TWI480184B - Vehicle suspension structure - Google Patents

Description

Vehicle suspension structure

The present invention relates to a suspension structure, and more particularly to a vehicle suspension structure that utilizes an elastic body having a nonlinear elastic coefficient to perform gravity damping to achieve a good suspension effect.

In general vehicles, vehicle suspension devices are provided, which are mainly equipped with metal springs, hydraulic damping devices or air pressure damping devices to carry the weight of the vehicle body and provide appropriate elasticity to cope with the vibration of the vehicle body caused by the road conditions. Generally speaking, when the human body rides on a vehicle, the road vibration is most comfortable from 1 Hz to 1.5 Hz. The vibration frequency above this interval makes the person feel stiff, and the vibration at 0.5 Hz to 0.8 Hz makes people feel dizzy. Therefore, the suspension devices of most vehicles are designed to make the resonance frequency of the vehicle body with the road surface vibration between 1 Hz and 1.5 Hz. However, it can be known from the following equation that the resonant frequency of the vehicle body is related not only to the spring rate of the spring but also to the total mass of the system.

Where f is the frequency, k is the elastic coefficient, and m is the mass.

It is therefore foreseen that when a vehicle using a spring suspension device carries more passengers, the total mass of the vehicle will increase, causing the resonance frequency of the entire vehicle to decrease. When the total mass of the vehicle is the smallest when only one person is driving, the resonance frequency will increase. Thus, the resonant frequency of the vehicle as it travels varies with the number of passengers, and it will be difficult to control between comfortable resonance frequencies. Therefore the general public The way in which vehicles solve this problem is to substantially increase the weight of empty vehicles, so that the increase in the quality of passengers has little effect on the overall quality change. However, the side effect of this method is to increase the useless load in a large amount, so that a large amount of energy is wasted on the quality of the car body, which is not an ideal modern design of energy saving and environmental protection.

In addition, since the resonance frequency is related to the elastic coefficient and the total mass. The total mass varies with the number of passengers. This is an uncontrollable parameter. Therefore, in order to maintain the resonance frequency, there is not much difference. It is possible to design an elastic coefficient that can change with the mass, that is, the elastic coefficient. It can be increased synchronously as the mass increases, so that the ratio is always maintained at a certain value to obtain a constant resonance frequency. The fluid spring disclosed in U.S. Patent No. 3,944,004 utilizes the compressibility of a special fluid, which can provide different elasticity under different pressures, so that the elastic coefficient of the suspension device can be changed with the load to maintain the resonance frequency. It is greatly changed by the weight of the load. However, its disadvantage is the environmental problem of the related oil seal and oil leakage caused by the use of liquid. Moreover, the expensive manufacturing costs involved in precision machining are also the main reasons why they cannot be applied in large quantities.

In view of this, the inventors of the present invention have conceived and designed a vehicle suspension structure to improve the lack of the prior art, thereby enhancing the industrial use and utilization.

In view of the above-described problems of the prior art, it is an object of the present invention to provide a vehicle suspension structure for maintaining the vibration frequency of the vehicle as it travels within a comfortable range for the passenger.

In accordance with the purpose of the present invention, a vehicle suspension structure is proposed that includes a tapered elastomer, a compression member, and a top member. Tapered elastomer has a relatively narrow end and a wide mouth The elastic coefficient of the end and the tapered elastomer has a nonlinear characteristic. The pressing member is movably disposed above the neck end. The abutting member is connected to the wide mouth end.

Wherein, when the pressing member presses the tapered elastic body such that the relative distance between the neck end and the wide mouth end becomes smaller, the elastic modulus of the tapered elastic body can be gradually increased nonlinearly.

Wherein, when the pressing member presses the tapered elastic body downward, the ratio of the neck end of the tapered elastic body divided by the sectional area of the wide mouth end may increase.

Wherein, the vehicle suspension structure may further comprise a housing, which may have an accommodation space and an opening therethrough, one end of the pressing member may be exposed outside the opening, and the bottom of the accommodation space may include a top abutting member.

Wherein, when the number of the tapered elastic bodies is N, N is a positive integer greater than 1, and each of the tapered elastic bodies may be stacked in the same direction in the accommodating space, and the pressing member may be disposed at the closest opening. Above the constricted end of the tapered elastomer.

The vehicle suspension structure may further include N-1 partition members, which may be respectively disposed between the tapered elastic bodies, and the circumference of each partition member may correspond to the peripheral wall of the accommodating space.

The material, size and shape of all or part of the N tapered elastomers may be the same.

Wherein, when the number of the tapered elastic bodies is N, N is a positive integer greater than 1, and each of the tapered elastic bodies may be disposed in the accommodating space without overlapping, and the wide mouth end of each tapered elastic body may be connected to At the bottom of the accommodating space, the pressing member may be disposed above the constricted end of each tapered elastic body.

The material, size and shape of each tapered elastic body may be the same.

As described above, if the vehicle suspension structure of the present invention is installed in a vehicle, since the elastic modulus of the tapered elastic body of the vehicle suspension structure can be increased synchronously as the load of the vehicle increases, the vibration frequency of the vehicle can be increased. Maintained within a predetermined range to maintain the resonant frequency of the vehicle in a more comfortable interval.

1, 2, 3‧ ‧ vehicle suspension structure

11, 21, 31‧‧‧ Tapered Elastomers

111, 211, 311‧‧ ‧ shrink end

112, 212, 312‧‧‧ wide mouth

12‧‧‧Top member

13, 23, 33‧‧‧Compression members

22‧‧‧Parts

24, 32‧‧‧ shell

241, 321‧‧‧ accommodating space

242, 322‧‧‧ the bottom of the accommodation space

243, 323‧‧ ‧ openings

Figure 1 is a schematic view of a first embodiment of a vehicle suspension structure of the present invention.

Fig. 2 is a schematic view showing a second embodiment of the vehicle suspension structure of the present invention.

Figure 3 is a schematic view showing a third embodiment of the vehicle suspension structure of the present invention.

Fig. 4 is a graph showing the deformation amount and the load amount of the vehicle suspension structure of the present invention.

The technical features, contents, and advantages of the present invention, as well as the advantages thereof, can be understood by the present inventors, and the present invention will be described in detail with reference to the accompanying drawings. The subject matter is only for the purpose of illustration and description. It is not intended to be a true proportion and precise configuration after the implementation of the present invention. Therefore, the scope and configuration relationship of the attached drawings should not be interpreted or limited. First described.

Please refer to FIG. 1 , which is a schematic view of a first embodiment of a vehicle suspension structure of the present invention. Fig. 1(a) is a first schematic view showing a first embodiment of the vehicle suspension structure of the present invention. Figure 1(b) is a second schematic view of the first embodiment of the vehicle suspension structure of the present invention. As shown, the vehicle suspension structure 1 of the present invention includes a tapered elastic body 11, a pressing member 13, and a top abutting member 12. The tapered elastic body 11 has a constricted end 111 and a wide end 112, and the elastic modulus of the tapered elastic body 11 has a nonlinear characteristic. The pressing member 13 is movably disposed above the neck end 111. The abutment member 12 is coupled to the wide mouth end 112. Wherein, the car of the invention The suspension structure 1 is a non-linear damping structure, which is not limited to use in a vehicle suspension device, and can be applied to various shock absorbers, and the invention is not limited thereto.

In this embodiment, when the pressing member 13 presses the tapered elastic body 11 such that the relative distance between the narrow end 111 of the tapered elastic body 11 and the wide mouth end 112 becomes gradually smaller, the tapered elastic body 11 The ratio of the cross-sectional area of the constricted end 111 divided by the cross-sectional area of the wide-mouthed end 112 increases with the urging force of the nip member 13, and the elastic modulus of the tapered elastic body 11 gradually increases with nonlinearity.

Therefore, if the vehicle suspension device used in the vehicle uses the vehicle suspension structure 1 of the present invention, when the vehicle is only driving one person, the total mass of the vehicle at this time is m1, and the elastic coefficient of the tapered elastic body 11 is k1. Therefore, the vibration frequency of the vehicle can be expressed as . When the vehicle carries more passengers, the total mass of the vehicle will increase to m2, and the elastic modulus of the tapered elastic body 11 will increase to k2 with the total mass of the vehicle. At this time, the vibration frequency of the vehicle can be expressed as . Since the elastic modulus of the tapered elastic body 11 of the vehicle suspension structure 1 of the present invention can be changed with the total mass of the vehicle, the elastic modulus of the tapered elastic body 11 can be designed to be divided by the ratio of the total mass of the vehicle to maintain the root number. Within a predetermined range, that is, | f 1- f 2|< ε , ε is a preset value to obtain a vibration frequency that makes the passenger more comfortable, and the vibration frequency is approximately between 1 Hz and 1.5 Hz.

Incidentally, since the vehicle suspension structure 1 of the present invention is installed in a vehicle suspension device in a vehicle, the resonance frequency of the vehicle can be maintained within a predetermined value or a predetermined range regardless of the total mass of the vehicle. Avoiding the use of conventional spring suspension devices reduces the impact of mass quality on overall quality changes and significantly increases the weight of empty vehicles. Therefore, The vehicle using the vehicle suspension structure 1 of the present invention can reduce the weight of the empty vehicle to achieve the effect of fuel saving and energy saving.

Please refer to FIG. 2, which is a schematic view of a second embodiment of the vehicle suspension structure of the present invention. As shown, the vehicle suspension structure 2 of the present invention includes three tapered elastic bodies 21, two partition members 22, a pressing member 23, and a housing 24. The housing 24 has an accommodation space 241 and an opening 243 therethrough, and the bottom portion 242 of the accommodation space 241 serves as the abutment member 12 as in the first embodiment. The tapered elastic bodies 21 are stacked in the same direction in the accommodating space 241, and the elastic coefficients of the tapered elastic bodies 21 have nonlinear characteristics. One end of the pressing member 23 is exposed outside the opening, and the pressing member 23 is disposed above the neck end 211 of the tapered elastic body 21 closest to the opening 243. Each of the partitioning members 22 is disposed between each of the tapered elastic bodies 21, and the peripheral edge of each of the partitioning members 22 corresponds to the peripheral wall of the accommodating space 241, so that the pressing member 23 is pressed and the tapered elastic body 21 is moved downward by the pressing force. Or when it moves upward due to its elastic restoring force, it can move more stably in the accommodating space 241 without shaking left and right. The number of the tapered elastic body 21 and the partitioning member 22 can be designed according to the needs of the user, and the present invention is not limited thereto.

In this embodiment, the materials, sizes, and shapes of the respective tapered elastic bodies 21 in the straight-shaped vehicle suspension structure 2 are the same, in other words, the elastic properties of the respective tapered elastic bodies 21 under the same pressing force. The coefficients are substantially the same, but are not limited to this. The respective tapered elastic bodies 21 arranged vertically may have different materials, sizes or shapes, so that the respective tapered elastic bodies 21 exhibit different elastic coefficients under the same pressing force, and thus the elastic coefficient of the straight tubular suspension structure 2 The non-linear curve with the load capacity can be designed according to the user's needs. Further, the partition members provided between the respective tapered elastic bodies 21 are respectively abutted against the tapered elastic body 21 provided thereon and the tapered elastic body 21 press-fitted thereunder.

Please refer to FIG. 3, which is a schematic view of a third embodiment of the vehicle suspension structure of the present invention. Fig. 3(a) is a first schematic view showing a third embodiment of the vehicle suspension structure of the present invention. Figure 3(b) is a second schematic view of a third embodiment of the vehicle suspension structure of the present invention. As shown, the vehicle suspension structure 3 of the present invention includes three tapered elastic bodies 31, a pressing member 33, and a housing 32. The housing 32 has an accommodating space 321 and an opening 323, and the bottom 322 of the accommodating space 321 can be used as the abutting member 12 of the first embodiment. The tapered elastic bodies 31 are disposed in the accommodating space 321 without overlapping. The wide end 312 of each tapered elastic body 31 is connected to the bottom 322 of the accommodating space 321 , and the elastic coefficients of the tapered elastic bodies 31 are non- Linear characteristics. The pressing members 33 are evenly disposed above the neck ends 311 of the respective tapered elastic bodies 31. The number of the tapered elastic bodies 31 can be designed according to the needs of the user, and the invention is not limited thereto. The actuating relationship between the pressing member of the vehicle suspension structure 3 and the tapered elastic body 31 of this embodiment and the pressing member of the vehicle suspension structure 1 of the first embodiment and the tapered elastic body 11 Similarly, the present invention will not be described again for the sake of brevity.

Please refer to FIG. 4, which is a graph of deformation amount and load amount of the vehicle suspension structure of the present invention. As shown in the figure, the graph of the deformation amount and the load amount is an upward curved curve, and the slope of each point on the line is the elastic coefficient under each load amount. Since the slope of this curve gradually increases from left to right, the elastic coefficient of the vehicle suspension structure of the present invention is a nonlinear elastic coefficient.

In summary, the vehicle suspension structure of the present invention can vary depending on the pressing force of the pressing member due to the elastic modulus of the tapered elastic body. Therefore, if the vehicle suspension structure is installed in the vehicle, regardless of the total mass of the vehicle. Both can maintain the resonant frequency of the vehicle at a fixed value, thus avoiding the use of conventional spring suspension devices to reduce the quality of the passengers to the overall quality change The impact of the increase in the weight of empty cars. Therefore, the vehicle using the vehicle suspension structure of the present invention can reduce the weight of the empty vehicle to achieve the effect of fuel saving and energy saving.

The above is intended to be illustrative only and not limiting. Any equivalent modifications or alterations to the spirit and scope of the invention are intended to be included in the scope of the appended claims.

2‧‧‧Vehicle suspension structure

21‧‧‧Conical Elastomer

211‧‧‧ shrink end

212‧‧‧ wide mouth

22‧‧‧Parts

23‧‧‧Compression members

24‧‧‧Shell

241‧‧‧ accommodating space

242‧‧‧ The bottom of the space

243‧‧‧ openings

Claims (9)

A vehicle suspension structure comprising: a tapered elastic body having a solid tapered structure having a relatively constricted end and a wide mouth end, and one of the elastic coefficients of the tapered elastic body has nonlinear characteristics a pressing member disposed on the shrink end; and a top member connected to the wide mouth end; wherein the cone is when the total mass of the vehicle is a first mass The elastic system correspondingly has a first elastic coefficient, and one of the first vibration frequencies corresponding to the vehicle meets the following conditions: Wherein f1 is the first vibration frequency, k1 is the first elastic coefficient, and m1 is the first mass; wherein when the total mass of the vehicle is a second mass, the tapered elastic system has corresponding a second modulus of elasticity, and one of the second vibration frequencies corresponding to the vehicle meets the following conditions: Where f2 is the second vibration frequency, k2 is the second elastic coefficient, and m2 is the second mass; wherein the elastic modulus of the tapered elastic body is divided by the total mass of the vehicle After opening the root number, the following conditions are met: | f 1- f 2|<ε; where f1 is the first vibration frequency, f2 is the second vibration frequency, and ε is a predetermined vibration frequency difference. . The vehicle suspension structure according to claim 1, wherein the pressing member presses the tapered elastic body such that a relative distance between the narrowing end and the wide mouth end gradually becomes smaller, The coefficient of elasticity of the tapered elastomer gradually increases in a nonlinearity. The vehicle suspension structure of claim 1, wherein the cross-sectional area of the constricted end of the conical elastic body is divided by the wide mouth when the pressing member presses the conical elastic body downward. The ratio of the cross-sectional area of the end is increased. The vehicle suspension structure of claim 1, further comprising a housing having an accommodating space and an opening therethrough, one end of the pressing member exposing the opening, the accommodating The bottom member of the space contains the abutment member. The vehicle suspension structure of claim 4, wherein when the number of the tapered elastic bodies is N, each of the tapered elastic systems is sequentially stacked in the accommodating space in the same direction. The pressing member is disposed over the constricted end of the tapered elastomer closest to the opening, wherein N is a positive integer greater than one. The vehicle suspension structure according to claim 5, further comprising N-1 partition members respectively disposed between the tapered elastic bodies, wherein a periphery of each of the partition members corresponds to the receiving The perimeter wall of space. The vehicle suspension structure according to claim 5, wherein all or part of each of the tapered elastic bodies has the same material, size and shape. The vehicle suspension structure of claim 4, wherein the cone is When the number of the elastic bodies is N, the tapered elastic systems are disposed in the accommodating space without overlapping, and the wide end of each of the tapered elastic bodies is connected to the bottom of the accommodating space, and the pressure is A component is disposed over the constricted end of each of the tapered elastomers, wherein N is a positive integer greater than one. The vehicle suspension structure according to claim 8, wherein each of the tapered elastic bodies has the same material, size and shape.