CN112179610A - Eddy current damper for segment model test, vibration device and experimental method - Google Patents
Eddy current damper for segment model test, vibration device and experimental method Download PDFInfo
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- CN112179610A CN112179610A CN202011197185.1A CN202011197185A CN112179610A CN 112179610 A CN112179610 A CN 112179610A CN 202011197185 A CN202011197185 A CN 202011197185A CN 112179610 A CN112179610 A CN 112179610A
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Abstract
The invention relates to the technical field of pneumatic tests, and particularly discloses an eddy current damper for testing a segment model, wherein the linear eddy current damper is arranged at two ends of the segment model and is arranged diagonally, and comprises a rigid insulating rod, a metal sheet and two permanent magnets; the lower end of the rigid insulating rod is connected with the metal sheet, and the upper end of the rigid insulating rod is connected with the suspension arm; the two permanent magnets are placed under the metal sheet, and the two permanent magnets keep a distance to form a magnetic field. The invention also discloses a vibration device which comprises the segment model, springs, two suspension arms and a linear eddy current damper, wherein the suspension arms are fixedly connected to two ends of the segment model and are symmetrically arranged, the springs are connected to two ends of each suspension arm and above and below the suspension arms, and the other ends of the springs are fixedly arranged in the pneumatic laboratory; the upper end of the rigid insulating rod is detachably connected with the suspension arm, so that the problem that the existing vibrating device has errors is solved. An experimental method based on the vibration device is also disclosed, and data support and great convenience are provided for testers.
Description
Technical Field
The invention relates to the technical field of pneumatic tests, in particular to an eddy current damper, a vibration device and an experimental method for testing a segment model.
Background
After the vortex vibration phenomenon occurs to the autogiro bridge, the vortex vibration problem of the bridge structure draws wide attention. In the field of bridge wind engineering at present, the vortex vibration performance of a structure is often researched by performing a wind tunnel experiment. A spring suspension section model coupling vibration test is derived, and is a main method for obtaining a large number of civil structure wind-induced vibration responses (flutter, vortex, galloping, buffeting and the like) and pneumatic parameter identification, wherein the civil structures comprise flexible structures such as a bridge girder, a suspender, a guy cable, a power transmission line and a mast.
The spring suspension section model vibration system provides a vertical bending-torsion coupled linear vibrator, linear elastic stiffness is provided through a tensioned spring, a certain structural damping ratio is applied to simulate the damping characteristic of an actual structure, and sometimes the size of the structural damping ratio is changed, so that the influence rule of the actually applied damper on the wind-induced vibration response of the civil structure is investigated. During testing, it is best that the structural damping characteristics remain linear. The traditional device for applying structural damping in wind tunnel experiments comprises: a steel wire ring damping ring is added on a spring, a TMD damper is applied on a suspension arm, and the like, and the traditional experimental method has the following problems: (1) structural damping varies significantly with model amplitude; (2) the static wind deformation of the model under different wind speeds often influences the structural damping; (3) it is difficult to adjust the vertical and torsional damping independently. The above-mentioned drawbacks of the conventional method may cause significant errors in the wind tunnel test results. Therefore, it is necessary to provide a new damping ratio device to provide linear structural damping.
Disclosure of Invention
An object of the present invention is to provide a linear eddy current damper and a vibration device including the same, which solve the problem of error in the conventional vibration device.
The invention also aims to provide an experimental method based on the vibration device, which provides data support and great convenience for testers.
The invention is realized by the following technical scheme:
the linear eddy current dampers are arranged at two ends of the segment model and are arranged diagonally, and each linear eddy current damper comprises a rigid insulating rod, a metal sheet and two permanent magnets;
the lower end of the rigid insulating rod is connected with the metal sheet, and the upper end of the rigid insulating rod is connected with the suspension arm;
two permanent magnets are placed under the metal sheet, the two permanent magnets keep the distance, and the N level of one permanent magnet layer is opposite to the S level of the other permanent magnet layer to form a magnetic field.
Furthermore, a fixed box is arranged right below the metal sheet, and the two permanent magnets are fixed on the front panel and the rear panel of the fixed box.
Further, the metal sheet is detachably connected with the rigid insulating rod.
Furthermore, the metal sheet is made of copper or aluminum.
Furthermore, the metal sheet is round and has the thickness of 1 mm-3 mm.
The invention discloses a vibration device for testing a segmental model, which comprises the segmental model, springs, two suspension arms and a linear eddy current damper, wherein the suspension arms are fixedly connected to two ends of the segmental model and are symmetrically arranged; the upper end of the rigid insulating rod is connected with a connecting plate which is detachably connected with the suspension arm.
The invention also discloses an experimental method based on the vibration device, which specifically comprises the following steps:
in the process of vertical/torsional vibration of the wind-induced segment model, the suspension arm drives the metal sheet to move in a magnetic field formed by the two permanent magnets, magnetic induction lines are cut, eddy current is formed in the metal sheet, the magnetic field between the permanent magnets generates damping force on the eddy current, and the eddy current damping coefficient is calculated according to the damping force.
Further, in the vertical vibration process of the wind-induced segment model, the suspension arm moves upwards along with the segment model, the suspension arm drives the rigid insulating rod and the metal sheet to move upwards, the vertical damping force applied to the metal sheet by the magnetic field calculates a vertical damping coefficient and a vertical damping ratio according to the vertical damping force, and the calculation formula is as follows:
wherein B is the magnetic field intensity, d and r are the thickness and radius of the metal sheet, respectively, ρ is the resistivity of the metal sheet, and Ce,yIs a vertical damping coefficient, ξe,yIs the vertical damping ratio, me,yFor the vertical equivalent mass, omega, of the segmental modelyThe circular frequency of vertical vibration of the segmental model.
Further, in the process of torsional vibration of the wind-induced segment model, the suspension arm twists along with the segment model, the suspension arm drives the rigid insulating rod and the metal sheet to twist, the torsional damping force applied to the metal sheet by the magnetic field is calculated according to the torsional damping force, and the calculation formula is as follows:
in the formula I1The distance of the rigid insulating rod from the center of the suspension arm is l2Is the distance between the center of the metal sheet and the center line of the suspension arm, Ce,αIs the torsional damping coefficient, xie,αTo obtain a torsional damping ratio, Je,αIs the equivalent moment of inertia of the segment model system; omegaαThe circular frequency of torsional vibration of the segmental model.
Further, when the magnetic field formed by the two permanent magnets is not uniform or has magnetic leakage, the magnetic field intensity B is obtained by inverse calculation through actually measuring the damping ratio, and the specific steps are as follows:
s1, mounting the lower end of the rigid insulating rod with the radius r0A thickness d0Resistivity is rho0The metal sheet of (1);
s2, vertically exciting the segment model at zero wind speed, and collecting free vibration attenuation response time course y (t)i)；
S3 response time course y (t) from vertical free attenuationi) To obtain a peak point QiFrom the peak point Q of the responseiTo obtain0：
Wherein N is the number of response peak points;
s4 logarithmic decrement0Calculating vertical damping ratio xi0：
S5, removing the linear eddy current damper from the suspension arm, and calculating the damping ratio without the linear eddy current damper
S6 structural damping ratio caused by the linear eddy current damper
Obtaining the magnetic field strength B as follows:
compared with the prior art, the invention has the following beneficial technical effects:
the invention discloses a linear eddy current damper and a vibration device comprising the same, wherein the linear eddy current damper is arranged at two ends of a segment model and is arranged diagonally so as to enable damping characteristics to be uniformly distributed; the two permanent magnets are fixedly arranged right below the metal sheet to form a magnetic field. In the process of vertical/torsional vibration of the wind-induced segment model, the suspension arm drives the metal sheet to move between magnetic fields formed by the two permanent magnets, the magnetic induction lines are cut, eddy current is formed in the metal sheet, the magnetic fields between the permanent magnets generate damping force on the eddy current, and the damping coefficient and the damping ratio can be calculated through the damping force. According to the knowledge of electromagnetism, the eddy current damping coefficient is only related to the parameters such as the geometric dimension and the resistance characteristic of the metal sheet, the magnetic field intensity of the permanent magnet and the like, is not related to the vertical bending/torsion amplitude of the segmental model and the static balance position, and can avoid the problem that the damping coefficient of the traditional damping device is obviously changed along with the amplitude and the static wind deformation of the model; the geometric dimension of the metal sheet is adjusted, the distance between the front panel and the rear panel of the fixed box is fixed, and the size of the vertical bending and torsional damping coefficient is adjusted. Therefore, the device can effectively realize the application of the damping ratio of the linear structure in the wind tunnel vibration test process of the segment model, the damping characteristic is not influenced by large-amplitude vibration and static wind deformation of the model, and the precision of the wind tunnel experiment test is obviously improved. The device has simple structure, convenient operation of damping adjustment and good economical efficiency.
Furthermore, a fixed box is arranged under the metal sheet, and the two permanent magnets are fixed on the front panel and the rear panel of the fixed box, so that the position can be conveniently moved as long as the fixed box is moved.
Furthermore, the metal sheet and the rigid insulating rod are detachably connected, preferably fixed by a fine bolt, and the metal sheet is convenient to replace.
Furthermore, the upper end of the rigid insulating rod is fixed with the suspension arm through the connecting plate, the rigid insulating rod is thin, the contact area of the connection part of the rigid insulating rod and the suspension arm is small, and the connection is more stable after the connecting plate is added.
The invention also discloses an experimental simulation method based on the spring suspension section model vibration device, a formula of a damping coefficient and a damping ratio can be calculated and deduced through experimental simulation, subsequent simulation is facilitated, and the formula can show that the radius r and the eccentric distance l of a metal sheet are changed1And l2And the magnetic field intensity B can adjust the vertical damping and the torsional damping, thereby providing data support and great convenience for testers.
Drawings
Fig. 1 is a schematic view of the overall arrangement of a spring suspension segment model vibration device of the present invention;
FIG. 2 is a schematic structural diagram of a linear eddy current damper according to the present invention;
FIG. 3 is a simulation diagram of an experimental state of the segmental model of the invention during vertical vibration;
FIG. 4 is a simulation of the experimental conditions of the segmental model of the invention during torsional vibration;
FIG. 5 is a graph showing vertical damping ratio as a function of amplitude without and with linear eddy current dampers applied;
FIG. 6 is a graph showing vertical damping ratio as a function of amplitude without and with linear eddy current dampers applied.
Wherein, 1 is the rigidity insulator spindle, 2 is the sheetmetal, 3 is the permanent magnet, 4 is the fixed case, 5 is the connecting plate, 6 is the davit, 7 is the segmental model, 8 is the spring.
Detailed Description
The present invention will now be described in further detail with reference to specific examples, which are intended to be illustrative, but not limiting, of the invention.
As shown in FIG. 2, the invention discloses a linear eddy current damper, which comprises a rigid insulating rod 1, a metal sheet 2 and two permanent magnets 3; the lower end of the rigid insulating rod 1 is connected with the metal sheet 2; two permanent magnets 3 are fixedly placed under the metal sheet 2, the two permanent magnets 3 keep the distance, and the N level of one permanent magnet 3 layer is opposite to the S level of the other permanent magnet 3 layer to form an approximately uniform magnetic field.
More preferably, a fixing box 4 is arranged right below the metal sheet 2, and the two permanent magnets 3 are fixed on the front and rear panels of the fixing box 4, so that the position can be conveniently moved as long as the fixing box 4 is moved.
Preferably, the metal sheet 2 is detachably connected with the rigid insulating rod 1, and is preferably fixed by a fine bolt, so that the metal sheet 2 is convenient to replace.
As shown in fig. 1, the invention discloses a spring suspension segmental model vibration device for segmental model wind tunnel testing, which comprises a segmental model 7, springs 8, two suspension arms 6 and a linear eddy current damper, wherein the suspension arms 6 are fixedly connected to two ends of the segmental model 7 and are symmetrically arranged, the springs 8 are respectively connected to two ends of the suspension arms 6 and above and below the two ends, and the other ends of the springs 8 are fixedly arranged in a wind-driven laboratory; the linear eddy current dampers are disposed at both ends of the segment model 7 and are diagonally arranged so that the damping characteristics are uniformly distributed.
Preferably, the upper end of the rigid insulating rod 1 is fixed with the suspension arm 6 through the connecting plate 5, the rigid insulating rod 1 is thin, the contact area of the connection part of the rigid insulating rod 1 and the suspension arm 6 is small, and the connection is more stable after the connecting plate 5 is added. The connecting plate 5 and the suspension arm 6 can be detachably connected, and can be adhered or connected through bolts, so that the installation and the disassembly are convenient.
In the process of vertical/torsional vibration of the wind-induced segment model 7, the suspension arm 6 drives the metal sheet 2 to move between magnetic fields formed by the two permanent magnets 3, magnetic induction lines are cut, eddy current is formed in the metal sheet 2, and the magnetic fields between the permanent magnets 3 generate damping force on the eddy current. The magnitude of the eddy current damping coefficient can be calculated by an electromagnetic theory, and the specific steps are as follows:
according to the vertical motion shown in fig. 3, the vertical (y-direction) damping force can be expressed as:
in the formula, FyVertical damping force is applied to the metal sheet 2 by a magnetic field formed by the permanent magnet 3 when the model moves vertically; b is the magnetic field intensity; vyThe moving speed of the metal sheet 2 in the y direction; d and r are the thickness of the metal damping sheet respectivelyDegree and radius; ρ is the resistivity of the metal sheet 2.
The vertical eddy current damping coefficient is:
in the formula, Ce,yIs a vertical damping coefficient, ξe,yIs the vertical damping ratio, me,yIs the vertical equivalent mass of the segment model 7; omegayThe circular frequency of the vertical vibration of the segment model 7.
According to the torsional movement shown in fig. 4, the torsional damping force can be expressed as:
in the formula, MαA damping force F exerted on the metal sheet 2 by the magnetic field formed by the permanent magnet 3 when the model is in torsional motionαThe torque generated; vαIs the speed of movement at the centre of the metal sheet 2; l1The distance of the rigid insulating rod 1 from the center of the suspension arm 6 is l2The distance of the centre of the metal sheet 2 from the centre line of the boom 6,
is the torsional angular velocity.
The torque generated by the eddy current damping force is:
the eddy current damping coefficient of the torsional vibration can be calculated by the following formula:
in the formula, Ce,αIs the torsional damping coefficient, xie,αTo obtain a torsional damping ratio, Je,αEquivalent moment of inertia for the segment model 7 system; omegaαThe circular frequency of torsional vibration of the segment model 7.
Considering that there may be some non-uniformity in the magnetic field between the two permanent magnets 3 and there may also be leakage flux in the magnetic circuit, the magnetic field strength B in equations (2) and (5) can be obtained by inverse calculation through the actual damping ratio in order to take the above factors into consideration. The method comprises the following specific steps:
(1) mounting radius r0A thickness d0Resistivity is rho0The metal sheet 2.
(2) Under zero wind speed, the segment model 7 is vertically excited, and the free vibration attenuation response time course y (t) is collectedi)。
(3) Free decay of the response time course y (t) from the verticali) To obtain a peak point QiAnd the logarithmic decrement can be obtained from the response peak point:
wherein, N is the number of the response peak points.
(4) Logarithmic decrement0The vertical damping ratio xi can be obtained0：
(5) Removing the eddy current damper from the suspension arm 6, and adopting the steps (2) to (4) to identify the damping ratio without the damper
(6) The structural damping ratio caused by the eddy current damper is
The magnetic field strength B obtained by substituting the above-mentioned magnetic field strength into the equations (2) to (3) is:
from the equations (2) and (5), it can be understood that by changing the radius r of the metal piece 2, the eccentric distance l1And l2Vertical and torsional damping can be adjusted.
FIGS. 5 and 6 show that in a wind tunnel experiment of a bridge girder segment model, no eddy current damper is applied (i.e. "no damper" in the figure), an eddy current damper is applied, and two metal sheets 2 with different radiuses are adopted (i.e. "eddy current damper is applied" in the figure, radius R of metal sheet 2 is R)1"and" applying an eddy current damper, radius R of the metal sheet 22"), the vertical damping ratio and the torsional damping ratio are regular with the amplitude. It can be found that when the eddy current damper is not applied, the vertical damping ratio and the torsional damping ratio of the spring suspension section model vibration system are changed along with the amplitude due to the friction at the joint of the spring 8 and the interference of the ambient air, but after the linear eddy current damper is applied on the basis, the vertical damping ratio and the torsional damping ratio are translated upwards by a constant on the basis of the original damping curve, so that the proposed linear eddy current damper can be kept as a constant in a large amplitude range of the model, namely, the ideal linear damping assumption is met.
Claims (10)
1. The eddy current damper for testing the segment model is characterized in that the linear eddy current damper is arranged at two ends of the segment model (7) and is arranged diagonally, and the linear eddy current damper comprises a rigid insulating rod (1), a metal sheet (2) and two permanent magnets (3);
the lower end of the rigid insulating rod (1) is connected with the metal sheet (2), and the upper end of the rigid insulating rod is connected with the suspension arm (6);
two permanent magnets (3) are placed under the metal sheet (2), the two permanent magnets (3) keep a distance, and the N level of one permanent magnet (3) layer is opposite to the S level of the other permanent magnet (3) layer to form a magnetic field.
2. The eddy current damper for segment model testing according to claim 1, wherein a fixing box (4) is provided directly below the metal sheet (2), and the two permanent magnets (3) are fixed on the front and rear panels of the fixing box (4).
3. An eddy current damper for segment model testing according to claim 1, characterized in that the metal sheet (2) is detachably connected with the rigid insulating rod (1).
4. The eddy current damper for segment model testing according to claim 1, characterized in that the metal sheet (2) is made of copper or aluminum.
5. The eddy current damper for segment model testing as claimed in claim 1, wherein the metal sheet (2) is circular and has a thickness of 1mm to 3 mm.
6. A vibration device for testing a segmental model is characterized by comprising the segmental model (7), springs (8), two suspension arms (6) and the linear eddy current damper as claimed in any one of claims 1 to 5, wherein the suspension arms (6) are fixedly connected to two ends of the segmental model (7) and are symmetrically arranged, the springs (8) are respectively connected to two ends of each suspension arm (6) and above and below the suspension arm, and the other ends of the springs (8) are fixedly arranged in a pneumatic laboratory;
the upper end of the rigid insulating rod (1) is connected with a connecting plate (5), and the connecting plate (5) is detachably connected with the suspension arm (6).
7. The experimental method of the vibration device according to claim 6, specifically comprising:
in the process of vertical/torsional vibration of the wind-induced segment model (7), the suspension arm (6) drives the metal sheet (2) to move in a magnetic field formed by the two permanent magnets (3), magnetic induction lines are cut, eddy current is formed in the metal sheet (2), the magnetic field between the permanent magnets (3) generates damping force on the eddy current, and the eddy current damping coefficient is calculated according to the damping force.
8. The experimental method of claim 7, wherein during the vertical vibration of the wind-induced segment model (7), the suspension arm (6) moves upwards along with the phase model, the suspension arm (6) drives the rigid insulating rod (1) and the metal sheet (2) to move upwards, the vertical damping force applied to the metal sheet (2) by the magnetic field is calculated according to the vertical damping force to obtain a vertical damping coefficient and a vertical damping ratio, and the calculation formula is as follows:
wherein B is the magnetic field intensity, d and r are the thickness and radius of the metal sheet (2), respectively, ρ is the resistivity of the metal sheet (2), Ce,yIs a vertical damping coefficient, ξe,yIs the vertical damping ratio, me,yIs the equivalent mass, omega, of the segment model (7) in the vertical directionyIs the circular frequency of the vertical vibration of the segmental model (7).
9. The experimental method of claim 7, wherein during the torsional vibration of the wind-induced segment model (7), the suspension arm (6) is twisted along with the phase model, the suspension arm (6) drives the rigid insulating rod (1) and the metal sheet (2) to twist, the torsional damping force applied to the metal sheet (2) by the magnetic field is calculated according to the torsional damping force to obtain a torsional damping coefficient and a torsional damping ratio, and the calculation formula is as follows:
in the formula I1The distance of the rigid insulating rod (1) deviating from the center of the suspension arm (6) |2Is the distance between the center of the metal sheet (2) and the center line of the suspension arm (6), Ce,αIs the torsional damping coefficient, xie,αTo obtain a torsional damping ratio, Je,αIs the equivalent moment of inertia of the segment model (7) system; omegaαIs the circular frequency of the torsional vibration of the segment model (7).
10. The experimental method according to claim 7, characterized in that when the magnetic field formed by the two permanent magnets (3) is not uniform or leaks, the magnetic field strength B is obtained by inverse calculation through actually measuring the damping ratio, and the specific steps are as follows:
s1, installing the lower end of the rigid insulating rod (1) with the radius r0A thickness d0Resistivity is rho0The metal sheet (2);
s2, vertically exciting the segment model (7) at zero wind speed, and collecting the free vibration attenuation response time course y (t)i)；
S3 response time course y (t) from vertical free attenuationi) To obtain a peak point QiFrom the peak point Q of the responseiTo obtain0：
Wherein N is the number of response peak points;
s4 logarithmic decrement0Calculating vertical damping ratio xi0：
S5, removing the linear eddy current damper from the suspension arm (6), and calculating the damping ratio without the linear eddy current damper
S6 structural damping ratio caused by the linear eddy current damper
Obtaining the magnetic field strength B as follows:
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112853927A (en) * | 2021-01-12 | 2021-05-28 | 大连理工大学 | Heave plate-spring combined control device for inhibiting flutter of marine long-span bridge |
| CN112945514A (en) * | 2021-01-29 | 2021-06-11 | 同济大学 | Bridge segment model wind tunnel test suspension system based on magnetic suspension principle |
| CN113063561A (en) * | 2021-03-29 | 2021-07-02 | 长安大学 | Support testing device in wind tunnel for ensuring binary flow characteristics of segment model |
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- 2020-10-30 CN CN202011197185.1A patent/CN112179610A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112853927A (en) * | 2021-01-12 | 2021-05-28 | 大连理工大学 | Heave plate-spring combined control device for inhibiting flutter of marine long-span bridge |
| CN112945514A (en) * | 2021-01-29 | 2021-06-11 | 同济大学 | Bridge segment model wind tunnel test suspension system based on magnetic suspension principle |
| CN112945514B (en) * | 2021-01-29 | 2022-06-24 | 同济大学 | Bridge segment model wind tunnel test suspension system based on magnetic suspension principle |
| CN113063561A (en) * | 2021-03-29 | 2021-07-02 | 长安大学 | Support testing device in wind tunnel for ensuring binary flow characteristics of segment model |
| CN113063561B (en) * | 2021-03-29 | 2023-08-29 | 长安大学 | Wind tunnel inner support testing device for guaranteeing binary flow characteristics of segment model |
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