Method, device, equipment and medium for selecting swing clamp cylinder

Abstract

The application discloses a type selection method, device, equipment and medium of a rotary clamping cylinder, and the method comprises the following steps: determining a first working condition and a second working condition of the cylinder; acquiring type selection parameters including a clamping point distance and a required cylinder speed; determining an initial cylinder diameter value based on a required clamping force and the clamping point distance, and combining a working condition rule to perform static verification; after the static verification passes, performing rotational inertia verification based on the required cylinder speed and a pressure plate parameter; and outputting a target model after the verification passes. Through working condition classification, quantitative bending moment and the additional dynamic rotational inertia verification link, the application overcomes the defects that the traditional static type selection is separated from the actual mechanical working condition, effectively avoids cylinder overload and motion instability, and meets the accuracy requirement of type selection under high rhythm and high precision working conditions.

Description

Technical Field

[0001] This invention relates to the technical field of industrial automation component selection, and in particular to a method, apparatus, equipment and medium for selecting a rotary clamping cylinder. Background Technology

[0002] Rotary clamping cylinders, as pneumatic actuators integrating rotary avoidance and linear clamping, are widely used in industrial fields such as automobile manufacturing, automated assembly, and robotics. As manufacturing systems continuously increase their requirements for the precision and reliability of actuators, their selection technology has evolved from being dominated by manual experience to digital automatic matching.

[0003] For example, in the prior art, patent CN119782380A discloses an automatic cylinder selection and matching method. This technology constructs a mapping database between cylinder categories and auxiliary components. Based on the input cylinder model and quantity, it can automatically retrieve and match corresponding auxiliary components, thereby generating a bill of materials (BOM) and a selection and matching table. This type of automatic selection scheme based on database retrieval improves the management efficiency of standard parts configuration to a certain extent and represents a typical development achievement of cylinder selection in terms of information technology and material management at this stage.

[0004] However, the aforementioned existing technologies have significant shortcomings in addressing the selection requirements for rotary clamping cylinders with complex mechanical characteristics. Taking the aforementioned comparative document CN119782380A as an example, its core logic is limited to the material-level matching of model and auxiliary components. Essentially, it is still a static pairing detached from actual mechanical conditions, completely ignoring the dynamic characteristics during cylinder operation. Traditional rotary clamping cylinder selection often relies solely on rough estimations based on installation space, air source pressure, and static clamping force, lacking consideration for the rotational inertia generated by the pressure plate (especially non-standard pressure plates) during rotation and the external bending moment caused by the distance between clamping points. Because existing technologies have failed to establish a first-condition classification based on general-purpose pressure plates and user-defined non-standard pressure plates, and have not refined the second-condition verification rules such as single / double-sided or different geometric orientation connections, and lack a dynamic rotational inertia verification step based on cylinder speed and pressure plate parameters, the selection results are difficult to match the real dynamic operating environment, easily leading to cylinder overload or operational instability, and failing to meet the selection accuracy requirements under high-cycle, high-precision operating conditions. Summary of the Invention

[0005] To overcome the shortcomings of existing technical solutions, embodiments of the present invention provide a method, apparatus, equipment, and medium for selecting a rotary clamping cylinder.

[0006] The technical solution adopted by this invention to solve its technical problem is: In a first aspect, the present invention provides a method for selecting a rotary clamping cylinder, the method comprising: Determine the type of rotary clamping cylinder to be selected and the first working condition of the rotary clamping cylinder, wherein the first working condition is a general-purpose pressure plate or a user-designed non-standard pressure plate; Based on the first working condition, determine the second working condition of the rotary clamping cylinder; Obtain the selection parameters of the rotary clamping cylinder, which include at least the operating pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance, and rotation direction; Based on the required clamping force and clamping point distance, determine the initial cylinder diameter value of the rotary clamping cylinder; According to the verification rules corresponding to the first and second working conditions, the rotary clamping cylinder is statically verified using the selection parameters and the initial cylinder diameter value. When the static verification is passed, the rotational inertia of the rotary clamping cylinder is verified based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value. When the rotational inertia verification is passed, the initial cylinder diameter value is determined as the target cylinder diameter value, and the model of the rotary clamping cylinder corresponding to the target cylinder diameter value is output.

[0007] Secondly, the present invention provides a selection device for a rotary clamping cylinder, the device employing the selection method for a rotary clamping cylinder as described in the first aspect above, the selection device comprising: The first determining module is used to determine the type of rotary clamping cylinder to be selected and the first working condition of the rotary clamping cylinder, wherein the first working condition is a general pressure plate or a user-designed non-standard pressure plate. The second determining module is used to determine the second working condition of the rotary clamping cylinder based on the first working condition; The acquisition module is used to acquire the selection parameters of the rotary clamping cylinder. The selection parameters include at least the operating pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance, and rotation direction. The third determining module is used to determine the initial cylinder diameter value of the rotary clamping cylinder based on the required clamping force and the distance between the clamping points; The static verification module is used to perform static verification on the rotary clamping cylinder according to the verification rules corresponding to the first working condition and the second working condition, using the selection parameters and the initial cylinder diameter value. The rotational inertia verification module is used to verify the rotational inertia of the rotary clamping cylinder based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value when the static verification passes. The output module is used to determine the initial cylinder diameter value as the target cylinder diameter value when the rotational inertia verification is passed, and to output the model of the rotary clamping cylinder corresponding to the target cylinder diameter value.

[0008] Thirdly, the present invention also provides a computer device, the computer device including a processor, a network interface, a memory and a communication bus, wherein the processor, the network interface and the memory communicate with each other through the communication bus; Memory, used to store computer programs; When the processor executes the program stored in the memory, it implements the steps of the method for selecting the rotary clamping cylinder described in any one of the first aspects above.

[0009] Fourthly, the present invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the steps of the method for selecting a rotary clamping cylinder as described in any one of the first aspects above.

[0010] Compared with the prior art, the beneficial effects of the present invention are: By clearly distinguishing between general-purpose pressure plates and user-specific non-standard pressure plates, and refining the second working conditions such as single-sided and double-sided types and connections with different geometric postures, a precise premise is provided for formulating differentiated verification rules. Addressing the issue of traditional selection methods not considering external bending moments, the clamping point distance is incorporated into the selection parameters, and the initial cylinder diameter value is determined in conjunction with the required clamping force, thereby quantifying the torque effect caused by the pressure plate length into the basic selection. After completing rigorous static verification based on the working condition rules, the rotational inertia verification step combines the required cylinder speed with the pressure plate parameters to calculate the dynamic rotational inertia generated when the non-standard pressure plate rotates. This comprehensively integrates complex mechanical dynamic characteristics into the selection logic, effectively avoiding cylinder overload or operational instability, and meeting the accuracy requirements for selection under high-cycle, high-precision working conditions. Attached Figure Description

[0011] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0012] Figure 1 This is a flowchart of the selection method according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the pressure plate type in the first working condition of this embodiment of the invention; Figure 3 This is a structural diagram illustrating the specific classification of the second working condition when the first working condition is a general pressure plate, according to an embodiment of the present invention. Figure 4 This is a schematic diagram of the structure of a single-arm pressure plate according to an embodiment of the present invention; Figure 5This is a schematic diagram of the structure of the double-arm type pressure plate according to an embodiment of the present invention; Figure 6 This is a schematic diagram of the structural parameters and rotational inertia calculation model for six second working conditions when the first working condition of this invention is a user non-standard pressure plate; Figure 7 This is a diagram showing the bending moment according to an embodiment of the present invention; Figure 8 This is a diagram of the moment of inertia of an embodiment of the present invention; Figure 9 This is a block diagram of the selection device according to an embodiment of the present invention; Figure 10 This is a schematic block diagram of a computer device according to an embodiment of the present invention. Detailed Implementation

[0013] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0014] It should be understood that, when used in this specification and the appended claims, the terms "comprising" and "including" indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.

[0015] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.

[0016] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.

[0017] To address the issue that existing technologies lack a dynamic rotational inertia verification process based on cylinder speed and pressure plate parameters, which makes it difficult for selection results to match the actual dynamic operating environment and easily leads to cylinder overload or operational instability, thus failing to meet the accuracy requirements for selection under high-cycle and high-precision operating conditions, this invention provides a method, device, equipment, and medium for selecting rotary clamping cylinders.

[0018] The following details the specific steps of a method for selecting a rotary clamping cylinder according to an embodiment of the present invention, based on the appendix. Figure 1-8 As shown, the specific steps of the selection method for this rotary clamping cylinder include: Step S110: Determine the type of rotary clamping cylinder to be selected and the first working condition of the rotary clamping cylinder. The first working condition is a general-purpose pressure plate or a user-designed non-standard pressure plate.

[0019] Specifically, the selection system guides users through initial configuration via a human-machine interface. First, it reads the equipment's preset model database and displays a list of available rotary clamping cylinder types. Users select the specific cylinder type in the system based on the process clearance requirements of the automated production line, such as a 90° rotary clamping cylinder, a 90° constant rotary clamping cylinder, a 180° rotary clamping cylinder, or a 360° rotary clamping cylinder. Then, the system displays a working condition selection interface, requiring the user to confirm the first working condition of the end effector. If the user selects the "Universal Pressure Plate" option on the interface, the system determines that the current working condition is standard and locks the standard pressure plate parameters provided by the cylinder manufacturer in the background, such as the standard pressure plate length, weight, and center of gravity position, as known constants for calculating the moment of inertia in subsequent basic solutions.

[0020] It should be noted that for applications requiring customized fixtures, when the user selects a non-standard pressure plate in the first working condition option of the human-machine interface, the system not only records the judgment result of this first working condition but also triggers the corresponding parameter input module. The system will require the user to input the detailed physical properties of the non-standard pressure plate, including but not limited to the plate's geometry (e.g., thin rods or square plates), its length, width, height, mass, and other external dimensions, as well as its center of gravity offset. By binding these custom parameters of the non-standard pressure plate with the previously determined cylinder type, the system can perform complex bending moment synthesis calculations for the non-standard pressure plate in subsequent basic solutions.

[0021] In this way, by strictly distinguishing between general-purpose pressure plates and user-specific non-standard pressure plates, the simplified parameters of standard parts are not mistakenly applied to complex non-standard pressure plates, and the errors in torque and moment of inertia calculation caused by ambiguous working condition definitions are eliminated, effectively reducing the risk of cylinder overload or incomplete rotation.

[0022] Step S120: Determine the second working condition of the rotary clamping cylinder based on the first working condition.

[0023] Specifically, in some embodiments, when the selected system determines that the first working condition is a general-purpose pressure plate in the preliminary steps, the system further determines the second working condition based on the path guidance of the first working condition. That is, the system calls the standard pressure plate database and asks the user or the user to identify the stress pattern of the standard pressure plate according to the design drawings, and determines the second working condition as either a double-sided or single-sided type. If the system determines it to be a single-sided type, then in the subsequent static verification, only the bending moment generated by the clamping force on one side is calculated; if it is determined to be a double-sided type, then the stress on both sides is calculated according to the principle of torque superposition. This implementation method quickly matches the corresponding mechanical boundary conditions for the standard application scenario through a simple binary search.

[0024] In other embodiments, for complex customized production lines, when the first working condition is determined to be a user-designed non-standard pressure plate, the system triggers geometric modeling analysis logic to determine the second working condition. For example, when the user-input non-standard pressure plate is a slender rod-like structure, the second working condition is refined into one of the following three types based on the connection position between the rod and the cylinder rotation shaft: the rotation shaft is perpendicularly connected to the end of the rod; the rotation shaft is perpendicularly connected to the center of gravity of the rod; or the rotation shaft is perpendicularly connected to one end of the rod and the other end has an eccentric load. The system locks one of the above spatial connection relationships as the current second working condition, thereby establishing an accurate rigid body kinematic model for subsequent calculation of the gravitational bending moment and the moment of inertia about the rotation shaft of the non-standard pressure plate.

[0025] In another embodiment, following the non-standard pressure plate scenario of the previous embodiment, if the user-input non-standard pressure plate is a square plate structure with certain width and height dimensions, the system, based on the guidance of the first working condition, further determines the second working condition as different posture combinations of the square plate and the cylinder rotation axis. For example, the system determines the second working condition as the square plate vertically connected to the rotation axis with its center of gravity coinciding with the axis of rotation, or as the square plate horizontally connected to the rotation axis with the square plate perpendicular to the cylinder. By solidifying the installation posture of the two-dimensional planar component in three-dimensional space into a specific second working condition, it ensures that when facing large-sized, asymmetrical non-standard pressure plates, the selection system can still extract the correct feature parameters for subsequent verification.

[0026] Therefore, this step exhaustively enumerates and solidifies the installation posture of the pressure plate as the second working condition, avoiding the serious distortion assumption in traditional selection that all pressure plates are equivalent to point masses or simple cantilever beams. This ensures that the subsequent calculation of rotational inertia and verification of bending moment are completely consistent with the real laws of rigid body mechanics, thus improving the reliability of the selection results.

[0027] Step S130: Obtain the selection parameters of the rotary clamping cylinder. The selection parameters include at least the operating pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance, and rotation direction.

[0028] Specifically, in one embodiment, after determining the cylinder type and the first and second operating conditions, the selection system guides the user to input specific selection parameters through a structured form on the system's front-end interface. The system accurately collects the operating pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance, and rotation direction. After obtaining these parameters, the system directly transmits them to the initial cylinder diameter determination module in the basic scheme. Specifically, based on the obtained required clamping force F and clamping point distance, combined with the cylinder's lever arm conversion relationship, the system reverse-engineers and determines the initial cylinder diameter value of the rotary clamping cylinder, thereby transforming abstract process requirements into specific hardware dimensional specifications.

[0029] In another embodiment, the collaborative application of the selection parameters obtained above in the "static verification" stage of the basic scheme is explained. When the system determines that the first working condition is a non-standard user pressure plate (e.g., the rotating shaft is perpendicularly connected to the end of the thin rod), the system will call the required clamping force F and clamping point distance L1 obtained in this step. According to the torque physical equation M=F×L, the clamping bending torque M1 can be accurately calculated. At the same time, combined with the pressure plate weight parameter, the pressure plate gravity bending torque M2 is calculated using the clamping point distance L1. After the two are superimposed to generate the total torque M, it is compared with the allowable bending torque Mr obtained by looking up the initial cylinder diameter value. In this process, the clamping point distance L1, as a lever arm parameter, determines the rigor of the static verification.

[0030] In another embodiment, regarding the verification of the rotational inertia of the basic scheme based on the selection parameters obtained above, the system uses the required cylinder speed V obtained in this step as a search condition, and looks up the table in the pre-built cylinder performance database to obtain the maximum allowable rotational inertia I1 corresponding to the speed threshold. Subsequently, the system calculates the actual rotational inertia I2 by combining the pressure plate parameters corresponding to the initial cylinder diameter value, such as pressure plate length and weight.

[0031] The internal transmission mechanism of the rotary clamping cylinder to achieve the rotary action mainly relies on the helical pair formed by the helical groove and the pin inside the cylinder to convert the linear motion of the piston into rotational motion. By comparing I2 and I1, it is verified whether the huge inertial resistance generated by the pressure plate under the obtained required cylinder speed V, that is, the set rotational acceleration, exceeds the allowable stress limit of the material when it is converted into the squeezing and shearing force on the side wall of the helical groove and the pin. This ensures that the helical transmission mechanism will not jam, abnormally wear or structurally damage due to overload during dynamic rotation.

[0032] In addition, the rotation direction parameters are also recorded by the system and used to verify spatial interference in complex multi-axis tooling.

[0033] Therefore, by obtaining dynamic and geometric parameters that are easily overlooked, such as the clamping point distance L1 and the required cylinder speed V, accurate data support is provided for subsequent bending moment calculation and rotational inertia verification. This avoids problems such as cylinder spindle breakage or damage to the internal spiral groove and pin mechanism caused by incorrect lever arm estimation or speed-induced inertia exceeding the limit.

[0034] Step S140: Determine the initial cylinder diameter of the rotary clamping cylinder based on the required clamping force and the distance between the clamping points.

[0035] Specifically, in one embodiment, the selection system uses a mechanical analysis method to determine the initial cylinder diameter. The system first extracts the required clamping force F and clamping point distance L1 obtained in previous steps, and calculates the external load torque to be overcome at the clamping point according to the torque formula M_load = F × L1. Then, the system combines the torque conversion characteristics of the internal helical groove and pin-shaft mechanism of this model of rotary clamping cylinder, which converts linear motion into rotational motion. For example, based on the equivalent rotational arm r calculated from the helical groove lead, the system back-calculates the theoretical thrust required by the cylinder piston: F_thrust = M_load / r. After obtaining the theoretical thrust, the system calls the previously obtained operating pressure P, and combines it with the cylinder pressure area formula S = F_thrust / (P × η), where η is a preset mechanical efficiency coefficient, to calculate the theoretical cylinder diameter. This is then rounded up according to the corresponding standard cylinder diameter series, such as 20mm, 25mm, 32mm, 40mm, etc., to accurately determine the initial cylinder diameter value of the rotary clamping cylinder.

[0036] In another embodiment, the system uses the required cylinder speed V obtained in this step as a search condition, looks up the table in the pre-built cylinder performance database, and obtains the maximum allowable moment of inertia I1 corresponding to the speed threshold; then, the system calculates the actual moment of inertia I2 by combining the pressure plate parameters corresponding to the initial cylinder diameter value, such as pressure plate length and weight.

[0037] The essence of comparing I2 and I1 is to verify whether the compressive shear force generated by the inertia of the pressure plate on the internal screw pair under a set rotational acceleration exceeds the material limit, thereby preventing the mechanism from experiencing dynamic overload.

[0038] In addition, the rotation direction parameters are also recorded by the system and used to verify spatial interference in complex multi-axis tooling.

[0039] Therefore, by obtaining dynamic and geometric parameters that are easily overlooked, such as the clamping point distance L1 and the required cylinder speed V, accurate data support is provided for subsequent bending moment calculation and rotational inertia verification. This completely avoids the problems of cylinder spindle bending and breakage caused by incorrect lever arm estimation, as well as jamming or mechanical damage to the internal spiral groove and pin shaft mating mechanism caused by speed-induced inertia exceeding the limit.

[0040] Step S150: Based on the verification rules corresponding to the first and second working conditions, perform static verification on the rotary clamping cylinder using the selection parameters and initial cylinder diameter value.

[0041] Specifically, in one embodiment, the selection system determines that the first working condition is a general-purpose pressure plate, and the second working condition is a single-sided or double-sided type. At this time, the static verification rule corresponding to the standard working condition is invoked, using a table lookup comparison method. Specifically, firstly, the initial cylinder diameter value determined in the previous steps is retrieved from a preset standard parts database, and a corresponding standard pressure plate is automatically configured for the initial cylinder diameter value, and the standard clamping point distance L2 of the standard pressure plate is obtained. Subsequently, by extracting the operating pressure P from the selection parameters, the maximum clamping distance L3 that the corresponding model of the current initial cylinder diameter value can withstand under the operating pressure is determined by looking up a table. During the execution of the static verification logic, it is determined whether the condition L2 < L3 is met. If L2 > L3, the static verification is deemed unqualified, the system marks the cylinder model corresponding to the initial cylinder diameter value as unqualified and excludes it, and simultaneously triggers recursive logic to re-determine a larger initial cylinder diameter value. If L2 < L3 is met, the static verification is deemed successful, and the subsequent process begins.

[0042] It should be noted that the selection system determines the first working condition to be a non-standard pressure plate for the user. For example, the second working condition is where the rotating shaft of the rotary clamping cylinder is vertically connected to the end of the thin rod. In this case, the system calls the static verification rules corresponding to the non-standard working condition and uses the torque synthesis calculation method. The system first uses the required clamping force F and the clamping point distance L1 in the selection parameters to calculate the clamping bending torque M1 according to the torque formula (the obtained calculation formula is M1=F×L1). Then, it extracts the pressure plate weight m and the clamping point distance L1 in the selection parameters to calculate the pressure plate gravity bending torque M2 caused by the pressure plate's own weight (the obtained calculation formula is M2=m×g×L1 / 2 or calculated according to the specific center of gravity position). The total torque M is determined by superimposing the two (the obtained calculation formula is M=M1+M2).

[0043] After obtaining the total torque M, the rated allowable bending torque Mr of the cylinder spindle for this model is obtained by looking up the table using the initial cylinder diameter value. Then, the static verification logic is executed to determine whether M < Mr. If M > Mr, it means that the spindle strength of the initial cylinder diameter value cannot withstand the huge cantilever bending moment generated by the non-standard pressure plate. The system determines that the static verification has failed, excludes this model, and re-executes the previous calculation steps. If M < Mr, the static verification is determined to be successful.

[0044] Step S160: When the static verification is passed, the rotational inertia of the rotary clamping cylinder is verified based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value.

[0045] Specifically, in one embodiment, for a standard configuration scenario, when the system determines that the preceding static verification (such as the verification of the maximum clamping distance of the standard pressure plate L2 < L3) has passed, the rotational inertia verification process is triggered. The system first extracts the required cylinder speed V from the selection parameters and, combined with the currently determined initial cylinder diameter value, performs a two-dimensional lookup in the preset cylinder dynamic performance database to obtain the maximum permissible rotational inertia I1 that the transmission mechanism inside the cylinder, based on the helical groove and pin shaft cooperation, can withstand at that cylinder diameter and speed. Subsequently, the system calls the pressure plate parameters corresponding to the initial cylinder diameter value, i.e., the preset weight and geometric dimensions of the standard pressure plate, and calculates the actual rotational inertia I2 of the standard pressure plate about the rotation axis using rigid body dynamics formulas. When executing the comparison logic, if the calculated I2 is less than the I1 obtained from the lookup table, it is determined that the inertial resistance generated by the pressure plate during rotation does not exceed the dynamic bearing limit of the helical pair. The cylinder model corresponding to the initial cylinder diameter value has passed the rotational inertia verification and has the ability to rotate smoothly at that speed without jamming or structural damage.

[0046] In another embodiment, for complex non-standard customized scenarios, such as a first working condition involving a user-designed non-standard pressure plate and a second working condition where "the rotating shaft of the rotary clamping cylinder is vertically connected to the end of a thin rod," after the system confirms that the total torque M generated by the non-standard pressure plate is less than the allowable bending torque Mr (i.e., static verification passed), the maximum allowable moment of inertia I1 is obtained by looking up a table based on the "required cylinder speed V." At this time, the system extracts the pressure plate parameters corresponding to the initial cylinder diameter value bound in the previous working condition. Due to the change in the pressure plate shape, the system automatically adapts to the corresponding physical model, such as the formula for calculating the moment of inertia corresponding to the initial cylinder diameter value:

[0047] The system accurately calculates the actual rotational inertia I generated by the non-standard pressure plate. The system compares I with I1. If I < I1, the rotational inertia verification is deemed successful. If I ≥ I1, it indicates that the inertia of the non-standard pressure plate is too large at the set cylinder speed, which will cause a violent impact or failure to reach the position when the cylinder starts and stops. The system then determines that the verification has failed and triggers the model reselection mechanism.

[0048] After obtaining the total torque M, the rated allowable bending torque Mr of the cylinder spindle for this model is obtained by looking up the table using the initial cylinder diameter value. Then, the static verification logic is executed to determine whether M < Mr. If M > Mr, it means that the spindle strength of the initial cylinder diameter value cannot withstand the huge cantilever bending moment generated by the non-standard pressure plate. The system determines that the static verification has failed, excludes this model, and re-executes the previous calculation steps. If M < Mr, the static verification is determined to be successful.

[0049] Step S170: When the moment of inertia verification is passed, the initial cylinder diameter value is determined as the target cylinder diameter value, and the model of the rotary clamping cylinder corresponding to the target cylinder diameter value is output.

[0050] Specifically, after completing the preliminary steps, if the calculated actual moment of inertia I is less than the maximum allowable moment of inertia I1 obtained by looking up the cylinder speed table, the selection system immediately terminates the current iterative calculation loop. At this time, the status flag of the initial cylinder diameter value, such as 32mm, which was previously calculated based on the clamping force and the distance between the clamping points, is changed from pending verification to the target cylinder diameter value in the system memory. Subsequently, the system automatically calls the cylinder type initially determined in the basic scheme, such as a 90° rotary clamping cylinder, and the currently locked target cylinder diameter value of 32mm. It performs a multi-condition joint search in the complete product database in the background, extracts the specific product code of the manufacturer that fully matches these two core features, and renders and outputs this model as the final selection result directly to the result display area of ​​the human-computer interaction interface.

[0051] To more clearly demonstrate the ultimate decision-making role of this step in the overall iterative logic of the basic solution, if the system determines during the moment of inertia verification stage that the actual moment of inertia I is greater than or equal to the maximum allowable moment of inertia I1, i.e., the verification fails, the system will not execute the output action of this step. Instead, the system will mark and exclude the cylinder model corresponding to the currently failed initial cylinder diameter value, and then re-execute the steps of determining the initial cylinder diameter value and its subsequent static verification and moment of inertia verification according to the preset cylinder diameter increment sequence, for example, automatically stepping from 32mm to 40mm. Only when the system automatically iterates and finds a larger cylinder diameter value that simultaneously meets the static torque requirement and the dynamic inertia requirement will this step be finally triggered, establishing the final cylinder diameter value obtained from the iteration as the target cylinder diameter value, and accurately outputting the model of the larger-sized rotary clamping cylinder, thereby ensuring the safe and usable output model.

[0052] according to Figures 3-6 As shown, in some specific embodiments, the second working condition of the rotary clamping cylinder is determined according to the first working condition, specifically including the following steps: If the first working condition is a general-purpose pressure plate, the second working condition includes a double-arm pressure plate or a single-arm pressure plate.

[0053] Specifically, when the selection system determines the first working condition to be a general-purpose pressure plate in the preliminary steps, it triggers standard part shape recognition logic to determine the second working condition. The system interface provides structural topology options to guide the user in confirming the distribution of the standard pressure plate relative to the cylinder rotation axis. If the system identifies that the clamping force is symmetrically distributed on both sides of the rotation axis, the system determines the second working condition as a double-arm pressure plate, commonly referred to as a double-sided pressure plate structure in engineering. If the system identifies that the clamping force exists only on one side of the rotation axis, forming a cantilever force state, the second working condition is determined as an arm-type pressure plate, i.e., a single-sided pressure plate structure. The system binds the determined double-arm or single-arm type as a tag to the current selection task for subsequent static torque verification to call the corresponding force analysis model.

[0054] It should be noted that when the second working condition is a single-arm pressure plate, the formula for calculating the moment of inertia is: , ; When the second working condition is a double-arm pressure plate, the formula for calculating the moment of inertia is: , ; .

[0055] If the first working condition is a non-standard pressure plate, the second working condition is the connection position between the non-standard pressure plate and the rotating shaft.

[0056] Specifically, for complex customized production lines, when the first working condition is determined to be a non-standard pressure plate, 3D spatial geometric modeling logic is triggered. At this time, the second working condition is defined as the connection position between the non-standard pressure plate and the rotating shaft. For example, when the user-input non-standard pressure plate is a slender rod-shaped structure, the second working condition is specifically determined according to the user-specified installation nodes as either the rotating shaft being perpendicularly connected to the end of the cylindrical rod or the rotating shaft being perpendicularly connected to the center of gravity of the cylindrical rod. Similarly, when the non-standard pressure plate is a square plate structure with specific width and height dimensions, the system determines the second working condition as either the square plate being vertically connected to the rotating shaft with its center of gravity coinciding with the rotating shaft, or the square plate being connected to the end of the rotating shaft with the plates perpendicular to each other. By analyzing these specific connection positions, the spatial relative coordinates between the mass distribution center of the non-standard pressure plate and the cylinder rotation center are precisely located.

[0057] For standard clamping plates, a clear distinction is made between double-arm and single-arm types. With a double-arm type, the torques on both sides can partially cancel each other out during clamping, while with a single-arm type, a pure cantilever bending torque is generated on the cylinder spindle. This feature accurately identifies the stress pattern, ensuring that the torque calculations in subsequent static verification fully match the actual stress state, avoiding the risk of cylinder spindle bending and breakage due to mistakenly calculating a single-arm clamping plate as a double-arm clamping plate.

[0058] The magnitude of the moment of inertia of a rigid body is highly dependent on the position of the rotation axis. This solution can directly define the connection position between the non-standard pressure plate and the rotation axis as the second working condition. This is equivalent to establishing the coordinate origin of the calculus calculation in advance before entering the complex moment of inertia verification. This allows the system to accurately apply the parallel axis theorem or the direct integration method to calculate the real dynamic resistance. This allows for a precise determination of whether the transmission mechanism inside the cylinder, which is composed of a spiral groove and a pin, can smoothly overcome the dynamic resistance at this speed without jamming or mechanical damage. This ensures the smoothness of mechanical action while avoiding the cost waste caused by blindly selecting oversized cylinders.

[0059] according to Figure 6 As shown, in a further embodiment, if the first working condition is a non-standard pressure plate, and the second working condition is the connection position between the non-standard pressure plate and the rotating shaft, specifically including the following: The first working condition is a cylindrical rod or a square pressure plate, and the second working condition is any one of the following: Operating Condition 1: The rotating shaft of the rotary clamping cylinder is vertically connected to the end of the cylindrical rod; Operating Condition 2: The rotating shaft of the rotary clamping cylinder is vertically connected to the center of gravity of the cylindrical rod; Operating Condition 3: The rotating shaft of the rotary clamping cylinder is vertically connected to one end of the cylindrical rod, and the other end of the cylindrical rod is connected to a load; Operating Condition 4: The square pressure plate is vertically connected to the rotating shaft of the rotary clamping cylinder, and the center of gravity of the square pressure plate coincides with the axis of the rotating shaft; Operating Condition 5: The rotating shaft of the rotary clamping cylinder is connected to the end of the square pressure plate, and the square pressure plate is perpendicular to the rotary clamping cylinder; Operating Condition 6: The square pressure plate is horizontally connected to the rotating shaft of the rotary clamping cylinder, and the center of gravity of the square pressure plate coincides with the axis of the rotating shaft.

[0060] Specifically, the selection system performs refined matching for the second working condition of non-standard rod-shaped fixtures. When the user inputs a cylindrical cross-sectional feature for the non-standard pressure plate, the system defines the pressure plate model as a cylindrical rod and requires the user to further confirm its assembly topology with the rotating shaft. If the system identifies that one end face of the cylindrical rod is fixed to the normal plane of the cylinder's rotating shaft, the second working condition is determined to be that the rotating shaft of the rotary clamping cylinder is perpendicularly connected to the end of the cylindrical rod; if the system identifies that the rotating shaft is inserted at the center of mass of the cylindrical rod, it is determined to be that the rotating shaft is perpendicularly connected to the center of mass of the cylindrical rod; if the system identifies that one end of the cylindrical rod is connected to the rotating shaft and the other end is loaded with an external workpiece (load), it is determined to be that the rotating shaft is perpendicularly connected to one end of the cylindrical rod and the other end of the cylindrical rod is connected to a load. The system locks one of the above spatial connection relationships to determine whether to treat the entire cylindrical rod as a cantilever beam model or a balance lever model in subsequent calculations.

[0061] The selection system performs refined matching for the second working condition of non-standard plate-shaped fixtures. When the non-standard pressure plate input by the user has a wide surface feature, the system defines it as a square pressure plate and determines the working condition based on its spatial posture. For example, if the square pressure plate is in a vertical plane and its center of mass perpendicular line intersects the axis of the cylinder rotation, the system determines the second working condition as the square pressure plate vertically connected to the rotation axis of the rotary clamping cylinder, and the center of mass of the square pressure plate coincides with the axis of the rotation axis; if one edge of the square pressure plate is connected to the rotation axis and the plate surface forms a 90-degree angle with the cylinder body to form a suspended state, the system determines that the rotation axis of the rotary clamping cylinder is connected to the end of the square pressure plate, and the square pressure plate is perpendicular to the rotary clamping cylinder; if the square pressure plate is in a horizontal plane and its center of mass passes through the rotation axis, the system determines that the square pressure plate is horizontally connected to the rotation axis of the rotary clamping cylinder, and the center of mass of the square pressure plate coincides with the axis of the rotation axis. The system locks the corresponding second working condition based on these three different attitudes, thus providing a judgment benchmark for whether the parallel axis theorem needs to be introduced in the subsequent rotational inertia verification.

[0062] For example, the user inputs that the non-standard pressure plate is made of steel plate, with a length a=200mm, a width b=100mm, and a weight m1=2kg; a cylindrical clamping head with a diameter D=50mm and a weight m2=1kg is welded to the edge of the steel plate. The cylinder rotation shaft is connected to one edge along the length of the steel plate, and the entire clamp is vertically suspended in space.

[0063] During execution, firstly, the pressure plate with a length-to-width ratio of 2:1 was identified, indicating a wide profile, and it was classified as a square pressure plate. Then, the spatial attitude parameters were analyzed, showing that the pressure plate was in a vertical plane, the rotation axis did not pass through the center of gravity (offset at the end), and there was additional mass at the edges. This 3D structure was matched to a preset topology library, accurately determining that the second working condition was that the rotation axis of the rotary clamping cylinder was connected to the end of the square pressure plate, and the square pressure plate was perpendicular to the rotary clamping cylinder. Next, a feature label corresponding to this working condition was generated and passed to the mechanical calculation engine. In subsequent static verification, the engine, based on this label, automatically locked the lever arm of the gravitational bending moment to a / 2 (i.e., 100mm) and superimposed the eccentric moment of the cylindrical clamping head. In subsequent rotational inertia verification, based on this label, the engine abandoned the simple central axis formula and automatically decomposed it into: the inertia of the square plate itself I1=m1×(a 2 +b 2 ) / 12, plus the additional inertia m1×(a / 2) generated by the offset of the square plate. 2 In addition to the inertia of the cylindrical clamping head itself and the additional inertia generated by its offset, the total actual rotational inertia I is finally synthesized for comparison and verification.

[0064] The final output is based on the total torque and total inertia calculated above, combined with the verification rules, and outputs a selection report for one of the models that has passed static and dynamic verification, with a target cylinder diameter of 63mm.

[0065] It should be noted that when the rotating shaft of the rotary clamping cylinder is perpendicularly connected to the end of the cylindrical rod in the second working condition, the formula for calculating the moment of inertia is: When the second working condition is that the rotating shaft of the rotary clamping cylinder is vertically connected to one end of the cylindrical rod, and the other end of the cylindrical rod is connected to a load, the formula for calculating the moment of inertia is: When the second working condition is that the square pressure plate is vertically connected to the rotating shaft of the rotary clamping cylinder, and the center line of gravity of the square pressure plate coincides with the axis of the rotating shaft, the formula for calculating the moment of inertia is: When the second working condition involves the rotary clamping cylinder's rotating shaft connected to the end of the square pressure plate, and the square pressure plate is perpendicular to the rotary clamping cylinder, the formula for calculating the moment of inertia is: When the second working condition is that the square pressure plate is horizontally connected to the rotating shaft of the rotary clamping cylinder, and the center line of gravity of the square pressure plate coincides with the axis of the rotating shaft, the formula for calculating the moment of inertia is: .

[0066] In a further embodiment, when the first working condition is a general pressure plate, the steps are as follows: according to the verification rules corresponding to the first and second working conditions, the rotary clamping cylinder is statically verified using the selection parameters and the initial cylinder diameter value, specifically including the following steps: Based on the initial cylinder diameter value, a standard pressure plate length is configured for the rotary clamping cylinder by referring to a table; based on the operating pressure, the maximum clamping distance corresponding to the initial cylinder diameter value is determined by referring to a table; it is then determined whether the standard pressure plate length is less than the maximum clamping distance; if the standard pressure plate length is less than the maximum clamping distance, the static verification is considered to have passed.

[0067] Specifically, when the selection system determines that the first working condition is a general-purpose pressure plate in the preliminary steps, it triggers the static verification logic for this standard part. First, it extracts the currently calculated initial cylinder diameter value, such as 40mm, and performs an initial lookup operation in the preset standard part database. This automatically matches the manufacturer's default standard pressure plate for the 40mm cylinder diameter cylinder and reads the physical length of the standard pressure plate, which is recorded as the standard pressure plate length. Then, it extracts the operating pressure from the selection parameters, such as 0.5MPa, and performs a second lookup operation in conjunction with the initial cylinder diameter value of 40mm to obtain the limit cantilever distance that the cylinder spindle can withstand without plastic deformation under this specific air pressure, which is recorded as the maximum clamping distance. Subsequently, it executes the judgment logic to confirm that the standard pressure plate length, such as 150mm, is strictly less than the maximum clamping distance, such as 180mm. Based on this, it is determined that the standard configuration corresponding to the initial cylinder diameter value does not exceed the static bending safety threshold, and the static verification passes. The system then releases this model to enter the subsequent rotational inertia verification stage.

[0068] To demonstrate the protection mechanism of this feature in the iterative logic of the basic scheme, if the system finds during the above table lookup comparison that the configured standard pressure plate length, for example 150mm, is greater than the maximum clamping distance obtained from the table lookup at the current operating pressure, for example 120mm, then under the current low air pressure, the output torque of the 40mm cylinder diameter is insufficient to safely support the cantilever lever force generated when the 150mm long standard pressure plate is clamped. At this time, the system determines that the static verification has failed and immediately triggers the fault tolerance and reselection mechanism preset in the basic scheme: the system marks the 40mm cylinder diameter and the corresponding standard pressure plate combination as having excessive static bending torque and excludes it. Then, it automatically re-executes the configuration of the standard pressure plate length and subsequent comparison and judgment steps according to the preset cylinder diameter increment sequence, such as jumping to a 50mm cylinder diameter, until a qualified initial cylinder diameter value that meets the condition that the standard pressure plate length is less than the maximum clamping distance is found.

[0069] For example, firstly, the standard parts library is queried using 32mm as the index to configure the rotary clamping cylinder with the manufacturer's default 32mm cylinder diameter exclusive double-sided standard pressure plate, and its standard pressure plate length L2=150mm is read. Then, using the 32mm cylinder diameter and 0.4MPa operating pressure as combined conditions, the cylinder dynamic performance parameter table is queried to obtain the allowable safety cantilever limit of the 32mm cylinder spindle under 0.4MPa air pressure, that is, the maximum clamping distance L3=180mm. Next, the internal logic judgment module of the system compares the values ​​and confirms that 150mm<180mm is true. Finally, a status label indicating that the static verification has passed is generated, and the combination of the 32mm cylinder model and the 150mm standard pressure plate is released, automatically flowing into the rotational inertia verification stage based on the required cylinder speed.

[0070] In some specific embodiments, when the first working condition is a non-standard pressure plate, the selection parameters also include the weight of the non-standard pressure plate; the steps are to perform static verification of the rotary clamping cylinder using the selection parameters and the initial cylinder diameter value according to the verification rules corresponding to the first and second working conditions, specifically including the following steps: Calculate the clamping bending moment based on the required clamping force and clamping point distance; calculate the gravity bending moment of the non-standard pressure plate based on the weight of the non-standard pressure plate and clamping point distance; determine the total moment based on the clamping bending moment and the gravity bending moment of the non-standard pressure plate; obtain the allowable bending moment from the table based on the initial cylinder diameter value; determine whether the total moment is less than the allowable bending moment; if the total moment is less than the allowable bending moment, the static verification is deemed to have passed.

[0071] Specifically, the selection system determines in the preliminary steps that the first working condition is a non-standard pressure plate, such as when the rotating shaft is perpendicularly connected to the end of a thin rod, and then triggers the non-standard static verification logic. First, it obtains the extended selection parameters, namely the weight of the non-standard pressure plate. In the calculation phase, the system extracts the required clamping force F and clamping point distance L1 obtained from the basic scheme, and calculates the clamping bending moment M1 generated by the workpiece reaction force according to the torque physical equation M1=F×L1. Subsequently, the system uses the obtained non-standard pressure plate weight m combined with the center of gravity offset distance and clamping point distance L1 under this specific second working condition to calculate the gravitational bending moment M2 generated by the pressure plate's own weight. M1 and M2 are vector-superimposed to determine the total moment M, M=M1+M2. In the comparison phase, the initial cylinder diameter value obtained from the preliminary calculation is used to look up the allowable bending moment Mr of the cylinder spindle for this model in a preset hardware performance database. During the execution of the judgment logic, it is confirmed that the calculated total torque M is strictly less than the allowable bending torque Mr obtained from the table. Based on this, it is determined that the cylinder spindle with the initial cylinder diameter value has sufficient safety margin in the static clamping state. The static verification is deemed to have passed, and it is released to the subsequent rotational inertia verification stage.

[0072] It should be noted that, assuming the system finds during the non-standard pressure plate verification that the total torque M after superposition is greater than or equal to the allowable bending torque Mr obtained from the table based on the current initial cylinder diameter value, then, under the current non-standard pressure plate weight and cantilever geometry parameters, the section modulus of the cylinder spindle corresponding to this initial cylinder diameter is insufficient. Forcing its use would lead to irreversible bending deformation or even breakage of the spindle. Based on this, the system determines that the static verification has failed and immediately triggers the reselection mechanism in the basic scheme. That is, the initial cylinder diameter value and the corresponding cylinder model are marked as exceeding the static bending moment limit and discarded. Subsequently, the system automatically re-determines the initial cylinder diameter value according to the cylinder diameter increment sequence, for example, jumping from 32mm to 40mm. For larger cylinder diameters, the system re-executes the calculation of M1 and M2 and the comparison with the new allowable bending torque Mr, until an iterative search finds a qualified model that satisfies the condition that the total torque M is less than the allowable bending torque Mr.

[0073] For example, first, calculate the clamping bending moment M1 = 500N × 0.1m = 50N·m. Then, based on the second working condition of the thin rod end connection, calculate the bending moment generated by gravity. The gravity lever arm is the distance from the center of gravity to the rotation axis (0.1m). The gravity bending moment M2 = 2kg × 9.8m / s² × 0.1m = 1.96N·m. Determine the total moment M = M1 + M2 = 50 + 1.96 = 51.96N·m. Based on the initial cylinder diameter of 32mm, look up the table to obtain the corresponding allowable bending moment Mr = 29.08N·m. Finally, it is determined that the total moment of 51.96N·m is not less than the allowable bending moment of 29.08N·m, therefore the static verification is deemed to have failed. The system automatically increases the initial cylinder diameter to 40mm and looks up the table again to obtain the new allowable bending moment Mr = 29.08N·m. It should be noted that 32 / 40 belongs to the same range. If it still fails, the diameter will be increased to 50mm. The table is consulted to obtain Mr = 102.49 N·m. At this point, it is determined that 51.96 N·m < 102.49 N·m, and the static verification is deemed to have passed. The system will then use 50mm as the valid initial cylinder diameter value to proceed to the next process.

[0074] In some specific embodiments, when the static verification passes, the step is to verify the rotational inertia of the rotary clamping cylinder based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value, specifically including: The maximum moment of inertia is obtained by looking up a table based on the required cylinder speed.

[0075] Specifically, this step is executed when the preceding static verification result is passed. The system extracts the required cylinder speed V from the selection parameters and, in conjunction with the currently determined cylinder type, searches the pre-built cylinder dynamic performance database. Since the rotary clamping cylinder converts linear motion into rotational motion through the internal helical groove and pin engagement, the maximum driving torque provided by this helical transmission mechanism has a fixed physical upper limit. Under the limitation of the maximum driving torque, the maximum allowable moment of inertia of the system is inversely proportional to the angular acceleration of the rotational motion; that is, the faster the required cylinder speed, the smaller the maximum allowable moment of inertia threshold. Thus, by using a two-dimensional lookup table of speed-cylinder diameter / model, the maximum moment of inertia I1 corresponding to the current operating rhythm can be quickly obtained as a benchmark threshold for subsequent dynamic safety assessment.

[0076] The actual moment of inertia of the rotary clamping cylinder is calculated based on the pressure plate parameters configured according to the initial cylinder diameter value.

[0077] Specifically, the physical parameters of the pressure plate associated with the initial cylinder bore value, such as mass, overall dimension and the like, are extracted, and a rigid body dynamics model matching the current working condition is called for calculation. In some embodiments, if the first working condition corresponds to a universal pressure plate, the system directly calls the pre-stored rotation inertia constant of the pressure plate in the standard part database, or directly obtains the actual rotation inertia by using a simple uniform rod / plate formula. In other embodiments, if the first working condition corresponds to a user-defined non-standard pressure plate, the system needs to perform micro-element decomposition calculation according to the spatial topology of the second working condition. For example, for a thin rod-shaped pressure plate, the system adopts an integration formula for a thin rod rotating around its end or center of gravity; for a square plate with an eccentric load, the system decomposes it into a main rectangular plate and edge cylinders, calculates the inertia of each part around its own center of mass, then superimposes the additional inertia caused by the eccentric distance by using the parallel axis theorem, and finally synthesizes to obtain the total actual rotation inertia I2.

[0078] Determine whether the actual rotation inertia is less than the maximum rotation inertia.

[0079] Specifically, the calculated actual rotation inertia I2 is numerically and logically compared with the maximum rotation inertia I1 obtained through table look-up in the previous step. This step is to verify whether the driving torque of the cylinder output shaft can overcome the maximum inertia resistance torque generated by the pressure plate under the currently required cylinder speed. The system sets the safety judgment condition as I2<I1 to ensure that a reasonable dynamic safety margin is reserved in practical application and avoid fatigue damage during long-term operation.

[0080] If the actual rotation inertia is less than the maximum rotation inertia, it is determined that the rotation inertia check passes.

[0081] Specifically, when it is confirmed that the above condition I2<I1 is satisfied, a judgment result that the check passes is output. This result and the result that the static check passes together constitute the necessary and sufficient condition for the initial cylinder bore value to be confirmed as the target cylinder bore value, and then the system will proceed to the model output step; conversely, if the judgment result is negative, the system determines that the dynamic check fails, triggers an iteration mechanism, eliminates the model corresponding to the initial cylinder bore value, and automatically increases the cylinder bore by one level to re-execute the calculation and check process.

[0082] By way of example, it is determined that the first working condition is a user-defined non-standard pressure plate, the second working condition is that the square plate is vertically connected to the rotating shaft, the center of gravity line coincides with the axis of the rotating shaft, and each end edge of the square plate is provided with a cylindrical clamping load. The obtained model selection parameters comprise that the required cylinder speed V is 0.3s (representing fast rotation), the mass m1 of the square plate is 2kg, the length a is 200mm, and the width b is 100mm; the mass m2 of each cylindrical load at two ends is 1kg, and the diameter D is 50mm. The system has obtained an initial cylinder bore value of 40mm based on the clamping force in the previous process, and the static check has been passed.

[0083] Based on an initial cylinder diameter of 40mm and a required cylinder speed of 0.3s, the maximum moment of inertia I1 of this cylinder model at high speed is calculated to be 1200×10−4kg·m. 2 Then, the actual moment of inertia I2 is calculated, and the system decouples the model into three parts according to the second working condition.

[0084] The moment of inertia of the central square plate about its central axis is I. 板 =m1×(a 2 +b 2 ) / 12=2×(0.2 2 +0.1 2 ) / 12≈83.3×10 −4 kg·m. The moment of inertia of a single-sided cylindrical load (applying the parallel axis theorem) is I. 柱 =m2×D 2 / 8+m2×(a / 2) 2 =1×(0.05 2 / 8)+1×(0.1) 2 ≈103.1×10−4kg·m 2 Due to bilateral symmetry, the total actual moment of inertia is I² = I² / 2. 板 +2×I 柱 =83.3 + 2 × 103.1 = 289.5 × 10 −4 kg·m 2 .

[0085] Judgment 289.5×10 −4 Is it less than 1200×10? −4 The result was yes. Finally, the system determined that the moment of inertia verification was passed, allowing the initial cylinder diameter value of 40mm to be used as the target cylinder diameter value, and outputting the corresponding cylinder model.

[0086] In some specific embodiments, the selection method further includes the following steps: If the static verification or the moment of inertia verification fails, the rotary clamping cylinder model corresponding to the initial cylinder diameter value will be marked and excluded, and the process will return to the previous step of determining the initial cylinder diameter value of the rotary clamping cylinder based on the required clamping force and the distance between the clamping points.

[0087] Specifically, the system continuously monitors and receives returned results. If any static verification fails—for example, if the calculated total torque exceeds the allowable bending torque or the actual moment of inertia exceeds the maximum moment of inertia—this exception handling process is immediately triggered, acting as a branch router to intercept candidate objects that do not meet the safety threshold from the normal output channel. In some embodiments, when the execution condition is triggered, the system immediately retrieves the rotary clamping cylinder model associated with the currently failed initial cylinder diameter value. In the background candidate model pool or database, a failure status bit is written for that specific model, for example, setting the Available field to False or appending its identification code to the exclusion list array in memory. This operation ensures that in subsequent iterations, the system will not repeatedly retrieve the same model that has been proven to have insufficient mechanical performance, avoiding an infinite loop and achieving strict data isolation. After completing data isolation, the system clears the temporary intermediate variables generated in the current cycle, such as the total torque value and actual moment of inertia value calculated in the previous cycle, and redirects the program's execution pointer back to the step of determining the initial cylinder diameter value of the rotary clamping cylinder based on the required clamping force and the distance between the clamping points. This achieves a seamless logical connection and prepares for the introduction of a new calculation benchmark.

[0088] It should be noted that the above-mentioned re-execution steps are not a simple repetition in place without any changes. Instead, the parameters are incremented according to the preset optimization strategy. That is, when recalculating the initial cylinder diameter value, the initial cylinder diameter value that was excluded in the previous round is read, and the preset standardized cylinder diameter series, such as 20mm, 25mm, 32mm, 40mm, 50mm, 63mm, 80mm, etc., is automatically locked and jumped to the next larger cylinder diameter position. Based on the new cylinder diameter value after the jump, the pressure plate parameters are reconfigured and the static and dynamic dual verification links are entered again to form a complete iterative closed loop. 20 / 25 7.9 32 / 40 29.08 50 / 63 102.49 Based on the initial cylinder diameter value mentioned above, for example, the initial cylinder diameter value calculated based on F and L1 is 32mm. Upon entering static verification, the total torque M = 150.5 N·m is calculated. Based on 32mm, the allowable bending torque Mr = 29.08 N·m is obtained from the table. It is determined that M (150.5) > Mr (29.08), and the static verification fails. Therefore, model A corresponding to 32mm is marked as excluded, and a return is triggered. In the national standard series, the next grade after 32mm is identified as 40mm. 40mm is used as the new initial cylinder diameter value, and the allowable bending torque Mr corresponding to 40mm is again obtained from the table, which is still 29.08 N·m (note that 32 and 40 belong to the same bending resistance grade, so M (150.5) > Mr (29.08)). The static verification fails again, so model B corresponding to 40mm is marked as excluded, and a return is triggered again.

[0089] Continue jumping to 50mm as the initial cylinder bore diameter value, recheck the table to obtain the allowable bending moment corresponding to 50mm Mr=102.49 N·m. At this time, it is determined that M (150.5) is still greater than Mr (102.49), the static check fails, so model C with 50mm bore diameter is excluded, and a return is triggered.

[0090] The system jumps to 63mm as the initial cylinder bore diameter value, checks the table to obtain the allowable bending moment corresponding to 63mm Mr=102.49N·m, determines that M (150.5)>Mr (102.49), the check still fails, so model D with 63mm bore diameter is excluded, and a return is triggered.

[0091] The system jumps to 80mm as the initial cylinder bore diameter value, checks the table to obtain the allowable bending moment corresponding to 80mm Mr=250 N·m. At this time, it is determined that M (150.5)<Mr (250), the static check passes, then the moment of inertia check is continued by using the corresponding pressure plate parameters of 80mm. Assuming that the check also passes, the target rotary clamping cylinder model corresponding to 80mm bore diameter is finally output.

[0092] It can be seen that by converting the above tedious manual trial-and-error process into millisecond-level automatic algorithm traversal, the system in the embodiment continuously spans 5 cylinder bore gears, and automatically completes the whole process of calculation-failure-reselection-re-calculation that originally takes half an hour within one second, which can eliminate the potential safety hazard left by manual gear skipping and missed calculation to a certain extent.

[0093] The embodiment of the present invention further provides a model selection apparatus 100 for a rotary clamping cylinder, and the model selection apparatus 100 is configured to perform any of the foregoing embodiments of the model selection method for a rotary clamping cylinder.

[0094] Specifically, the specific structure of a model selection apparatus 100 for a rotary clamping cylinder provided by the embodiment of the present invention is elaborated in detail below. According to the attached Figure 9 as shown in , the specific structure of the model selection apparatus 100 includes the following: a first determining module 110, configured to determine the type of the rotary clamping cylinder to be selected and a first working condition of the rotary clamping cylinder, wherein the first working condition is a general pressure plate or a user's non-standard pressure plate; a second determining module 120, configured to determine a second working condition of the rotary clamping cylinder according to the first working condition; an obtaining module 130, configured to obtain model selection parameters of the rotary clamping cylinder, wherein the model selection parameters at least include working pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance and rotation direction; a third determining module 140, configured to determine an initial cylinder bore diameter value of the rotary clamping cylinder based on the required clamping force and the clamping point distance; The static verification module 150 is used to perform static verification on the rotary clamping cylinder according to the verification rules corresponding to the first working condition and the second working condition, using the selection parameters and the initial cylinder diameter value. The rotational inertia verification module 160 is used to verify the rotational inertia of the rotary clamping cylinder based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value when the static verification is passed. The output module 170 is used to determine the initial cylinder diameter value as the target cylinder diameter value when the rotational inertia verification is passed, and to output the model of the rotary clamping cylinder corresponding to the target cylinder diameter value.

[0095] The present invention further provides a computer device, which can be used to execute the selection method of the rotary clamping cylinder in any of the above embodiments.

[0096] See Figure 10 The computer device 500 includes a processor 502, a memory, and a network interface 505 connected via a communication bus 501. The memory may include a storage medium 503 and internal memory 504.

[0097] The storage medium 503 may store an operating system 5031 and a computer program 5032. When the computer program 5032 is executed, it causes the processor 502 to execute a selection method for a rotary clamping cylinder. The storage medium 503 may be a volatile storage medium or a non-volatile storage medium.

[0098] The processor 502 provides computing and control capabilities to support the operation of the entire computer device 500.

[0099] The internal memory 504 provides an environment for the operation of the computer program 5032 in the storage medium 503. When the computer program 5032 is executed by the processor 502, the processor 502 can execute the selection method of the rotary clamping cylinder.

[0100] This network interface 505 is used for network communication, such as providing data transmission. Those skilled in the art will understand that... Figure 10 The structure shown is merely a block diagram of a portion of the structure related to the present invention and does not constitute a limitation on the computer device 500 to which the present invention is applied. The specific computer device 500 may include more or fewer components than shown in the figure, or combine certain components, or have different component arrangements.

[0101] The processor 502 is used to run the computer program 5032 stored in the memory to implement the corresponding function in the above-mentioned selection method of the rotary clamping cylinder.

[0102] Those skilled in the art will understand that Figure 10 The embodiments of the computer device shown do not constitute a limitation on the specific configuration of the computer device. In other embodiments, the computer device may include more than Figure 10 More or fewer components, or combinations of certain components, or different arrangements of components. For example, in some embodiments, a computer device may include only memory and a processor; in such embodiments, the structure and function of the memory and processor are different from those of other components. Figure 10 The embodiments shown are consistent and will not be described again here.

[0103] It should be understood that, in this embodiment of the invention, the processor 502 may be a Central Processing Unit (CPU), or it may be other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), field-programmable gate arrays (FPGAs), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. The general-purpose processor may be a microprocessor or any conventional processor.

[0104] In another embodiment of the invention, a computer-readable storage medium is provided. This computer-readable storage medium may be volatile or non-volatile. The computer-readable storage medium stores a computer program, which, when executed by a processor, implements the steps included in the above-described method for selecting a rotary clamping cylinder.

[0105] Those skilled in the art will readily understand that, for the sake of convenience and brevity, the specific working processes of the devices, apparatuses, and units described above can be referred to the corresponding processes in the foregoing method embodiments, and will not be repeated here. Those skilled in the art will recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, computer software, or a combination of both. To clearly illustrate the interchangeability of hardware and software, the composition and steps of each example have been generally described in terms of function in the foregoing description. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this invention.

[0106] In the embodiments provided by this invention, it should be understood that the disclosed devices, apparatuses, and methods can be implemented in other ways. For example, the apparatus embodiments described above are merely illustrative. For instance, the division of units is only a logical functional division, and in actual implementation, there may be other division methods. Units with the same function may be grouped into one unit. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. In addition, the coupling or direct coupling or communication connection shown or discussed may be an indirect coupling or communication connection through some interfaces, devices, or units, or it may be an electrical, mechanical, or other form of connection.

[0107] The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of the embodiments of the present invention, depending on actual needs.

[0108] In addition, the functional units in the various embodiments of the present invention can be integrated into one processing unit, or each unit can exist physically separately, or two or more units can be integrated into one unit.

[0109] The integrated units described above can be implemented in either hardware or software functional units.

[0110] If the integrated unit is implemented as a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art, or all or part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a computer-readable storage medium and includes several instructions to cause a computer device (which may be a personal computer, a data transmitter, or a network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present invention. The aforementioned computer-readable storage medium includes various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), magnetic disks, or optical disks.

[0111] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A method for selecting a rotary clamping cylinder, characterized in that, The selection method includes: Determine the type of rotary clamping cylinder to be selected and the first working condition of the rotary clamping cylinder, wherein the first working condition is a general-purpose pressure plate or a non-standard pressure plate; Based on the first working condition, determine the second working condition of the rotary clamping cylinder; Obtain the selection parameters of the rotary clamping cylinder, which include at least the operating pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance, and rotation direction; Based on the required clamping force and clamping point distance, determine the initial cylinder diameter value of the rotary clamping cylinder; According to the verification rules corresponding to the first and second working conditions, the rotary clamping cylinder is statically verified using the selection parameters and the initial cylinder diameter value. When the static verification is passed, the rotational inertia of the rotary clamping cylinder is verified based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value. When the rotational inertia verification is passed, the initial cylinder diameter value is determined as the target cylinder diameter value, and the model of the rotary clamping cylinder corresponding to the target cylinder diameter value is output.

2. The selection method for the rotary clamping cylinder according to claim 1, characterized in that, Determining the second operating condition of the rotary clamping cylinder based on the first operating condition includes: If the first working condition is a general-purpose pressure plate, the second working condition includes a double-arm pressure plate or a single-arm pressure plate; If the first working condition is a non-standard pressure plate, the second working condition is the connection position between the non-standard pressure plate and the rotating shaft of the rotary clamping cylinder.

3. The selection method for the rotary clamping cylinder according to claim 2, characterized in that, If the first working condition is a non-standard pressure plate, and the second working condition is the connection position between the non-standard pressure plate and the rotating shaft of the rotary clamping cylinder, it includes: The first working condition is a cylindrical rod or a square pressure plate, and the second working condition is any one of the following six working conditions: Operating Condition 1: The rotating shaft of the rotary clamping cylinder is vertically connected to the end of the cylindrical rod; Operating Condition 2: The rotating shaft of the rotary clamping cylinder is vertically connected to the center of gravity of the cylindrical rod; Condition 3: The rotating shaft of the rotary clamping cylinder is vertically connected to one end of the cylindrical rod, and the other end of the cylindrical rod is connected to a load. Condition 4: The square pressure plate is vertically connected to the rotating shaft of the rotary clamping cylinder, and the center line of gravity of the square pressure plate coincides with the axis of the rotating shaft. Condition 5: The rotating shaft of the rotary clamping cylinder is connected to the end of the square pressure plate, and the square pressure plate is perpendicular to the rotary clamping cylinder. Condition 6: The square pressure plate is horizontally connected to the rotating shaft of the rotary clamping cylinder, and the center line of gravity of the square pressure plate coincides with the axis of the rotating shaft.

4. The selection method for the rotary clamping cylinder according to claim 2, characterized in that, When the first working condition is a general-purpose pressure plate, the step of performing static verification of the rotary clamping cylinder using the selection parameters and initial cylinder diameter value according to the verification rules corresponding to the first and second working conditions includes: Based on the table lookup of the initial cylinder diameter value, a standard pressure plate length is configured for the rotary clamping cylinder; Based on the table lookup of the operating pressure, the maximum clamping distance corresponding to the initial cylinder diameter value is determined; Determine whether the length of the standard pressure plate is less than the maximum clamping distance; If the length of the standard pressure plate is less than the maximum clamping distance, the static verification is deemed to have passed.

5. The selection method for the rotary clamping cylinder according to claim 2, characterized in that, When the first working condition is a non-standard pressure plate, the selection parameters also include the weight of the non-standard pressure plate. The step of performing static verification of the rotary clamping cylinder using the selection parameters and the initial cylinder diameter value, based on the verification rules corresponding to the first and second working conditions, includes: Calculate the clamping bending moment based on the required clamping force and the distance between clamping points; The gravitational bending moment of the non-standard pressure plate is calculated based on its weight and the distance between clamping points. The total torque is determined based on the clamping bending torque and the gravity bending torque of the non-standard pressure plate; The allowable bending moment is obtained by looking up a table based on the initial cylinder diameter value; Determine whether the total torque is less than the allowable bending torque; If the total torque is less than the allowable bending torque, the static verification is deemed to have passed.

6. The selection method for the rotary clamping cylinder according to claim 1, characterized in that, The step of verifying the rotational inertia of the rotary clamping cylinder based on the pressure plate parameters corresponding to the required cylinder speed and initial cylinder diameter includes: The maximum moment of inertia is obtained by looking up a table based on the required cylinder speed. The actual moment of inertia of the rotary clamping cylinder is calculated based on the pressure plate parameters configured according to the initial cylinder diameter value. Determine whether the actual moment of inertia is less than the maximum moment of inertia; If the actual moment of inertia is less than the maximum moment of inertia, then the moment of inertia verification is deemed to have passed.

7. The method for selecting a rotary clamping cylinder according to claim 1, characterized in that, The selection method also includes: If the static verification fails or the rotational inertia verification fails, the rotary clamping cylinder model corresponding to the initial cylinder diameter value is marked and excluded, and the process is repeated to determine the initial cylinder diameter value of the rotary clamping cylinder based on the required clamping force and clamping point distance.

8. A selection device for a rotary clamping cylinder, characterized in that, The device employs the selection method for the rotary clamping cylinder as described in any one of claims 1-7, wherein the selection device comprises: The first determining module is used to determine the type of rotary clamping cylinder to be selected and the first working condition of the rotary clamping cylinder, wherein the first working condition is a general pressure plate or a user-designed non-standard pressure plate. The second determining module is used to determine the second working condition of the rotary clamping cylinder based on the first working condition; The acquisition module is used to acquire the selection parameters of the rotary clamping cylinder. The selection parameters include at least the operating pressure, required clamping force, clamping stroke, required cylinder speed, clamping point distance, and rotation direction. The third determining module is used to determine the initial cylinder diameter value of the rotary clamping cylinder based on the required clamping force and the distance between the clamping points; The static verification module is used to perform static verification on the rotary clamping cylinder according to the verification rules corresponding to the first working condition and the second working condition, using the selection parameters and the initial cylinder diameter value. The rotational inertia verification module is used to verify the rotational inertia of the rotary clamping cylinder based on the pressure plate parameters corresponding to the required cylinder speed and the initial cylinder diameter value when the static verification passes. The output module is used to determine the initial cylinder diameter value as the target cylinder diameter value when the rotational inertia verification is passed, and to output the model of the rotary clamping cylinder corresponding to the target cylinder diameter value.

9. A computer device, characterized in that, The computer device includes a processor, a network interface, a memory, and a communication bus, wherein the processor, network interface, and memory communicate with each other through the communication bus; Memory, used to store computer programs; When the processor executes the program stored in the memory, it implements the steps of the selection method for the rotary clamping cylinder according to any one of claims 1-7.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by the processor, it implements the steps of the method for selecting a rotary clamping cylinder as described in any one of claims 1-7.

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