Passive self-adaptive tuning vibration absorber based on variable-rigidity leaf spring

Abstract

The invention relates to the technical field of vibration control, in particular to a passive self-adaptive tuning vibration absorber based on a variable-rigidity leaf spring, which comprises an external frame, and a mechanical sensing mechanism, a mechanical driving mechanism, a mechanical transmission mechanism and a tuning vibration absorption mechanism which are arranged on the external frame, the outer frame is used for being installed on an engineering structure and synchronously moves along with the engineering structure. The mechanical sensing mechanism is in transmission connection with the mechanical driving mechanism, the mechanical driving mechanism is in transmission connection with the mechanical transmission mechanism, the tuning vibration absorption mechanism comprises a leaf spring, and the mechanical transmission mechanism is used for changing the effective length of the leaf spring, so that the tuning rigidity and the tuning frequency of the device are continuously adjusted. The passive self-adaptive tuning of the frequency of the vibration absorber is realized by adopting a pure mechanical structure, external power supply is not needed, the structure is reliable, and the passive self-adaptive tuning vibration absorber is suitable for broadband and multi-order modal vibration control occasions.

Description

Technical Field

[0001] This invention relates to the field of vibration control technology, and in particular to a passive adaptive tuning vibration absorber based on a variable stiffness blade spring. Background Technology

[0002] Tuned vibration absorption technology is one of the important means of vibration control for engineering structures. Currently, the main tuned vibration absorption control methods include passive, semi-active, and active methods. Traditional tuned vibration absorption control methods are mainly passive, such as tuned mass dampers (TMDs) and tuned liquid dampers (TLDs). However, these devices are usually tuned for a specific mode of the structure, have a limited operating frequency band, and are quite sensitive to changes in system parameters. In actual engineering, due to factors such as design and construction errors, material aging, structural damage, and changes in external loads, the devices are prone to frequency detuning, resulting in a significant degradation of vibration reduction performance.

[0003] Compared to traditional tuned vibration absorption control methods, adaptive tuned vibration absorbers exhibit stronger robustness and achieve superior vibration control performance under multimodal and wide-frequency excitation conditions. An adaptive tuned vibration absorber is a device that automatically adjusts the dynamic characteristics of the structure-absorber system according to changes in the excitation frequency. Currently, adaptive tuning is mainly achieved through active or semi-active methods. While these methods offer advantages in tuning flexibility and control performance, they typically rely on sensors, actuators, and external power supplies.

[0004] Recent research has proposed passive adaptive tuned vibration absorbers that rely entirely on mechanical structures to achieve tuning functionality. Driven by the vibration response of the main structure, they automatically adjust damping, stiffness, or equivalent mass parameters when the system response exceeds a preset threshold. These devices require no external power supply and offer advantages such as simple structure, high reliability, and strong robustness, demonstrating promising application potential in multi-modal vibration control. However, the implementation forms of existing passive adaptive tuned vibration absorbers remain relatively limited, and some devices still have certain limitations in engineering applications, such as dependence on fixed bases or grounding conditions, and insufficient stability during the tuning process. Summary of the Invention

[0005] The main objective of this invention is to provide a passive adaptive tuning vibration absorber based on a variable stiffness leaf spring, which aims to solve the technical problem of existing passive adaptive tuning vibration absorbers being dependent on a fixed base or grounding conditions.

[0006] To achieve the above objectives, the present invention proposes a passive adaptive tuning vibration absorber based on a variable stiffness leaf spring, comprising an external frame, and a mechanical sensing mechanism, a mechanical drive mechanism, a mechanical transmission mechanism, and a tuning vibration absorption mechanism disposed on the external frame. The external frame is used to be installed on the engineering structure and moves synchronously with the engineering structure; The mechanical sensing mechanism is driven by the mechanical drive mechanism, which is driven by the mechanical transmission mechanism. The tuning vibration damping mechanism includes a leaf spring, and the mechanical transmission mechanism is used to change the effective length of the leaf spring, so as to continuously adjust the tuning stiffness and tuning frequency of the device.

[0007] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the mechanical sensing mechanism includes a sensing spring, a four-bar linkage and a sensing mass block. The sensing spring is connected to the outer frame, the four-bar linkage is connected to the sensing spring, the sensing mass is connected to the four-bar linkage, and the sensing mass corresponds to the mechanical drive mechanism. This mechanical sensing mechanism is used to sense the vibration of an engineering structure and to cause relative motion in the sensing mass block.

[0008] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the mechanical drive mechanism includes a vibration-sensing drive wheel, a pawl, a ratchet, and a drive shaft. The vibration-sensing drive wheel is rotatably mounted on the external frame and is rotatably connected to the drive shaft. The ratchet is located on the side of the vibration-sensing drive wheel and is fixedly connected to the drive shaft; the pawl is rotatably mounted on the side of the vibration-sensing drive wheel and cooperates with the ratchet, and the vibration-sensing drive wheel corresponds to the sensing mass block.

[0009] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the vibration sensing drive wheel includes a drive wheel body and a U-shaped arm that are fixedly connected. The drive wheel body is rotatably connected to the transmission shaft, and the U-shaped arm is correspondingly arranged with the sensing mass block. The mechanical drive mechanism is driven based on the relative motion generated by the mechanical sensing mechanism.

[0010] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the mechanical transmission mechanism includes a main drive mechanism, which includes a first transmission component, a second transmission component and a moving component. The drive shaft is driven to the first drive assembly, and the first drive assembly is driven to the second drive assembly; The moving component includes a slide rail, a slider, a connecting member, and a movable fulcrum frame. The second transmission component is drivenly connected to the connecting member. The slider is fixedly connected to the connecting member. The movable fulcrum frame is fixedly connected to the connecting member. The slider is slidably connected to the slide rail. The slide rail is fixed to the outer frame. The movable fulcrum frame is connected to the tuning vibration absorption mechanism.

[0011] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the first transmission component includes a main swing arm, a drive gear and a main pivot; the number of the main swing arms is two, and the two main swing arms are respectively located on the front and rear sides of the drive gear; One end of the main swing arm located at the front is fixedly connected to the drive shaft and rotates synchronously with the drive shaft, while the other end is fixedly connected to the main pivot. One end of the main swing arm located at the rear is rotatably connected to the outer frame, and the other end is fixedly connected to the main pivot. The main pivot is fixedly connected to the drive gear; the main pivot is driven by the second transmission assembly.

[0012] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the second transmission component includes a fixed rod, a driven arm, a driven gear and a secondary pivot. One end of the fixed rod is rotatably connected to the main pivot; the secondary pivot is rotatably connected to the other end of the fixed rod, and the secondary pivot is fixedly connected to the driven gear. One end of the swing arm is pivotally mounted on the connecting member, and the other end is fixedly connected to the secondary pivot. The driving gear meshes with the driven gear.

[0013] The passive adaptive tuning vibration absorber based on variable stiffness leaf spring of the present invention is further improved in that the mechanical transmission mechanism includes a secondary drive mechanism, pulleys and a conveyor belt. There are two pulleys, one of which is fixed on the drive shaft and the other is fixed on the secondary drive mechanism. The conveyor belt is wound between the two pulleys.

[0014] The passive adaptive tuning vibration absorber based on variable stiffness blade spring of the present invention is further improved in that the tuning vibration absorber includes a fixed groove, a blade spring and a tuning mass block. One end of the leaf spring is fixedly connected to the outer frame through the fixed groove, and the tuning mass block is fixedly connected to the other end of the leaf spring. The tuning vibration absorption mechanism adopts a cantilever beam structure, including a leaf spring that is fixedly connected to the tuning mass block.

[0015] The passive adaptive tuning vibration absorber based on variable stiffness leaf springs of the present invention is further improved in that the tuning vibration absorption mechanism adopts a simply supported beam structure, and a leaf spring is fixed on each of the left and right sides of the tuning mass block.

[0016] The technical solution of the present invention has the following beneficial effects: The passive adaptive tuned vibration absorber based on variable stiffness leaf springs of this invention achieves vibration response sensing, driving, and transmission through a purely mechanical structure comprising a mechanical sensing mechanism, a mechanical driving mechanism, a mechanical transmission mechanism, and a tuned vibration absorption mechanism. It requires no external power supply, resulting in a simple structure and high reliability. Simultaneously, the variable stiffness leaf springs in the tuned vibration absorption mechanism enable adaptive tuning of the vibration absorption parameters, giving the device a wide operating frequency band. This allows it to be applicable to the control requirements of broadband vibrations and multi-mode vibrations, thereby improving its applicability in engineering vibration control applications under complex conditions and solving the technical problem of existing passive adaptive tuned vibration absorbers' dependence on fixed bases or grounding conditions.

[0017] The device of this invention requires no external grounding; the mechanical sensing, driving, transmission, and tuning vibration absorption mechanisms are all integrated within the external frame. In practical applications, simply fixing the external frame to the engineering structure to be controlled enables adaptive tuning and control of the structure's vibration. The installation is simple, and it has strong engineering applicability.

[0018] This invention employs a combination of leaf springs and a tuning mass as the basic unit for tuning and vibration absorption. Utilizing the characteristic that leaf springs of different effective lengths correspond to different equivalent stiffnesses, adaptive adjustment of tuning parameters is achieved. By adjusting the position of the movable fulcrum frame on the leaf spring, the effective length of the leaf spring is changed, thereby enabling continuous adjustment of the device's tuning stiffness and tuning frequency. Compared with existing passive adaptive tuning devices, using leaf springs as the tuning elastic element ensures stable force states and controllable parameter changes during tuning. The stiffness adjustment method based on changes in effective length exhibits better tuning stability and reliability. Attached Figure Description

[0019] 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 of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the overall structure of Embodiment 1 of the passive adaptive tuning vibration absorber based on variable stiffness blade springs of the present invention; Figure 2 This is a schematic diagram of the overall structure of Embodiment 2 of the passive adaptive tuning vibration absorber based on variable stiffness leaf springs of the present invention; Figure 3 This is a schematic diagram of the mechanical sensing mechanism; Figure 4 This is a schematic diagram of the mechanical drive mechanism; Figure 5 This is a schematic diagram of the mechanical transmission mechanism in Embodiment 1; Figure 6 This is a schematic diagram of the structure of the tuning vibration absorption mechanism in Embodiment 1; Figure 7 This is a schematic diagram of the mechanical transmission mechanism in Embodiment 2; Figure 8 This is a schematic diagram of the structure of the tuning vibration absorption mechanism in Embodiment 2; Figure 9 This is a schematic diagram illustrating the working principle of a mechanical sensing mechanism; Figure 10 This is a front view of the sensing mass block and the vibration-driven wheel; Figure 11 This is a schematic diagram illustrating the working principle of the sensing mass block driving the vibration drive wheel to rotate counterclockwise (A represents the rightward movement of the sensing mass block, and B represents the counterclockwise rotation of the vibration drive wheel). Figure 12 This is a schematic diagram illustrating the working principle of the sensing mass block driving the vibration drive wheel to rotate clockwise (C represents the leftward movement of the sensing mass block, and D represents the clockwise rotation of the vibration drive wheel).

[0021] Explanation of icon numbers: 1-External frame; 2-Rigid arm; 3-Sensing spring; 4-Rigid connecting rod; 5-Sensing mass block; 6-First bearing support; 7-Vibration-sensing drive wheel; 8-Pawl; 9-Ratchet; 10-Drive shaft; 11-Main swing arm; 12-Fixed rod; 13-Driven swing arm; 14-Driving gear; 15-Driven gear; 16-Main pivot; 17-Secondary pivot; 18-Second bearing support; 19-Slide rail; 20-Slider; 21-Connecting component; 22-Modible fulcrum frame; 23-Fixed groove; 24-Leaf spring; 25-Tuning mass block; 26-Pulley; 27-Conveyor belt; 28-Secondary drive shaft. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0023] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0024] Furthermore, in this invention, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0025] In this invention, unless otherwise explicitly specified and limited, the terms "connection," "fixed," etc., should be interpreted broadly. For example, "fixed" can mean a fixed connection, a detachable connection, or an integral part; it can mean a mechanical connection or an electrical connection; it can mean a direct connection or an indirect connection through an intermediate medium; it can mean the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0026] Furthermore, the technical solutions of the various embodiments of the present invention can be combined with each other, but only if they are feasible for those skilled in the art. If the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such combination of technical solutions does not exist and is not within the scope of protection claimed by the present invention.

[0027] like Figures 1-12 As shown, the present invention proposes a passive adaptive tuning vibration absorber based on a variable stiffness leaf spring, including an outer frame 1, and a mechanical sensing mechanism, a mechanical drive mechanism, a mechanical transmission mechanism and a tuning vibration absorption mechanism disposed on the outer frame 1. The external frame 1 is used to be installed on the engineering structure and moves synchronously with the engineering structure, thereby realizing passive sensing and tuning control of the vibration response of the engineering structure. The mechanical sensing mechanism is driven by the mechanical drive mechanism, which is driven by the mechanical transmission mechanism. The tuning vibration damping mechanism includes a leaf spring, and the mechanical transmission mechanism is used to change the effective length of the leaf spring, so as to continuously adjust the tuning stiffness and tuning frequency of the device.

[0028] Preferably, such as Figure 1 and Figure 3 As shown, the mechanical sensing mechanism includes a sensing spring 3, a four-bar linkage, and a sensing mass block 5; the sensing spring 3 is connected to the outer frame 1, the four-bar linkage is connected to the sensing spring 3, and the sensing mass block 5 is connected to the four-bar linkage. The sensing mass block 5 corresponds to the mechanical drive mechanism; the mechanical sensing mechanism is used to sense the vibration of the engineering structure and cause the sensing mass block 5 to move relative to it.

[0029] Specifically, an L-shaped rigid arm 2 is inverted inside the outer frame 1. There are two sensing springs 3 and two sensing mass blocks 5. The four-bar linkage consists of four rigid links 4 hinged in pairs to form a rhombic four-bar linkage mechanism. The upper and lower ends of the rhombic four-bar linkage mechanism are connected to the sensing springs 3, and the left and right ends are connected to the sensing mass blocks 5. One end of the sensing spring 3 located at the upper end is connected to the rhombic four-bar linkage mechanism, and the other end is fixedly connected to the outer frame 1 through the rigid arm 2.

[0030] When the engineering structure vibrates, the outer frame 1 moves synchronously with the engineering structure. The mechanical sensing mechanism is used to sense the vibration response of the engineering structure and to cause the sensing mass block 5 to move relative to it. The rhomboid four-bar linkage is equivalent to a lever mechanism, which is used to convert the vertical relative motion into the lateral relative motion and to amplify the displacement.

[0031] like Figure 9 The schematic diagram of the working principle of the mechanical sensing mechanism shown can be expressed as follows, based on the principle of dynamics: The equation of motion of the sensing mass block 5 can be expressed as: ; in, The total mass of sensor mass block 5 and The stiffnesses of the sensing springs 3, located at the upper and lower ends of the rhomboid four-bar linkage, are respectively. The length of rigid link 4, Let be the angle between rigid link 4 and the vertical direction. Let ω be the angular velocity of the rigid link 4 and the vertical direction. Let be the angular acceleration of the rigid link 4 and the vertical direction. Let be the initial angle between rigid link 4 and the vertical direction. For the acceleration response of external frame 1, Indicates time.

[0032] From this equation of motion, we can see that the included angle of rigid link 4 is... The acceleration response of the external frame 1 can be determined. This means that the motion of the external frame 1 is converted into the relative motion of the sensing mass block 5. Furthermore, for a given acceleration response threshold of the external frame 1, a corresponding angle can be determined. The threshold is then used to obtain the lateral relative displacement threshold of the sensing mass block 5.

[0033] Meanwhile, the displacement responses of points A and B and They can be represented as follows: , and Functional relationship: ; ; Therefore, it can be concluded that as long as the initial included angle is reasonably selected in the design... And ensure that the angle between the rigid connecting rod 4 and the vertical direction is maintained during the operation of the device. Satisfaction makes > By establishing the geometric relationship conditions, the amplification effect of the relative displacement response can be achieved.

[0034] Preferably, such as Figure 4 As shown, the mechanical drive mechanism includes a vibration-sensing drive wheel 7, a pawl 8, a ratchet 9, and a drive shaft 10. The vibration-sensing drive wheel 7 is rotatably mounted on the outer frame 1 and is rotatably connected to the drive shaft 10. The ratchet 9 is disposed on the side of the vibration-sensing drive wheel 7 and is fixedly connected to the drive shaft 10. The pawl 8 is rotatably mounted on the side of the vibration-sensing drive wheel 7 and cooperates with the ratchet 9. The vibration-sensing drive wheel 7 corresponds to the sensing mass block 5. Specifically, the outer frame 1 is provided with a first bearing support 6 for the rotatable mounting of the drive shaft 10.

[0035] Preferably, the vibration-sensing drive wheel 7 includes a drive wheel body and a U-shaped arm fixedly connected. The drive wheel body is rotatably connected to the transmission shaft 10, and the U-shaped arm is correspondingly arranged with the sensing mass block 5. The mechanical drive mechanism is driven based on the relative motion generated by the mechanical sensing mechanism. When the sensing mass block 5 generates relative displacement under vibration, it contacts the U-shaped arm and drives the vibration-sensing drive wheel 7 to rotate, thereby achieving unidirectional intermittent rotation of the transmission shaft 10 through the cooperation of the pawl 8 and the ratchet 9. The spacing of the U-shaped arms is mainly designed based on the lateral relative displacement threshold of the sensing mass block 5, so that when the displacement of the sensing mass block 5 reaches the preset threshold, the vibration-sensing drive wheel 7 can be driven to rotate.

[0036] The sensing mass block reciprocates relative to the external frame 1 in the horizontal direction as the frame vibrates. Its range of motion can be expressed as […]. , During vibration, when the relative displacement amplitude of the sensing mass 5 exceeds a preset threshold, it will contact and collide with the U-shaped arm of the vibration-sensing drive wheel 7, thereby causing the drive wheel body to rotate. Within each vibration cycle, the pawl 8 engages with the ratchet 9 only once within its effective stroke range, driving the ratchet 9 to rotate at a fixed angle. Subsequently, the pawl 8 separates from the ratchet 9, thus ensuring that a single vibration cycle exceeding the threshold corresponds to only one unidirectional fixed-angle rotation of the ratchet.

[0037] Specifically, such as Figures 10-12As shown, when the sensing mass block 5 moves to the right (A), when it exceeds the relative displacement threshold of the sensing mass block 5, it contacts the right side of the U-shaped arm of the vibration-sensing drive wheel 7. Since the drive wheel body is fixed to the U-shaped arm, it drives the U-shaped arm to rotate to the right, which in turn drives the drive wheel body to rotate counterclockwise (B). The pawl 8 rotates counterclockwise with the vibration-sensing drive wheel 7 and engages with the ratchet 9 once, thereby driving the ratchet 9 to rotate at a fixed angle. Then, pawl 8 separates from ratchet 9 (i.e., the ratchet is rotated by the pawl by a fixed angle). Then, the pawl will no longer contact the ratchet, thus enabling the ratchet to move in a stepping motion (wherein the angle is mentioned). The relative displacement angle between the pawl 8 and the ratchet 9 can be determined. When the sensing mass block 5 moves to the left by C, when it exceeds the relative displacement threshold of the sensing mass block 5, it contacts the left side of the U-shaped arm of the vibration drive wheel 7, causing the drive wheel body to rotate clockwise by D. The pawl 8 rotates clockwise with the vibration drive wheel 7. Since the pawl 8 and the ratchet 9 only have a unidirectional meshing characteristic in the counterclockwise direction, the pawl 8 cannot drive the ratchet 9 to rotate in this direction, thus forming a no-stroke. This realizes the conversion from the relative displacement of the sensing mass block 5 to the unidirectional stepping output of the drive shaft 10.

[0038] Example 1: As Figure 5 As shown, the mechanical transmission mechanism includes a main drive mechanism, which includes a first transmission component, a second transmission component, and a moving component. The transmission shaft 10 is driven to the first transmission component, and the first transmission component is driven to the second transmission component. The moving component includes a slide rail 19, a slider 20, a connecting member 21, and a movable fulcrum frame 22. The second transmission component is driven to the connecting member 21. The slider 20 is fixedly connected to the connecting member 21. The movable fulcrum frame 22 is fixedly connected to the connecting member 21. The slider 20 is slidably connected to the slide rail 19. The slide rail 19 is fixed to the outer frame 1. The movable fulcrum frame 22 is connected to the tuning vibration absorption mechanism.

[0039] Preferably, the first transmission assembly includes a main swing arm 11, a drive gear 14, and a main pivot 16; there are two main swing arms 11, two fixed rods 12, and two driven swing arms 13, each located on the front and rear sides of the drive gear 14 respectively; one end of the main swing arm 11 located on the front side is fixedly connected to the drive shaft 10 and rotates synchronously with the drive shaft 10, and the other end is fixedly connected to the main pivot 16; one end of the main swing arm 11 located on the rear side is rotatably connected to the outer frame 1, and the other end is fixedly connected to the main pivot 16; the main pivot 16 is fixedly connected to the drive gear 14; the main pivot 16 is drively connected to the second transmission assembly. The outer frame 1 is provided with a second bearing support 18 for the main swing arm 11 to connect to, and one end of the main swing arm 11 located on the rear side is rotatably connected to the second bearing support 18 via a pivot.

[0040] Preferably, the second transmission assembly includes a fixed rod 12, a driven arm 13, a driven gear 15, and a secondary pivot 17; one end of the fixed rod 12 is rotatably connected to the main pivot 16; the secondary pivot 17 is rotatably connected to the other end of the fixed rod 12, and the secondary pivot 17 is fixedly connected to the driven gear 15; one end of the driven arm 13 is rotatably mounted on the connecting member 21 via a pivot, and the other end is fixedly connected to the secondary pivot 17; the driving gear 14 meshes with the driven gear 15.

[0041] Through the above structure, the mechanical transmission mechanism converts the rotational output of the mechanical drive mechanism into linear movement of the movable fulcrum frame 22 along the slide rail 19.

[0042] Specifically, by reasonably setting the lengths of the main swing arm 11, the fixed rod 12, and the driven swing arm 13, as well as the radius ratio of the driving gear 14 to the driven gear 15, the linear movement range and transmission efficiency of the slide rail 19 can be adjusted.

[0043] Preferably, the tuned vibration absorption includes a fixed groove 23, a leaf spring 24, and a tuning mass block 25; one end of the leaf spring 24 is fixedly connected to the outer frame 1 through the fixed groove 23, and the tuning mass block 25 is fixedly connected to the other end of the leaf spring 24. like Figure 6 As shown, the tuning vibration absorption mechanism adopts a cantilever beam structure, which includes only one leaf spring 24 fixedly connected to the tuning mass block 25.

[0044] The movable fulcrum frame 22 is located in the middle of the leaf spring 24 and can move along its length direction, thereby changing the effective length of the leaf spring 24 and realizing adaptive adjustment of the tuning stiffness and tuning frequency.

[0045] In this embodiment, the tuning frequency of the vibration absorber for: ; in, Let be the elastic modulus of leaf spring 24. Let be the moment of inertia of the cross section of leaf spring 24. It is the mass of the tuning mass block 25. The linear density of leaf spring 24. The effective length of the leaf spring 24 is given, and this parameter can be adjusted via adaptive tuning in the embodiments.

[0046] Example 2: Figure 1 and Figure 2As shown, the difference between this embodiment and Embodiment 1 is that the mechanical transmission mechanism includes not only the main drive mechanism, but also the auxiliary drive mechanism, pulley 26 and conveyor belt 27. The tuning vibration absorption mechanism adopts a simply supported beam structure. The structure and working principle of the remaining mechanical sensing mechanism and mechanical drive mechanism are the same as those in Embodiment 1, and will not be described again here.

[0047] like Figure 7 As shown, in this embodiment, the mechanical transmission mechanism, based on Embodiment 1, further includes pulleys 26, a conveyor belt 27, and a secondary drive shaft 28. The pulleys 26 are fixedly connected to the drive shaft 10 and the secondary drive shaft 28 respectively, and the conveyor belt 27 is wound between the two pulleys 26 to achieve synchronous power transmission.

[0048] One end of the auxiliary drive shaft 28 is fixedly connected to the main swing arm 11 on the right side, and the other end is rotatably mounted on the outer frame 11 via the second bearing support 18. This structure enables the mechanical transmission mechanisms on both sides of the device to operate synchronously.

[0049] like Figure 8 As shown, in this embodiment, the tuning vibration absorption mechanism adopts a simply supported beam structure. A leaf spring 24 is respectively installed on the left and right sides of the tuning mass block 25 and is fixedly connected to the external frame 11. The movable fulcrum frame 22 acts on the two leaf springs 24 respectively, and by synchronously changing the effective length of the leaf springs on both sides, adaptive adjustment of the tuning frequency is achieved.

[0050] In this embodiment, the tuning frequency of the vibration absorber for: ; in, Let be the elastic modulus of leaf spring 24. Let be the moment of inertia of the cross section of leaf spring 24. It is the mass of the tuning mass block 25. The linear density of leaf spring 24. The effective length of the leaf spring 24 is given, and this parameter can be adjusted via adaptive tuning in the embodiments.

[0051] The above description is only a preferred embodiment of the present invention and does not limit the scope of the present invention. All equivalent structural transformations made under the inventive concept of the present invention using the contents of the present invention specification and drawings, or direct / indirect applications in other related technical fields, are included within the protection scope of the present invention.

Claims

1. A passive adaptive tuned vibration absorber based on a variable stiffness leaf spring, characterized in that, It includes an outer frame (1), and a mechanical sensing mechanism, a mechanical drive mechanism, a mechanical transmission mechanism and a tuning vibration absorption mechanism disposed on the outer frame (1); The external frame (1) is used to be installed on the engineering structure and moves synchronously with the engineering structure; The mechanical sensing mechanism is driven by the mechanical drive mechanism, which is driven by the mechanical transmission mechanism. The tuning vibration absorption mechanism includes a leaf spring, and the mechanical transmission mechanism is used to change the effective length of the leaf spring, so as to continuously adjust the tuning stiffness and tuning frequency of the device.

2. The passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 1, characterized in that, The mechanical sensing mechanism includes a sensing spring (3), a four-bar linkage, and a sensing mass block (5). The sensing spring (3) is connected to the outer frame (1), the four-bar linkage is connected to the sensing spring (3), the sensing mass block (5) is connected to the four-bar linkage, and the sensing mass block (5) corresponds to the mechanical drive mechanism. The mechanical sensing mechanism is used to sense the vibration of the engineering structure and cause the sensing mass block (5) to move relative to it.

3. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 2, characterized in that, The mechanical drive mechanism includes a vibration-sensing drive wheel (7), a pawl (8), a ratchet (9), and a drive shaft (10). The vibration-sensing drive wheel (7) is rotatably mounted on the outer frame (1), and the vibration-sensing drive wheel (7) is rotatably connected to the transmission shaft (10); The ratchet (9) is disposed on the side of the vibration-sensing drive wheel (7) and is fixedly connected to the drive shaft (10); the pawl (8) is rotatably mounted on the side of the vibration-sensing drive wheel (7) and cooperates with the ratchet (9); the vibration-sensing drive wheel (7) corresponds to the sensing mass block (5).

4. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 3, characterized in that, The vibration-sensing drive wheel (7) includes a drive wheel body and a U-shaped arm that are fixedly connected. The drive wheel body is rotatably connected to the transmission shaft (10), and the U-shaped arm is correspondingly arranged with the sensing mass block (5). The mechanical drive mechanism is driven based on the relative motion generated by the mechanical sensing mechanism.

5. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 4, characterized in that, The mechanical transmission mechanism includes a main drive mechanism, which includes a first transmission component, a second transmission component, and a moving component. The drive shaft (10) is driven to the first drive assembly, and the first drive assembly is driven to the second drive assembly; The moving component includes a slide rail (19), a slider (20), a connecting member (21), and a movable fulcrum frame (22). The second transmission component is drivenly connected to the connecting member (21). The slider (20) is fixedly connected to the connecting member (21). The movable fulcrum frame (22) is fixedly connected to the connecting member (21). The slider (20) is slidably connected to the slide rail (19). The slide rail (19) is fixed to the outer frame (1). The movable fulcrum frame is connected to the tuning vibration absorption mechanism.

6. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 5, characterized in that, The first transmission assembly includes a main swing arm (11), a drive gear (14), and a main pivot (16); there are two main swing arms (11), which are located on the front and rear sides of the drive gear (14), respectively. One end of the main swing arm (11) located on the front side is fixedly connected to the drive shaft (10) and rotates synchronously with the drive shaft (10), while the other end is fixedly connected to the main pivot (16). One end of the main swing arm (11) located on the rear side is rotatably connected to the outer frame (1), and the other end is fixedly connected to the main pivot (16); The main pivot (16) is fixedly connected to the drive gear (14); the main pivot (16) is drive-connected to the second transmission assembly.

7. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 6, characterized in that, The second transmission assembly includes a fixed rod (12), a driven arm (13), a driven gear (15), and a secondary pivot (17). One end of the fixed rod (12) is rotatably connected to the main pivot (16); the secondary pivot (17) is rotatably connected to the other end of the fixed rod (12), and the secondary pivot (17) is fixedly connected to the driven gear (15); The arm is pivotally mounted on the connecting member (21) from one end of the swing arm (13), and fixedly connected to the sub-pivot (17) from the other end. The driving gear (14) meshes with the driven gear (15).

8. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 7, characterized in that, The mechanical transmission mechanism includes a secondary drive mechanism, pulleys (26) and a conveyor belt (27). There are two pulleys (26), one of which is fixed on the drive shaft (10) and the other is fixed on the secondary drive mechanism. The conveyor belt (27) is wound between the two pulleys (26).

9. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 1, characterized in that, The tuned vibration absorption includes a fixed groove (23), a blade spring (24), and a tuning mass block (25); One end of the leaf spring (24) is fixedly connected to the outer frame (1) through the fixed groove (23), and the tuning mass block (25) is fixedly connected to the other end of the leaf spring (24). The tuning vibration absorption mechanism adopts a cantilever beam structure, including a leaf spring (24) fixedly connected to the tuning mass block (25).

10. A passive adaptive tuning vibration absorber based on a variable stiffness leaf spring according to claim 9, characterized in that, The tuning vibration absorption mechanism adopts a simply supported beam structure, and a leaf spring (24) is fixed on each of the left and right sides of the tuning mass block (25).

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