Novel aluminum alloy fuel tank structure

Abstract

This invention discloses a novel aluminum alloy fuel tank structure, comprising a tank body, an L-shaped bracket fitted to the outer side of the tank body, and a pull strap with an L-shaped structure hinged to the top of the bracket, which matches the top of the tank body. The bottom end of the pull strap is pre-tightened to the bottom end of the bracket via an inclined pre-tightening bolt. A lower rubber pad is provided between the bracket and the tank body; an upper rubber pad is provided between the pull strap and the tank body; vertically arranged partitions with flanges are fixedly installed on the inner wall of the tank body at locations corresponding to the bracket; the partitions have several evenly distributed ribs on their vertical dividing plates; several plug weld holes are evenly distributed on the flanges of the partitions; the partitions are integrated with the tank body through the plug weld holes; a first circular hole is opened at the 90° bend of the lower rubber pad; a second circular hole is opened at the 90° bend of the upper rubber pad. This novel aluminum alloy fuel tank structure significantly reduces stress at the partition welds, welding time, and welding rod consumption, and reduces the wall thickness of the partitions and the tank body while meeting service life requirements.

Description

Technical Field

[0001] This invention relates to the field of fuel tanks, specifically to a novel aluminum alloy fuel tank structure. Background Technology

[0002] The fuel tank is one of the core components of a commercial vehicle. If the fuel tank cracks or leaks, it will not only affect the normal operation of the vehicle, but also lead to a major safety accident.

[0003] As a crucial component of the fuel tank assembly, the fuel tank baffle provides necessary rigidity when securing the fuel tank strap to ensure its effectiveness. Simultaneously, the baffle must withstand the impact forces generated by fuel sloshing during vehicle movement, acceleration, and deceleration. However, existing methods for securing the fuel tank baffle to the fuel tank boom have the following drawbacks:

[0004] (1) One type is to punch protrusions at the four rounded corners of the tank arm and punch grooves at the four corresponding rounded corners of the partition. Then, the partition is fixed by using the pre-tightening force of the pull belt to keep the grooves and protrusions in contact. In this type of tank, the connection in the middle of the partition is relatively weak. Under harsh working conditions, it is easy to shake, wear the surface, generate impurities, and affect the quality of the oil.

[0005] (2) Another method is to fully weld the edge of the partition to the tank wall. Although this reduces the risk of weld cracking to a certain extent, it brings problems of low welding efficiency and large weld consumption. Summary of the Invention

[0006] The purpose of this invention is to provide a novel aluminum alloy fuel tank structure to solve the problems mentioned in the background art, such as the existing fastening method of fuel tank partition and fuel tank cylinder arm, which makes the fuel tank prone to shaking, surface wear, impurities, and affecting fuel quality, as well as low welding efficiency and high weld consumption.

[0007] To achieve the above objectives, the present invention provides the following technical solution: a novel aluminum alloy fuel tank structure, comprising a tank body, an L-shaped bracket fixedly fitted to the outside of the tank body, the top of the bracket being hinged to the top of an L-shaped pull strap matching the tank body; the bottom of the pull strap being pre-tightened to the bottom of the bracket by an inclined pre-tightening bolt; and a lower rubber pad being fitted between the inner wall of the bracket and the outer wall of the tank body; an upper rubber pad being fitted between the inner wall of the aforementioned pull strap and the outer wall of the tank body; vertically arranged partitions with flanges being fixedly fitted to the inner wall of the tank body at locations corresponding to the brackets; several ribs being evenly distributed on the vertically dividing plate of the partitions; several plug welding holes being evenly distributed on the flanges of the partitions; the partitions being integrated with the tank body through the plug welding holes; a first round hole being opened at the 90° bend of the lower rubber pad; and a second round hole being opened at the 90° bend of the upper rubber pad.

[0008] In the above technical solution, preferably, the plug welding hole is located at the center of the partition flange.

[0009] In the above technical solution, preferably: the partition is a square structure; the chamfer of the square partition is a rounded chamfer; the plug welding holes are not only evenly distributed on the straight flange of the partition; the plug welding holes are also evenly distributed on the rounded chamfer of the partition.

[0010] In the above technical solution, preferably: there are two plug welding holes at the chamfered corner of the partition plate; and three plug welding holes at the straight flange of the partition plate 3.

[0011] In the above technical solution, preferably, the plug weld hole is a strip-shaped plug weld hole with a rounded chamfer.

[0012] In the above technical solution, preferably: the box body cross-section is 700x700mm; the ribs are long strip structures; the rib width is ≥3dmm, where d is the width of the weld hole of the partition flange, and 8mm≤d≤12mm; the rib height is ≥1dmm; the rib length is Z, and 100≤Z≤1.5Tmm, where T is the width of the partition flange.

[0013] In the above technical solution, preferably: the center distance between adjacent plug weld holes at the straight flange of the partition is L, 80mm≤L≤100mm; the distance H from the center of the plug weld hole to the outer side of the flange of the partition satisfies 0.5T mm≤H≤0.6T mm, where T is the width of the flange of the partition; the length B of the plug weld hole satisfies 0.5T mm≤B≤0.7T mm; the distance between adjacent plug weld holes at the chamfered corner of the partition and the plane of angular symmetry is ≥4d mm, where d is the width of the plug weld hole at the flange of the partition, and 8mm≤d≤12mm; other parameters of the plug weld holes at the chamfered corner of the partition are consistent with the parameters of the plug weld holes at the straight flange of the partition.

[0014] In the above technical solution, preferably: there are two first circular holes, and the diameter of the two first circular holes is d2, and satisfies 10mm≤d2≤0.8m, where m is the length of the flange on both sides of the π-shaped bracket; the centers of the two first circular holes are respectively located at the center of the π-shaped bracket; the diameter of the second circular hole is d1, and satisfies 20mm≤d1≤0.8T, where T is the width of the flange of the partition.

[0015] In the above technical solution, preferably: when the partition is impacted by oil in the ±X direction, the pressure Pm at point B in the middle of the partition is 0.6 times the pressure P1 at point A at the bottom of the partition, i.e., Pm / P1 = 0.6; when the partition is impacted in the x direction, the weld of the plug weld hole mainly bears the shear force; and when the normal pressure Fz in the vertical direction of the partition is 1 / 0.6 = 1.6 times the normal pressure Fy in the y direction of the partition, the friction between the partition and the box body will achieve optimal protection for the weld of the plug weld hole; at this time, the preload force of the preload bolt, i.e., the angle θ between the axial force of the preload bolt and the horizontal direction x, satisfies That is, the axial force inclination angle of the pre-tightening bolt is θ = 58°.

[0016] In the above technical solution, preferably, both the box body and the partition are made of aluminum alloy.

[0017] Compared with the prior art, the beneficial effects of the present invention are:

[0018] 1. By placing the weld seam in the long strip plug weld hole in the middle of the partition flange, the normal pressure generated by the pre-tensioning force of the pull belt and the friction between the pressing surfaces are used to "protect" the middle weld seam, and according to the pressure distribution characteristics of the oil on the partition and cylinder wall under different vehicle operating conditions.

[0019] 2. The weld arrangement has been optimized. By matching the stiffness of the partition and rubber pad, sufficient clamping force and friction are ensured near the optimized weld.

[0020] 3. Based on the stress characteristics of the weld seams at different flanges of the upper, lower, left, and right partitions, the angle of the axial force direction of the pre-tightening bolts was rationally designed. The improvements made will significantly reduce the stress at the partition weld seams, welding time, and electrode consumption, and reduce the thickness of the partition and cylinder walls while meeting the service life requirements.

[0021] 4. Overcome the problem of unreasonable distribution of preload on the weld seam of the oil tank diaphragm caused by the uncertain angle of the pull-down bolt in the existing technology, as well as its derivative problems. Attached Figure Description

[0022] Figure 1 This is the front view of the present invention;

[0023] Figure 2 This is an exploded view of the present invention;

[0024] Figure 3 For the present invention Figure 2 A combination diagram;

[0025] Figure 4 Axonometric drawing of the diaphragm;

[0026] Figure 5 This is the front view of the partition;

[0027] Figure 6 This is a schematic diagram showing the distribution of the weld holes in the diaphragm.

[0028] Figure 7 for Figure 6 Dimensional drawing of the weld holes in the middle partition plate;

[0029] Figure 8 Axonometric drawing of the bracket;

[0030] Figure 9 Axonometric drawing of the lower rubber pad;

[0031] Figure 10 Isometric view of the upper rubber pad;

[0032] Figure 11 This is a schematic diagram of the present invention subjected to an x-axis impact;

[0033] Figure 12 This is a schematic diagram of the present invention subjected to an impact in the y-direction;

[0034] Figure 13 This is a schematic diagram of the present invention subjected to a z-axis impact;

[0035] Figure 14 This is a schematic diagram showing the expected inclination angle of the bolt in this invention;

[0036] In the diagram: 1. Housing; 2. Oil nozzle; 3. Partition; 4. Lower rubber pad; 5. Bracket; 6. Upper rubber pad; 7. Strap; 8. Welded hole; 9. Rib; 10. First round hole; 11. Second round hole; 12. Preload bolt. Detailed Implementation

[0037] The following will refer to the appendices in the embodiments of the present invention. Figures 1-14 The technical solutions in the embodiments of the present invention are clearly and completely described herein. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0038] A novel aluminum alloy fuel tank structure includes a tank body 1. An L-shaped bracket 5 is fixedly fitted to the outer side of the tank body 1. The top of the bracket 5 is hinged to the top of an L-shaped pull strap 7 that matches the tank body 1. The bottom of the pull strap 7 is pre-tightened to the bottom of the bracket 5 by an inclined pre-tightening bolt 12. A lower rubber pad 4 is fitted between the inner wall of the bracket 5 and the outer wall of the tank body 1. An upper rubber pad 6 is fitted between the inner wall of the pull strap 7 and the outer wall of the tank body 1.

[0039] The inner wall of the box 1 is fixed with vertically arranged partitions 3 with flanges at the corresponding brackets 5; the partitions 3 are vertically divided by a number of ribs 9 evenly distributed; by designing ribs 9 near the middle of the flanges of the partitions 3, the ribs 9 can increase the local rigidity.

[0040] The partition 3 has several weld holes 8 evenly distributed at its flange; the partition 3 is connected to the box body 1 through the weld holes 8; a first round hole 10 is opened at the 90° bend of the aforementioned lower rubber pad 4; a second round hole 11 is opened at the 90° bend of the aforementioned upper rubber pad 6.

[0041] Regarding the stiffness matching design of the rubber pads: Circular holes are designed at the chamfered corners of the upper and lower rubber pads. These localized openings allow for adjustment of the normal pressure distribution of the pull strap at the chamfered corners and the center of partition 3, preventing excessive concentration of preload at the rounded corners. The diameter of the circular holes is determined to ensure that the normal pressure around the weld hole in the center of partition 3 is not less than the normal pressure around the weld hole at the chamfered corner.

[0042] Specifically: a 36mm diameter circular hole is designed at the chamfer center of the upper rubber pad 6, and two 26mm diameter circular holes are opened at the chamfer of the upper rubber pad 6. The center of the circular holes is located at the center of the flanges on both sides of the fuel tank bracket 5. The purpose of setting the circular holes on the upper and lower rubber pads is to transfer the concentrated pre-tightening stress of the rubber pad from the original chamfer to the middle of the flange of the partition 3 for reasonable distribution.

[0043] In the above embodiments, preferably, the plug welding hole 8 is located at the center of the flange of the partition plate 3.

[0044] In the above embodiments, preferably: the partition 3 is a square structure; the chamfer of the square partition 3 is a rounded chamfer; the plug welding holes 8 are not only evenly distributed on the straight flange of the partition 3; the plug welding holes 8 are also evenly distributed on the rounded chamfer of the partition 3.

[0045] In the above embodiments, preferably: there are two plug welding holes 8 at the chamfered corner of the partition 3; and there are three plug welding holes 8 at the straight flange of the partition 3.

[0046] In the above embodiments, preferably, the plug welding hole 8 is a strip-shaped plug welding hole with a rounded chamfer.

[0047] Regarding the arrangement of the plug weld hole 8: The weld between the flange of the partition plate 3 and the oil tank body is arranged at the center of the flange. When oil impacts from different directions, the preload of the tension belt 7, the normal clamping force generated by the flange of the partition plate 3, and the resulting frictional force always "protect" the central weld, thus significantly reducing the shear force transmitted to the weld. Compared to the weld edge arrangement, the centrally located plug weld hole 8 is not subject to bending moment.

[0048] Regarding the distribution of the plug weld holes 8: The plug weld holes 8 are arranged in the middle of the flange of the partition plate 3 and at the four rounded chamfers. Three plug weld holes 8 are arranged in the middle position, and two plug weld holes 8 are arranged at the chamfers. The upper and lower plug weld holes 8 welds mainly bear the impact force from the x-direction, while the front and rear plug weld holes 8 welds bear part of the x-direction and y-direction impact forces. The equivalent concentrated force of the oil is located near the center position. The middle weld needs to bear the main impact shear force of the oil, and at the same time, it can reduce the bending moment generated by the oil impact force on the four corner welds. Meanwhile, the plug weld holes 8 welds at the four corners play an auxiliary role in dispersing the moment.

[0049] Regarding the shape of the plug weld hole 8: The plug weld hole 8 is a closed strip shape. Compared to a single strip weld, the stress of the closed plug weld hole 8 is continuously distributed, which can reduce stress concentration at the ends. At the same time, the annular plug weld hole ensures the weld length without significantly weakening the stiffness of the partition plate 3.

[0050] Specifically: the design of the location, shape, and size of the plug weld holes 8 is as follows: there are three plug weld holes 8 in the middle of each flange; the distance between the plug weld holes 8 on both sides and the center of the middle hole is no more than 100mm; the distance between the plug weld holes 8 and the outer edge of the flange is no less than 25mm; the width of the plug weld hole 8 is 10mm; and the length is no more than 25mm. Two plug weld holes 8 are symmetrically distributed at the four chamfers of the partition plate 3; the straight-line distance between the two plug weld holes 8 and the center of the chamfer is no less than 40mm.

[0051] In the above embodiments, preferably: the cross-sectional dimensions of the box body 1 are 700x700mm; the rib 9 is a long strip structure; the width of the rib 9 is ≥3d mm, where d is the width of the flange plug welding hole 8 of the partition 3, and 8mm≤d≤12mm; the height of the rib 9 is ≥1d mm; the length of the rib 9 is Z, and 100≤Z≤1.5T mm, where T is the flange width of the partition 3.

[0052] Specifically: the width of the rib 9 is not less than 30mm and the height is not less than 10mm. The outer side of the rib 9 extends to the chamfer of the flange of the partition plate 3, and the inner side extends to a distance of more than 40mm from the chamfer. The partition plate 3 is installed inside the tank body wall, and the circumferential weld is completed at the welding hole 8 of the partition plate 3. The rib 9 is located at the geometric center of the flange.

[0053] In the above embodiments, preferably: the center distance between adjacent plug weld holes 8 at the straight flange of the partition 3 is L, 80mm≤L≤100mm; the distance H between the center of the plug weld hole 8 and the outer side of the flange of the partition 3 satisfies 0.5T mm≤H≤0.6T mm, where T is the width of the flange of the partition 3; the length B of the plug weld hole 8 satisfies 0.5T mm≤B≤0.7T mm; the distance between adjacent plug weld holes 8 at the rounded chamfer of the partition 3 and the plane of angular symmetry is ≥4d mm, where d is the width of the plug weld hole 8 at the flange of the partition 3, and 8mm≤d≤12mm; other parameters of the plug weld hole 8 at the rounded chamfer of the partition 3 are the same as those of the plug weld hole 8 at the straight flange of the partition 3.

[0054] Regarding the matching design of the stiffness of the partition plate 3: By designing the rib 9 near the middle of the flange of the partition plate 3, the local stiffness can be increased. The pre-tightening force of the pull strip 7 will generate a large normal pressure and friction force in the position with high stiffness, thereby achieving "fixed-point protection" of the weld.

[0055] In the above embodiments, preferably: there are two first circular holes 10, and the diameter of both first circular holes 10 is d2, satisfying 10mm≤d2≤0.8m, where m is the length of the flanges on both sides of the π-shaped bracket 5; the centers of the two first circular holes 10 are respectively located at the center of the π-shaped bracket 5; the diameter of the second circular hole 11 is d1, and satisfies 20mm≤d1≤0.8T, where T is the width of the flange of the partition 3.

[0056] Specifically: the diameter of the first circular hole 10 is 26mm, and the diameter of the second circular hole 11 is 36mm.

[0057] In the above embodiments, preferably: when the partition 3 is impacted by oil in the ±X direction, the pressure Pm at point B in the middle of the partition 3 is 0.6 times the pressure P1 at point A at the bottom of the partition 3, i.e., Pm / P1 = 0.6; when the partition 3 is impacted in the x direction, the weld of the plug weld hole 8 of the partition 3 mainly bears shear force; and when the normal pressure Fz in the vertical direction of the partition 3 is 1 / 0.6 = 1.6 times the normal pressure Fy in the y direction of the partition 3, the friction between the partition 3 and the housing 1 will achieve optimal protection for the weld of the plug weld hole 8; at this time, the preload force of the preload bolt 12, i.e., the angle θ between the axial force of the preload bolt 12 and the horizontal direction x, satisfies That is, the axial force inclination angle of the pre-tightening bolt 12 is θ = 58°.

[0058] When in use: design the pre-tightening bolt 12 at the corresponding installation position at the lower end of the oil tank bracket 5 and the pull strap 7, ensuring that the pre-tightening bolt 12 is close to the lower front chamfer of the oil tank, and that the axis after pre-tightening forms a 58-degree angle with the horizontal direction.

[0059] It should be noted that the directional design of the preload bolt 12 is as follows:

[0060] When the oil is impacted in the ±X direction, the baffle 3 is mainly subjected to the impact force in the x direction. The baffle 3 in the middle of the oil tank is subjected to the greatest impact force. The pressure Pm at point B in the middle of the baffle 3 is about 0.6 times the pressure P1 at point A at the bottom.

[0061] When the oil impacts in the -y and +z directions, the force on the partition 3 is relatively small. The main stress forms are the shear force and bending moment generated by the pressure-bearing area of ​​the middle partition 3 on the area of ​​the pull belt 7. The load is mainly borne by the pull belt 7. When the deformation of the pull belt 7 is large, the weld of the partition 3 will bear part of the load.

[0062] When the oil impacts in the +y and -z directions, the pressure in the bearing area of ​​the middle partition 3 will generate shear force and bending moment on the edge of the +y side bracket 5 of the oil tank. The weld of the partition 3 is located in the middle of the bracket 5 and is subjected to less force.

[0063] When a vehicle is in motion, the fuel tank is actually subjected to impact acceleration from two or three directions simultaneously.

[0064] When subjected to an impact in the x-direction, the weld of the diaphragm 3 mainly bears the shear force; only when the vertical normal pressure Fz is 1 / 0.6 = 1.6 times the y-direction normal pressure Fy can the friction between the diaphragm 3 and the cylinder achieve optimal protection for the weld.

[0065] When subjected to impacts in the y and z directions, the welds on the +y and -z sides near the L-shaped bracket will be protected by the bracket 5, and there will not be much stress at the welds; the welds on the -y and +z sides near the pull belt 7 are mainly protected by the pre-tension force of the pull belt 7, and the normal pressure required by the pull belt 7 is related to the magnitude of the impact acceleration.

[0066] Taking into account the stress and pressure distribution at the weld of the baffle 3, since the force on the fuel tank baffle 3 during vehicle operation is mainly due to the impact of oil in the x direction, and Pm / P1 = 0.6.

[0067] The local normal pressure on partition 3 is proportional to the pressure. Only when the normal pressure Fz on the upper and lower flanges of partition 3 is 1 / 0.6 = 1.6 times the normal pressure Fy on the left and right flanges, will the friction between partition 3 and the cylinder achieve a reasonable distribution of the weld seam. At this time, the angle θ between the bolt preload axial force and the horizontal direction x satisfies... Therefore, θ = 58°, and the included angle θ is ultimately designed to be 58°.

[0068] In the above embodiments, preferably, both the housing 1 and the partition 3 are made of aluminum alloy. The housing 1, made of aluminum alloy, has good strength, is lightweight, and is corrosion-resistant.

[0069] Furthermore, preferably, a fuel filler nozzle 2 is fixedly connected to one side of the top of the tank 1 for refueling. In use, fuel is added to the tank through the fuel filler nozzle 2 on the tank 1.

[0070] The underlying principle of this invention is as follows: In the aluminum alloy fuel tank structure, the weld between the flange of the partition plate 3 and the fuel tank body 1 is located at the center of the flange. When oil impacts from different directions, the pre-tensioning force of the strap 7 on the flange of the partition plate 3 and the resulting frictional force always "protect" the central weld, thus significantly reducing the shear force transmitted to the weld. Compared to welds arranged at the edges, welds arranged in the center are not subject to bending moments. Plug holes 8 are arranged in the center of the flange of the partition plate 3 and at the four chamfers. Three welds are arranged in the center, and two welds are arranged at the chamfers: the upper and lower welds bear the main impact force from the X direction, while the front and rear welds bear part of the X and Y direction impact forces. The equivalent concentrated force of the oil is located near the center. The central weld needs to bear the main impact shear force of the oil, while reducing the bending moment generated by the oil impact force on the four corner welds. The welds at the four corners serve an auxiliary function. The plug weld holes 8 are closed strips and are fully welded. Compared to open welds, they do not cause stress abrupt changes, thus eliminating the problem of local cracking and reducing the level of concentrated stress. At the same time, the annular plug weld holes 8 do not significantly weaken the stiffness of the partition plate 3 while ensuring the weld length.

[0071] As for the preload of the pull strap 7, a larger portion of the preload and friction will be distributed and borne at the location of higher rigidity of the partition 3. Therefore, the pull strap 7 will gradually transfer this larger preload and friction to the ribs 9 on the partition 3. The ribs 9 are arranged at the geometric midpoint of the plug weld hole 8. Therefore, the ribs 9 at the center line can effectively absorb and bear a larger preload and friction, thereby achieving "fixed-point protection" of the plug weld hole 8 through the ribs 9.

[0072] Circular holes are designed at the chamfers of the upper and lower rubber pads. By making local openings, the normal pressure distribution of the pull strap 7 at the chamfer of the partition 3 and in the middle of the partition 3 can be adjusted to prevent the preload from being excessively concentrated at the rounded corners.

[0073] Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A novel aluminum alloy fuel tank structure, comprising a tank body (1), characterized in that: An L-shaped bracket (5) is fixed to the outside of the box (1). The top of the bracket (5) is hinged to the top of the L-shaped pull strap (7) that matches the box (1). The bottom of the pull strap (7) is pre-tightened to the bottom of the bracket (5) by an inclined pre-tightening bolt (12). A lower rubber pad (4) is provided between the inner wall of the bracket (5) and the outer wall of the box (1). An upper rubber pad (6) is provided between the inner wall of the pull strap (7) and the outer wall of the box (1). The inner wall of the body (1) is fixed with vertically arranged partitions (3) with flanges at the corresponding brackets (5); the partitions (3) are evenly distributed with several ribs (9) on the vertically dividing plate; the flanges of the partitions (3) are evenly distributed with several plug welding holes (8); the partitions (3) are connected to the box body (1) through the plug welding holes (8); the lower rubber pad (4) has a first round hole (10) at the 90° bend; the upper rubber pad (6) has a second round hole (11) at the 90° bend. The plug welding hole (8) is located at the center of the flange of the partition plate (3); The partition (3) is a square structure; the chamfer of the square partition (3) is a rounded chamfer; the plug welding holes (8) are not only evenly distributed on the straight flange of the partition (3); the plug welding holes (8) are also evenly distributed on the rounded chamfer of the partition (3); The partition (3) has two plug weld holes (8) at the rounded chamfer position; the partition (3) has three plug weld holes (8) at the straight flange position; The plug weld hole (8) is a strip-shaped plug weld hole with rounded chamfers; When the partition (3) is impacted by oil in the ±X direction, the pressure Pm at point B in the middle of the partition (3) is 0.6 times the pressure P1 at point A at the bottom of the partition (3), i.e., Pm / P1 = 0.6; when the partition (3) is impacted in the x direction, the weld of the plug weld hole (8) of the partition (3) mainly bears the shear force; and when the normal pressure in the vertical direction of the partition (3) It is the normal pressure in the y-direction of the partition (3). When the friction force between the partition plate (3) and the box body (1) is 1 / 0.6 = 1.6 times, the optimal protection of the weld seam of the plug weld hole (8) will be achieved. At this time, the pre-tightening force of the pre-tightening bolt (12) is the angle between the axial force of the pre-tightening bolt (12) and the horizontal direction x. satisfy That is, the axial force angle of the preload bolt (12). =58°.

2. The novel aluminum alloy fuel tank structure according to claim 1, characterized in that: The box body (1) has a cross-sectional dimension of 700x700mm; the rib (9) is a long strip structure; the width of the rib (9) is ≥3d mm, where d is the width of the flange plug weld hole (8) of the partition (3), and 8mm≤d≤12mm; the height of the rib (9) is ≥1d mm; the length of the rib (9) is Z, and 100≤Z≤1.5T mm, where T is the flange width of the partition (3).

3. The novel aluminum alloy fuel tank structure according to claim 1, characterized in that: The center distance between adjacent plug weld holes (8) at the straight flange of the partition (3) is L, 80mm≤L≤100mm; the distance H between the center of the plug weld hole (8) and the outer side of the flange of the partition (3) satisfies 0.5T mm≤H≤0.6T mm, where T is the width of the flange of the partition (3); the length B of the plug weld hole (8) satisfies 0.5T mm≤B≤0.7T mm; the distance between the adjacent plug weld hole (8) at the rounded chamfer of the partition (3) and the plane of angular symmetry is ≥4d mm, where d is the width of the plug weld hole (8) at the flange of the partition (3), and 8mm≤d≤12mm; the other parameters of the plug weld hole (8) at the rounded chamfer of the partition (3) are the same as the parameters of the plug weld hole (8) at the straight flange of the partition (3).

4. The novel aluminum alloy fuel tank structure according to claim 1, characterized in that: There are two first circular holes (10), and the diameter of the two first circular holes (10) is d2, and satisfies 10mm≤d2≤0.8m, where m is the length of the flange on both sides of the π-shaped bracket (5); the centers of the two first circular holes (10) are respectively located at the center of the π-shaped bracket (5); the diameter of the second circular hole (11) is d1, and satisfies 20mm≤d1≤0.8T, where T is the width of the flange of the partition (3).

5. The novel aluminum alloy fuel tank structure according to claim 1, characterized in that: Both the box body (1) and the partition (3) are made of aluminum alloy.

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