Tuned mass electromagnetic damper and building structure equipped with the damper

Abstract

Tuned mass electromagnetic damper and building structure provided with the damper, relate to building shock absorption technical field, wherein the tuned mass electromagnetic damper includes the rod-shaped component, the rotor of the sleeve setting on the rod-shaped component and the stator of the setting in the rotor outside, the rotor and the stator between load magnetic field, the rod-shaped component and the rotor between the motion conversion mechanism of being equipped with cooperation, the motion conversion mechanism is configured as in the process of the rod-shaped component along axial reciprocating motion drives the rotor to rotate to the same direction to form induced current.The present application can reduce the volume and mass size of flywheel in conventional damper to facilitate installation, and can improve the reliability of tuned mass electromagnetic damper.

Description

Technical Field

[0001] This invention relates to the field of building vibration reduction technology, and in particular to a tuned mass electromagnetic damper and a building structure equipped with the damper. Background Technology

[0002] Tuned viscous mass dampers (TVMDs) are widely used in engineering vibration control due to their significant advantages in vibration control.

[0003] TVMDs typically consist of inertial elements, springs, and energy dissipation elements (EDEs). Currently, common TVMD dampers used in engineering practice include... Figure 1 As shown, the traditional TVMD dissipates vibration energy by displacing a flywheel in the forward-backward direction (axis of the screw) through a ball screw connected to the building structure. For example, when the screw moves forward, it drives the flywheel to rotate clockwise, and when the screw moves backward, it drives the flywheel to rotate counterclockwise. However, during an actual earthquake, the amplitude and frequency of the building structure's swaying are not fixed values, so the displacement conversion of the screw in the forward-backward direction during the vibration is uncertain, which in turn leads to uncertainty in the flywheel's direction of rotation. Furthermore, due to the large size and mass of the flywheel, a huge instantaneous torque is generated on the screw at the moment the flywheel's direction of rotation changes. Excessive instantaneous torque can easily cause "slippage" in the transmission structure between the flywheel and the screw, or even cause the screw to break, thus causing the TVMD to fail. At the same time, the replacement cost after the screw is damaged is also very high. Based on the above analysis, it can be seen that traditional TVMDs often cannot guarantee a sufficiently reliable continuous function in the face of sudden earthquakes and have the disadvantage of high operating costs. The large size and mass of the flywheel also pose significant challenges during installation. Summary of the Invention

[0004] One of the objectives of this invention is to provide a tuned mass electromagnetic damper that can reduce the size and mass of the flywheel for easier installation and improve the reliability of the TVMD.

[0005] To solve the above-mentioned technical problems, the present invention adopts the following technical solution: a tuned mass electromagnetic damper, comprising a rod-shaped component, a rotor sleeved on the rod-shaped component, and a stator disposed outside the rotor. A magnetic field is loaded between the rotor and the stator. A motion conversion mechanism is provided between the rod-shaped component and the rotor. The motion conversion mechanism is configured to drive the rotor to rotate in the same direction to generate an induced current during the reciprocating motion of the rod-shaped component along the axial direction.

[0006] Preferably, the rotor is provided with a permanent magnet for generating a magnetic field, and the stator is provided with a coil for cutting magnetic field lines to generate an induced current; or the stator is provided with a permanent magnet for generating a magnetic field, and the rotor is provided with a coil for cutting magnetic field lines to generate an induced current.

[0007] More preferably, the motion conversion mechanism includes a motion constraint structure and a force transmission component disposed between the rod-shaped component and the rotor. The motion constraint structure includes a first constraint structure and a second constraint structure. The first constraint structure is configured to constrain the force transmission component via a first helical path during the forward axial movement of the rod-shaped component, causing relative motion between the two. The second constraint structure is configured to constrain the force transmission component via a second helical path during the backward axial movement of the rod-shaped component, causing relative motion between the two. The first helical path and the second helical path have opposite directions of rotation. During the reciprocating axial movement of the rod-shaped component, the first constraint structure and the second constraint structure alternately constrain the force transmission component and alternately generate relative motion along the first helical path and the second helical path, so that the direction of the force driving the rotor to rotate remains unchanged.

[0008] More preferably, the first constraint structure includes a first limiting guide structure that forms a first spiral path, and the second constraint structure includes a second limiting guide structure that forms a second spiral path. The force transmission component can abut against the first limiting guide structure or the second limiting guide structure. The first limiting guide structure and the second limiting guide structure intersect and break at their intersection to form a notch. The size of the notch is limited so that, during the process of the rod-shaped component changing its direction of movement, the force transmission component can enter the second spiral path from the first spiral path or enter the first spiral path from the second spiral path through the notch.

[0009] More preferably, the first constraint structure includes multiple sets of parallel spaced first limiting guide structures and each first limiting guide structure constructs a first spiral path that is parallel to each other; the second constraint structure includes multiple sets of parallel spaced second limiting guide structures and each second limiting guide structure constructs a second spiral path that is parallel to each other; and the intersection of any set of first limiting guide structures and second limiting guide structures is broken and a gap is formed.

[0010] More preferably, the force transmission components are in multiple sets and their number is the same as the number of the first limiting guide structure or the second limiting guide structure.

[0011] More preferably, the first limiting guide structure includes a first guide surface extending along a first spiral path, and the second limiting guide structure includes a second guide surface extending along a second spiral path, wherein the force transmission component can abut against the first guide surface or the second guide surface.

[0012] More preferably, the first limiting guide structure is a first protrusion arranged along a first spiral path, the second limiting guide structure is a second protrusion arranged along a second spiral path, a first guide surface extending along the first spiral path is provided on one side of the first protrusion, a second guide surface extending along the second spiral path is provided on one side of the second protrusion, and the force transmission component is a pin, the side peripheral surface of the pin can abut against the first guide surface or the second guide surface.

[0013] More preferably, the motion constraint structure is disposed on the outer peripheral surface of the rod-shaped component, and the force transmission component is disposed on the inner peripheral surface of the rotor.

[0014] In addition, the present invention also provides a building structure which is provided with the above-mentioned tuned mass electromagnetic damper.

[0015] When the rod-shaped component reciprocates along the axial direction, the rotor is driven to rotate in one direction by the motion conversion mechanism. This avoids the risk of "slippage" or breakage of the rod-shaped component due to excessive torque caused by instantaneous reverse rotation. When applied to building structures, it can ensure the long-term operation of the tuned mass electromagnetic damper, improve the service life of the damper, enable the building structure to have continuous seismic resistance reliability, and reduce maintenance and replacement costs.

[0016] By applying a magnetic field between the rotor and the stator, an induced current is generated in the rotor during rotation, which in turn causes the rotor to be subjected to a force. Therefore, even if the size and mass of the rotor are greatly reduced, it can still generate the same level of force as an existing flywheel during rotation. This allows it to dissipate the translational energy of the rod-shaped components during vibration, thereby providing damping and achieving shock absorption. Replacing the flywheel with such a rotor is more convenient and easier to install due to its smaller size. Attached Figure Description

[0017] Figure 1 A cross-sectional schematic diagram of an existing tuned viscous mass damper;

[0018] Figure 2 This is a schematic diagram of the overall structure in an embodiment of the present invention;

[0019] Figure 3 This is a perspective structural diagram of the rod-shaped component and the rotor in an embodiment of the present invention;

[0020] Figure 4 This is a schematic diagram of the rod-shaped component in the embodiment;

[0021] Figure 5 This is a schematic diagram of the rotor and stator structure in the embodiment;

[0022] Figure 6 This is a schematic diagram of the structure when the rotor is in the middle position of the rod-shaped component in the embodiment.

[0023] In the picture:

[0024] 1—Rod-shaped component 2—Rotor 3—Stator

[0025] 4 – Permanent magnet; 5 – Coil; 6 – First protrusion

[0026] 7 – Second protrusion; 8 – Pin; 9 – Ball joint

[0027] 10 - Standard lead screw; 11 - Standard flywheel; 12 - Nut

[0028] 13 – Friction material; 14 – Disc spring; 15 – Crossed roller bearing

[0029] 16—Inner tube; 17—Sealing ring; 18—Viscous material

[0030] 19 — Radial bearing. Implementation

[0031] To facilitate understanding by those skilled in the art, the present invention will be further described below with reference to embodiments and accompanying drawings. The content mentioned in the embodiments is not intended to limit the present invention.

[0032] It should be noted in advance that, in this invention, unless otherwise explicitly specified and limited, terms such as "installation," "connection," "joining," and "fixing" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. Those skilled in the art can understand the specific meaning of these terms in this invention according to the specific circumstances. Furthermore, in this invention, unless otherwise explicitly specified and limited, "on" or "under" a second feature can include direct contact between the first and second features, or contact between the first and second features not in direct contact but through another feature between them.

[0033] like Figures 1 to 5As shown, a tuned mass electromagnetic damper includes a rod-shaped component 1, a rotor 2 sleeved on the rod-shaped component 1, and a stator 3 disposed outside the rotor 2. A magnetic field is applied between the rotor 2 and the stator 3. A matching motion conversion mechanism is provided between the rod-shaped component 1 and the rotor 2. The motion conversion mechanism is configured to drive the rotor 2 to rotate in the same direction during the axial reciprocating motion of the rod-shaped component 1 to generate an induced current. It is important to understand that the relative displacement between the rod-shaped component 1 and the rotor 2 is still the relative displacement form of a conventional lead screw and flywheel in existing tuned mass dampers. Regardless of how far the rod-shaped component 1 moves forward or backward, although the rotor 2 is displaced relative to the rod-shaped component 1, its position remains unchanged within the tuned mass damper. Furthermore, a magnetic field is applied between the rotor 2 and the stator 3, and the rotor 2 can generate an induced current during rotation, thereby applying a force to the rotor 2.

[0034] In the above structure, the rotor 2 is provided with permanent magnets 4 for generating a magnetic field, and the stator 3 is provided with coils 5 for cutting magnetic field lines to generate an induced current; or the stator 3 is provided with permanent magnets 4 for generating a magnetic field, and the rotor 2 is provided with coils 5 for cutting magnetic field lines to generate an induced current. In this embodiment, preferably, a plurality of permanent magnets 4 are evenly spaced on the outer peripheral surface of the rotor 2, and the stator 3 is coaxially provided with an inner peripheral surface spaced from the outer peripheral surface of the rotor 2, and a plurality of coils 5 are evenly spaced along the annular axis on the inner peripheral surface of the stator 3. Those skilled in the art should know that by setting a permanent magnet 4, a magnetic field is generated in the area between the outer circumferential surface of the rotor 2 and the inner circumferential surface of the stator 3. When the rotor 2 rotates, the coil 5 set on the inner circumferential surface of the stator 3 cuts the magnetic field lines, thereby generating an induced current. The rotor 2 is also subjected to a force, which ensures that the stator 3 has a sufficiently large force during rotation, achieving the same effect as the force generated by an existing large-volume flywheel. It can also dissipate the translational energy of the rod-shaped component during vibration to provide damping and achieve shock absorption. Replacing the flywheel with such a rotor 2 is more convenient and easier to install due to its smaller size. Of course, it is also possible to set the coil on the outer circumferential surface of the rotor 2 and the permanent magnet on the inner circumferential surface of the stator 3. This can also achieve the effect of cutting the magnetic field lines and applying a force to the rotor 2 during rotation. However, since the stator 3 is stationary, the advantage of setting the coil 5 on the stator 3 is that it is easier to ground the coil 5, so that the induced current generated during the cutting of the magnetic field lines can be more easily conducted away. Those skilled in the art should know that the permanent magnet 4 and coil 5 in the accompanying drawings are simplified representations. In reality, for example, coil 5 can be a structure wound around a protrusion on the inner circumference of the stator.

[0035] Specifically, the motion conversion mechanism includes a motion constraint structure and a force transmission component disposed between the rod-shaped component 1 and the rotor 2. The motion constraint structure includes a first constraint structure and a second constraint structure. The first constraint structure is configured to constrain the force transmission component via a first helical path during the forward axial movement of the rod-shaped component 1, causing relative motion between the two components. The second constraint structure is configured to constrain the force transmission component via a second helical path during the backward axial movement of the rod-shaped component 1, causing relative motion between the two components. The first helical path and the second helical path have opposite directions of rotation. During the reciprocating axial movement of the rod-shaped component 1, the first constraint structure and the second constraint structure alternately constrain the force transmission component and alternately generate relative motion along the first helical path and the second helical path, so that the direction of the force driving the rotor 2 to rotate remains unchanged.

[0036] The first constraint structure includes a first limiting guide structure that constructs a first spiral path, and the second constraint structure includes a second limiting guide structure that constructs a second spiral path. The force transmission component can abut against either the first or second limiting guide structure. The first and second limiting guide structures intersect and break at their intersection to form a notch. The size of the notch is limited so that, during the change of movement direction of the rod-shaped component 1, the force transmission component can enter the second spiral path from the first spiral path or vice versa via the notch. The first constraint structure includes multiple sets of parallel, spaced-apart first limiting guide structures, each constructing a parallel first spiral path. The second constraint structure includes multiple sets of parallel, spaced-apart second limiting guide structures, each constructing a parallel second spiral path. The intersection of any set of first and second limiting guide structures is broken, forming a notch.

[0037] Based on the above, there are multiple sets of force transmission components, and their number is the same as the number of the first limiting guide structure or the second limiting guide structure. The first limiting guide structure includes a first guide surface extending along a first helical path, and the second limiting guide structure includes a second guide surface extending along a second helical path. The force transmission component can abut against the first guide surface or the second guide surface. When the rod-shaped component 1 and the rotor 2 undergo relative displacement, the force transmission component can move to any first guide surface in any first helical path or to any second guide surface in any second helical path. As long as it contacts the first guide surface or the second guide surface, when the rod-shaped component 1 moves axially, the force transmission component can be pushed to rotate in the same direction as the guide surface moves.

[0038] For structural stability and reliability considerations, the first limiting and guiding structure is a first protrusion 6 arranged along a first helical path, and the second limiting and guiding structure is a second protrusion 7 arranged along a second helical path. A first guide surface extending along the first helical path is provided on one side of the first protrusion 6, and a second guide surface extending along the second helical path is provided on one side of the second protrusion 7. The force transmission component is a pin 8. During the guiding process of the rotor 2, the side circumferential surface of the pin 8 can abut against the first or second guide surface. Furthermore, the structure of the pin 8 can be optimized. In this embodiment, the motion constraint structure is set on the outer circumferential surface of the rod-shaped component 1, while the force transmission component is set on the inner circumferential surface of the rotor 2. Therefore, the end face of the pin 8 facing the center of the rotor 2 can be set as an inclined surface to facilitate better contact and fit between the outer circumferential surfaces of the rod-shaped component 1, resulting in smoother movement.

[0039] Those skilled in the art will know that the overall damper structure also includes Figure 1 The other parts of the structure can be formed by existing structures such as the conventional lead screw 10 and conventional flywheel 11, nut 12, friction material 13, disc spring 14, crossed roller bearing 15, inner tube 16, sealing ring 17, viscous material 18, radial bearing 19, etc., to form an integral tuned mass damper structure. The two ends of the damper are connected to the building structure by ball joints 9. Since this application only modifies the conventional lead screw 10 and conventional flywheel 11, the connection relationships between other structures in the damper will not be described in detail. In practical applications, those skilled in the art only need to replace the conventional lead screw 10 in the existing tuned mass damper with the rod-shaped component 1 of this application, and replace the conventional flywheel 11 with the rotor 2 and stator 3 of this application.

[0040] The tuned mass electromagnetic damper provided in the above embodiment can be installed in the damping structure connecting two opposite floor walls of a building, or in the damping structure of engineering structures such as bridges. When the building or bridge vibrates, the main structure sways back and forth, and the tuned mass electromagnetic damper in the damping structure also sways back and forth. At this time, the rod-shaped component 1 in the tuned mass electromagnetic damper will drive the rotor 2 to rotate due to the back-and-forth movement, so as to convert the instantaneous displacement generated by the structural vibration into the rotation of the rotor 2 through the translation of the rod-shaped component 1, and consume it through the rotation of the rotor 2. That is, by converting the energy expression form, damping force is provided to achieve the damping effect, thereby enabling the building, bridge and other structures to quickly return to stability. So, during the back-and-forth movement of the rod-shaped component 1, the rotor 2 in this embodiment can always maintain rotation in the same direction (counterclockwise direction as shown in the figure). Specifically, it is achieved as follows:

[0041] like Figure 3As shown, assuming that in the initial natural state, all the pins 8 on the inner wall of the rotor 2 fall on the first guide surface of the first protrusion 6 corresponding to the leftmost end of the rod-shaped component 1, when the building structure vibrates, causing the tuned mass electromagnetic damper to move back and forth due to swaying, when the rod-shaped component 1 moves forward, the first guide surface of the first protrusion 6 will push against the corresponding pin 8, causing the pin 8 to move along the first guide surface, that is, to begin moving along the first helical path. Then, the rotor 2 is pushed towards... Figure 3 It has rotated counterclockwise as shown.

[0042] It should be noted that when the rod-shaped component 1 continues to move forward, the pin 8 will disengage from the first guide surface on the original first protrusion 6. However, due to inertia, the pin 8 will continue to move along the first spiral path and be "caught" by the next first protrusion 6 on that path, thus continuing to be pushed to rotate counterclockwise. When the rod-shaped component 1 stops moving, the rotor 2 will also stop rotating. If the position of the rotor 2 when it stops rotating makes the pin 8 exactly in the gap between the two first protrusions 6, then when the rod-shaped component 1 moves forward again, because the outer circumference of the rod-shaped component 1 is distributed with first protrusions 6, the pin 8 will still fall onto one of the first protrusions 6 in the other set. There is no need to worry about the pin 8 losing support during the movement of the rod-shaped component 1. Once supported by the first guide surface of the first protrusion 6, the pin 8 will inevitably continue to move along the first spiral path during the movement of the rod-shaped component 1, thus maintaining the counterclockwise rotation of the rotor 2.

[0043] When the rod-shaped component 1 begins to move in the opposite direction, i.e., backward, the second protrusion 7 quickly contacts the pin 8, causing the second guide surface to support the pin 8 and push it along the second helical path. As the pin 8 moves along the second helical path, the rotor 2 continues to rotate counterclockwise. It is evident that regardless of whether the rod-shaped component 1 moves forward or backward, it causes the rotor 2 to rotate counterclockwise, i.e., in the same direction. This is due to the segmented constraint structure of the two helical paths distributed on the outer circumference of the rod-shaped component 1. While the protrusion spacing shown in the figure appears slightly large, in practical applications, the distance between each group of protrusions can be even closer, allowing the pin 8 to more easily and quickly contact the guide surface on the corresponding protrusion.

[0044] In this embodiment, a preferred structure is used to demonstrate the movement of the damper. Four force transmission components, namely four pins 8, are provided on the inner wall of the rotor 2. At the same time, four sets of protrusions are provided on the outer wall of the rod-shaped component 1. Each set of protrusions includes two first protrusions 6 and two second protrusions 7 that are staggered with the two first protrusions 6. Here, a simulation under vibration is performed using a section of rod-shaped component 1. Within a certain length range on rod-shaped component 1, a set of protrusions is provided for each pin 8. When there are four pins 8 and they are evenly distributed in a ring, the four sets of protrusions are also evenly distributed in a ring on the outer circumference of the same length range of rod-shaped component 1, that is, a set of protrusions is distributed every 90 degrees. Each set of protrusions includes two first protrusions 6 and two second protrusions 7 that are staggered with the two first protrusions 6. Then, the distribution of the four sets of protrusions in the ring within the total length range of this section of rod-shaped component 1 is set as three columns. These three columns are evenly spaced along the length direction of rod-shaped component 1. In practical applications, the gap between each column can be set to be shorter than that shown in the figure.

[0045] Assuming that initially each pin 8 falls on the first guide surface of the corresponding first protrusion 6, and the rotor 2 is engaged with... Figure 3 The rod-shaped component 1 shown in the diagram starts to vibrate on the four sets of protrusions in the foremost column. The vibration energy is transferred to the tuned mass electromagnetic damper, causing the rod-shaped component 1 to move forward initially. Each first protrusion 6's first guide surface pushes the corresponding pin 8, causing the pin 8 to move along its corresponding first guide surface. This movement follows a first helical path, thus driving the rotor 2 to rotate counterclockwise until the pin 8 moves to another first protrusion 6 in the same group. At this point, the rod-shaped component 1 continues to move forward, and the first guide surface of that first protrusion 6 pushes the pin 8, causing it to continue moving along the first helical path until it reaches the first protrusion 6 in the second column of protrusions (i.e., the group of protrusions in the middle of the rod-shaped component 1 in the diagram). Figure 6 As shown in the figure, the approximate trajectory of the pin 8 moving along the first spiral path is indicated by the dashed arrow. When the rod-shaped component 1 moves forward, the movement and path of the pin 8 are the same as before.

[0046] When the rod-shaped component 1 suddenly begins to retract, assuming that each pin 8 now rests on the first protrusion 6 of the corresponding group of four protrusions in the middle row of the rod-shaped component 1, due to the instantaneous backward movement of the rod-shaped component 1, the position of the pin 8 will not change significantly in a short time when it loses support. Instead, as the rod-shaped component 1 moves backward, the second protrusion 7 in the same group of protrusions will shift and abut against the corresponding pin 8. This is equivalent to the pin 8 instantly falling onto the second guide surface. In other words, the pin 8 is instantly switched to the second spiral path. Therefore, when the rod-shaped component 1 continues to move backward, it becomes the second protrusion 7. The second guide surface pushes the pin 8 to move. Under the push of the second guide surface, the pin 8 will move along the second spiral path. The direction of movement of this path causes the pin 8 to still rotate in the counterclockwise direction. And like the movement principle of the first spiral path, the pin 8 moves from a set of protrusions in the middle row of the rod-shaped component 1 to a set of protrusions in the frontmost row of the rod-shaped component 1. Of course, those skilled in the art should know that the rotor 2 has already rotated 90 degrees at this time. The pin 8 moves from a set of protrusions in the middle row to another set of protrusions in the frontmost row that is offset from the set of protrusions in the middle row. During this process, the rotor 2 still maintains counterclockwise rotation.

[0047] As can be seen from the above embodiments, the force distribution of this invention differs from that of existing classic TVMDs. The most significant difference is that regardless of whether the rod-shaped component 1 is displaced in the forward or reverse direction, it only drives the rotor 2 to rotate in one direction. This prevents abrupt changes in the rotor 2's direction of rotation caused by the instantaneous switching of the rod-shaped component 1's displacement. This avoids the problem of excessive instantaneous torque on the rod-shaped component 1 caused by sudden rotation of the rotor 2, improving the durability and service life of the rod-shaped component 1 and ensuring the reliability of the damper. Secondly, the motion constraint structure in the helical path of the rod-shaped component 1 is segmented, ensuring that the rotor 2 maintains flexible rotational characteristics even with uncertain displacement values ​​and directions.

[0048] Those skilled in the art will understand that the examples in the above embodiments are merely for illustrating the action coordination relationship between the rod-shaped component 1 and the rotor 2. Therefore, the structure is simplified for ease of understanding. However, in practical applications, the length of the rod-shaped component 1 is consistent with the length of the lead screw in an existing tuned mass damper, and the rotor 2 is simply much smaller in volume and mass than a conventional flywheel. In fact, the surface of the rod-shaped component 1 can also be provided with multiple rows of protrusions, and each row can also be provided with more groups of protrusions. The number of protrusions in each group is not necessarily four, but can be more. In addition, the spacing between protrusions in adjacent rows can also be adjusted to make them closer together. The most ideal setting can be obtained through adjustment to ensure that the movement of the rotor 2 is smoother and more fluid. This embodiment only lists one form of protrusion distribution to illustrate the motion principle.

[0049] By modifying the conventional lead screw 10 and flywheel 11 structure in traditional tuned mass dampers to the structure described in this application, the tuned mass damper can drive the rotor 2 to always rotate in the same direction during application. This avoids the problem of excessive instantaneous torque on the rod-shaped component 1 when the rotor 2 undergoes a sudden change in direction, greatly reducing the risk of damage to the rod-shaped component 1 and improving its durability. As those skilled in the art know, in practical applications, a set of tuned mass dampers used in building or bridge engineering structures is very expensive. The total cost of a high-quality damper of this type, combined with a corresponding vibration reduction structure, can even reach tens of thousands of yuan. If a single earthquake damages a damper, it must be disassembled and replaced, resulting in significant losses and considerable maintenance difficulties. Furthermore, major earthquakes often inevitably lead to aftershocks, some of which are of considerable magnitude. If the damper's lead screw is damaged during the initial strong earthquake due to repeated instantaneous steering of the flywheel, disrupting the overall damper structure, even if the building or bridge structure is spared damage from the strong earthquake, the damper will no longer be able to provide effective damping when a larger aftershock strikes again. This would pose a significant risk of damage to the building or bridge. However, when the tuned mass electromagnetic damper designed in this application is adopted, not only is the installation convenient due to the reduction in the volume and mass of rotor 2, but also because rotor 2 will not cause damage to rod-shaped component 1 due to the huge torque generated by instantaneous switching of direction, the entire tuned mass electromagnetic damper can continue to work stably for a long time. Therefore, even after experiencing the first strong earthquake, when encountering subsequent aftershocks of greater intensity, the tuned mass electromagnetic damper can still provide shock absorption to prevent the building or bridge structure from being easily damaged. It can be seen that the application value of this tuned mass electromagnetic damper is very high. Through the improvement of reliability, it can not only reduce the huge cost of replacing the damper after damage, but also effectively improve its value in strong earthquakes and aftershocks. This is a technical effect that existing tuned mass electromagnetic dampers cannot achieve, and it is a design that can bring about completely creative technical achievements.

[0050] To facilitate understanding by those skilled in the art of the improvements of this invention over the prior art, some of the accompanying drawings and descriptions have been simplified. The above embodiments are preferred implementations of this invention. In addition, this invention can be implemented in other ways. Any obvious substitutions without departing from the concept of this technical solution are within the protection scope of this invention.

Claims

1. A tuned mass electromagnetic damper, characterized in that: The device includes a rod-shaped component (1), a rotor (2) sleeved on the rod-shaped component (1), and a stator (3) disposed outside the rotor (2). A magnetic field is applied between the rotor (2) and the stator (3). A matching motion conversion mechanism is provided between the rod-shaped component (1) and the rotor (2). The motion conversion mechanism is configured to drive the rotor (2) to rotate in the same direction to generate an induced current during the axial reciprocating motion of the rod-shaped component (1). The motion conversion mechanism includes a motion constraint structure and a force transmission component disposed between the rod-shaped component (1) and the rotor (2). The motion constraint structure includes a first constraint structure and a second constraint structure. The constraint structure is configured to transmit the constraint force via a first helical path during the forward axial movement of the rod-shaped member (1), causing relative motion between the two. The second constraint structure is configured to transmit the constraint force via a second helical path during the backward axial movement of the rod-shaped member (1), causing relative motion between the two. The first and second helical paths have opposite directions of rotation. During the axial reciprocating motion of the rod-shaped member (1), the first and second constraint structures alternately transmit the constraint force, generating relative motion between them along the first and second helical paths, thereby driving the rotor (2). The direction of the rotational force remains unchanged. The motion constraint structure is set on the outer circumferential surface of the rod-shaped component (1), and the force transmission component is set on the inner circumferential surface of the rotor (2). The first constraint structure includes a first limiting guide structure that constructs a first helical path, and the second constraint structure includes a second limiting guide structure that constructs a second helical path. The force transmission component can abut against the first limiting guide structure or the second limiting guide structure. The first limiting guide structure and the second limiting guide structure intersect and break at their intersection to form a notch. The size of the notch is limited to the force transmission component during the process of the rod-shaped component (1) changing its direction of movement. The component can enter the second spiral path from the first spiral path or enter the first spiral path from the second spiral path through the gap. The first constraint structure includes multiple sets of parallel and spaced first limiting guide structures, and each first limiting guide structure constructs a first spiral path that is parallel to each other. The second constraint structure includes multiple sets of parallel and spaced second limiting guide structures, and each second limiting guide structure constructs a second spiral path that is parallel to each other. The intersection of any set of first limiting guide structures and second limiting guide structures is broken and a gap is formed. There are multiple sets of force transmission components, and their number is the same as the number of first limiting guide structures or second limiting guide structures.

2. The tuned mass electromagnetic damper according to claim 1, characterized in that: The rotor (2) is provided with a permanent magnet (4) for forming a magnetic field, and the stator (3) is provided with a coil (5) for cutting magnetic field lines to form an induced current; or the stator (3) is provided with a permanent magnet (4) for forming a magnetic field, and the rotor (2) is provided with a coil (5) for cutting magnetic field lines to form an induced current.

3. The tuned mass electromagnetic damper according to claim 1, characterized in that: The first limiting guide structure includes a first guide surface extending along a first spiral path, and the second limiting guide structure includes a second guide surface extending along a second spiral path. The force transmission component can abut against the first guide surface or the second guide surface.

4. The tuned mass electromagnetic damper according to claim 3, characterized in that: The first limiting guide structure is a first protrusion (6) arranged along a first spiral path, and the second limiting guide structure is a second protrusion (7) arranged along a second spiral path. A first guide surface extending along the first spiral path is provided on one side of the first protrusion (6), and a second guide surface extending along the second spiral path is provided on one side of the second protrusion (7). The force transmission component is a pin (8), and the side circumferential surface of the pin (8) can abut against the first guide surface or the second guide surface.

5. A building structure, characterized in that: The device is equipped with a tuned mass electromagnetic damper as described in any one of claims 1-4.

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