Thermal testing of steam turbines
and turbine equipment

In recent years, in the line of energy saving, attention has increased to fuel consumption standards for enterprises generating heat and electricity, therefore, for generating enterprises, the actual efficiency indicators of heat and power equipment are becoming important.

At the same time, it is known that the actual efficiency indicators under operating conditions differ from the calculated (factory), therefore, in order to objectively standardize fuel consumption for the generation of heat and electricity, it is advisable to test the equipment.

On the basis of equipment test materials, normative energy characteristics and a layout (order, algorithm) for calculating the norms of specific fuel consumption are developed in accordance with RD 34.09.155-93 "Guidelines for the compilation and maintenance of energy characteristics of thermal power plant equipment" and RD 153-34.0-09.154 -99 "Regulations on the regulation of fuel consumption at power plants."

Of particular importance is the testing of heat and power equipment for facilities operating equipment put into operation before the 70s and where modernization and reconstruction of boilers, turbines, auxiliary equipment was carried out. Without testing, normalization of fuel consumption according to the calculated data will lead to significant errors not in favor of generating enterprises. Therefore, the costs of thermal testing are negligible compared to the benefits.

The objectives of thermal testing of steam turbines and turbine equipment: determination of actual economy; obtaining thermal characteristics; comparison with manufacturer's warranties; obtaining data for standardization, control, analysis and optimization of turbine equipment operation; obtaining materials for the development of energy characteristics; development of measures to improve efficiency

The objectives of express testing of steam turbines: determination of the feasibility and scope of repairs; assessment of the quality and effectiveness of the repair or modernization; assessment of the current change in the efficiency of the turbine during operation.

Modern technologies and the level of engineering knowledge make it possible to economically upgrade units, improve their performance and increase their service life.

The main goals of modernization are:

reduction of power consumption of the compressor unit;

increase in compressor performance;

increasing the power and efficiency of the process turbine;

reduction of natural gas consumption;

increasing the operational stability of equipment;

reducing the number of parts by increasing the pressure of compressors and operating turbines at a smaller number of stages while maintaining and even increasing the efficiency of the power plant.

The improvement of the given energy and economic indicators of the turbine unit is carried out through the use of modernized design methods (solution of the direct and inverse problems). They are related:

with the inclusion of more correct models of turbulent viscosity in the calculation scheme,

taking into account the profile and end blockage by the boundary layer,

elimination of separation phenomena with an increase in the diffuseness of the interblade channels and a change in the degree of reactivity (pronounced non-stationarity of the flow before the occurrence of surge),

the possibility of identifying an object using mathematical models with genetic parameter optimization.

The ultimate goal of modernization is always to increase the production of the final product and minimize costs.

An integrated approach to the modernization of turbine equipment

When carrying out modernization, Astronit usually uses an integrated approach, in which the following components of the technological turbine unit are reconstructed (modernized):

compressor;

• centrifugal compressor-supercharger;

  intercoolers;

  multiplier;

  Lubrication system;

  air cleaning system;

  automatic control and protection system.

Modernization of compressor equipment

The main areas of modernization practiced by Astronit specialists:

replacement of flow parts with new ones (the so-called replaceable flow parts, including impellers and vaned diffusers), with improved characteristics, but in the dimensions of existing housings;

reduction in the number of stages due to the improvement of the flow path based on three-dimensional analysis in modern software products;

application of easy-to-work coatings and reduction of radial clearances;

replacement of seals with more efficient ones;

replacement of compressor oil bearings with "dry" bearings using magnetic suspension. This eliminates the use of oil and improves the operating conditions of the compressor.

Implementation of modern control and protection systems

To improve operational reliability and efficiency, modern instrumentation, digital automatic control and protection systems (both individual parts and the entire technological complex as a whole), diagnostic systems and communication systems are being introduced.

STEAM TURBINES

Nozzles and blades.

Thermal cycles.

Rankine cycle.

Reheat cycle.

Cycle with intermediate extraction and utilization of exhaust steam heat.

Turbine structures.

Application.

OTHER TURBINES

Hydraulic turbines.

gas turbines.

Scroll upScroll down

Also on topic

AIRCRAFT POWER PLANTS

ELECTRIC ENERGY

SHIP POWER PLANTS AND PROPULSIONS

HYDROPOWER

TURBINE

TURBINE, prime mover with rotational movement of the working body for converting the kinetic energy of the flow of a liquid or gaseous working fluid into mechanical energy on the shaft. The turbine consists of a rotor with blades (bladed impeller) and a casing with nozzles. Branch pipes bring in and divert the flow of the working fluid. Turbines, depending on the working fluid used, are hydraulic, steam and gas. Depending on the average direction of flow through the turbine, they are divided into axial, in which the flow is parallel to the axis of the turbine, and radial, in which the flow is directed from the periphery to the center.

STEAM TURBINES

The main elements of a steam turbine are the casing, nozzles and rotor blades. Steam from an external source is supplied to the turbine through pipelines. In the nozzles, the potential energy of the steam is converted into the kinetic energy of the jet. The steam escaping from the nozzles is directed to curved (specially profiled) working blades located along the periphery of the rotor. Under the action of a jet of steam, a tangential (circumferential) force appears, causing the rotor to rotate.

Nozzles and blades.

Steam under pressure enters one or more fixed nozzles, in which it expands and from where it flows out at high speed. The flow exits the nozzles at an angle to the plane of rotation of the rotor blades. In some designs, the nozzles are formed by a series of fixed blades (nozzle apparatus). The vanes of the impeller are curved in the direction of flow and arranged radially. In an active turbine (Fig. 1, a) the flow channel of the impeller has a constant cross section, i.e. the speed in relative motion in the impeller does not change in absolute value. The steam pressure in front of the impeller and behind it is the same. In a jet turbine (Fig. 1, b) flow channels of the impeller have a variable cross section. The flow channels of a jet turbine are designed so that the flow rate in them increases, and the pressure decreases accordingly.

R1; c - blading the impeller. V1 is the steam velocity at the outlet of the nozzle; V2 is the speed of steam behind the impeller in a fixed coordinate system; U1 – peripheral speed of the blade; R1 is the speed of steam at the impeller inlet in relative motion; R2 is the speed of steam at the outlet of the impeller in relative motion. 1 - bandage; 2 - scapula; 3 – rotor." title="(!LANG:Fig. 1. TURBINE BLADES. a - active impeller, R1 = R2; b - jet impeller, R2 > R1; c - impeller blades. V1 - steam speed at the nozzle outlet; V2 is the steam velocity behind the impeller in a fixed coordinate system; U1 is the circumferential velocity of the blade; R1 is the steam velocity at the impeller inlet in relative motion; R2 is the steam velocity at the impeller outlet in relative motion. 1 - bandage; 2 - blade; 3 - rotor.">Рис. 1. РАБОЧИЕ ЛОПАТКИ ТУРБИНЫ. а – активное рабочее колесо, R1 = R2; б – реактивное рабочее колесо, R2 > R1; в – облопачивание рабочего колеса. V1 – скорость пара на выходе из сопла; V2 – скорость пара за рабочим колесом в неподвижной системе координат; U1 – окружная скорость лопатки; R1 – скорость пара на входе в рабочее колесо в относительном движении; R2 – скорость пара на выходе из рабочего колеса в относительном движении. 1 – бандаж; 2 – лопатка; 3 – ротор.!}

Turbines are usually designed to be on the same shaft as the device that consumes their energy. The speed of rotation of the impeller is limited by the tensile strength of the materials from which the disk and blades are made. For the most complete and efficient conversion of steam energy, turbines are made multi-stage.

Thermal cycles.

Rankine cycle.

In a turbine operating according to the Rankine cycle (Fig. 2, a), steam comes from an external steam source; there is no additional steam heating between the turbine stages, there are only natural heat losses.

Reheat cycle.

In this cycle (Fig. 2, b) steam after the first stages is sent to the heat exchanger for additional heating (overheating). Then it returns to the turbine again, where its final expansion takes place in subsequent stages. Increasing the temperature of the working fluid allows you to increase the efficiency of the turbine.

Rice. 2. TURBINES WITH DIFFERENT HEAT CYCLES. a – simple Rankine cycle; b – cycle with intermediate steam heating; c - cycle with intermediate steam extraction and heat recovery.

Cycle with intermediate extraction and utilization of exhaust steam heat.

The steam at the outlet of the turbine still has significant thermal energy, which is usually dissipated in the condenser. Part of the energy can be taken from the condensation of the exhaust steam. Some part of the steam can be taken from the intermediate stages of the turbine (Fig. 2, in) and is used for preheating, for example, feed water or for any technological processes.

Turbine structures.

The working medium expands in the turbine, so the last stages (low pressure) must have a larger diameter in order to pass the increased volume flow. The increase in diameter is limited by the allowable maximum stresses due to centrifugal loads at elevated temperatures. In split-flow turbines (Figure 3), the steam passes through different turbines or different turbine stages.

Rice. 3. TURBINES WITH FLOW BRANCHING. a - double parallel turbine; b – double turbine of parallel action with oppositely directed flows; c – turbine with flow branching after several stages of high pressure; d - compound turbine.

Application.

To ensure high efficiency, the turbine must rotate with high speed, however, the number of revolutions is limited by the strength of the materials of the turbine and the equipment that is on the same shaft with it. Electric generators in thermal power plants are rated at 1800 or 3600 rpm and are usually installed on the same shaft as the turbine. Centrifugal superchargers and pumps, fans and centrifuges can be installed on the same shaft with the turbine.

The low speed equipment is coupled to the high speed turbine via a reduction gear, such as in marine engines where the propeller must rotate at 60 to 400 rpm.

OTHER TURBINES

Hydraulic turbines.

In modern hydraulic turbines, the impeller rotates in a special housing with a volute (radial turbine) or has a guide vane at the inlet to ensure the desired flow direction. The appropriate equipment is usually installed on the shaft of a hydroturbine (an electric generator at a hydroelectric power station).

gas turbines.

The gas turbine uses the energy of gaseous combustion products from an external source. Gas turbines are similar in design and principle of operation to steam turbines and are widely used in engineering. see also AIRCRAFT POWER PLANTS; ELECTRIC ENERGY; SHIP POWER PLANTS AND PROPULSIONS; HYDROPOWER.

Literature

Uvarov V.V. Gas turbines and gas turbine plants. M., 1970
Verete A.G., Delving A.K. Marine steam power plants and gas turbines. M., 1982 equipment: basic (boiler plants and steam turbines) and auxiliary. For powerful turbines(And it's about...

Thermal trial gas turbine plant

Laboratory work>> Physics

UPI "Department" Turbines and engines "Laboratory work No. 1" Thermal trial gas turbine plant" Option ... as part of the complex equipment the test stand was turned on ... the launcher was applied steam turbine built on the basis...

Choice of diaphragm blade welding method steam turbines (2)

Coursework >> Industry, production

Melting using thermal energy (arc, ... details steam turbines. shoulder blades steam turbines subdivided... – manufacturability, – availability of the necessary equipment, – availability of qualified personnel, – ... with relevant trials. Thereafter...

Thermal power unit scheme

Diploma work >> Physics

... test; ... equipment thermal power plants. – M.: Energoatomizdat, 1995. Ryzhkin V.Ya. Thermal... power stations. – M.: Energoatomizdat, 1987. Shklover G.G., Milman O.O. Research and calculation of condensing devices steam turbines ...

The main objectives of the tests are to assess the actual state of the turbine plant and its components; comparison with the manufacturer's guarantees and obtaining the data necessary for planning and standardizing its work; optimization of modes and implementation of periodic monitoring of the efficiency of its work with the issuance of recommendations to improve efficiency.

Depending on the objectives of the work, the total scope of tests and measurements, as well as the types of instruments used, are determined. So, for example, tests according to category I of complexity (such tests are also called "balance" or complete tests) of head samples of turbines, turbines after reconstruction (modernization), as well as turbines that do not have a typical energy characteristic, require a large amount of measurements of an increased accuracy class with the obligatory balancing the main steam and water consumption.

Based on the results of several tests of turbines of the same type in the 1st category of complexity, typical energy characteristics are developed, the data of which are taken as the basis for determining the normative indicators of equipment.

With all other types of tests (according to the II category of complexity), as a rule, particular tasks are solved, associated, for example, with determining the efficiency of repairing a turbine plant or upgrading its individual components, periodic monitoring of the state during the overhaul period, experimental finding of some correction dependences for the deviation of parameters from nominal, etc. Such tests require a much smaller volume of measurements and allow the widespread use of standard instruments with their mandatory verification before and after testing; in this case, the thermal scheme of the turbine plant should be as close as possible to the design one. Processing of test results for the II category of complexity is carried out according to the method of "constant flow rate of live steam" (see section E.6.2) using correction curves according to typical energy characteristics or manufacturers.

Along with the above tests, narrower goals can also be pursued, for example, determining the comparative efficiency of regimes with "cut-off LPC" for T-250 / 300-240 turbines, finding corrections to power for changes in exhaust steam pressure in the condenser when operating according to the heat curve, determining losses in the generator, the maximum throughput of the steam inlet and the flow path, etc.

In these Guidelines, the main attention is paid to issues related only to testing turbines in category I of complexity, as representing the greatest complexity at all stages. The test procedure for the II category of complexity will not present great difficulties after mastering the methodology for testing for the I category of complexity, since tests for the II category of complexity, as a rule, require a much smaller amount of measurements, cover the units and elements of the turbine plant, controlled by the I category of complexity, consist of a small number of experiments that do not require compliance with strict and numerous requirements for the thermal scheme and conditions for their implementation.

B. TEST PROGRAM

B.one. General provisions

After a clear clarification of the goals and objectives of the tests, in order to draw up their technical program, it is necessary to carefully familiarize yourself with the turbine plant and have complete information about:

Condition and its compliance with design data;

Its capabilities in terms of ensuring the flow of live steam and steam of controlled extractions, as well as the electrical load in the required range of their change;

Its ability to maintain during the experiments the parameters of steam and water close to nominal and the constancy of the opening of the steam distribution organs;

Opportunities for its operation under the design thermal scheme, the presence of restrictions and intermediate inlets and outlets of extraneous steam and water and the possibility of their exclusion or, as a last resort, accounting;

Possibilities of the measuring circuit to ensure reliable measurements of parameters and costs in the entire range of their change.

The sources of obtaining this information may be the technical specifications (TS) for the supply of equipment, instructions for its operation, audit reports, lists of defects, analysis of the readings of regular recording devices, personnel interviews, etc.

The test program should be drawn up in such a way that, based on the results of the experiments, the dependencies of both the general efficiency indicators of the turbine plant (live steam and heat flow rates from the electric load and the steam flow rates of controlled extractions) and private indicators characterizing the efficiency can be calculated and plotted in the required range. individual compartments (cylinders) of the turbine and auxiliary equipment(e.g. internal efficiencies, stage pressures, temperature differences of heaters, etc.).

The general efficiency indicators obtained from the test make it possible to evaluate the level of a turbine plant in comparison with guarantees and data on turbines of the same type, and also serve as the starting material for planning and standardizing its operation. Particular performance indicators, by analyzing them and comparing them with design and regulatory data, help to identify units and elements that work with reduced efficiency, and timely outline measures to eliminate defects.

IN 2. Structure of the test program

The technical test program consists of the following sections:

Test objectives;

List of modes. In this section, for each series of regimes, the flow rates of live steam and steam to controlled extractions, pressures in controlled extractions and electrical load are indicated, as well as a brief description of thermal scheme, number of experiments and their duration;

- general test conditions. This section specifies the basic requirements for the thermal scheme, gives the limits for the deviation of steam parameters, the method for ensuring the constancy of the regime, etc.

The test program is agreed with the heads of the workshops: boiler-turbine, adjustment and testing, electrical, PTO and is approved by the chief engineer of the power plant. In some cases, for example, when testing prototype turbines, the program is also agreed with the manufacturer and approved by the chief engineer of the power system.

AT 3. Development of test programs for turbines of various types

B.3.1. Condensing and backpressure turbines

The main characteristics of turbines of this type are the dependences of the flow rate of live steam and heat (total and specific) on the electrical load, so the main part of the test program is devoted to experiments to obtain precisely these dependences. Experiments are carried out with the design thermal scheme and nominal steam parameters in the range of electrical loads from 30-40% of the nominal to maximum.

To be able to build the characteristics of turbines with backpressure in the entire range of change of the latter, either three series of experiments (at maximum, nominal and minimum backpressures), or only one series (at nominal backpressure) and experiments to determine the correction to power for a change in backpressure, are carried out.

The choice of intermediate loads is carried out in such a way as to cover all the characteristic points of dependencies, corresponding, in particular:

The opening times of the control valves;

Switching the power source of the deaerator;

Switching from a feed electric pump to a turbopump;

Connecting the second boiler body (for double-block turbines).

The number of experiments on each of the loads is: 2-3 at maximum, nominal and characteristic points and 1-2 at intermediate ones.

The duration of each of the experiments, excluding the adjustment of the mode, is at least 1 hour.

Before the main part of the test, it is planned to carry out so-called calibration experiments, the purpose of which is to compare the flow rates of live steam obtained by independent methods, which will make it possible to judge the "density" of the installation, i.e., the absence of noticeable unaccounted for steam and water supplies or their removal from the cycle. Based on the analysis of the convergence of the compared costs, in addition, a conclusion is made about the greater reliability of determining any of them; in this case, when processing the results, a correction factor is introduced to the flow rate obtained by another method. Carrying out these experiments may be especially necessary in the case when one of the narrowing measuring devices is installed or performed with a deviation from the rules.

It should also be taken into account that the results of calibration experiments can be used to more accurately determine by calculation the internal efficiency of the LPC, since in this case the number of quantities involved in the energy balance equation of the installation is reduced to a minimum.

To carry out calibration experiments, such a thermal scheme is assembled in which the flow rate of live steam can be almost entirely measured in the form of condensate (or exhaust steam for backpressure turbines), which is achieved by turning off the regenerative extractions at the HPH (or transferring their condensate to a cascade drain to the condenser ), a deaerator, if possible, on the LPH (if there is a device for measuring the condensate flow after the condensate pumps) and all withdrawals for general station needs. In this case, all steam and water inlets and their outlets from the turbine plant cycle must be reliably turned off and equal levels in the condenser at the beginning and end of each experiment must be ensured.

The number of calibration experiments in the range of changes in the flow rate of live steam from minimum to maximum is at least 7-8, and the duration of each is at least 30 minutes, provided that the pressure drops on the flow meters and the parameters of the environment in front of them are recorded every minute.

In the absence of a reliable dependence of the change in power on the pressure of the exhaust steam, it becomes necessary to conduct so-called vacuum experiments, during which the thermal scheme practically corresponds to that collected for calibration experiments. In total, two series of experiments are carried out with a change in the pressure of the exhaust steam from minimum to maximum: one - at a steam flow rate in the LPR close to the maximum, and the second - about 40% of the maximum. Each series consists of 10-12 experiments with an average duration of 15-20 minutes. When planning and conducting vacuum experiments, one should specifically mention the need to ensure the minimum possible fluctuations in the initial and final parameters of the steam in order to eliminate or minimize corrections to the turbine power in order to take them into account and, therefore, obtain the most representative and reliable dependence. The program should also stipulate a way to artificially change the pressure of the exhaust steam from experience to experience (for example, air inlet into the condenser, reduction of pressure of the working steam in front of the ejectors, change in the flow rate of cooling water, etc.).

Along with the above, some special experiments can be planned (for example, to determine the maximum power and throughput of the turbine, with a sliding pressure of live steam, to test the effectiveness of the implementation of various measures to determine the efficiency of the LPC, etc.).

B.3.2. Turbines with controlled steam extraction for heating

Turbines of this type (T) are made either with one stage of T-extraction taken from the chamber in front of the regulating body (these are, as a rule, turbines of old production and low power, for example, T-6-35, T-12-35, T- 25-99, etc., in which single-stage heating of network water is carried out), or with two stages of T-selection, one of which is fed from a chamber in front of the regulatory body (NTO), and the second - from a chamber located, as a rule, on two stages higher than the first (WTO) are, for example, turbines T-50-130, T, T-250/300-240 and others, currently produced and operating according to a more economical scheme with multi-stage heating of network water.

In turbines with multi-stage, and after a corresponding reconstruction and in turbines with single-stage heating of network water, in order to utilize the heat of the exhaust steam under the heat schedule mode, a built-in bundle (IP) is specially allocated in the condenser, in which the network water is preheated before it is supplied to the IWW. Thus, depending on the number of stages of heating of network water, there are modes with one-stage heating (LHTO is on), two-stage (HTO and WTO are on) and three-stage (HP, LHT and WTO are on).

The main dependence characteristic of turbines of this type is the mode diagram, which reflects the relationship between the flow rates of live steam and steam in the T-extraction and electric power. Being necessary for planning purposes, the regime diagram is at the same time the source material for calculation and normalization economic indicators turbine installations.

The regime diagrams for the operation of the turbine with one-, two- and three-stage schemes for heating network water are taken as two-field. Their upper field shows the dependences of the turbine power on the flow rate of live steam when operating according to the heat schedule, i.e. with a minimum steam flow in the LPR and various pressures in the RTO.

The lower field of the regime diagram contains the dependences of the maximum heating load on the turbine power, corresponding to the above-mentioned lines of the upper field. Additionally, lines are plotted on the lower field that characterize the dependence of the change in electric power on the heating load when the turbine is operating according to the electrical schedule, i.e., when steam passes in the low-pressure cylinder, greater than the minimum (only for one- and two-stage heating of network water).

Summer operation modes of turbines in the absence of heating load are characterized by dependences of the same type as for condensing turbines.

When testing turbines of this type, as well as for condensing turbines, it may also be necessary to experimentally determine some correction curves for turbine power for deviations of individual parameters from the nominal ones (for example, pressure of the exhaust steam or RTO steam).

Thus, the test program for turbines of this type consists of three sections:

Experiments on the condensation regime;

Experiments for constructing a regime diagram;

Experiments to obtain correction curves.

Each section is discussed separately below.

B.3.2.1. Condensation mode with off pressure regulator in RTO

This section consists of three parts, similar to those specified in the test program for the condensing turbine (calibration experiments, experiments with the design thermal scheme and experiments to determine the correction to the power for the change in exhaust steam pressure in the condenser) and does not require special explanations.

However, in view of the fact that, as a rule, the maximum flow rate of live steam in calibration experiments for turbines of this type is determined by the maximum pass in the LPP, the provision of a pressure drop in the narrowing devices on the live steam lines in the range above this flow rate to the maximum is carried out either by throttling the live steam, either by turning on the HPH with the direction of their heating steam condensate to the condenser, or by turning on the controlled selection and its gradual increase.

B.3.2.2. Experiments for constructing a regime diagram

From the structure of the diagram described above, it follows that in order to construct it, it is necessary to carry out the following series of experiments:

Thermal graph with different pressures in the RTO (to obtain the main dependencies of the upper and lower fields of the diagram. For each of the modes with one-, two- and three-stage heating of network water, 3-4 series are planned (6-7 experiments in each) with different constants pressures in the RHE equal to or close to the maximum, minimum and average, respectively.The range of change in the flow rate of live steam is determined mainly by the limitations of the boiler, the requirements of the instructions and the possibility of reliable measurement of costs;

Electric graph with constant pressure in the RTO (to obtain the dependence of power change on change in heating load). For each of the modes with one- and two-stage heating of network water at a constant flow rate of live steam, 3-4 series are planned (5-6 experiments in each) with a constant pressure in the RTO and a variable heating load from maximum to zero; It is recommended to turn off the HPT for the best accuracy.

B.3.2.3. Experiments for constructing correction curves for power for the deviation of individual parameters from their nominal values

It is necessary to carry out the following series of experiments:

Heat curve with constant live steam flow and variable pressure in the RHE (to determine the correction to the turbine power for a change in pressure in the RHE). For modes with one- and two-stage (or three-stage) heating of network water, two series of 7-8 experiments are carried out at a constant flow rate of fresh steam in each and a change in pressure in the RTO from minimum to maximum. The change in pressure in the RTO is achieved by changing the flow of network water through the PSV with the constant opening of the live steam valves and the minimum opening of the LPR rotary diaphragm.

The high pressure heaters are disabled to improve the accuracy of the results;

Experiments for calculating the correction to the power for the change in the pressure of the exhaust steam in the condenser. Two series of experiments are carried out at steam flow rates in the condenser of the order of 100 and 40% of the maximum. Each series consists of 9-11 experiments with a duration of about 15 minutes in the entire range of exhaust steam pressure change, carried out by air inlet into the condenser, change in cooling water flow rate, steam pressure by the main ejector nozzles, or flow rate of the steam-air mixture sucked from the condenser.

B.3.3. Turbines with controlled steam extraction for production

Turbines of this type have a very limited distribution and are produced either as condensing (P) or with backpressure (PR). In both cases, the diagram of their operation modes is single-field and contains the dependences of the electric power on the flow rates of live steam and P-extraction steam.

By analogy with sect. B.3.2 The test program also contains three sections.

B.3.3.1. Mode without P-selection

It is necessary to carry out the following experiments:

- "taring". Carried out under the conditions specified in sec. B.3.1 and B.3.2.1;

Under normal thermal conditions. They are carried out with the pressure regulator in the P-extraction turned off at a constant pressure of the exhaust steam (for turbines of the PR type).

B.3.3.2. Experiments for constructing a regime diagram

Due to the fact that the steam in the P-extraction chamber is always superheated, it is sufficient to conduct one series of experiments with controlled steam extraction, based on the results of which the characteristics of the HP and LPP are then calculated and plotted, and then the mode diagram.

B.3.3.3. Experiments for constructing correction curves for power

If necessary, experiments are carried out to determine the corrections to the power for changes in the pressure of the exhaust steam and steam in the P-extraction chamber.

B.3.4. Turbines with two adjustable steam extractions for production and heating (PT type)

The regime diagram for turbines of this type does not fundamentally differ from the traditional diagrams of double-selection turbines PT-25-90 and PT-60 with one heat extraction outlet and is also performed as a two-field one, while the upper field describes modes with production extraction, and the lower field describes modes with heat extraction at one - and two-stage heating of network water. Thus, to build a diagram, you need to have the following dependencies:

HPC and LPC capacities from the steam consumption at the inlet at the nominal pressures in the P-extraction and RTO and zero heating load (for the upper field) selected for the nominal pressures;

Changes in the total power of the switchable compartment (SW) and LPR for two-stage heating and LPR for one-stage heating from changes in the heating load.

In order to obtain the mentioned dependencies, it is necessary to carry out the following series of experiments.

B.3.4.1. Condensing mode

In this mode, experiments are carried out:

- "calibration" (PVD and pressure regulators in the selections are disabled). Such experiments are carried out with the thermal scheme of the installation assembled in such a way that the flow rate of live steam passing through the flow meter can be measured almost entirely in the form of condensate using a narrowing device installed on the main condensate line of the turbine. The number of experiments is 8-10 with the duration of each 30-40 minutes (see sections B.3.1 and B.3.2.1);

To calculate the power correction for the change in exhaust steam pressure in the condenser. The pressure regulators in the extractions are turned off, regeneration is turned off, except for LPH No. 1 and 2 (see Section B.3.1);

To determine the correction to power for a change in steam pressure in the RTO (HPH is off, the P-extraction pressure regulator is on). 4 series are carried out with a constant flow of fresh steam (4-5 experiments in each), in two of which the pressure in the WTO changes in steps from minimum to maximum, and in the other two - in the LTO;

With the design thermal scheme. Carried out under conditions similar to those specified in Sect. B.3.1.

B.3.4.2. Modes with production selection

A series of 4-5 experiments is carried out in the range of flow rates from the maximum in the condensing mode () to the maximum allowable when the HPC is fully loaded for steam ().

The value of P-selection is selected according to the conditions of the CHPP, based on the desirability of providing controlled pressure behind the HPC in the entire series of experiments.

B.3.4.3. Modes with heat extraction according to the electrical schedule (to obtain the dependence of power change on the change in heat load)

These modes are similar to those carried out during testing of turbines without P-bleed.

For modes with one- and two-stage heating of network water with the HPH turned off and the flow rate of live steam unchanged, 3-4 series of 5-6 experiments are carried out in each with a constant pressure in the RTO close to the minimum, intermediate and maximum, respectively.

The heating load varies from maximum to zero in each series of experiments by changing the flow of network water through the tube bundles of the IWW.

D. TEST PREPARATION

D.1. General provisions

Preparation for testing is usually carried out in two stages: the first covers work that can and should be carried out relatively long before testing; the second covers the work that is carried out immediately before the tests.

The first stage of preparation includes the following works:

Detailed familiarization with the turbine plant and instrumentation;

Drawing up a technical test program;

Drawing up an experimental control scheme (measurement scheme) and a list of preparatory work;

Drawing up a list (specification) of the necessary instrumentation, equipment and materials.

At the second stage of preparation, the following is performed:

Technical management and supervision of the implementation of preparatory work on the equipment;

Installation and adjustment of the measurement scheme;

Control technical condition equipment and thermal scheme before testing;

Breakdown of measurement points by observation logs;

Drawing up work programs for individual series of experiments.

D.2. Familiarization with the turbine plant

When familiarizing yourself with the turbine installation, you must:

Examine the technical conditions for the supply and design data of the manufacturer, certificates of technical inspections, defect logs, operational data, standards and instructions;

To study the thermal scheme of the turbine plant from the point of view of identifying and, if necessary, eliminating or taking into account various intermediate inlets and outlets of steam and water for the duration of the test;

Determine what measurements need to be made to solve the problems posed before the test. Check in place the presence, condition and location of available measuring devices suitable for use during testing as main or backup;

By checking on site and interviewing the operating personnel, as well as studying the technical documentation, identify all noticed malfunctions in the operation of the equipment, relating, in particular, to the density of shut-off valves, heat exchangers (regenerative heaters, PSV, condenser, etc.), operation of the control system , the ability to maintain stable load conditions and steam parameters (fresh and controlled extractions) required during testing, the operation of level controllers in regenerative heaters, etc.

As a result of a preliminary acquaintance with the turbine plant, it is necessary to clearly understand all the differences in its thermal scheme from the design one and the parameters of steam and water from the nominal ones that may occur during testing, as well as ways to take these deviations into account when processing the results.

D.3. Measurement scheme and list of preparatory work

After a detailed acquaintance with the turbine plant and drawing up a technical test program, one should begin to develop a measurement scheme with a list of measured quantities, the main requirement for which is to provide the possibility of obtaining representative data characterizing the efficiency of the turbine plant as a whole and its individual elements in the entire range of modes outlined by the technical program. To this end, when developing a measurement scheme, it is recommended that the following principles be taken as a basis:

Use for measuring the main parameters of steam and water, generator power and flow rates of sensors and instruments of maximum accuracy;

Ensuring that the measurement limits of the selected instruments correspond to the expected range of changes in the fixed values;

Maximum duplication of measurements of the main quantities with the possibility of their comparison and mutual control. Connecting duplicate sensors to different secondary devices;

Use within reasonable limits of regular measuring instruments and sensors.

The measurement scheme for the turbine plant during the test, the lists of preparatory work (with sketches and drawings) and measurement points, as well as the list of necessary instrumentation (specification) are drawn up as an appendix to the technical program.

D.3.1. Drawing up a measurement scheme and a list of preparatory work for a turbine in operation

The thermal circuit of the turbine plant during the test must ensure a reliable separation of this installation from the general circuit of the power plant, and the measurement circuit must ensure the correct and, if possible, direct determination of all the quantities necessary to solve the problems posed before the test. These measurements should give a clear idea of ​​the flow balance, steam expansion process in the turbine, operation of the steam distribution system and auxiliary equipment. All critical measurements (for example, live steam flow rate, turbine power, parameters of live and exhaust steam, reheat steam, flow rate and temperature of feed water, main condensate, steam pressure and temperature in controlled extraction, and a number of others) must be duplicated, using the connection of independent primary converters to duplicating secondary devices.

A list of measurement points is attached to the thermal scheme, indicating their name and number according to the scheme.

Based on the developed measurement scheme and a detailed acquaintance with the installation, a list of preparatory work for testing is drawn up, which indicates where and what measures must be taken to organize a particular measurement and bring the circuit or equipment to a normal state (repair of fittings, installation of plugs, cleaning of surfaces heating heaters, condenser, elimination of hydraulic leaks in heat exchangers, etc.). In addition, the list of works provides, if necessary, for the organization of additional lighting at observation sites, the installation of signaling devices and the manufacture of various stands and fixtures for mounting primary converters, connecting (impulse) lines and secondary devices.

The list of preparatory work must be accompanied by sketches for the manufacture of the necessary primary measuring devices (bosses, fittings, thermometric sleeves, measuring narrowing devices, etc.), sketches of the tie-in locations of these parts, as well as various stands and fixtures for installing devices. It is also desirable to attach to the list a summary sheet for materials (pipes, fittings, cable, etc.).

The primary measuring devices listed above, as well as the necessary materials, are selected according to current standards in accordance with the parameters of the measured medium and technical requirements.

D.3.2. Drawing up a measurement scheme and a list of preparatory work for a newly installed turbine

For a newly mounted turbine, in particular the prototype, a slightly different approach is required to compiling a measurement scheme (or experimental control - EC) and issuing a task for preparatory work. In this case, the preparation of the turbine for testing should begin already during its design, which is caused by the need to provide in advance additional tie-ins in pipelines for the installation of measuring devices, since with modern thick-walled pipelines and large volume measurements, caused by the complexity of the thermal scheme, it is practically impossible to perform all these works by power plants after the equipment is put into operation. In addition, the EC project includes a significant amount of instrumentation and necessary materials that the power plant is not able to purchase with their non-centralized supply.

Just as in preparation for testing turbines already in operation, it is necessary first to study the technical conditions for the supply and design data of the manufacturer, the thermal scheme of the turbine plant and its relationship with general scheme power plant, become familiar with regular measurements of steam and water parameters, decide what can be used during the test as main or backup measurements, etc.

After clarifying the above questions, you can begin to draw up a technical task. design organization for inclusion in the working design of station instrumentation of the EC project for thermal testing of the turbine plant.

- explanatory note, which sets out the basic requirements for the design and installation of the EC circuit, the selection and location of instrumentation; explanations are given for the equipment for recording information, the features of the use of types of wires and cables, the requirements for the room in which it is supposed to place the EC shield, etc.;

Scheme of the EC of the turbine plant with the name and numbers of measurement positions;

Specification for instrumentation;

Schemes and drawings for the manufacture of non-standard equipment (shield devices, segment diaphragms, intake devices for measuring vacuum in a condenser, etc.);

Schemes of pipe connections of pressure and differential pressure transducers, which provide various options for connecting them, indicating the numbers of measurement positions;

List of measured parameters with their breakdown by recording devices with indication of position numbers.

The places of insertion of measuring devices for EC on the working drawings of pipelines are usually indicated by the design organization and the manufacturer (each in its own design area) according to the terms of reference. If there are no tie-ins anywhere on the drawings, this is done by the enterprise that issued technical task on the EC with a mandatory visa of the organization that issued this drawing.

It is desirable to install the EC circuit during the installation of the standard volume of instrumentation of the turbine plant, which makes it possible to start testing soon after the turbine plant is put into operation.

As an example, appendices 4-6 show the schemes of the main measurements during testing of turbines of various types.

D.4. Selection of instrumentation

The selection of instrumentation is carried out in accordance with the list compiled on the basis of the measurement scheme during testing.

For this purpose, only such instruments should be used, the readings of which can be verified by checking with exemplary ones. Devices with a unified output signal for automatic registration of parameters are selected according to the class of accuracy and reliability in operation (stability of readings).

The list of instrumentation required for testing should indicate the name of the measured quantity, its maximum value, type, accuracy class and instrument scale.

Due to the large volume of measurements when testing modern high-power steam turbines the registration of measured parameters during experiments is often carried out not by observers using direct-acting instruments, but by automatic recording devices with readings recorded on a chart tape, multi-channel recording devices with recording on punched tape or magnetic tape, or operational information-computer complexes (CIC). In this case, measuring devices with a unified output current signal are used as primary measuring devices. However, in the conditions of power plants (vibration, dustiness, the influence of electromagnetic fields, etc.), many of these devices do not provide the necessary stability of readings and require constant adjustment. More preferable in this regard are the recently produced tensoresistor converters "Sapphire-22", which have a high accuracy class (up to 0.1-0.25) of sufficient stability. However, it should be borne in mind that when using the above transducers, it is desirable to duplicate the most critical measurements (for example, pressure in a controlled T-extraction, vacuum in a condenser, etc.) (at least during the period of accumulating experience in working with them), using mercury appliances.

To measure the pressure drop in the narrowing device, the following are used: up to a pressure of 5 MPa (50 kgf / cm2), two-pipe differential pressure gauges DT-50 with glass tubes, and at pressures above 5 MPa, single-tube differential pressure gauges DTE-400 with steel tubes, in which the mercury level is measured visually on a scale using an inductive pointer.

In an automated system for measuring the pressure drop, transducers with a unified output signal of the DME type of accuracy class 1.0 of the Kazan Instrument-Making Plant, DSE type of accuracy class 0.6 of the Ryazan plant "Teplopribor" and the above-mentioned tensoresistor transducers "Sapphire-22" ("Sapphire- 22DD") of the Moscow Instrument-Making Plant "Manometr" and the Kazan Instrument-Making Plant.

As direct-acting pressure measuring devices, for pressures above 0.2 MPa (2 kgf / cm2), spring pressure gauges of accuracy class 0.6 of the MTI type of the Moscow Instrument-Making Plant "Manometr" are used, and for pressures below 0.2 MPa (2 kgf /cm2) - mercury U-shaped pressure gauges, single-tube cup vacuum gauges, barovacuummetric tubes, as well as spring vacuum gauges and pressure vacuum gauges with an accuracy class of up to 0.6.

on newly installed equipment to obtain actual indicators and draw up standard characteristics;
periodically during operation (at least 1 time in 3-4 years) to confirm compliance with regulatory characteristics.
Based on the actual indicators obtained in the process of thermal testing, the ND on fuel use is compiled and approved, the validity period of which is set depending on the degree of its development and the reliability of the source materials, the planned reconstructions and upgrades, equipment repairs, but cannot exceed 5 years.
Based on this, full thermal tests to confirm the compliance of the actual characteristics of the equipment with the regulatory ones should be carried out by specialized commissioning organizations at least once every 3-4 years (taking into account the time required to process the test results, confirm or revise the RD).
By comparing the data obtained as a result of tests on the assessment of the energy efficiency of a turbine plant (the maximum achievable electric power with the corresponding specific consumption for the generation of electricity in condensing and controlled extraction modes with a calculated thermal scheme and with nominal parameters and conditions, the maximum achievable steam and heat supply for turbines with controlled extractions, etc.), an expert organization on fuel use makes a decision to confirm or revise the RD.

List
used literature to chapter 4.4
1. GOST 24278-89. Stationary steam turbine plants for driving electric generators at TPPs. General technical requirements.
2. GOST 28969-91. Stationary steam turbines of low power. General technical requirements.
3. GOST 25364-97. Stationary steam turbine units. Vibration standards for shafting supports and General requirements to taking measurements.
4. GOST 28757-90. Heaters for the regeneration system of steam turbines of thermal power plants. General specifications.
5. Collection of administrative documents for the operation of energy systems (Heat engineering part) .- M .: CJSC Energoservice, 1998.
6. Guidelines for the verification and testing of automatic control systems and protection of steam turbines: RD 34.30.310.- M .:
SPO Soyuztekhenergo, 1984. (SO 153-34.30.310).
Amendment to RD 34.30.310. – M.: SPO ORGRES, 1997.
7. Typical instruction for the operation of oil systems of turbine plants with a capacity of 100-800 MW, operating on mineral oil: RD 34.30.508-93 .- M .: SPO ORGRES, 1994.
(SO 34.30.508-93).
8. Guidelines for the operation of condensing units of steam turbines of power plants: MU 34-70-122-85 (RD 34.30.501).-
M.: SPO Soyuztekhenergo, 1986. (SO 34.30.501).
9. Typical operating instructions for systems
regeneration of high pressure power units with a capacity of 100-800 MW; RD 34.40.509-93, - M.: SPO ORGRES, 1994. (SO 34.40.509-93).
10. Typical instruction for operation of the condensate path and low-pressure regeneration system of power units with a capacity of 100-800 MW at CHP and KES: RD 34.40.510-93, - M .: SPO ORGRES, 1995. (SO 34.40.510-93).
P. Golodnova O.S. Operation of oil supply systems and seals of turbogenerators with; hydrogen cooling. - M.: Energy, 1978.
12. Typical operating instructions for the gas-oil system for hydrogen cooling of generators: RD 153-34.0-45.512-97.- M .: SPO ORGRES,
1998. (SO 34.45.512-97).
13. Guidelines for the conservation of thermal power equipment: RD 34.20,591-97. -
M.: SPO ORGRES, 1997. (SO 34.20.591-97).
14. Regulation on the regulation of fuel consumption at power plants: RD 153-34.0-09.154-99. – M.:
SPO ORGRES, 1999. (SO 153-34.09.154-99).

This CMEA standard applies to stationary steam turbines for driving turbine generators of power plants and establishes the basic rules for the acceptance of turbines and auxiliary equipment during and after installation and testing.

1. GENERAL PROVISIONS

1.1. During the acceptance of the turbine, quality control of the installation is carried out in order to ensure reliable and uninterrupted operation of the turbine and auxiliary equipment during operation. At the same time, control is also exercised over the fulfillment of labor protection, safety and fire safety requirements.

The basic rules for the installation of turbines are given in the information appendix.

1.2. Acceptance of the turbine into operation should consist of the following stages:

1) checking the completeness and technical condition of the turbine and auxiliary equipment before assembly and installation;

2) acceptance of assembly units and turbine systems after installation work;

3) acceptance of assembly units and systems of the steam turbine unit based on the results of their testing;

4) acceptance of the turbine based on the results of comprehensive tests of the steam turbine unit (power unit).

2. ACCEPTANCE OF ASSEMBLY UNITS AND SYSTEMS

2.1. Checking the completeness and technical condition of the turbine assembly units and auxiliary equipment should be carried out as the equipment arrives for installation.

At the same time, the absence of damage and defects of the equipment, the preservation of color, preservative and special coatings, and the integrity of seals are checked.

2.2. Each mechanism, apparatus and system of the steam turbine unit after assembly and installation must pass the tests provided for in the technical documentation. If necessary, an audit can be carried out with the elimination of identified defects.

2.3. The acceptance program shall include the tests and checks necessary to ensure the reliable operation of the steam turbine unit, including:

1) checking the tightness of stop and control valves;

2) verification of the correctness of the readings of measuring instruments, blocking and protection of the unit's systems;

3) checking the correct operation and preliminary adjustment of the regulators of the unit's systems;

9) checking the operation of the regeneration system;

10) checking the density of the vacuum system of the unit.

3. ACCEPTANCE OF THE TURBINE FOR OPERATION

3.1. The final stage of acceptance of the turbine into operation should be a comprehensive test for 72 h when operating for its intended purpose and at nominal electrical and thermal loads.

If, under the conditions of operation of the power plant, the rated loads cannot be achieved, the steam turbine set should be accepted according to the results of tests at the maximum possible load.

3.2. The criterion for acceptance of the turbine into operation should be the absence within the specified time of complex testing of defects that prevent long-term operation.

If, according to the operating conditions of the power plant, complex tests cannot continue for the specified time, the turbine is considered to have passed the tests if there are no defects during the actual time of the complex tests.

3.3. Acceptance of the turbine for operation must be confirmed by a corresponding entry in the form or passport for the turbine in accordance with ST SEV 1798-79.

INFORMATION APPENDIX

BASIC RULES FOR INSTALLATION OF TURBINES

1. The machine room and foundations must be freed from formwork, scaffolding and cleared of debris. Openings must be fenced, and channels, trays and hatches must be closed.

2. In preparation for installation work in winter conditions, windows should be glazed, doorways closed, and heating of the engine room and structures in which a temperature of at least +5 ° C is required for the installation of turbine equipment should be put into operation.

3. On the foundations handed over for the installation of equipment, marking axes for the main equipment must be applied and elevation marks must be fixed.

4. On the foundations intended for the installation of the turbine, the axles must be applied to the embedded metal parts, and the elevation marks must be fixed on the benchmarks.

The axes and benchmarks fixed on the foundation must be located outside the contour of the foundation frames and other supporting structures. Deviations from the design dimensions should not exceed the values ​​established by the supplier in the technical documentation for the production and acceptance of work on the construction of concrete, reinforced concrete and metal structures of foundations.

5. When performing installation work, the requirements of instructions and rules for labor protection and safety must be observed.

6. During installation, the equipment must be cleaned of preservative lubricants and coatings, with the exception of surfaces that must remain covered with protective compounds during the operation of the equipment. Protective coatings on the internal surfaces of the equipment should be removed, as a rule, without dismantling the equipment.

7. Immediately before installing the equipment, the foundation bearing surface must be cleaned to clean concrete and washed with water.

8. Equipment having machined bearing surfaces should be installed on precisely calibrated rigid bearing surfaces of the foundation surface.

9. During the installation process, the bench assembly of the turbine must be repeated in compliance with the clearances, centering of mating assembly units in accordance with the passports and technical requirements.

10. Deviations from the design binding dimensions and marks, as well as from horizontal, vertical, alignment and parallelism during installation of equipment should not exceed the allowable values ​​specified in the technical documentation and installation instructions certain types equipment.

11. During the installation of equipment, the quality control of the work performed, provided for in the technical documentation, must be carried out.

Identified defects must be eliminated before the next installation operations.

12. Concealed work performed during the installation process is checked to determine whether their performance meets the technical requirements. Hidden include work on assembling machines and their assembly units, checking clearances, tolerances and fits, aligning equipment and other work if their quality cannot be verified after subsequent installation or construction work.

13. The equipment supplied for installation should not be disassembled, except when it is provided for disassembly during installation. specifications, instructions or technical documentation.

14. Pipelines and heat exchangers of the steam turbine unit systems must be delivered to the installation site cleaned and mothballed.

2. Subject - 17.131.02.2-76.

3. The CMEA standard was approved at the 53rd meeting of the PCC .

4. Dates for the start of application of the CMEA standard:

5. The term of the first inspection is 1990, the frequency of inspection is 10 years.

The owners of the patent RU 2548333:

The invention relates to the field of mechanical engineering and is intended for testing turbines. Tests of steam and gas turbines of power and power propulsion plants on autonomous stands are an effective means of advancing the development of new technical solutions, which makes it possible to reduce the volume, cost and overall time of work on the creation of new power plants. The technical problem solved by the invention is the elimination of the need to remove the hydraulic brake used during testing of the working fluid; decrease in frequency maintenance work with hydraulic brake; creating the possibility of changing the characteristics of the tested turbine in a wide range during testing. The method is carried out using a stand containing a turbine under test with a working fluid supply system, a hydraulic brake with working fluid supply and discharge pipelines, in which, according to the invention, a container with a working fluid filling system is used, suction and discharge lines of a liquid loading pump with a system of sensors built into them, calibrated for power readings of the tested turbine, while a throttling device and / or a package of throttling devices is installed in the discharge line, and a liquid load pump is used as a hydraulic brake, the shaft of which is kinematically connected to the tested turbine, and the working fluid is supplied to the liquid load pump in a closed cycle with the possibility of its partial reset and supply to the circuit during testing. 2 n. and 4 z.p. f-ly, 1 ill.

The invention relates to the field of mechanical engineering and is intended for testing turbines.

Tests of steam and gas turbines of power and power propulsion plants on autonomous stands are an effective means of advancing the development of new technical solutions, which makes it possible to reduce the volume, cost and overall time of work on the creation of new power plants.

The experience of creating modern power plants indicates that most of the experimental work is transferred to unit tests and their fine-tuning.

There is a known method for testing turbines, based on the absorption and measurement of the power developed by the turbine, using a hydraulic brake, and the frequency of rotation of the turbine rotor during testing, at given values ​​of the air parameters at the turbine inlet, is supported by changing the load of the hydraulic brake by adjusting the amount supplied to the balancing the stator of the hydraulic brake of water, and the set value of the degree of pressure reduction of the turbine is provided by changing the position of the throttle valve installed on the outlet air duct of the stand (see the journal Bulletin of PNRPU. Aerospace Technology. No. 33, article by V.M. Kofman “Methodology and experience in determining the efficiency of gas turbine engines according to the results of their tests on the turbine stand "Ufa State Aviation University 2012 - Prototype).

The disadvantage of this method is the need for frequent bulkheads and flushing of the internal cavities of the hydraulic brake due to the precipitation of hydroxide from process water used as a working fluid, the need to remove the working fluid used in the hydraulic brake during testing, the possibility of cavitation of the hydraulic brake when adjusting its load and, therefore, breakdown hydraulic brakes.

Known stand for testing pumps, containing a tank, a piping system, measuring instruments and devices (see RF patent No. 2476723, MPK F04D 51/00, according to application No. 2011124315/06 of 06/16/2011).

The disadvantage of the known stand is the inability to test turbines.

A well-known stand for testing turbines in natural conditions, containing a hydraulic brake, a receiver for supplying compressed air, a combustion chamber, a tested turbine (see. short course lectures "Testing and ensuring the reliability of aircraft gas turbine engines and power plants", Grigoriev V.A., Federal State Budgetary educational institution higher vocational education Samara State Aerospace University named after Academician S.P. Koroleva (National Research University Samara 2011)).

The disadvantage of the known stand is the need for frequent bulkheads and flushing of the internal cavities of the hydraulic brake due to precipitation of hydroxide from process water used as a working fluid, the inability to change the characteristics of the tested turbine in a wide range during testing, the need to remove the working fluid used in the hydraulic brake during testing .

Known stand for testing gas turbine engines, containing the test engine, consisting of a turbine and a working fluid supply system, a hydraulic brake with pipelines for supplying and discharging water, an adjustable valve and a rater scale (see guidelines "Automated procedure for metrological analysis of a torque measurement system during testing of a gas turbine engine "Federal State Budgetary Educational Institution of Higher Professional Education "Samara State Aerospace University named after Academician S.P. Korolev (National Research University)" Samara 2011 - Prototype).

The disadvantage of the known stand is the need for frequent bulkheads and flushing of the internal cavities of the hydraulic brake due to precipitation of hydroxide from process water used as a working fluid, the inability to change the characteristics of the tested turbine in a wide range during testing, the need to remove the working fluid used in the hydraulic brake during testing , the possibility of cavitation of the hydraulic brake when regulating its load and, consequently, the breakdown of the hydraulic brake.

The technical problem solved by the invention is:

Exclusion of the need to remove the spent hydraulic brake during testing of the working fluid;

Reducing the frequency of routine maintenance with hydraulic brakes;

Creating the possibility of changing the characteristics of the tested turbine in a wide range during testing.

This technical problem is solved by the fact that with a known method of testing turbines, based on measuring the power absorbed by the hydraulic brake, developed by the turbine, and maintaining the rotor speed of the tested turbine during testing, at given values ​​of the parameters of the working fluid at the inlet to the tested turbine, by controlling the amount of the working fluid supplied to the hydraulic brake, according to the invention, a liquid load pump kinematically connected with the tested turbine is used as a hydraulic brake, the flow rate of the outgoing working fluid from which is throttled and / or regulated by changing its characteristics, and the operation of the liquid load pump is carried out in a closed cycle with the ability to work with partial discharge and supply of working fluid to the circuit during the test, and the characteristics of the tested turbine are determined by the measured characteristics of the liquid loading pump.

The method is carried out using a stand containing a turbine under test with a working fluid supply system, a hydraulic brake with working fluid supply and discharge pipelines, in which, according to the invention, a container with a working fluid filling system is used, suction and discharge lines of a liquid loading pump with a system of sensors built into them, calibrated for power readings of the tested turbine, while a throttling device and / or a package of throttling devices is installed in the discharge line, and a liquid load pump is used as a hydraulic brake, the shaft of which is kinematically connected to the tested turbine, and the working fluid is supplied to the liquid load pump in a closed cycle with the possibility of its partial reset and supply to the circuit during testing.

In addition, to implement the method according to the invention, a steam generator with a supply system for fuel and working medium components, for example, hydrogen-oxygen or methane-oxygen, is used as a source of working fluid for the tested turbine.

Also, to implement the method according to the invention, a working fluid flow regulator is installed in the discharge pipeline of the load pump.

In addition, to implement the method according to the invention, chemically treated water is used as the working fluid in the liquid load pump.

Additionally, to implement the method according to the invention, a block for its chemical preparation is included in the system for filling the container with working fluid.

The specified set of features exhibits new properties, consisting in the fact that thanks to it it becomes possible to reduce the frequency of routine maintenance with a liquid load pump used as a hydraulic brake, eliminate the need to remove the working fluid used in the hydraulic brake during testing, create the possibility of changing a wide range of characteristics of the tested turbines by changing the characteristics of the liquid load pump.

A schematic diagram of the turbine test bench is shown in figure 1, where

1 - system for filling the container with the working fluid;

2 - block of chemical preparation of the working fluid;

3 - capacity;

4 - pressurization system of the container with the working fluid;

5 - valve;

6 - suction line;

7 - discharge line;

8 - liquid loading pump;

9 - system for supplying the working fluid to the tested turbine;

10 - tested turbine;

11 - steam generator;

12 - system for supplying fuel and working medium components;

13 - package of throttling devices;

14 - working fluid flow regulator;

15 - pressure sensor;

16 - temperature sensor;

17 - sensor for recording the flow of the working fluid;

18 - vibration sensor;

19 - filter;

20 - valve.

The turbine test stand consists of a working fluid filling system 1 with a working fluid chemical preparation unit 2, a tank 3, a pressurization system for a working fluid tank 4, a valve 5, suction 6 and discharge 7 lines, a liquid loading pump 8, a working fluid supply system 9 into the tested turbine 10, steam generator 11, supply system for fuel and working medium components 12, a package of throttling devices 13, a working fluid flow regulator 14, pressure sensors, temperature sensors, recording the working fluid flow rate and vibration 15, 16, 17, 18, filter 19 and valve 20.

The principle of operation of the turbine test bench is as follows.

The operation of the turbine test bench begins with the fact that, through the system for filling with working fluid 1 using unit 2, chemically prepared water used as a working fluid enters tank 3. After filling tank 3 through system 4, it is pressurized with neutral gas to the required pressure . Then, when the valve 5 is opened, the suction 6, discharge 7 lines and the liquid load pump 8 are filled with working fluid.

Further, through system 9, the working fluid is fed to the blades of the tested turbine 10.

As a device for generating the working fluid of the tested turbine, a steam generator 11 (for example, hydrogen-oxygen or methane-oxygen) is used, into which fuel and working medium components are supplied through system 12. When the fuel components are burned in the steam generator 11 and the working medium is added, high-temperature steam is formed, which is used as the working fluid of the tested turbine 10.

When the working fluid hits the blades of the tested turbine 10, its rotor, which is kinematically connected to the shaft of the liquid load pump 8, starts to move. The torque from the rotor of the tested turbine 10 is transmitted to the shaft of the liquid load pump 8, the latter of which is used as a hydraulic brake.

The pressure of chemically treated water after the liquid loading pump 8 is triggered using a package of throttling devices 13. To change the flow rate of chemically treated water through the liquid loading pump 8, a working fluid flow regulator 14 is installed in the discharge pipeline 7. The characteristics of the liquid loading pump 8 are determined according to the readings of sensors 15, 16, 17. The vibration characteristics of the liquid load pump 8 and the tested turbine 10 are determined by the sensors 18. The filtration of chemically treated water during the operation of the stand is carried out through the filter 19, and it is drained from the tank 3 through the valve 20.

To prevent overheating of the working fluid in the circuit of the liquid load pump 8 during long-term testing of the turbine, it is possible to partially reset it when valve 20 is opened, as well as to supply additional tank 3 through the filling system with working fluid 1 during the test.

Thus, due to the use of the invention, the need to remove the working fluid after the liquid load pump used as a hydraulic brake is eliminated, it becomes possible to reduce between start-up routine maintenance on the test bench and, during testing, obtain an extended characteristic of the tested turbine.

1. A method for testing turbines, based on measuring the power absorbed by the hydraulic brake developed by the turbine, and maintaining the rotor speed of the tested turbine during testing, at given values ​​of the parameters of the working fluid at the inlet to the tested turbine, by controlling the amount of working fluid supplied to the hydraulic brake, which differs by the fact that a liquid load pump kinematically connected with the tested turbine is used as a hydraulic brake, the flow rate of the outgoing working fluid from which is throttled and/or regulated by changing its characteristics, and the operation of the liquid load pump is carried out in a closed cycle with the possibility of working with partial discharge and supply of working fluid. fluid into the loop during the test, the turbine being tested being measured from the measured performance of the fluid loading pump.

2. The stand for implementing the method according to claim 1, containing the tested turbine with a working fluid supply system, a hydraulic brake with working fluid supply and discharge pipelines, characterized in that it contains a container with a working fluid filling system, suction and discharge lines of a liquid loading pump with a system of sensors mounted in them, calibrated for the power readings of the tested turbine, while a throttling device and / or a package of throttling devices is installed in the discharge line, and a liquid load pump is used as a hydraulic brake, the shaft of which is kinematically connected to the tested turbine, and the working fluid into the liquid the load pump is supplied in a closed cycle with the possibility of its partial reset and supply to the circuit during testing.

3. Stand according to claim 2, characterized in that a steam generator with a system for supplying fuel and working medium components, for example, hydrogen-oxygen or methane-oxygen, is used as a source of the working fluid for the tested turbine.

4. The stand according to claim 2, characterized in that a working fluid flow regulator is installed in the discharge pipeline of the liquid loading pump.

5. Stand according to claim 2, characterized in that chemically treated water is used as the working fluid in the liquid loading pump.

6. Stand according to claim 2, characterized in that the system for filling the container with working fluid includes a block for its chemical preparation.

Similar patents:

The invention can be used in the process of determining the technical condition of the diesel fine filter (F). The method consists in measuring the fuel pressure at two points of the diesel fuel system, the first of the pressures PTH is measured at the inlet to the filter for fine fuel cleaning, the second pressure PTD is measured at the outlet of the filter.

Method for monitoring the technical condition and maintenance of a gas turbine engine with an afterburner. The method includes measuring the fuel pressure in the manifold of the afterburner combustion chamber of the engine, which is carried out periodically, comparing the obtained value of fuel pressure in the manifold of the afterburner combustion chamber of the engine with the maximum allowable value, which is preliminarily set for of this type engines, and when the last cleaning of the collector and afterburner nozzles is exceeded, the medium is forcibly pumped out of its internal cavity using a pumping device, such as a vacuum pump, and the pressure created by the pumping device is periodically changed.

The invention relates to radar and can be used to measure the backscatter amplitude diagrams of an aircraft turbojet engine. The stand for measuring the amplitude diagrams of backscattering of aircraft turbojet engines contains a turntable, receiving, transmitting and recording devices radar station, platform angular position meter, front and at least one rear rack with the object of study placed on them.

The invention relates to the field of diagnostics, and in particular to methods for assessing the technical condition of rotary units, and can be used in assessing the condition of bearing assemblies, such as wheel-motor units (KMB) of rolling stock of railway transport.

The invention can be used in fuel systems of internal combustion engines of vehicles. The vehicle contains a fuel system (31) having a fuel tank (32) and a tank (30), a diagnostic module having a control hole (56), a pressure sensor (54), a control valve (58), a pump (52) and a controller .

The invention relates to the maintenance of motor vehicles, in particular to methods for determining environmental safety Maintenance cars, tractors, combines and other self-propelled machines.

The invention can be used to diagnose internal combustion engines (ICE). The method consists in recording noise in the internal combustion engine cylinder.

The invention can be used for diagnosing the high-pressure fuel equipment of diesel automotive and tractor engines under operating conditions. The method for determining the technical condition of the fuel equipment of a diesel engine lies in the fact that, with the engine running, the dependences of the change in fuel pressure in the high-pressure fuel line are obtained and these dependences are compared with the reference ones.

The invention relates to the field of aircraft engine building, namely to aircraft gas turbine engines. In the method of serial production of gas turbine engines, parts are manufactured and completed Assembly units, elements and components of modules and engine systems.

The invention relates to test benches for determining the characteristics and limits of stable operation of the compressor as part of a gas turbine engine. To shift the operating point according to the characteristics of the compressor stage to the boundary of stable operation, it is necessary to introduce the working fluid (air) into the interblade channel of the guide vane of the studied compressor stage. The working fluid is fed directly into the interblade channel of the studied stage using a jet nozzle with an oblique cut. The flow rate of the working fluid is controlled by a throttle valve. Also, the working fluid can be fed into the hollow blade of the guide vane of the studied stage and exit into the flow path through a special system of holes on the profile surface, causing the separation of the boundary layer. Allows you to explore the characteristics of individual stages of the axial compressor as part of the gas turbine engine, to study the operating modes of the axial compressor stage at the boundary of stable operation without negative impacts on the elements of the engine under study. 2 n. and 1 z.p. f-ly, 3 ill.

The invention can be used for diagnosing the operability of the air swirl system in the inlet pipeline of an internal combustion engine (ICE). The method consists in determining the position of the movable shaft (140) of the drive (PVP) using a mechanical stop (18) to act on the element (13) of the kinematic chain in order to limit the movement of the PVP in the first direction (A) in the first control position (CP1) and checking using the position detection means (141) whether the PVP has stopped at the first control position (CP1) or has gone beyond it. Additional techniques of the method are given. A device for implementing the method is described. The technical result is to increase the accuracy of diagnosing performance. 2 n. and 12 z.p. f-ly.

The invention can be used to control the angular parameters of the gas distribution mechanism (GDM) of an internal combustion engine (ICE) during running-in at the stand of a repaired ICE and during life diagnostics in operation. The device for diagnosing the timing of the internal combustion engine contains a goniometer for measuring the angle of rotation of the crankshaft (KV) from the moment the inlet valve of the first support cylinder (POC) begins to open to the shaft position corresponding to the top dead center (TDC) of the POC, a disk with a graduated scale connected to the KV of the internal combustion engine , a fixed arrow-pointer (SU), installed so that the tip of the SU is opposite the graduated scale of the rotating disk. The device contains a position sensor KV, corresponding to the TDC of the POC, and a valve position sensor, a stroboscope, with a high-voltage transformer and a spark gap, controlled through the control unit (CU) by the position sensor KV. Each valve position sensor is connected by means of the control unit to the power supply unit (BP) and, when changing its position, generates a strobe light pulse relative to the stationary control unit. The difference between the fixed values ​​during the operation of the valve sensor and during the operation of the TDC sensor corresponds to the numerical value of the angle of rotation KV from the moment the valve starts to open to the moment corresponding to the arrival of the first cylinder piston at TDC. The technical result is to reduce the measurement error. 1 ill.

The invention relates to mechanical engineering and can be used in testing equipment, namely in stands for testing machines, their units, angles and parts. The torque loading mechanism (1) contains a gear assembly (2) and an actuator assembly (3). The gear assembly (2) includes an inner part (4) and outer parts (5) and (6). The inner part (4) contains gears (17) and (18), which, assembled with each other, have threaded holes for special technological screws (66) and (67). The outer parts (5) and (6) contain gears (29) and (31), in the diaphragms of which (28), (30) and (34) there are holes that allow you to place special technological bolts (70) with nuts in them. (71) for rigid fastening of the gears (29) and (31) against rotation relative to each other in order to perform dynamic balancing. Achieves torque up to 20,000 Nm at input speeds up to 4,500 rpm with low vibration levels. 3 ill.

The invention relates to the field of aircraft engine building, namely to aircraft turbojet engines. Fine-tuning is subjected to an experimental turbojet engine, made double-circuit, two-shaft. Fine-tuning of the turbojet engine is carried out in stages. At each stage, one to five turbojet engines are tested for compliance with the specified parameters. At the finishing stage, an experienced turbojet engine is subjected to a multi-cycle test. When performing the test stages, an alternation of modes is carried out, which in duration exceeds the programmed flight time. Typical flight cycles are formed, on the basis of which the program determines the damageability of the most loaded parts. Based on this, determine required amount loading cycles during testing. Form the full scope of tests, including a quick change of cycles in the full register from a quick exit to the maximum or full forced mode to a complete stop of the engine and then a representative cycle long work with multiple alternation of modes over the entire operating spectrum with a different swing of the range of mode changes, exceeding the flight time by at least 5 times. A quick exit to the maximum or forced mode for a part of the test cycle is carried out at the rate of acceleration and reset. The technical result consists in increasing the reliability of test results at the stage of development of experimental turbojet engines and expanding the representativeness of the assessment of the resource and reliability of the turbojet engine in a wide range of regional and seasonal conditions for the subsequent flight operation of engines. 5 z.p. f-ly, 2 ill.

The invention relates to the field of aircraft engine building, namely to aircraft gas turbine engines. Fine-tuning is subjected to an experimental gas turbine engine, made double-circuit, two-shaft. Fine-tuning of the gas turbine engine is carried out in stages. At each stage, one to five gas turbine engines are tested for compliance with the specified parameters. Examine and, if necessary, replace with a modified one any of the modules damaged in tests or not meeting the required parameters - from a low-pressure compressor to an all-mode rotary jet nozzle, including an adjustable jet nozzle and a rotary device detachably attached to the afterburner combustion chamber, the axis of rotation of which is turned relative to the horizontal axis by angle not less than 30°. The test program with subsequent refinement includes engine tests to determine the effect of climatic conditions on changes in the operational characteristics of an experimental gas turbine engine. The tests were carried out with the measurement of engine operation parameters in various modes within the programmed range of flight modes for a specific series of engines, and the resulting parameters are brought to standard atmospheric conditions, taking into account changes in the properties of the working fluid and the geometric characteristics of the engine flow path when atmospheric conditions change. The technical result consists in improving the performance characteristics of the gas turbine engine, namely the thrust and reliability of the engine during operation in the full range of flight cycles in various climatic conditions, as well as in simplifying the technology and reducing labor costs and energy intensity of the gas turbine engine testing process at the stage of fine-tuning the experimental gas turbine engine. 3 w.p. f-ly, 2 ill., 4 tab.

The invention relates to the field of aircraft engine building, namely to aircraft turbojet engines. The turbojet engine is made double-circuit, twin-shaft. The axis of rotation of the rotary device relative to the horizontal axis is rotated by an angle of at least 30° clockwise for the right engine and by an angle of at least 30° counterclockwise for the left engine. The engine was tested under a multi-cycle program. When performing the test stages, an alternation of modes is carried out, which in duration exceeds the programmed flight time. Typical flight cycles are formed, on the basis of which the program determines the damageability of the most loaded parts. Based on this, the required number of loading cycles during testing is determined. The full scope of tests is formed, including a quick change of cycles in the full register from a quick exit to the maximum or full forced mode to a complete engine shutdown and then a representative cycle of long-term operation with multiple alternation of modes over the entire operating spectrum with a different swing of the range of mode changes that does not exceed the flight time less than 5-6 times. A quick exit to the maximum or forced mode for a part of the test cycle is carried out at the rate of acceleration and reset. The technical result consists in increasing the reliability of the test results and expanding the representativeness of the assessment of the resource and reliability of the turbojet engine in a wide range of regional and seasonal conditions for the subsequent flight operation of the engines. 8 w.p. f-ly, 1 ill.

The invention relates to the field of aircraft engine building, namely to aircraft gas turbine engines. Fine-tuning is subjected to an experimental gas turbine engine, made double-circuit, two-shaft. Fine-tuning of the gas turbine engine is carried out in stages. At each stage, one to five gas turbine engines are tested for compliance with the specified parameters. The test program with subsequent refinement includes engine tests to determine the effect of climatic conditions on changes in the operational characteristics of an experimental gas turbine engine. The tests were carried out with the measurement of engine operation parameters in various modes within the programmed range of flight modes for a specific series of engines and the resulting parameters are brought to standard atmospheric conditions, taking into account changes in the properties of the working fluid and the geometric characteristics of the engine flow path when atmospheric conditions change. The technical result consists in improving the performance characteristics of gas turbine engines, namely thrust, with an experimentally proven resource, and engine reliability during operation in the full range of flight cycles in various climatic conditions, as well as in simplifying the technology and reducing labor costs and energy intensity of the gas turbine engine testing process at the stage of fine-tuning the experimental GTD. 3 w.p. f-ly, 2 ill., 4 tab.

The invention relates to the field of aircraft engine building, namely to aircraft gas turbine engines. In the method of serial production of a gas turbine engine, parts are manufactured and assembly units, elements and assemblies of engine modules and systems are completed. At least eight modules are assembled - from a low-pressure compressor to an all-mode adjustable jet nozzle. After assembly, the engine is tested according to a multi-cycle program. When performing the test stages, an alternation of modes is carried out, which in duration exceeds the programmed flight time. Typical flight cycles are formed, on the basis of which the program determines the damageability of the most loaded parts. Based on this, the required number of loading cycles during testing is determined. The full scope of tests is formed, including a quick change of cycles in the full register from a quick exit to the maximum or full forced mode to a complete engine shutdown and then a representative cycle of long-term operation with multiple alternation of modes over the entire operating spectrum with a different swing of the range of mode changes that does not exceed the flight time less than 5 times. A quick exit to the maximum or forced mode for a part of the test cycle is carried out at the rate of acceleration and reset. The technical result consists in increasing the reliability of test results at the stage of serial production and expanding the representativeness of the assessment of the resource and reliability of the gas turbine engine in a wide range of regional and seasonal conditions for the subsequent flight operation of the engines. 2 n. and 11 z.p. f-ly, 2 ill.

The invention relates to the field of aircraft engine building, namely to aircraft turbojet engines. Fine-tuning is subjected to an experimental turbojet engine, made double-circuit, two-shaft. Fine-tuning of the turbojet engine is carried out in stages. At each stage, one to five turbojet engines are tested for compliance with the specified parameters. The test program with subsequent refinement includes engine tests to determine the effect of climatic conditions on changes in the operational characteristics of an experimental turbojet engine. The tests are carried out with the measurement of engine operation parameters in various modes within the programmed range of flight modes for a specific series of engines and the resulting parameters are brought to standard atmospheric conditions, taking into account changes in the properties of the working fluid and the geometric characteristics of the engine flow path when atmospheric conditions change. The technical result consists in improving the operational characteristics of the turbojet engine, namely thrust, with an experimentally proven resource, and the reliability of the engine during operation in the full range of flight cycles in various climatic conditions, as well as in simplifying the technology and reducing labor costs and energy consumption of the process of testing the turbojet engine at the stage of fine-tuning the experimental TRD. 3 w.p. f-ly, 2 ill.

The invention relates to the field of mechanical engineering and is intended for testing turbines. Tests of steam and gas turbines of power and power propulsion plants on autonomous stands are an effective means of advancing the development of new technical solutions, which makes it possible to reduce the volume, cost and overall time of work on the creation of new power plants. The technical problem solved by the invention is the elimination of the need to remove the hydraulic brake used during testing of the working fluid; reduction in the frequency of routine maintenance with hydraulic brakes; creating the possibility of changing the characteristics of the tested turbine in a wide range during testing. The method is carried out using a stand containing a turbine under test with a working fluid supply system, a hydraulic brake with working fluid supply and discharge pipelines, in which, according to the invention, a container with a working fluid filling system is used, suction and discharge lines of a liquid loading pump with a system of sensors built into them, calibrated for power readings of the tested turbine, while a throttling device or a package of throttling devices is installed in the discharge line, and a liquid load pump is used as a hydraulic brake, the shaft of which is kinematically connected to the tested turbine, and the working fluid is supplied to the liquid load pump in a closed cycle with the possibility its partial discharge and supply to the circuit during testing. 2 n. and 4 z.p. f-ly, 1 ill.