Dumper tail door locking mechanism, optimization design method thereof and dumper

Abstract

The invention discloses an optimization design method for a tail door locking mechanism of a dumper. The method comprises the following steps: 1, carrying out theoretical analysis on size parameters of the tail door locking mechanism of the dumper and obtaining a theoretical analysis result; 2, establishing a multi-body dynamic simulation model of a tail door locking mechanism, a cargo compartment and cargos of the dumper, simulating the lifting and unloading process of the cargo compartment, and outputting a chain force-chain eccentric angle curve; 3, a strength simulation model of the dumper tail door locking mechanism is established, strength checking is carried out on the dumper tail door locking mechanism, and the stress of the adjusting bolt and the stress of the adjusting bolt pin shaft are output; 4, adjusting the size parameters of the dumper tail door locking mechanism based on the theoretical analysis result in the step 1, repeating the step 2 and the step 3 on the basis of the adjusted size parameters, outputting the stress of the adjusting bolt and the adjusting bolt pin shaft corresponding to the adjusted size parameters, and obtaining the size parameter range of the dumper tail door locking mechanism. The invention further relates to a dump truck tail door locking mechanism and a dump truck.

Description

Technical Field

[0001] The present invention relates to the technical field of dump trucks, in particular to a dump truck tailgate locking mechanism, an optimization design method for the dump truck tailgate locking mechanism, and a dump truck having the dump truck tailgate locking mechanism. Background Art

[0002] Off-road mining dump trucks operate in harsh working conditions such as mines. Their tailgate locking mechanism is a key device to ensure that the tailgate remains closed during transportation and opens in time during unloading.

[0003] However, since off-road mining dump trucks are often overloaded, frequent lifting and unloading operations cause key components such as the adjusting bolts and pins in the tailgate locking mechanism to easily break and fail, seriously affecting the vehicle's safety and work efficiency. Summary of the Invention

[0004] In view of this, the present invention provides a dump truck tailgate locking mechanism and an optimized design method thereof, which can significantly reduce the stress level of the adjusting bolt and the adjusting bolt pin during unloading, improve the reliability of the dump truck tailgate locking mechanism, and avoid safety accidents caused by untimely unlocking during unloading.

[0005] An embodiment of the present invention provides a method for optimizing the design of a tailgate locking mechanism of a dump truck, comprising: Step 1: Conducting a theoretical analysis on the dimensional parameters of the dump truck tailgate locking mechanism and obtaining theoretical analysis results; Step 2: Using multi-body dynamics simulation software to establish a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism, cargo compartment, and cargo, simulate the process of the cargo compartment lifting and unloading, and output a chain force-chain eccentricity angle curve; Step 3: Using finite element analysis software to establish a strength simulation model of the dump truck tailgate locking mechanism, using the chain force-chain eccentricity angle curve extracted in step 2 as input, performing a strength check on the dump truck tailgate locking mechanism, and outputting the stress of the adjusting bolt and the adjusting bolt pin; Step 4: Adjust the dimensional parameters of the dump truck tailgate locking mechanism based on the theoretical analysis results in step 1, repeat steps 2 and 3 based on the adjusted dimensional parameters, output the stress of the adjusting bolt and the adjusting bolt pin corresponding to the adjusted dimensional parameters, and obtain the dimensional parameter range of the dump truck tailgate locking mechanism.

[0006] Furthermore, a method for theoretically analyzing the dimensional parameters of the dump truck tailgate locking mechanism includes: Establish the mathematical relationship between the tail hook opening angle β and the dimensional parameters A, B, H of the dump truck tailgate locking mechanism and the cargo box lifting angle α , and the mathematical relationship between the speed of the tail hook opening angle increase Where A is the distance from the lift hinge point O of the cargo box lift pin to the axis Q of the tail hook pin; B is the distance from the axis R of the chain pin to the axis Q of the tail hook pin; H is the distance from the axis P of the adjusting bolt pin to the lift hinge point O of the cargo box lift pin; According to the geometric relationship, the tail hook opening angle β is obtained as:

[0007] The distance C from the axis P of the adjusting bolt pin to the axis Q of the tail hook pin is:

[0008] The distance L from the axis P of the adjusting bolt pin to the axis Q of the tail hook pin is:

[0009] but:

[0010] Then the increasing speed of the tail hook opening angle β is:

[0011] Theoretical analysis results obtained from the dimensional parameters of the dump truck tailgate locking mechanism include: increasing the increasing speed of the tail hook opening angle β and / or reducing the tail hook separation angle γ.

[0012] Furthermore, the method for increasing the increasing speed of the tail hook opening angle β includes increasing the distance H from the axis P of the adjusting bolt pin to the lifting hinge point O of the cargo box lifting pin and / or reducing the distance B from the axis R of the chain pin to the axis Q of the tail hook pin.

[0013] Furthermore, the range of the distance B from the axis R of the chain pin to the axis Q of the tail hook pin is: 80≤B≤120mm, and the range of the distance H from the axis P of the adjusting bolt pin shaft to the lifting hinge point O of the car lifting pin shaft is: 300≤H≤600mm.

[0014] Furthermore, the method of reducing the tail hook separation angle γ includes reducing the distance from the contact position between the tailgate hook and the tailgate to the axis Q of the tail hook pin.

[0015] Furthermore, the range of the tail hook separation angle γ is: 20°≤γ≤25° Furthermore, in step 2, a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism is established with the dimensional parameters of the dump truck's tailgate locking mechanism being A=1160, B=100, H=300, and γ=30°. In step 4, a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism is established with the adjusted dimensional parameters of the dump truck's tailgate locking mechanism being A=1160, B=100, H=500, and γ=21°.

[0016] Furthermore, the tail hook opening angle β is the angle at which the tailgate hook rotates around the tail hook pin; the chain eccentric angle θ is the angle at which the axis of the chain deviates from the axis of the adjusting bolt; and the tail hook separation angle γ is the angle of the tail hook opening angle β when the tailgate hook is out of contact with the tailgate.

[0017] The embodiment of the present invention further provides a dump truck tailgate locking mechanism for being arranged on a dump truck, the dump truck tailgate locking mechanism comprising a tailgate hook, a chain and a chain seat; the cargo compartment of the dump truck is provided with a tailgate hook support seat, one end of the tailgate hook is hinged to the tailgate hook support seat through a tail hook pin, an adjusting bolt is provided on the chain seat, one end of the adjusting bolt is provided with an adjusting bolt pin shaft, one end of the chain is hinged to the middle part of the tailgate hook through a chain pin, the other end of the chain is connected to the adjusting bolt pin shaft, and the chain seat is fixed to the On the frame of the dump truck, the cargo box is hinged to the frame through the cargo box lifting pin shaft; it is characterized in that the dimensional parameters of the dump truck tailgate locking mechanism are obtained by the above-mentioned dump truck tailgate locking mechanism optimization design method; wherein, the range of the distance B from the axis R of the chain pin to the axis Q of the tail hook pin is: 80≤B≤120mm, the range of the distance H from the axis P of the adjusting bolt pin shaft to the lifting hinge point O of the box lifting pin shaft is: 300≤H≤600mm, and the range of the tail hook separation angle γ is: 20°≤γ≤25°.

[0018] An embodiment of the present invention further provides a dump truck, comprising the above-mentioned dump truck tailgate locking mechanism.

[0019] In summary, the dump truck tailgate locking mechanism, dump truck tailgate locking mechanism optimization design method, and dump truck of the present invention have the following beneficial effects: 1. By increasing the speed of the tail hook opening angle, the mechanism can be unlocked in time, which significantly reduces the peak load of the chain force and the chain eccentricity angle, thereby reducing the stress level of the adjusting bolt and the adjusting bolt pin; 2. By reducing the tail hook separation angle, the mechanism can be unlocked in time, further reducing the influence of chain force and chain eccentricity, thereby reducing the stress level of the adjusting bolt and adjusting bolt pin; 3. Adopt an optimization method that combines theoretical analysis, multi-body dynamics simulation, and finite element simulation to ensure the scientificity and reliability of the design; 4. It increases the service life of the locking mechanism under harsh working conditions, avoids safety accidents caused by untimely unlocking during unloading, and reduces the failure rate and maintenance costs.

[0020] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the following preferred embodiments are specifically cited and described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a schematic diagram of the locking mechanism of the tailgate of a dump truck.

[0022] Figure 2 It is a schematic diagram for defining the tail hook opening angle.

[0023] Figure 3 It is a schematic diagram that defines the chain eccentricity angle.

[0024] Figure 4 It is a schematic diagram for defining the tail hook separation angle.

[0025] Figure 5 It is a schematic diagram of the steps of the dump truck tailgate locking mechanism optimization design method of the present invention.

[0026] Figure 6 It is a schematic diagram that defines the dimensional parameters of the tailgate locking mechanism of a dump truck.

[0027] Figure 7 This is a schematic diagram of the tail hook opening angle-cargo compartment lifting angle curve corresponding to different dimensional parameters of the dump truck's tailgate locking mechanism.

[0028] Figures 8A to 8C It is a schematic diagram simulating the process of lifting and unloading the cargo compartment of a dump truck.

[0029] Figure 9 It is a schematic diagram of the tail hook opening angle-cargo compartment lifting angle curve and the chain eccentric angle-cargo compartment lifting angle curve.

[0030] Figure 10 It is a schematic diagram of the chain force-chain eccentric angle curve.

[0031] Figure 11 It is a schematic diagram of a strength simulation model of a dump truck tailgate locking mechanism of a preferred embodiment of the present invention.

[0032] Figure 12 It is a schematic diagram of the strength verification results of the tailgate locking mechanism of a dump truck in a preferred embodiment of the present invention.

[0033] Figure 13 It is a schematic diagram of the dump truck's tailgate locking mechanism reducing the tail hook separation angle.

[0034] Figure 14 This is a schematic diagram of the dump truck's tailgate locking mechanism when the tailgate hook and tailgate are about to lose contact when the tail hook separation angle is large.

[0035] Figure 15 This is a schematic diagram of the dump truck's tailgate locking mechanism when the tailgate hook and tailgate are about to disengage when the tail hook separation angle is small.

[0036] Figure 16 This is a schematic diagram of the chain force-chain eccentric angle comparison curve of the dump truck tailgate locking mechanism before and after adjusting the dimensional parameters.

[0037] Figure 17 It is a schematic diagram of a strength simulation model of a dump truck tailgate locking mechanism of a preferred embodiment of the present invention after adjusting dimensional parameters.

[0038] Figure 18 It is a schematic diagram of the strength verification result of the tailgate locking mechanism of a dump truck after adjusting the dimensional parameters of the preferred embodiment of the present invention. DETAILED DESCRIPTION

[0039] In order to further illustrate the technical means and effects adopted by the present invention to achieve the predetermined purpose of the invention, the present invention is described in detail below with reference to the accompanying drawings and preferred embodiments.

[0040] The dump truck tailgate locking mechanism is used to be arranged on the dump truck for closing / unlocking the tailgate 103 of the dump truck, and the dump truck is, for example, an off-road mining dump truck. Figure 1 This is a schematic diagram of the dump truck tailgate locking mechanism, please refer to Figure 1 The dump truck's tailgate locking mechanism includes a tailgate hook 1, a chain 2, and a chain base 3. Specifically, a tailgate hook support base 4 is fixedly mounted on the lower rear side of the dump truck's cargo compartment 101. One end of the tailgate hook 1 is hinged to the tailgate hook support base 4 via a tail hook pin 5. The chain base 3 is equipped with an adjustment bolt 7, one end of which is equipped with an adjustment bolt pin 71. One end of the chain 2 is hinged to the middle of the tailgate hook 1 via a chain pin 6, and the other end of the chain 2 is connected to the adjustment bolt pin 71. The chain base 3 is fixed to the vehicle frame 102 located below the cargo compartment 101. The cargo compartment 101 is hinged to the vehicle frame 102 via a cargo compartment lift pin 8.

[0041] When the dump truck begins to unload, the front of the cargo compartment 101 is lifted under the control of the hydraulic system, and the cargo compartment 101 tilts backward with the cargo compartment lifting pin 8 as the rotation center. The tailgate 103 is pushed by its own weight and / or the material, and its lower edge pushes the tailgate hook 1, which rotates outward around the chain pin 6, and the tailgate 103 gradually opens. When the cargo compartment 101 rotates to a certain angle, the tailgate hook 1 flips backward and downward under the action of gravity until it is completely separated from the tailgate 103, and the tailgate 103 is also freed from the restraint of the tailgate hook 1. After the material is completely unloaded, the front of the cargo compartment 101 rotates and descends under the control of the hydraulic system. At this time, the tailgate hook 1 rotates inward under the pull of the chain 2. When the tailgate 103 is closed, the tailgate hook 1 just locks the tailgate 103, and the chain 2 tightens to lock the door.

[0042] Figure 2 This is a diagram to define the tail hook opening angle, please refer to Figure 2 The tailgate hook opening angle β is defined as the angle at which the tailgate hook 1 rotates about the tailgate hook pin 5. During unloading of the cargo compartment 101, the tailgate hook 1 rotates about the tailgate hook pin 5. This rotation angle is the tailgate hook opening angle β. The tailgate hook opening angle β is 0° when the tailgate 103 is fully closed and the tailgate hook 1 is securely fastened to the tailgate 103.

[0043] Figure 3 This is a schematic diagram to define the chain eccentric angle, please refer to Figure 3 The chain eccentric angle θ is defined as the angle between the axis of the chain 2 and the axis of the adjusting bolt 7. During the lifting process of the cargo box 101, as the tailgate hook 1 tilts, the axis of the chain 2 and the axis of the adjusting bolt 7 will deviate by a certain angle, which is the chain eccentric angle θ. When the axis of the chain 2 and the axis of the adjusting bolt 7 coincide, the chain eccentric angle θ is 0°.

[0044] Figure 4 This is a diagram to define the tail hook separation angle, please refer to Figure 4 The tail hook separation angle γ is defined as the tail hook opening angle β when the tailgate hook 1 disengages from the tailgate 103. As the cargo box 101 is raised, the tail hook opening angle β gradually increases. When the cargo box 101 is raised to a certain angle, the tailgate hook 1 disengages from the tailgate 103. The tail hook opening angle β at this point is the tail hook separation angle γ.

[0045] The main reasons for the high stress levels of the adjusting bolt 7 and the adjusting bolt pin 71 in the tailgate locking mechanism include: 1. The rate of increase of the tail hook opening angle β is directly related to the dimensional parameters of the tailgate locking mechanism. Existing designs fail to fully consider the impact of dimensional parameters on the rate of increase of the tail hook opening angle, resulting in delayed unlocking of the structure and excessively high peak chain force (the load on chain 2). 2. The chain eccentric angle θ is large, which increases the bending moment on the adjusting bolt 7 and easily causes structural failure; 3. If the tail hook separation angle γ is too large, it will also cause a delay in the unlocking time of the structure, further aggravating the negative impact of the chain force and the chain eccentric angle θ. In extreme cases, it may cause a rollover accident due to failure to unlock in time.

[0046] Figure 5 This is a schematic diagram of the steps of the dump truck tailgate locking mechanism optimization design method of the present invention. Figure 6 This is a diagram that defines the dimensional parameters of the dump truck tailgate locking mechanism. Figure 5 and Figure 6 , among which, in Figure 6 In the figure: A is the distance from the lifting hinge point O (that is, the axis center) of the car lifting pin shaft 8 to the axis center Q of the tail hook pin 5; B is the distance from the axis center R of the chain pin 6 to the axis center Q of the tail hook pin 5; H is the distance from the axis center P of the adjusting bolt pin shaft 71 to the lifting hinge point O of the car lifting pin shaft 8; the cargo car lifting angle α is the rotation angle of the cargo car 101 relative to the frame 102 during the lifting process; C is the length of the chain 2, specifically the distance from the axis center P of the adjusting bolt pin shaft 71 to the axis center Q of the tail hook pin 5; L is the distance from the axis center P of the adjusting bolt pin shaft 71 to the axis center Q of the tail hook pin 5.

[0047] The optimization design method of the dump truck tailgate locking mechanism in the preferred embodiment of the present invention specifically includes: Step 1: Conduct theoretical analysis on the dimensional parameters of the dump truck tailgate locking mechanism and obtain theoretical analysis results.

[0048] Specifically, a mathematical relationship is established between the tail hook opening angle β and the dimensional parameters A, B, H of the dump truck tailgate locking mechanism and the cargo compartment lifting angle α. , and the mathematical relationship between the speed of the tail hook opening angle increase .

[0049] According to the geometric relationship, the tail hook opening angle β is obtained as:

[0050] The distance C (also known as the chain length) from the axis P of the adjusting bolt pin to the axis Q of the tail hook pin is:

[0051] The distance L between points P and Q is:

[0052] but

[0053] Then the increasing speed of the tail hook opening angle β (i.e. the effect of the tail hook opening angle β on the cargo box lifting angle) The partial derivative of

[0054] The increasing speed of the tail hook opening angle β is directly related to the dimensional parameters of the dump truck's tailgate locking mechanism. As the cargo compartment lifting angle α increases, when β=γ, the tail hook opening angle β increases to the tail hook separation angle γ, at which time the dump truck's tailgate locking mechanism is unlocked.

[0055] Figure 7 This is a diagram of the tail hook opening angle-cargo compartment lifting angle curve corresponding to different size parameters of the dump truck tailgate locking mechanism. Figure 7 The theoretical analysis results of the dimensional parameters of the dump truck tailgate locking mechanism can be intuitively expressed as follows: 1) When the tail hook separation angle γ remains unchanged, increasing H and / or decreasing B can significantly increase the increasing rate of the tail hook opening angle β (i.e., the slope of the curve), so that the tail hook opening angle β can be increased to the tail hook separation angle γ at a smaller cargo box lifting angle α, allowing the dump truck tailgate locking mechanism to unlock; 2) When the mechanism size remains unchanged, reducing the tail hook separation angle γ can also achieve the tail hook opening angle β increasing to the tail hook separation angle γ at a smaller cargo box lifting angle α, allowing the dump truck tailgate locking mechanism to unlock; 3) At the same time, increasing the increasing rate of the tail hook opening angle β and decreasing the tail hook separation angle γ can also achieve the tail hook opening angle β increasing to the tail hook separation angle γ at a smaller cargo box lifting angle α, allowing the dump truck tailgate locking mechanism to unlock.

[0056] In summary, by increasing the rate of increase of the tail hook opening angle β and / or decreasing the tail hook separation angle γ, the dump truck tailgate locking mechanism can be unlocked at a smaller cargo bed lift angle α. Increasing the rate of increase of the tail hook opening angle β further includes increasing the distance H between the axis P of the adjusting bolt pin 71 and the lift hinge point O of the cargo bed lift pin 8 and / or increasing the distance B between the axis R of the control chain pin 6 and the axis Q of the tail hook pin 5.

[0057] Step 2: Use multi-body dynamics simulation software (such as ADAMS) to establish a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism, cargo compartment 101, and cargo, simulate the process of cargo compartment 101 lifting and unloading, and output the relationship between the cargo compartment lifting angle α, tail hook opening angle β, chain force, and chain eccentricity angle θ.

[0058] Figures 8A to 8C This is a schematic diagram simulating the process of lifting and unloading cargo compartment of a dump truck. Figure 9 It is a schematic diagram of the curve of tail hook opening angle-cargo box lifting angle and the curve of chain eccentric angle-cargo box lifting angle; Figure 10 This is a diagram of the chain force-chain eccentricity curve; please refer to Figures 8A to 10Specifically, a multi-body dynamics simulation model of the dump truck tailgate locking mechanism is established with the dimensional parameters of the dump truck tailgate locking mechanism: A=1160, B=100, H=300, γ=30° to simulate the process of cargo compartment lifting and unloading. The process of cargo compartment lifting and unloading includes the entire process of the cargo compartment 101 lifting the cargo compartment angle α from 0° to the maximum angle, wherein, Figure 8A The multi-body dynamics simulation diagram is shown when α=0°, β=0°, and θ=0°. At this time, the cargo compartment 101 is not lifted. Figure 8B The multi-body dynamics simulation diagram is shown when α=9°, β=30°, and θ=8.6°. At this time, the tailgate 103 is about to be separated from the tailgate hook 1, and the dump truck tailgate locking mechanism is unlocked. Figure 8C The multi-body dynamics simulation diagram when α=15° is shown. At this time, the cargo is moved out of the cargo compartment 101 and the tailgate 103 is completely separated from the tailgate hook 1.

[0059] The relationship between the cargo box lifting angle α, the tail hook opening angle β, the chain force, and the chain eccentricity angle θ is as follows: Figure 9 As shown in the figure, it can be seen that as the cargo box lifting angle α increases, the tail hook opening angle β and the chain eccentric angle θ increase proportionally until they reach a maximum value when the tailgate 103 is about to be separated from the tailgate hook 1.

[0060] The relationship between chain force and chain eccentricity angle θ is as follows Figure 10 As shown in the figure, when the chain force reaches peak load F, the chain eccentric angle θ is at its maximum. At this point, the adjusting bolt 7 is subjected to a large bending moment, which can easily lead to structural damage. Therefore, if the tailgate hook 1 is not unhooked early, the load on the chain 2 will increase sharply, and the chain eccentric angle θ will also increase, which is the fundamental cause of failure of the dump truck's tailgate locking mechanism.

[0061] The chain force-chain eccentricity angle curve is extracted based on ADAMS analysis and used as the input for the next finite element simulation.

[0062] Step 3: Use finite element analysis software (such as Hyperworks) to establish a strength simulation model of the dump truck's tailgate locking mechanism. Using the chain force-chain eccentricity angle curve extracted in step 2 as the input condition, perform a strength check on the dump truck's tailgate locking mechanism and output the stress of the adjusting bolt 7 and the adjusting bolt pin 71.

[0063] Figure 11 Schematic diagram of the strength simulation model of the tailgate locking mechanism of a dump truck according to a preferred embodiment of the present invention. Figure 12 This is a schematic diagram of the strength verification results of the dump truck tailgate locking mechanism of the preferred embodiment of the present invention. Please refer to Figure 11 and Figure 12Specifically, the strength simulation model of the dump truck tailgate locking mechanism includes the chain 2, chain seat 3, adjustment bolt 7, adjustment bolt pin 71, frame 102 and other related components. The dimensional parameters of the dump truck tailgate locking mechanism are A=1160, B=100, H=300, and γ=30°. The chain force-chain eccentricity angle curve extracted by ADAMS analysis in step 2 is used as input conditions to carry out strength verification of the dump truck tailgate locking mechanism (such as Figure 11 As shown in FIG), the stress of key components such as the output adjusting bolt 7 and the adjusting bolt pin 71 (as shown in FIG) Figure 12 shown).

[0064] Step 4: Based on the theoretical analysis results from Step 1, adjust the dimensional parameters of the dump truck's tailgate locking mechanism. Repeat Steps 2 and 3 based on the adjusted dimensional parameters, output the stresses of key components such as the adjusting bolt 7 and the adjusting bolt pin 71 corresponding to the adjusted dimensional parameters, and obtain the dimensional parameter range of the dump truck's tailgate locking mechanism. The method for adjusting the dimensional parameters of the dump truck's tailgate locking mechanism includes increasing the rate of increase of the tail hook opening angle β or decreasing the tail hook separation angle γ. The method for increasing the rate of increase of the tail hook opening angle β further includes increasing the distance H between the axis P of the adjusting bolt pin 71 and the lifting hinge O of the cargo lift pin 8, and increasing the distance B between the axis R of the control chain pin 6 and the axis Q of the tail hook pin 5.

[0065] Specifically, based on theoretical analysis, the dimensional parameters of the dump truck tailgate locking mechanism are optimized. The stress of the adjusting bolt 7 and the adjusting bolt pin 71 can be reduced by increasing the increasing speed of the tail hook opening angle β (that is, increasing the distance H from the axis P of the adjusting bolt pin 71 to the lifting hinge point O of the car lifting pin 8 or increasing the distance B from the axis R of the control chain pin 6 to the axis Q of the tail hook pin 5) or reducing the tail hook separation angle γ.

[0066] Figure 13 This is a schematic diagram of the dump truck's tailgate locking mechanism reducing the tail hook separation angle. Figure 13 In the figure, the tailgate hook 1a corresponds to a larger tail hook separation angle, and the tailgate hook 1b corresponds to a smaller tail hook separation angle. Figure 14 This is a schematic diagram of the dump truck's tailgate locking mechanism when the tailgate hook is about to disengage from the tailgate at a large tail hook separation angle. In the figure, the tail hook separation angle γ = 29.7° (approximately 30°). Figure 15 This is a schematic diagram of the dump truck's tailgate locking mechanism when the tailgate hook is about to disengage from the tailgate at a small tailgate separation angle. In the figure, the tailgate separation angle γ is 21°.

[0067] Furthermore, the method of reducing the tail hook separation angle γ includes reducing the distance from the contact position between the tailgate hook 1 and the tailgate 103 to the axis Q of the tailgate hook pin 5, for example, by reducing the height of the tailgate hook 1, changing the shape of the tailgate hook 1, etc., so as to change the contact position between the tailgate hook 1 and the tailgate 103.

[0068] The method of repeating step 2 and step 3 with adjusted dimensional parameters includes: repeating step 2 with adjusted dimensional parameters, outputting a chain force-chain eccentric angle curve, repeating step 3 again with the adjusted dimensional parameters and the chain force-chain eccentric angle curve extracted by analysis in step 2 as parameters, and outputting the stress of the adjusting bolt 7 and the adjusting bolt pin 71.

[0069] Specifically, ADAMS was used again to conduct multi-body dynamics simulation with the adjusted dimensional parameters of the dump truck tailgate locking mechanism to extract the corresponding chain peak load F and chain eccentricity angle θ. Figure 16 Figure 3 is a schematic diagram of the chain force-chain eccentric angle comparison curve of the dump truck tailgate locking mechanism before and after dimensional parameter adjustment. The solid line is the chain force-chain eccentric angle curve before dimensional parameter adjustment, and the corresponding dimensional parameters of the dump truck tailgate locking mechanism are A=1160, B=100, H=300, and γ=30°. The dotted line is the chain force-chain eccentric angle curve after dimensional parameter adjustment, and the corresponding dimensional parameters of the dump truck tailgate locking mechanism are A=1160, B=100, H=500, and γ=21°.

[0070] Figure 17 This is a schematic diagram of a strength simulation model of a dump truck tailgate locking mechanism of a preferred embodiment of the present invention after adjusting the size parameters. Figure 18 The following is a schematic diagram of the strength verification results of the dump truck tailgate locking mechanism after adjusting the size parameters of the preferred embodiment of the present invention. Table 1 is a comparison of the results before and after adjusting the size parameters of the dump truck tailgate locking mechanism. Figures 16 to 18 Combined with Table 1, it can be seen that after the dimensional parameters of the dump truck tailgate locking mechanism are adjusted, the stress of key components such as the adjusting bolt 7 and the adjusting bolt pin 71 is greatly reduced, and the peak load F of the chain force is reduced to roughly half of that before adjustment, effectively reducing the load on the chain 2.

[0071]

[0072] Table 1 Comparison of the dump truck tailgate locking mechanism before and after adjusting the size parameters After optimizing the dump truck tailgate locking mechanism using the above-mentioned optimization design method, the dimensional parameter ranges of the dump truck tailgate locking mechanism of the present invention were obtained. Among them, the distance B from the axis R of the chain pin 6 to the axis Q of the tail hook pin 5 is preferably in the range of 80≤B≤120mm, the distance H from the axis P of the adjusting bolt pin shaft 71 to the lifting hinge point O of the compartment lifting pin shaft 8 is preferably in the range of 300≤H≤600mm, and the tail hook separation angle γ is preferably in the range of 20°≤γ≤25°. By adjusting the above dimensional parameters, the cargo compartment lifting angle α when the mechanism is unlocked during the unloading process of the dump truck tailgate locking mechanism can be achieved in the range of 4°≤α≤5°, and the chain eccentric angle θ is in the range of θ≤5°, significantly reducing the stress on the adjusting bolt 7 and the adjusting bolt pin shaft 71.

[0073] The optimization design method for the tailgate locking mechanism of a dump truck provided by the present invention adopts an optimization method that combines theoretical analysis, multi-body dynamics simulation, and finite element simulation. By increasing the increase rate of the tail hook opening angle and reducing the tail hook separation angle, the stress level of the adjusting bolt and the adjusting bolt pin shaft during unloading can be significantly reduced, thereby improving the reliability of the locking mechanism and avoiding safety accidents caused by untimely unlocking during unloading.

[0074] Therefore, the present invention has the following beneficial effects: 1. By increasing the speed of the tail hook opening angle, the mechanism can be unlocked in time, which significantly reduces the peak load of the chain force and the chain eccentricity angle, thereby reducing the stress level of the adjusting bolt and the adjusting bolt pin; 2. By reducing the tail hook separation angle, the mechanism can be unlocked in time, further reducing the influence of chain force and chain eccentricity, thereby reducing the stress level of the adjusting bolt and adjusting bolt pin; 3. Adopt an optimization method that combines theoretical analysis, multi-body dynamics simulation, and finite element simulation to ensure the scientificity and reliability of the design; 4. It increases the service life of the locking mechanism under harsh working conditions, avoids safety accidents caused by untimely unlocking during unloading, and reduces the failure rate and maintenance costs.

[0075] The above description is merely a preferred embodiment of the present invention and does not constitute any form of limitation to the present invention. Although the present invention has been disclosed as a preferred embodiment, it is not intended to limit the present invention. Any technician familiar with the present profession can make some changes or modifications to equivalent embodiments of equivalent changes using the technical contents disclosed above without departing from the scope of the technical solution of the present invention. However, any simple modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention are still within the scope of the technical solution of the present invention.

Claims

1. A dump truck tailgate locking mechanism optimization design method, characterized in that: include: Step 1: Conducting a theoretical analysis on the dimensional parameters of the dump truck tailgate locking mechanism and obtaining theoretical analysis results; Step 2: Using multi-body dynamics simulation software to establish a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism, cargo compartment, and cargo, simulate the process of the cargo compartment lifting and unloading, and output a chain force-chain eccentricity angle curve; Step 3: Using finite element analysis software to establish a strength simulation model of the dump truck tailgate locking mechanism, using the chain force-chain eccentricity angle curve extracted in step 2 as input, performing a strength check on the dump truck tailgate locking mechanism, and outputting the stress of the adjusting bolt and the adjusting bolt pin; Step 4: Adjust the dimensional parameters of the dump truck tailgate locking mechanism based on the theoretical analysis results in step 1, repeat steps 2 and 3 based on the adjusted dimensional parameters, output the stress of the adjusting bolt and the adjusting bolt pin corresponding to the adjusted dimensional parameters, and obtain the dimensional parameter range of the dump truck tailgate locking mechanism.

2. The optimization design method for the tailgate locking mechanism of a dump truck according to claim 1, characterized in that: The method for theoretically analyzing the dimensional parameters of the dump truck tailgate locking mechanism includes: Establish the mathematical relationship between the tail hook opening angle β and the dimensional parameters A, B, H of the dump truck tailgate locking mechanism and the cargo box lifting angle α , and the mathematical relationship between the speed of the tail hook opening angle increase Where A is the distance from the lift hinge point O of the cargo box lift pin to the axis Q of the tail hook pin; B is the distance from the axis R of the chain pin to the axis Q of the tail hook pin; H is the distance from the axis P of the adjusting bolt pin to the lift hinge point O of the cargo box lift pin; According to the geometric relationship, the tail hook opening angle β is obtained as: The distance C from the axis P of the adjusting bolt pin to the axis Q of the tail hook pin is: The distance L from the axis P of the adjusting bolt pin to the axis Q of the tail hook pin is: but: Then the increasing speed of the tail hook opening angle β is: Theoretical analysis results obtained from the dimensional parameters of the dump truck tailgate locking mechanism include: increasing the increasing speed of the tail hook opening angle β and / or reducing the tail hook separation angle γ.

3. The optimization design method for the tailgate locking mechanism of a dump truck according to claim 2, characterized in that: Methods for increasing the speed of increasing the tail hook opening angle β include increasing the distance H from the axis P of the adjusting bolt pin to the lifting hinge point O of the cargo box lifting pin and / or reducing the distance B from the axis R of the chain pin to the axis Q of the tail hook pin.

4. The optimization design method for the tailgate locking mechanism of a dump truck according to claim 3, characterized in that: The range of the distance B from the axis R of the chain pin to the axis Q of the tail hook pin is: 80≤B≤120mm, and the range of the distance H from the axis P of the adjusting bolt pin shaft to the lifting hinge point O of the car lifting pin shaft is: 300≤H≤600mm.

5. The optimization design method for the tailgate locking mechanism of a dump truck according to claim 2, characterized in that: The method of reducing the tail hook separation angle γ includes reducing the distance from the contact position between the tailgate hook and the tailgate to the axis Q of the tail hook pin.

6. The optimization design method for the tailgate locking mechanism of a dump truck according to claim 5, characterized in that: The range of the tail hook separation angle γ is: 20°≤γ≤25°.

7. The optimization design method for the tailgate locking mechanism of a dump truck according to claim 1, characterized in that: In step 2, a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism is established with the dimensional parameters of the dump truck's tailgate locking mechanism being A=1160, B=100, H=300, and γ=30°. In step 4, a multi-body dynamics simulation model of the dump truck's tailgate locking mechanism is established with the adjusted dimensional parameters of the dump truck's tailgate locking mechanism being A=1160, B=100, H=500, and γ=21°.

8. The optimization design method for the tailgate locking mechanism of a dump truck according to any one of claims 1 to 7, characterized in that: The tail hook opening angle β is the angle at which the tailgate hook rotates around the tail hook pin; the chain eccentric angle θ is the angle at which the axis of the chain deviates from the axis of the adjusting bolt; and the tail hook separation angle γ is the angle of the tail hook opening angle β when the tailgate hook is out of contact with the tailgate.

9. A dump truck tailgate locking mechanism, which is used to be arranged on a dump truck, and the dump truck tailgate locking mechanism includes a tailgate hook, a chain and a chain seat; the cargo compartment of the dump truck is provided with a tailgate hook support seat, one end of the tailgate hook is hinged to the tailgate hook support seat through a tail hook pin, and an adjusting bolt is provided on the chain seat, one end of the adjusting bolt is provided with an adjusting bolt pin shaft, one end of the chain is hinged to the middle part of the tailgate hook through a chain pin, and the other end of the chain is connected to the adjusting bolt pin shaft, the chain seat is fixed to the frame of the dump truck, and the cargo compartment is hinged to the frame through a cargo compartment lifting pin shaft; it is characterized in that The dimensional parameters of the dump truck tailgate locking mechanism are obtained by the optimization design method of the dump truck tailgate locking mechanism as described in any one of claims 1 to 8; wherein, the range of the distance B from the axis R of the chain pin to the axis Q of the tail hook pin is: 80≤B≤120mm, the range of the distance H from the axis P of the adjusting bolt pin shaft to the lifting hinge point O of the car lifting pin shaft is: 300≤H≤600mm, and the range of the tail hook separation angle γ is: 20°≤γ≤25°.

10. A dump truck, characterized in that: It includes the dump truck tailgate locking mechanism as claimed in claim 9.

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