CN201697772U - Experimental system for damping dynamic response of shrouded blades - Google Patents
Experimental system for damping dynamic response of shrouded blades Download PDFInfo
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- CN201697772U CN201697772U CN201020241286XU CN201020241286U CN201697772U CN 201697772 U CN201697772 U CN 201697772U CN 201020241286X U CN201020241286X U CN 201020241286XU CN 201020241286 U CN201020241286 U CN 201020241286U CN 201697772 U CN201697772 U CN 201697772U
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Abstract
The utility model discloses an experimental system for damping dynamic response of shrouded blades, comprising an experiment table, a signal exciting unit and a signal testing unit, wherein the experiment table comprises a base, a loading device fixed on the base and a clamp for clamping more than two shrouded blades; the loading device comprises a shroud for loading; the shroud for loading is parallel to a shroud at the top of the shrouded blades and is in contact during loading; the signal exciting unit is connected with one shrouded blade and applies the exciting force on the shrouded blade; and the signal testing unit is connected with other shrouded blades which are not excited. The utility model has the advantages of simple structure, low cost, wide application range and high testing accuracy; in addition, the utility model can be used for testing the dynamic response of collision vibration as well as frictional vibration of the shrouded blades at the same time.
Description
Technical field
The utility model relates to the mechanical vibration field of test instrument, relates in particular to a kind of experimental system of calibration tape shroud blade vibration performance.
Background technology
Blade in the turbomachinery is the key component that realizes energy conversion, blade also can be subjected to the effect of periodicity exciting force and produce vibratory response and dynamic stress, thereby cause the vibrating fatigue of blade to be damaged, show according to related data, the blade vibration fault accounts for more than 30% of power machine fault, therefore, reduce the blade resonance dynamic stress, the safe reliability that improves blade just seems important further.Because the aerodynamic characteristic and the damping behavior of shrouded blade all obviously are better than lacing wire and convex shoulder blade, at present, adopt band hat structure blade to become development trend.
The damping mechanism of band hat damping structure mainly contains two kinds of frictional damping vibration damping and collisional damping vibration dampings: when carrying out the frictional damping vibration damping, the blade twist restitution produces the contact normal pressure in integral shroud surface of contact mutual extrusion, and the integral shroud surface of contact consumed energy that slides mutually reaches the purpose of vibration damping; When carrying out the collisional damping vibration damping, there is certain interval (i.e. gap between the hat) between integral shroud and integral shroud, relies on the mode consumed energy of collision between hat to reach the vibration damping purpose.Because the nonlinear characteristic of collision or fricting movement between integral shroud and the integral shroud, this is just very complicated to add vibration characteristics that shrouded blade produces under the effect of steam flow excitation power, makes theoretical at present and numerical method be difficult to accurately predict the vibratory response and the damping vibration attenuation effect of shrouded blade; And it is consuming time too many to carry out finite element analogy emulation, and needs to simplify in to the analytical parameter setup of solid model and iterative process and handle, and is subject to the influence of computer capacity and counting yield, is difficult to relate to steady-state vibration usually.Therefore, the experimental study that carries out shrouded blade damping vibration attenuation becomes the ten minutes important means of inquiring into shrouded blade damping vibration attenuation mechanism, and the damping structure optimal design that can be shrouded blade provides crucial guidance.
From the lot of documents of having delivered, the characteristic of the dry-friction damping of people's shrouded blade has had more deep understanding and understanding, in the modeling of surface of contact friction force and be subjected to have obtained bigger progress aspect the response analysis of frictional constraint blade.At present, less to the research of shrouded blade friction damping experiment, the experimental study of this respect yet is only limited to the discussion of the fricting movement rule between two blades; And still do not set up a kind of contact-impact model that effectively relatively meets actual demands of engineering.Simultaneously, the contrast of the effectiveness in vibration suppression of these two kinds of damping vibration attenuation modes is not also carried out as yet.Which kind of vibration damping mode of blade to(for) concrete what length should adopt just can obtain best effectiveness in vibration suppression, and the optimal design of how to carry out the shrouded blade damping, still lacks mature theory and instructs.
The utility model content
Technical problem to be solved in the utility model just is: at the technical matters that prior art exists, the utility model provide a kind of simple in structure, with low cost, applied widely, measuring accuracy is high, can be used for carrying out the experimental system of the shrouded blade damping vibration attenuation dynamic response of shrouded blade crash shock and the test of frictional vibration dynamic response simultaneously.
For solving the problems of the technologies described above, the utility model by the following technical solutions:
A kind of experimental system of shrouded blade damping vibration attenuation dynamic response, it is characterized in that: comprise experiment table, signal excitation unit and signal testing unit, described experiment table comprises base and is fixed in the charger on the base and is used for the anchor clamps of two above shrouded blades of clamping, described charger comprises loading uses integral shroud, described loading is and when loading contact parallel with the integral shroud at shrouded blade top with integral shroud, described signal excitation unit links to each other with a shrouded blade and this shrouded blade is applied exciting force, and described signal testing unit is not linked to each other by the shrouded blade of exciting with all the other.
As further improvement of the utility model:
Described loading is fixed in a ring-type with integral shroud and is loaded on the disk, described ring-type loads disk and is fixed on the support by stand, described support be fixed on the base and on the support length direction along shrouded blade offer oblong aperture, described stand is sheathed in the oblong aperture.
Offer the positioning hole that is used to regulate described shrouded blade length on the described base.
Be provided with thick roll adjustment piece between the described adjacent shrouded blade, be provided with thin roll adjustment piece between described shrouded blade and the anchor clamps.
Described signal excitation unit comprises signal generator, power amplifier and vibrator, the output terminal of described signal generator links to each other with the input end of described power amplifier, the output terminal of described power amplifier links to each other with described vibrator, and described vibrator links to each other with shrouded blade.
The monitor port of described power amplifier is provided with oscillograph.
Described signal testing unit comprises sensor, signal analyzer and computing machine, described sensor with do not linked to each other by the shrouded blade of exciting, the output terminal of described sensor links to each other with described signal analyzer, described signal analyzer links to each other with described computing machine.
Described shrouded blade is uniform cross section prismatic blade, uniform cross section twisted blade, variable cross section prismatic blade or variable cross section twisted blade, and the integral shroud of described shrouded blade is parallelogram integral shroud or Z type integral shroud.
Compared with prior art, advantage of the present utility model is:
1, the experimental system of shrouded blade damping vibration attenuation dynamic response of the present utility model, simple in structure, with low cost, can carry out the experiment of collisional damping vibration damping and the experiment of frictional damping vibration damping of shrouded blade simultaneously, analyze the influence rule of dependency structure parameter to damping vibration attenuation, the experimental result of gained and analysis are to improving or set up shrouded blade damped vibration (friction or collision) kinetic model, instructing the optimal design of shrouded blade damping structure to have very important using value.
2, the experimental system of shrouded blade damping vibration attenuation dynamic response of the present utility model to have the gap between the adjacent integral shroud of the loose type integral shroud of collisional quenching, can change gap between hat by the thickness that changes roll adjustment piece between anchor clamps; At friction damping is main close-fitting type integral shroud, during work under centrifugal action shrouded blade produce twist recovery power, adjacent integral shroud surface of contact is compressed mutually produces the contact normal pressure; And come to apply needed contact normal pressure to the integral shroud surface of contact by loading disk, can realize test under gap, different initial normal pressure, different integral shroud contact angle and different exciting forces between different band shroud blade length, different integral shroud form, different integral shroud contact angle, different hat, the tangent bending vibration dynamic response when shrouded blade bumps vibration or frictional vibration; Data obtain the amplitude frequency curve of shrouded blade vibration by experiment then, and then analyze the influence rule of these system structure parameters to collisional quenching or friction damping effect, and the damping property of shrouded blade is estimated.
3, the experimental system of shrouded blade damping vibration attenuation dynamic response of the present utility model, apply initial normal pressure by the signal excitation unit to the shrouded blade that is subjected to exciting, and the vibration performance by signal testing unit testing and analytic band shroud blade, have the high advantage of measuring accuracy.
4, the experimental system of shrouded blade damping vibration attenuation dynamic response of the present utility model goes for the shrouded blade and the integral shroud thereof of various structures, various models, and its scope of application is very wide.
Description of drawings
Fig. 1 is the framed structure synoptic diagram of the utility model embodiment;
Fig. 2 is the perspective view of the utility model embodiment experimental system;
Fig. 3 is the plan structure synoptic diagram of experiment table among the utility model embodiment;
Fig. 4 is the transformational relation synoptic diagram of pressure-loaded mode and normal pressure among the utility model embodiment;
Fig. 5 is that shrouded blade is the amplitude-frequency response synoptic diagram the during gap between 6.25N, different hat at exciting force among the utility model embodiment;
Fig. 6 is that shrouded blade gap between hat of the utility model embodiment is acceleration time domain waveform and the power spectrum synoptic diagram under 0.5mm, the different excitation force frequency;
Wherein: (a) for the shrouded blade of the utility model embodiment gap between hat is 0.5mm, acceleration time domain waveform synoptic diagram when excitation force frequency is 30Hz;
(b) for the shrouded blade of the utility model embodiment gap between hat is 0.5mm, power spectrum synoptic diagram when excitation force frequency is 30Hz;
(c) for the shrouded blade of the utility model embodiment gap between hat is 0.5mm, acceleration time domain waveform synoptic diagram when excitation force frequency is 36.87Hz;
(d) for the shrouded blade of the utility model embodiment gap between hat is 0.5mm, power spectrum synoptic diagram when excitation force frequency is 36.87Hz;
(e) for the shrouded blade of the utility model embodiment gap between hat is 0.5mm, acceleration time domain waveform synoptic diagram when excitation force frequency is 40Hz;
(f) for the shrouded blade of the utility model embodiment gap between hat is 0.5mm, power spectrum synoptic diagram when excitation force frequency is 40Hz;
Fig. 7 is that the shrouded blade of the utility model embodiment is at the initial normal pressure of the difference amplitude-frequency response synoptic diagram in following time.
Marginal data:
1, experiment table; 101, base; 102, support; 1021, stand; 103, anchor clamps; 104, positioning hole; 105, shrouded blade; 1051, loading integral shroud; 106, oblong aperture; 21, thick roll adjustment piece; 22, thin roll adjustment piece; 3, load disk; 4, signal generator; 5, power amplifier; 6, oscillograph; 7, vibrator; 8, sensor; 9, signal analyzer; 10, computing machine.
Embodiment
Below with reference to Figure of description and specific embodiment the utility model is described in further details.
As Fig. 1, shown in Figure 2, the experimental system of shrouded blade damping vibration attenuation dynamic response of the present utility model, comprise experiment table 1, signal excitation unit and signal testing unit, experiment table 1 comprises base 101 and is fixed in the charger on the base 101 and is used for the anchor clamps 103 of two above shrouded blades 105 of clamping, charger comprises loading uses integral shroud 1051, load and when loading contact parallel with the integral shroud at shrouded blade 105 tops with integral shroud 1051, the signal excitation unit links to each other with a shrouded blade 105 and this shrouded blade 105 is applied exciting force, and the signal testing unit is not linked to each other by the shrouded blade 105 of exciting with all the other.
In the present embodiment, load with integral shroud 1051 and be fixed on the ring-type loading disk 3, ring-type loads disk 3 and is fixed on the support 102 by stand 1021, support 102 be fixed on the base 101 and on the support 102 length direction along shrouded blade 105 offer oblong aperture 106, stand 1021 is sheathed in the oblong aperture 106; Can be by charger loading thereon with applying required initial normal pressure on integral shroud 1051 surface of contact, thus realize the frictional vibration dynamic response of shrouded blade 105 under the different initial normal pressure conditions of test.
Offer the positioning hole 104 that is used for accommodation zone shroud blade 105 length on the base 101.Can go deep into the length of the depth adjustment shrouded blade 105 in the positioning hole 104 by shrouded blade 105, thereby realize the crash shock dynamic response of the shrouded blade 105 of test different length.
Be provided with thick roll adjustment piece 21 between the adjacent shrouded blade 105, be provided with thin roll adjustment piece 22 between shrouded blade 105 and the anchor clamps 103.Carrying out crash shock when experiment, can promptly be preced with a gap by the gap that the thin roll adjustment piece 22 of changing different-thickness is adjusted between the integral shrouds, thereby realize calibration tape shroud blade 105 crash shock dynamic response the during gap between the difference hat.
The signal excitation unit comprises signal generator 4, power amplifier 5 and vibrator 7, the output terminal of signal generator 4 links to each other with the input end of power amplifier 5, the output terminal of power amplifier 5 links to each other with vibrator 7, and vibrator 7 is fixed on the shrouded blade 105 by push rod.Conditioning signal generator 4 scalable frequency sizes, power amplifier 5 is regulated the exciting force sizes makes shrouded blade 105 that the power of vibration take place, and can realize that calibration tape shroud blade 105 is at different exciting force sizes, frictional vibration dynamic response under different excitation force frequencies.
The signal testing unit comprises sensor 8, signal analyzer 9 and computing machine 10, sensor 8 with do not linked to each other by the shrouded blade 105 of exciting, the output terminal of sensor 8 links to each other with signal analyzer 9, signal analyzer 9 links to each other with computing machine 10.Can obtain experimental data by sensor 8, thereby analyze the amplitude frequency curve that obtains shrouded blade 105 vibrations by signal analyzer 9 and computing machine 10, analyze the influence rule of different parameters, finally the damping property of shrouded blade 105 is estimated collisional quenching or friction damping effect.
The monitor port of power amplifier 5 is provided with oscillograph 6.During test, can obtain corresponding exciting force size by the voltage signal conversion of reading on the oscillograph 6.
Shrouded blade 105 is uniform cross section prismatic blade, uniform cross section twisted blade, variable cross section prismatic blade or variable cross section twisted blade, and the integral shroud of shrouded blade 105 is parallelogram integral shroud or Z type integral shroud.By changing multi-form integral shroud and integral shroud, can test the shrouded blade 105 crash shock dynamic response and the frictional vibration dynamic response under various conditions of different integral shroud forms, different integral shroud contact angles with contact angle (angle of surface of contact and flexural vibrations direction) between different hats.
Adopt the experimental system of the shrouded blade 105 damping vibration attenuation dynamic responses of present embodiment, the shrouded blade 105 to 30 ° of integral shrouds of contact angle between long 400mm, band Z type hat carries out crash shock experiment and frictional vibration experiment respectively.
1, crash shock experiment
(1) mounting strap shroud blade: as shown in Figure 3, at first choose three z type integral shrouds with contact angle between 30 ° of hats, and respectively two integral shrouds are fastened on 2 long 400mm plate blade tops, an integral shroud is installed on the loading disk 3 of experiment table 1 as loading with integral shroud 1051; Then shrouded blade 105 is packed in the positioning hole 104, and keep its integral shroud and load with integral shroud 1051 end faces on same surface level.Add gap between thick roll adjustment piece 21 (thick iron block) and thin roll adjustment piece 22 (thin iron block) adjusting hat at two shrouded blades, 105 roots, shrouded blade 105 roots are fastened on the base 101 of experiment table 1 with anchor clamps 103 then, go out gap width between concrete hat between integral shroud with vernier caliper measurement.
(2) connected system: when experiment, earlier that the push rod of vibrator 7 is fixing with nut and shrouded blade 105, sensor 8 usefulness double faced adhesive tapes are fixed on shrouded blade 105 tops (need guarantee that all sensor 8 is attached to same position when at every turn testing), then by the experimental system that connects shown in Figure 1.In this experiment, signal generator 4 adopts YB1602 type function signal generator 4, produces required harmonic signal; Power amplifier 5 adopts GF-20W power amplifier 5, output to JZ-2 type electromagnetic exciter 7 after receiving harmonic signal, its monitoring interface is received YB43020BF type oscillograph 6, and sensor 8 adopts the PV-901 acceleration transducer, and signal analyzer 9 adopts the SA-78FFT analyser.
(3) response test: guarantee that by adjusting signal generator 4 signal intensities and power amplifier 5 gain buttons exciting force is certain value in the test frequency scope, the voltage signal of reading on the oscillograph 6 this moment can obtain corresponding exciting force size (because the exciting force size of power on the power amplifier 5 and vibrator 7 is linear, therefore can obtain the exciting force size by the conversion of the voltage signal on the power amplifier 5); Under this exciting force effect, regulate the frequency output of the frequency control exciting force of signal generator 4 then.Steady-state response for the research crash shock, to each excited frequency, at (counting on the FFT signal analyzer 9) after 200 vibration periods, on the time-domain diagram of signal analyzer 9, read its vibration amplitude, the main frequency and the amplitude thereof of reader crash shock signal content on FFT amplitude-frequency spectrum.The data of the vibration signal on the signal analyzer 9 are saved on the data-storing card, can read and analyze at computing machine 10 enterprising line data.
By top test, analyze and to obtain long 400mm, contact angle is 30 ° a z type shrouded blade 105 between hat, the exciting force size for the 6.25N effect under, the amplitude-frequency response (amplitude-frequency response curve) between difference is preced with during the gap is as shown in Figure 5; Acceleration time domain waveform under the different excitation force frequencies when gap is 0.5mm between hat and power spectrum chart are shown in (a)～(f) among Fig. 6.
Change the length of shrouded blade 105, change the integral shroud of contact angle between different hats, repeat above-mentioned steps, can be under different exciting force effects to shrouded blade 105 crash shocks response test.
2, frictional vibration experiment
(1) mounting strap shroud blade: at first choose three z type integral shrouds, and two integral shrouds are fastened on 2 long 400mm plate blade tops respectively, an integral shroud is installed on the loading disk 3 of experiment table 1 as loading with integral shroud 1051 with contact angle between 30 ° of hats; To load parallel and be in contact with one another then with surface of contact furnishing between the hat on integral shroud 1051 and the shrouded blade 105, install thick roll adjustment piece 21 (thick iron block) and thin roll adjustment piece 22 (thin iron block) additional at 105 of two shrouded blades and 103 of anchor clamps again, with anchor clamps 103 shrouded blade 105 roots are fastened on experiment table 1 base 101 then.
(2) connected system: the step of step syn-collision vibration damping experiment is identical.
(3) apply contact surface positive pressure: as shown in Figure 4, at first converse the amount of force F that needs apply according to surface of contact position between contact surface positive pressure, F force position and the hat of contact angle degree, needs between hat by formula on loading disc, conversion relational expression is:
Wherein, F is the acting force that is applied on the loading disc, and N is the acting force on the surface of contact between hat, and α touches feeler indirectly for hat, if F and N are respectively L and lcos α to the arm of force that reverses that shroud and loading disc system produce, determine different initial normal pressures after recording correlation parameter according to following formula.(it should be noted that, the actual normal pressure that is added on the integral shroud surface of contact should deduct the friction force that loads on disk 3 and the support 102, but for this experiment table 1, the surface of contact that will load the stand 1021 on disk 3 and the support 102 with gauze during experiment polishes smooth as far as possible, reducing friction as far as possible and making its variation is not very greatly, thereby ignores its effect analytic band shroud blade 105 vibration characteristics are not had too much influence).Hang weight or directly apply the acting force that size is the conversion result at the bolt that loads disk 3 then, will load disk 3 after stable and be fixed on the support 102 etc. force value with tautness meter, constant with the initial normal pressure of surface of contact in the assurance test process.
(4) response test: step is identical with the step of collisional quenching experiment.
By top test, analysis obtains as shown in Figure 7, long 400mm, and contact angle is 30 ° a z type shrouded blade 105 between hat, the amplitude-frequency response when exciting force is 6.25N, different initially normal pressure.Change the length of shrouded blade 105, change the integral shroud of contact angle between different hats, repeat above-mentioned steps, can be under different exciting force effects to shrouded blade 105 frictional vibrations response test.
By above-mentioned interpretation as can be known:
(1) when 105 of shrouded blades comes in contact collision, because hat is touched the non-linear effects that hits indirectly, the spectrum component of excitation force frequency has appearred being different from shrouded blade 105 vibratory responses, and variation along with excitation force frequency, frequency multiplication, frequency division have appearred, and along with the increase of excitation force frequency even the chaos phenomenon of multifrequency frequency band occurred, has the typical nonlinear feature.
(2) exist the amplitude of shrouded blade 105 of contact-impact damping more much smaller than the amplitude of single blade, peak swing can be reduced to about original 0.35 times, contact-impact between illustrating between shrouded blade 105 hats has good damping vibration attenuation effect, exists gap between an only hat (or interval) and makes the collisional quenching effect reach best.
(3) exist shrouded blade 105 peak swings of contact friction damping can be reduced to about 0.4 times of single blade, contact friction between illustrating between shrouded blade 105 hats has good damping vibration attenuation effect, simultaneously, along with initial normal pressure increases, shrouded blade 105 crest frequencies begin to be offset to the right, the frictional damping vibration damping has good fm role, exists best initial normal pressure, makes dry-friction damping reach maximum to the consumption of shrouded blade 105 vibrational energies.
These experimental results have proved that shrouded blade damping vibration attenuation experimental system of the present utility model can be used for studying and solving the contact-impact vibration damping of shrouded blade 105 and the problem of friction damping.It can also be used for the education experiment of mechanical vibration aspect.
Below only be preferred implementation of the present utility model, protection domain of the present utility model also not only is confined to the foregoing description, and all technical schemes that belongs under the utility model thinking all belong to protection domain of the present utility model.Should be pointed out that for those skilled in the art the some improvements and modifications not breaking away under the utility model principle prerequisite should be considered as protection domain of the present utility model.
Claims (8)
1. the experimental system of a shrouded blade damping vibration attenuation dynamic response, it is characterized in that: comprise experiment table (1), signal excitation unit and signal testing unit, described experiment table (1) comprises base (101) and is fixed in the charger on the base (101) and is used for the anchor clamps (103) of two above shrouded blades of clamping (105), described charger comprises loading uses integral shroud (1051), described loading is and when loading contact parallel with the integral shroud at shrouded blade (105) top with integral shroud (1051), described signal excitation unit links to each other with a shrouded blade (105) and this shrouded blade (105) is applied exciting force, and described signal testing unit is not linked to each other by the shrouded blade of exciting (105) with all the other.
2. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 1, it is characterized in that: described loading is fixed in a ring-type with integral shroud (1051) and is loaded on the disk (3), described ring-type loads disk (3) and is fixed on the support (102) by stand (1021), described support (102) is fixed on the base (101) and support (102) upward offers oblong aperture (106) along the length direction of shrouded blade (105), and described stand (1021) is sheathed in the oblong aperture (106).
3. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 1 and 2 is characterized in that: offer the positioning hole (104) that is used to regulate described shrouded blade (105) length on the described base (101).
4. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 1 and 2, it is characterized in that: be provided with thick roll adjustment piece (21) between the described adjacent shrouded blade (105), be provided with thin roll adjustment piece (22) between described shrouded blade (105) and the anchor clamps (103).
5. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 1 and 2, it is characterized in that: described signal excitation unit comprises signal generator (4), power amplifier (5) and vibrator (7), the output terminal of described signal generator (4) links to each other with the input end of described power amplifier (5), the output terminal of described power amplifier (5) links to each other with described vibrator (7), and described vibrator (7) links to each other with shrouded blade (105).
6. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 5 is characterized in that: the monitor port of described power amplifier (5) is provided with oscillograph (6).
7. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 1 and 2, it is characterized in that: described signal testing unit comprises sensor (8), signal analyzer (9) and computing machine (10), described sensor (8) with do not linked to each other by the shrouded blade of exciting (105), the output terminal of described sensor (8) links to each other with described signal analyzer (9), and described signal analyzer (9) links to each other with described computing machine (10).
8. the experimental system of shrouded blade damping vibration attenuation dynamic response according to claim 1 and 2, it is characterized in that: described shrouded blade (105) is uniform cross section prismatic blade or uniform cross section twisted blade or variable cross section prismatic blade or variable cross section twisted blade, and the integral shroud of described shrouded blade (105) is parallelogram integral shroud or Z type integral shroud.
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