Calculation method for deflection of main spring of two-stage auxiliary spring type non-constant frequency variable grade rigidity leaf spring
A calculation method and auxiliary spring technology, applied in the field of vehicle suspension leaf springs, can solve problems such as unsatisfactory and complicated calculation of main spring deflection
Inactive Publication Date: 2017-05-17
SHANDONG UNIV OF TECH
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Problems solved by technology
However, the calculation of the deflection of the main spring during the gradual change process is very complicated due to the two-stage secondary spring type non-equal bias frequency type gradient stiffness leaf spring, which is not only related to the structural parameters of the main spring and secondary spring, the clamping stiffness of the main spring, and the It is related to the composite clamping stiffness of secondary springs at all levels, and is also related to the contact load
According to the researched data, it can be seen that the calculation method of the main spring deflection of the two-stage auxiliary spring type non-equal deviation frequency type gradient stiffness leaf spring has not been given before, and most of them use the prototype test method to determine the main spring deflection. Therefore, It cannot meet the requirements of the rapid development of the vehicle industry and the modern CAD design and software development of suspension springs and suspensions
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[0039] Embodiment: The width b of a certain two-stage auxiliary spring type non-equal bias frequency type gradient stiffness leaf spring is 63mm, half of the clamping distance L of the saddle bolt 0 =50mm, elastic modulus E=200GPa, allowable stress [σ]=430MPa. The total number of main and auxiliary springs is N=5, wherein the number of main reeds is n=3, and the thickness of each main spring is h 1 =h 2 =h 3 =8mm, half of the active length is L 1T =525mm,L 2T =450mm, L 3T =350mm; half of the clamping length of each main spring is L 1 =L 1T -L 0 / 2=500mm, L 2 =L 2T -L 0 / 2=425mm, L 3 =L 3T -L 0 / 2=325mm. The number of sheets of the first secondary spring m 1 = 1 piece, thickness h A11 =h 4 =13mm, half of the active length is L A11T =250mm, half of the clamping length is L A11 =L 4 =L A11T -L 0 / 2=225mm. The number of pieces of secondary secondary spring m 2 = 1, thickness h A21 =h 5 =13mm, half of the active length is L A21T =150mm, half of the clampi...
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The invention relates to a calculation method for deflection of a main spring of a two-stage auxiliary spring type non-constant frequency variable grade rigidity leaf spring, and belongs to the technical field of suspension plate springs. According to the calculation method, the deflection of the main spring of the two-stage auxiliary spring type non-constant frequency variable grade rigidity leaf spring under various loadings can be calculated according to the structural parameters, modulus of elasticity, U-bolt clamping distance, specified load, and contact load of every time of each main spring and auxiliary spring. A prototype load deflection test result shows that the calculation method for deflection of the main spring of the two-stage auxiliary spring type non-constant frequency variable grade rigidity leaf spring is correct, which lays the groundwork for reliable design of the two-stage auxiliary spring type non-constant frequency variable grade rigidity leaf spring and CAD software development. Using the method can obtain an accurate and reliable main spring deflection calculation value under different loads, and improve product design level, quality and performance, and vehicle ride comfort and safety; meanwhile, the costs of design and test are reduced, and the rate of product development is increased.
Description
technical field [0001] The invention relates to a vehicle suspension leaf spring, in particular to a method for calculating the deflection of a main spring of a two-stage auxiliary spring type non-equal bias frequency type gradient stiffness leaf spring. Background technique [0002] In order to improve the design requirements of the ride comfort of the vehicle under the rated load, a two-stage secondary spring type gradient stiffness leaf spring can be used. The initial tangent arc height of the spring and the second-stage auxiliary spring, and the two-stage gradual gap allow the auxiliary spring to bear the load in advance, thereby reducing the stress of the main spring, that is, the two-stage auxiliary spring adopts a non-equal frequency type gradient stiffness leaf spring suspension , where the deflection of the main spring under different loads affects the gradient stiffness of the leaf spring, the static and dynamic deflection and bias frequency of the suspension, the ...
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IPC IPC(8): G06F17/50
CPCG06F30/17G06F30/20
Inventor 周长城于曰伟汪晓马驰骋杨腾飞王凤娟邵明磊
Owner SHANDONG UNIV OF TECH