CN214796748U - Wheel with sound absorption device - Google Patents
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- CN214796748U CN214796748U CN202022599451.5U CN202022599451U CN214796748U CN 214796748 U CN214796748 U CN 214796748U CN 202022599451 U CN202022599451 U CN 202022599451U CN 214796748 U CN214796748 U CN 214796748U
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Abstract
The application relates to a wheel with a sound absorption device, wherein the sound absorption device (10) is arranged in a wheel air chamber (30) to reduce acoustic resonance, the sound absorption device comprises two resonance sound absorption structure units which are connected in parallel, a first sound absorption frequency band of a first resonance sound absorption structure unit (10-1) and a second sound absorption frequency band of a second resonance sound absorption structure unit (10-2) are adjacent to each other or partially overlapped, and the resonance frequency of the wheel air chamber is contained at the adjacent position of the first sound absorption frequency band and the second sound absorption frequency band or in the overlapped area of the first sound absorption frequency band and the second sound absorption frequency band. According to the utility model provides a technical scheme can realize the organic combination of helmholtz resonance sound absorption and structural resonance sound absorption on the wheel, and the sound absorption frequency band is wideer, the sound absorption volume is higher, reaches more effective sound absorption effect.
Description
Technical Field
The utility model relates to a wheel with sound absorber, especially be furnished with pneumatic tire's auto wheel.
Background
In the normal running process of the vehicle, the excitation of the road surface to the wheels and the excitation of the wheel axle to the wheels caused by the rotation unbalance of the wheels can excite an air chamber in the wheels to generate acoustic resonance, and the resonance is transmitted to a vehicle body structure through the wheel axle and a suspension system and then radiates noise in the vehicle. The noise characteristics of the car noise suppression device are mainly low-frequency narrow bands, the magnitude is high, noise interference is formed for the interior passenger environment of the car, and effective control is needed.
Currently, there are numerous studies and patents that provide methods to effectively control such acoustic resonances. The method mainly adopts a sound absorption control principle, wherein the Helmholtz resonance sound absorption is widely applied and has a good effect. For example, chinese patents CN101301842B, CN104981359B, CN105209267B, and CN104908513B relate to a series of wheel technical solutions implemented based on helmholtz resonator noise reduction method. However, in the solutions known from the prior art, the constructive design and mounting structure of the helmholtz resonator is complex and also not ideal in terms of its sound absorption effect. In particular, since the conditions during four-wheel driving are different, there are a plurality of narrow-band high-value noises with different distribution characteristics, so that the noises present a larger noise value in a wider frequency band, which is contrary to the advantages of helmholtz narrow-band sound absorption. Therefore, the structure based on the helmholtz sound absorption principle still needs to be continuously developed and improved. Meanwhile, the structure based on the principle is various, and a space for further improvement is provided in the aspects of amplitude and bandwidth control. In addition, the helmholtz sound absorption principle is also suitable to be combined with other noise reduction principles (such as box-type structure resonance sound absorption) to make up for the deficiency of the helmholtz principle, so that the efficiency of controlling the resonance of the air chamber can be effectively improved, but the integration of various noise reduction principles at present is not popularized and applied in the aspect of reducing the acoustic resonance of the wheel air chamber.
Further, in the case of the prior art, the helmholtz resonator is complicated in structural design and mounting structure, and for this reason, a resonator component ("sub-air chamber member") is configured with a flange-like thin plate flange ("rim portion"), a groove ("groove portion") is formed in a specially configured wall surface of the boss, and positioning and fixing of the resonator component is achieved by the flange-like thin plate flange and the groove portion of the wall surface being engaged with each other, and this engagement mechanism is difficult to secure the connection strength due to its thin-walled feature, and on the other hand, since the connection and fitting of both the components are achieved substantially depending on the structural dimensional accuracy, high demands are made on the processing and manufacturing of the components, and the alignment and mounting work of both the components is troublesome, and the final mounting and fastening force cannot be controlled.
Furthermore, KR101822271B1 discloses an aluminum wheel, wherein resonator tubes are mounted along the circumference of the rim, and the resonator tubes are fixed by: the rim is provided with a single side wall extending along the circumferential direction of the rim, and the single side wall is provided with a buckling bulge extending towards the center of the rim; a flange at one side and a flange at the other side are formed at two sides of the resonance tube; the resonance tube is inserted into and hooked on the buckling bulge by a flange at one side, threads are formed on the flange at the other side, and the resonance tube is matched and fixed on the circumferential surface of the wheel rim by a nut member matched with the resonance tube. The fixing scheme of the resonator tube also has the problems of unreasonable structure, high manufacturing requirement, inconvenient assembly and the like, and the final mounting and fastening force is still difficult to control.
SUMMERY OF THE UTILITY MODEL
The utility model discloses plan to provide a wheel with sound absorbing device to partly or overcome the above-mentioned defect that exists among the prior art completely, especially optimal design helmholtz sound absorption structure, have the acoustic resonance control of certain frequency difference in order to be adapted to four wheel air chambers, realize the noise reduction of broader band.
To this end, the present invention provides a wheel with a sound absorber, the sound absorber is installed inside a wheel air chamber to reduce acoustic resonance, wherein the sound absorber includes at least two resonance sound absorbing structural units, a first sound absorbing frequency band of a first resonance sound absorbing structural unit and a second sound absorbing frequency band of a second resonance sound absorbing structural unit are adjacent to each other or partially overlap with each other, and a resonance frequency of the wheel air chamber is contained in an adjacent place of the first sound absorbing frequency band and the second sound absorbing frequency band or an overlapping region of the first sound absorbing frequency band and the second sound absorbing frequency band; the sound absorption device is constructed as a box body formed by connecting the first resonance sound absorption structure unit and the second resonance sound absorption structure unit in parallel, and the box body is fixed on a hub of a wheel.
The utility model provides a technical scheme is mainly based on following thought: firstly, two single-hole resonance sound absorption structures are adopted, each sound absorption structure corresponds to sound absorption frequency with certain bandwidth, the sound absorption frequency bands of the two single-hole resonance sound absorption structures are different and are close to (or comprise) the resonance frequency of a wheel air chamber, the two sound absorption structures are connected in parallel and combined for installation, and then sound energy with wider frequency bands can be absorbed, so that the defects that the low-frequency sound absorption capacity is difficult to improve under the limited volume by single Helmholtz resonance sound absorption and the sound absorption frequency bands are narrow are overcome on the control principle; secondly, the sound absorption device adopts a rectangular hexahedral box-shaped structure, is particularly made of plastic materials, and preferably designs the structural resonance frequency of the sound absorption device to be consistent with the resonance frequency of the wheel air chamber, so that the sound absorption quantity can be further increased on the basis of Helmholtz resonance sound absorption, and the sound absorption frequency band can be expanded; thirdly, the utility model discloses a two parallelly connected sound absorbing structure (like the helmholtz syntonizer of haplopore), its simple structure, processing is convenient. .
According to one embodiment, the sound absorber is a box of cuboid shape integrally formed from a metal material or a plastic material.
According to one embodiment, the sound absorber is a cuboid box made by a 3D printing process, preferably made of a plastic material.
According to the utility model discloses, the sound absorbing device is box-type structure. Accordingly, the sound absorber has two sides which bound the two ends of the housing in the circumferential direction of the wheel hub, wherein one end forms an open-ended side with an opening into the interior cavity of the housing and the other end forms a closed-ended side.
The utility model discloses when promoting wheel air chamber resonance control effect, to the structural design in sound absorber, still ensure to realize its contour machining through the production technique that is suitable for, according to the utility model discloses, sound absorbing structure can adopt 3D printing technology to carry out high-efficient preparation, is convenient for realize box-shaped sound absorber's flexible production.
It should be noted that the "cuboid shape" in the present application is not strictly limited to a regular cuboid shape in a geometric sense, but may substantially have a shape similar to a cuboid, wherein one or more faces are configured to have a certain curvature (e.g., the bottom surface of the box body has a circular arc shape adapted to the outer surface profile of the rim) and/or have a local convex or concave structure (e.g., for installation or fixation), may not be absolutely orthogonal between intersecting faces, may not be absolutely parallel between opposing faces, and does not affect the implementation of the technical solution of the present invention.
According to one embodiment, it is advantageous if the first and second resonant sound-absorbing structural units of the sound absorber each form a single-hole helmholtz resonator, wherein the interior of the housing is divided by a partition extending in the circumferential direction of the wheel hub into a first and a second cavity arranged next to one another, wherein the openings of the first and second hollow tubes are formed on the side of the open end, wherein the openings open into the wheel air chamber and the first and second hollow tubes each extend into the first and second cavities at a distance corresponding to their tube length.
As described above, the two sound absorbing structures (i.e., the first resonance sound absorbing structure unit and the second resonance sound absorbing structure unit connected in parallel) of the sound absorbing device have different sound absorbing frequency bands, but both are close to (or include) the resonance frequency of the wheel air chamber. Therefore, specifically for the above embodiment, the resonance frequencies of the two helmholtz resonators are different, and the resonance frequency of the first helmholtz resonator formed as the first resonance sound absorption structural unit is equal to or higher than the resonance frequency of the wheel air chamber, and the resonance frequency of the second helmholtz resonator formed as the second resonance sound absorption structural unit is equal to or lower than the resonance frequency of the wheel air chamber. It is expedient here for the difference between the resonance frequency of the first helmholtz resonator and the resonance frequency of the wheel gas chamber to be not more than 50% of the resonance frequency of the wheel gas chamber; the difference between the resonance frequency of the second helmholtz resonator and the resonance frequency of the wheel air chamber is also not more than 50% of the resonance frequency of the wheel air chamber.
Further, the structural parameters of the box body of the sound absorption device are determined by the preset sound absorption coefficients and the sound absorption amounts of the two helmholtz resonators, and the structural parameters comprise the thicknesses of the baffle plate and the plate bodies on the side surfaces of the open end and the closed end, the hole diameters and the pipe lengths of the first hollow pipe and the second hollow pipe, and the shapes, the volumes and the wall thicknesses of the first cavity and the second cavity.
Advantageously, the sound absorber is integrally formed as a structural resonance sound absorber having a first order natural mode frequency corresponding to the first order natural mode frequency of the wheel air chamber.
According to one embodiment, a plurality of sound absorbers are arranged on the hub of the wheel side by side or distributed along the circumferential direction of the hub, so as to optimize or adapt to the sound absorption and noise reduction requirements of the whole wheel or the dynamic balance characteristics of the whole wheel. In particular, a plurality of box-shaped sound absorbers may be arranged uniformly along the circumferential direction of the wheel hub, for example, two box-shaped sound absorbers may be arranged symmetrically along the circumferential direction of the wheel hub, that is, mounted opposite to each other in the diameter direction of the wheel, for a specific case of a specific vehicle type.
According to one embodiment, the sound absorber rests with the bottom side of the housing against the outer rim surface of the hub in the mounted state. In this connection, it is expedient if the sound absorber is provided with at least one bend extending transversely along its housing, which bend divides the sound absorber of the cassette into at least two sections in the longitudinal direction of its housing, in order to adapt the bottom of the housing to the circular-arc-shaped contour of the outer surface of the rim in the mounted state. The bending part can be designed as a material weak part of the box body, can be continuous or discontinuous along the transverse direction of the box body, can transversely extend through the box body, and can also only extend on a part of the transverse section of the box body.
According to one embodiment, the sound absorber is fastened to the hub of the wheel by means of a strap (for example, a steel band) which is pressed from the top side of the housing of the sound absorber against the outer surface of the rim of the wheel hub and fastens the sound absorber around the hub, the two ends of the strap being fixedly connected by means of a snap connection, the tension of the strap being adjustable and/or displayable by means of a fastening tool.
In this connection, it is advantageous if the sound absorber has a U-shaped recess on its box top face for the insertion of the strap.
The utility model discloses the beneficial technological effect that can realize lies in very much, has constituteed a comprehensive sound absorbing structure configuration by two resonance sound absorption units and overall structure resonance sound absorption, realizes the organic combination of helmholtz resonance sound absorption and structure resonance sound absorption promptly on the wheel, reaches more effective sound absorption effect, and this embodiment is in: firstly, the sound absorption frequency band is wider; secondly, the sound absorption quantity is higher.
Drawings
In which some exemplary embodiments of the invention are shown. The embodiments and figures disclosed herein are to be regarded as illustrative rather than restrictive. It is also noted that for purposes of clarity of illustration, certain features are not necessarily drawn to scale in the drawings.
Fig. 1 is a schematic view of the mounting of the sound absorbing device on a wheel.
Fig. 2 is a schematic view of a sound absorber according to a preferred embodiment arranged on a wheel hub.
Fig. 3 is a schematic view of the construction principle of the sound absorbing device.
Fig. 4 is a diagram of noise reduction amount actually measured by using a test platform to simulate the working condition of a wheel/tire under a driving state of an automobile in an application example.
Wherein: 1-the side surface of the opening end of the box body, 1' -the side surface of the closed end of the box body, 2-a first hollow tube, 2 w-the wall of the first hollow tube, 3-a first cavity, 4-a second hollow tube, 4 w-the wall of the second hollow tube, 5-a second cavity, 6-a partition plate and 7-a U-shaped groove; 10-sound absorption device, 10-1-first resonance sound absorption structure unit, 10-2-second resonance sound absorption structure unit, 20-wheel hub, 30-wheel air chamber, 40-tire and 50-binding belt.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some, but not all, embodiments of the present application. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
The terms "first," "second," and the like in the description and claims of the present application and in the accompanying drawings are used for distinguishing between different objects and not for describing a particular order. Furthermore, the terms "comprising" and "having," as well as any variant thereof, are intended to cover a non-exclusive inclusion. For example, a process, method, article, or apparatus that comprises a list of steps or elements is not limited to those listed but may alternatively include other steps or elements not listed or inherent to such process, method, article, or apparatus. It will be understood by those skilled in the art that throughout the present specification and claims, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in the orientation or positional relationship indicated in the drawings for convenience and simplicity of description, and do not indicate or imply that the referenced device, mechanism, structure, or element must have a particular orientation, be constructed and operated in a particular orientation, and thus are not to be considered as limiting.
Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.
The present application provides a wheel, particularly an automotive wheel equipped with a pneumatic tire 40, having a sound absorber 10 mounted within the wheel air chamber 30 for reducing acoustic resonance, as shown in fig. 1. According to the present invention, the sound absorption device includes at least two resonance sound absorption structure units, wherein the first sound absorption frequency band of the first resonance sound absorption structure unit 10-1 and the second sound absorption frequency band of the second resonance sound absorption structure unit 10-2 are adjacent to each other or partially overlapped, and the resonance frequency f of the wheel air chamber 300Contained in the adjacent place of the first sound absorption frequency band and the second sound absorption frequency band or the overlapping area of the first sound absorption frequency band and the second sound absorption frequency band; the sound absorbing device is constructed as a case body composed of the first resonance sound absorbing structural unit 10-1 and the second resonance sound absorbing structural unit 10-2 connected in parallel, and the case body is fixed to a hub 20 of a wheel (see fig. 2 and 3).
Fig. 2 is a schematic view of a sound absorber according to a preferred embodiment arranged on a wheel hub.
According to the actual requirement, it is possible to arrange a plurality of sound absorbers 10 side by side on the hub 20 of the wheel, or arrange a plurality of sound absorbers 10 distributed along the circumferential direction of the hub. The sound absorber 10 rests with the bottom side of the housing against the outer rim surface of the hub 20 in the mounted state. In this connection, the sound absorber 10 is expediently provided with at least one bend extending transversely along its housing, which divides the sound absorber cassette or sound absorber cassette assembly into at least two sections in the longitudinal direction of its housing, in order to adapt the housing base to the circular-arc-shaped contour of the outer surface of the rim in the installed state. The bending part can be designed as a material weak part of the box body, can be continuous or discontinuous along the transverse direction of the box body, can transversely extend through the box body, and can also only extend on a part of the transverse section of the box body.
The sound absorber 10 may be fastened to the hub 20 of the wheel by a fastening band (e.g., a steel band) 50 which presses the sound absorber 10 from the top surface of the case of the sound absorber 10 toward the outer surface of the rim of the hub of the wheel and fastens the sound absorber 10 around the hub 20, and both ends of the fastening band are fixedly connected by a snap, and the fastening force of the fastening band can be set and/or displayed by a fastening tool. Suitably, the sound absorber 10 is provided with a U-shaped groove 7 (see fig. 3) on the top surface of its case for embedding the binding band.
Fig. 3 shows the general outer structure and inner construction of a single sound absorber. Preferably, the sound absorbing device 10 is a rectangular parallelepiped case integrally formed of a plastic material, and may be manufactured through a 3D printing process. As shown in particular in fig. 3, the sound absorber 10 has two sides bounding the two ends of the housing in the circumferential direction of the wheel hub, one of the ends forming an open-ended side 1 with an opening into the interior cavity of the housing and the other end forming a closed-ended side 1'. The first resonance sound absorbing structural unit 10-1 and the second resonance sound absorbing structural unit 10-2 of the sound absorbing device 10 form a single-hole helmholtz resonator, respectively, wherein the interior of the case body is divided into a first cavity 3 and a second cavity 5 arranged side by a partition plate 6 extending along the circumferential direction of the wheel hub, nozzles of a first hollow tube 2 and a second hollow tube 4 are formed on the open end side 1, each nozzle opens into the wheel air chamber, and the first hollow tube and the second hollow tube extend into the first cavity 3 and the second cavity 5 at a distance corresponding to the tube lengths thereof, respectively.
As described above, the two sound absorbing structures (i.e., the first resonance sound absorbing structure unit and the second resonance sound absorbing structure unit connected in parallel) of the sound absorbing device have different sound absorbing frequency bands, but both are close to (or include) the resonance frequency of the wheel air chamber. The resonance frequencies of the two helmholtz resonators are not the same (i.e. fr)1≠fr2) And the resonance frequency fr of the first Helmholtz resonator formed as the first resonance sound absorbing structural unit 10-11Is equal to or higher than the resonance frequency f of the wheel air chamber 300(i.e., fr)1≥f0) And the resonance frequency fr of the second Helmholtz resonator formed as the second resonance sound absorbing structural unit 10-22Less than or equal to the resonance frequency f of the wheel air chamber 300(i.e., fr)2≤f0). Suitably, the resonance frequency fr of the first helmholtz resonator is1Resonant frequency f with the wheel air chamber 300The difference is not more than 50% of the resonance frequency of the wheel air chamber; resonance frequency fr of the second Helmholtz resonator2Resonant frequency f with the wheel air chamber 300The difference is also no greater than 50% of the resonant frequency of the wheel air chamber.
Here, the structural parameters of the case of the sound-absorbing box 10, including the thickness of the partition plate 5 and the plate bodies of the open-end side 1 and the closed-end side 1', the orifice diameter and the tube length of each of the hollow tubes, and the shape, volume and wall thickness of the first cavity 3 and the second cavity 5, are determined by the predetermined sound absorption coefficients and the sound absorption amounts of the two helmholtz resonators.
According to the present invention, it is advantageous that the sound absorber 1 integrally forms a structural resonance sound absorber, and as the structural resonance sound absorber, the first-order natural mode frequency thereof is identical to the first-order natural mode frequency of the wheel air chamber 30. This will be further explained below.
In particular, fig. 3 shows a schematic view of the construction principle of the sound absorber according to the present invention, which is embodied as a box-shaped structure formed by injection molding and having a rectangular parallelepiped shape, and is divided into two cavities, i.e., a first cavity 3 and a second cavity 5, by a thin plate (i.e., a partition 6 perpendicular to a surface connected with the partition). Two hollow pipe walls (a first hollow pipe wall 2w and a second hollow pipe wall 4w respectively) extending towards the interior of the box body are arranged on one side face (namely the side face 1 of the opening end vertical to the partition board) of the box-type structure, the two hollow pipe walls and the wall face of the cavity form a first hollow pipe 2 and a second hollow pipe 4, the first hollow pipe 2 is communicated with the first cavity 3, and the second hollow pipe 4 is communicated with the second cavity 5. The plane of the pipe orifice at one end of the hollow pipe and the side surface (namely the side surface 1 of the opening end) of the box body are on the same surface, and the first hollow pipe 2 and the second hollow pipe 4 can have different pipe orifice apertures or pipe orifice cross-sectional areas; the tube length extends into the cavity and the first hollow tube 2 and the second hollow tube 4 may have different tube lengths. The first hollow pipe 2 and the second hollow pipe 4 are communicated with a tire air chamber (namely a wheel air chamber), and the box-type structure is integrally arranged on the circular arc circumferential surface of the hub to form a parallel Helmholtz resonance sound absorption structure. Compared with single-cavity single-hole type Helmholtz resonance sound absorption, the structural configuration has wider sound absorption frequency band. Relevant parameters of the structural configuration are determined by using the sound absorption coefficient and the sound absorption quantity of the Helmholtz resonance sound absorption structure.
The box-type structure is preferably made of plastic materials with certain rigidity and strength, clings to the circular arc circumference of the hub and is fixedly installed by utilizing a steel belt. In the parallel helmholtz resonance sound absorption structure under the installation mode, two first-order natural modal frequencies are separated and are close to the first-order natural modal frequency of the wheel air chamber, so that the sound absorption and noise reduction frequency band is expanded.
The natural mode of the structure meets the design requirements through plate thickness and shape adjustment, and the adjustment needs to be realized through finite element calculation. On one hand, the design of the resonant sound absorption structure can further increase the sound absorption quantity of the resonant sound absorption structure, and the sound absorption bandwidth can also be further increased through the design.
The box-type sound absorption device is provided with a U-shaped groove on the upper surface, the box-type structure has an arc shape, and the installation mode is that a steel belt passes through the U-shaped groove and is fixed around the hub in a circle. It is also possible to arrange a plurality of cassette sound-absorbing structures on the hub according to the actual needs and the specific design situation, and a steel belt is wound around the hub to fix the several cassette sound-absorbing structures on the hub together. The steel band junction is fastened with the buckle, and fastening force can show with fastening tool to judge the firm degree of installation.
The relevant parameters of the box structure having a rectangular hexahedral shape shown in fig. 3 are determined using the sound absorption coefficient and the sound absorption amount of the helmholtz resonance sound absorbing structure, as follows:
let Z be the surface acoustic impedance of the resonant structure. Zp is the acoustic impedance of the hole of the perforated structure and Za is the acoustic impedance of the cavity. Zp and Za are calculated as in equations (1) and (2), and then Z is calculated as in equation (3), and the sound absorption coefficient is calculated as in equation (4).
Z＝Zp+Za (3)
Where ρ is air density, c is air sound velocity, ω is 2 pi f, f is frequency, γ is air motion viscosity coefficient, γ is 1.53 x 10-5m2And s. t is the thickness of the plate, D is the aperture, δ is the perforation rate of the plate, and D is the thickness of the cavity. Zr is the relative specific acoustic impedance of the resonant structure.
Let R be the real part of Zr, X be the imaginary part of Zr, the sound absorption coefficient alpha of resonance sound absorption structure is:
the resonance frequency fr of the perforated plate can be calculated by equation (5):
the sound absorption quantity calculation formula is as follows:
A＝αS (6)
wherein: and A is the sound absorption quantity of the resonance sound absorption structure.
S is the cross section area of the hollow pipe 2/4 of the resonance sound absorption structure.
Fig. 3 shows a box-shaped structure having a rectangular hexahedral shape as a resonance sound absorbing structure, in which the first-order natural mode frequency coincides with the first-order natural mode frequency of the wheel air chamber. The natural frequency of the steel plate reaches the design requirement through plate thickness and shape adjustment, and the adjustment mode of the steel plate needs to be realized through finite element calculation.
As shown in fig. 3, the sound absorbing resonance structure is designed with a U-shaped groove 7 on the upper surface in order to be mounted on the hub 20 shown in fig. 2. As shown in fig. 1 and 2, the mounting is performed by passing a steel band as a binding band 50 through and into the U-shaped groove 7, and fixing the resonance sound absorbing structure by pressing it against the hub around the periphery of the hub. The steel strip 3 may be fastened to the hub around its circumference by one or more sound-absorbing structures. The steel band junction is fastened with the buckle, and fastening force can show with fastening tool to judge the firm degree of installation.
Fig. 4 is a diagram of noise reduction amount actually measured by using a test platform to simulate the working condition of a wheel/tire under a driving state of an automobile in an application example.
In an application example test, the natural frequency of an air chamber of a certain automobile in a driving state is calculated by using certain commercial software, and for the natural frequency, the geometric dimensions and the sound absorption performance of the resonance sound absorption structure of the sound absorption device shown in fig. 3 are designed and debugged according to the formulas (1) to (6). The sound absorption device with the corresponding resonance sound absorption structure is manufactured by adopting plastic materials and utilizing a 3D printing method, and the resonance sound absorption structure (the sound absorption device) is installed on a test platform to carry out sound absorption and noise reduction tests. The test platform is manufactured according to the shape of a tire and the shape of an air chamber of the tire under a certain automobile driving state, a loudspeaker arranged on the wall surface of the test platform emits sound signals, a sound field is formed in the air chamber, the loudspeaker arranged on the wall surface can detect the size of the sound field in the air chamber, and the sound absorption device can be arranged according to the actual configuration mode in the air chamber. And measuring the sound pressure level collected on the wall surface before and after the sound absorption device is installed, and evaluating the noise reduction effect of the sound absorption device through comparison. According to the evaluation method, the noise reduction effect of the sound absorption device is evaluated by using the difference of sound pressure levels obtained by two times of measurement on the interested frequency band.
It can be seen from fig. 4 that, near tire air chamber natural frequency 200Hz, the utility model discloses a resonance sound absorption structure noise reduction effect is obvious, adopts a resonance sound absorption structure (sound absorber) maximum noise reduction volume alright reach 3.7dB, and the bandwidth of making an uproar is fallen and is exceeded 20 Hz. A real vehicle may use more such resonant sound absorbing structures (sound absorbers) and the effective noise reduction will be greater.
The foregoing detailed description of the embodiments of the present application has been presented to illustrate the principles and implementations of the present application, and the above description of the embodiments is only provided to help understand the core concepts of the present application; meanwhile, for those skilled in the art, according to the idea of the present application, there may be variations in the specific embodiments and the application scope, and in summary, the content of the present specification should not be construed as a limitation to the present application.
Claims (13)
1. A wheel with sound absorption means, which sound absorption means (10) are installed inside a wheel air chamber (30) for reducing acoustic resonance, characterized in that the sound absorption means comprise at least two resonance sound absorption structural units, wherein a first sound absorption frequency band of a first resonance sound absorption structural unit (10-1) and a second sound absorption frequency band of a second resonance sound absorption structural unit (10-2) adjoin each other or partially overlap each other, and the resonance frequency (f) of the wheel air chamber (30)0) Contained in the adjacent place of the first sound absorption frequency band and the second sound absorption frequency band or the overlapping area of the first sound absorption frequency band and the second sound absorption frequency band; the sound absorption device is formed by connecting the first resonance sound absorption structure unit (10-1) and the second resonance sound absorption structure unit (10-2) in parallelA box body is formed, and the box body is fixed on a hub (20) of a wheel;
the first resonance sound absorption structure unit (10-1) and the second resonance sound absorption structure unit (10-2) of the sound absorption device (10) respectively form a single-hole Helmholtz resonator.
2. A wheel according to claim 1, characterized in that said sound absorbing means (10) is a box of parallelepiped shape made in one piece of metal material or plastic material.
3. A wheel according to claim 1, characterized in that said sound absorbing means (10) is a parallelepiped-shaped box made by a 3D printing process.
4. A wheel according to claim 1, characterized in that the sound-absorbing means (10) has two sides bounding the two ends of the box in the circumferential direction of the wheel hub, one of the ends forming an open-ended side (1) with an opening into the cavity inside the box and the other end forming a closed-ended side (1').
5. A wheel according to claim 4, characterized in that the interior of the box body is divided into a first cavity (3) and a second cavity (5) arranged side by a partition (6) extending circumferentially along the wheel hub, that on said open end side (1) there are formed orifices of a first hollow tube (2) and a second hollow tube (4), each opening into the wheel air chamber and extending into the first cavity (3) and the second cavity (5) at a distance corresponding to their tube length, respectively.
6. A wheel according to claim 5, characterized in that the resonance frequencies of the two Helmholtz resonators are different and that the resonance frequency (fr) of the first Helmholtz resonator formed as the first resonant sound-absorbing structural unit (10-1)1) Greater than or equal to the resonance frequency (f) of the wheel air chamber (30)0) And a second helm formed as a second resonant sound-absorbing structural unit (10-2)Resonance frequency (fr) of a Hutz resonator2) Less than or equal to the resonance frequency (f) of the wheel air chamber (30)0)。
7. A wheel according to claim 6, characterized in that the resonance frequency (fr) of said first Helmholtz resonator1) A resonance frequency (f) with the wheel air chamber (30)0) The difference is not more than 50% of the resonance frequency of the wheel air chamber; resonance frequency (fr) of the second Helmholtz resonator2) A resonance frequency (f) with the wheel air chamber (30)0) The difference is also no greater than 50% of the resonant frequency of the wheel air chamber.
8. A wheel according to claim 5, characterized in that the structural parameters of the casing of the sound absorbing device (10), including the plate thickness of the partition (6) and the open-end (1) and closed-end (1'), the orifice diameter and the tube length of the first (2) and second (4) hollow tubes, the shape, volume and wall thickness of the first (3) and second (5) cavities, are determined by the predetermined sound absorption coefficients and sound absorption quantities of the two Helmholtz resonators.
9. A wheel according to any of claims 1 to 8, wherein the sound absorber (10) is formed integrally as a structural resonance sound absorber having a first order natural modal frequency corresponding to the first order natural modal frequency of the wheel air chamber (30).
10. A wheel according to any of claims 1 to 8, wherein a plurality of said sound absorbers (10) are provided side by side on the hub (20) of the wheel, or a plurality of said sound absorbers (10) are provided distributed along the circumference of the hub.
11. A wheel according to any of claims 1 to 8, characterized in that the sound absorber (10) in the mounted state rests with the bottom surface of the housing against the outer surface of the rim of the hub (20).
12. A wheel according to any of claims 1 to 8, wherein the sound absorber (10) is fastened to the hub (20) of the wheel by means of a strap (50) which is pressed from the top side of the casing of the sound absorber (10) against the outer surface of the rim of the wheel hub and which fastens the sound absorber (10) around the hub (20), the two ends of the strap being fixedly connected by snap fastening, the tension of the strap being adjustable and/or displayable by means of a fastening tool.
13. A wheel according to claim 12, characterized in that said sound absorbing means (10) are provided with a U-shaped groove (7) on the top face of its case for embedding said tie.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022599451.5U CN214796748U (en) | 2020-11-11 | 2020-11-11 | Wheel with sound absorption device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022599451.5U CN214796748U (en) | 2020-11-11 | 2020-11-11 | Wheel with sound absorption device |
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| Publication Number | Publication Date |
|---|---|
| CN214796748U true CN214796748U (en) | 2021-11-19 |
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| CN202022599451.5U Active CN214796748U (en) | 2020-11-11 | 2020-11-11 | Wheel with sound absorption device |
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| CN (1) | CN214796748U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114452638A (en) * | 2022-02-18 | 2022-05-10 | 罗永梅 | Hydraulic road pressure sensing feedback VR bicycle |
| CN114495886A (en) * | 2020-11-11 | 2022-05-13 | 中信戴卡股份有限公司 | Wheel with sound absorption device |
-
2020
- 2020-11-11 CN CN202022599451.5U patent/CN214796748U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114495886A (en) * | 2020-11-11 | 2022-05-13 | 中信戴卡股份有限公司 | Wheel with sound absorption device |
| CN114452638A (en) * | 2022-02-18 | 2022-05-10 | 罗永梅 | Hydraulic road pressure sensing feedback VR bicycle |
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