CN113155014A - Circumferential pull rod rotor pull rod dynamic strain measurement system - Google Patents
Circumferential pull rod rotor pull rod dynamic strain measurement system Download PDFInfo
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- G01—MEASURING; TESTING
- G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
- G01B7/00—Measuring arrangements characterised by the use of electric or magnetic techniques
- G01B7/16—Measuring arrangements characterised by the use of electric or magnetic techniques for measuring the deformation in a solid, e.g. by resistance strain gauge
- G01B7/18—Measuring arrangements characterised by the use of electric or magnetic techniques for measuring the deformation in a solid, e.g. by resistance strain gauge using change in resistance
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Abstract
A dynamic strain measurement system for a pull rod of a circumferential pull rod rotor comprises a driving motor, an experimental rotor, a generator, a lubricating oil tank, a frequency converter, a pull rod dynamic strain acquisition system and a data acquisition and processing system. The experimental rotor comprises an experimental rotor turbine shaft section and an experimental rotor compressor shaft section, and the two shaft sections are connected through an intermediate coupler. The pull rod dynamic strain acquisition system comprises a strain gauge, a high-speed slip ring and a dynamic strain acquisition instrument; the strain gauge is installed on a turbine wheel disc pull rod, strain signals pass through a wire passing hole of a pull rod rotor wheel disc set and a wire passing hole of a flange disc to be connected with a slip ring rotor and a slip ring stator, then the slip ring signals are output to a dynamic strain acquisition instrument, and the strain acquisition instrument outputs the strain signals to a data acquisition and processing system. The invention can perform dynamic experiment of the whole rotor through the intermediate coupling, and can perform dynamic strain measurement of the pull rod, thereby solving the problem that the pull rod cannot lead out a signal wire after the pull rod is installed and pre-tightened on the pull rod rotor experiment table.
Description
Technical Field
The invention relates to the technical field of rotating machinery experiment systems, in particular to a dynamic strain measurement system for a pull rod of a circumferential pull rod rotor.
Background
In recent years, as the application of heavy-duty gas turbines is becoming widespread, the dynamic characteristics, operational safety, and reliability of the tie rod rotor, which is an important rotating machine, are important. However, the research on heavy gas turbines in China is not mature, and complete design theory and experimental data are lacked. Therefore, the experimental study on the dynamic characteristics of the pull rod rotor can provide important experimental reference for the design, manufacture and safety evaluation of the rotor.
At present, a corresponding pull rod rotor experiment system is available in China, and can be used for experimental research of static and dynamic characteristics, but the existing experiment system still has the following defects: firstly, the existing part of pull rod rotor experiment tables are static experiment tables, dynamic experiments cannot be carried out, and the difference between the structural form of the rotor and the actual rotor is large; secondly, the existing partial pull rod rotor dynamic experiment table can only carry out dynamic experiments of a compressor wheel disc or a turbine wheel disc independently, and cannot carry out an integral rotor experiment comprising the compressor wheel disc and the turbine wheel disc; third, the rotating speed of the current pull rod rotor dynamic experiment table can only reach the second-order critical rotating speed, and the third-order critical rotating speed cannot be experimentally measured under the laboratory condition.
A pull rod in the circumferential pull rod rotor system is one of key parts of a heavy-duty gas turbine, and is mainly used for providing pretightening force for a compressor wheel disc or a turbine wheel disc of the heavy-duty gas turbine and ensuring the stability and the reliability of the operation of the rotor system. After the pull rod is pre-tightened, the pull rod can bear large axial load and centrifugal force load generated by high-speed operation of the pull rod rotor, and in addition, the stress state of the pull rod can be changed due to long-term operation, so that the pull rod is loosened or bent and deformed. Therefore, the method has important significance for monitoring the deformation of the pull rod in the operation process. The tie rod is used as a key fastening structure in the tie rod rotor, and the dynamic strain characteristic of the tie rod during operation has important influence on the reliability and the service life of the whole operation of the rotor. Changes in the tension rod stress-strain state caused by long-term operation may affect the operation of the entire tension rod rotor. However, there is little mention of methods and means for dynamic strain monitoring of tie rods during operation.
At present, pull rod rotor experiment tables with different structural forms exist in China, strain electric signals acquired by strain gauges are output to a strain gauge acquisition system through signal wires by installing the strain gauges on a pull rod, and then the strain state of the pull rod after pre-tightening can be obtained. However, for the measurement of the strain of the pull rod, the current experiment table can only measure the strain of the pull rod under different pretightening forces in a static state, and cannot monitor the strain condition of the pull rod in real time in the rotation process of the pull rod rotor.
Disclosure of Invention
The invention aims to provide a system for dynamically measuring the strain of a pull rod of a circumferential pull rod rotor aiming at the problem that an integral rotor comprising a compressor wheel disk group and a turbine wheel disk group cannot monitor the strain condition of the pull rod in real time in the rotating process, so that the problem that the stability and reliability of the whole pull rod rotor can be influenced by the change of the stress-strain state of the pull rod caused by long-term operation, and the dynamic strain measurement of the pull rod rotor is realized.
The technical scheme of the invention is as follows:
the utility model provides a circumference pull rod rotor pull rod developments measurement system that meets an emergency, this system is including supporting base, driving motor, experiment rotor, generator, lubricating-oil tank, converter, foil gage and data acquisition and processing system, its characterized in that: the system also includes a dynamic strain acquisition instrument; the experimental rotor comprises an experimental rotor turbine shaft section and an experimental rotor compressor shaft section; the experimental rotor turbine shaft section is connected with the experimental rotor compressor shaft section through an intermediate coupler; after disassembly, the experimental rotor turbine shaft section or the experimental rotor compressor shaft section can be independently installed between the first rolling bearing and the second rolling bearing; the experimental rotor turbine shaft section comprises a turbine pull rod wheel disc set, a first turbine shaft and a second turbine shaft, and the turbine pull rod wheel disc set is installed and pre-tightened through a turbine wheel disc pull rod; the first turbine shaft is connected with the turbine pull rod wheel disc set through a first turbine shaft flange disc; the strain gauge is arranged on a pull rod of the turbine wheel disc; installing a high-speed slip ring on the first turbine shaft, wherein the ring consists of a slip ring rotor and a slip ring stator; the strain gauge is connected with the slip ring rotor through a strain gauge signal output line via a pull rod rotor wheel disc group wire through hole and a flange disc wire through hole, the slip ring stator is connected with the dynamic strain acquisition instrument through a high-speed slip ring signal output line, and the dynamic strain acquisition instrument outputs a strain signal to the data acquisition and processing system for data calculation, analysis and storage.
Preferably, the wire passing holes of the pull rod rotor wheel disc set and the wire passing holes of the flange disc are symmetrically arranged on the turbine pull rod wheel disc set and the flange disc of the first turbine shaft respectively, and the numbers of the wire passing holes and the flange disc of the pull rod rotor wheel disc set are the same. 6 fastening bolts are arranged on the first turbine shaft flange; the number of the pull rod rotor wheel disc group wire passing holes and the number of the flange plate wire passing holes are 2.
In the technical scheme, the experimental rotor compressor shaft section comprises a compressor wheel disc group without a pull rod, a compressor wheel disc group with a pull rod, a compressor wheel disc and a compressor shaft; the compressor wheel disc group without the pull rod, the compressor wheel disc group with the pull rod and the compressor wheel disc are arranged on the compressor shaft through the expansion sleeve. The compressor wheel disc comprises a first-stage compressor wheel disc and a second-stage compressor wheel disc; the compressor shafts include a first compressor shaft and a second compressor shaft; the compressor wheel set without the pull rod is arranged on the first compressor shaft through the expansion sleeve, and the compressor wheel set with the pull rod is pre-tightened through the compressor wheel plate pull rod; the first compressor shaft is connected with a compressor wheel disk set without a pull rod through a first compressor shaft flange plate; the second compressor shaft is connected with a compressor wheel disk set containing a pull rod through a second compressor shaft flange.
Further, the diameters of the gas compressor wheel disc in the experimental rotor gas compressor shaft section and the wheel disc in the turbine pull rod wheel disc group are respectively between 250 and 450mm, and the thicknesses are 10-30 mm; the compressor and turbine shafts are the same diameter and are in the range of 35-55 mm.
Further, the total length of the experimental rotor is 2.3-2.4m, the wheel discs of the compressors in the shaft section of the experimental rotor compressor are seventeen stages, four stages of the wheel discs of the compressors containing the pull rods are total, eleven stages of the wheel discs of the compressors without the pull rods are total, and two stages of the rest of the wheel discs of the compressors are total; the turbine pull rod wheel disc group in the experimental rotor turbine shaft section has four stages.
Further, the ratio of the diameter of the compressor and turbine shafts to the corresponding disk diameter is in the range of 1: 3-1: 10 is between; the ratio of the total mass of the experimental rotor to the mass of all individual discs was 50: 1-15: 1, and the third-order critical speed of the experimental rotor is controlled to be between 3000rpm and 5000 rpm. The ratio of the diameters of the compressor and turbine shafts to the corresponding diameters of the discs is in the range of 1: 3-1: 10 is between; the ratio of the total mass of the experimental rotor to the mass of all individual discs was 50: 1-15: 1, and the third-order critical speed of the experimental rotor is controlled to be between 3000rpm and 5000 rpm.
Furthermore, the data acquisition and processing system comprises a disc type torquemeter for acquiring torque signals in the running process of the rotor, a first horizontal direction acceleration sensor and a second horizontal direction acceleration sensor for respectively acquiring horizontal vibration acceleration signals of the turbine and the compressor, a first vertical direction acceleration sensor and a first vertical direction acceleration sensor for respectively adopting vertical vibration acceleration signals of the turbine and the compressor, a displacement sensor for acquiring vibration displacement signals of the rotor and a photoelectric encoder for acquiring real-time rotating speed signals; the signal collected by the sensor is input to the signal conditioner through a signal line, conditioned by the signal conditioner and output to the signal collection card, and finally the signal is calculated, analyzed, displayed and stored by a real-time display computer system comprising data collection software.
Compared with the prior art, the invention has the following advantages and prominent technical effects: firstly, the dynamic experiment of the whole rotor can be carried out through the intermediate coupling, and meanwhile, the component level experiment of the rotor can be carried out; by adjusting the pre-tightening force of the pull rod, the rotor dynamics characteristics under different contact states can be researched; the invention aims at simultaneously comprising a compressor shaft section wheel disc set and a turbine shaft section wheel disc set; the symmetrical wire passing holes are formed in the pull rod rotor wheel disc set and the pull rod rotor shaft flange, so that the defect that the dynamic strain measurement of the pull rod rotor is implemented due to the fact that a signal wire cannot be led out after the pull rod is installed and pre-tightened in a traditional pull rod rotor experiment table is overcome; the flange plate with the fastening bolt and the wire passing hole is convenient to mount, can be popularized to other pull rod rotor structures, and has good use convenience and universality.
In a word, the invention well solves the problem of dynamic strain measurement of the pull rod rotor, can quickly and effectively measure the real-time strain of the pull rod rotor, and has important engineering application value.
Drawings
Fig. 1 is a schematic view of the overall structure of a circumferential pull rod rotor experiment system and a pull rod dynamic strain measurement system.
Fig. 2 is a structural diagram of a dynamic strain measurement system of the pull rod.
FIG. 3 is a schematic three-dimensional view of a turbine disk.
FIG. 4 is a sectional view of the experimental rotor compressor shaft section configuration.
FIG. 5 is a sectional view of the experimental rotor shaft section configuration.
In the figure: 1-a circumferential pull rod rotor experimental system; 2-driving the motor; 3-a flange plate; 4-disc torquemeter; 5-a first resilient coupling; 6-a first horizontal direction acceleration sensor; 7-experimental rotor turbine shaft section; 8-a turbine shaft; 8 a-a first turbine shaft; 8 b-a second turbine shaft; 9-a displacement sensor; 10-testing the shaft section of the rotor compressor; 11-compressor shaft; 11 a-a first compressor shaft; 11 b-a second compressor shaft; 12-a second horizontal direction acceleration sensor; 13-a photoelectric encoder; 14-a second resilient coupling; 15-a generator; 16-a support base; 17-a first rolling bearing; 18-a first vertical direction acceleration sensor; 19-intermediate coupling; 20-lubricating oil pipe; 21-frequency converter control line; 22-a second vertical direction acceleration sensor; 23-a second rolling bearing; 24-a lubricating oil tank; 25-a frequency converter; 26-sensor signal line; 27-a signal conditioner; 28-signal acquisition card; 29-a data acquisition and processing system; 30-compressor disk set without tie rod; 31-a first compressor shaft flange; 32-a compressor wheel disc pull rod; 33-a compressor pulley set with a pull rod; 34-a second compressor shaft flange; 35-a second stage compressor wheel disc; 36-a first stage compressor disk; 37-a first turbine shaft flange; 38-turbine wheel disc tie rod; 39-turbine disk set; 40-a second turbine shaft flange. 41-high speed slip ring signal output line; 42-high speed slip ring stator; 43-high speed slip ring rotor; 44-strain gage signal output lines; 45-pull rod rotor wheel disc group wire passing holes; 46-a strain gauge; 47-dynamic strain acquisition instrument; 48-flange plate wire through holes; 49-fastening bolts.
Detailed Description
The overall structure, the working principle and the working process of the circumferential pull rod rotor experiment table and the pull rod dynamic strain measurement system are described in detail with reference to the accompanying drawings.
Fig. 1 is a schematic view of the overall structure of a circumferential pull rod rotor experiment table and a pull rod dynamic strain measurement system 1, which mainly comprises a support base 16, a driving motor 2, an experiment rotor, a generator 15, a lubricating oil tank 24, a frequency converter 25, a data acquisition and processing system and a pull rod dynamic strain measurement system. The experimental rotor comprises an experimental rotor turbine shaft section 7 and an experimental rotor compressor shaft section 10; one end of the experimental rotor turbine shaft section is connected with an output shaft of the driving motor 2 through a first rolling bearing 17 and a first elastic coupling 5 in sequence; one end of the experimental rotor compressor shaft section 10 is connected with the generator 15 through a second rolling bearing 23 and a second elastic coupling 14; the other ends of the experimental rotor turbine shaft section 7 and the experimental rotor compressor shaft section 10 are connected through an intermediate coupling 19 to form an integral rotor detachable structure; after disassembly, the test rotor turbine shaft section 7 or the test rotor compressor shaft section 10 can be mounted separately between the first rolling bearing 17 and the second rolling bearing 23.
According to the circumferential pull rod rotor experiment table, the driving motor 2 is controlled in rotating speed through the frequency converter 25, the driving motor 2 can provide constant rotating speed for an experiment rotor, the driving motor 2 is connected with the disc type torquemeter 4 through the flange plate 3, and the disc type torquemeter 4 can measure the torque in real time in the rotor operation process. The disc type torque meter 4 is connected with an experimental rotor turbine shaft section 7 through a first elastic coupling 5; the experimental rotor turbine shaft section 7 is connected with the compressor shaft section wheel disc group 10 through an intermediate coupling 19, and the intermediate coupling 19 is detachable, so that the turbine shaft section wheel disc group 7 and the experimental rotor compressor shaft section 10 can respectively perform independent static or dynamic experiments. The experimental rotor compressor shaft section 10 is connected to a generator 15 via a second flexible coupling 14. The generator 15 is used to provide load torque. The first rolling bearing 17 and the second rolling bearing 23 are used to support the integrated rotor composed of the experimental rotor turbine shaft section 7 and the experimental rotor compressor shaft section 10. The support base 16 provides support for the whole circumferential pull rod rotor experiment system, a T-shaped groove is formed in the support base, and the bases of the driving motor 2 and the engine 15 are installed in the T-shaped groove. The first horizontal direction acceleration sensor 6 and the first vertical direction acceleration sensor 18 are mounted on a bearing seat of the first rolling bearing 17, and are used for measuring vibration acceleration signals generated on the first rolling bearing. The second horizontal direction acceleration sensor 12 and the second vertical direction acceleration sensor 22 are mounted on a bearing seat of the second rolling bearing 23, and are used for measuring vibration acceleration signals generated on the first rolling bearing. A displacement sensor 9 is mounted near the turbine shaft 8 for measuring a displacement signal. The photoelectric encoder 13 is mounted between the second rolling bearing 23 and the second elastic coupling 14. The inverter control line 21 is used for transmitting an inverter control signal to control the driving motor 2 to output a constant rotation speed and to control the generator 15 to output a constant torque. The lubricating oil pipe 20 supplies lubricating oil to the first rolling bearing 17 and the second rolling bearing 23 through the lubricating oil tank 24 to lubricate the two bearings.
The sensor signal line 26 in the signal acquisition and data analysis system acquires the electrical signals output by the first horizontal acceleration sensor 6, the first vertical acceleration sensor 18, the second horizontal acceleration sensor 12, the second vertical acceleration sensor 22, the displacement sensor 9 and the photoelectric encoder 13, outputs the electrical signals to the signal conditioner 27, conditions the electrical signals acquired by the sensors by the signal conditioner and outputs the conditioned electrical signals to the signal acquisition card 28, the signal acquisition card 28 outputs the electrical signals to the data acquisition and processing system 29 including data acquisition software and real-time display, and the sensor signals are calculated, analyzed, displayed and stored by the computer system.
Fig. 2 and fig. 3 are a structural diagram of a dynamic strain measurement system of a tie rod and a three-dimensional structural diagram of a turbine wheel disk, respectively. The pull rod dynamic strain acquisition system comprises an experimental rotor turbine shaft section 7, a strain gauge 46, a high-speed slip ring and a dynamic strain acquisition instrument 47; the high-speed slip ring consists of a slip ring rotor 43 and a slip ring stator 42; the strain gauge 46 is mounted on the turbine disk tie rod 38; and the high-speed slip ring stator 42 and the high-speed slip ring rotor 43 are arranged on the experimental rotor turbine shaft section 7 and used for acquiring dynamic strain signals. The experimental rotor turbine shaft section 7 comprises a turbine drag link wheel disk group 39, a first turbine shaft 8a and a second turbine shaft 8 b; the high-speed slip ring is arranged on a first turbine shaft 8a, the first turbine shaft 8a is connected with the experimental rotor turbine shaft section 7 through a first turbine shaft flange 37, a fastening bolt 49 is arranged on the first turbine shaft 8a and is provided with a flange through hole 48, and a second turbine shaft 8b is connected with the experimental rotor turbine shaft section 7 through a second turbine shaft flange 40.
The experimental rotor turbine shaft section 7 is provided with a pull rod rotor disk group wire passing hole 45, a strain electric signal collected by a strain gauge 46 is output to the high-speed slip ring rotor 43 through a strain gauge signal output line 44, the strain gauge signal output line 44 can pass through the pull rod rotor disk group wire passing hole 45 and a flange plate wire passing hole 48, and then the strain electric signal of the high-speed slip ring rotor 43 is led out to the high-speed slip ring signal output line 41 through the high-speed slip ring stator 42. In the running process of the rotor system, the strain gauge 46, the strain gauge signal output line 44 and the high-speed slip ring rotor 43 can rotate together with the experiment table, so that the real-time output of the dynamic strain signal of the pull rod rotor is realized.
The strain gauge is connected with a slip ring rotor 43 through a strain gauge signal output line 44 via a pull rod rotor wheel disc group wire through hole 45 and a flange disc wire through hole 48, a slip ring stator 42 is connected with a dynamic strain acquisition instrument 47 through a high-speed slip ring signal output line 41, and the dynamic strain acquisition instrument outputs a strain signal to a data acquisition and processing system 29 for data calculation, analysis and storage.
The pull rod rotor wheel disc group wire passing holes and the flange plate wire passing holes are respectively and uniformly arranged on the turbine pull rod wheel disc group and the first turbine shaft flange plate, and the quantity of the pull rod rotor wheel disc group wire passing holes and the quantity of the flange plate wire passing holes are the same. The first turbine shaft flange plate is preferably provided with 6 fastening bolts 49; the number of the pull rod rotor wheel set wire through holes 45 and the flange plate wire through holes 48 is preferably 2.
Fig. 4 is a schematic structural diagram of an experimental rotor compressor shaft section 10, which includes a compressor wheel disc set 30 without a tie rod, a compressor wheel disc set 33 with a tie rod, other compressor wheel discs, and a compressor shaft 11; the compressor wheel set 30 without the tie rod, the compressor wheel set 33 with the tie rod and the two-stage compressor wheel are mounted on the compressor shaft through the expansion sleeves. The compressor wheel disc comprises a first-stage compressor wheel disc 36 and a second-stage compressor wheel disc 35; the compressor shaft 11 includes a first compressor shaft 11a and a second compressor shaft 11 b; the compressor disk set 30 without the tie rod is mounted on the first compressor shaft 11a through an expansion sleeve, and the compressor disk set 33 with the tie rod is pre-tightened through a compressor disk tie rod 32; the first compressor shaft 11a is connected to a compressor disk set 30 without tie rods via a first compressor shaft flange 31; the second compressor shaft 11b is connected with a compressor pulley set 33 containing a pull rod through a second compressor shaft flange 34; a first-stage compressor disk 36 and a second-stage compressor disk 35 are mounted on the second compressor shaft 11b via an expansion sleeve.
FIG. 5 is a schematic illustration of the construction of the experimental rotor shaft section. The experimental rotor turbine shaft section 7 comprises a turbine wheel disc group 39 and a turbine shaft 8, the turbine shaft comprises a first turbine shaft 8a and a second turbine shaft 8b, and the turbine wheel disc group 39 is installed and pre-tightened through a turbine wheel disc pull rod 38; the first turbine shaft 8a is connected to a turbine tie rod disk set 39 via a first turbine shaft flange 37, and the second turbine shaft 8b is connected to the turbine tie rod disk set 39 via a second turbine shaft flange 40.
The total length of the experimental rotor is 2.3-2.4m, the number of compressor wheel discs in an experimental rotor compressor shaft section 10 is seventeen, the number of compressor wheel discs containing pull rods is four, the number of compressor wheel disc groups without pull rods is eleven, the number of other compressor wheel discs (a second-stage compressor wheel disc 35 and a first-stage compressor wheel disc 36 are two, the number of turbine pull rod wheel disc groups in an experimental rotor turbine shaft section 7 is four, the diameters of the compressor wheel discs and the wheel discs in the experimental rotor compressor shaft section 10 are respectively 250-450mm, the thicknesses of the compressor wheel discs and the turbine wheel disc groups are 10-30mm, the diameters of the compressor shaft 11 and the turbine shaft 8 are the same and within the range of 35-55mm, the ratio of the diameters of the compressor shaft 11 and the turbine shaft 8 to the corresponding wheel disc diameters is 1: 3-1: 10, the ratio of the overall mass of the experimental rotor to the mass of all the single wheel discs is 50: 1-15: 1, and the third-order critical rotating speed of the experimental rotor is controlled to be between 3000rpm and 5000 rpm.
The working process of the whole circumferential pull rod rotor pull rod dynamic strain measurement system is as follows: the frequency converter 25 controls the driving motor 2 to output a constant rotating speed, drives the integral rotor composed of the turbine shaft segment pulley disc group 7 and the compressor shaft segment pulley disc group 10 to rotate at the constant rotating speed, and drives the generator 15 to generate electricity. In the operation process, the strain gauge 46 is installed on the turbine disk pull rod 38, the strain electric signal is output to the high-speed slip ring rotor 43 through the strain gauge signal output line 44, the strain electric signal output by the high-speed slip ring rotor 43 is acquired by the high-speed slip ring stator 42, then the electric signal is output to the dynamic strain acquisition instrument 47 through the high-speed slip ring signal output line 41, the dynamic strain acquisition instrument 47 outputs the conditioned signal to the data acquisition and processing system 29, and the data acquisition and processing system 29 performs real-time calculation, analysis and storage on the strain electric signal.
Claims (10)
1. The utility model provides a circumference pull rod rotor pull rod dynamic strain measurement system, this system is including supporting base (16), driving motor (2), experiment rotor, generator (15), lubricating-oil tank (24), converter (25) and data acquisition and processing system (29), its characterized in that: the system also comprises a pull rod dynamic strain acquisition system; the experimental rotor comprises an experimental rotor turbine shaft section (7) and an experimental rotor compressor shaft section (10); the experimental rotor turbine shaft section (7) is connected with the experimental rotor compressor shaft section (10) through an intermediate coupler (19); after disassembly, the experimental rotor turbine shaft section (7) or the experimental rotor compressor shaft section (10) can be independently installed between the first rolling bearing (17) and the second rolling bearing (23); the experimental rotor turbine shaft section (7) comprises a turbine wheel disc set (39), a first turbine shaft (8a) and a second turbine shaft (8b), and the turbine wheel disc set (39) is installed and pre-tightened through a turbine wheel disc pull rod (38); the first turbine shaft (8a) is connected with a turbine pull rod wheel disc set (39) through a first turbine shaft flange plate (37);
the pull rod dynamic strain acquisition system comprises a strain gauge (46), a high-speed slip ring and a dynamic strain acquisition instrument (47); the strain gauge (46) is arranged on a turbine wheel disc pull rod (38); mounting a high-speed slip ring on the first turbine shaft (8a), the ring consisting of a slip ring rotor (43) and a slip ring stator (42); the strain gauge is connected with a slip ring rotor (43) through a strain gauge signal output line (44) via a pull rod rotor wheel disc group wire passing hole (45) and a flange disc wire passing hole (48), a slip ring stator (42) is connected with a dynamic strain acquisition instrument (47) through a high-speed slip ring signal output line (41), and the dynamic strain acquisition instrument outputs a strain signal to a data acquisition and processing system (29) for data calculation, analysis and storage.
2. The system for measuring the dynamic strain of the circumferential tension rod rotor tension rod according to claim 1, wherein the tension rod rotor wheel disc group wire through hole (45) and the flange plate wire through hole (48) are respectively and uniformly arranged on the turbine tension rod wheel disc group (39) and the first turbine shaft flange plate (37) and are the same in number.
3. The system for measuring the dynamic strain of the tension rod of the circumferential tension rod rotor according to claim 2, wherein 6 fastening bolts (49) are arranged on the flange plate of the first turbine shaft; the number of the pull rod rotor wheel disc group wire passing holes (45) and the number of the flange disc wire passing holes (48) are 2.
4. A circumferential tie rotor tie dynamic strain measurement system as claimed in claim 1, 2 or 3, wherein: the experimental rotor compressor shaft section (10) comprises a compressor wheel disc set (30) without a pull rod, a compressor wheel disc set (33) with a pull rod, a compressor wheel disc and a compressor shaft (11); the compressor wheel disc set (30) without the pull rod, the compressor wheel disc set (33) with the pull rod and the compressor wheel disc are arranged on the compressor shaft through the expansion sleeve.
5. The circumferential tie rod rotor tie rod dynamic strain measurement system of claim 4, wherein: the compressor wheel disc comprises a first-stage compressor wheel disc (36) and a second-stage compressor wheel disc (35); the compressor shaft (11) comprises a first compressor shaft (11a) and a second compressor shaft (11 b); the compressor wheel disc set (30) without the pull rod is arranged on the first compressor shaft (11a) through an expansion sleeve, and the compressor wheel disc set (33) with the pull rod is pre-tightened through a compressor wheel disc pull rod (32); the first compressor shaft (11a) is connected with a compressor wheel disk set (30) without a pull rod through a first compressor shaft flange (31); the second compressor shaft (11b) is connected to a compressor disk set (33) comprising a tie rod via a second compressor shaft flange (34).
6. The system for measuring the dynamic strain of the pull rod of the circumferential pull rod rotor as claimed in claim 1, wherein the diameters of the gas compressor wheel disc in the experimental rotor gas compressor shaft section (10) and the wheel disc in the turbine pull rod wheel disc group (39) are respectively between 250 mm and 450mm, and the thicknesses are respectively 10-30 mm; the compressor shaft (11) and the turbine shaft (8) have the same diameter and are in the range of 35-55 mm.
7. The system for measuring the dynamic strain of the tie rod of the circumferential tie rod rotor as recited in claim 1, wherein the total length of the experimental rotor is 2.3-2.4m, and the total length of the wheel discs of the compressor in the compressor section (10) of the experimental rotor is seventeen stages, wherein the number of the wheel discs of the compressor containing the tie rod is four stages, the number of the wheel discs of the compressor without the tie rod is eleven stages, and the number of the wheel discs of the rest compressor is two stages; the turbine pull rod wheel disc group in the experimental rotor turbine shaft section (7) has four stages in total.
8. The circumferential tie rod rotor tie rod dynamic strain measurement system of claim 1, wherein: the ratio of the diameter of the compressor shaft (11) and the turbine shaft (8) to the corresponding diameter of the wheel disc is 1: 3-1: 10 is between; the ratio of the total mass of the experimental rotor to the mass of all individual discs was 50: 1-15: 1, and the third-order critical speed of the experimental rotor is controlled to be between 3000rpm and 5000 rpm.
9. The circumferential tie rod rotor tie rod dynamic strain measurement system of claim 1, wherein: the ratio of the diameter of the compressor shaft (11) and the turbine shaft (8) to the corresponding diameter of the wheel disc is 1: 3-1: 10 is between; the ratio of the total mass of the experimental rotor to the mass of all individual discs was 50: 1-15: 1, and the third-order critical speed of the experimental rotor is controlled to be between 3000rpm and 5000 rpm.
10. The circumferential tie rod rotor tie rod dynamic strain measurement system of claim 1, wherein: the data acquisition and processing system comprises a disc type torquemeter (4) for acquiring torque signals in the running process of a rotor, a first horizontal direction acceleration sensor (6) and a second horizontal direction acceleration sensor (12) for respectively acquiring horizontal vibration acceleration signals of a turbine and a gas compressor, a first vertical direction acceleration sensor (18) and a first vertical direction acceleration sensor (22) for respectively adopting vertical vibration acceleration signals of the turbine and the gas compressor, a displacement sensor (9) for acquiring vibration displacement signals of the rotor and a photoelectric encoder (13) for acquiring real-time rotating speed signals; the signal collected by the sensor is input to a signal conditioner (27) through a signal line (26), is conditioned by the signal conditioner and then is output to a signal acquisition card (28), and finally is calculated, analyzed, displayed and stored by a computer system (29) comprising data acquisition software and real-time display.
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| CN202110274627.6A CN113155014A (en) | 2021-03-15 | 2021-03-15 | Circumferential pull rod rotor pull rod dynamic strain measurement system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113720606A (en) * | 2021-08-30 | 2021-11-30 | 湖南工程学院 | Tool for designing shafting of direct-drive permanent magnet wind turbine generator and design method |
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| CN113720606A (en) * | 2021-08-30 | 2021-11-30 | 湖南工程学院 | Tool for designing shafting of direct-drive permanent magnet wind turbine generator and design method |
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