Stent pushing mechanism tongue plate strength checking method, system, device and medium

Abstract

This invention relates to a method, system, device, and medium for verifying the strength of a tongue plate in a support moving mechanism. The method includes: acquiring the lifting load parameters, geometric parameters, and cross-sectional parameters of the tongue plate of the support moving mechanism; constructing an overall force balance model based on the lifting load parameters and geometric parameters; determining the input load transmitted to the tongue plate according to the force distribution relationship of the lifting load in the support moving mechanism; constructing a local equivalent force model based on the input load and multiple stress locations; determining the cross-section to be verified and the equivalent bending moment based on the cross-sectional parameters; performing cross-sectional weakening equivalent processing on the cross-section to be verified to obtain the cross-sectional bending resistance parameters; performing bending stress conversion based on the equivalent bending moment and the cross-sectional bending resistance parameters; and obtaining the strength verification result based on preset verification conditions. Therefore, this invention can continuously characterize overall load transmission, local stress, cross-sectional weakening, and safety status, improving the accuracy and engineering applicability of tongue plate strength verification.

Description

Technical Field

[0001] This invention relates to the field of coal mine fully mechanized mining technology, and in particular to a method, system, equipment, and medium for verifying the strength of the tongue plate in a support pushing mechanism. Background Technology

[0002] In fully mechanized coal mining faces, hydraulic supports typically work in conjunction with scraper conveyors to perform operations such as support shifting, conveyor pushing, and floor lifting. The support shifting mechanism, as a crucial component for transmitting the shifting force and floor lifting reaction force of the hydraulic support, usually includes components such as shifting jacks, shifting rods, tongue plates, pins, guide sleeves, and connecting seats. During operation, the shifting force, floor lifting reaction force, as well as eccentric loads and impact loads, are transmitted through these components. Because the tongue plate is usually located at the connection and force transmission points, stress concentration easily occurs at its root, hole, and contact area during use. Therefore, the strength of the tongue plate affects the operational reliability of the support shifting mechanism.

[0003] Currently, common methods for strength analysis of hydraulic support pushing mechanisms include analytical calculations based on mechanics of materials and finite element simulation analysis. Analytical calculations based on mechanics of materials typically estimate strength based on component stress, section parameters, and material parameters. The calculation process is relatively straightforward and suitable for engineering design and routine verification scenarios. However, due to the relationships between components in the support pushing mechanism, such as pin connections, contact, and guiding fits, the actual load transmission path within the mechanism is quite complex. Therefore, if the calculation is simplified to consider only the entire component or a single stress location, the calculation results may deviate from the actual local stress state.

[0004] Finite element simulation analysis typically requires building a 3D model and performing mesh generation, boundary condition setting, contact relationship definition, and load application to obtain relatively detailed stress distribution results. However, because this method demands high modeling accuracy, boundary condition setting, and software operation, its cost and time are relatively high in scenarios such as on-site maintenance, initial scheme selection, or batch verification. Furthermore, when structural dimensions or operating parameters change, it is often necessary to readjust the model or calculation conditions, making it unsuitable for quickly completing strength verification of multiple schemes. Summary of the Invention

[0005] (a) Technical problems to be solved

[0006] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides a method, system, equipment and medium for verifying the strength of the tongue plate in a support pushing mechanism. It solves the technical problems that the material mechanics analysis method in the strength verification of the support pushing mechanism is insufficient in representing the actual local stress state of the tongue plate, while the finite element simulation method is complex to model and not convenient for rapid verification.

[0007] (II) Technical Solution

[0008] To achieve the above objectives, the main technical solutions adopted by the present invention include:

[0009] In a first aspect, embodiments of the present invention provide a method for verifying the strength of a tongue plate in a support pushing mechanism. The support pushing mechanism includes a pushing rod and a tongue plate connected to the pushing rod. The method includes:

[0010] Obtain the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate;

[0011] Based on the lifting load parameters, the lifting load acting on the support pushing mechanism under the lifting working condition is formed, and the overall force balance model of the support pushing mechanism is constructed in combination with the geometric parameters of the support pushing mechanism.

[0012] In the overall force balance model, the input load transmitted to the tongue plate is determined based on the force distribution relationship of the lifting load in the support pushing mechanism.

[0013] Based on the input load and multiple stress locations of the tongue plate, a local equivalent stress model of the tongue plate is constructed. Based on the local equivalent stress model and the cross-sectional parameters of the tongue plate, the cross-section of the tongue plate to be checked and the equivalent bending moment of the cross-section to be checked are determined.

[0014] Based on the cross-sectional parameters of the tongue plate, the cross-sectional weakening equivalent treatment is performed on the cross-sectional section to be checked to obtain the cross-sectional bending parameters of the cross-sectional section to be checked.

[0015] Based on the equivalent bending moment and section bending parameters of the section to be checked, the bending stress of the section to be checked is converted, and the tongue plate is checked for safety according to the bending stress conversion result and the preset check conditions to obtain the strength check result of the tongue plate.

[0016] Optionally, the lifting load acting on the support moving mechanism under the lifting condition is formed based on the lifting load parameters, and an overall force balance model of the support moving mechanism is constructed in combination with the geometric parameters of the support moving mechanism, including:

[0017] The lifting force exerted by the lifting drive component on the support pushing mechanism is determined based on the lifting load parameters.

[0018] Based on the geometric parameters of the support pushing mechanism, determine the equivalent force position at the front end, the force position at the rear end of the support pushing mechanism, and the position of the lifting force, and determine the lever arm relationship between the position of the lifting force and the equivalent force position at the front end and the force position at the rear end of the support pushing mechanism.

[0019] The equivalent force-bearing position at the front end and the force-bearing position at the tail end of the support pushing mechanism are taken as the force-bearing positions at both ends, and the position where the lifting force acts is taken as the input position of the lifting force between the two force-bearing positions. Based on the lever arm relationship, an overall force distribution model for the support pushing mechanism to distribute the lifting force is constructed.

[0020] The front equivalent force-bearing position is the equivalent position located near the tongue plate where the lifting force is applied and which bears the distribution of the lifting force. The tail force-bearing position of the support pushing mechanism is the position in the support pushing mechanism that is set relative to the front equivalent force-bearing position and bears the distribution of the lifting force.

[0021] Optionally, in the overall force balance model, based on the force distribution relationship of the lifting load in the support pushing mechanism, the input load transmitted to the tongue plate is determined, including:

[0022] In the overall force balance model, the front lever arm is determined based on the projection distance along the length of the push rod from the position of the lifting force to the equivalent force position at the front end.

[0023] The rear lever arm is determined based on the projected distance along the length of the pushing rod from the position of the lifting force to the force position at the tail end of the support pushing mechanism.

[0024] The total lever arm between the two force positions is determined based on the projected distance from the equivalent force position at the front end to the force position at the rear end of the support pushing mechanism along the length of the pushing rod.

[0025] Based on the proportional relationship between the front lever arm, the rear lever arm and the total lever arm, the lifting force is distributed at both ends to obtain the front distribution force corresponding to the equivalent front force position and the tail distribution force corresponding to the tail force position of the support pushing mechanism.

[0026] The front-end force is used as the input load transmitted to the tongue plate through the front-end equivalent force-bearing position.

[0027] Optionally, based on the input load and multiple force-bearing locations of the tongue plate, a local equivalent force model of the tongue plate is constructed, including:

[0028] Based on the assembly relationship of the tongue plate in the support pushing mechanism, the front force position of the tongue plate that bears the input load is determined, and the front force position is taken as the load application position;

[0029] Based on the contact relationship between the tongue plate and the adjacent force-bearing components in the support pushing mechanism, and the tail end force-bearing position on the tongue plate along the length direction opposite to the front force-bearing position, multiple force-bearing positions along the length direction of the tongue plate are determined; wherein, the adjacent force-bearing components include connecting components and guiding components that contact the tongue plate;

[0030] The location of the force boundary is determined based on the force location other than the load application location among multiple force locations;

[0031] Based on the load application location, the force boundary location, the distance between the load application location and each force boundary location, and the distance between adjacent force boundary locations, a local equivalent force model is constructed to obtain the local equivalent force parameters of the tongue plate at multiple force locations.

[0032] Optionally, based on the local equivalent stress model and the cross-sectional parameters of the tongue plate, the cross-section to be checked of the tongue plate and the equivalent bending moment of the cross-section to be checked are determined, including:

[0033] Based on the local equivalent force parameters, multiple force locations, and the cross-sectional position along the length of the tongue plate obtained from the local equivalent force model, the bending moment variation relationship of the tongue plate along the length direction is determined.

[0034] Based on the bending moment variation relationship, determine the location of the maximum bending moment on the tongue plate or the location of the section that meets the preset bending moment condition;

[0035] Determine the position of the hole section on the tongue plate based on the cross-sectional parameters of the tongue plate;

[0036] At least one of the following is identified as the section to be checked: the location of the maximum bending moment, the section location that meets the preset bending moment condition, the section location of the hole, the preset adjacent area of ​​the load application location, and the preset adjacent area of ​​the force boundary location.

[0037] The equivalent bending moment of the section to be checked is determined based on the local equivalent stress parameters, multiple stress locations, and the position of the section to be checked along the length of the tongue plate.

[0038] Optionally, based on the cross-sectional parameters of the tongue plate, the cross-section to be checked is subjected to equivalent cross-sectional weakening treatment to obtain the cross-sectional bending parameters of the cross-section to be checked, including:

[0039] Extract the cross-sectional dimension parameters and hole dimension parameters of the section to be checked from the cross-sectional parameters of the tongue plate; wherein, the hole dimension parameters include at least one of the following: hole diameter, hole width, hole height, and the projected dimension of the hole in the cross-section to be checked;

[0040] The original section of the section to be checked is determined based on the cross-sectional dimension parameters, and the weakened area in the original section that does not participate in the bending load is determined based on the hole dimension parameters;

[0041] The weakened area is subtracted from the original cross section to form the equivalent bearing section of the cross section to be checked;

[0042] Based on the geometric parameters of the equivalent bearing section, the flexural modulus of the section to be checked is determined and used as the flexural parameter of the section to be checked.

[0043] Optionally, based on the equivalent bending moment and section bending parameters of the section to be checked, the bending stress of the section to be checked is converted, and the tongue plate is subjected to a safety check based on the bending stress conversion result and the preset check conditions to obtain the strength check result of the tongue plate, including:

[0044] Based on the ratio between the equivalent bending moment of the section to be checked and the bending resistance parameter of the section, the bending stress of the section to be checked is converted to obtain the bending stress of the section to be checked.

[0045] The safety factor of the tongue plate is obtained based on the ratio between the preset stress limit and the bending stress of the section to be checked.

[0046] The safety factor of the tongue plate is compared with the preset safety threshold to obtain the safety check judgment result used to characterize whether the tongue plate meets the strength requirements;

[0047] The bending stress of the section to be checked, the safety factor of the tongue plate, and the safety check judgment result are used as the strength check result of the tongue plate.

[0048] In a second aspect, embodiments of the present invention provide a tongue plate strength verification system for a support pushing mechanism. The support pushing mechanism includes a pushing rod and a tongue plate connected to the pushing rod. The system includes:

[0049] The parameter acquisition module is used to acquire the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate;

[0050] The overall force modeling module is used to generate the lifting load acting on the support pushing mechanism under the lifting condition based on the lifting load parameters, and to construct the overall force balance model of the support pushing mechanism in combination with the geometric parameters of the support pushing mechanism.

[0051] The input load equivalent module is used to determine the input load transmitted to the tongue plate in the overall force balance model based on the force distribution relationship of the lifting load in the support pushing mechanism.

[0052] The local stress modeling module is used to construct a local equivalent stress model of the tongue plate based on the input load and multiple stress locations of the tongue plate, and to determine the cross section of the tongue plate to be checked and the equivalent bending moment of the cross section to be checked based on the local equivalent stress model and the cross section parameters of the tongue plate.

[0053] The section weakening processing module is used to perform equivalent section weakening processing on the section to be checked based on the section parameters of the tongue plate, so as to obtain the section bending resistance parameters of the section to be checked.

[0054] The verification result generation module is used to perform bending stress conversion on the section to be verified based on the equivalent bending moment and section bending parameters of the section to be verified, and to perform safety verification on the tongue plate according to the bending stress conversion result and the preset verification conditions, so as to obtain the strength verification result of the tongue plate.

[0055] Thirdly, embodiments of the present invention provide a tongue plate strength verification device for a support pushing mechanism, comprising: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, the instructions being executed by the at least one processor to cause the at least one processor to perform the tongue plate strength verification method in the support pushing mechanism as described above.

[0056] Fourthly, embodiments of the present invention provide a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, implement the tongue plate strength verification method in the support pushing mechanism as described above.

[0057] (III) Beneficial Effects

[0058] The beneficial effects of this invention are:

[0059] First, by acquiring the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate, the present invention enables the strength verification process to simultaneously consider the load source, the force position of the mechanism, and the cross-sectional characteristics of the tongue plate, thereby providing more complete basic data for the strength verification of the tongue plate.

[0060] Furthermore, the present invention forms the lifting load acting on the support pushing mechanism under the lifting condition based on the lifting load parameters, and constructs an overall force balance model in combination with the geometric parameters of the support pushing mechanism, so that the load transmission relationship under the lifting condition can be characterized at the overall level of the support pushing mechanism, thereby reducing the force deviation caused by checking only a single component or a single position.

[0061] Furthermore, in the overall force balance model, the present invention determines the input load transmitted to the tongue plate based on the force distribution relationship of the lifting load in the support pushing mechanism, so that a continuous load transmission relationship is formed between the overall force of the support pushing mechanism and the local force of the tongue plate, thereby improving the pertinence of the local strength verification of the tongue plate.

[0062] Next, this invention constructs a local equivalent stress model based on the input load and multiple stress locations of the tongue plate. Based on this model and the tongue plate's cross-sectional parameters, it determines the cross-section to be checked and its equivalent bending moment. This allows the stress states at multiple points—the front and rear ends of the tongue plate and its contact area with adjacent components—to be incorporated into the verification process, thus more closely approximating the stress state of the tongue plate under actual working conditions. Furthermore, this invention performs a cross-sectional weakening equivalent treatment on the cross-section to be checked, thereby making the characterization of the bending resistance of the cross-section to be checked more closely resemble the actual cross-sectional state.

[0063] Furthermore, the present invention performs bending stress conversion based on the equivalent bending moment and bending resistance parameters of the section to be checked, and performs safety verification based on the bending stress conversion result and preset verification conditions to obtain the strength verification result of the tongue plate. This allows the verification result to reflect the bending stress level and safety margin of the section to be checked, thereby improving the reliability of the tongue plate strength judgment.

[0064] Therefore, the present invention can continuously verify the overall load transfer, local stress state, equivalent bending moment of the section to be verified, section weakening effect, and strength safety state of the tongue plate in the support pushing mechanism, which is beneficial to improving the accuracy of the tongue plate strength verification and engineering applicability, and reducing the failure risk of tongue plate bending deformation, shear fracture, etc. Attached Figure Description

[0065] Figure 1 A schematic diagram of the overall process of the method provided for implementing the present invention;

[0066] Figure 2 A three-dimensional structural schematic diagram of the support pushing mechanism provided for the implementation of the present invention;

[0067] Figure 3 A detailed flowchart illustrating step S2 of the method provided for implementing the present invention;

[0068] Figure 4 The actual working posture and force of the support pushing mechanism provided for the implementation of the present invention

[0069] Schematic diagram;

[0070] Figure 5 A detailed flowchart illustrating step S3 of the method provided for implementing the present invention;

[0071] Figure 6 A flowchart illustrating the first part of step S4 of the method provided for implementing the present invention;

[0072] Figure 7 A flowchart illustrating the second part of step S4 of the method provided for implementing the present invention;

[0073] Figure 8 A schematic diagram of the force on the tongue plate in the method provided for implementing the present invention;

[0074] Figure 9 A schematic diagram of the specific process of step S5 of the method provided for implementing the present invention.

[0075] Figure 10 A detailed flowchart of step S6 of the method provided for implementing the present invention is shown below;

[0076] Figure 11 A simplified calculation diagram of the tongue plate strength provided for the implementation of the present invention.

[0077] [Explanation of Labels in the Attached Images]

[0078] 1: Connector; 2: Tongue plate; 3: Bottom lifting jack; 4: Push rod; 5: Push jack. Detailed Implementation

[0079] To better explain and facilitate understanding of the present invention, the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

[0080] like Figure 1 As shown in the embodiment of the present invention, a method for verifying the strength of a tongue plate in a support pushing mechanism is proposed. The support pushing mechanism includes a pushing rod and a tongue plate connected to the pushing rod. The method includes: obtaining the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate; forming the lifting load acting on the support pushing mechanism under the lifting condition based on the lifting load parameters, and constructing an overall force balance model of the support pushing mechanism in combination with the geometric parameters of the support pushing mechanism; in the overall force balance model, determining the force distribution relationship of the lifting load in the support pushing mechanism, and determining the force transferred to the tongue plate. The input load of the tongue plate is determined. Based on the input load and multiple stress positions of the tongue plate, a local equivalent stress model of the tongue plate is constructed. Based on the local equivalent stress model and the cross-sectional parameters of the tongue plate, the cross-section to be checked and the equivalent bending moment of the cross-section to be checked are determined. Based on the cross-sectional parameters of the tongue plate, the cross-section to be checked is subjected to cross-sectional weakening equivalent treatment to obtain the cross-sectional bending parameters of the cross-section to be checked. Based on the equivalent bending moment and cross-sectional bending parameters of the cross-section to be checked, the bending stress of the cross-section to be checked is converted. Based on the bending stress conversion results and the preset check conditions, the tongue plate is checked for safety to obtain the strength check results of the tongue plate.

[0081] First, by acquiring the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate, the present invention enables the strength verification process to simultaneously consider the load source, the force position of the mechanism, and the cross-sectional characteristics of the tongue plate, thereby providing more complete basic data for the strength verification of the tongue plate.

[0082] Furthermore, the present invention forms the lifting load acting on the support pushing mechanism under the lifting condition based on the lifting load parameters, and constructs an overall force balance model in combination with the geometric parameters of the support pushing mechanism, so that the load transmission relationship under the lifting condition can be characterized at the overall level of the support pushing mechanism, thereby reducing the force deviation caused by checking only a single component or a single position.

[0083] Furthermore, in the overall force balance model, the present invention determines the input load transmitted to the tongue plate based on the force distribution relationship of the lifting load in the support pushing mechanism, so that a continuous load transmission relationship is formed between the overall force of the support pushing mechanism and the local force of the tongue plate, thereby improving the pertinence of the local strength verification of the tongue plate.

[0084] Next, this invention constructs a local equivalent stress model based on the input load and multiple stress locations of the tongue plate. Based on this model and the tongue plate's cross-sectional parameters, it determines the cross-section to be checked and its equivalent bending moment. This allows the stress states at multiple points—the front and rear ends of the tongue plate and its contact area with adjacent components—to be incorporated into the verification process, thus more closely approximating the stress state of the tongue plate under actual working conditions. Furthermore, this invention performs a cross-sectional weakening equivalent treatment on the cross-section to be checked, thereby making the characterization of the bending resistance of the cross-section to be checked more closely resemble the actual cross-sectional state.

[0085] Furthermore, the present invention performs bending stress conversion based on the equivalent bending moment and bending resistance parameters of the section to be checked, and performs safety verification based on the bending stress conversion result and preset verification conditions to obtain the strength verification result of the tongue plate. This allows the verification result to reflect the bending stress level and safety margin of the section to be checked, thereby improving the reliability of the tongue plate strength judgment.

[0086] Therefore, the present invention can continuously verify the overall load transfer, local stress state, equivalent bending moment of the section to be verified, section weakening effect, and strength safety state of the tongue plate in the support pushing mechanism, which is beneficial to improving the accuracy of the tongue plate strength verification and engineering applicability, and reducing the failure risk of tongue plate bending deformation, shear fracture, etc.

[0087] To better understand the above technical solutions, exemplary embodiments of the present invention will be described in more detail below with reference to the accompanying drawings. Although exemplary embodiments of the present invention are shown in the drawings, it should be understood that the present invention can be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present invention can be understood more clearly and thoroughly, and that the scope of the present invention can be fully conveyed to those skilled in the art.

[0088] Specifically, embodiments of the present invention provide a method for verifying the strength of a tongue plate in a support pushing mechanism, comprising:

[0089] S1. Obtain the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate.

[0090] like Figure 2 As shown, the support pushing mechanism includes components such as a pushing jack 5, a pushing rod 4, a tongue plate 2, a connector 1, and a bottom-lifting jack 3. The tongue plate 2 is connected to the pushing rod 4 and is located on the force transmission path of the support pushing mechanism. The bottom-lifting force generated by the bottom-lifting jack 3 under bottom-lifting conditions is transmitted to the pushing rod 4 and the tongue plate 2 through the support pushing mechanism. Based on the above structural relationship, in this step, the bottom-lifting load parameters used to determine the bottom-lifting load, the geometric parameters used to characterize the load transmission position relationship, and the cross-sectional parameters used to characterize the bearing capacity of the tongue plate 2 are obtained.

[0091] S2. Based on the lifting load parameters, form the lifting load acting on the support pushing mechanism under the lifting working condition, and construct the overall force balance model of the support pushing mechanism in combination with the geometric parameters of the support pushing mechanism.

[0092] Furthermore, such as Figure 3 As shown, step S2 includes:

[0093] S21. Determine the lifting force of the support pushing mechanism by the lifting drive component in the support pushing mechanism based on the lifting load parameters.

[0094] In one specific embodiment, such as Figure 4 As shown, the lifting drive component is a lifting jack 3. The lifting load parameters include the opening hydraulic pressure P of the lifting jack 3 and the cylinder diameter D of the lifting jack 3. Based on the pressure-bearing area and opening hydraulic pressure of the lifting jack 3, the lifting force F acting on the support pushing mechanism by the lifting jack 3 is determined, and its calculation relationship is as follows:

[0095] F = π × (D / 2) 2 ×P;

[0096] Where P is the hydraulic pressure for opening the bottom lifting jack 3, in MPa; D is the cylinder diameter of the bottom lifting jack 3, in mm; and F is the lifting force, in N.

[0097] S22. Determine the equivalent force position at the front end, the force position at the rear end of the support pushing mechanism, and the position of the lifting force based on the geometric parameters of the support pushing mechanism, and determine the lever arm relationship between the position of the lifting force and the equivalent force position at the front end and the force position at the rear end of the support pushing mechanism.

[0098] The equivalent force-bearing position at the front end is the equivalent position located near the tongue plate 2 where the lifting force is applied and bears the force distribution effect. This equivalent force-bearing position can be the connector, the force-bearing point at the front end of the push rod, the contact / cooperation force transmission point between the push rod and the tongue plate, or an equivalent position determined along the length of the push rod. The force-bearing position at the rear end of the support pushing mechanism is the position within the support pushing mechanism that is set relative to the equivalent force-bearing position at the front end and bears the force distribution effect. This rear force-bearing position can be the force-bearing point at the rear end of the push rod 4, the support point at the rear end of the push rod 4, the contact or cooperation force transmission point between the push rod 4 and the rear end connecting structure, or an equivalent position determined along the length of the push rod 4.

[0099] S23. Using the equivalent force-bearing position at the front end and the force-bearing position at the tail end of the support pushing mechanism as the force-bearing positions at both ends, and using the position of the lifting force as the input position of the lifting force between the two force-bearing positions, a general force distribution model for the support pushing mechanism to distribute the lifting force is constructed based on the lever arm relationship.

[0100] Specifically, the support pushing mechanism under the lifting condition is equivalent to an integral force-bearing component along the length of the pushing rod 4 as a whole, with forces at both ends and a load between the two ends. The equivalent force-bearing position at the front end and the force-bearing position at the rear end of the support pushing mechanism constitute the force-bearing positions at both ends, and the position where the lifting force acts constitutes the lifting force input position located between the force-bearing positions at both ends. The overall force distribution model includes the force-bearing positions at both ends, the lifting force input position, the lever arm of the lifting force input position relative to the force-bearing positions at both ends, and the distributed force at the force-bearing positions at both ends.

[0101] In this overall force distribution model, such as Figure 4 As shown, the lifting force F is taken as the input load at the lifting force input position, the distribution force corresponding to the equivalent force position at the front end is taken as the front distribution force F1, and the distribution force corresponding to the force position at the tail end of the support pushing mechanism is taken as the tail distribution force F2. The lifting force F is distributed at both ends through the torque balance relationship.

[0102] According to the torque balance relationship, the distributed forces at both ends are related to the lever arm from the point of application of the lifting force to the opposite end. When the front lever arm is L1, the rear lever arm is L2, and the total lever arm is L, the magnitudes of the front distributed force F1 and the rear distributed force F2 are respectively:

[0103] F1 = (F × L2) / L;

[0104] F2 = (F × L1) / L;

[0105] Wherein, L is the projected distance along the length of the push rod 4 from the equivalent force position at the front end to the force position at the rear end of the support pushing mechanism, in mm; L1 is the projected distance along the length of the push rod 4 from the position of the lifting force to the equivalent force position at the front end, in mm; L2 is the projected distance along the length of the push rod 4 from the position of the lifting force to the force position at the rear end of the support pushing mechanism, in mm. F1 and F2 are used to represent the magnitude of the distributed force; when establishing a force direction coordinate system, F1 and F2 can be assigned corresponding positive and negative signs according to the load direction.

[0106] Therefore, the overall force distribution model is used to characterize the equivalent distribution relationship between the lifting force at the front equivalent force position and the force position at the rear end of the support pushing mechanism, without limiting the actual structural form of the support pushing mechanism.

[0107] S3. In the overall force balance model, the input load transmitted to the tongue plate is determined based on the force distribution relationship of the lifting load in the support pushing mechanism.

[0108] Furthermore, such as Figure 5 As shown, step S3 includes:

[0109] S31. In the overall force balance model, the front lever arm is determined based on the projection distance from the position of the lifting force to the equivalent force position at the front end along the length of the push rod.

[0110] S32. Determine the rear lever arm based on the projection distance along the length of the pushing rod from the position of the lifting force to the tail end of the support pushing mechanism.

[0111] S33. Determine the total lever arm between the two force positions based on the projection distance from the equivalent force position at the front end to the force position at the rear end of the support pushing mechanism along the length of the pushing rod.

[0112] S34. Based on the proportional relationship between the front lever arm, the rear lever arm and the total lever arm, the lifting force is distributed at both ends to obtain the front distribution force corresponding to the equivalent front force position and the tail distribution force corresponding to the tail force position of the support pushing mechanism.

[0113] S35. The front-end distribution force is used as the input load transmitted to the tongue plate through the front-end equivalent force-bearing position.

[0114] Also refer to Figure 4It can be seen that, based on the overall force distribution model, the force distribution results at both ends are further equivalently processed. Through step S2, the lifting force F under the lifting condition is distributed to the equivalent force position at the front end and the equivalent force position at the rear end of the support pushing mechanism according to the overall lever arm relationship of the support pushing mechanism, forming the front distribution force F1 and the rear distribution force F2 respectively. Among them, the front distribution force F1 corresponds to the equivalent force position at the front end, which is the equivalent position located near the tongue plate 2 at the point of action of the lifting force and bearing the force formed by the distribution of the lifting force. Therefore, the front distribution force F1 can characterize the force transmitted from the overall force of the support pushing mechanism to the tongue plate 2. The rear distribution force F2 is used to characterize the distribution effect of the force position at the rear end of the support pushing mechanism, and together with the front distribution force F1, it satisfies the overall force balance relationship.

[0115] Based on this, the front-end distribution force F1 is used as the input load transmitted to the tongue plate 2 through the front-end equivalent force position, and is used to construct the local equivalent force model of the tongue plate 2, thereby realizing the connection between the overall force analysis results of the support pushing mechanism and the local equivalent force model of the tongue plate 2.

[0116] S4. Based on the input load and multiple stress positions of the tongue plate, construct a local equivalent stress model of the tongue plate, and based on the local equivalent stress model and the cross-sectional parameters of the tongue plate, determine the cross-section of the tongue plate to be checked and the equivalent bending moment of the cross-section to be checked.

[0117] Furthermore, such as Figure 6 As shown, step S4 involves constructing a local equivalent force model of the tongue plate 2 based on the input load and multiple force-bearing locations of the tongue plate 2, including:

[0118] S41. Based on the assembly relationship of the tongue plate in the support pushing mechanism, determine the front force-bearing position of the tongue plate that receives the input load, and take the front force-bearing position as the load application position. This front force-bearing position is used to characterize the load application position after the overall force of the support pushing mechanism is transmitted to the tongue plate.

[0119] S42. Based on the contact relationship between adjacent force-bearing components in the tongue plate and the support pushing mechanism, and the tail force-bearing position on the tongue plate along the length direction opposite to the front force-bearing position, determine multiple force-bearing positions along the length direction of the tongue plate; wherein, the adjacent force-bearing components include connecting components and guiding components that are in contact with the tongue plate.

[0120] Specifically, the multiple force-bearing locations include the top of the tongue plate 2, the position where the tongue plate 2 contacts the connecting member, the position where the tongue plate 2 contacts the guide member, and the tail end of the tongue plate 2. The connecting member is the connector 1, and the guide member is the guide plate. Correspondingly, the top of the tongue plate 2 corresponds to a force F on the top of the tongue plate 2. 11 The force F at the contact point between the tongue plate 2 and the connector 1 corresponds to the contact point between the tongue plate 2 and the connector 1. 12The force F at the contact point between the tongue plate 2 and the guide plate corresponds to the contact point between the tongue plate 2 and the guide plate. 23 The position of the tail end of tongue plate 2 corresponds to the force F acting on the tail end of tongue plate 2. 24 .

[0121] S43. Determine the force boundary position based on the force position other than the load application position among multiple force positions.

[0122] In this step, the force-bearing locations other than the load application locations are used as contact boundary locations, support boundary locations, or reaction force locations in the local equivalent force model of the tongue plate 2. In this way, the contact or support effects of the tongue plate 2 at the connecting members, guide members, and tail end locations are incorporated into the local force analysis.

[0123] S44. Based on the load application location, the force boundary location, the distance between the load application location and each force boundary location, and the distance between adjacent force boundary locations, construct a local equivalent force model to obtain the local equivalent force parameters of the tongue plate at multiple force locations.

[0124] Specifically, the local equivalent force model treats the tongue plate 2 as a force-bearing component with multiple force-bearing positions along its length. The input load F1, the load application position, the force boundary position, the distance between the load application position and each force boundary position, and the distance between adjacent force boundary positions are used as the basis for solving the local equivalent force parameters of the tongue plate 2.

[0125] In one specific embodiment, the local equivalent force model includes methods for determining the force F at the tip of the tongue plate 2. 11 The force F at the contact point between the tongue plate 2 and the connector 1 12 The force F at the contact point between the tongue plate 2 and the guide plate 23 and the force F at the tail end of tongue plate 2 24 The equivalent force relationship is as follows:

[0126] F 11 =L 12 / (L) 11 -L 12 )×F1;

[0127] F 12 =(L 11 / L 12 )×(-F 11 );

[0128] F 23 =F 11 +F 12 -F 24 ;

[0129] F 24 =[F 12×(L 12 -L 11 )-(F 11 +F 12 )×L 23 ] / (L 24 -L 23 );

[0130] Among them, L 11 L is the distance from the pin hole at the end of connector 1 to the top of tongue plate 2, in mm. 12 L is the distance from the pin hole at the end of connector 1 to the point where the tail end of connector 1 contacts the tongue plate 2, in mm. 23 L is the distance from the top of tongue plate 2 to the contact point between the guide plate and tongue plate 2, in mm. 24 The distance from the top contact point of tongue plate 2 to the tail end of tongue plate 2 is in mm.

[0131] Using the aforementioned local equivalent force model, the interaction between the tongue plate 2 and the connecting member, the guide member, and the tail end position can be transformed into local equivalent force parameters that can be used for bending moment calculation, based on the input load F1.

[0132] Next, as Figure 7 As shown, step S4, based on the local equivalent force model and the cross-sectional parameters of the tongue plate 2, determines the cross-section of the tongue plate 2 to be checked and its equivalent bending moment, including:

[0133] S45. Based on the local equivalent force parameters, multiple force locations, and cross-sectional positions along the length of the tongue plate obtained from the local equivalent force model, determine the bending moment variation relationship of the tongue plate along the length direction.

[0134] In this step, the force F at the tip of tongue plate 2 in the local equivalent force parameters is... 11 The force F at the contact point between the tongue plate 2 and the guide plate 23 This can be further converted into a force used for bending moment calculation. Let F be the equivalent force at the tip of the tongue plate 2 used for bending moment calculation. 11 The equivalent force at the contact point between the tongue plate 2 and the guide plate used for bending moment calculation is F. 23 ', then can be represented as: F 11 '=-F 11 ;F 23 '=F 23 .

[0135] Furthermore, according to F 11 '、F 23 The distance relationship along the length of the tongue plate 2 is used to determine the front support force f1 and the rear support force f2 of the tongue plate 2. In a specific embodiment, the front support force f1 and the rear support force f2 satisfy: f1 = -[F 11'×(L0+b)+F 23 [×b] / (a+L0+b;f2=-[F 23 '×(L0+a)+F 11 [×a] / (a+L0+b). Where L0 is F 11 'with F 23 The distance between ' is in mm; a is F 11 'Distance to f1, in mm; b is F 23 'Distance to f2, in mm.

[0136] Based on the front support force f1 and the rear support force f2, the front bending moment M1 and the rear bending moment M2 of the tongue plate 2 are further obtained: M1=f1×a; M2=f2×b.

[0137] Therefore, the bending moment variation relationship of the tongue plate 2 along its length can be obtained. This bending moment variation relationship is used to characterize the bending moment distribution state of the tongue plate 2 at different cross-sectional positions, and provides a basis for subsequently determining the cross-section to be checked and the equivalent bending moment of the cross-section to be checked.

[0138] S46. Based on the bending moment variation relationship, determine the location of the maximum bending moment on the tongue plate or the location of the section that meets the preset bending moment condition.

[0139] In this step, the location of the peak bending moment, the location of a large bending moment change, or the location where the bending moment reaches a preset threshold are determined based on the bending moment variation relationship, and these locations are considered as potential dangerous section locations. Preset bending moment conditions include bending moment greater than a preset threshold, bending moment change rate greater than a preset threshold, or being located within a preset neighborhood of the peak bending moment.

[0140] S47. Determine the position of the hole section on the tongue plate according to the cross-sectional parameters of the tongue plate.

[0141] Specifically, the location of the hole section can be the location of the hole on the tongue plate 2 that mates with the connector 1 and the pin, or the location of the section on the tongue plate 2 that is affected by the contact, limitation or mating of the guide member; the preset adjacent area of ​​the load application location includes the connection force transmission area between the tongue plate 2 and the push rod 4 or the connecting member.

[0142] S48. Determine at least one of the following as the section to be checked: the location of the maximum bending moment, the section location that meets the preset bending moment condition, the section location of the hole, the preset adjacent area of ​​the load application location, and the preset adjacent area of ​​the force boundary location.

[0143] In this step, the sections to be checked include sections with large bending moments, sections weakened by holes, sections near the input load area, and sections near the support or contact boundary. By simultaneously considering the bending moment variation, the location of the hole weakening, and the area near the stress boundary, the selection of the sections to be checked can better match the distribution of dangerous sections of the tongue plate 2 under actual bottom-raising conditions.

[0144] S49. Determine the equivalent bending moment of the section to be checked based on the local equivalent stress parameters, multiple stress locations, and the position of the section to be checked in the length direction of the tongue plate.

[0145] Subsequently, based on the position of the section to be checked along the length of the tongue plate 2, this position is substituted into the bending moment variation relationship along the length of the tongue plate 2 to obtain the equivalent bending moment of the section to be checked. In a specific embodiment, when the section to be checked is located at... Figure 8 Within the range of bending moment variation at the rear end shown, where X is the distance from the tail end of tongue plate 2 to the calculated position, and b is F... 23 When calculating the distance to f2, the section bending moment M of the section to be checked is determined based on the rear bending moment M2 and the calculated position X. For example, M = (X / b) × M2, where X is the distance from the tail end of tongue plate 2 to the calculated position, in mm. This section bending moment M is used as the equivalent bending moment of the section to be checked, and is subsequently used to perform bending stress conversion in conjunction with the section bending resistance parameters.

[0146] S5. Based on the cross-sectional parameters of the tongue plate, perform cross-sectional weakening equivalent treatment on the cross-section to be checked to obtain the cross-sectional bending parameters of the cross-section to be checked.

[0147] Furthermore, such as Figure 9 As shown, step S5 includes:

[0148] S51. Extract the cross-sectional dimension parameters and hole dimension parameters of the section to be checked from the cross-sectional parameters of the tongue plate; wherein, the hole dimension parameters include at least one of the hole diameter, hole width, hole height, and the projected dimension of the hole in the cross-section to be checked.

[0149] The cross-sectional dimension parameters characterize the cross-sectional geometry of the section to be checked without considering the weakening effect of holes. The hole dimension parameters characterize the weakening effect of the cross-section formed by pin holes, connecting holes, or other hole structures at the section to be checked. In a specific embodiment, the cross-sectional dimension parameters include the width B and height H at the section to be checked, and the hole dimension parameters include the hole diameter φ at the section to be checked. Wherein, B is the width at the calculation location, in mm; H is the height at the calculation location, in mm; and φ is the hole diameter at the calculation location, in mm.

[0150] S52. Determine the original section of the section to be checked based on the cross-sectional dimension parameters, and determine the weakened area in the original section that does not participate in the bending load based on the hole dimension parameters.

[0151] In this step, the cross-section determined by width B and height H is used as the original cross-section of the cross-section to be checked. When there is a hole in the cross-section to be checked, the projected area of ​​the hole in the bending load direction does not participate in or participates less in the bending load, so the area corresponding to the hole size parameters is determined as the weakening area. In the case of a circular hole, the projected width of the cross-section corresponding to the hole diameter φ is used as the weakening width.

[0152] S53. Subtract the weakened area from the original cross section to form the equivalent bearing section of the cross section to be checked.

[0153] By subtracting the weakened region corresponding to the hole from the original cross-section, an equivalent load-bearing cross-section can be obtained for calculating the flexural modulus. In a specific embodiment, when the width of the original cross-section is B and the weakened width of the hole is φ, the effective width of the equivalent load-bearing cross-section can be expressed as B-φ. This equivalent load-bearing cross-section is used to characterize the portion of the cross-section that actually participates in flexural load-bearing after the hole weakens.

[0154] S54. Based on the geometric parameters of the equivalent bearing section, determine the flexural modulus of the section to be checked, and use it as the flexural parameter of the section to be checked.

[0155] Furthermore, the geometric parameters of the equivalent bearing section include its effective width and height. In a specific embodiment, the effective width of the equivalent bearing section is B-φ, and the height is H. Then, the flexural modulus W of the section to be checked satisfies: W=(B-φ)×H 2 / 6. Therefore, the equivalent bending capacity of the section to be checked can be obtained by deducting the weakened area of ​​the hole, so that the subsequent bending stress conversion can reflect the influence of the hole on the bearing capacity of the section.

[0156] S6. Based on the equivalent bending moment and section bending parameters of the section to be checked, the bending stress of the section to be checked is converted, and the tongue plate is checked for safety according to the bending stress conversion result and the preset check conditions to obtain the strength check result of the tongue plate.

[0157] Furthermore, such as Figure 10 As shown, step S6 includes:

[0158] S61. Based on the ratio between the equivalent bending moment of the section to be checked and the bending resistance parameter of the section, the bending stress of the section to be checked is converted to obtain the bending stress of the section to be checked.

[0159] Based on the relationship between bending moment and bending modulus, the bending stress σ of the section to be checked can be calculated. Its expression is: σ=M / W, where σ is the bending stress of the section to be checked, M is the equivalent bending moment of the section to be checked, and W is the bending modulus of the section to be checked.

[0160] S62. Based on the ratio between the preset stress limit and the bending stress of the section to be checked, the safety factor of the tongue plate is obtained.

[0161] The preset stress limit can be the allowable stress, yield strength reduction value, or design allowable stress of the tongue plate 2 material. In a specific embodiment, the preset stress limit is denoted as [σ]. The safety factor K of the tongue plate 2 is determined according to the ratio between the preset stress limit [σ] and the bending stress σ of the section to be checked, and its expression is: K=[σ] / σ;

[0162] S63. Compare the safety factor of the tongue plate with a preset safety threshold to obtain a safety verification judgment result characterizing whether the tongue plate meets the strength requirements. The preset safety threshold is set based on the material of the tongue plate 2, the working conditions of the support pushing mechanism, and the design safety requirements. In a specific embodiment, the preset safety threshold is 1.5. When the safety factor K is greater than 1.5, it is determined that the tongue plate 2 meets the strength requirements, and the design and selection of the tongue plate 2 are reasonable; when the safety factor K is less than or equal to 1.5, it is determined that the tongue plate 2 does not meet the strength requirements, and adjustments need to be made to the structural dimensions, material parameters, or design parameters of the support pushing mechanism of the tongue plate 2.

[0163] S64. The bending stress of the section to be checked, the safety factor of the tongue plate, and the safety check judgment result are used as the strength check result of the tongue plate.

[0164] The final strength verification results include the bending stress σ of the section to be verified, the safety factor K, the judgment result of whether the tongue plate 2 meets the strength requirements, and the corresponding design adjustment prompts when the strength requirements are not met. In this way, the local stress of the tongue plate 2, the bending moment of the section to be verified, and the bending resistance after the section is weakened can be transformed into quantifiable strength evaluation results, thereby providing a basis for the structural design, selection verification, or on-site maintenance of the tongue plate 2.

[0165] In one specific implementation, to adapt to the need for rapid verification on-site, the calculation process for the bending moment at multiple stress locations and sections of the tongue plate 2 can be simplified based on the overall stress analysis approach described above, forming a simplified verification process. This simplified verification process takes the lifting load as input and sequentially determines the maximum bending moment, the equivalent bending moment of the section to be verified, the moment of inertia of the section, the bending stress conversion result, and the strength verification result, thereby reducing the steps of solving for the reaction force at each contact location one by one.

[0166] like Figure 11 As shown, the simplified method includes the following steps.

[0167] First, the lifting force F is determined based on the lifting load parameters. In one specific embodiment, the lifting load parameters include the opening hydraulic pressure P of the lifting jack 3 and the cylinder diameter D of the lifting jack 3. Then, the lifting force F satisfies: F = π × (D / 2)2 ×P. Where P is the opening hydraulic pressure of the lifting jack 3, in MPa; D is the cylinder diameter of the lifting jack 3, in mm; and F is the lifting force, in N.

[0168] Secondly, the maximum bending moment Mmax is determined based on the lifting force F and the lever arm relationship in the simplified verification model. In a specific embodiment, the lever arms on both sides of the lifting force application location in the simplified verification model are L1 and L2, respectively, then the maximum bending moment Mmax is determined. max Satisfy: M max =F×L1×L2 / (L1+L2). Where L1 and L2 are the equivalent force arms on both sides of the position where the lifting force is applied, and the unit is mm.

[0169] Subsequently, based on the maximum bending moment M max The equivalent bending moment M of the section to be checked is determined by its positional relationship along the length direction. In a specific embodiment, the distance relationship between the section to be checked and the location of the maximum bending moment is characterized by L and L1. Then, the equivalent bending moment M satisfies: M = (L1 / L1) / L1. s )×M max Where M is the equivalent bending moment of the section to be checked; L s L1 is the equivalent length parameter related to the relationship between the section to be checked and the bending moment; L2 is the lever arm parameter corresponding to the position of the section to be checked. Under different check positions, L and L1 can be adjusted according to... Figure 11 The bending moment variation relationship shown is determined.

[0170] Then, calculate the moment of inertia Msection, and the calculation relationship is: Msection 截 =(B1×H 3 ) / 12; where B1 is the effective width of the cross-section at the calculated location, in mm; H is the height at the calculated location, in mm.

[0171] Next, the bending stress σ at the calculated location of tongue plate 2 is calculated, and the calculation relationship is: σ = [(M / M 截 [M] × H / 2. Where M is the section bending moment, M 截 Let H be the moment of inertia of the cross section, and H be the height at the calculated position.

[0172] Furthermore, after obtaining the bending stress σ, the safety factor K of the tongue plate 2 is determined according to the ratio of the preset stress limit [σ] to the bending stress σ: K = [σ] / σ. When the safety factor K is greater than the preset safety threshold, the tongue plate 2 is deemed to meet the strength requirements. In a specific embodiment, the preset safety threshold is 1.5; when K is greater than 1.5, the design and selection of the tongue plate 2 are considered reasonable.

[0173] By employing the simplified verification process described above, the calculations of lifting force, maximum bending moment, equivalent bending moment of the section to be verified, bending stress, and safety factor can be completed quickly without disassembling the multiple contact points of the tongue plate 2 one by one. This simplified verification process is suitable for rapid on-site verification, initial scheme selection, or batch verification scenarios, and is beneficial to improving the efficiency of tongue plate 2 strength verification.

[0174] Furthermore, this invention also provides a tongue plate strength verification system for a support pushing mechanism. The support pushing mechanism includes a pushing rod and a tongue plate connected to the pushing rod. The system includes: a parameter acquisition module for acquiring the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate; an overall force modeling module for generating the lifting load acting on the support pushing mechanism under the lifting condition based on the lifting load parameters, and constructing an overall force balance model of the support pushing mechanism in combination with the geometric parameters of the support pushing mechanism; and an input load equivalence module for determining the load transmitted to the tongue plate in the overall force balance model based on the force distribution relationship of the lifting load in the support pushing mechanism. The system includes: an input load for the plate; a local stress modeling module, used to construct a local equivalent stress model of the tongue plate based on the input load and multiple stress locations of the tongue plate, and to determine the cross-section to be checked and the equivalent bending moment of the cross-section based on the local equivalent stress model and the cross-sectional parameters of the tongue plate; a cross-section weakening processing module, used to perform equivalent cross-section weakening processing on the cross-section to be checked based on the cross-sectional parameters of the tongue plate to obtain the cross-sectional bending resistance parameters of the cross-section to be checked; and a verification result generation module, used to perform bending stress conversion on the cross-section to be checked based on the equivalent bending moment and cross-sectional bending resistance parameters of the cross-section to be checked, and to perform a safety verification of the tongue plate based on the bending stress conversion results and preset verification conditions to obtain the strength verification result of the tongue plate.

[0175] Furthermore, embodiments of the present invention provide a tongue plate strength verification device for a support pushing mechanism, comprising: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, the instructions being executed by the at least one processor to cause the at least one processor to perform the tongue plate strength verification method in the support pushing mechanism as described above.

[0176] Subsequently, this embodiment of the invention provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, implement the tongue plate strength verification method in the support pushing mechanism as described above.

[0177] In summary, this invention provides a method, system, equipment, and medium for verifying the strength of the tongue plate in a support moving mechanism. Addressing the problem of tongue plate strength verification in a support moving mechanism, this invention, considering the overall force transmission relationship of the support moving mechanism under lifting conditions, determines the input load transmitted to the tongue plate via the equivalent force position at the front end. Furthermore, it constructs a local equivalent force model based on multiple force positions of the tongue plate to determine the cross-section to be verified and its equivalent bending moment. By performing equivalent section weakening treatment on the cross-section to be verified and obtaining the section bending resistance parameters, this invention can connect the local force on the tongue plate, the weakening of the hole, and the bending stress conversion process, thereby obtaining the strength verification result of the tongue plate.

[0178] Therefore, this invention helps to improve the matching degree between the tongue plate strength verification results and the actual stress state, reduces the risk of strength failure caused by local stress concentration and cross-sectional weakening, and improves the operational reliability of the support pushing mechanism. Furthermore, in some embodiments, this invention can also provide a simplified calculation scheme, quickly calculating the maximum bending moment, cross-sectional bending moment, bending stress, and safety factor based on the lifting force, thereby adapting to the rapid verification needs of engineering sites and improving the efficiency of tongue plate strength verification.

[0179] Those skilled in the art will understand that embodiments of the present invention can be provided as methods, systems, or computer program products. Therefore, the present invention can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, the present invention can take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0180] This invention is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the invention. It will be understood that each block of the flowchart illustrations and / or block diagrams, as well as combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions.

[0181] It should be noted that any reference numerals placed between parentheses in the claims should not be construed as limiting the claims. The word "comprising" does not exclude the presence of components or steps not listed in the claims. The word "a" or "an" preceding a component does not exclude the presence of a plurality of such components. The invention can be implemented by means of hardware comprising several different components and by means of a suitably programmed computer. In claims that enumerate several means, several of these means may be embodied by the same hardware. The use of the terms first, second, third, etc., is merely for convenience of expression and does not indicate any order. These terms can be understood as part of the component names.

[0182] Furthermore, it should be noted that in the description of this specification, the terms "one embodiment," "some embodiments," "embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Furthermore, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0183] Although preferred embodiments of the invention have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the claims should be interpreted to include both the preferred embodiments and all changes and modifications falling within the scope of the invention.

[0184] Obviously, those skilled in the art can make various modifications and variations to this invention without departing from its spirit and scope. Therefore, if these modifications and variations fall within the scope of the claims of this invention and their equivalents, then this invention should also include these modifications and variations.

Claims

1. A method for verifying the strength of a tongue plate in a support pushing mechanism, characterized in that, The support pushing mechanism includes a pushing rod and a tongue plate connected to the pushing rod, and the method includes: Obtain the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate; Based on the lifting load parameters, the lifting load acting on the support pushing mechanism under the lifting working condition is formed, and the overall force balance model of the support pushing mechanism is constructed in combination with the geometric parameters of the support pushing mechanism. In the overall force balance model, the input load transmitted to the tongue plate is determined based on the force distribution relationship of the lifting load in the support pushing mechanism. Based on the input load and multiple stress locations of the tongue plate, a local equivalent stress model of the tongue plate is constructed. Based on the local equivalent stress model and the cross-sectional parameters of the tongue plate, the cross-section of the tongue plate to be checked and the equivalent bending moment of the cross-section to be checked are determined. Based on the cross-sectional parameters of the tongue plate, the cross-sectional weakening equivalent treatment is performed on the cross-sectional section to be checked to obtain the cross-sectional bending parameters of the cross-sectional section to be checked. Based on the equivalent bending moment and section bending parameters of the section to be checked, the bending stress of the section to be checked is converted, and the tongue plate is checked for safety according to the bending stress conversion result and the preset check conditions to obtain the strength check result of the tongue plate.

2. The method for verifying the strength of the tongue plate in the support pushing mechanism as described in claim 1, characterized in that, Based on the lifting load parameters, the lifting load acting on the support moving mechanism under the lifting condition is calculated. Then, combined with the geometric parameters of the support moving mechanism, an overall force balance model of the support moving mechanism is constructed, including: The lifting force exerted by the lifting drive component on the support pushing mechanism is determined based on the lifting load parameters. Based on the geometric parameters of the support pushing mechanism, determine the equivalent force position at the front end, the force position at the rear end of the support pushing mechanism, and the position of the lifting force, and determine the lever arm relationship between the position of the lifting force and the equivalent force position at the front end and the force position at the rear end of the support pushing mechanism. The equivalent force-bearing position at the front end and the force-bearing position at the tail end of the support pushing mechanism are taken as the force-bearing positions at both ends, and the position where the lifting force acts is taken as the input position of the lifting force between the two force-bearing positions. Based on the lever arm relationship, an overall force distribution model for the support pushing mechanism to distribute the lifting force is constructed. The front equivalent force-bearing position is the equivalent position located near the tongue plate where the lifting force is applied and which bears the distribution of the lifting force. The tail force-bearing position of the support pushing mechanism is the position in the support pushing mechanism that is set relative to the front equivalent force-bearing position and bears the distribution of the lifting force.

3. The method for verifying the strength of the tongue plate in the support pushing mechanism as described in claim 2, characterized in that, In the overall force balance model, based on the force distribution relationship of the lifting load in the support pushing mechanism, the input load transmitted to the tongue plate is determined, including: In the overall force balance model, the front lever arm is determined based on the projection distance along the length of the push rod from the position of the lifting force to the equivalent force position at the front end. The rear lever arm is determined based on the projected distance along the length of the pushing rod from the position of the lifting force to the force position at the tail end of the support pushing mechanism. The total lever arm between the two force positions is determined based on the projected distance from the equivalent force position at the front end to the force position at the rear end of the support pushing mechanism along the length of the pushing rod. Based on the proportional relationship between the front lever arm, the rear lever arm and the total lever arm, the lifting force is distributed at both ends to obtain the front distribution force corresponding to the equivalent front force position and the tail distribution force corresponding to the tail force position of the support pushing mechanism. The front-end force is used as the input load transmitted to the tongue plate through the front-end equivalent force-bearing position.

4. The method for verifying the strength of the tongue plate in the support pushing mechanism as described in claim 1, characterized in that, Based on the input load and multiple force locations of the tongue plate, a local equivalent force model of the tongue plate is constructed, including: Based on the assembly relationship of the tongue plate in the support pushing mechanism, the front force position of the tongue plate that bears the input load is determined, and the front force position is taken as the load application position; Based on the contact relationship between the tongue plate and the adjacent force-bearing components in the support pushing mechanism, and the tail end force-bearing position on the tongue plate along the length direction opposite to the front force-bearing position, multiple force-bearing positions along the length direction of the tongue plate are determined; wherein, the adjacent force-bearing components include connecting components and guiding components that contact the tongue plate; The location of the force boundary is determined based on the force location other than the load application location among multiple force locations; Based on the load application location, the force boundary location, the distance between the load application location and each force boundary location, and the distance between adjacent force boundary locations, a local equivalent force model is constructed to obtain the local equivalent force parameters of the tongue plate at multiple force locations.

5. The method for verifying the strength of the tongue plate in the support pushing mechanism as described in claim 4, characterized in that, Based on the local equivalent stress model and the cross-sectional parameters of the tongue plate, the cross-section to be checked and the equivalent bending moment of the cross-section to be checked are determined, including: Based on the local equivalent force parameters, multiple force locations, and the cross-sectional position along the length of the tongue plate obtained from the local equivalent force model, the bending moment variation relationship of the tongue plate along the length direction is determined. Based on the bending moment variation relationship, determine the location of the maximum bending moment on the tongue plate or the location of the section that meets the preset bending moment condition; Determine the position of the hole section on the tongue plate based on the cross-sectional parameters of the tongue plate; At least one of the following is identified as the section to be checked: the location of the maximum bending moment, the section location that meets the preset bending moment condition, the section location of the hole, the preset adjacent area of ​​the load application location, and the preset adjacent area of ​​the force boundary location. The equivalent bending moment of the section to be checked is determined based on the local equivalent stress parameters, multiple stress locations, and the position of the section to be checked along the length of the tongue plate.

6. The method for verifying the strength of the tongue plate in the support pushing mechanism as described in claim 1, characterized in that, Based on the cross-sectional parameters of the tongue plate, the cross-section to be checked is subjected to equivalent cross-sectional weakening treatment to obtain the cross-sectional bending parameters of the cross-section to be checked, including: Extract the cross-sectional dimension parameters and hole dimension parameters of the section to be checked from the cross-sectional parameters of the tongue plate; wherein, the hole dimension parameters include at least one of the following: hole diameter, hole width, hole height, and the projected dimension of the hole in the cross-section to be checked; The original section of the section to be checked is determined based on the cross-sectional dimension parameters, and the weakened area in the original section that does not participate in the bending load is determined based on the hole dimension parameters; The weakened area is subtracted from the original cross section to form the equivalent bearing section of the cross section to be checked; Based on the geometric parameters of the equivalent bearing section, the flexural modulus of the section to be checked is determined and used as the flexural parameter of the section to be checked.

7. The method for verifying the strength of the tongue plate in the support pushing mechanism as described in claim 1, characterized in that, Based on the equivalent bending moment and section bending parameters of the section to be checked, the bending stress of the section to be checked is converted, and the tongue plate is safely checked according to the bending stress conversion results and the preset check conditions to obtain the strength check results of the tongue plate, including: Based on the ratio between the equivalent bending moment of the section to be checked and the bending resistance parameter of the section, the bending stress of the section to be checked is converted to obtain the bending stress of the section to be checked. The safety factor of the tongue plate is obtained based on the ratio between the preset stress limit and the bending stress of the section to be checked. The safety factor of the tongue plate is compared with the preset safety threshold to obtain the safety check judgment result used to characterize whether the tongue plate meets the strength requirements; The bending stress of the section to be checked, the safety factor of the tongue plate, and the safety check judgment result are used as the strength check result of the tongue plate.

8. A tongue plate strength verification system for a support pushing mechanism, characterized in that, The support pushing mechanism includes a pushing rod and a tongue plate connected to the pushing rod, and the system includes: The parameter acquisition module is used to acquire the lifting load parameters of the support pushing mechanism, the geometric parameters of the support pushing mechanism, and the cross-sectional parameters of the tongue plate; The overall force modeling module is used to generate the lifting load acting on the support pushing mechanism under the lifting condition based on the lifting load parameters, and to construct the overall force balance model of the support pushing mechanism in combination with the geometric parameters of the support pushing mechanism. The input load equivalent module is used to determine the input load transmitted to the tongue plate in the overall force balance model based on the force distribution relationship of the lifting load in the support pushing mechanism. The local stress modeling module is used to construct a local equivalent stress model of the tongue plate based on the input load and multiple stress locations of the tongue plate, and to determine the cross section of the tongue plate to be checked and the equivalent bending moment of the cross section to be checked based on the local equivalent stress model and the cross section parameters of the tongue plate. The section weakening processing module is used to perform equivalent section weakening processing on the section to be checked based on the section parameters of the tongue plate, so as to obtain the section bending resistance parameters of the section to be checked. The verification result generation module is used to perform bending stress conversion on the section to be verified based on the equivalent bending moment and section bending parameters of the section to be verified, and to perform safety verification on the tongue plate according to the bending stress conversion result and the preset verification conditions, so as to obtain the strength verification result of the tongue plate.

9. A tongue plate strength verification device for a support pushing mechanism, characterized in that, include: At least one processor; and memory that is communicatively connected to at least one processor; The memory stores instructions that can be executed by at least one processor, which are executed by at least one processor to cause the at least one processor to perform the tongue plate strength verification method in the support pushing mechanism as described in any one of claims 1-7.

10. A computer-readable storage medium storing computer-executable instructions thereon, characterized in that, When the executable instructions are executed by the processor, they implement the tongue plate strength verification method in the support pushing mechanism as described in any one of claims 1-7.

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