Broadband vibration absorber, installation assembly of broadband vibration absorber and vehicle

Abstract

The utility model provides a broadband vibration absorber, a mounting assembly of the broadband vibration absorber and a vehicle, and belongs to the technical field of vehicles. The broadband vibration absorber comprises a mass block, an inner shaft and a rubber bushing; the inner shaft is coaxially arranged in a center hole of the mass block in a penetrating mode. The rubber bushing is vulcanized between the mass block and the inner shaft; the rubber bushing is divided into the first vibration reduction rubber section and the second vibration reduction rubber section in the axis direction of the rubber bushing, the hardness of the first vibration reduction rubber section is larger than that of the second vibration reduction rubber section, different vibration energy can be absorbed, and therefore broadband vibration absorption is achieved. Through the hardness segmented design of the rubber bushings and the installation directions of the rubber segments with different hardness, absorption of different vibration frequencies can be achieved, the purposes of broadband vibration absorption, lightweight design, rapid adaptation to frequency changes and simplification of the installation and adjustment process are achieved, the NVH performance of a vehicle can be effectively improved, and the service life of the vehicle is prolonged. The problems that an existing vibration absorber is narrow in frequency bandwidth, too large in weight and insufficient in frequency adaptability are solved.

Description

TECHNICAL FIELD

[0001] The utility model belongs to the vehicle technical field, concretely relates to a wideband vibration absorber, the mounting assembly of wideband vibration absorber and vehicle. BACKGROUND

[0002] In the field of vehicle engineering, vibration control is one of the key technologies to improve vehicle comfort and structural integrity. During the operation of the vehicle, components such as the powertrain, transmission system, and tires will generate excitation energy, causing the vehicle to vibrate. In order to effectively suppress these vibrations, a vibration absorber is usually designed on the vibration transmission path or the response structure. The main function of the vibration absorber is to reduce the vibration response of the system by absorbing vibration energy, thereby improving the NVH (Noise, Vibration and Harshness) performance of the vehicle.

[0003] However, the existing vibration absorber design has the following technical problems:

[0004] (1) Narrow frequency bandwidth: Traditional single vibration absorbers can usually only effectively absorb vibration energy near the design frequency, with an effective frequency bandwidth of ±3Hz of the design frequency. This narrow-band vibration absorption characteristic makes the vibration absorber only work in a limited frequency range, unable to cover a wider frequency range, resulting in limited vibration suppression effect on other frequencies in the vehicle system.

[0005] (2) Weight problem of multi-frequency vibration absorber: In order to expand the frequency range of the vibration absorber, the existing technology usually adopts a multi-frequency vibration absorber design. The multi-frequency vibration absorber achieves the absorption of vibrations of different frequencies by increasing multiple mass blocks, but this design significantly increases the overall weight of the vibration absorber, which is contrary to the trend of lightweight design of vehicles, and increases the load and energy consumption of the vehicle.

[0006] (3) Insufficient frequency adaptability due to production tolerance: During vehicle production, due to manufacturing tolerance, the natural frequency of the vehicle system may shift. The existing vibration absorber design lacks the ability to quickly adapt to frequency changes, resulting in the vibration absorber may not effectively match the vibration characteristics of the system in actual application, thereby reducing the damping effect. In addition, the adjustment process of the traditional vibration absorber is complex, and it is difficult to complete the frequency re-matching in a short time, affecting the production efficiency and performance verification of the vehicle.

[0007] In summary, the existing vibration absorber design has obvious deficiencies in frequency bandwidth, weight control, and frequency adaptability, and there is an urgent need for a vibration absorber structure that can effectively absorb vibration energy in a wide frequency range and quickly adapt to frequency changes to meet the higher requirements for vibration control in vehicle engineering. UTILITY MODEL CONTENTS

[0008] The utility model discloses an embodiment provides a broadband vibration absorber, the mounting assembly of broadband vibration absorber and vehicle, to be able to effectively absorb vibration energy in broadband range, and can quickly adapt to frequency change.

[0009] In one embodiment, a first end of the first damping rubber segment close to the mass block is provided with a counterbore coaxial with the central hole of the mass block.

[0010] In one embodiment, a second end of the second damping rubber segment close to the mass block is provided with a protruding portion coaxial with the central hole of the mass block.

[0011] The protruding portion is used to offset the center of gravity of the mass block to the first damping rubber segment or the second damping rubber segment.

[0012] In one embodiment, a distance L11 between an axial end surface of the first damping rubber segment and a first end surface of the mass block is 25-35% of the total axial length LL of the mass block, and the end surface of the first damping rubber segment does not protrude beyond a step surface formed by the counterbore.

[0013] In one embodiment, an axial end surface of the second damping rubber segment does not protrude beyond an outer end surface of the protruding portion, and a distance L22 between the axial end surface of the second damping rubber segment and a second end surface of the mass block is 3-8% of the total axial length LL of the mass block.

[0014] In combination with the first aspect, in an implementable manner, the axial length LL2 of the protruding portion is 15-25% of the total axial length LL of the mass. The size of the counterbore and the protruding portion can be controlled to precisely control the degree of gravity center deviation, so that the gravity center can be more accurately landed on the first damping rubber segment or the second damping rubber segment.

[0015] In combination with the first aspect, in an implementable manner, the axial length of the first damping rubber segment is greater than the axial length of the second damping rubber segment. This combination of damping rubber segments with different lengths can more accurately cope with the frequency and amplitude of vibration in different directions, prolonging the service life of the damper.

[0016] In combination with the first aspect, in an implementable manner, the axial length L1 of the first damping rubber segment is 60-70% of the total axial length L of the rubber bushing; and the axial length L2 of the second damping rubber segment is 30-40% of the total axial length L of the rubber bushing. The purpose of this embodiment is to precisely control the gravity center deviation by controlling the size of the rubber bushing with different hardnesses: so that the gravity center can be more accurately landed on the first damping rubber segment or the second damping rubber segment.

[0017] In combination with the first aspect, in an implementable manner, the total axial length L of the rubber bushing is 60-70% of the total axial length LL of the mass. By designing the size of the total axial length of the rubber bushing and the total axial length of the mass, the tightness of the connection between the mass and the rubber bushing can be ensured, and at the same time, the extrusion space for the gravity center deviation of the mass can be left, so as to achieve the purpose of moving the mass gravity center of the vibration absorber when different mounting surfaces are installed, and then realize the vibration absorption effect of different bushing segment hardnesses on different frequency vibration energies.

[0018] The wideband vibration absorber provided by the utility model has the advantages that: (1) in view of the problem of narrow frequency bandwidth of a single vibration absorber, the rubber bushing is divided into the first damping rubber segment and the second damping rubber segment with different hardnesses, so that the vibration absorber can absorb vibration energy in different frequency ranges. The first damping rubber segment has relatively large hardness and is suitable for absorbing high-frequency vibration; and the second damping rubber segment has relatively small hardness and is suitable for absorbing low-frequency vibration. This design enables the vibration absorber to absorb vibration energy in a wide frequency range, improving the applicability and effectiveness of the vibration absorber and solving the problem of narrow frequency bandwidth of a traditional vibration absorber.

[0019] (2) in view of the weight problem of a multi-frequency vibration absorber, the wideband vibration is realized by changing the hardness of the rubber bushing, so that the weight of the vibration absorber is reduced, and the design trend of vehicle lightening is met.

[0020] (3) In view of the problem that the existing vibration absorber design lacks quick frequency adaptation, the vibration absorber can be installed by adjusting the installation orientation of the rubber bushing according to different hardnesses to adapt to different vibration environments, without a complex adjustment process, thereby enhancing the flexibility and applicability of the vibration absorber.

[0021] In a second aspect, the utility model embodiment further provides a mounting assembly of the wide-frequency vibration absorber, which comprises the wide-frequency vibration absorber and a mounting body, the mounting body is provided with a mounting surface, the mounting surface is an inclined surface, the wide-frequency vibration absorber is fixed on the mounting surface through a connecting bolt penetrating the inner shaft, and the included angle θ between the center line of the connecting bolt and the perpendicular line perpendicular to the mounting surface is 3-6°. Different installation orientations are adjusted according to the different hardness differences of the rubber bushing, different vibration frequencies are generated under different installation modes, the frequency of the vibration absorber is quickly adjusted, and the purpose of widening the vibration absorption frequency bandwidth of the vibration absorber is achieved, so that the technical effect that the vibration absorber can quickly adapt to frequency changes is achieved. Through the design of the installation angle of the vibration absorber, the frequency difference caused by manufacturing tolerances in the vehicle production process can also be quickly adapted, and real-time adjustment can be achieved through simple disassembly and assembly, thereby improving the production efficiency and performance verification of the vehicle.

[0022] In a third aspect, the utility model embodiment further provides a vehicle comprising the wide-frequency vibration absorber or the mounting assembly of the wide-frequency vibration absorber.

[0023] The vehicle provided by the application achieves the purposes of wide-frequency vibration absorption, lightweight design, quick frequency adaptation, and simplifying the installation and adjustment process by adopting the vibration absorber based on the hardness segmentation, so that the vibration absorber has a wide application prospect in the vehicle engineering field and can effectively improve the NVH performance of the vehicle, thereby meeting the higher requirements for vibration control in vehicle engineering and solving the problems of narrow frequency bandwidth, excessive weight, and insufficient frequency adaptability of the existing vibration absorber. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 A structural schematic view of the wide-frequency vibration absorber provided by the utility model embodiment is shown in the figure.

[0025] Figure 2 The rubber bushing is arranged along Figure 1 the A-A line in the figure.

[0026] Figure 3 A three-dimensional structural schematic view of the wide-frequency vibration absorber provided by the utility model embodiment is shown in the figure. Figure 1 ;

[0027] Figure 4 A three-dimensional structural schematic view of the wide-frequency vibration absorber provided by the utility model embodiment is shown in the figure. Figure 2 ;

[0028] Figure 5The mounting assembly schematic view of the wideband vibration absorber provided by the embodiment of the present utility model (the end with large hardness faces the mounting surface);

[0029] Figure 6 The mounting assembly schematic view of the wideband vibration absorber provided by the embodiment of the present utility model (the end with small hardness faces the mounting surface);

[0030] Figure 7 The mounting vibration absorption curve diagram of the wideband vibration absorber with different hardness directions provided by the embodiment of the present utility model;

[0031] Mark explanation:

[0032] 1, mass block; 11, counterbore; 12, protruding part; 2, inner shaft; 3, connecting bolt; 4, rubber bushing; 41, first damping rubber section; 42, second damping rubber section; 5, mounting surface; 6, inner tube. Specific implementation

[0033] In order to make the technical problems, technical solutions and beneficial effects of the present utility model clearer and more apparent, the present utility model will be further described in detail below in combination with the drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present utility model and do not limit the present utility model.

[0034] The same as the understanding in the "Examination Guidelines", in the present application, the expressions "greater than", "less than", "exceed" are understood as not including the number; the expressions "above", "below", "within" are understood as including the number. For example, the hardness of the first damping rubber section is greater than the hardness of the second damping rubber section, which means that the hardness of the two rubber sections is different.

[0035] It should be further pointed out that, since the mass block, the inner shaft and the rubber bushing are coaxially arranged in the present application, the axes of the three components coincide, therefore the "axial direction" involved in the claims and description of the present utility model is uniquely determined.

[0036] Please refer to Figures 1 to 4 for the description of the wideband vibration absorber provided by the present utility model. The wideband vibration absorber comprises: a mass block 1 with a central hole, an inner shaft 2 and a rubber bushing 4; the inner shaft 2 is coaxially arranged in the central hole of the mass block 1; the rubber bushing 4 is vulcanized between the mass block 1 and the inner shaft 2; the rubber bushing 4 is divided into a first damping rubber section 41 and a second damping rubber section 42 along its axial direction, the hardness of the first damping rubber section 41 is greater than the hardness of the second damping rubber section 42; when the first damping rubber section 41 faces the mounting surface 5 or the second damping rubber section 42 faces the mounting surface 5, different vibration energies can be absorbed, realizing wideband vibration absorption. Figure 2 The center line a is the boundary line of the first damping rubber section 41 and the second damping rubber section 42.

[0037] The broadband vibration absorber provided by the utility model has the beneficial effects that, compared with the prior art,

[0038] (1) In view of the problem of narrow frequency bandwidth of a single vibration absorber, the rubber bushing 4 is divided into the first damping rubber section 41 and the second damping rubber section 42 with different hardnesses, so that the vibration absorber can absorb vibration energy in different frequency ranges. The first damping rubber section 41 has relatively large hardness and is suitable for absorbing high-frequency vibration; the second damping rubber section 42 has relatively small hardness and is suitable for absorbing low-frequency vibration. This design enables the vibration absorber to absorb vibration energy in a wider frequency range, improving the applicability and effectiveness of the vibration absorber. The problem of narrow frequency bandwidth of a traditional vibration absorber is solved.

[0039] Rubber with relatively low hardness: better absorption effect on low-frequency vibration, because low-hardness rubber can absorb more vibration energy when deformed, effectively reducing the influence of low-frequency vibration.

[0040] Rubber with relatively high hardness: stronger inhibition ability on high-frequency vibration, but poor effect on low-frequency vibration. High-hardness rubber can provide better damping effect under high-frequency vibration, but has poor absorption ability on low-frequency vibration.

[0041] When selecting rubber materials, the hardness of the rubber needs to be determined according to the specific use environment and the characteristics of the vibration frequency. For occasions that need to absorb low-frequency vibration, rubber with relatively low hardness should be selected; for occasions that need to suppress high-frequency vibration, rubber with relatively high hardness should be selected. In addition, the thickness and shape of the rubber also affect its damping effect. Rubber with larger thickness can absorb more vibration energy, and rubber parts with circular or spherical shape have better damping effect.

[0042] The hardness of rubber is usually measured by a Shore hardness tester. The selection of the rubber bushing 4 of the present application is as follows: for example, for the first damping rubber section 41 with relatively high hardness, measured by Shore hardness, medium-hardness rubber can be selected, for example, nitrile rubber, chlorobutyl rubber with a hardness of 40HA-90HA; ethylene-propylene-diene rubber, fluororubber with a hardness of 60HA-80HA.

[0043] For the second damping rubber section 42 with relatively low hardness, softer rubber can be selected, for example, silicone rubber with a hardness of 20HA-60HA; natural rubber with a hardness of 30HA-90HA; nitrile rubber, chlorobutyl rubber with a hardness of 40HA-90HA.

[0044] The hardness value unit HA above represents the Shore A hardness series.

[0045] (2) In order to solve the problem of the weight of the multi-frequency vibration absorber, the hardness of the rubber bushing 4 is changed to achieve wide-frequency vibration absorption, thereby avoiding the addition of an extra mass block 1, reducing the weight of the vibration absorber, and meeting the design trend of vehicle lightening.

[0046] (3) In order to solve the problem of the lack of quick adaptation to frequency changes in the existing vibration absorber design, the vibration absorber can be installed by adjusting the installation orientation of the rubber bushing 4 according to the hardness to adapt to different vibration environments, without the need for complex adjustment processes, thereby enhancing the flexibility and applicability of the vibration absorber.

[0047] This wide-frequency vibration absorber has many advantages in practical applications. Due to its unique structural design, it can flexibly adjust the vibration absorption mode according to different vibration environments. For example, in some industrial equipment, when the equipment produces low-frequency vibrations, the second damping rubber section 42 can be oriented towards the mounting surface 5 to effectively absorb low-frequency vibration energy, thereby reducing noise, wear and tear, and possible malfunctions caused by high-frequency vibrations of the equipment.

[0048] When facing some precision instruments and equipment, these devices often produce high-frequency and small-amplitude vibrations. In this case, it is more appropriate to orient the first damping rubber section 41 towards the mounting surface 5. The second damping rubber section 42 has a higher hardness and its elastic properties can more accurately adapt to high-frequency vibrations, efficiently absorbing high-frequency vibration energy and ensuring the stable operation of precision instruments, thereby improving the measurement accuracy and service life of the instruments.

[0049] In addition, in the automotive field, this wide-frequency vibration absorber also has broad application prospects. Cars produce various vibrations during driving, such as engine vibrations, body vibrations caused by road bumps, etc. The wide-frequency vibration absorber can be installed near the support part of the engine or the chassis suspension system. When the vehicle is driving on different road conditions, the installation mode of the wide-frequency vibration absorber can be adjusted according to the actual vibration situation, effectively improving the ride comfort of the vehicle, while also reducing the fatigue damage between automobile parts caused by long-term vibration, thereby prolonging the overall service life of the vehicle.

[0050] In some embodiments, referring to Figure 2As shown, the first end of the mass block 1 close to the first damping rubber section 41 is provided with a counterbore 11 coaxial with the central hole of the mass block 1. This structure of providing a counterbore 11 at one end of the mass block 1 can realize the center of gravity offset to the first damping rubber section 41 or the second damping rubber section 42 during installation. The mass block 1 is provided with a counterbore 11 at one end, so that the two ends of the mass block 1 form an asymmetric structure. This asymmetric structure design realizes the following effects for the vibration absorber: first, it is beneficial to the center of gravity offset and realizes the wideband vibration absorption effect. This asymmetric structure design makes the center of gravity of the mass block 1 can be offset to the rubber bushing 4 with different hardness according to the different installation directions. Specifically, when the side of the counterbore 11 faces the mounting surface 5, the center of gravity will be offset to the rubber bushing 4 with higher hardness (such as the first damping rubber section 41 with a hardness of 60HA); when the end without the counterbore 11 faces the mounting surface 5, the center of gravity will be offset to the rubber bushing 4 with lower hardness (such as the second damping rubber section 42 with a hardness of 45HA).

[0051] Because the rubber bushing 4 with different hardness has different absorption effects on different frequency vibrations, the rubber bushing 4 with lower hardness is more suitable for absorbing low-frequency vibrations, and the rubber bushing 4 with higher hardness is more suitable for absorbing high-frequency vibrations. By adjusting the center of gravity offset direction of the mass block 1, the vibration absorber can effectively absorb vibration energy in different frequency ranges, thereby realizing wideband vibration absorption.

[0052] Second, the installation flexibility can quickly adapt to frequency changes: due to the design of the counterbore 11 or the protruding part 12, the vibration absorber can quickly adapt to different vibration environments by simply adjusting the installation direction. For example, when the natural frequency of the vehicle system changes due to manufacturing tolerances, the installation direction of the vibration absorber can be adjusted to offset the center of gravity to the appropriate rubber bushing 4, so that the vibration characteristics of the system can be quickly matched.

[0053] Third, the difference design of the two ends of the mass block 1 facilitates the differentiation of the hardness of the two ends, so as to realize the purpose of quickly adjusting the frequency and reducing the adjustment time. When one state installation does not meet the frequency requirement, the other orientation installation can be quickly and accurately completed by disassembling and reassembling, avoiding the installation replacement adjustment time caused by the same installation orientation of the two times. The traditional vibration absorber needs complex adjustment when the frequency changes, but the frequency matching can be realized by simply adjusting the installation direction, reducing the adjustment time and process complexity, improving the production efficiency and performance verification speed of the vehicle.

[0054] Optionally, referring to Figure 2As shown, the second end of the mass block 1 close to the second damping rubber section 42 has a protruding part 12 coaxial with the center hole of the mass block 1, which can realize the gravity center offset on the first damping rubber section 41 or the second damping rubber section 42. The asymmetric structure design of the embodiment with the counterbore 11 at one end of the mass block 1 achieves the same effect, which will not be described here.

[0055] Optionally, referring to Figure 2 As shown, the first end of the mass block 1 close to the first damping rubber section 41 is provided with a counterbore 11 coaxial with the center hole of the mass block 1, and the second end of the mass block 1 close to the second damping rubber section 42 has a protruding part 12 coaxial with the center hole of the mass block 1; which can realize the gravity center offset on the first damping rubber section 41 or the second damping rubber section 42. The embodiment designs the counterbore 11 at one end of the mass block 1 and the protruding part 12 at the other end, which has the effect of only designing the counterbore 11 or the protruding part 12, which will not be described here. Of course, compared with only designing the counterbore 11 or the protruding part 12 at one end, the two-end design can improve the accuracy of gravity center offset adjustment and achieve the best damping effect.

[0056] Moreover, the design of the counterbore 11 and the protruding part 12 at both ends of the mass block 1 avoids the problem of unstable gravity center. If both ends of the mass block 1 are designed as protrusions or counterbores 11, it may cause unstable gravity center or extrusion deformation. The embodiment ensures the stability of the gravity center offset through the structure of one end protruding and the other end counterbore 11, avoiding unnecessary deformation or failure of the vibration absorber during vibration.

[0057] Therefore, the design of the counterbore 11 and the protruding structure at both ends of the mass block 1, by realizing the gravity center offset to the rubber bushing 4 of different hardness, brings many beneficial effects such as wide frequency vibration absorption, fast adaptation to frequency changes, optimized vibration absorption effect, lightweight design, enhanced flexibility and applicability, etc. This design not only solves the problems of narrow frequency bandwidth, excessive weight and insufficient frequency adaptability of traditional vibration absorbers, but also significantly improves the application value of the vibration absorber in vehicle engineering, meeting the higher requirements of vehicle vibration control.

[0058] In some embodiments, referring to Figure 2 As shown, the distance L11 from the axial end face of the first damping rubber section 41 to the first end face of the mass block 1 is 25-35% of the total axial length LL of the mass block 1, and the end face of the first damping rubber section 41 does not protrude on the step face formed by the counterbore 11. In simple terms, the embodiment reserves a section of the rubber bushing 4 blank area at one end of the counterbore 11, that is, the inner shaft 2 and the mass block 1 are not completely connected by vulcanization, leaving a rubber extrusion space for the gravity center offset of the mass block 1.

[0059] It is illustrated that the total axial length LL of the mass 1 includes the length of the protrusion 12 and the axial length of the counterbore 11.

[0060] In some embodiments, referring to Figure 2 It is illustrated that the axial end surface of the second damping rubber segment 42 does not protrude from the outer end surface formed by the protrusion 12, and the distance L22 from the axial end surface of the second damping rubber segment 42 to the second end surface of the mass 1 is 3-8% of the total axial length LL of the mass 1. Similarly, a rubber vulcanization blank area is also reserved between the protrusion 12 and the inner shaft 2 to provide a rubber extrusion space for the gravity center offset of the mass 1.

[0061] In some embodiments, referring to Figure 2 It is illustrated that the axial length LL2 of the protrusion 12 is 15-25% of the total axial length LL of the mass 1. Among them, the axial length LL1 of the counterbore 11 is 10-15% of the total axial length LL of the mass 1.

[0062] The purpose of the present embodiment is to achieve precise control of the gravity center offset by controlling the size of the protrusion 12 and the counterbore 11: the size design (such as the depth of the counterbore 11, the height of the protrusion, the diameter, etc.) of the counterbore 11 and the protrusion 12 can accurately control the degree of gravity center offset, so that the gravity center can fall more accurately on the first damping rubber segment 41 or the second damping rubber segment 42. For example, when the gravity center needs to be more offset to the first damping rubber segment 41, the depth of the counterbore 11 near the first damping rubber segment 41 can be appropriately increased or the height of the protrusion 12 near the second damping rubber segment 42 can be appropriately reduced; conversely, when the gravity center is desired to be offset to the second damping rubber segment 42, the depth of the counterbore 11 can be reduced or the height of the protrusion 12 can be increased. In this way, the position of the gravity center can be flexibly adjusted according to the actual damping requirement, so as to achieve the best damping effect.

[0063] Among them, the protrusion 12 is a rotating body with the axis of the mass 1 as the rotating shaft, and the shape can be a circular truncated cone or a circular cylinder. The diameter of the protrusion 12 is smaller than the diameter of the mass 1.

[0064] In some embodiments, referring to Figure 2 It is illustrated that the axial length of the first damping rubber segment 41 is greater than the axial length of the second damping rubber segment 42. This is beneficial to achieve differentiated damping effect in different directions. Since the axial length of the first damping rubber segment 41 is longer, it can provide a larger deformation space when bearing axial vibration, thereby effectively absorbing and buffering larger axial impact force. The second damping rubber segment 42 has lower hardness, so the axial length is designed to be relatively short to avoid deformation failure. This combination of damping rubber segments with different lengths can more accurately cope with the frequency and amplitude of vibration in different directions, prolonging the service life of the damper.

[0065] In some embodiments, referring to Figure 2 As shown, the axial length L1 of the first damping rubber segment 41 is 60-70% of the total axial length L of the rubber bushing 4; the axial length L2 of the second damping rubber segment 42 is 30-40% of the total axial length L of the rubber bushing 4. Similarly, the purpose of the present embodiment is to achieve precise control of the center of gravity shift by controlling the different hardness sizes of the rubber bushing 4: so that the center of gravity can be more accurately on the first damping rubber segment 41 or the second damping rubber segment 42. For example, when the center of gravity needs to be shifted more to the first damping rubber segment 41, the depth of the counterbore 11 near the end of the first damping rubber segment 41 can be appropriately increased or the height of the raised portion 12 near the end of the second damping rubber segment 42 can be appropriately reduced; conversely, when the center of gravity is desired to be shifted to the second damping rubber segment 42, the depth of the counterbore 11 can be reduced or the height of the raised portion 12 can be increased. In this way, the position of the center of gravity can be flexibly adjusted according to the actual damping requirements, so as to achieve the best damping effect.

[0066] In some embodiments, referring to Figure 2 As shown, the total axial length L of the rubber bushing 4 is 60-70% of the total axial length LL of the mass block 1. By designing the total axial length of the rubber bushing 4 and the total axial length of the mass block 1, the tightness of the connection between the mass block 1 and the rubber bushing 4 can be ensured, and at the same time, the extrusion space for the center of gravity shift of the mass block 1 can be left, so as to achieve the purpose of moving the center of gravity of the vibration absorber when different mounting surfaces 5 are used, and to realize the vibration absorption effect of different bushing segment hardnesses on different frequency vibration energies.

[0067] As shown in Figure 2 Overall, the wideband vibration absorber provided by the present application further comprises an inner tube 6 that is interference-fitted to the wall of the central hole of the mass block 1, the inner tube 6 has a supporting effect on the mass block 1, the rubber bushing 4 is vulcanized between the inner tube 6 and the inner shaft 2, and when mounted, the connecting bolt 3 passes through the central hole of the inner shaft 2, and the inner shaft 2 has a supporting effect on the connecting bolt 3.

[0068] By designing the rubber bushing 4 with segmented hardness, the asymmetric design of the counterbore 11 and the raised portion 12 structure at both ends of the mass block 1, and the size design, the effective frequency bandwidth of the vibration absorber is expanded from the traditional ±3Hz to ±5Hz, which significantly improves the applicability and effectiveness of the vibration absorber.

[0069] For the size control involved in the present application, which has not been enumerated one by one, the corresponding values of each size are as follows:

[0070] Referring to Figure 1 and Figure 2 When the axial length LL of the mass block 1 is 100mm and the diameter D is 110mm, the corresponding values of each size are as follows:

[0071] The distance L11 between the end face of the first damping rubber section 41 and the first end face of the mass 1 is 25-35 mm. For example, L11 is 25 mm, 26 mm, 27 mm, 30 mm, 32 mm, 33 mm, 35 mm, etc.

[0072] The distance L22 between the end face of the second damping rubber section 42 and the second end face of the mass 1 is 3-8 mm. For example, L22 is 3 mm, 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, etc.

[0073] The axial length LL2 of the protrusion 12 is 15-25 mm. LL2 is 15 mm, 16 mm, 19 mm, 20 mm, 21 mm, 23 mm, 25 mm, etc.

[0074] The axial length LL1 of the counterbore 11 is 10-15 mm, and the diameter d of the counterbore 11 is 50-65 mm; LL1 is 10 mm, 12 mm, 14 mm, 15 mm, and the diameter d of the counterbore 11 is 50 mm, 60 mm, 62 mm, 65 mm.

[0075] The total axial length L of the rubber bushing 4 is 60-70 mm. L is 60 mm, 62 mm, 65 mm, 68 mm, 70 mm, etc.

[0076] The axial length L1 of the first damping rubber section 41 is 36-50 mm; L1 is 35 mm, 37 mm, 40 mm, 45 mm, 50 mm.

[0077] The axial length L2 of the second damping rubber section 42 is 18-28 mm; L2 is 18 mm, 20 mm, 22 mm, 25 mm, 28 mm, etc.

[0078] The hardness of the first damping rubber section 41 is 55-65 HA, and the hardness of the second damping rubber section 42 is 40-50 HA; for example, the hardness of the first damping rubber section 41 is 55 HA, 58 HA, 60 HA, 62 HA, 65 HA, etc.; the hardness of the second damping rubber section 42 is 40 HA, 45 HA, 50 HA, etc.

[0079] For example, referring to Figure 5 , Figure 6 and Figure 7 , the included angle between the center line of the connecting bolt 3 and the perpendicular to the mounting surface 5 is 3-6°, when the hardness of the second damping rubber section 42 is 45 HA, and towards the mounting surface 5, at this time the mass of the vibration absorber is designed to be centered on the second damping rubber section 42, at this time the vibration absorbing frequency of the vibration absorber is 29 Hz; Figure 7In the middle, c is the vibration absorbing curve of the second damping rubber section 42 towards the mounting surface 5.

[0080] When the hardness of the first damping rubber section 41 is 60HA and towards the mounting surface 5, the mass of the vibration absorber is designed to be centered on the first damping rubber section 41, and the vibration absorbing frequency of the vibration absorber is 34 Hz, with an effective frequency bandwidth of ±5 Hz. Figure 7 In the middle, d is the vibration absorbing curve of the first damping rubber section 41 towards the mounting surface 5.

[0081] The above dimensions are based on the assumption that the total length LL of the mass block 1 is 100mm, and in actual application, they can be adjusted according to specific design requirements.

[0082] In the above embodiments, the description of each embodiment focuses on different aspects, and the parts not described or recorded in a certain embodiment can be referred to the related description of other embodiments.

[0083] Based on the same inventive concept, the embodiments of the present application also provide a mounting assembly of a wideband vibration absorber, which comprises the wideband vibration absorber and a mounting body, the mounting body is provided with a mounting surface 5, the mounting surface 5 is an inclined surface, the wideband vibration absorber is fixed on the mounting surface 5 through a connecting bolt 3 penetrating the inner shaft 2, and the included angle θ between the center line of the connecting bolt 3 and the perpendicular line perpendicular to the mounting surface 5 is 3-6°.

[0084] Referring to Figure 5 and Figure 6 , in the figure, b is the perpendicular line perpendicular to the mounting surface 5.

[0085] The present application realizes different vibration absorbing frequencies in different mounting modes by adjusting the mounting direction of the rubber bushing 4 with different hardness differences, quickly adjusts the frequency of the vibration absorber and widens the frequency bandwidth of the vibration absorber, so as to achieve the technical effect that the vibration absorber can quickly adapt to frequency changes; and through the design of the mounting angle of the vibration absorber, the frequency difference caused by manufacturing tolerances in the vehicle production process can also be quickly adapted, which can be adjusted in real time through simple disassembly and assembly, thereby improving the production efficiency and performance verification of the vehicle.

[0086] Vibration absorbing effect in different mounting modes: the vibration absorber can adjust the mounting direction to make the rubber bushing sections with different hardnesses face the mounting surface 5, thereby adapting to different vibration environments. For example, in a low-frequency vibration environment, the rubber bushing 4 with lower hardness can be directed towards the mounting surface 5 to effectively absorb low-frequency vibrations; in a high-frequency vibration environment, the rubber bushing 4 with higher hardness can be directed towards the mounting surface 5 to effectively absorb high-frequency vibrations. This flexibility enables the vibration absorber to be widely used in different vibration scenarios, such as industrial equipment, precision instruments and automobiles.

[0087] Based on the same inventive concept, the utility model embodiment further provides a vehicle comprising the wide-frequency vibration absorber or the mounting assembly of the wide-frequency vibration absorber.

[0088] The vehicle provided by the application achieves wide-frequency vibration absorption, lightweight design, rapid frequency adaptation, and the purposes of simplifying the installation and adjustment process, so that the vibration absorber has a wide application prospect in the field of vehicle engineering, can effectively improve the NVH performance of the vehicle, and meets the higher requirements for vibration control in vehicle engineering.

[0089] NVH performance: refers to the abbreviation of noise, vibration and harshness (Noise, Vibration, Harshness), which is an important indicator for measuring the comfort of an automobile.

[0090] The advantages of the wide-frequency vibration absorber in vehicle application: in the field of automobiles, the wide-frequency vibration absorber can be installed near the engine support part or the chassis suspension system, effectively absorbing the engine vibration and the vehicle body vibration caused by road bumps. By adjusting the installation direction of the vibration absorber, the vibration absorption effect of the vibration absorber can be flexibly adjusted according to different road conditions and vibration frequencies, thereby improving the ride comfort of the vehicle, reducing the fatigue damage of parts caused by long-term vibration, and prolonging the service life of the vehicle.

[0091] The above is only a preferred embodiment of the utility model, and is not used to limit the utility model, and any modification, equivalent replacement and improvement made within the spirit and principle of the utility model should be included in the protection scope of the utility model.

Claims

1. A broadband vibration absorber, characterized by, The mass block (1) has a central hole; The inner shaft (2) is coaxially arranged in the central hole of the mass block (1); and The rubber bushing (4) is vulcanized between the mass block (1) and the inner shaft (2); the rubber bushing (4) is divided into a first damping rubber section (41) and a second damping rubber section (42) along the axial direction thereof, and the hardness of the first damping rubber section (41) is greater than that of the second damping rubber section (42); When the first damping rubber section (41) faces the mounting surface (5) or the second damping rubber section (42) faces the mounting surface (5), different vibration energies can be absorbed to achieve wide-frequency vibration absorption. A counterbore (11) coaxial with the central hole of the mass block (1) is arranged on the first end of the mass block (1) close to the first damping rubber section (41); and / or 2. The broadband vibration absorber of claim 1, wherein A protruding portion (12) coaxial with the central hole of the mass block (1) is arranged on the second end of the mass block (1) close to the second damping rubber section (42); so as to realize the gravity center offset to the first damping rubber section (41) or the second damping rubber section (42). The distance L11 from the axial end face of the first damping rubber section (41) to the first end face of the mass block (1) is 25-35% of the total axial length LL of the mass block (1), and the end face of the first damping rubber section (41) does not protrude from the step face formed by the counterbore (11).

3. The broadband vibration absorber of claim 2, wherein The axial end face of the second damping rubber section (42) does not protrude from the outer end face of the protruding portion (12), and the distance L22 from the axial end face of the second damping rubber section (42) to the second end face of the mass block (1) is 3-8% of the total axial length LL of the mass block (1).

4. The broadband vibration absorber of claim 3, wherein The axial length LL2 of the protruding portion (12) is 15-25% of the total axial length LL of the mass block (1).

5. The broadband vibration absorber of claim 2, wherein The axial length of the first damping rubber section (41) is greater than that of the second damping rubber section (42).

6. The broadband vibration absorber of any one of claims 1-5, wherein, The axial length L1 of the first damping rubber section (41) is 60-70% of the total axial length L of the rubber bushing (4), and the axial length L2 of the second damping rubber section (42) is 30-40% of the total axial length L of the rubber bushing (4).

7. The broadband vibration absorber of claim 6, wherein The total axial length L of the rubber bushing (4) is 60-70% of the total axial length LL of the mass block (1).

8. The broadband vibration absorber of claim 7, wherein, The mounting assembly comprises the wide-frequency vibration absorber according to any one of claims 1-8 or the wide-frequency vibration absorber according to claim 9.

9. A mounting assembly for a broadband vibration absorber, comprising: ​ 10. A vehicle characterized by comprising: ​

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