Ear parameter design method based on double friction loss and ear transmission structure

Abstract

This invention relates to the field of watch accessory technology, specifically a spring bar parameter design method and spring bar transmission structure based on dual friction loss. By constructing a precise force transmission model considering dual friction loss, it incorporates inclined plane friction analysis and guide rail friction analysis into a unified mechanical analysis framework, improving the accuracy of parameter calculation for push-button quick-release spring bars. It proposes the concept of a force transmission efficiency factor, using a first efficiency factor and a second efficiency factor to quantify the force transmission efficiency loss in the push-button spring bar transmission link, facilitating engineering calculations and parameter optimization. Furthermore, it establishes a spring adaptation model and a stroke matching model, further forming a complete push-button spring bar parameter design system. This achieves coordinated optimization of key parameters such as push-button force, pin ejection force, stroke, and spring elastic coefficient, enabling precise matching of push-button force and pin ejection force during production design, ensuring the consistency and reliability of the operating feel of push-button quick-release spring bar products.

Description

Technical Field

[0001] This invention relates to the technical field of watch accessories, and in particular to a method for designing spring bar parameters based on dual frictional losses and a spring bar transmission structure. Background Technology

[0002] Spring bars are crucial components connecting the watch strap to the case, and their performance directly affects the efficiency of strap assembly and reliability. Traditional spring bars are typically installed and removed using tools, requiring specialized tools to compress the spring pins to complete the process, which is cumbersome and can easily damage the watch case surface.

[0003] As consumers increasingly demand personalization and convenience in their watches, push-button quick-release spring bars are gradually becoming a mainstream trend in high-end watch accessories. These spring bars integrate a push-button mechanism, allowing users to quickly release the strap simply by pressing a button, without the need for any tools.

[0004] However, existing button-type spring clips have the following technical problems in the design process: (1) Lack of scientific mechanical analysis methods: Existing button-type spring clip designs mostly rely on empirical values ​​and fail to establish an accurate mathematical model between button force and pin ejection force, resulting in inconsistent operation feel of spring clip products; (2) Incomplete consideration of friction loss: There are two levels of loss in the transmission link: inclined plane friction and guide rail friction. Existing methods often only consider single-level friction or completely ignore the influence of friction, resulting in design deviation; (3) Lack of theoretical guidance for parameter matching: There is a lack of systematic matching relationship between key parameters such as spring selection and stroke design, making it difficult to achieve optimal design; Therefore, there is an urgent need for a parameter design method for button-type quick-release spring clips that considers dual friction loss, so as to solve the problems of imperfect button-type spring clip design and inaccurate multi-parameter matching in the existing technology.

[0005] This invention was proposed in response to the shortcomings of existing technologies. Summary of the Invention

[0006] This invention aims to provide a spring ear parameter design method and spring ear transmission structure based on dual friction loss. By establishing a force transmission model that considers dual friction loss, it achieves precise matching between button force and pin ejection force, thereby improving the accuracy and consistency of product design.

[0007] The technical solution adopted by this invention to solve its technical problem is: This invention provides a method for designing spring ear parameters based on dual frictional losses, comprising the following steps: S1. Determine the design input parameters for the push-button quick-release spring bar transmission structure. The design input parameters include the target value of the pin push-out force F. p Pin travel L p The slope angle θ and the system friction coefficient K; S2. Determine the target value F of the pin push-out force. p A matching force transmission efficiency factor, the force transmission efficiency factor including a first efficiency factor α1 and a second efficiency factor α2, wherein the first efficiency factor α1 = sinθ - K·cosθ, and the second efficiency factor α2 = cosθ - K·sinθ; a comprehensive transmission efficiency value η is generated based on the first efficiency factor α1 and the second efficiency factor α2, the comprehensive transmission efficiency value η = α1 × α2. S3. Determine the force transmission model that matches the force transmission efficiency factor, and determine the target value F of the pin ejection force based on the force transmission model. p The design of the corresponding button force F; the force transmission model is: F=2F p / η; S4. Determine the pin travel L. p A stroke matching model adapted to the slope angle θ is used to determine the stroke L of the pin. p The corresponding key travel distance L; the travel distance matching model is: L=L p ·tanθ; S5. Determine the target value F of the pin push-out force. p A matching spring model is used, and the target value F of the pin push-out force is determined based on the spring model. p The appropriate spring constant K s The spring fitting model is: K s =F p / (L p +δ), where δ is the spring pre-compression; S6. Verify the effectiveness of the design range of the designed button force F, and determine whether the design range of the designed button force F meets the preset operating force range. If it does not meet the requirements, adjust the slope angle θ and / or the system friction coefficient K, and repeat steps S2 to S5.

[0008] As described above, in the spring ear parameter design method based on dual friction loss, in step S2, the force transmission efficiency factor is calculated according to the friction loss model, which includes inclined plane friction loss and guide rail friction loss during pin movement. When the designed button force F is applied to an inclined plane with the slope angle θ, the designed button force F decomposes into a net thrust P = F·α1 along the inclined plane, and the net thrust P decomposes into a pin retraction thrust P·α2, so that the total push-out force of the pin in the button-type quick-release spring ear is: 2F p =F·α1·α2.

[0009] In the spring ear parameter design method based on dual friction loss as described above, the system friction coefficient K ranges from 0.1 to 0.3, and the reference value of the system friction coefficient K is set to 0.19.

[0010] As described above, in the spring ear parameter design method based on dual frictional losses, the target value of the pin push-out force F p The value range is 0.5N to 3.0N, and the pin stroke L p The value range is 0.5mm to 1.5mm.

[0011] In the spring ear parameter design method based on dual friction loss as described above, the spring pre-compression δ is 0.5mm to 1.2mm.

[0012] In the spring ear parameter design method based on dual frictional loss as described above, the preset operating force range in step S6 is 5N to 12N.

[0013] The spring ear parameter design method based on dual frictional loss, as described above, further includes: S7. Collect multiple sets of button force F and corresponding pin push force F. p Actual measured data; S8. Based on the force transmission model, determine the friction verification model corresponding to the friction coefficient K of the system. The friction verification model is: F·sinθcosθ·K²-F·K+(F·sinθcosθ-2F p )=0; S9. Calculate multiple sets of experimental values ​​of the system friction coefficient K based on the friction verification model, and obtain the average value of the multiple sets of experimental values ​​of the system friction coefficient K. Compare and verify the average value with the benchmark value of the system friction coefficient K.

[0014] The present invention also provides a spring ear transmission structure, which is designed using the parameter design method described above. The transmission structure is disposed in the outer shell of a button-type quick-release spring ear. The transmission structure includes a button, at least one pin, and a transmission surface disposed between the pin and the button. The transmission surface has a ramp angle θ with the horizontal plane. The button slides with the pin through the transmission surface, so that the pin can extend and retract inside and outside the outer shell. The pin is also connected to an elastic element for extending the pin to the outside of the outer shell.

[0015] In the spring-ear drive structure described above, at least one of the relative sliding surfaces of the button and the pin is subjected to a surface treatment that reduces the coefficient of friction.

[0016] Compared with the prior art, the beneficial effects of the present invention are: 1. By constructing an accurate force transmission model that considers the dual frictional losses generated during the push-button spring bar transmission process, the inclined plane friction analysis and guide rail friction analysis are systematically incorporated into a unified mechanical analysis framework, which improves the accuracy of the calculation of push-button quick-release spring bar design parameters. 2. This invention proposes the concept of force transmission efficiency factor, which quantifies the force transmission efficiency loss of the button-type spring ear drive link through the first efficiency factor and the second efficiency factor, facilitating engineering calculations and parameter optimization; 3. This invention also establishes a spring adaptation model and a stroke matching model, further forming a complete parameter design system for button-type spring bars. It realizes the coordinated optimization of key parameters such as button force, pin ejection force, stroke, and spring elastic coefficient. In the production and design process, it can achieve precise matching between button force and pin ejection force, ensuring the consistency and reliability of the operation feel of button-type quick-release spring bar products, and improving the scientificity and efficiency of button-type quick-release spring bar product design. 4. Based on a suitable fixed value for the spring elastic coefficient and the fixed value for the inclined plane angle, this invention can optimize the operating feel and connection reliability of the spring ear by adjusting the system friction coefficient in the spring ear transmission structure, thereby enhancing the long-term reliability of the spring ear and facilitating quantitative and systematic fine adjustments by the manufacturer on a fixed spring ear structure.

[0017] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. Attached Figure Description

[0018] Figure 1 The flowchart of the button-type quick-release spring bar parameter design method of the present invention Figure 1 ; Figure 2 The flowchart of the button-type quick-release spring bar parameter design method of the present invention Figure 2 ; Figure 3 This is a perspective view of the push-button quick-release spring bar of the present invention; Figure 4 for Figure 3 Section A-A Figure 1 ; Figure 5 for Figure 3 Section A-A Figure 2 ; Figure 6 for Figure 3 Section A-A Figure 3 .

[0019] In the diagram: 11-Outer shell; 12-Pin; 13-Button; 10-Transmission surface; 15-Elastic element; θ-Slope angle; L-Button travel; L p - Pin travel. Detailed Implementation

[0020] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The described embodiments are merely some, not all, of the embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0021] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0022] Furthermore, the use of terms such as "first" and "second" in this invention is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. Additionally, the technical solutions of the various embodiments can be combined with each other, but only on the basis of being achievable by those skilled in the art. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this invention.

[0023] Example 1: like Figures 1 to 6 As shown, this invention provides a spring ear parameter design method based on dual frictional losses, comprising the following steps: S1. Determine the design input parameters for the push-button quick-release spring bar transmission structure. The design input parameters include the target value of the pin push-out force F. p Pin travel L p The slope angle θ and the system friction coefficient K; S2. Determine the target value F of the pin push-out force. p A matching force transmission efficiency factor, the force transmission efficiency factor including a first efficiency factor α1 and a second efficiency factor α2, wherein the first efficiency factor α1 = sinθ - K·cosθ, and the second efficiency factor α2 = cosθ - K·sinθ; a comprehensive transmission efficiency value η is generated based on the first efficiency factor α1 and the second efficiency factor α2, the comprehensive transmission efficiency value η = α1 × α2. S3. Determine the force transmission model that matches the force transmission efficiency factor, and determine the target value F of the pin ejection force based on the force transmission model. p The design of the corresponding button force F; the force transmission model is: F=2F p / η; S4. Determine the pin travel L. p A stroke matching model adapted to the slope angle θ is used to determine the stroke L of the pin. p The corresponding key travel distance L; the travel distance matching model is: L=L p ·tanθ; S5. Determine the target value F of the pin push-out force. p A matching spring model is used, and the target value F of the pin push-out force is determined based on the spring model. p The appropriate spring constant K s The spring fitting model is: K s =F p / (L p +δ), where δ is the spring pre-compression; S6. Verify the effectiveness of the design range of the designed button force F, and determine whether the design range of the designed button force F meets the preset operating force range. If it does not meet the requirements, adjust the slope angle θ and / or the system friction coefficient K, and repeat steps S2 to S5.

[0024] This invention constructs a precise force transmission model that considers the dual frictional losses generated during the push-button spring ear drive process. It systematically incorporates inclined plane friction analysis and guide rail friction analysis into a unified mechanical analysis framework, improving the accuracy of design parameter calculations for push-button quick-release spring ears. This invention proposes the concept of a force transmission efficiency factor, using a first efficiency factor α1 and a second efficiency factor α2 to quantitatively characterize the force transmission efficiency loss in the push-button spring ear drive chain, facilitating engineering calculations and parameter optimization. Furthermore, this invention establishes a spring adaptation model and a stroke matching model, further forming a complete parameter design system for push-button spring ears, realizing the calculation of push-button force, The coordinated optimization of key parameters such as pin ejection force, stroke, and spring elasticity coefficient enables precise matching between button force and pin ejection force during the production and design process. This ensures the consistency and reliability of the operating feel of button-type quick-release spring clip products, improving the scientific nature and efficiency of button-type quick-release spring clip product design. In addition, based on appropriate fixed values ​​for spring elasticity coefficient and inclined plane angle, this invention can optimize the operating feel and connection reliability of spring clips by adjusting the system friction coefficient in the spring clip transmission structure, enhancing the long-term reliability of spring clips and facilitating quantitative and systematic fine adjustments by manufacturers on fixed spring clip structures.

[0025] Furthermore, in step S2, the force transmission efficiency factor is calculated based on the friction loss model, which includes inclined plane friction loss and guide rail friction loss during pin movement. When the designed button force F acts on the inclined plane with the slope angle θ, the designed button force F decomposes to generate a net thrust P=F·α1 along the inclined plane, and the net thrust P decomposes to generate a pin retraction thrust P·α2, so that the total pin ejection force in the button-type quick-release spring ear is: 2F p =F·α1·α2.

[0026] Specifically, the design of the button F is decomposed into a tangential component F·sinθ and a normal component F·cosθ via an inclined plane. The normal component F·cosθ generates an inclined plane friction force f1 = K·F·cosθ, which in turn generates a net thrust along the inclined plane capable of overcoming this friction force, providing the driving force for the pin movement. This net thrust P = F·α1, i.e., P = F·(sinθ - K·cosθ) (Equation 1). Furthermore, the net thrust P is further decomposed into a horizontal effective thrust P·cosθ and a normal force P·sinθ perpendicular to the guide rail. This normal force P·sinθ generates a guide rail friction force f2 = K·P·sinθ, which in turn generates a pin retraction thrust P·α2 capable of overcoming the guide rail friction force. In this embodiment, the button spring bar is preferably configured with symmetrical double-sided pins, and the total ejection force of the double-sided pins is 2F. p = P·cosθ - K·P·sinθ = P·(cosθ - K·sinθ) (Equation 2), Based on Equations 1 and 2 above, the force transmission model formula is obtained: 2F p =F·(sinθ - K·cosθ)·(cosθ - K·sinθ) (Equation 3), further obtaining the quantitative model of the designed key force F as: F = 2F p / [(sinθ - K·cosθ)·(cosθ - K·sinθ)] (Equation 4), the force F output from the pin is established through Equation 4. pEquation 4 establishes a precise and predictable inverse design mapping relationship between the functional goals represented by the design button force F and the user experience represented by the design button force F. It mathematically couples structural parameters (such as the ramp angle θ) and material performance parameters (such as the system friction coefficient K) with the tactile feel, enabling designers to accurately predict and optimize the final user tactile feel during the product drawing stage. This changes the traditional spring ear R&D model that relies on trial and error with physical samples. Simultaneously, Equation 4 reveals the sensitivity and amplification effect of the ramp angle θ and the system friction coefficient K on the design button force F, providing a quantitative basis for the tolerance design of key parameters in the spring ear structure and the selection of friction control processes. This ensures a high degree of consistency in the tactile feel of spring ear products during mass production, solving the industry problem of large design deviations and inconsistent tactile feel in spring ear products, and achieving an upgrade from experience-based design to scientific design.

[0027] In step S2, the first efficiency factor represents the efficiency of converting the button force into net thrust along the inclined plane after overcoming the friction of the inclined plane. The closer the first efficiency factor α1 is to 1, the smaller the friction loss of the inclined plane and the higher the utilization rate of the button force, which is beneficial to guiding the design of the slope angle. In addition, in actual production, the sliding pair in the spring ear can be surface treated by polishing, injecting lubricating oil, etc., to reduce the system friction coefficient, thereby increasing the first efficiency factor α1 and reducing the required button force. The second efficiency factor represents the efficiency of converting the net thrust into effective horizontal thrust after overcoming the friction of the guide rail. The closer the second efficiency factor α2 is to 1, the smaller the friction loss of the guide rail and the higher the horizontal transmission efficiency of the net thrust, which is beneficial to balancing the design of the slope angle, so that the slope angle obtains a suitable design range between the first efficiency factor α1 and the second efficiency factor α2.

[0028] In this embodiment, the frictional losses of the inclined plane transmission and guide rail transmission stages are characterized in detail by the first efficiency factor α1 and the second efficiency factor α2, respectively. The comprehensive transmission efficiency η formed by the product of the two factors completely describes the overall conversion efficiency from button force to pin output force. The quantitative modeling of dual frictional losses solves the product design deviation problem caused by "single-stage friction neglect" or "complete neglect of friction" in previous spring ear designs. The first and second efficiency factors simplify the complex frictional physics in spring ear into directly calculable parameters, enabling designers to quickly and accurately complete the parameter matching of system friction coefficient and ramp angle, ensuring consistent operation feel of spring ear products in different batches. In addition, the force transmission model including the comprehensive transmission efficiency η, together with the stroke matching model and spring adaptation model, constitute a closed-loop design system, supporting the coordinated optimization of button force, stroke, and spring stiffness, solving the long-standing problems in button spring ear design such as reliance on experience, lack of system design model, and difficulty in consistent product quality.

[0029] In this embodiment, the slope angle θ ranges from 34° to 45°. This range is determined based on the mathematical model of force transmission efficiency factors α1=sinθ-K·cosθ and α2=cosθ-K·sinθ, and through system optimization analysis. Within this angle range, the first efficiency factor α1 and the second efficiency factor α2 can achieve a better balance, so that the comprehensive transmission efficiency η=α1×α2 is maintained at a high level, thereby satisfying the pin ejection force F. p Under the premise of meeting the requirements, the design button force F is effectively reduced, optimizing the user's operating feel. At the same time, combined with the travel matching model, it can be seen that this range avoids the problem of low force transmission efficiency caused by too small a ramp angle, and also prevents the problem of too long button travel L caused by too large a ramp angle, ensuring the compactness of the spring bar structure and the assembly reliability.

[0030] Furthermore, the slope angle θ is preferably set to 38°.

[0031] In this embodiment, the system friction coefficient K ranges from 0.1 to 0.3, with a baseline value of 0.19. This defined range provides designers with direct parameter input, avoiding the blindness of experience-based selection and improving the design efficiency of spring ear products. Furthermore, this range takes into account the friction coefficient variations that may be caused by different surface treatment processes, ensuring the robustness of the design scheme in actual production. In addition, combined with the quantitative analysis of the first efficiency factor α1 and the second efficiency factor α2, designers can optimize the system transmission efficiency within this range by adjusting the K value (such as by using lubrication or surface coating), achieving a synergistic balance between button force, operating feel, and assembly reliability, thereby improving the consistency of spring ear products and user experience.

[0032] Furthermore, to verify the effectiveness of the range of values ​​for the system friction coefficient K, this embodiment compares and verifies the range of values ​​for the system friction coefficient K by combining the friction characteristics of typical material combinations (such as metal-metal, metal-plastic), actual process feasibility, and statistical analysis of measured data. By back-calculating the K value using 15 sets of measured data, all valid solutions for K values ​​fall within the range of 0.1 ≤ K ≤ 0.3, ensuring the reliability of the range of values ​​for the system friction coefficient K. The reference value K = 0.19 produces the smallest deviation, which is within the allowable range for engineering applications, enabling the force transmission formula to have high predictive accuracy in practical applications. By establishing this reference value, the difference between the actual K value and the reference value can be directly compared in practical applications, quickly determining whether the system friction characteristics are abnormal, and allowing for targeted surface treatment or structural optimization of the spring bar transmission pair. Secondly, using a unified reference value in the design can reduce performance fluctuations between different batches and products from different suppliers, ensuring the yield rate of the spring bar and ensuring that key user experience indicators such as button feel and assembly reliability remain stable.

[0033] In this embodiment, the target value F of the pin push-out force p The value range is 0.5N to 3.0N, and the pin stroke L p The value range is 0.5mm to 1.5mm; the target value of the pin ejection force F p The value range of the pin and the pin travel L p The value range is based on a comprehensive consideration of ergonomics, the reliability of the spring ear structure, and the miniaturization requirements of spring ear products. Specifically, the pin top output force F p The lower limit of 0.5N ensures the reliability of the pin lifting action and its resistance to environmental interference (such as slight sticking), and the pin lifting force F p The upper limit of 3.0N avoids excessive button operation force (F) affecting the feel; pin travel (L) p The lower limit of 0.5mm ensures sufficient pin travel to achieve clear tactile feedback, and the pin travel L... p The upper limit of 1.5mm aligns with the design trend of wristwatches and other electronic products that pursue thinness and compactness. This is achieved by adjusting the target value F of the pin's top force. p The value range of the pin and the pin travel L p The synergistic optimization of the value range clarified the user's need for buttons to provide a clear tactile feel and a comfortable force, as well as the hardware constraints of the compact spring ear structure. This was then achieved through the geometric relationship L = L p ·tanθ and friction verification model 2F p = F·(sinθ-Kcosθ)(cosθ-Ksinθ), mapping user requirements to hardware constraints as F p and L p The quantitative indicators were then used to perform boundary verification by combining the known ranges of the slope angle θ (34°~45°) and the friction coefficient K (0.1~0.3). This confirmed that the combination of parameters was fully feasible within the theoretical models of the force transmission model, stroke matching model and spring adaptation model, and could cover most application scenarios, thus improving the universality of spring ear products.

[0034] In this embodiment, the spring pre-compression amount δ is 0.5mm to 1.2mm. The range of the spring pre-compression amount δ is formed based on a comprehensive consideration of structural reliability, tactile optimization, and fatigue life. Specifically, the lower limit of the spring pre-compression amount δ, 0.5mm, ensures that the spring has sufficient preload in the initial position to avoid false triggering of the button due to vibration or gravity, while providing clear force feedback for the initial pressing stage. The upper limit of the spring pre-compression amount δ, 1.2mm, prevents excessive compression that could lead to excessive spring stress or plastic deformation, while also taking into account the space compactness requirements of the thin and light design of the spring, thereby improving operational reliability, optimizing user experience, extending the service life of the spring, and enhancing the adjustability of the spring transmission system design.

[0035] Furthermore, the spring pre-compression amount δ is preferably 0.5 mm.

[0036] In this embodiment, in step S6, the preset operating force range is 5N to 12N. Specifically, the lower limit of the preset operating force range, 5N, is suitable for the button feel and minimum trigger force of various mainstream electronic products, improving the universality of the spring ear product. The upper limit of the preset operating force range, 12N, is suitable for the threshold range of human finger pressing comfort, preventing user fatigue caused by prolonged or repetitive operation, and balancing the durability and operating comfort of the internal structure of the spring ear. In addition, the preset operating force range provides a reasonable and reliable design range benchmark, transforming subjective feel requirements into objective mechanical indicators, which facilitates subsequent spring selection and reasonable design of ramp angles. It also enhances the quality controllability of the spring ear product. The clear force range enables the standardization of button force testing on the production line, which helps to ensure the consistency of feel of mass-produced products.

[0037] As an optional embodiment of this solution, taking typical design conditions as an example, measurements are performed on spring ear samples to verify the reliability of the spring ear parameter design method. Specifically: S1. Determine the design input parameters: Target value of pin ejection force F p =1.2N, pin stroke L p =1.0mm, slope angle θ=38°, system friction coefficient K=0.19; S2, Computational power transfer efficiency factor: Given θ = 38°, calculate the trigonometric function values: sin38° = 0.6157, cos38° = 0.7880; The first efficiency factor α1 = sinθ - K·cosθ = 0.6157 - 0.19 × 0.7880 = 0.4660; The second efficiency factor α2 = cosθ - K·sinθ = 0.7880 - 0.19 × 0.6157 = 0.6710; The overall transmission efficiency η = α1 × α2 = 0.4660 × 0.6710 = 0.3127; S3. Calculate the key force for design: F=2F p / η=2×1.2 / 0.3127=7.67N; S4. Calculate key travel: L=L p ·tanθ=1.0×tan38°=1.0×0.7813=0.78mm; S5. Calculate the spring constant: K s =F p / (L p+δ)=1.2 / (1.0+0.5)=0.8N / mm; S6. Parameter verification: The designed button force F=7.67N meets the operating force range requirement of 5N~12N, and the design parameters are valid.

[0038] Example 2: like Figures 2 to 6 As shown, in this embodiment 2, based on the above embodiment 1, in order to improve the effectiveness and reliability of the button-type spring ear parameter design method, the parameter design method further includes: S7. Collect multiple sets of button force F and corresponding pin push force F. p Actual measured data; S8. Based on the force transmission model, determine the friction verification model corresponding to the friction coefficient K of the system. The friction verification model is: F·sinθcosθ·K²-F·K+(F·sinθcosθ-2F p )=0; S9. Calculate multiple sets of experimental values ​​of the system friction coefficient K based on the friction verification model, and obtain the average value of the multiple sets of experimental values ​​of the system friction coefficient K. Compare and verify the average value with the benchmark value of the system friction coefficient K.

[0039] This invention adds closed-loop verification steps S7-S9 to the parameter design method. First, the method moves from laboratory verification to feedback collection in practical application scenarios. By measuring multiple springbox samples from the same batch, multiple sets of key force F and pin ejection force F are collected. p The measured data were used to validate theoretical models such as the force transmission model, stroke matching model, and spring adaptation model in the actual processing environment of spring ears, significantly improving the engineering reliability of the parameter design method. Secondly, an optimization model for the system friction coefficient K was derived through the force transmission model: (F·sinθcosθ·K² - F·K + (F·sinθcosθ - 2F)) p Equation 5 quantifies the complex nonlinear frictional effects during spring ear transmission into analytically calculable parameters, enabling designers to directly deduce the K value under actual spring ear operating conditions based on measured data. Finally, by calculating the average value of multiple experimental K values ​​and comparing it with the preset benchmark value (K=0.19), a dynamic optimization mechanism of "design → measurement → calibration" is formed, transforming the system friction coefficient from a fixed empirical value into a key variable that can be corrected and tracked.

[0040] This closed-loop design significantly enhances the adaptability and reliability of the parameter design method. When the measured average value of the system friction coefficient K deviates little from the benchmark value, it verifies the robustness of the spring bar design. When the measured average value of the system friction coefficient K deviates significantly from the benchmark value, it can promptly prompt process adjustments (such as lubrication improvement or surface treatment) in the early stages of processing. This enables rapid prediction of spring bar product performance, facilitates timely adjustment of processing technology, reduces spring bar development costs, ensures consistent button feel, improves product yield, and supports continuous process optimization.

[0041] Taking a typical operating condition as an example, this embodiment provides the process for verifying the system friction coefficient: To verify the accuracy of the system's friction coefficient K=0.19 baseline value, 15 sets of measured data were collected (as shown in Table 1 below) for verification. Verification conditions: slope angle θ=38°. Expanding the force transmission formula into an optimization model formula with respect to K: F·sinθcosθ·K²-F·K+(F·sinθcosθ-2F p )=0; Substituting θ = 38° (sin38°·cos38° = 0.4852) and the measured values ​​F and F for each group... p Find the value, solve for K, and filter out valid solutions (0.1≤K≤0.3). The verification result is as follows: Table 1: Measured data (θ=38°)

[0042] As shown in Table 1 above: Number of valid solutions: Valid K values ​​were obtained for all 15 sets of data; Average K value: 0.181; Standard deviation of K value: 0.041; Deviation from the benchmark value: |0.19-0.181|=0.009, relative deviation is about 4.7%.

[0043] The verification conclusion is that the above deviation results are within the allowable range of the project (<10%), proving that the benchmark value K=0.19 can be used for design calculations, and verifying the accuracy of the mechanical model.

[0044] Example 3: like Figures 3 to 6As shown, the present invention also provides a transmission structure for a button-type quick-release spring bar. The transmission structure is designed using the parameter design method described above. The transmission structure is disposed in the housing 11 of the button-type quick-release spring bar. The transmission structure includes a button 13, at least one pin 12, and a transmission surface 10 disposed between the pin 12 and the button 13. The button 13 and the pin 12 are slidably connected to the housing 11. The transmission surface 10 has a ramp angle θ with the horizontal plane. The button 13 slides with the pin 12 through the transmission surface 10, so that the pin 12 extends and retracts between the inside and outside of the housing 11. The housing 11 is provided with a guide hole corresponding to the pin 12 to ensure the stable extension and retraction of the pin 12. The pin 12 is also connected to an elastic element 15 for extending the pin 12 to the outside of the housing 11. Optionally, the elastic element 15 is preferably a spring.

[0045] As an optional embodiment of this solution, a transmission member 14 is provided between the button 13 and the pin 12, and a transmission surface 10 is provided between the transmission member 14 and the button 13. At least one of the relative sliding surfaces between the transmission member 14 and the button 13 forms the transmission surface 10. The vertical movement of the button 13 relative to the housing 11 is converted into the horizontal movement of the pin 12 relative to the housing 11 through the transmission surface 10, thereby enabling the pin 12 to extend and retract inside and outside the housing 11.

[0046] Furthermore, at least one of the relative sliding surfaces of the button 13 and the pin 12 is subjected to a surface treatment that can reduce the coefficient of friction; optionally, the surface treatment can be performed by polishing, adding lubricating oil, etc., which is not specifically limited here.

[0047] As an optional embodiment of this solution, the transmission component 14 is integrally molded from plastic, and the button 13 and the housing 11 are integrally molded from metal material, wherein the plastic includes at least nylon and the metal material includes at least stainless steel.

[0048] The above examples are merely illustrative of the technical content of the present invention to facilitate easier understanding by the reader, but do not imply that the implementation of the present invention is limited to these examples. Any technical extensions or re-creations made based on the present invention are protected by the present invention. The scope of protection of the present invention is defined by the claims.

Claims

1. A spring ear parameter design method based on dual frictional loss, characterized in that, Includes the following steps: S1. Determine the design input parameters for the push-button quick-release spring bar transmission structure. The design input parameters include the target value of the pin push-out force F. p Pin travel L p The slope angle θ and the system friction coefficient K; S2. Determine the target value F of the pin push-out force. p A matching force transmission efficiency factor, the force transmission efficiency factor including a first efficiency factor α1 and a second efficiency factor α2, wherein the first efficiency factor α1 = sinθ - K·cosθ, and the second efficiency factor α2 = cosθ - K·sinθ; a comprehensive transmission efficiency value η is generated based on the first efficiency factor α1 and the second efficiency factor α2, the comprehensive transmission efficiency value η = α1 × α2. S3. Determine the force transmission model that matches the force transmission efficiency factor, and determine the target value F of the pin ejection force based on the force transmission model. p The design of the corresponding button force F; the force transmission model is: F=2F p / η; S4. Determine the pin travel L. p A stroke matching model adapted to the slope angle θ is used to determine the stroke L of the pin. p The corresponding key travel distance L; the travel distance matching model is: L=L p ·tanθ; S5. Determine the target value F of the pin push-out force. p A matching spring model is used, and the target value F of the pin push-out force is determined based on the spring model. p The appropriate spring constant K s The spring fitting model is: K s =F p / (L p +δ), where δ is the spring pre-compression; S6. Using the slope angle θ as a fixed quantity, verify the effectiveness of the design range of the designed button force F, and determine whether the design range of the designed button force F meets the preset operating force range. If it does not meet the requirements, adjust the system friction coefficient K and repeat steps S2 to S5.

2. The spring ear parameter design method based on dual frictional loss as described in claim 1, characterized in that, In step S2, the force transmission efficiency factor is calculated according to the friction loss model, which includes inclined plane friction loss and guide rail friction loss during pin movement. When the designed button force F is applied to an inclined plane with the slope angle θ, the designed button force F decomposes into a net thrust P = F·α1 along the inclined plane, and the net thrust P decomposes into a pin retraction thrust P·α2, so that the total push-out force of the pin in the button-type quick-release spring ear is: 2F p =F·α1·α2.

3. The spring ear parameter design method based on dual frictional loss as described in claim 1, characterized in that, The system friction coefficient K ranges from 0.1 to 0.3, with a base value of 0.

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4. The spring ear parameter design method based on dual frictional loss as described in claim 1, characterized in that, The target value of the pin push-out force F p The value range is 0.5N to 3.0N, and the pin stroke L p The value range is 0.5mm to 1.5mm.

5. The spring ear parameter design method based on dual frictional loss as described in claim 1, characterized in that, The pre-compression of the spring, δ, is 0.5 mm to 1.2 mm.

6. The spring ear parameter design method based on dual frictional loss as described in claim 1, characterized in that, In step S6, the preset operating force range is 5N to 12N.

7. The spring ear parameter design method based on dual frictional loss as described in claim 1, characterized in that, The parameter design method further includes: S7. Collect multiple sets of button force F and corresponding pin push force F. p Actual measured data; S8. Based on the force transmission model, determine the friction verification model corresponding to the friction coefficient K of the system. The friction verification model is: F·sinθcosθ·K²-F·K+(F·sinθcosθ-2F p )=0; S9. Calculate multiple sets of experimental values ​​of the system friction coefficient K based on the friction verification model, and obtain the average value of the multiple sets of experimental values ​​of the system friction coefficient K. Compare and verify the average value with the benchmark value of the system friction coefficient K.

8. A spring ear transmission structure, characterized in that, The spring ear transmission structure is designed using the parameter design method as described in any one of claims 1 to 7. The transmission structure is disposed in the housing of the button-type quick-release spring ear. The transmission structure includes a button, at least one pin, and a transmission surface disposed between the pin and the button. The transmission surface has the slope angle θ between itself and the horizontal plane. The button slides with the pin through the transmission surface, so that the pin can extend and retract between the inside and outside of the housing. The pin is also connected to an elastic element for extending the pin to the outside of the housing.

9. The spring ear transmission structure as described in claim 8, characterized in that, At least one of the relative sliding surfaces of the button and the pin is subjected to a surface treatment that reduces the coefficient of friction.

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