Cogeneration steam turbine T-50/60-130 is designed to drive an electric generator and has two heat extraction outlets for distributing heat for heating. Like other turbines with a capacity of 30-60 MW, it is intended for installation at thermal power plants of medium and small cities. The pressure in both heating and production extraction is maintained by regulating rotary diaphragms installed in the LPC.

The turbine is designed to operate at the following nominal parameters:

superheated steam pressure – 3.41 MPa;

temperature of superheated steam - 396°C;

· rated power of the turbine - 50 MW.

Sequence technological process the working fluid is as follows: the steam generated in the boiler is sent through the steam pipelines to the cylinder high pressure the turbine, having worked out at all stages of the HPC, enters the LPC and then enters the condenser. In the condenser, the exhaust steam is condensed due to the heat given off to the cooling water, which has its own circulation circuit (circulating water), then, using condensate pumps, the main condensate is sent to the regeneration system. This system includes 4 HDPE, 3 HPH and a deaerator. The regeneration system is designed to heat the feed water at the boiler inlet to a certain temperature. This temperature has a fixed value and is indicated in the turbine passport.

The thermal circuit diagram is one of the basic diagrams of a power plant. Such a diagram gives an idea of ​​the type of power plant and the principle of its operation, revealing the essence of the technological process of energy generation, and also characterizes the technical equipment and thermal efficiency of the plant. It is necessary to calculate the heat and energy balances of the installation.

This diagram shows 7 extractions, two of which are also heat extraction, i.e. are intended for heating of network water. The drains from the heaters are discharged either to the previous heater or with the help of drainage pumps to the mixing point. After the main condensate has passed 4 LPHs, it enters the deaerator. The main significance of which is not to heat the water, but to purify it from oxygen, which causes corrosion of pipeline metals, screen pipes, pipes of superheaters and other equipment.

Basic elements and conventions:

K- (capacitor)

KU - boiler plant

HPC - high pressure cylinder

LPC - low pressure cylinder

EG - electric generator

OE - ejector cooler

PS - network heater

PVK - peak hot water boiler

TP - heat consumer

KN - condensate pump

DN - drainage pump

PN - feed pump

HDPE - high pressure heater

LDPE - low pressure heater

D - deaerator

Scheme.1 Thermal diagram of the T50 / 60-130 turbine

Table 1.1. Nominal values ​​of the main parameters of the turbine

Table 1.2. Steam parameters in the selection chamber

Heater	Steam parameters in the selection chamber	Amount of selected steam, kgf/s
Pressure, MPa	Temperature, °С
PVD7	3,41		3,02
PVD6	2,177		4,11
PVD5	1,28		1,69
Deaerator	1,28		1,16
HDPE4	0,529		2,3
PNDZ	0,272		2,97
PND2	0,0981	-	0,97
PND1	0,04	-	0,055

1. The typical energy characteristic of the turbine unit T-50-130 TMZ was compiled on the basis of thermal tests of two turbines (carried out by Yuzhtekhenergo at the Leningradskaya CHPP-14 and Sibtechenergo at the Ust-Kamenogorsk CHPP) and reflects the average efficiency of the turbine unit that has undergone a major overhaul and operates according to the factory design thermal scheme (graph ) and under the following conditions, taken as nominal:

Pressure and temperature of fresh steam in front of the turbine stop valves - respectively - 130 kgf / cm 2 * and 555 ° C;

* Absolute pressures are given in the text and graphs.

The maximum allowable consumption of live steam is 265 t/h;

The maximum allowable steam flow rates through the switchable compartment and low pressure pump are 165 and 140 t/h, respectively; limit values ​​for steam flow through certain compartments correspond to specifications TU 24-2-319-71;

Exhaust steam pressure:

a) to characterize the condensation mode with constant pressure and performance characteristics with selections for two- and one-stage heating of network water - 0.05 kgf / cm 2;

b) to characterize the condensation mode at a constant flow rate and temperature of the cooling water in accordance with the thermal characteristic of the K-2-3000-2 condenser at W = 7000 m 3 / h and t in 1 \u003d 20 ° С - (graph);

c) for the operation mode with steam extraction with three-stage heating of network water - in accordance with the schedule;

The high and low pressure regeneration system is fully included; steam is supplied to the deaerator 6 kgf / cm 2 from III or II selections (with a decrease in steam pressure in the chamberIII selection up to 7 kgf / cm 2 steam is supplied to the deaerator from II selection);

The feed water flow rate is equal to the live steam flow rate;

The temperature of the feed water and the main condensate of the turbine after the heaters corresponds to the dependencies shown in the graphs and ;

The increase in the enthalpy of feed water in the feed pump - 7 kcal/kg;

The efficiency of the electric generator corresponds to the warranty data of the Electrosila plant;

The range of pressure regulation in the upper heating selection - 0.6 - 2.5 kgf / cm 2, and in the lower - 0.5 - 2.0 kgf / cm 2;

Heating of network water in the heating plant - 47 °С.

The test data underlying this energy characteristic were processed using the “Tables of Thermophysical Properties of Water and Steam” (Publishing House of Standards, 1969).

The condensate of the heating steam of the high-pressure heaters is cascaded into HPH No. 5, and from it is fed into the deaerator 6 kgf/cm 2 . With steam pressure in the chamber III selection below 9 kgf / cm 2, the heating steam condensate from HPH No. 5 is sent to HPH 4. At the same time, if the steam pressure in the chamber II selection above 9 kgf/cm 2 , heating steam condensate from HPH No. 6 is sent to the deaerator 6 kgf/cm 2 .

Heating steam condensate from low-pressure heaters is cascaded into LPH No. 2, from which it is fed by drain pumps to the main condensate line behind LPH No. 2. Heating steam condensate from LPH No. 1 is drained into the condenser.

The upper and lower network water heaters are connected respectively to VI and VII turbine selections. The condensate of the heating steam of the upper heating water heater is supplied to the main condensate line downstream of LPH No. 2, and the lower one is fed into the main condensate line downstream of LPH No. I.

2. The composition of the turbine unit, along with the turbine, includes the following equipment:

Generator type TV-60-2 of the Electrosila plant with hydrogen cooling;

Four low pressure heaters: HDPE No. 1 and HDPE No. 2 of type PN-100-16-9, HDPE No. 3 and HDPE No. 4 of type PN-130-16-9;

Three high pressure heaters: HPH No. 5 type PV-350-230-21M, HPH No. 6 type PV-350-230-36M, HPH No. 7 type PV-350-230-50M;

Surface two-way capacitor K2-3000-2;

Two main three-stage ejectors EP-3-600-4A and one starter (one main ejector is constantly in operation);

Two network water heaters (upper and lower) PSS-1300-3-8-1;

Two condensate pumps 8KsD-6´ 3 driven by electric motors with a power of 100 kW (one pump is constantly in operation, the other is in reserve);

Three condensate pumps for network water heaters 8KsD-5´ 3 driven by electric motors with a capacity of 100 kW each (two pumps are in operation, one is in reserve).

3. In the condensing mode of operation with the pressure regulator turned off, the total gross heat consumption and fresh steam consumption, depending on the power at the generator outputs, are analytically expressed by the following equations:

At a constant vapor pressure in the condenser P 2 = 0.05 kgf / cm 2 (graph, b)

Q o \u003d 10.3 + 1.985N t + 0.195 (N t - 45.44) Gcal / h;

D o \u003d 10.8 + 3.368 N t + 0.715 (N t - 45.44) t / h; (2)

At constant flow ( W = 7000 m 3 / h) and temperature ( t in 1 = 20 °C) cooling water (chart, a):

Q o \u003d 10.0 + 1.987 N t + 0.376 (N t - 45.3) Gcal / h; (3)

D o \u003d 8.0 + 3.439 N t + 0.827 (N t - 45.3) t / h. (4)

The heat and live steam consumption for the power specified in the operating conditions are determined according to the above dependencies with the subsequent introduction of the necessary corrections (graphs , , ); these corrections take into account deviations in operating conditions from nominal (from characteristic conditions).

The system of correction curves practically covers the entire range of possible deviations of the operating conditions of the turbine unit from the nominal ones. This makes it possible to analyze the operation of the turbine unit in a power plant.

The corrections are calculated for the condition of maintaining a constant power at the generator outputs. If there are two or more deviations from the nominal operating conditions of the turbogenerator, the corrections are algebraically summed up.

4. In the mode with heat extractions, the turbine unit can operate with one-, two- and three-stage heating of network water. The corresponding typical mode diagrams are shown in the graphs (a - d), , (a - j), A and .

The diagrams indicate the conditions for their construction and the rules for using them.

Typical mode diagrams allow you to directly determine for the accepted initial conditions (N t , Q t , P m) steam flow to the turbine.

On the graphs (a - d) and T-34 (a - k) mode diagrams are shown expressing the dependence D o \u003d f (N t, Q t ) at certain pressure values ​​in controlled extractions.

It should be noted that the regime diagrams for one- and two-stage heating of network water, expressing the dependence D o \u003d f (N t, Q t , P m) (graphs and A), are less accurate due to certain assumptions made in their construction. These mode diagrams can be recommended for use when indicative calculations. When using them, it should be borne in mind that the diagrams do not clearly indicate the boundaries that define all possible modes (in terms of the maximum steam flow rates through the corresponding sections of the turbine flow path and the maximum pressures in the upper and lower extractions).

For more exact definition values ​​of steam flow to the turbine for a given thermal and electrical load and steam pressure in controlled extraction, as well as determining the zone of permissible operating modes, use the mode diagrams presented in the graphs(a - d) and (a - j).

Specific heat consumption for electricity generation for the corresponding operating modes should be determined directly from the graphs(a - d) - for single-stage heating of network water and (a - k)- for two-stage heating of network water.

These graphs are based on the results of special calculations using the characteristics of the sections of the flow path of the turbine and the heat and power plant and do not contain inaccuracies that appear when plotting regime diagrams. The calculation of specific heat consumption for electricity generation using regime diagrams gives a less accurate result.

To determine the specific heat consumption for the production of electricity, as well as the steam consumption for the turbine according to the graphs(a - d) and (a - k) at pressures in controlled extractions for which graphs are not directly given, the interpolation method should be used.

For operating mode with three-stage heating of network water specific consumption heat for electricity production should be determined according to the schedule, which is calculated according to the following relationship:

q t \u003d 860 (1 + ) + kcal / (kW× h), (5)

where Q pr - permanent other heat losses, for turbines 50 MW, taken equal to 0.61 Gcal / h, according to the "Instructions and guidelines on the regulation of specific fuel consumption at thermal power plants (BTI ORGRES, 1966).

The signs of the corrections correspond to the transition from the conditions for constructing the regime diagram to operational ones.

If there are two or more deviations from the nominal operating conditions of the turbine unit, the corrections are algebraically summed up.

Corrections to the power for the parameters of live steam and the temperature of the return network water correspond to the data of the factory calculation.

For the condition of maintaining a constant amount of heat supplied to the consumer ( Q t = const ) when changing the parameters of live steam, it is necessary to make an additional correction to the power, taking into account the change in steam consumption in the extraction due to a change in the enthalpy of steam in the controlled extraction. This correction is determined by the following dependencies:

When operating according to the electrical schedule and a constant steam flow to the turbine:

D \u003d -0.1 Q t (P o - ) kW; (6)

D \u003d +0.1 Q t (t about -) kW; (7)

When working according to the thermal schedule:

D \u003d +0.343 Q t (P o - ) kW; (eight)

D \u003d -0.357 Q t (t about -) kW; (9) T-37.

When determining the heat use of network water heaters, the subcooling of the heating steam condensate is assumed to be 20 °C.

When determining the amount of heat perceived by the built-in beam (for three-stage heating of network water), the temperature difference is assumed to be 6 °C.

The electric power developed according to the heating cycle due to the release of heat from controlled extractions is determined from the expression

N tf = W tf × Q t MW, (12)

where W tf - specific generation of electricity according to the heating cycle under the appropriate modes of operation of the turbine unit is determined according to the schedule.

The electrical power developed by the condensation cycle is defined as the difference

N kn \u003d N t - N tf MW. (thirteen)

5. The method for determining the specific heat consumption for generating electricity for various modes of operation of the turbine unit when the specified conditions deviate from the nominal ones is explained by the following examples.

Example 1: Condensing mode with the pressure regulator switched off.

Given: N t \u003d 40 MW, P o \u003d 125 kgf / cm 2, t about \u003d 550 ° C, P 2 \u003d 0.06 kgf / cm 2; thermal scheme - calculated.

It is required to determine the consumption of live steam and the gross specific heat consumption under given conditions ( N t = 40 MW).

Example 2. Operating mode with controlled steam extractions with two- and one-stage heating of network water.

A. Operating mode according to the thermal schedule

Given: Q t = 60 Gcal/h; R tv \u003d 1.0 kgf / cm 2; R o \u003d 125 kgf / cm 2; t o \u003d 545 ° С; t2 = 55 °С; heating of network water - two-stage; thermal scheme - calculated; other conditions are nominal.

It is required to determine the power at the generator outputs, the consumption of fresh steam and the specific gross heat consumption under given conditions ( Q t \u003d 60 Gcal / h).

In table. the calculation sequence is given.

The operating mode for single-stage heating of network water is calculated similarly.

practice report

6. Turbine T-50-130

Single-shaft steam turbine T-50-130 with a rated power of 50 MW at 3000 rpm with condensation and two heating steam extractions is designed to drive a generator alternating current, type TVF 60-2 with a capacity of 50 MW with hydrogen cooling. The turbine put into operation is controlled from the control panel.

The turbine is designed to operate with fresh steam parameters of 130 ata, 565 C 0 measured in front of the stop valve. The nominal temperature of the cooling water at the inlet to the condenser is 20 С 0 .

The turbine has two heating outlets, upper and lower, designed for stepwise heating of network water in boilers. The feed water is heated sequentially in the refrigerators of the main ejector and the steam suction ejector from the seals with a stuffing box heater, four HDPE and three HPH. HPH No. 1 and No. 2 are fed with steam from heating extractions, and the remaining five - from unregulated extractions after 9, 11, 14, 17, 19 steps.

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Turbine T -100/120-130

Single-shaft steam turbine T 100/120-130 with a rated power of 100 MW at 3000 rpm. With condensation and two heating steam extractions, it is designed for direct drive of an alternating current generator, type TVF-100-2 with a capacity of 100 MW, with hydrogen cooling.

The turbine is designed to operate with fresh steam parameters of 130 ata and a temperature of 565C, measured in front of the stop valve.

The nominal temperature of the cooling water at the inlet to the condenser is 20C.

The turbine has two heating outlets: upper and lower, designed for stepwise heating of network water in boilers.

The turbine can take a load of up to 120 MW at certain values ​​of heating steam extractions.

Turbine PT -65/75-130/13

Condensing turbine with controlled steam extraction for production and district heating without reheating, two-cylinder, single-flow, with a capacity of 65 MW.

The turbine is designed to operate with the following steam parameters:

Pressure in front of the turbine 130 kgf / cm 2,

Steam temperature in front of the turbine 555 °С,

Steam pressure in the production selection 10-18 kgf / cm 2,

Steam pressure in heating extraction 0.6-1.5 kgf / cm 2,

Nominal steam pressure in the condenser 0.04 kgf/cm 2 .

The maximum steam consumption for the turbine is 400 t/h, the maximum steam extraction for production is 250 t/h, maximum amount released heat from hot water- 90 Gcal/h.

The turbine regenerative plant consists of four low-pressure heaters, a 6 kgf/cm2 deaerator, and three high-pressure heaters. Part of the cooling water after the condenser is taken to the water treatment plant.

Turbine T-50-130

The single-shaft steam turbine T-50-130 with a rated power of 50 MW at 3000 rpm with condensation and two heating steam extractions is designed to drive an alternating current generator of the TVF 60-2 type with a power of 50 MW and hydrogen cooling. The turbine put into operation is controlled from the control panel.

The turbine is designed to operate with fresh steam parameters of 130 ata, 565 C 0 measured in front of the stop valve. The nominal temperature of the cooling water at the inlet to the condenser is 20 С 0 .

The turbine has two heating outlets, upper and lower, designed for stepwise heating of network water in boilers. The feed water is heated sequentially in the refrigerators of the main ejector and the steam suction ejector from the seals with a stuffing box heater, four HDPE and three HPH. HPH No. 1 and No. 2 are fed with steam from heating extractions, and the remaining five - from unregulated extractions after 9, 11, 14, 17, 19 steps.

Capacitors

Main purpose condensation device is the condensation of the exhaust steam of the turbine and the provision of optimal steam pressure behind the turbine under nominal operating conditions.

In addition to maintaining the pressure of the exhaust steam at the level required for the economical operation of the turbine plant, it ensures the maintenance of the exhaust steam condensate and its quality in accordance with the requirements of the PTE and the absence of subcooling in relation to the saturation temperature in the condenser.

	Type before and after marking	Capacitor type	Estimated amount of cooling water, t/h	Nominal steam consumption for the condenser, t/h
	dismantling

Technical data of the capacitor 65KTsST:

Heat transfer surface, m 3 3000

Number of cooling pipes, pcs. 5470

Internal and outside diameter, mm 23/25

Length of condenser pipes, mm 7000

Pipe material - copper-nickel alloy MNZh5-1

Nominal consumption of cooling water, m 3 / h 8000

Number of cooling water passes, pcs. 2

Number of cooling water flows, pcs. 2

Mass of the condenser without water, t. 60.3

Mass of the condenser with filled water space, t 92.3

Mass of the condenser with filled vapor space during hydrotesting, t 150.3

The coefficient of cleanliness of the pipes, adopted in the thermal calculation of the condenser 0.9

Cooling water pressure, MPa (kgf/cm2) 0.2(2.0)

Cogeneration turbines with a capacity of 40-100 MW

Cogeneration turbines with a capacity of 40-100 MW for initial steam parameters of 130 kgf / cm 2, 565ºС are designed as a single series, united by common basic solutions, unity of design and wide unification of components and parts.

Turbine T-50-130 with two heating steam extractions at 3000 rpm, rated power 50 MW. Subsequently, the rated power of the turbine was increased to 55 MW with a simultaneous improvement in the efficiency guarantee of the turbine.

The T-50-130 turbine is made of two cylinders and has a single-flow exhaust. All extractions, regenerative and heating, together with the exhaust pipe are located in one low pressure cylinder. In the high pressure cylinder, steam expands to the pressure of the upper regenerative extraction (about 34 kgf / cm 2), in the low pressure cylinder - to the pressure of the lower heating extraction

For the T-50-130 turbine, it was optimal to use a two-ring control wheel with a limited isentropic drop and to make the first group of stages with a small diameter. The high-pressure cylinder of all turbines has 9 stages - regulating and 8 pressure stages.

Subsequent stages located in the medium or low pressure cylinder have a higher volumetric steam flow and are made with larger diameters.

All stages of the turbines of the series have aerodynamically worked out profiles;

The blading of HP and HP is made with radial and axial whiskers, which made it possible to reduce the gaps in the flow path.

The high-pressure cylinder is made counterflow relative to the medium-pressure cylinder, which made it possible to use one thrust bearing and a rigid coupling while maintaining relatively small axial clearances in the flow path of both the HPC and the HPC (or the LPC for 50 MW turbines).

The implementation of heating turbines with one thrust bearing was facilitated by the balance achieved in the turbines of the main part of the axial force within each individual rotor and the transfer of the remaining force, limited in magnitude, to the bearing operating in both directions. In cogeneration turbines, in contrast to condensing turbines, axial forces are determined not only by the steam flow rate, but also by the pressures in the steam extraction chambers. Significant changes in the forces on the flow path take place in turbines with two heating extractions when the outside air temperature changes. Since the steam flow remains unchanged in this case, this change in axial force cannot practically be compensated by the dummis and is completely transferred to the thrust bearing. A factory-made study of variable turbine operation, as well as bifurcation