Traction torsional motion vane device for controlling wind-induced vibration and bridge box girder

Abstract

This invention discloses a traction-torsional motion airfoil device for controlling wind-induced vibration, comprising: two airfoils, respectively located on both sides of the main beam in the transverse direction and both capable of rotating relative to the main beam; a traction-torsional motion mechanism, including: a displacement amplification mechanism disposed on one side of the main beam in the longitudinal direction, comprising a fixed center gear and two amplification gears meshing with the fixed center gear; two main beam displacement transmission racks, respectively meshing with the two amplification gears; two phase difference conversion mechanisms, respectively connected to the two main beam displacement transmission racks; two airfoil displacement transmission racks, each phase difference conversion mechanism cooperating with the corresponding airfoil displacement transmission rack via a steering gear; and two airfoil gears, each airfoil gear fixed on one side of the airfoil in the longitudinal direction and meshing with the corresponding airfoil displacement transmission rack. This invention adjusts the attitude according to the torsion of the main beam, and achieves optimal control effect through a set phase difference, without requiring external energy input.

Description

Technical Field

[0001] This invention relates to the field of bridge technology, and in particular to a traction torsional motion wing plate device for controlling wind-induced vibration and a bridge box girder. Background Technology

[0002] Active aerodynamic vanes are an effective measure for controlling wind-induced vibration and static stability in long-span bridges. Compared to passive aerodynamic measures, active vane-type measures can adjust the spatial attitude and operating state of the device in real time according to the specific form of bridge wind-induced vibration, achieving bridge wind-induced vibration control in a more proactive manner. They have the ability to break through the control limits of traditional passive aerodynamic measures and also have the potential to dynamically change the control mode to automatically adapt to special wind climates. However, compared to passive aerodynamic measures, active aerodynamic vanes often require external energy input. When long-span bridges are affected by extreme wind environments such as typhoons, they often face risks such as energy supply obstruction. Therefore, the control stability of active aerodynamic vanes is insufficient, and the risk is relatively high. When aerodynamic vanes are connected to the main beam in a general mechanical way, this shortcoming can be compensated for. However, they can only perform feedback motion with the same frequency and phase as the main beam vibration. Existing research shows that there is a certain phase difference between the optimal aerodynamic vane feedback motion and the torsional motion of the main beam. Same-frequency and same-phase control cannot effectively improve the wind vibration performance of the main beam-vane system. Summary of the Invention

[0003] To address the shortcomings of existing technologies, the present invention aims to provide a traction torsional motion wing plate device and a bridge box girder for controlling wind-induced vibrations.

[0004] To achieve the above objectives, an embodiment of the present invention provides the following technical solution:

[0005] A device for controlling wind-induced vibrations via a torsional airfoil includes:

[0006] Two flanges are located on both sides of the main girder in the transverse direction and are both capable of rotating relative to the main girder;

[0007] The torsion motion mechanism includes:

[0008] A displacement amplification mechanism is disposed on one side of the main beam in the longitudinal direction. The displacement amplification mechanism includes a fixed center gear and two amplification gears that mesh with the fixed center gear.

[0009] Both main beam displacement transmission racks extend horizontally, and the two main beam displacement transmission racks mesh with the two amplifying gears respectively;

[0010] Two phase difference conversion mechanisms are provided, and the two phase difference conversion mechanisms are respectively connected to the two main beam displacement transmission racks;

[0011] Both wing plate displacement transmission racks extend horizontally, and each phase difference conversion mechanism is engaged with the corresponding wing plate displacement transmission rack via a steering gear;

[0012] Two wing gears, each of which is fixed to one side of the longitudinal bridge of the wing and meshes with the corresponding wing displacement transmission rack.

[0013] As a further improvement of the present invention, the amplifying gear includes a first amplifying gear and a second amplifying gear meshing with the first amplifying gear. The first amplifying gear meshes with the fixed center gear, and the second amplifying gear meshes with the main beam displacement transmission rack.

[0014] As a further improvement of the present invention, the number of teeth of the fixed center gear is twice the number of teeth of the first amplifying gear, and the number of teeth of the first amplifying gear is twice the number of teeth of the second amplifying gear.

[0015] As a further improvement of the present invention, the fixed center gear, the first amplifying gear, and the second amplifying gear are all involute gears.

[0016] As a further improvement of the present invention, the phase difference conversion mechanism includes a vertical rod, a rocker arm, a horizontal rod, and a phase difference output rack. The vertical rod is connected to the main beam displacement transmission rack. One end of the rocker arm is connected to the vertical rod and the horizontal rod respectively. The other end of the rocker arm can rotate relative to the main beam. The horizontal rod is connected to the phase difference output rack.

[0017] As a further improvement of the present invention, a vertical elongated hole is provided in the vertical rod, a horizontal elongated hole is provided in the horizontal rod, and a first support shaft is provided at one end of the rocker arm, with the two ends of the first support shaft respectively inserted into the vertical elongated hole and the horizontal elongated hole.

[0018] As a further improvement of the present invention, a bearing rod is provided on one side of the longitudinal bridge direction of the main beam, and a second support shaft is provided at the other end of the rocker arm, the second support shaft being connected to the bearing rod.

[0019] As a further improvement of the present invention, the wing plate displacement transmission rack includes a wing plate displacement transmission rod, a first transmission rack and a second transmission rack respectively connected to both ends of the wing plate displacement transmission rod, wherein the first transmission rack meshes with the steering gear and the second transmission rack meshes with the wing plate gear.

[0020] As a further improvement of the present invention, two guide blocks are provided on one side of the longitudinal bridge direction of the main beam, and each of the flange displacement transmission rods moves along the corresponding guide block.

[0021] A bridge box girder includes the aforementioned traction torsional motion wing plate device for controlling wind-induced vibration.

[0022] The beneficial effects of this invention are:

[0023] (1) In this invention, the torsional displacement of the main beam is connected to the wing plate through a displacement amplification mechanism and a phase difference conversion mechanism. When the bridge vibrates, the wing plate device can adjust its attitude in real time according to the torsional displacement of the main beam to achieve torsional motion with adjustable phase difference. When the main beam does not vibrate, the wing plate has no driving force source and remains stationary, which can ensure the optimal aerodynamic shape of the main beam.

[0024] (2) The device is driven entirely by the torsional motion of the main beam, which avoids the dilemma of additional energy input, greatly improves the reliability of the wing control, and significantly reduces the risk.

[0025] (3) A pre-set phase difference can be maintained between the torsional motion of the main beam and the torsional motion of the flange to achieve the best wind-induced vibration control effect.

[0026] (4) Both the displacement amplification mechanism and the phase difference conversion mechanism can be replaced according to different control parameters, and different main beam displacement amplification coefficients and phase differences can be set to ensure good control effect for different bridge sections. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 This is a schematic diagram of a preferred embodiment of the present invention, showing the structure disposed on the main beam.

[0029] Figure 2 This is a schematic diagram of the structure of the displacement amplification mechanism and the two main beam displacement transmission racks in a preferred embodiment of the present invention;

[0030] Figure 3 This is a schematic diagram of the phase difference conversion mechanism according to a preferred embodiment of the present invention;

[0031] Figure 4 This is a schematic diagram of the transmission structure of the phase difference output rack, steering gear, wing plate displacement transmission rack, and wing plate gear according to a preferred embodiment of the present invention.

[0032] Figure 5 This is a schematic diagram of the working state of the flange device when the main beam is twisted by 2° according to a preferred embodiment of the present invention;

[0033] Figure 6 for Figure 5 A magnified diagram of the result of A in the middle;

[0034] In the diagram: 1. Main beam; 11. First support rod; 12. Second support rod; 13. Bearing rod; 14. Limiting block; 15. Third support rod; 16. Guide block; 17. Support rod; 18. Support shaft; 2. Wing plate; 3. Displacement amplification mechanism; 31. Fixed center gear; 32. Amplifying gear; 33. First amplifying gear; 34. Second amplifying gear; 4. Main beam displacement transmission rack; 5. Phase difference conversion mechanism; 51. Vertical rod; 511. Vertical elongated hole; 52. 521. Rocker arm; 522. First support shaft; 523. Second support shaft; 534. Horizontal rod; 535. Horizontal elongated hole; 54. Phase difference output rack; 6. Wing plate displacement transmission rack; 61. Wing plate displacement transmission rod; 62. First transmission rack; 63. Second transmission rack; 7. Steering gear; 8. Wing plate gear; 91. First meshing point; 92. Second meshing point; 93. Third meshing point; 94. Fourth meshing point; 95. Fifth meshing point; 96. Sixth meshing point. Detailed Implementation

[0035] To enable those skilled in the art to better understand the technical solutions of this invention, the technical solutions of the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this invention, and not all embodiments. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of this invention.

[0036] Please see Figures 1-4 This application discloses a traction torsional motion wingplate device for controlling wind-induced vibration, including two wingplates 2, located on opposite sides of a main beam 1 in the transverse direction and both capable of rotating relative to the main beam 1; a traction torsional motion mechanism, comprising: a displacement amplification mechanism 3, disposed on one side of the main beam 1 in the longitudinal direction, the displacement amplification mechanism 3 including a fixed center gear 31 and two amplification gears 32 meshing with the fixed center gear 31; two main beam displacement transmission racks 4, both extending horizontally, meshing with the two amplification gears 32 respectively; two phase difference conversion mechanisms 5, each connected to the two main beam displacement transmission racks 4; two wingplate displacement transmission racks 6, both extending horizontally, each phase difference conversion mechanism 5 cooperating with the corresponding wingplate displacement transmission rack 6 via a steering gear 7; and two wingplate gears 8, each wingplate gear 8 fixed on one side of the wingplate 2 in the longitudinal direction and meshing with the corresponding wingplate displacement transmission rack 6.

[0037] The motion of the main girder 1 under wind-induced vibration can be considered as a single-frequency sinusoidal motion. Since the torsional angle of the main girder 1 is often very small during wind-induced vibration, the displacement amplification mechanism 3 is set to amplify the torsional motion fed back to the flange 2, thus effectively controlling the wind-induced vibration. The amplification gear 32 includes a first amplification gear 33 and a second amplification gear 34 meshing with the first amplification gear 33. The first amplification gear 33 meshes with the fixed center gear 31, and the second amplification gear 34 meshes with the main girder displacement transmission rack 4.

[0038] The fixed center gear 31 acts as an absolute coordinate system fixed to one side of the longitudinal direction of the main beam 1, preventing rotation. The main beam 1 is equipped with a first support rod 11 and a second support rod 12. A first amplifying gear 33 is mounted on the first support rod 11, and a second amplifying gear 34 is mounted on the second support rod 12. When the main beam 1 twists, the first amplifying gear 33 and the second amplifying gear 34 will revolve around the fixed center gear 31 and rotate on their own axes. To ensure a constant transmission ratio during transmission, the fixed center gear 31, the first amplifying gear 33, and the second amplifying gear 34 are all involute gears. The ratio of the number of teeth on the first amplifying gear 33 to the number of teeth on the fixed center gear 31 is the first displacement amplification ratio, and the ratio of the number of teeth on the second amplifying gear 34 to the number of teeth on the first amplifying gear 33 is the second displacement amplification ratio. Preferably, the number of teeth on the fixed center gear 31 is twice the number of teeth on the first amplifying gear 33, and the number of teeth on the first amplifying gear 33 is twice the number of teeth on the second amplifying gear 34. Therefore, the first displacement amplification ratio is 1:2, meaning the rotation angle of the first amplifying gear 33 is twice the torsional displacement of the main beam 1. Similarly, the second displacement amplification ratio is 1:2, meaning the rotation angle of the second amplifying gear 34 is twice the rotation angle of the first amplifying gear 33. In other words, the torsional displacement of the main beam 1 is amplified four times by the displacement amplification mechanism 3, which can significantly increase the flutter critical wind speed and achieve optimal wind-induced vibration control. The fixed center gear 31 meshes with the first amplifying gear 33 at the first meshing point 91, and the first amplifying gear 33 meshes with the second amplifying gear 34 at the second meshing point 92.

[0039] The displacement amplification mechanism engages with the main beam displacement transmission rack 4 at the third meshing point 93 via the second amplification gear 34, converting the rotation of the main beam 1 into the translation of the main beam displacement transmission rack 4. This completes the gain amplification of the torsional motion from the main beam 1 to the flange 2.

[0040] In this embodiment, the phase difference conversion mechanism 5 includes a vertical rod 51, a rocker arm 52, a horizontal rod 53, and a phase difference output rack 54. The vertical rod 51 is connected to the main beam displacement transmission rack 4. One end of the rocker arm 52 is connected to the vertical rod 51 and the horizontal rod 53 respectively, and the other end of the rocker arm 52 can rotate relative to the main beam 1. The horizontal rod 53 is connected to the phase difference output rack 54.

[0041] Specifically, a vertical elongated hole 511 is provided in the vertical rod 51, a horizontal elongated hole 531 is provided in the horizontal rod 53, and a first support shaft 521 is provided at one end of the rocker arm 52. The two ends of the first support shaft 521 are respectively placed into the vertical elongated hole 511 and the horizontal elongated hole 531.

[0042] Specifically, a load-bearing rod 13 is provided on one side of the main beam 1 along the longitudinal direction, and a second support shaft 522 is provided at the other end of the rocker arm 52, which is connected to the load-bearing rod 13. Preferably, the load-bearing rod 13 is L-shaped.

[0043] In order to limit the movement of the phase difference output rack 54, it is preferable to provide a limit block 14 on one side of the longitudinal bridge of the main beam 1, and the phase difference output rack 54 moves along the limit block 14.

[0044] Thus, when the main beam displacement transmission rack 4 translates, it drives the rocker arm 52 via the vertical rod 51. The rocker arm 52 drives the horizontal rod 53, which in turn drives the phase difference output rack 54, causing the phase difference output rack 54 to translate as well. The translation of the main beam displacement transmission rack 4 is a sinusoidal motion with the same frequency and phase as the torsional motion of the main beam 1. This motion is then converted into a uniform angular velocity circular motion of the rocker arm 52, which in turn drives the phase difference output rack 54 to convert it back into a sinusoidal motion with the same frequency but different phase. The installation angle between the phase difference output rack 54 and the main beam displacement transmission rack 4 is the phase difference between their motions, preferably 90°. When the installation angle between the phase difference output rack 54 and the main beam displacement transmission rack 4 changes, the phase difference between their motions will also change.

[0045] The phase difference output rack 54 meshes with the steering gear 7, and the translation of the phase difference output rack 54 drives the steering gear 7 to rotate.

[0046] In order to facilitate the rotation of the steering gear 7 and improve the stability of the transmission, it is preferable that a third support rod 15 is provided on one side of the longitudinal bridge of the main beam 1, and the steering gear 7 is sleeved on the third support rod 15.

[0047] The preferred wing plate displacement transmission rack 6 includes a wing plate displacement transmission rod 61, a first transmission rack 62 and a second transmission rack 63 respectively connected to the two ends of the wing plate displacement transmission rod 61. The first transmission rack 62 meshes with the steering gear 7, and the second transmission rack 63 meshes with the wing plate gear 8.

[0048] The phase difference output rack 54 meshes with the steering gear 7 at the fourth meshing point 94. The steering gear 7 meshes with the first transmission rack 62 of the wing plate displacement transmission rack 6 at the fifth meshing point 95. The steering gear 7 converts the translational motion of the phase difference output rack 54 into the translational motion of the wing plate displacement transmission rack 6. The second transmission rack 63 of the wing plate displacement transmission rack 6 meshes with the wing plate gear 8 at the sixth meshing point 96, converting the translational motion of the wing plate displacement transmission rack 6 into the rotation of the wing plate gear 8. The rotation of the wing plate gear 8 drives the wing plate 2 to rotate. This completes the transmission from the torsional displacement of the main beam 1 to the torsional motion of the wing plate 2.

[0049] To facilitate the translation of the wing plate displacement transmission rack 6, it is preferable to provide two guide blocks 16 on one side of the longitudinal bridge direction of the main beam 1. Each wing plate displacement transmission rod 61 moves along the corresponding guide block 16 and is guided and limited by the guide block 16.

[0050] To facilitate the rotation of the wing plate 2, it is preferable that a support rod 17 is provided on the transverse side of the main beam 1. The free end of the support rod 17 extends into the wing plate 2 and is fixed with a support shaft 18. The support shaft 18 extends out of the wing plate 2 and is fixed with the wing plate gear 8.

[0051] When the bridge is not vibrating, the entanglement torsional motion flange device remains stationary, maintaining the bridge's streamlined aerodynamic shape. However, when the bridge experiences vortex-induced vibration at low to medium wind speeds, or shows a tendency to flutter at higher wind speeds, the entanglement torsional motion flange device can be driven by the main girder 1 to generate a torsional motion with a phase difference. (See also...) Figure 5 , Figure 6 Specifically, the main beam 1 twists, the first amplifying gear 33 rotates around the fixed center gear 31, the rotation of the first amplifying gear 33 drives the second amplifying gear 34 to rotate, the second amplifying gear 34 drives the main beam displacement transmission rack 4 to translate, the phase difference output rack 54 is made to translate through the phase difference conversion mechanism 5, and then converted into the translation of the wing plate displacement transmission rack 6 through the steering gear 7, the second transmission rack 63 of the wing plate displacement transmission rack 6 drives the wing plate gear 8 to rotate, so the wing plate gear 8 drives the wing plate 2 to complete the torsional motion, change the aerodynamic force distribution on the bridge surface, improve aerodynamic characteristics, and ensure the safety of the bridge and traffic.

[0052] Another embodiment of the present invention provides a bridge box girder, including the entanglement torsional motion wing plate device for controlling wind-induced vibration as described in any of the above embodiments.

[0053] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0054] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A device for controlling wind-induced vibration of a torsional airfoil, characterized in that, include: Two flanges are located on both sides of the main girder in the transverse direction and are both capable of rotating relative to the main girder; The torsion motion mechanism includes: A displacement amplification mechanism is disposed on one side of the main beam in the longitudinal direction. The displacement amplification mechanism includes a fixed center gear and two amplification gears that mesh with the fixed center gear. Both main beam displacement transmission racks extend horizontally, and the two main beam displacement transmission racks mesh with the two amplifying gears respectively; Two phase difference conversion mechanisms are provided, each connected to one of the two main beam displacement transmission racks. Each phase difference conversion mechanism includes a vertical rod, a rocker arm, a horizontal rod, and a phase difference output rack. The vertical rod is connected to the main beam displacement transmission rack. One end of the rocker arm is connected to both the vertical and horizontal rods, and the other end of the rocker arm is rotatable relative to the main beam. The horizontal rod is connected to the phase difference output rack. A vertical elongated hole is provided in the vertical rod, and a horizontal elongated hole is provided in the horizontal rod. A first support shaft is provided at one end of the rocker arm, with both ends of the first support shaft inserted into the vertical and horizontal elongated holes, respectively. A load-bearing rod is provided on one side of the main beam along the longitudinal direction, and a second support shaft is provided at the other end of the rocker arm, connected to the load-bearing rod. Two wing plate displacement transmission racks extend horizontally. Each phase difference conversion mechanism engages with the corresponding wing plate displacement transmission rack via a steering gear. Each wing plate displacement transmission rack includes a wing plate displacement transmission rod, a first transmission rack, and a second transmission rack connected to both ends of the wing plate displacement transmission rod, with the first transmission rack meshing with the steering gear. Two wing plate gears, each wing plate gear is fixed to one side of the longitudinal bridge of the wing plate and meshes with the corresponding wing plate displacement transmission rack, and the second transmission rack meshes with the wing plate gear.

2. The traction torsional motion airfoil device for controlling wind-induced vibration according to claim 1, characterized in that, The amplifying gear includes a first amplifying gear and a second amplifying gear that meshes with the first amplifying gear. The first amplifying gear meshes with the fixed center gear, and the second amplifying gear meshes with the main beam displacement transmission rack.

3. The device for controlling wind-induced vibration of a torsional airfoil according to claim 2, characterized in that, The number of teeth of the fixed center gear is twice the number of teeth of the first amplifying gear, and the number of teeth of the first amplifying gear is twice the number of teeth of the second amplifying gear.

4. The device for controlling wind-induced vibration of a torsional airfoil according to claim 2, characterized in that, The fixed center gear, the first amplifying gear, and the second amplifying gear are all involute gears.

5. The device for controlling wind-induced vibration of a torsional airfoil according to claim 1, characterized in that, Two guide blocks are provided on one side of the longitudinal bridge direction of the main beam, and each wing plate displacement transmission rod moves along the corresponding guide block.

6. A bridge box girder, characterized in that, Includes the entangled torsional motion airfoil device for controlling wind-induced vibration as described in any one of claims 1-5.

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