steam extractions to zero.
• with an increase in the pressure of live steam to 13.72 MPa and a temperature of up to 565 ° C, the operation of the turbine is allowed for no more than half an hour, and the total duration of the operation of the turbine at these parameters should not exceed 200 h / year.

For this turbine unit PT-80/100-130/13, a high-pressure heater No. 7 (PVD-475-230-50-1) is used. HPH-7 operates at steam parameters before entering the heater: pressure 4.41 MPa, temperature 420 °C and steam flow rate 7.22 kg/s. Feed water parameters in this case: pressure 15.93 MPa, temperature 233 °C and flow rate 130 kg/s.