A resonator capable of self-adjusting to the vibration excitation frequency

Abstract

The present invention relates to a resonator (1) comprising at least one first region (10) and at least one second region (20) arranged opposite to each other, at least one first hinge (11) connected to the said first region (10), at least one second hinge (21) connected to the said second region (20), and at least one lever (40) connected to the said first hinge (11) and the said second hinge (21) so as to be at least partially movable along a first axis (I). The novelty resides in that the resonator comprises at least one adjustment mechanism (50) positioned between the first region (10) and the second region (20) to maintain continuous resonance by automatically tracking the varying excitation vibration frequency, wherein the said adjustment mechanism (50) is capable of being positioned in the vicinity of the first hinge (11) so as to align the instantaneous center of velocity (II) of the lever (40) at a predetermined position in response to the varying excitation vibration frequency.

Description

[0001] A RESONATOR CAPABLE OF SELF-ADJUSTING TO THE VIBRATION

[0002] EXCITATION FREQUENCY

[0003] TECHNICAL FIELD

[0004] The invention relates to a resonator that maximizes the incoming vibration .

[0005] PRIOR ART

[0006] Resonators are devices that undergo vibration at high amplitude at a specific frequency . Based on the principle of resonance , resonators amplify external vibrations when they coincide with their natural frequencies . Owing to these characteristics , they are widely used in acoustic, electronic, mechanical , and optical systems . Various types of resonators exist . One of them is levertype resonators . Lever-type resonators are devices that employ the principle of mechanical leverage in order to maximize vibration at a specific frequency .

[0007] In prior art resonators , in order to isolate translational mechanical vibrations , passive systems self-adj usting to excitation frequency either employ flexible beams or wires or require high-amplitude vibrations to take advantage of centrifugal acceleration . There are passive systems that can adj ust according to torsional vibrations in rotating systems ; however, such systems operate only with torsional vibrations and do not function when subj ected to translational vibrations . Systems that are capable of self-adj usting under translational vibrations are generally active or adaptive , and require sensors , actuators , control circuits , and electrical power . Accordingly, in addition to the cost of the devices , the need for maintenance and repair also arises for the mentioned devices . Furthermore , the aforementioned devices require external energy, which results in additional energy costs . As a result , all the aforementioned problems have made it necessary to introduce an innovation in the relevant technical field .

[0008] BRIEF DESCRIPTION OF THE INVENTION

[0009] The present invention relates to a resonator, aimed at eliminating the aforementioned disadvantages and providing new advantages in the relevant technical field .

[0010] An obj ect of the invention is to provide a resonator that can adj ust itself to the mechanical vibration excitation frequency in a passive adaptive manner . (without sensors , actuators , control circuits , PLCs , computers , or other electronic control equipment ) .

[0011] Another obj ect of the invention is to provide a resonator that can continuously remain in a resonant state by following the excitation frequency when it changes .

[0012] Another obj ect of the invention is to provide a resonator that enables the harvesting of energy from variable-frequency vibrations .

[0013] Another obj ect of the invention is to provide a resonator capable of absorbing variable-frequency vibrations .

[0014] Another obj ect of the invention is to provide a resonator that can operate without external electrical or magnetic energy input , and without the need for a power source or battery .

[0015] To achieve all the above-mentioned obj ects and those that will become apparent from the detailed description below, the present invention relates to a resonator comprising at least one first region and at least one second region positioned opposite each other to maximize the incoming vibration, at least one first hinge associated with the said first region, at least one second hinge associated with the said second region, and at least one lever connected to the said first hinge and the said second hinge so as to be at least partially movable along at least one first axis . Accordingly, the novelty lies in comprising at least one adj ustment mechanism positioned between the first region and the second region to enable the resonator to continuously remain in resonance by self-tracking the excitation vibration frequency when it changes , the said adj ustment mechanism being capable of aligning , in the vicinity of the first hinge , the instantaneous velocity center of the lever with a predetermined position in accordance with the varying excitation vibration frequency . Thus , by automatically adapting to varying frequencies , the resonator continuously remains in a resonant state , thereby enhancing performance in energy harvesting or vibrationabsorbing applications .

[0016] One embodiment of the invention is characterized in that it comprises at least one bearing provided at the first hinge and the second hinge , said bearing being coupled with the lever .

[0017] One of a possible embodiment of the invention is that the adj ustment mechanism comprises at least two fins connected to the lever, the said fins being connected to the lever at equal distances from the first hinge and located on both sides of the first hinge . Thus , the fins ensure that the instantaneous velocity center of the lever remains in the correct position .

[0018] A feature of a possible embodiment of the invention is that the said adj ustment mechanism comprises at least one platform to which the other ends of the fins are connected .

[0019] A feature of a possible embodiment of the invention is that it comprises at least one elastic element that connects the adj ustment mechanism to the first region" , the said elastic element essentially being a spring . Thus , the vibrations occurring in the system are effectively isolated by the elastic element , and the adj ustment mechanism is maintained approximately fixed relative to the ground, thereby enabling the excitation vibrations to be managed more efficiently .

[0020] A feature of a possible embodiment of the invention is that the natural frequency of the platform in the excitation axis is lower than the operating frequency range to which the resonator will be tuned . BRIEF DESCRIPTION OF THE FIGURES

[0021] Figure 1 shows the vibration transmission graph of the resonator of the invention .

[0022] Figure 2 shows a superimposed representative view of the motion that occurs when a vibration below the resonance frequency ( f < fp ) is applied from the first region to the resonator of the invention .

[0023] Figure 3 shows a superimposed representative view of the motion that occurs when a vibration at the resonance frequency ( f = fp ) is applied from the first region to the resonator of the invention .

[0024] Figure 4 shows a superimposed representative view of the motion that occurs when a vibration at a frequency between the resonance frequency and the anti-resonance frequency ( fp < f < fz ) is applied from the first region to the resonator of the invention . Figure 5 shows a superimposed representative view of the motion that occurs when a vibration at the anti-resonance frequency ( f = fz ) is applied from the first region to the resonator of the invention .

[0025] Figure 6 shows a superimposed representative view of the motion that occurs when a vibration above the anti-resonance frequency ( f > fz ) is applied from the first region to the resonator of the invention .

[0026] Figure 7a shows a representative view of the resonator of the invention when a vibration at a specific frequency is applied from the first region .

[0027] Figure 7b shows a representative view of the resonator of the invention when the excitation frequency is below the resonance frequency, and the instantaneous velocity center is to the left of the first hinge .

[0028] Figure 7c shows a representative view of the resonator of the invention when the instantaneous velocity center aligns with the first hinge again and resonance is achieved . DETAILED DESCRIPTION OF THE INVENTION

[0029] In this detailed description, the resonator (1) of the invention is explained with examples that serve only to better illustrate the subject and do not impose any limiting effect.

[0030] The invention relates to a resonator (1) capable of resonating with variable-frequency vibrations from a specific source. The resonator (1) of the invention is a lever-type resonator (40) that maximizes the vibration occurring on one side and transmits it to the other side. The invention can be used as a dynamic vibration absorber or for vibration energy harvesting over a wide frequency band in fields where variable-frequency mechanical vibrations occur, including the transportation industry such as automotive, marine, railway, and aerospace, home appliances, the energy sector, the military industry, and the machinery industry. That is, by maximizing the vibration that it receives from one side and transmits it to the other, the resonator can both dampen vibrations on one side and enable energy generation from the maximized vibrations transmitted to the other side.

[0031] The resonator (1) comprises at least one first region (10) . The said first region (10) is the source of vibration and is the area where the vibration initially reaches the resonator (1) . In other words, the resonator (1) is connected to the vibration source via the first region (10) . Accordingly, the first region (10) can be connected to a machine, device, or the like where the vibration is intended to be dampened.

[0032] The resonator (1) comprises at least one second region (20) . The said second region (20) is the area where the vibration is intended to be maximized and transmitted. Accordingly, since the vibration is maximized in the second region (20) , energy can be generated using piezoelectric, magnetic, or other methods. During resonance, the weight (70) at the end of the lever (40) is also subjected to high-amplitude vibrations, allowing energy harvesting through or near the weight (70) by piezoelectric, magnetic, or other methods.

[0033] At least one balancing element (60) is positioned between the first region (10) and the second region (20) . The said balancing element (60) is elastically deformable and, in a possible embodiment of the invention, exhibits spring-like characteristics. The balancing element (60) has a balancing element stiffness (k) and a balancing element damping (c) . The function of the balancing element (60) is to support the loads between the first region (10) and the second region (20) under static conditions. In order to achieve a high resonance amplitude, the damping (c) value of the balancing element should be low, preferably close to zero.

[0034] At least one first hinge (11) is connected to the first region (10) , and at least one second hinge (21) is connected to the second region (20) . At least one bearing (30) is disposed on the facing sides of the first hinge (11) and the second hinge (21) . At least one lever (40) is positioned within the said bearing (30) , and the lever (40) is configured to allow at least partial movement along at least one first axis (I) . The said lever (40) is rigid and moves without deflection within the operating frequency range of the system. The lever (40) is also able to make a rotational movement around the first hinge (11) and the second hinge (21) . The point at which the said rotational movement is made is the instantaneous velocity center (IT) of the lever (40) . That is, it rotates around the instantaneous velocity center (IT) .

[0035] The lever (40) is connected to the first hinge (11) and the second hinge (21) via the bearings (30) . At least one weight (70) can be positioned on one side of the lever (40) . The said weight (70) has a predetermined magnitude and is controlled to ensure that the vibration excitation frequency coincides with the resonance frequency of the system. The resonator (1) comprises at least one adjustment mechanism (50) consisting of at least two fins (51) connected to the lever (40) at least one of their ends, the fins operating in opposite directions to enable the resonator to self-adapt to varying excitation frequencies. In other words, mechanical self- adjusting of the resonator (1) is achieved through rubber or similar friction providing fins (51) . The fins (51) are essentially configured to have impact-transmitting characteristics. The fins (51) are positioned under (or above, or one under and one above) the lever (40) at two points equidistant from the first hinge, facing in opposite directions, and are capable of exerting force on the lever (40) .

[0036] In a current embodiment of the invention, the fins can move independently of each other, whereas in another embodiment, the fins are interconnected via gears or another mechanism, so that the movement of one fin results in the opposite movement of the other .

[0037] The adjustment mechanism (50) comprises at least one platform (52) . The said platform (52) is connected to the fins (51) at both ends. To provide this connection, at the hinge where each fin (51) is connected to the platform (52) , at least one elastic component (kt) and at least one damper (ct) are provided. The elastic component (kt) is a spring, particularly a torsion spring. The damper (ct) is a damping element. The midpoint of the platform (52) is positioned on the central axis of the first hinge ( 11 ) .

[0038] The platform (52) is connected to the first region (10) via at least one elastic element (53) . The said elastic element (53) being a spring.

[0039] The said fins (51) simultaneously generate opposing forces, namely a first force (Fl) and a second force (F2) , along the first axis (I) and the net force resulting from these forces causes the resonator (1) to adjust in the direction of the larger force. In other words, it drives the movement of the lever (40) . When the lever (40) moves along the first axis (I) , the lever ratio changes, which in turn alters the natural frequency of the system. As the lever (40) moves along the first axis (I) and the instantaneous velocity center (II) of the lever (40) aligns with the first hinge (11) , the resonator (1) reaches a resonant state. When the resonator (1) reaches resonant state, the net force on the lever (40) becomes zero, and since the lever (40) ratio does not change, the natural frequency remains constant and equal to the excitation frequency. Thus, the resonant state is achieved. When the excitation frequency changes (i.e., the frequency of the vibration coming from the first region (10) ) , the instantaneous velocity center (II) of the lever (40) changes, and one of the opposing first force (Fl) or second force (F2) acting on the lever (40) becomes larger than the other and the lever (40) then moves in the direction of the larger force, causing the instantaneous velocity center (II) to align with the first hinge (11) . In other words, said adjustment mechanism (50) , through the fins (51) it comprises, can apply force to the lever (40) and drive the lever's (40) movement along the first axis

[0040] (I) , thereby ensuring that the instantaneous velocity center

[0041] (II) of the lever (40) reaches the first hinge (11) .

[0042] Accordingly, whether the excitation frequency decreases or increases, the lever (40) ratio adjusts accordingly, allowing the resonator (1) to always reach a resonant state. The operation of the resonator (1) does not require high-amplitude excitation vibrations or the generation of centrifugal accelerations on the lever (40) . The system can operate at small vibration amplitudes.

[0043] DETAILED DESCRIPTION OF THE FIGURES

[0044] Figure 1 shows the vibration transmission graph of the resonator (1) of the invention. Here, two critical frequencies are fp as the resonance frequency and fz as the anti-resonance frequency. Figure 2 shows a superimposed representative view of the motion that occurs when a vibration below the resonance frequency (f <fp) is applied from the first region (10) to the resonator (1) of the invention, the instantaneous velocity center (II) is located to the left of the first hinge (11) and is indicated by a dashed circle. The lever (40) performs pure rotational motion around this point (II) .

[0045] Figure 3 shows a superimposed representative view of the motion that occurs when a vibration at the resonance frequency (f = fp) is applied from the first region (10) to the resonator (1) of the invention, the instantaneous velocity center (II) is located at the first hinge (11) and is indicated by a dashed circle. The lever (40) performs pure rotational motion around the instantaneous velocity center (II) . Since the excitation occurs at the resonance frequency, the second region (20) , i.e. , the mass in the second region, reaches a high displacement. This is the condition in which the resonator is to be adjusted.

[0046] Figure 4 shows a superimposed representative view of the motion that occurs when a vibration at a frequency between the resonance and anti-resonance frequencies (fp < f< fz) is applied from the first region (10) to the resonator (1) of the invention. The instantaneous velocity center (II) is located between the first hinge (11) and the second hinge (21) and is indicated by a dashed circle .

[0047] Figure 5 shows a superimposed representative view of the motion that occurs when a vibration at the anti-resonance frequency (f = fz) is applied from the first region (10) to the resonator (1) of the invention. The instantaneous velocity center (II) is located at the second hinge (21) and is indicated by a dashed circle. The lever (40) rotates around this point (II) . Since the point of the instantaneous velocity center (II) always has zero velocity, no excitation is transmitted to the mass in the second region (20) in this case. Consequently, the displacement of the mass in the second region (20) is zero.

[0048] Figure 6 shows a superimposed representative view of the motion that occurs when a vibration above the anti-resonance frequency (f > fz) is applied from the first region (10) to the resonator (1) of the invention. The instantaneous velocity center (II) is located to the right of the second hinge (21) and is indicated by a dashed circle. The lever (40) performs pure rotational motion around this point (II) .

[0049] Figures 7a, 7b, and 7c represent the resonator's (1) selfadjustment to the excitation frequency from the first region (10) to reach a resonant state. Figure 7a shows a representative view of the resonator (1) when a vibration at a specific frequency is applied from the first region.

[0050] Figure 7b illustrates the condition in the resonator (1) when the excitation frequency is below the resonance frequency, showing a representative view where the instantaneous velocity center (II) is to the left of the first hinge (11) . When the lever (40) strikes the fins (51) , a first force (Fl) and a second force (F2) are generated proportional to the impact of velocity. In this example, since the excitation frequency is below the resonance frequency, the instantaneous velocity center (II) is located to the left of the first hinge (11) as in Figure 2. Consequently, the velocity and force on the right side of the first hinge (11) are greater (V2 > VI and F2 > Fl) , causing the lever (40) to move to the right.

[0051] The lever (40) continues to move along the axis of the lever (40) until it begins to rotate around the point of the first hinge (11) as shown in Figure 3. Finally, when the rotation center of the lever (40) (the instantaneous velocity center (II) ) aligns with the first hinge (11) , the net force becomes zero, and the resonator (1) reaches the resonant state.

[0052] If the excitation frequency in the first region (10) is below the natural frequency, the lever (40) moves to the right; if it is above, the lever (40) moves to the left to reach the balanced resonant position. When the excitation frequency changes, the instantaneous velocity center (II) of the lever (40) also changes. Consequently, the balance between the first force (Fl) and the second force ( F2 ) generated by the fins (51) is disturbed, and the net force from the fins (51) along the lever (40) axis moves the lever (40) until balance is restored.

[0053] Figure 7c shows a representative view of the resonator (1) in which the instantaneous velocity center (II) aligns again with the first hinge (11) , achieving resonance. In the balanced position, the instantaneous velocity center (II) coincides with the first hinge (11) , and the resonant state is established.

[0054] In order for the second region (20) to have a high resonance amplitude, the damping (c) value between the first region (10) and the second region (20) must be low. The closer the damping value (c) is to zero, the higher the resonance amplitude. The adjustment mechanism (50) has a mass (mt) and is connected to the first region (10) via the elastic element (53) , which has an elastic element stiffness (kv) and elastic element damping (cv) . The natural frequency of the adjustment mechanism mass (mt) must be below the operating frequency range of the resonator (1) .

[0055] The lever ratio of the resonator (1) , that is, the ratio (11 / 12) of the first distance (11) between the first hinge (11) and the second hinge (21) to the second distance (12) between the first hinge (11) and the weight (70) , can change the natural frequency of the resonator (1) by altering the weight (70) at the end of the lever (40) . When resonance is achieved, the instantaneous velocity center (II) of the lever (40) coincides with the first hinge (11) where the excitation occurs, and the impact velocities at the ends of the two fins (51) used for adjustment, i.e., the first velocity (VI) and the second velocity (V2) , as well as the adjustment forces generated from these impacts, i.e. , the first force (Fl) and the second force (F2)— become equal.

[0056] In light of all the foregoing, the invention operates as follows: As can be seen in Figures 2-6, the lever (40) performs rotational motion around a point at each frequency range. This point is the instantaneous velocity center (II) for the lever (40) , and its position depends on the frequency of the vibration applied from the first region (10) . In Figures 2-6, the instantaneous velocity center (II) is located at the center of the circle indicated by dashed lines . In levertype resonators (1) , as the vibration frequency applied from the first region (10) increases, the position of the lever's (40) instantaneous velocity center (II) changes monotonically. As the frequency increases from Figure 2 to Figure 6, the instantaneous velocity center (II) shifts to the right (toward the weight (70) ; left would be toward the balancing element (60) ) . The rightward shift is related to the current placement of the system. If the end of the lever (40) were directed to the left and the second hinge (21) were to the left of the first hinge (11) , the instantaneous velocity center (II) would shift to the left as the frequency increases.

[0057] In Figure 3, the resonator (1) is in the resonant state, and at the resonance frequency (fp) , the instantaneous velocity center (II) is located at the first hinge (11) where the vibration excitation is applied. Since the first hinge (11) and the second hinge (21) to which the lever (40) is connected allow both rotation and translation along the lever axis (I) , the lever (40) can be shifted along the first axis (I) to change the position of the instantaneous velocity center (II) . Therefore, when the excitation frequency changes, the lever (40) shifts so that the instantaneous velocity center (II) aligns with the first hinge (11) , restoring resonance. In other words, as the excitation frequency changes, the resonance frequency follows it, so that the system remains in resonance at all times.

[0058] To align the instantaneous velocity center (II) of the lever (40) with the first hinge (11) , both vertical and horizontal forces are applied to the lever (40) at two points equidistant from the first hinge (11) . These forces are applied by the fins (51) in the adjustment mechanism (50) . While the vertical forces do not affect the lever ratio of the lever (40) , the horizontal forces— i.e., the first force (Fl) and the second force (F2)— can shift the lever (40) along the first axis (I) , thereby changing the lever ratio. In other words, these forces enable movement of the lever (40) along the first axis (I) .

[0059] These forces are proportional to the velocities at the points where they are applied. As the distance from the instantaneous velocity center (II) increases, the linear velocity also increases. Therefore, of the two points equidistant from the first hinge (11) , the point farther from the instantaneous velocity center (II) will have a higher velocity, and the impact force at the fin tip located farther from the instantaneous velocity center will also be greater. This causes the lever (40) to move in the direction indicated by the farther fin tip, and the instantaneous velocity center (II) will move in the same direction .

[0060] When the instantaneous velocity center (II) coincides with the first hinge (11) where the vibration excitation is applied, the two horizontal forces become equal, thereby adjusting the system to the resonant frequency. This process is illustrated in Figures 7a, 7b, and 7c.

[0061] The platform (52) carrying the fins (51) is connected to the first region (10) via an elastic element (53) , and the natural frequency of this platform (52) in the excitation direction is well below the operating frequency range in which the resonator (1) described in the invention is to be adjusted. Therefore, within the resonator's (1) operating frequency range, the platform (52) moves at an amplitude much lower than the excitation amplitude of the first region (10) , behaving almost as if it were stationary. Since the fins (51) are positioned on the platform (52) , they also appear fixed relative to the ground. Consequently, impact forces transmitted to the lever (40) at the tips of the fins (51) are proportional to the distances from the instantaneous velocity center (II) of the lever (40) to the fins (51) . Thus, during its movement, the lever (40) strikes both fins (51) . At the moment of contact, due to the fins (51) engaging the lever axis (I) at a shallow angle, horizontal forces along the first axis (I) are generated, proportional to the impact velocities, i.e. , a first velocity (VI) and a second velocity (V2) , resulting in a first force (Fl) and a second force (F2) . Since the force at the higher-velocity point is greater, a net force pushing the lever (40) in that direction is produced, causing the lever (40) to move accordingly.

[0062] The resonator (1) can match its natural frequency to the excitation frequency using the drive vibrations from the first region (10) without any additional energy input. In other words, if the resonator (1) is mounted on another vibrating main system, it automatically adjusts to the frequency at which the main system vibrates, acting like a dynamic vibration absorber. Therefore, it can be used to reduce the vibration level of the main system. Even if the main system's vibration frequency changes, the resonator (1) follows the varying frequency, functioning as a self-adjusting dynamic vibration absorber.

[0063] The resonator (1) can reach high amplitudes due to vibrations from the first region (10) being in resonance, making it suitable for energy harvesting. Resonator systems used in the current state of the art for energy harvesting; effective operation occurs only when the drive matches the natural frequency. However, if the natural frequency of these conventional resonators is fixed and the excitation frequency differs from the natural frequency, the vibration amplitude decreases, and efficiency drops. In contrast, the resonator (1) of the present invention can adjust itself to different drive frequencies, enabling effective operation not only at a single frequency but also across variable drive frequencies.

[0064] In an alternative hinge configuration, the insides of the hinges have a nut-like helical structure, and the lever body is in the form of a jaw (rod) . The fins (51) are positioned on either side to rotate the jaw in two opposite directions, and the torques the fins (51) apply to the jaw are proportional to their distances from the instantaneous center of velocity (II) . If the net torque is not zero, the jaw rotates along its axis, and when the instantaneous center of velocity (II) aligns with the first hinge (11) , balance is achieved. In balanced state, the system reaches resonance. Instead of a nut-like interior and jaw lever (40) body, ball screws and threaded shafts can also be used. Accordingly, a resonator (1) has been provided that can adjust itself to the mechanical vibration excitation frequency in a passive adaptive manner (without including sensors, actuators, control circuits, PLCs, or computers, or any other electronic control equipment and without requiring external electrical energy) ; that is, when the excitation frequency changes, it autonomously follows said frequency and continuously remains in a resonant state. As a result, the use of the aforementioned devices can be eliminated, and the cost, system complexity, and weight are reduced, while the system continuously adapts to varying frequencies and maintains the resonant state.

[0065] Thus, the resonator (1) is enabled to operate solely by using the energy of the mechanical vibrations driving it (i.e., from a vibration source of an object, machine, or the like, which is connected to the first region (10) ) without requiring any external electrical energy input, power supply, or battery. Accordingly, energy savings are achieved.

[0066] The scope of protection of the invention is defined in the appended claims and should by no means be limited to what is described in this detailed description for exemplary purposes. It is clear that a person skilled in the art could, without departing from the main concept of the invention, develop similar configurations based on the foregoing description. REFERENCESS SHOWN IN THE FIGURES

[0067] 1 Resonator

[0068] 10 First Region

[0069] 11 First Hinge

[0070] 20 Second Region

[0071] 21 Second Hinge

[0072] 30 Bearing

[0073] 40 Lever

[0074] 50 Adjustment Mechanism

[0075] 51 Fin

[0076] (kt) Elastic Component

[0077] (ct) Damper

[0078] 52 Platform

[0079] 53 Elastic Element

[0080] (kv) Elastic Element Stiffness

[0081] (cv) Elastic Element Damping

[0082] (mt) Adjustment Mechanism Mass 60 Balancing Element

[0083] (k) Balancing Element Stiffness

[0084] (c) Balancing Element Damping

[0085] 70 Weight

[0086] (I) First axis

[0087] (II) Instantaneous Velocity Center

[0088] (Fl) First Force

[0089] (F2) Second Force

[0090] (VI) First Velocity

[0091] (V2) Second Velocity

[0092] (11) First Distance

[0093] (12) Second Distance

Claims

CLAIMS1. A resonator (1) comprising at least one first region (10) and at least one second region (20) disposed opposite to each other to maximize the incoming vibration, at least one first hinge (11) connected to the first region (10) , at least one second hinge (21) connected to the second region (20) , and at least one lever (40) connected to the first hinge (11) and the second hinge (21) so as to be at least partially movable along at least one first axis (I) , wherein the resonator comprises at least one adjustment mechanism(50) positioned between the first region (10) and the second region (20) to continuously maintain resonance by self- adjusting to follow changes in the excitation vibration frequency, and wherein the adjustment mechanism (50) is configured to align the instantaneous velocity center (II) of the lever (40) at a predetermined position in the vicinity of the first hinge (11) depending on the varying excitation vibration frequency.

2. A resonator (1) according to claim 1, wherein it uses only the energy of the vibration excitation coming from the first region (10) while self-adjusting to the varying vibration excitation frequency, without requiring any other external energy source (electrical, magnetic, etc. ) .

3. A resonator (1) according to claim 1, wherein it comprises at least one bearing (30) provided in the first hinge (11) and second hinge (21) , said bearing being coupled with the lever ( 40 ) .

4. A resonator (1) according to claim 1, wherein the adjustment mechanism (50) comprises at least two fins (51) coupled with the lever (40) .

5. A resonator (1) according to claim 4, wherein the said fins(51) are connected to the lever (40) so they are equidistant from the first hinge (11) and remain on both sides of the first hinge (11) .

6. A resonator (1) according to claim 1, wherein the said adjustment mechanism (50) comprises at least one platform (52) to which the other ends of the fins (51) are coupled.

7. A resonator (1) according to claim 1, wherein it comprises at least one elastic element (53) that connects the adjustment mechanism (50) to the first region (10) .

8. A resonator (1) according to claim 7, wherein the said elastic element (53) is essentially a spring.

9. A resonator (1) according to claim 8, wherein the natural frequency of the said platform (52) in the direction of excitation is below the operating frequency range at which the resonator (1) is to be adjusted.

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