RU110413U1 - TURBO INSTALLATION FOR AC GENERATOR - Google Patents

Abstract

 1. A turbine unit for an alternating current generator, comprising a gas or steam driven turbine and an alternating current generator on a common shaft, auxiliary equipment including at least one oil pump and an electrical monitoring and control circuit, characterized in that a base frame was introduced in the form of vertical struts rigidly fixed on a horizontal support and at least one horizontal base plate fixed to the said racks, while the turbine and alternator mounted on said horizontal base plate, and accessory devices with electrical control and monitoring circuit are arranged under a horizontal support plate between the uprights. ! 2. The turbine installation according to claim 1, characterized in that the auxiliary equipment comprises an oil supply system for lubricating the bearings of the turbine and generator. ! 3. The turbine installation according to claim 1, characterized in that the auxiliary equipment comprises a condensation installation for collecting condensate from the turbine cavity. ! 4. The turbine installation according to claim 1, characterized in that the auxiliary equipment comprises a sealing system for automatically maintaining the vapor pressure in the turbine seals within 0.02-0.07 kgf / cm2. ! 5. Turbo-installation according to claim 1, characterized in that the auxiliary equipment comprises a technical water supply system for cooling oil and elements of auxiliary equipment. ! 6. Turbo installation according to claim 1, characterized in that the auxiliary equipment contains an automatic protection system to prevent the occurrence or further development of an accident

Description

The utility model relates to electrical engineering and can be used in gas-turbine installations having separate mounting of a gas generator and a free turbine on a foundation frame.

There is a method of mounting a gas generator and a free turbine of a gas turbine drive, in which the gas generator and a free turbine are mounted separately on the foundation frame via a connection unit (see the diagram of the gas turbine unit G6 of the company "AEI", Shubenko-L. Shubin and other gas turbine units. Atlas. constructions and circuits, 2nd ed., revised and enlarged M., "Mechanical Engineering", 1976, 164 p., Fig. II-17 and II-21, §II-3). In the aforementioned diagram, the gas turbine installation is shown in an idle state. In this idle state, the connection node is in a free, undeformed state due to the absence of external forces.

A disadvantage of the known mounting method is that during the installation process uncontrolled mounting voltages are introduced into the elements of the connection unit of the gas generator and the free turbine, which, together with the loads acting during the operation of the gas turbine drive: compressive forces from temperature deformations of the gas generator bodies and the free turbine in the axial direction, internal pressure - reduce the reliability and life of the structure.

There is a method of mounting a gas generator and a free turbine of a gas turbine drive, which consists in pre-installing the gas generator and a free turbine on the foundation frame and securing the bodies of the gas generator and the free turbine with each other via a connection unit (see patent US 4044442 A, IPC B23P 15/04, 1977).

A disadvantage of the known mounting method is also that during the installation process uncontrolled mounting voltages are introduced into the elements of the connection unit of the gas generator and the free turbine, which, together with the loads acting during the operation of the gas turbine drive: compressive forces from temperature deformations of the gas generator bodies and the free turbine in the axial direction , internal pressure - reduce the reliability and resource design.

The technical task of the aforementioned invention is to increase the installation efficiency in terms of ensuring, during subsequent operation, the design to reduce the existing loads in the junction of the gas generator bodies and the free turbine of the gas turbine drive, to provide strength unloading of the junction and increase its life.

A known method of mounting a gas generator and a free turbine of a gas turbine drive includes pre-installing the gas generator and a free turbine on the foundation frame, subsequent installation in the transition section from the gas generator to the free turbine of the connection unit containing the bellows, and fastening the connection unit containing the bellows, previously one side to the body of the gas generator or a free turbine. Then, the final installation and fastening of the gas generator and the free turbine on the foundation frame at the mounting distance is performed, after which the connection unit containing the bellows is fastened, the opposite side to the body of the free turbine or gas generator, respectively. The final installation and fastening of the gas generator and the free turbine on the foundation frame is carried out at a mounting distance determined by the dependence protected by the invention. When attaching the connection unit containing the bellows, the opposite side to the housing of a free turbine or gas generator, respectively, stretch the bellows in the direction of the axis of the gas turbine drive by an amount determined by the dependence protected by the present invention, that is, to eliminate mounting gaps between the connection unit containing the bellows, and gas generator housings and free turbines. The invention allows to reduce the loads acting in the junction of the gas generator and the free turbine of the gas turbine drive, as well as to provide unloading of the bellows and increase its life (RU 2386833, IPC F02C 7/20, F02C 7/28, 03/28/2008).

The disadvantage of this technical solution, as well as the above, are the unavoidable internal structural stresses in the elements of the gas turbine drive, which reduce the reliability of its operation and cause a decrease in the efficiency.

A known turbine installation for an alternator, implemented in an electrical system for a turbine / alternator, comprising a gas-driven turbine and a permanent magnet alternating current generator on a common shaft, comprising said alternating current generator having a permanent magnet rotor and a stator winding, AC bus connected to the stator winding, AC output circuit, inverter connected to the AC output circuit, first contactor for connecting the inverter the rotor to the stator circuit, a DC bus connected to the inverter, a rectifier connected between the AC bus and the DC bus, a temporary power source connected to the DC bus, a master device connected in such a way as to cause the inverter to switch, a signal generator, driven by signals received from rotation of the common shaft, an open-loop oscillation generator, a second contactor for connecting either a signal generator or an open-loop oscillator threads to the inverter, the system controller for switching during start-up of the first contactor to the connection position of the inverter circuit to the AC bus and switching the second contactor to the connection position of the signal generator to the master device and for switching during the power output mode of the first contactor to the inverter AC bus and switching the second contactor to the position of connecting the oscillation generator of the open system to the master, so that during In the start-up mode, the alternator functions as an electric motor, increasing the turbine speed to a safe ignition speed, and in the energy output mode, the electric system generates alternating current electricity with a frequency that is not related to the rotation speed of the alternator to the alternating current output circuit (RU 2224352, IPC H02P 9/04, H02P 9/44, 12/03/1997).

In this technical solution, adopted as a prototype, the aforementioned common drawback for analogues of the mutual mechanical influence of the turbine and generator, eliminating the reliability of the turbine, is eliminated.

The disadvantage of the prototype is the low efficiency of the installation due to losses in the bearings of the rotating elements of the installation, especially when the rotation speed of the turbine is increased, as well as the significant dimensions of the installation, the length of its communication lines and the uncertainty of the spatial orientation of the elements of auxiliary equipment.

The technical result of the utility model is to increase the efficiency of the installation by reducing mechanical losses in the bearings of the rotating elements of the installation, energy losses in the communication lines and sealing elements of the turbine, as well as reducing the dimensions of the installation, the length of its communication lines and optimizing the spatial orientation of the elements of auxiliary equipment

The specified technical result is achieved in that in a turbine installation for an alternating current generator, comprising a turbine driven by gas or steam and an alternating current generator on a common shaft, auxiliary equipment including at least one oil pump and an electrical control circuit and control, a foundation frame has been introduced in the form of vertical struts rigidly fixed on a horizontal support and at least one horizontal base plate fixed on said racks, while the turbine an AC generator mounted on said horizontal base plate, and accessory devices with electrical control and monitoring circuit are arranged under a horizontal support plate between the uprights.

In addition, the auxiliary equipment includes an oil supply system for lubricating the bearings of the turbine and generator.

In addition, the auxiliary equipment contains a condensation unit for collecting condensate from the turbine cavity.

In addition, the auxiliary equipment contains a sealing system for automatically maintaining the vapor pressure in the turbine seals in the range of 0.02-0.07 kgf / cm ² .

In addition, auxiliary equipment contains a technical water supply system for cooling oil and elements of auxiliary equipment.

In addition, auxiliary equipment contains an automatic protection system to prevent the occurrence or further development of an accident in case of damage to individual nodes or deviation of the operating mode from the norm.

In addition, the electrical control and control circuit includes a system for automatically controlling idling, heating and condensation modes with predetermined electric and thermal loads and an instantaneous reset to zero electrical load.

In addition, the oil supply system for lubricating the bearings of the turbine and generator contains at least one oil pump-regulator, made in one piece with the common shaft of the turbine and generator.

The utility model is illustrated by drawings.

Figure 1 - shows a General view of the installation with the layout of its systems on the foundation frame;

Figure 2 - presents a diagram of the oil supply to the thrust bearings of the rotating elements of the installation of the oil supply system.

A turbine installation for an alternating current generator, contains a gas or steam driven turbine 1 and an alternating current generator 2 on a common shaft 3, connected by a clutch 27, eliminating the mutual mechanical influence of the elements of the turbine and the generator on each other, auxiliary equipment, including an oil pump a regulator 4, made in one piece with the common shaft of the turbine and generator, and an electric circuit for monitoring and control 5. A foundation frame 6 is introduced into the turbine installation in the form of rigidly mounted on a horizontal support 7 vertical racks 8 and at least one horizontal base plate 9 mounted on the said racks, while the turbine 1 and the alternator 2 are installed on the horizontal base plate, and auxiliary equipment with devices for electrical control and control circuits are placed under the horizontal base plate between racks.

The auxiliary equipment contains an oil supply system 10 for lubricating the bearings 11 and 12 of the turbine and generator, a condensation unit 13 for collecting condensate from the turbine cavity, a sealing system 14 for automatically maintaining the vapor pressure in the turbine seals within 0.02-0.07 kgf / cm ² , a technical water supply system 15 for cooling oil and auxiliary equipment elements, an automatic protection system 16 to prevent the occurrence or further development of an accident if individual components are damaged or Onen mode from the norm. An automatic control system for idling 17, heating and condensation modes with predetermined electric and thermal loads and an instantaneous reset to zero electrical load is introduced into the control and control circuitry.

At the output end of the shaft 3, in the bearings 23, a pathogen 18 of the control and control electric circuit is mounted on the bearings 23. From the oil tank 22 by the pump-regulator 4 through the oil supply line 19 it is supplied to the bearings 11 of the turbine, the generator 12 bearings and the exciter bearings 23. And through the oil drainage line 20, connected to all bearings, it goes back to the tank for subsequent circulation. An oil cooler 21 is installed on the oil intake line from the tank 22 in front of the suction inlet of the controller 4; it is cooled by a technical water supply system 15. The working steam enters through the steam supply line 24 to the turbine 1 and is supplied through the steam exhaust line 26 to the condensation unit 13 to collect condensate from turbine cavity. Through the pipelines of the cooling line 26 from the technical water supply system 15, the condensation unit 13 and the oil cooler 21 are cooled to the temperature set by the design, controlled by the automatic control system 17.

The set of features of the installation is aimed at reducing mechanical and energy losses and reduces the dimensions of the device as a whole, the efficiency is significantly increased.

The operation of a turbine installation and its systems can be shown with a specific implementation example.

Steam turbine P-6-1,2 / 0,5 / type P (internal structural elements not shown), condensing with adjustable production selection, rated power 6 MW, with a rotation speed of 3000 rpm, with an initial absolute steam pressure of 12 kgf / cm2 is intended for direct drive of an alternator T-6-2UZ.

Fresh steam through the supply line of 24 steam enters through two stop valves and, having passed the steam distribution mechanism, enters the flow part of the turbine.

Behind the 3rd stage of the flow part, a part of the steam is taken into regulated production selection, and the rest of the steam continues to work on the turbine blades, expanding to the pressure in the condenser of the condensation unit 13 to collect condensate from the turbine cavity.

To protect the condenser (internal structural elements of the condensing unit 13 are not shown) from excessive pressure increase on the exhaust part of the turbine housing, two safety diaphragms are installed.

To protect the turbine from increasing pressure in a regulated production take-off, a safety device consisting of pulse and safety valves is installed on the steam line of this selection.

The condensate of the steam spent in the turbine is collected in the condensate collector of the condenser, from where it is pumped out by one of the condensate pumps, the second condensate pump is a backup.

All condensate after the condensate pump is supplied to the level controller: part of the condensate is immediately after the pump, the other part is after the successive passage through the coolers of the main ejector and suction ejector.

The entire condensate stream passes through a level regulator, where it is automatically distributed in the proportion necessary to maintain a constant level in the condensate collector: part of the condensate is sent to the condenser for recycling, and part to the deaerator.

When the turbine is operating with the level control turned off, the condensate flow rate to the deaerator and recirculation are changed manually in order to maintain a constant level in the condensate collector using valves with electric actuators on the outlet line to the deaerator in addition to the level control and on the manual recirculation line.

Steam from the second chamber of the front end seal is discharged into the first chamber of the rear seal, and excess steam from the same line enters the seal regulator together with a pair of leaks from the rods of the control and stop valves.

In this line, the seal regulator of the seal system 14 (internal structural elements not shown) maintains a constant pressure slightly exceeding atmospheric pressure - 0.02-0.07 kgf / cm ² . To do this, the regulator of seals at idle and low turbine loads automatically feeds steam from the station line into the sealing system, and if there is an excess of steam (with large loads on the turbine), it automatically diverts it from the seal system to the turbine adapter pipe.

The extreme chambers of the front and rear end seals, as well as the chamber seals of the actuator rods of the rotary diaphragm and the seal regulator, are connected to the suction ejector, which maintains an absolute pressure in them slightly below atmospheric 97-98 KPa (0.97-0.98 kgf cm ² abs).

To supply steam jet ejectors and a seal regulator, steam is used from the main steam line with an absolute pressure of 1.2 MPa (12 kgf cm ² ) and a temperature of 270 ° C.

If necessary, the turbine can work with the seal regulator turned off, for which by-pass lines with fittings are provided for supplying steam to the sealing system and for dumping excess steam from the sealing system to the turbine adapter pipe.

The cooling water in the oil coolers and air coolers of the generator is supplied by industrial water pumps.

In this case, the water entering to cool the oil coolers and air coolers passes through a water filter. For cleaning, the filter is turned off with the help of valves from the pressure line and the reverse flow of water through the valve 101 and 102 is washed into the sewer.

Drainages of the turbine unit are directed:

- from the steam pipe of fresh steam - to the drainage line of high pressure:

- from the coolers of the suction ejector and from the cooler of the second stage of the main ejector - through hydraulic gates to the atmospheric pressure drainage line;

- from the cooler of the first stage of the main ejector - through a hydraulic shutter to a condenser;

- from the turbine housing and steam pipelines within the turbine - into the adapter pipe between the turbine and the condenser;

- from the bottom point of the steam line after the drainage was performed with two exits: one outlet to the atmosphere (to the funnel), the second exit to the transition pipe between the turbine and the condenser;

- from a blanked pipe emerging from the bottom of the turbine housing, - a permanent drainage through a restrictive washer with a diameter of 5 mm to the upper part of the condenser.

Air outlets from the water filters of the condensate pumps are directed into the condenser.

The turbine is a single-shaft single-cylinder unit, the flow part of which consists of a single-walled control stage and thirteen single-walled pressure stages.

With a controlled production sampling chamber, the turbine is divided into a part of high pressure (CVP) and part of low pressure (NPV). CVP and NPV turbines consist of 3 and 11 stages, respectively.

CVP - from the steam inlet to the production selection consists of a single-walled regulating stage and 2 pressure levels.

NPP - from production selection to exhaust to the condenser consists of a control stage with a rotary diaphragm and 10 pressure levels.

The turbine rotor is flexible with mounted disks, connected to the generator rotor by means of a rigid coupling. At the front end of the shaft there is a neck of the front support bearing and a thrust bearing flange, which is also the impeller of the main oil pump. The impeller of the main oil pump is integral with the shaft. Turbine front bearing combined, support and thrust. Rear turbine bearing

Oil supply system for turbine unit and VPU.

The oil supply system 10 for lubricating the bearings 11 and 12 of the turbine and the generator of the turbine unit is designed to provide the oil with the desired temperature and pressure of the lubrication system of the bearings of the turbine and generator, a hydrodynamic regulation and protection system for the turbine.

The oil supply system includes (the entire composition is not shown):

- main oil tank (MB);

- a block of oil pumps, which includes a drainage oil tank with electric pumps installed on it (starting, parking, emergency and pumping) and an alarm level switch;

- remote switch

- hydraulic pressure switch in the lubrication system;

- pressure sensors, emergency pressure and parking oil pumps;

- the main oil pump regulator 4 (GMN - made integrally with the rotor shaft);

- starting oil pump with a block of relief and check valves (PMN):

- emergency oil electric pump (AMN);

- valve of the emergency emergency oil pump;

- pump shaft-turning device (NVU);

- oil injector (IM);

- oil coolers (MO);

- oil filter (MF);

- parking pump lubrication system (SNM);

- a pumping oil pump (PrMN);

- level gauge in the oil tank;

- pipelines and fittings;

- instrumentation.

The nominal design oil pressure in the control system is 10 kgf / cm ² .

The nominal design oil pressure in the lubrication system is 0.5 kgf cm ² .

When starting the turbine, the oil supply to the unit is from the starting oil electric pump (PMN). By means of a relief valve, a pressure of 8 kgf / cm ^{2 is} automatically maintained at the discharge of the PMN.

The oil flow from the PMN, moving the ball of the check valve, bypasses it and enters:

a) into the oil channel in the front bearing housing, where it presses the ball of the non-return valve to the seat, preventing the flow of power oil into the GMN discharge chamber, and is directed in two directions:

- part of the oil - to the assembly units of the control unit;

- the other part of the oil is fed to the automatic shutter, then through the hydraulic pressure switch in the lubrication system and the remote turbine switch it goes to the quick-locking device of the stop valves, to the hydraulic actuator of the quick-shut-off valve and through the valve to the closing relay of the control valves (as a pulse);

b) into the injector, where an additional amount of oil is sucked in from the oil tank and, mixed, is supplied through the oil coolers in two directions:

- part of the oil - into the suction chamber of the GMV;

- the other part of the oil passes through the throttle, moves the ball of the non-return valve to close the line to the AMS and SMN and through the oil filter enters the lubrication of the bearings of the unit.

To automatically turn on and off the PMN during start-ups and shutdowns of the turbine, as well as to test its automatic turn-on (ATS) on a working turbine, a pressure switch-pressure sensor connected to the pressure line between the check valves of the PMN and GMN is used.

When the pressure in the lubrication system drops to 0.25 kgf / cm, its oil supply starts from a backup (parking) oil electric pump with an alternating current motor (SMN) or from an emergency oil electric pump with a direct current motor (AMN).

The SMN and AMN are switched on (if for some reason the SMN did not turn on) automatically, which is ensured by a pressure switch-sensor connected to the lubrication system. With the help of a pressure switch-sensor, the ABP of electric pumps is also tested on a working turbine.

Oil from the drain tank is pumped into the oil tank using a transfer oil pump (PRMN), the inclusion and shutdown of which occurs automatically from the influence of the level switch.

The working oil is supplied to the shaft-turning device from the gear pump of the shaft-turning device (НВУ), the suction pipe of which is lowered into the oil tank below the oil level.

With an increase in the rotor speed, the oil pressure at the injection of the GMV increases and, when it becomes -8.2 kgf / cm, the PMN will automatically disconnect from the pressure sensor-pressure switch and the oil supply of the unit will take over the GMN.

In this case, the ball of the check valve on the discharge of the GMV moves, which will open the passage of oil through the valve. The oil flow will begin to move in the opposite direction, i.e. from the GMN to the PMN, and will press the ball of the non-return valve on the discharge of the PMN to the seat, preventing the oil from draining through the PMN.

At a nominal rotor speed of the rotor, the GMV maintains an oil pressure of 10 kgf / cm ² in the discharge line.

In the oil supply system, it is conditionally possible to distinguish four interconnected oil circulation circuits:

- the GMH suction circuit, in which the oil from the GMH injection line is fed to the injector, where it, leaving the nozzle at a high speed, draws oil from the tank into the diffuser in an amount that compensates for all drains from the system to the oil tank. From the injector, oil through oil coolers enters the suction chamber of the oil well;

- the lubrication system circuit, in which the oil from the GMN discharge line passes the injector, oil coolers, throttle, oil filter and enters the lubrication of the bearings of the unit;

- the loop of the control system, in which the oil from the GMN discharge line enters the control unit and from it returns to the inlet of the GMN:

- the circuit of the protection system, in which the oil from the GMN discharge line through the automatic shutter, the hydraulic pressure switch in the lubrication system and the remote turbine switch in parallel flows to the quick-locking device of the stop valves, to the hydraulic actuator of the quick-shut-off valve and through the valve to the closing relay of the control valves (as a pulse).

Oil drains directed:

- at the inlet of the oil well - from the assembly units of the control unit;

- to the oil tank - from the bearings of the unit and elements of the protection system (except for the hydraulic drive of the flap valve);

- to the drainage oil tank - from the hydraulic drive of the flap valve.

When the turbine stops, as the rotor speed decreases, the oil pressure at the discharge of the GMV decreases.

When the pressure drops to 7.2 kgf / cm ² , the PMN will automatically come into operation from the action of the pressure switch-sensor and will begin to maintain pressure at the level of 8 kgf / cm ² in the discharge line. In this case, the ball of the non-return valve at the discharge of the PMN will move and open the passage of oil through the valve. The oil flow will begin to move in the opposite direction (from the ПМН to the ГМН) and will press the ball of the non-return valve on the discharge of the ГМН to the seat, preventing the oil from draining through the ГМН.

From this moment, the oil supply to the unit will start from PMN. and oil flows will be distributed, as when starting a turbine.

In the event of a decrease in pressure in the lubrication system to 0.25 kgf / cm ² , an automatic shutdown device (SMN) or AMS occurs (if for some reason the SMN does not turn on) from the action of a pressure switch. Under the influence of the oil flow, the ball of the non-return valve on the discharge line of the pump included in the operation (media and AMS) will move and open the passage of oil through the valve from the pump side.

Further, the oil flow is directed to the check valve, presses the ball and blocking the line from the oil coolers, and through the filter enters the lubrication of the bearings of the unit. In this case, oil will come to the front bearing from the general lubrication system if the pressure in the latter exceeds the oil pressure in this bearing. In this case, the ball of the non-return valve will move and open the passage of oil from the general lubrication system to the bearing.

During the injection of SMN and AMN, the oil pressure is automatically maintained at ~ 1 kgf / cm ² using the corresponding relief valve.

The testing of the automatic switching on of the PMN, SMN and AMN is performed using two valves included in the set of each of the settings of the pressure switch sensors (one valve closes the oil supply to the sensor, the second - opens the oil drain from the sensor, simulating a pressure drop in the corresponding system).

Oil heating before starting the turbine up to 30-40 ° C, as well as oil separation should be carried out by station means.

The oil tank, common to the lubrication system and control system, has a capacity of 3.6 m3 (up to the upper level). The oil level indicator communicates with the internal cavity of the clean compartment of the oil tank using pipelines. Its upper showing part rises above the level of the turbine service site. The level gauge has contacts for the supply of light signals with a minimum of "0" and a maximum of "150" oil levels in the tank, which corresponds to 310 and 160 mm from the oil tank cap. Two rows of flat fine filters are installed in the special guides of the oil tank, which divide the internal cavity of the oil tank into three compartments.

Oil is taken into the suction of the pump unit from the left (third) compartment. A pipe with holes is welded to the flange of the suction pipe, closed at the top with a bottom to prevent absorption from the upper layers of oil saturated with air bubbles.

From the same compartment, the oil injector delivers oil to the intake of the GMV and to the bearings of the unit and the gear pump of the shaft-turning device is sucked in, the intake pipe of which is lowered to the lower oil level and sealed in the oil tank cap with an oil seal.

Oil is drained from the bearings of the turbine and generator through the holes in the receiving compartment of the tank, and then through two rows of flat coarse filters it enters the oil-air sump. Air is vented through the breather into the atmosphere. Through fine filters, oil is sent to the third (clean) compartment of the oil tank.

The degree of contamination of the filters can be judged by the change in the difference in oil levels in the extreme compartments of the tank. The grids are cleaned when the difference in oil levels on them reaches 75 mm.

The removal and cleaning of the flat filters must be carried out alternately. The oil filter type FM-65 is used to clean oil from mechanical impurities.

The oil filter is installed on the line for supplying oil to the lubrication system of the bearings of the turbine unit.

The two-section oil filter consists of a welded casing, in each section of which a filter bag is inserted.

A plug valve is placed between the cavities of the sections of the housing; by turning the handle, one of the filter sections is switched on.

On the cork tap there is a switch knob, on which there is a latch that fixes the position of the handle and the inscription “ON” is engraved. Depending on the position of the handle, the inscription “ON” is located above the filter section in operation.

The air exhaust from the inner cavity of the filter section included in the operation is carried out by a test valve.

Filter bags must be cleaned after each shutdown, repair, revision of the turbine and when the pressure in the lubrication system is reduced by 0.10-0.15 kgf / cm ² compared to the initial one.

To cool the oil circulating in the oil supply system, two oil coolers are used, one of which is reserve and is switched on when the working oil cooler does not provide cooling of the oil to a temperature of 40-45 ° C.

Regulation system.

The turbine installation is equipped with an automatic control system for 17 idling, heating and condensation modes with specified electrical and thermal loads and an instantaneous reset to zero electrical load, which provides the following main operating modes:

1) idling ~ the rotor speed is maintained and it is possible to smoothly change it within the operating range of the synchronizer;

2) heating mode (with the pressure regulator turned on and steam supplied to the controlled selection) - the specified electric and thermal loads are maintained when working in parallel with electric and thermal loads, or the rotor speed of the turbine (frequency of the mains) and the pressure in the controlled selection when working in individual electric and heat networks;

3) condensation mode (without supplying steam to the regulated selection, the pressure regulator is turned off) - the specified electrical load is maintained when working in parallel with the electric load or the rotation speed of the turbine rotor (frequency of the mains) when working in an individual electric network;

4) instantaneous reset to zero electrical load corresponding to the maximum consumption of fresh steam (including when the generator is disconnected from the network) - the turbine rotor speed is kept below the level of operation of the safety automat.

The automatic control system provides:

- the degree of unevenness of the speed control at nominal steam parameters of 4.5 ± 0.5% of nominal;

- speed synchronization range (2850-3150 rpm):

- the degree of insensitivity of the speed control system is not more than 0.3% of the nominal;

- the limits of regulation of the vapor pressure in the production selection from 3 to 5 kgf cm ² ;

- stable holding of the turbine at idle and the ability to change the speed when synchronizing the generator with the electric network:

- closing the control valves from the effects of the relay in case of operation of the elements of the protection system.

The structure of the regulatory system includes (the entire composition is not shown):

- main oil pump regulator 4 (rotor speed sensor):

- supply diaphragm of the pulsed line of the NPI;

- supply diaphragm pulse line CVP;

- pressure transformer;

- shut-off spool of the servomotor of CVP;

- CVD servomotor;

- pressure regulator for production steam extraction;

- shut-off spool of the NPV servomotor;

- NPV servomotor. An element of the protection system, a relay for closing control valves, is connected to the control circuit.

All assembly units and parts of the control system (except for the pump regulator) are located in the body of the control unit.

The system of automatic regulation of the turbine is single-pump, hydrodynamic with two stages of amplification (the first stage is flow-through, the second is cut-off).

The control system has two pulsed flow lines that control one — the CVD servomotor, and the other — the NPV servomotor. Changing each of the adjustable parameters leads to a change in oil flow through both impulse lines and, consequently, to the corresponding movements of the pistons of both servomotors. The feedbacks of each of the servomotors are made hydraulic and each act only on its own shut-off valve.

A centrifugal type main oil pump-regulator (GMN) with radially-drilled channels made in a thrust disk made in one piece with the turbine shaft is used as a rotor speed sensor.

To provide pressure in the suction line of the GMV, an oil injector (IM) is installed in the oil tank, the receiving chamber of which is always located under the oil level.

Oil is supplied to the injector nozzle from the GMN discharge line. The nominal design pressure in the GMN discharge line at a nominal speed of rotation (3000 rpm) is - 10 kgf / cm ² , in the suction line - 1.0 kgf / cm ² .

The design of the GMV is such that its pressure, depending on the speed of rotation, is almost independent of the flow rate, i.e. GMN characteristic (Q-H) is close to horizontal.

Such a flow of the characteristic of the oil well ensures stability, as well as high dynamic indicators of the quality of the regulatory process.

The dependence of the pressure head GMN on the speed is used as a control pulse. In this case, the change in the pressure head of the oil well (direct impulse) is perceived by the spool of the pressure transformer, to the lower piston of which the oil is supplied from the discharge line of the oil well, and to the upper one from the suction line of the oil well. The pressure difference above and below the spool is balanced by a spring.

Thus, the position of the spool of the pressure transformer relative to the sleeve depends on the rotational speed of the rotor. In this case, the rotor speed within the specified range is set by the spring tension, which can be changed using a synchronizer, either directly from the hand - using the flywheel, or remotely - using an electric motor controlled from buttons from the control and monitoring panel.

Under the control of a pressure transformer (synchronizer), the turbine idles and according to the electrical load schedule.

According to the thermal load schedule, the turbine is operated by a pressure regulator.

In this case, the synchronizer flywheel should be installed in the position corresponding to the nominal idle speed.

Bellows type industrial pressure regulator. The pressure force of the steam supplied from the chamber of this selection to the active area of the bellows is balanced by a spring. Thus, the position of the spool of the pressure regulator relative to the sleeve in which it is placed depends on the vapor pressure in the production sampling chamber. The transformer spool and pressure regulator spool each have two control edges, with which they change the passage area for oil drain from two flow impulse lines when the turbine operating mode changes. In this case, the spool of the pressure transformer changes the oil pressure in both impulse lines in one direction (either increases or decreases), and the spool of the pressure regulator in the production selection changes the oil pressure in the impulse lines of different directions. So, with an increase in the rotational speed of the turbine rotor, the pressure in both flow impulse lines increases and, conversely, with a decrease in the rotor speed, it decreases. With increasing steam pressure in the production take-off, the pressure in the flowing pulse line controlling the CVP servomotor increases, and in the flowing pulse line controlling the CVP servomotor decreases. With a decrease in steam pressure in the production selection, the pressure in the flowing pulse line controlling the CVP servomotor decreases, and in the flowing pulse line controlling the CVP servomotor increases.

The shut-off spools controlling the oil inlet from the discharge line of the main oil pump-regulator (GMN) into the working cavities of the corresponding servomotors and the oil release from the inoperative cavities to the GMN suction line, each lower connected to its flow pulse line. Opposite cavities of each of the shut-off spools are under the influence of oil pressure forces in the suction line of the GMV and the efforts of the corresponding spring. The working windows of the shut-off spool bushings, through which the cavities of the servomotors are supplied, are completely closed only with one strictly defined, so-called "average" position of each of the shut-off spools. Thus, the steady state of the system can be achieved only at specified pressures in the flow pulse lines, which are determined by the tension of the springs of the shut-off spools. In the flow pulse line of the CVP and the flow pulse line of the NPV, the nominal pressure is 4.0 kgf / cm ² .

When the turbine rotor rotational speed is changed, as well as when the steam pressure in the production sampling changes, the pressure in the flow pulse lines deviate from the nominal value, as a result, the shut-off spools move from their "average" positions, causing the pistons of the servomotors to move simultaneously. In this case, the passage areas of the steam distributions of the CVP and NPV, as well as the areas of the feedback slots of the servomotors of the CVP and the NPV, will change. The changes in pressure in the flowing impulse lines caused by this will be the opposite of those changes that caused the displacement of both spools from the “middle” position. Therefore, as the pistons of the servomotors move, the pressure in the flowing impulse lines will return to the nominal value, and the shut-off spools will return to their "average" positions. A new steady state of the system will be achieved when the turbine power and steam consumption in the production selection come in line with electric and thermal loads. In this case, the shut-off spools will again be in their "average" positions.

To limit the dynamic speed overshoot in the event of a discharge of electrical load, additional windows are provided in the sleeve of the pressure transformer through which, in this case, direct oil inlet (bypassing the supply diaphragm) from the GMN discharge line to the flow pulse line is provided. As a result, the pressure in the impulse line increases sharply, which causes an instant shutdown of the control valves of the CVP.

In the case described above, for the P-6-1.2 / 0.5 turbine, in addition to the above, oil is also introduced (bypassing the supply diaphragm) from the GMN injection line into the flow pulse line, which causes an instant shutdown of the NPP rotary diaphragm.

To change the rotational speed of the turbine rotor with a constant electrical load when operating in an individual electric network and to change the electric load when operating the turbine, a synchronizer is provided in the general electric network, which is a device by which the initial tension of the spring of the pressure transformer is changed. The synchronizer works both directly from the hand and remotely from the electric drive. The idle speed change of the turbine rotor speed using the synchronizer can be carried out within ± 5% of the nominal value. Changing the power of the turbine can be carried out using a synchronizer from zero to nominal.

To change the steam pressure in the production sampling chamber, a pressure regulator provides a drive with a remote control electric motor and handwheels for manual control, with which the initial tension of the regulator spring is changed.

The pressure regulator is designed to automatically control the pressure in the production selection from 3 to 5 kgf / cm ² .

The range of pressure changes in the production steam extraction chamber at various electrical and thermal loads, as well as the maximum possible steam consumption in production selection and fresh steam consumption in the turbine at various electrical loads are determined by the mode diagram (included in the turbine operating documents).

The control scheme also provides for automatic closing of the control valves of the CVP and the rotary diaphragm of the steam distribution of the NPV when any of the protection mechanism is triggered. The steam distribution organs are closed by means of a relay, which, when the oil pressure in the protection line drops due to the operation of any protection mechanism, makes high pressure oil inlet from the GMN discharge line into flowing impulse lines that control the CVP and NPV servomotors. As a result, the pressure in the flowing impulse lines increases sharply, the shut-off spools shift from their middle positions and, moving upwards, open the upper windows of the bushes through which high-pressure oil is admitted from the GMN discharge line to the lower cavities of the servomotors, and at the same time open the lower windows of said bushings through which oil is drained from the upper cavities of the servomotors to the suction line of the oil well. As a result, the pistons of the servomotors under the influence of oil pressure forces move upwards and thereby close the regulating bodies of the steam distribution of the CVP and NPV.

The opening of the control valves is done by cocking the elements of the protection system.

Automatic protection system.

The automatic protection system 16 is designed to prevent the occurrence or further development of an accident in case of damage to individual nodes or a significant deviation of the mode from the norm.

The automatic protection system includes the following components (not shown):

1) protection elements that act to shut off the supply of fresh steam to the turbine, these include:

- stop valves (2 pcs.), safety regulator with automatic shutter and device for hydraulic testing; remote turbine switch with electromagnetic drive; hydraulic pressure switch in the lubrication system; relay for closing control valves with a testing device, as well as a device for controlling the axial displacement of the rotor (two sensors and two indicating devices),

- an electronic tachometer, vibration equipment, pressure measuring devices in the control system, at the suction of the pump-regulator, in the lubrication system, in the condenser steam space and a device for measuring the temperature of fresh steam,

2) a protection device that acts to prevent the return of steam to the turbine from the production selection, it includes a quick-closing hydraulic shut-off valve,

3) steam safety devices, these include:

- two safety diaphragms on the exhaust of the turbine,

- pulse and safety spring valves on the steam pipe production selection.

The operation of the protection system.

From the discharge line of the main oil pump-regulator (from the starting electric pump - when starting and stopping the turbine), oil is supplied to the quick-locking devices of the stop valves and the hydraulic drive of the production shut-off valve through the automatic shutter, a hydraulic pressure switch in the lubricating system and a remote turbine switch.

From the protection line (the line in front of the stop valves), oil is pulsed as a pulse through the testing device to the closing relay of the control valves.

From the lubrication system, the oil as a pulse is supplied:

- to the hydraulic pressure switch in the lubrication system;

- to the signaling device for measuring pressure in the lubrication system:

- to the installation of a pressure sensor-relay of the emergency oil electric pump.

From the pressure oil line, oil is supplied as a pulse to the installation of a pressure sensor-switch for the starting oil electric pump.

The power oil supply under the hammer of the safety regulator for its testing is made through drilling in the rotor shaft.

The safety regulator is tested at the operating rotor speed when the automatic shutter flywheel is set to the "Test" position by supplying power oil under the hammer by manually pressing the oil valve with the pusher.

The stop valves allow the turbine to stop by instantly shutting off the supply of fresh steam to the turbine when the oil pressure in the working cavities of their quick-locking devices drops to less than 3 kgf / cm ² .

Such a drop in oil pressure in quick-locking devices occurs:

1) when the automatic shutter is triggered by the action of the safety regulator, or from the button of the automatic shutter manual switch;

2) when the remote switch of the turbine is triggered by an electric signal supplied to the tripping electromagnet of the protection elements (axial rotor shift, pressure drop in the lubrication system, maximum rotor speed, pressure drop at the inlet of the main oil regulator pump, increase in oil pressure in the control system, lowering the temperature of fresh steam, increasing the absolute pressure in the condenser, increasing the vibration of the turbine bearings), or from the control button; simultaneously with the actuation of the stop valves, the shut-off valve is forced to close due to the action of the hydraulic drive and the steam backflow:

3) when the hydraulic pressure switch in the lubrication system is activated.

The closing valve of the control valves closes the control valves of the CVP and the rotary diaphragm of the BHP simultaneously with the actuation of the quick-locking devices of the stop valves (in the same cases), which ensures the termination of the flow of fresh steam into the turbine in the event of a loose closing or jamming of the stop valves.

The safety regulator installed in the bore of the turbine rotor shaft provides automatic shutter release when the turbine rotor speed increases to 3360 rpm caused by malfunctioning speed control bodies (including when the load is unloaded from the turbine unit).

A special device is provided for the safety regulator, with the help of which it is possible to test the movement of the striker of the safety regulator on the go of the turbine without increasing the rotor speed and without triggering the stop valves. Moreover, for the period of such testing, the automatic shutter indicator should be set to the "test" position.

A remote switch of the turbine with an electromagnetic drive ensures that high-pressure oil is shut off and at the same time oil is drained from the working cavities of the quick-closing devices of the stop valves, from the hydraulic drive of the shut-off valve and from the pulse cavity of the closing relay of the control valves, causing a shut-off of the shut-off valves and control valves

CIA. PND rotary diaphragm and flap valve in case of:

1) the axial shift of the rotor from the working position by ± 0.8 mm - a signal simultaneously from two sensors of the devices for measuring axial shift according to the "2 of 2" principle;

2) decrease in pressure at the inlet of the main oil pump-regulator to 0.25 kgf / cm2 - a signal from the pressure measuring device;

3) reducing the pressure in the lubricating system to 0.25 kgf / cm2 - a signal from the pressure measuring device;

4) an increase in the oil pressure in the control system to 11.8 kgf cm2 - a signal from the pressure measuring device;

5) increasing the rotor speed to 55 s "(3300 rpm) signal from the sensor (primary transducer), electronic tachometer;

6) increasing the vibration of the front or rear turbine bearings to 11.2 mm / s, which corresponds to a double amplitude of vibration displacement of 100 microns - a signal from any of the vibration sensors of each of the bearings according to the "1 of 1" principle;

7) reducing the temperature of fresh steam to 245 ° C; the signal comes from a device for measuring the temperature of fresh steam;

8) increasing the absolute vapor pressure in the condenser up to 60 kPa (0.6 kgf cm2) - a signal from the pressure measuring device;

9) manually pressing the disconnecting button on the control panel of the turbine. The hydraulic pressure switch in the lubrication system receives a hydraulic signal and provides a cut-off of the high-pressure oil supply and at the same time drain oil from the working cavities of the quick-closing devices of the stop valves, from the hydraulic drive of the shut-off valve and from the pulse cavity of the closing relay of the control valves, thereby triggering the closing of the stop valves , regulating valves of CVP, rotary diaphragm of NPV and valve-flaps. with a decrease in pressure in the lubricating system to a value less than 0.25 kgf / cm ² .

A quick-closing shut-off valve is installed on the steam production steam line and serves to prevent steam backflow into the turbine from the steam extraction line.

The action of the hydraulic actuator on closing the flap valve occurs simultaneously with the closing of the stop valves from the actuation of any of the following protection elements:

1) automatic shutter;

2) a hydraulic pressure switch in the lubrication system;

3 remote turbine switches.

The turbine is equipped with steam safety devices that are installed:

1) on the steam line of production selection (composition - pulse and safety spring valves - actuation with increasing pressure to 6.6 kgf / cm2;

2) on the exhaust part of the turbine casing (composition - two safety diaphragms, triggering when the pressure increases to 0.2 kgf cm2.

Condensation unit.

The condensation unit consists of a condenser KP-540/2, a main ejector EO-50M, a starting ejector EP-150 / P and two condensate electric pumps.

Capacitor case of steel, welded construction. In the upper part there is a wide pipe for receiving steam from the turbine, in the lower part of the condensate collector with a flange for condensate drainage.

Pipe boards are welded to the ends of the body, front and rear water chambers are welded to the pipe boards.

Inside the housing, along its axis, brass cooling tubes are placed, flared on both sides in the tube plates and resting in the openings of the two tube walls. To direct the condensate flowing down from the tubes to the center of the condenser, partitions are used.

The vapor-air mixture is sucked out from the zones of arrangement of the lower bundles of tubes through two collectors placed along the inside of the condenser body. Each collector inside the rear water chamber is connected by a trench with its own pipe, through which the steam-air mixture is sucked off by a steam-jet ejector.

The capacitor is made regenerative. The condensate draining from the pipe system is heated by steam penetrating the lower part of the condenser along the cuts made in the pipe system.

Condensate is collected in a condensate collector, from where it is pumped out by a condensate pump.

Visual control of the level in the condensate tank is carried out using a water-indicating glass.

Two equalization vessels are installed on the condensate collector for connection to primary devices in remote monitoring and condensate level control systems.

The water condenser is made of two independent sections having separate inlet and outlet pipes for cooling water.

This design allows you to audit and clean the cooling tubes of one of the sections without stopping the turbine. In this case, the temperature of the steam in the condenser should not exceed 120 C.

Each section has two strokes of cooling water.

Water enters through the pipe into the front water chamber and through pipes located below the septum, enters the rear water chamber: then the water returns through pipes located above the partition into the front water chamber, from where it exits through the pipe.

Water chambers from the ends are closed by half-caps, which can open independently of one another. Anchor ties are used to create a single rigid system for the lid and tube plate.

For inspection and cleaning of water chambers in the half-caps there are hatches closed by covers.

The capacitor is placed on the foundation with spring supports. The condenser receiving pipe is connected to the turbine exhaust pipes through a transition pipe.

After the next revision, the capacitor must be subjected to a hydraulic test in accordance with the instructions of the assembly drawing of the capacitor. At the same time, for the test period, it is necessary to install rigid technological supports next to the spring supports.

To protect the condenser from excessive pressure increase in the steam space, two safety diaphragms are installed on the exhaust part of the turbine housing.

The system of automatic control of the condensate level in the condenser provides the necessary distribution of condensate flows and the maintenance of the condensate level in the condensate collector within specified limits.

The condenser is designed to work on circulating water with an inlet temperature of 4 to 35 C.

- The temperature of the supply water at the inlet to the condenser is not more than 70 ° C.

- The pressure of the mains water at the inlet to the condenser is not more than 2 kgf / cm2.

The main ejector is designed to remove air (vapor-air mixture) from the condenser to maintain the necessary pressure in it. The P-6-1,2 / 0,5 turbine is equipped with the main ejector EO-50M. The steam-jet main ejector is made of a two-stage sequential action and consists of the following main parts (not shown):

- housing;

- the first stage of the ejector;

- second stage of the ejector;

- two coolers;

- two lower water chambers.

The welded structure ejector body consists of two shells made of pipes and interconnected by a cover, a bottom and 4 side walls. Three internal partitions welded to the shells, the lid, the bottom and the side walls form 4 chambers inside the ejector body V. G. D. E. In the upper part of the shell, the shells are connected to the upper water chambers through compensators that accept thermal elongations of the housing during operation of the ejector . In the lower part of the housing there are special flanges for attaching the lower water chambers.

The first and second stages of the ejector, each consisting of a nozzle chamber, a diffuser, a nozzle holder with a nozzle, are mounted on the housing cover. Steam is supplied to the angle valves directly from the steam line. The diffuser of the first stage of the ejector is placed in chamber B, the diffuser of the second stage is placed in chamber D. Each stage of the ejector has its own cooler.

Each cooler consists of two tube sheets in which brass tubes are expanded. Between the tube plates, transverse and longitudinal partitions are welded, which serve to direct the movement of the vapor-air mixture.

The necessary distance between the transverse partitions is provided by distance tubes, which are dialed into four cooling tubes. The lower pipe boards are welded to the shells of the housing, the upper ones to the shells of the upper water chambers. The upper water chambers are closed with plugs on which test valves are installed to remove air when filling the ejector coolers with water.

To remove air during hydrotesting from the steam part of the coolers, special plugs are provided on the flanges of the upper water chambers.

The lower water chambers are attached to the lower flanges of the housing. The inner cavity of the lower water chambers is divided by partitions into two isolated sections: one section is connected to the cooling water supply pipes, and the second to the cooling water drain pipe.

In the lower part of the shells of the lower water chambers, paws with ribs are welded to install the ejector on the foundation.

Working steam (P = 6.0 kgf / cm ² ) enters through the angle valves to the nozzles of the first and second stages of the ejector.

A steam jet exiting at a high speed from the nozzle of the first stage entrains the vapor-air mixture supplied from the condenser to the inlet nozzle of the nozzle chamber of the first stage. The total flow of the vapor-air mixture compressed in the diffuser enters chamber B. Having risen upward, the mixture through the window in the casing enters the upper part of the first stage cooler and moves in the transverse-longitudinal direction from top to bottom. Most of the vapor from the vapor-air mixture condenses in the cooler, and the remaining mixture enters the chamber D through the bottom window in the shell. In the upper part of the chamber D there is an opening through which the air-vapor mixture enters the nozzle chamber of the second stage of the ejector, where it is captured by a stream of fresh steam leaving at high speed from the nozzle. The total flow of the mixture, compressed in the diffuser to a pressure slightly higher than atmospheric, enters the chamber D and. rising upward, through a window in the shell it enters the upper part of the cooler of the second stage and moves in the transverse-longitudinal direction from top to bottom.

The vapor contained in the mixture condenses, and air enters the chamber E through the lower window and is vented to the atmosphere through the pipe. The pipe has a flange for the installation of a throttle air meter.

Steam condensate from the first stage cooler enters the chamber D and is discharged through the hydraulic lock to the condenser, and from the second stage cooler to the chamber E and then through the hydraulic lock is diverted to the atmospheric pressure drainage line.

From chambers B and D, condensate is removed to the chambers, respectively G and E through openings in the lower part of the shells.

The cooling water in the ejector is the condensate supplied by the condensate pump.

The ejector is made of water from two separate sections having separate nozzles for the inlet and outlet of cooling water. Each section has two moves.

The ejector is equipped with the necessary instrumentation.

The starting ejector is designed to exhaust air from the condenser in order to create a vacuum in it before starting the turbine. The P-6-1,2 / 0,5 turbine is equipped with a starting ejector EP-150 / I.

The ejector consists of a welded steel casing to which a nozzle holder with a nozzle is attached from one end, and a diffuser is connected from the other end.

To the flanges of the housing are connected pipelines of the steam-air mixture from the condenser.

To the diffuser flange is connected the exhaust pipe of the vapor-air mixture into the atmosphere (outside the hall).

Working steam is supplied to the ejector nozzle.

A steam jet exiting at high speed from the nozzle traps air from the mixing chamber. The vapor-air mixture is compressed in the diffuser to a pressure slightly higher than atmospheric, and is discharged through the pipeline into the atmosphere.

When the ejector is turned off, first close the valves on the pipelines for supplying the steam-air mixture, and then the valve on the supply of working steam.

Condensing electric pump.

Two condensate electric pumps of the EKN-50-55 type are used to pump condensate from the condenser, one of which is a backup. The pump is a horizontal, centrifugal, sectional type, with an upstream axial vortex stage with one-sided arrangement of impellers.

The bearings of the rotor are two plain bearings, the lubrication of which is carried out by pumped water. Water for lubrication is taken from the first stage of the pump and is cleaned from mechanical impurities in the strainer.

The filter is single-section, consists of a housing, a filter bag, a cover and a special plug. The filtering element of the bag is a stainless steel mesh with polyamide edging.

When the pump is operating, the axial forces acting on the rotor are unloaded with a hydro-spot, consisting of a thrust disc, a persistent heel and a heel, designed to absorb starting and random loads.

Sealing system.

The system of seals 14 is designed to prevent steaming through the seals of the rods of the steam distribution mechanisms of CVP and NPV and air leaks through the end seals of the rotor shaft at all turbine operating modes.

The seal system includes (not shown):

1) installation of the seal regulator;

2) ejector suction system.

Installation of the seal regulator consists of an actuator (single-turn electric mechanism - MEO) and a seal regulator, which are mounted on a metal frame.

The actuator receives commands from the pressure sensor (DD) and, using a lever transmission, makes the corresponding movements of the gates of the seal regulator.

The operating documents of the MEO and the instrument contain instructions that should be followed when setting them up, checking their health, and servicing.

The chambers between the clips of the front end seal (PCU) and the rear end seal (ZKU) are connected according to the following diagram (count the chamber numbers along the steam through the seals):

- the first PCU chamber - through a valve with a condenser drain manifold:

- the second PCU chamber and the first ZKU chamber - are interconnected by a steam line that is connected to the seal regulator;

- the third PKU camera and the second ZKU camera - with a suction ejector.

The seal chambers of the stop valve rods and the steam distribution mechanism are also connected to the seal regulator, and the seal chambers of the actuator stem of the rotary diaphragm actuator and the stem of the seal regulator are connected to the suction ejector.

During start-up and light loads of the turbine, when the vapor pressure in the turbine housing in front of the end seals is lower than atmospheric, to prevent air from leaking through the seals, steam from the station line is automatically supplied to the second chamber of the front end seal and the first chamber of the rear end seal through the seal regulator.

As the load on the turbine increases, when the pressure in front of the seals increases, external steam supply to them is no longer required and the seal regulator will automatically close the steam supply from the station line, and the excess steam from the seals will be sent to the transition pipe between the turbine and the condenser.

Steam is discharged into the transition pipe between the turbine and the condenser from the sealing system:

- when starting the turbine, as well as when working under load;

- with increasing vapor pressure after the seal regulator more than 0.07 kgf cm ² .

At the same time, at all turbine operating modes, including starting ones, the seal regulator automatically maintains a vapor pressure in the sealing system within the range of 0.02-0.07 kgf / cm2.

If necessary, the turbine can work with the seal regulator turned off, for which purpose bypass lines with valves are provided for supplying steam to the sealing system and removing it from the seal regulator.

The vapor-air mixture from the last chambers of the end seals of the turbine (from the second ZKU and the third PKU), from the chambers of the seal of the actuator stem of the rotary diaphragm and the stem of the seal regulator is sucked out by the suction ejector, maintaining a pressure slightly lower than atmospheric pressure - 0.03-0.02 kgf / cm ² .

Seal adjuster.

The seal regulator is used to maintain constant steam pressure of 0.02-0.010 kgf / cm ² in the chambers of the elements of the sealing system, connected by a steam line, at all operating modes of the turbine, which includes: the first chamber ZKU (chamber numbers for the movement of steam through the seals), the second chamber PKU , chambers of sealing of rods of stop valves and the mechanism of steam distribution of CVP.

Ejector suction system.

The ejector of the suction system (shown) is designed to suck out the vapor-air mixture from the extreme compartments of the end seals of the turbine, the seals of the actuator stem of the rotary diaphragm and the stem of the seal regulator. The P-6-1,2 / 0,5 turbine is equipped with an EU-400 suction ejector.

The suction ejector is made single-stage with two sequential coolers and consists of the following main parts (not shown):

- housing;

- steam jet ejector;

- two coolers:

- two lower and two upper water chambers.

The welded ejector body consists of two shells made of pipes and connected through compensators to the upper water chambers. In the lower part of the housing there are special flanges for attaching the lower water chambers. The shells are interconnected by a lid, a bottom and four side walls. Three internal partitions, welded to the shells, cover, bottom and side walls form four chambers B, V. G, D. inside the ejector body.

The steam jet ejector is mounted on the cover of the ejector and consists of a nozzle chamber, a diffuser, a nozzle holder with a nozzle. The ejector diffuser is placed in the chamber G.

Coolers and water chambers (lower and upper) are unified with coolers and water chambers of the main ejector EO-30M.

From the sealing system, the air-vapor mixture enters chamber B, from where it is sucked into the upper part of the vacuum cooler through a window located in the upper part of the shell. Moving in the transverse-longitudinal direction from top to bottom, the mixture cools, part of the vapor condenses, and the remaining vapor-air mixture through the lower window in the shell enters the chamber B connected to the receiving nozzle of the nozzle chamber.

Steam is supplied to the angle valves directly from the steam line.

Working steam through an angle valve enters the nozzle. A steam jet leaving the nozzle at a high speed entrains the vapor-air mixture from the nozzle chamber connected to chamber B. The total stream of the vapor-air mixture compressed in the diffuser enters the chamber E of the ejector. From chamber D, the air-vapor mixture through the upper shell window enters the upper part of the atmospheric cooler and moves in the transverse-longitudinal direction from top to bottom. In the cooler, the steam condenses, and air through the lower window of the shell enters chamber D and is removed through the pipe into the atmosphere of the mashine.

From chambers B and D, condensate flows through openings in the lower part of the shells into cooler chambers adjacent to it and, together with the condensate formed there, through the lower windows in the shells flows, respectively, into chambers B and D, which are connected by flanges through hydraulic locks to the atmospheric drainage line pressure.

The ejector is equipped with the necessary instrumentation.

Technical water supply system 15 for cooling oil and auxiliary equipment elements.

Pumps technical water pipelines from the cooling tower with a pressure of 5 kgf / cm ² :

enters the turbine section, and then through the filter and pressure regulator (pressure decreases to 3 kgf / cm2) it is supplied to the oil coolers and air coolers of the turbine unit. Having passed the oil coolers and air coolers of the turbine unit, process water is piped to the cooling tower for cooling.

Thus, the technical result is achieved by a useful model, which consists in increasing the efficiency of the installation by reducing mechanical losses in the bearings of the rotating elements of the installation, energy losses in the communication lines and sealing elements of the turbine, as well as reducing the dimensions of the installation, the length of its communication lines and optimization of spatial orientation of auxiliary equipment elements.

Claims (8)

1. A turbine unit for an alternating current generator, comprising a gas or steam driven turbine and an alternating current generator on a common shaft, auxiliary equipment including at least one oil pump and an electrical monitoring and control circuit, characterized in that a base frame was introduced in the form of vertical struts rigidly fixed on a horizontal support and at least one horizontal base plate fixed to the said racks, while the turbine and alternator mounted on said horizontal base plate, and accessory devices with electrical control and monitoring circuit are arranged under a horizontal support plate between the uprights. 2. The turbine installation according to claim 1, characterized in that the auxiliary equipment comprises an oil supply system for lubricating the bearings of the turbine and generator. 3. The turbine installation according to claim 1, characterized in that the auxiliary equipment comprises a condensation installation for collecting condensate from the turbine cavity. 4. The turbine plant according to claim 1, characterized in that the auxiliary equipment comprises a sealing system for automatically maintaining the vapor pressure in the turbine seals within 0.02-0.07 kgf / cm ² . 5. Turbo-installation according to claim 1, characterized in that the auxiliary equipment comprises a technical water supply system for cooling oil and elements of auxiliary equipment. 6. Turbo installation according to claim 1, characterized in that the auxiliary equipment contains an automatic protection system to prevent the occurrence or further development of an accident in case of damage to individual nodes or deviation of the operating mode from the norm. 7. The turbine installation according to claim 1, characterized in that the electrical control and control circuit includes an automatic idle control system, heating and condensation modes with predetermined electric and thermal loads and an instantaneous reset to zero electrical load. 8. The turbine plant according to claim 2, characterized in that the oil supply system for lubricating the bearings of the turbine and generator contains at least one oil pump-regulator, made in one piece with the common shaft of the turbine and generator.