A design method of a combined energy absorption device, a vehicle design method, and a vehicle

Abstract

This invention relates to the field of vehicle engineering, and discloses a design method for a combined energy-absorbing device, a vehicle design method, and a vehicle. The combined energy-absorbing device includes a front end plate 1 and a base 4 arranged in parallel. Multiple corrugated spacer tubes 2 with identical structures are fixedly disposed on the base 4 between the front end plate 1 and the base 4. The base 4 includes multiple base plates 41 corresponding to and fixed to the corrugated spacer tubes 2. The design method includes S1: single-tube parameter selection, including multiple parameters of the corrugated spacer tube 2; S2: multi-tube parameter selection, including the selection of the number of tubes and the selection of the height difference of the base plates 41. The design method provided by this invention makes the load peak of a single tube more uniform. By designing a base with gradually increasing height, each tube is positioned at a different horizontal position, giving the multi-tube combined energy-absorbing device a stable impact force curve like a honeycomb structure, thereby achieving better compatibility of excellent energy absorption characteristics such as high energy dissipation, low initial peak value, and small load fluctuation.

Description

Technical Field

[0001] This invention relates to the field of vehicle engineering technology, and in particular to a design method for a combined energy absorption device, a vehicle design method, and a vehicle. Background Technology

[0002] With the continuous increase in high-speed rail speeds, the requirements for train safety are also becoming increasingly stringent. Train collisions are extremely serious accidents, and energy-absorbing protection devices installed on trains can protect people's lives and property in the first instance. As a key energy dissipation device in the vehicle's crashworthiness structure, the energy absorption characteristics of the energy-absorbing device directly affect the vehicle throughout the collision process. However, with the increasing standards for collision safety speeds, traditional thin-walled energy-absorbing elements can no longer meet the increasingly stringent energy dissipation requirements. The development of combined composite energy-absorbing devices is the future trend of vehicle energy-absorbing devices.

[0003] Thin-walled circular tube structures can absorb a large amount of energy when subjected to impact, thus absorbing the impact. Although simply increasing the number of tubes can multiply the energy absorption capacity of the energy-absorbing protection device, some problems also exist. For example, the initial peak load and load fluctuation may be too large, and the size of the energy-absorbing device may be changed to adapt to complex working conditions, thus failing to guarantee the energy absorption effect. These problems may prevent the device from effectively protecting people's lives and property in the event of an accident, causing unnecessary losses. Summary of the Invention

[0004] To overcome the above technical problems, the present invention aims to provide a design method for a combined energy absorption device, a vehicle design method, and a vehicle, which includes a structural design of the corrugations of a single corrugated tube and a combined design of the corrugations at different horizontal positions, and a design that fully separates all peak loads of the corrugated tubes at multiple different horizontal positions, thereby achieving good compatibility of high energy absorption, low initial peak value, and small load fluctuation in the combined energy absorption device.

[0005] This invention provides the following technical solution: First aspect This invention provides a design method for a combined energy-absorbing device. The combined energy-absorbing device includes a front end plate (1) and a base (4) arranged in parallel. Between the front end plate (1) and the base (4), multiple corrugated spacer tubes (2) with the same structure are fixedly arranged on the base (4). The base (4) includes multiple bottom plates (41) that are fixed corresponding to the corrugated spacer tubes (2). The corrugated spacer tube (2) includes multiple corrugations (21) and rings (22) arranged at intervals. The intersection line of the outer surface of the corrugation (21) and the longitudinal section is an arc. The outer surface of the ring (22) is a flat cylindrical shape. The design method includes the following steps: S1: Single tube parameter selection, select the single tube parameters of the corrugated spacer tube (2), the single tube parameters include the amplitude of the corrugation (21). A b ,cycle T b Wall thickness t b The thickness of the ring (22) t z ,high h z The diameter of the corrugated spacer (2) D and the number of ripples N b ; Wherein, the amplitude of the ripple (21) A b Selected as the initial peak impact force of the corrugated spacer (2) PF 1. Less than the initial peak load of a conventional thin-walled circular tube with the same material, height, diameter, and wall thickness as the corrugated spacer tube (2). PF 1t That is, satisfying PF 1 < PF 1t And cause the corrugated spacer (2) to form an orderly deformation mode along the loading direction during axial loading; The thickness of the ring (22) t z and height h z Selected as satisfying t z = h z And make the ring (22) impact the initial peak value of the corrugated spacer (2). PF 1. The maximum radial load experienced when it occurs P zh The maximum radial load that the ring (22) can withstand without deformation is smaller than the maximum radial load that the ring (22) can withstand. P rmax That is, satisfying P zh < P rmax ; S2: Multi-tube parameter selection, select the number of the corrugated spacer tubes (2). N And according to the period of the ripple (21) T b and the number of the corrugated spacers (2) N Determine the height difference Δ between adjacent base plates (41) HThis causes the load peaks of the multiple corrugated spacers (2) to be misaligned in the loading displacement; wherein the height difference Δ H Satisfy: Δ H = ( T b -2) / (2N) (33).

[0006] According to some implementation methods, step S1 includes the following steps in sequence: S10: Determine the period of the corrugated spacer (2) according to the operating conditions. ,cycle The height of the corrugations (21) of the corrugated spacer (2) is determined; S11: Wall thickness of the corrugations (21) The selection of the corrugations (21) and the material utilization rate η Wall thickness The following relationship must be satisfied: (twenty two) That is, the wall thickness t b satisfy t b ≤3 T b / 20; S12: The number of ripples (21) The selection of the number of ripples The following relationship must be satisfied: (twenty four) S13: Pipe fitting diameter D The selection of the diameter of the corrugated spacer (2) D Determined by the following formula: (25) S14: Amplitude of the ripple (21) The selection Based on the initial peak load of a traditional thin-walled circular tube under the ideal progressive folding mode The calculation formula is: (26); The initial impact peak value of the corrugated spacer (2) for: ; The structure will exhibit an ordered deformation pattern along the loading direction when the following inequality is satisfied. (28) when PF 1 < PF 1t At that time, the correspondingA b As the amplitude of the ripple (21); S15: Thickness of the ring (22) and height The selection of, The maximum load that the ring (22) can withstand without deformation under radial load. for: (29) Since the corrugated spacer tube (2) did not deform, In the corrugated spacer tube (2), the maximum radial load on the annulus (22) is at the peak of the initial impact force. When it appears; The ring (22) is subjected to the maximum radial load. for: (30) The maximum radial load on the ring (22) Less than the maximum radial load

[0007] P zh ≤ P rmax (31).

[0008] According to some implementation methods, step S2 specifically includes the following steps: S21: Number of pipe fittings N The selection of the number of corrugated spacers (2) N The following relationship must be satisfied: (32) S22: Height difference The selection is based on the number of the corrugated spacers (2). N Determine the height difference of the base plate (41) : (33).

[0009] Second aspect The present invention also provides a vehicle design method, wherein the energy absorption device of the vehicle is designed using the design method of any of the above-described combined energy absorption devices.

[0010] Third aspect The present invention also provides a vehicle in which the energy absorption device is designed using the design method of the combined energy absorption device described above.

[0011] Compared with the prior art, the present invention has the following beneficial effects: This invention provides a design method for a combined energy-absorbing device, a vehicle design method, and a vehicle. The combination method is relatively simple, and it focuses on the design of the corrugated spacer tube and the combined structure of the vehicle's energy-absorbing device, aiming to make the load peak of the corrugated spacer tube uniform. Using this design method, appropriate parameters can be selected and the energy absorption effect of the energy-absorbing device can be guaranteed when facing complex working conditions.

[0012] By designing a single energy-absorbing corrugated spacer, the peak load of a single pipe fitting is made more uniform. Specifically, half a cycle of the original sine curve of the corrugated pipe sidewall is replaced with a straight line, leaving only half a cycle for deformation. To prevent deformation of the straight section, the wall thickness of the straight section is increased. To increase the utilization rate of the pipe fitting when absorbing energy, the length of the straight section is shortened as much as possible. To obtain stable and orderly deformation, the diameter of the pipe fitting is controlled within a suitable range.

[0013] By designing a base with gradually increasing height, each tube is positioned at a different level, altering the position of the sidewall crests. The position of the crests determines the timing of the wrinkle deformation, which in turn determines the timing of the subsequent peak load. By assigning appropriate and varied horizontal positions to each tube, the entire device can undergo wrinkle deformation at as many moments as possible during the deformation process. This allows different tubes to compensate for each other during deformation, and the subsequent peak loads of each tube are fully separated, significantly reducing the subsequent load fluctuations of the combined structure. This gives the multi-tube combined energy absorption device a stable impact force curve like a honeycomb structure, thus achieving a good balance between high energy dissipation, low initial peak load, and small load fluctuations. Attached Figure Description

[0014] Figure 1 The expected effect of the multi-tube combination provided by the present invention.

[0015] Figure 2 A simplified theoretical model of the corrugated portion provided by this invention.

[0016] Figure 3 This is a schematic diagram showing the magnitude of α when the initial impact force peak occurs, as provided by the present invention.

[0017] Figure 4 The present invention provides the classical unit theory for thin-walled circular tubes.

[0018] Figure 5 The parameters to be determined for the corrugated spacer tube provided by this invention.

[0019] Figure 6 The parameters to be determined for the multi-tube combination provided by this invention.

[0020] Figure 7 A flowchart for selecting pipe fitting parameters provided by the present invention.

[0021] Figure 8 This is a schematic diagram of the deformation of the corrugated portion provided by the present invention.

[0022] Figure 9 This is a schematic diagram of the radial load on the annular portion provided by the present invention.

[0023] Figure 10 The height difference "∆H" provided by this invention is shown in the load-displacement curve.

[0024] Figure 11 An exploded view of the combined energy-absorbing device provided by the present invention.

[0025] Figure 12 A schematic diagram of the multi-tube combination structure of the combined energy absorption device provided by the present invention.

[0026] Figure 13 This is a schematic diagram of the base structure provided by the present invention.

[0027] Figure 14 The present invention provides the deformation mode and load-displacement curve of the corrugated spacer tube.

[0028] Figure 15 The load-displacement curves of each pipe component in the multi-pipe assembly provided by the present invention.

[0029] Figure 16 A comparison between the combined tube provided by this invention and the traditional stacked tube.

[0030] The numbers in the attached diagram are: Front end plate 1; Corrugated spacer tube 2; Corrugation 21; Ring 22; Outer shell 3; Inner cavity 31; Base 4; Bottom plate 41. Detailed Implementation

[0031] The present invention will now be described in detail with reference to embodiments and accompanying drawings. However, it should be understood that the embodiments and drawings are for illustrative purposes only and do not constitute any limitation on the scope of protection of the present invention. All reasonable modifications and combinations included within the inventive spirit of the present invention fall within the scope of protection of the present invention.

[0032] The principle of this invention is based on the single-mand theory, which is introduced as follows: 1.1 Theoretical Analysis of Corrugation Spacing Management 1.1.1 Average crushing force Existing literature includes HAO W, XIE J, WANG F, et al. Analytical model of thin-walled corrugated tubes with sinusoidal patterns under axial impacting[J / OL]. International Journal of Mechanical Sciences, 2017, 128: 1-16. https: / / doi.org / 10.1016 / j.ijmecsci.2017.03.033. Hao et al. conducted a detailed study on complete corrugated tubes and proposed a corresponding theoretical model. In their study, the deformation process of the corrugated tube was divided into two parts: the first half-cycle and the second half-cycle. The corrugated spacer used in this invention only requires the first half-cycle, and the simplified model is as follows: Figure 2 As shown.

[0033] In Hao et al.'s research, the energy absorbed by the bellows was further divided into the energy of bending deformation and the energy of membrane deformation.

[0034] The energy absorbed by the bellows during the bending deformation in the first half of the cycle is: (1) in The diameter of the bellows. The fully plastic bending moment per unit perimeter, For material flow stress, For thickness, amplitude , The length of a semi-arc and The relationship is shown in the following formula: (2) When a bellows degenerates into a round pipe ( (for folded length) It can be simplified to the following expression (3) The energy absorbed during the deformation of the bellows membrane in the first half of the cycle is: (4) In the formula The force per unit length of the plastic film.

[0035] Total membrane energy and eccentricity coefficient m It is irrelevant. When the bellows is degenerate into a circular tube, Restored to the following expression (5) The average breaking force is the sum of the energy dissipated by bending deformation and the energy dissipated by membrane deformation. (6) (7) semi-arc length Due to stationary conditions Determine the semi-arc length for (8) Substituting equation (8) into equation (7), the average crushing force is: (9) For bellows, the distance between the inner and outer folds is exactly the same, therefore, let's assume... That's reasonable. Take 0.75.

[0036] For round tubes: (10) The simulation and theoretical errors for the corrugated spacer used in this invention are shown in Table 1.

[0037] Table 1 Comparison of average breaking force of corrugated spacers

[0038] 1.1.2 Initial peak impact force According to the research of Hao et al., the expression for the instantaneous impact force of the bellows in the first half of the cycle is: (11) in: (12) The initial peak impact force occurs when the first fold is about to deform but has not yet deformed, such as... Figure 3 As shown. The size of α at this time is: (13) Substituting equation (13) into equation (11) yields the initial peak impact force of the corrugated spacer.

[0039] When the bellows degenerates into a round pipe ( n When =0), the initial crushing force occurs during the initial crushing process, that is, when hour, (14) For a bellows, the distance between the inner and outer folds is exactly the same. Assume... m =0.5 is reasonable for the theoretical analysis of the corrugated pipe. The error between the simulation data and the theoretical data for the corrugated spacer used in this invention is shown in Table 2: Table 2 Comparison of peak initial impact forces of corrugated spacers Initial peak impact force (N) 24001 23021 4.1 For a non-corrugated circular pipe, the eccentricity coefficient is... m It is arbitrary and uncertain; the normalizing force is... m =0.25 and m =0.75 alternating. In existing literature SINGACE AA, ELSOBKY H, REDDY TY. On the eccentricity factor in the progressive crushing of tubes[J / OL]. International Journal of Solids and Structures, 1995, 32(24): 3589-3602. https: / / doi.org / 10.1016 / 0020-7683(95)00020-B. Singace et al. derived m The value, (15) 1.2 Classical Element Theory of Thin-Walled Circular Tubes Alexander's classical unit theory for thin-walled circular tubes comes from the existing literature ALEXANDER J M. ANAPPROXIMATE ANALYSIS OF THE COLLAPSE OF THIN CYLINDRICAL SHELLS UNDER AXIALLOADING[J / OL]. The Quarterly Journal of Mechanics and Applied Mathematics, 1960, 13(1): 10-15. https: / / doi.org / 10.1093 / qjmam / 13.1.10. The literature discloses a method that can be used to derive the fold half-wavelength of the circular tube. Its simplified model diagram is as follows: Figure 4 As shown. When the curvature angle of the straight line segment... Increase At that time, the average tensile strain of the straight segment for: (16) In the formula D The diameter of the structure, The half-wavelength of the folds in the circular tube. t The thickness of the pipe fitting.

[0040] Therefore, the work done by the straight segment under tension It can be calculated using the following formula: (17) In the formula For the flow stress of the material, The yield strength of the material.

[0041] Work done by the bending deformation of the plastic hinge section Calculated using the following formula (18) The energy dissipated by a deformed fold during its complete formation can be determined by multiplying the average load by the fold wavelength: (19) The experimental results show that the structure's material utilization rate cannot reach 100% during the energy absorption process, and the actual deformation height of a single fold cannot reach [the required value]. Its value is approximately 70%-75% of the ideal half-wavelength of the fold. Therefore: (20) In the formula This refers to the material utilization rate of thin-walled circular tubes.

[0042] Unknown variable: wrinkled half wavelength The solution can be obtained by minimizing energy dissipation under stable asymptotic folding deformation: (twenty one) The technical solution of the present invention will now be described in conjunction with the accompanying drawings. Example 1

[0043] In fields requiring collision energy absorption, such as passive protection devices for trains and energy-absorbing devices for vehicles, space constraints often necessitate redesigning the dimensions of these devices. However, the crashworthiness of the redesigned energy-absorbing device cannot be guaranteed. Therefore, a design method for a modular energy-absorbing device is proposed, which allows for the selection of appropriate dimensional parameters under various operating conditions while maximizing crashworthiness. To facilitate application in practical conditions and the selection of suitable structural parameters, this embodiment proposes a design method for a modular energy-absorbing device. This design method is based on an energy-absorbing device constructed as follows: Figure 11 and Figure 12 The energy-absorbing device includes a front end plate 1 and a base 4 placed in parallel. Multiple cylindrical corrugated spacer tubes 2 are arranged on the base 4. The base 4 is composed of multiple bottom plates 41 fixed to the bottoms of the corrugated spacer tubes 2. The front end plate 1 and the base 1 are surrounded by a thin-walled outer shell 3. The cavity in the outer shell 3 forms an inner cavity 31, which accommodates the multiple corrugated spacer tubes 2. The base 4 is fixedly connected to the front end of the vehicle. Figure 12 Nine corrugated spacers are marked as A1 to A9.

[0044] The expected effect of the multi-tube combined energy absorption device is as follows Figure 1 As shown, the impact force peaks of other pipe fittings are evenly distributed between the two impact force peaks of pipe fitting 1, making the load-displacement curve of the combined pipe fitting very stable with almost no load fluctuation.

[0045] The structural parameters of the corrugated spacer 2 of the energy absorption device proposed in this embodiment are as follows: Figure 5 , Figure 6 As shown. The corrugated spacer tube 2 has multiple corrugations 21 and rings 22 spaced along its length. The intersection of the outer surface of the corrugation 21 and the longitudinal section is an arc, and the outer surface of the ring 22 is a flattened cylinder. Therefore, a single tube section includes the following 7 parameters: the amplitude of the corrugated section... ,cycle Wall thickness The thickness of the circular part ,high The diameter of the pipe fitting D Number of ripples The multi-pipe assembly includes the following two parameters: the number of pipe fittings. N Height difference between pipe fittings The parameters of the pipe fittings need to be selected in a specific order, and the selection process is as follows: Figure 7 As shown.

[0046] according to Figure 7 The design method for a combined energy absorption device includes the following steps: S1: Single tube parameter selection; S10: Period of a single corrugated spacer 2 The period needs to be determined first. This directly determines the height of a single corrugated section of the corrugated spacer 2, which can be selected according to the actual working conditions; S11: Corrugated section wall thickness The selection; The deformation process of the corrugated part is as follows: Figure 8 As shown. To ensure that the corrugated part is not torn during compression and to maximize material utilization. η Wall thickness The following relationship must be satisfied: (twenty two) At the same time, to ensure that the energy absorption of the pipe fittings is not too small, the wall thickness is... The largest possible value should be selected. If... Choosing too small a size will cause two problems: (1) the pipe fittings will become difficult to process; (2) the energy absorption capacity of the pipe fittings will decrease. Therefore, it is recommended to... Choose the largest possible size; S12: Number of ripples The selection; Guillow et al. studied the axial compression deformation mode of a circular tube using the same material as the present invention. This study is based on existing literature: GUILLOW SR, LU G, GRZEBIETA R H. Quasi-static axial compression of thin-walled circular aluminum tubes[J / OL]. International Journal of Mechanical Sciences, 2001, 43(9): 2103-2123. https: / / doi.org / 10.1016 / S0020-7403(01)00031-5. The literature indicates that when the height of a typical circular tube... ,diameter Wall thickness A circular tube will undergo circumferential deformation when the following relationship is satisfied: (twenty three) As can be seen from equation (23), the pipe fittings in this embodiment should not be too high, otherwise Euler instability will occur, and the number of corrugations will be affected. The height of the pipe fitting is directly determined by its diameter, so it must be limited. The height, diameter, and wall thickness of a standard round pipe are the same as those of a corrugated spacer pipe, with the wall thickness being the same as the corrugated portion. This is to avoid Euler instability in the corrugated spacer pipe due to excessive height, as standard round pipes are more prone to Euler instability than corrugated spacers. Therefore, if Euler instability does not occur in a standard round pipe at this height, it will certainly not occur in the corrugated spacer pipe. This is an analogy between the standard round pipe and the corrugated spacer pipe. The most direct factor determining the height of the corrugated spacer pipe is the number of corrugations. Therefore, this principle is used to determine the number of ripples. The constraints. According to Guillow et al., the number of ripples... The following relationship must be satisfied: (twenty four) S13: Pipe fitting diameter D The selection; When a corrugated spacer is reverted to a conventional circular tube with the same material, height, diameter, and wall thickness, if the initial impact force peak of the corrugated spacer is less than that of the conventional circular tube, then the corrugated spacer can achieve stable and orderly deformation under axial compression. The diameter is determined based on this principle. D Amplitude of the ripple portion According to equation (21), Diameter of corrugated spacer tube and traditional round tubeD It can be determined by the following formula: (25) S14: Amplitude of the rippled portion The selection; Based on the initial peak load of a traditional thin-walled circular tube under the ideal progressive folding mode The calculation formula is: (26) Peak initial impact force of the corrugated spacer for:

[0047] When the following inequalities are satisfied, the structure has higher stability and is more likely to exhibit an ordered deformation mode along the loading direction. (28) To ensure the energy absorption of the pipe fittings, the amplitude of the corrugated section... It should not be too large.

[0048] S15: Thickness of the circular portion and height The selection Because the limiting effect on the deformation of the corrugated parts is similar, to facilitate the selection of parameters, let To ensure the restraining effect of the ring on the deformation of the corrugated part, the ring must not deform under the maximum radial load. According to existing literature REID SR, REDDY TY. Effect of strain hardening on the lateral compression of tubes between rigid plates[J / OL]. International Journal of Solids and Structures, 1978, 14(3): 213-225. https: / / doi.org / 10.1016 / 0020-7683(78)90026-4. Reid et al. studied the maximum load that the ring can withstand without deformation under radial load. for: (29) Since the pipe fittings did not deform, In a corrugated spacer, the maximum radial load on the annular portion occurs at the peak of the initial impact force. When it appears, such as Figure 9 As shown.

[0049] The annular section experiences the greatest radial load. for: (30) Maximum radial load received by the annular section It must be less than the maximum radial load.

[0050] (31) S2: Multi-tube parameter selection; S21: Number of pipe fittings N The selection; The expected effect of combining the various corrugated spacers is as follows: Figure 10 As shown, the height difference between the various pipe fittings This is also the difference between the peak impact forces. To ensure the combination's effectiveness in reducing load fluctuations, the peak impact forces of each pipe component need to be evenly distributed; neither should any pipe component be without load at any given moment, nor should the peak impact forces be stacked at the same time. Based on extensive simulation data, when... This can effectively reduce load fluctuations. If the height difference is further reduced... The effect of reducing load fluctuations is not significant; in fact, it increases process costs. If the need to reduce load fluctuations is not significant, the height difference can be appropriately increased. Height difference The number of pipe fittings is directly determined. N Based on the above analysis, the number of pipe fittings N The following relationship must be satisfied: (32) S22: Height difference The selection; Based on the number of pipe fittings N The height difference can be determined. : (33).

[0051] Example 2 According to the design method provided in Embodiment 1, the structure of an energy absorption device consisting of corrugated spacers at different horizontal positions was first selected, such as... Figure 11 As shown, it includes a thin-walled outer shell 3 with an inner cavity 31, multiple corrugated spacer tubes 2 placed inside the inner cavity 31 for energy absorption, a front end plate 1 covering the inner cavity 31, and a base 4 covering the inner cavity 31. All the energy-absorbing corrugated spacer tubes 2 are exactly the same. The base 4 includes multiple base plates 41 corresponding to the corrugated spacer tubes 2. The base plates 41 have different horizontal heights, that is, the lower ends of the corrugated spacer tubes 2 have a height difference in the horizontal position.

[0052] The structural parameters of the corrugated spacer used in this embodiment are shown in Table 3: Table 3 Parameters of Corrugated Spacer The parameters of its multi-tube combination are shown in Table 4: Table 4 Multi-tube combination parameters parameter 9 1 Multi-tube combination methods such as Figure 12 As shown, nine pipe fittings, A1-A9, are arranged on the base 4, with a height difference between each base plate 41. The structure of base 4 is as follows Figure 13 As shown. This ensures that the peak impact forces among the nine pipe fittings are sufficiently misaligned and mutually compensate for each other, with pipe fittings deforming at all times, and that the peak impact forces do not overlap.

[0053] The deformation mode and load-displacement curve of the corrugated spacer are as follows: Figure 14 As shown, the corrugated spacer tube undergoes orderly and stable annular deformation, with each impact force peak corresponding to a fold deformation. Furthermore, the corrugated spacer tube is designed so that the intervals between each impact force peak are essentially the same, which is highly beneficial for subsequent multi-tube assembly.

[0054] The load-displacement curves of pipe fittings A1~A9 are as follows: Figure 15 As shown in the figure. It can be seen that when the height difference between the pipe fittings... At that time, all loads are fully separated, and the peak impact force is evenly distributed at every moment of deformation.

[0055] A comparison between the combined tube in this embodiment and a traditional stacked tube. Figure 16 As shown in Table 5, after the misalignment compensation of each pipe, compared with the traditional stacked pipe, the patented combined pipe reduces the load fluctuation by 67.2% while only reducing the energy absorption by 4.8%.

[0056] Table 5 Comparison between the combined tube provided by this invention and the traditional stacked tube Load fluctuation 1072 351 67.2 Energy absorbed (kJ) 14.57 13.86 4.8 The above embodiments are merely preferred embodiments of the present invention, and the scope of protection of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the present invention's concept are within the scope of protection of the present invention. It should be noted that for those skilled in the art, improvements and modifications made without departing from the principles of the present invention should also be considered within the scope of protection of the present invention.

Claims

1. A design method for a combined energy-absorbing device, the combined energy-absorbing device comprising a front end plate (1) and a base (4) arranged in parallel, wherein multiple corrugated spacer tubes (2) with identical structures are fixedly disposed on the base (4) between the front end plate (1) and the base (4); the base (4) comprises multiple bottom plates (41) fixed corresponding to the corrugated spacer tubes (2), the corrugated spacer tubes (2) comprising multiple corrugations (21) and rings (22) arranged at intervals, wherein the intersection line of the outer surface of the corrugation (21) and the longitudinal section is an arc, and the outer surface of the ring (22) is a flat cylindrical shape, characterized in that, The design method includes the following steps: S1: Single tube parameter selection, select the single tube parameters of the corrugated spacer tube (2), the single tube parameters include the amplitude of the corrugation (21). A b ,cycle T b Wall thickness t b The thickness of the ring (22) t z ,high h z The diameter of the corrugated spacer (2) D and the number of ripples N b ; Wherein, the amplitude of the ripple (21) A b Selected as the initial peak impact force of the corrugated spacer (2) PF 1 is less than the initial peak load of a conventional thin-walled circular tube with the same material, height, diameter, and wall thickness as the corrugated spacer tube (2). PF 1t That is, satisfying PF 1 < PF 1t And cause the corrugated spacer (2) to form an orderly deformation mode along the loading direction during axial loading; The thickness of the ring (22) t z and height h z Selected as satisfying t z = h z And make the ring (22) impact the initial peak value of the corrugated spacer (2). PF 1. The maximum radial load experienced when it occurs P zh The maximum radial load that the ring (22) can withstand without deformation is smaller than the maximum radial load that the ring (22) can withstand. P rmax That is, satisfying P zh < P rmax ; S2: Multi-tube parameter selection, select the number of the corrugated spacer tubes (2). N And according to the period of the ripple (21) T b and the number of the corrugated spacers (2) N Determine the height difference Δ between adjacent base plates (41) H This causes the load peaks of the multiple corrugated spacers (2) to be misaligned in the loading displacement; wherein the height difference Δ H satisfy: D H =( T b -2) / (2N) (33).

2. The design method of the combined energy absorption device according to claim 1, characterized in that: Step S1 includes the following steps in sequence: S10: Determine the period of the corrugated spacer (2) according to the operating conditions. ,cycle The height of the corrugations (21) of the corrugated spacer (2) is determined; S11: Wall thickness of the corrugations (21) The selection of the corrugations (21) and the material utilization rate η Wall thickness The following relationship must be satisfied: ； That is, the wall thickness t b satisfy t b ≤3 T b / 20; S12: The number of ripples (21) The selection of the number of ripples The following relationship must be satisfied: ； S13: Pipe fitting diameter D The selection of the diameter of the corrugated spacer (2) D Determined by the following formula: ； S14: Amplitude of the ripple (21) Selection Based on the initial peak load of a traditional thin-walled circular tube under the ideal progressive folding mode The calculation formula is: ； The initial impact peak value of the corrugated spacer (2) for: The structure will exhibit an ordered deformation pattern along the loading direction when the following inequality is satisfied. when PF 1 < PF 1t At that time, the corresponding A b As the amplitude of the ripple (21); S15: Thickness of the ring (22) and height The selection of, The maximum load that the ring (22) can withstand without deformation under radial load. for: ； Since the corrugated spacer tube (2) did not deform, In the corrugated spacer tube (2), the maximum radial load on the annulus (22) is at the peak of the initial impact force. When it appears; The ring (22) is subjected to the maximum radial load. for: ； The maximum radial load on the ring (22) Less than the maximum radial load , P zh ≤ P rmax (31)。 3. The design method of the combined energy absorption device according to claim 1, characterized in that: Step S2 specifically includes the following steps: S21: Number of pipe fittings N The selection of the number of corrugated spacers (2) N The following relationship must be satisfied: ； S22: Height difference The selection is based on the number of the corrugated spacers (2). N Determine the height difference of the base plate (41) : 。 4. A vehicle design method, characterized in that: The energy absorption device of the vehicle is designed using the design method of the combined energy absorption device as described in any one of claims 1 to 3.

5. A vehicle, characterized in that: The energy absorption device of the vehicle is designed using the design method of the combined energy absorption device as described in any one of claims 1 to 3.

Images