Silicone rubber ring damping system of fascia gun and damping effect calculation method
By calculating the shock absorption effect of the silicone rubber ring of the fascia gun using a mathematical model, the problem of design dependence on experience in the existing technology is solved, and accurate prediction and optimization are achieved, which significantly shortens the development cycle, reduces costs and improves product performance and reliability.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2026-01-13
- Publication Date
- 2026-03-27
AI Technical Summary
The design of silicone rubber shock absorbers in existing fascia guns lacks precise calculation methods, leading to a reliance on experience and repeated trials, which is time-consuming and costly, and makes it difficult to achieve optimal performance and reliability.
By employing a mathematical model combined with nonlinear mechanics of materials, a method for calculating the damping effect is established by quantitatively correlating the physical parameters of the silicone rubber ring with the damping effect. This method includes determining the crank eccentricity, connecting rod length, and damping ratio of the silicone rubber ring, and calculating the vibration transmissibility using the transmissibility formula in a single-degree-of-freedom system.
It enables accurate prediction and optimization during the design phase, shortens the development cycle, reduces costs, improves product performance and reliability, and ensures design consistency and repeatability.
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Figure CN121744713A_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The application relates to the technical field of fascia guns, in particular to a silicon rubber ring damping system of a fascia gun and a damping effect calculation method. BACKGROUND
[0002] As a high-frequency impact physiotherapy device, the fascia gun drives a slider to make reciprocating motion through an internal motor, generates high-frequency vibration to impact human soft tissue to achieve relaxation effect. In this process, the slider will collide with the limiting structure when it moves to the end of the stroke, generating a huge impact force and an uncomfortable noise, which can easily cause internal parts to loosen or be damaged over a long period of time, affecting product life and user experience. To solve this problem, the existing technology generally sets a silicon rubber damping ring at the collision contact part to absorb impact energy and reduce noise by using its high elastic modulus and damping characteristics. However, the design and selection of the silicon rubber damping ring currently depend on the experience of engineers and repeated physical trial and error tests, and there is a lack of a precise and efficient theoretical calculation method. The usual design process is to preliminarily determine the Shore hardness, cross-sectional shape and size of the rubber ring according to experience, then make a sample for installation test, and subjectively evaluate the damping effect by measuring the collision noise, motor current fluctuation or observing the slider rebound through high-speed photography. If the effect is not up to standard, the parameters are adjusted again and the sample is tested again, and this process is repeated, which consumes a lot of time, manpower and material costs, and the final result is heavily dependent on the personal experience of the designer, making it difficult to ensure optimization and consistency. In addition, due to the inability to accurately predict the damping performance in the design stage, it may lead to insufficient damping or over-damping design of the product. Insufficient damping will still have impact and noise problems, and over-damping design will excessively consume motor power and affect the impact force, ultimately making the product performance, reliability and cost unable to achieve the best balance. Therefore, there is an urgent need in the field for a method that can scientifically and quantitatively calculate the damping effect of the silicon rubber ring to guide the optimization design in the early stage and get rid of the excessive dependence on later tests. SUMMARY
[0003] The application provides a silicon rubber ring damping system of a fascia gun and a damping effect calculation method to at least solve the noise problem of the fascia gun in the related art and the problem of quantitatively calculating the damping effect of the silicon rubber ring of the fascia gun.
[0004] To achieve the above object, the application provides a silicone rubber ring damping system of a fascia gun, comprising a driving motor, a massage head and a transmission mechanism connecting the motor and the massage head, the transmission mechanism comprising a crank, a connecting rod and a sliding block, one end of the crank being connected with the output end of the driving motor, the other end being connected with the connecting rod, one end of the sliding block being connected with the connecting rod, the other end being connected with the massage head, the crank driving the sliding block and the massage head to reciprocate through the connecting rod, a positioning sleeve for limiting the sliding block in reciprocation being arranged outside the sliding block, a silicone rubber ring for collision damping in the reciprocation process being arranged outside the positioning sleeve; the positioning sleeve is a hollow cylinder, the inner diameter of which is equal to the outer diameter of the sliding block in clearance fit; the inner diameter of the silicone rubber ring is equal to the outer diameter of the positioning sleeve in close fit.
[0005] In some embodiments, the crank has a mounting hole position connected with the output end of the driving motor and a mounting shaft position connected with the connecting rod, the distance between the mounting hole position of the crank and the mounting shaft position of the crank being an eccentric distance, the eccentric distance being 4-10 mm.
[0006] In some embodiments, the connecting rod has a mounting hole position connected with the crank and a mounting hole position connected with the sliding block, the distance between the two mounting hole positions being a hole distance of the connecting rod, the hole distance being 30-40 mm, and one ball bearing being arranged at the connection of the two mounting hole positions of the connecting rod.
[0007] In some embodiments, the inner diameter of the silicone rubber ring is 20-38 mm, the outer diameter is 22-40 mm and the length is 15-30 mm.
[0008] In some embodiments, the sliding block is a cylindrical thin-walled part with a length of 20-50 mm, the outer diameter of the sliding block being 12-30 mm, one end of the sliding block having a radial mounting hole position matched with the connecting rod and the other end being connected with the massage head.
[0009] The application also provides a calculation method of damping effect of a silicone rubber ring of a fascia gun, based on the above-mentioned silicone rubber ring damping system of the fascia gun, comprising: determining the eccentric distance of the crank and the length of the connecting rod, taking the eccentric distance of the crank and the length of the connecting rod as fixed values, taking the damping ratio of the silicone rubber ring and the collision frequency ratio as variables, calculating the vibration transmissibility after the silicone rubber ring is installed through the transmissibility formula in a single degree of freedom system, and then calculating the damping effect of the silicone rubber ring.
[0010] In some embodiments, the transmissibility formula of the silicone rubber ring as a damping component is , wherein r is the frequency ratio, ζ is the damping ratio of the silicone rubber ring; the frequency ratio r = ω / ω nω = 2πn / 60, where ω is the system frequency. n The natural frequency is ωn, where n is the motor speed; the natural frequency ωn = In the formula, k is the compressive stiffness of the silicone rubber ring, and M is the mass supported by the silicone rubber ring.
[0011] In some embodiments, the compressive stiffness k of the silicone rubber ring is related to the shape factor S and the elastic modulus E, k = E × A × (1 + 2 × S²) / h, where A is the bearing area and h is the height of the silicone rubber ring; the bearing area A = π(Ro² - Ri²), where Ro is the outer diameter of the silicone rubber ring and Ri is the inner diameter of the silicone rubber ring; the shape factor S is the ratio of the bearing area to the free expansion area. = (Ro-Ri) / 2h.
[0012] In some embodiments, the deformation of the silicone rubber ring is mainly caused by the reaction of the slider, and therefore can be calculated equivalently, with the equivalent mass M = F. side / g, where F side The forced vibration force is denoted by g, and g is the gravitational constant.
[0013] In some embodiments, the forced vibration force F side = F rod ×sinφ ≈F rod ×sinθ×L1 / L2, where F rod The driving force of the connecting rod is θ, where θ is the crank angle, L1 is the crank eccentricity, and L2 is the connecting rod length; the driving force of the connecting rod is F. rod = T n / [L1(sinθ+L1 / L2sinθcosθ)], where T n This refers to the output torque of the motor.
[0014] Based on the above, the advantages of this application's technical solution compared to the prior art are:
[0015] 1. Achieve quantitative design and accurate prediction: By establishing a mathematical model that includes the nonlinear mechanical behavior of materials, the physical parameters of silicone rubber rings (such as hardness and cross-sectional dimensions) are quantitatively correlated with the damping effect, enabling accurate prediction of damping performance during the design stage, thus eliminating the reliance on experience and trial and error.
[0016] 2. Significantly shortens the development cycle and reduces costs: This method allows engineers to evaluate multiple design options by performing simulations and calculations on a computer, greatly reducing the number of physical prototypes and the time spent on repeated testing, thereby significantly shortening the product development cycle and reducing development costs and material waste;
[0017] 3. Optimize product performance and reliability: Through accurate calculation, the best balance point between shock absorption effect and motor power consumption, impact force can be found, avoiding "insufficient damping" or "over-damping" design, so as to optimize the impact experience, noise level and long-term operation reliability of the final product, and improve the comprehensive competitiveness of the product;
[0018] 4. Improve the consistency and repeatability of the design: Standardize and formalize the design process, reduce the fluctuations in design results caused by differences in personnel experience, and ensure the consistency and repeatability of the shock absorption system performance in different models of products or different batches of production. BRIEF DESCRIPTION OF DRAWINGS
[0019] The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiments of the present application and together with the description serve to explain the present application. In the drawings:
[0020] Figure 1 is a schematic diagram of the structure of an embodiment of the present application.
[0021] Legend of the drawings: crank 1; connecting rod 2; slider 3; silicone rubber ring 4; positioning sleeve 5. DETAILED DESCRIPTION
[0022] In order to make the purpose, technical scheme and advantages of the present application more clear, the present application is described and explained below in combination with the drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and do not limit the present application. Based on the embodiments provided in the present application, all other embodiments obtained by those of ordinary skill in the art without making creative efforts fall within the scope of the present application. In addition, it can be understood that although the efforts made in this development process can be complex and lengthy, some design, manufacture or production changes made on the basis of the technical content disclosed in the present application are only routine technical means for those of ordinary skill in the art related to the content disclosed in the present application, and should not be understood as insufficient disclosure of the present application.
[0023] In the present application, "embodiment" means that the specific features, structures or characteristics described in combination with the embodiment can be included in at least one embodiment of the present application. The appearance of this phrase in various places in the specification does not necessarily mean the same embodiment, nor is it an independent or alternative embodiment to other embodiments. Those of ordinary skill in the art explicitly and implicitly understand that the embodiments described in the present application can be combined with other embodiments without conflict.
[0024] Unless otherwise defined, technical terms and scientific terms used in the present application shall have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains. Unless otherwise defined, the terms "one", "a", "an", "the" and like terms referring to an element will not be limited to the singular but can comprise one or more elements unless otherwise indicated. The terms "comprising", "including", "containing", "have" and any variations thereof are intended to cover a non-exclusive inclusion such that processes, methods, articles, or apparatuses that comprise, include, contain, or have a list of steps or components that does not consist entirely of those listed are still within the scope of the present application. The terms "connected", "coupled", and "coupling" are not limited to direct and physical connections, but can include an indirect coupling or physical connection such as an electrical connection. The term "plurality" means two or more. The term "and / or" describes associated objects in association relationships, which means that there can be three relationships, for example, "A and / or B" can mean that A exists alone, A and B exist together, and B exists alone. The terms "first", "second", "third", and the like are merely used to distinguish similar objects, and do not represent a specific order of the objects.
[0025] In a first aspect, the present application provides a silicone rubber ring damping system of a fascia gun, comprising a driving motor, a massage head, and a transmission mechanism connecting the motor and the massage head, the transmission mechanism comprising a crank, a connecting rod, and a sliding block, one end of the crank being connected to the output end of the driving motor, the other end being connected to the connecting rod, one end of the sliding block being connected to the connecting rod, the other end being connected to the massage head, the crank driving the sliding block and the massage head to reciprocate through the connecting rod, a positioning sleeve being provided outside the sliding block for limiting the sliding block during reciprocation, and a silicone rubber ring being provided outside the positioning sleeve for collision damping during reciprocation.
[0026] In a second aspect, the present application further provides a method for calculating the damping effect of a silicone rubber ring of a fascia gun, based on the above-mentioned silicone rubber ring damping system of the fascia gun, comprising: determining the eccentricity of the crank and the length of the connecting rod, taking the eccentricity of the crank and the length of the connecting rod as fixed values, and taking the damping ratio and the collision frequency ratio of the silicone rubber ring as variables, calculating the vibration transmissibility after installing the silicone rubber ring through the transmissibility formula in the single degree of freedom system, and then calculating the damping effect of the silicone rubber ring.
[0027] Embodiments as Figure 1As shown, a kind of silicone rubber ring damping system of fascia gun, including drive motor, massage head and the transmission mechanism of transmission connection motor and massage head.Transmission mechanism includes crank 1, connecting rod 2 and slider 3, crank 1 one end is connected with the output end of drive motor, the other end is connected with connecting rod 2, slider 3 one end is connected with connecting rod 2, the other end is connected with massage head, crank 1 drives slider 3 and massage head reciprocating motion by connecting rod 2, slider 3 is provided with the positioning sleeve 5 for limiting slider 3 in reciprocating motion, positioning sleeve 5 is provided with silicone rubber ring 4 for collision damping in the process of reciprocating motion.
[0028] Specifically, positioning sleeve 5 is hollow cylinder with wall thickness of 1-3mm, its inner diameter is equal to the outer diameter of slider 3 with clearance fit, because the outer diameter surface of slider 3 and the inner diameter surface of positioning sleeve 5 slide reciprocating motion, the inner diameter of positioning sleeve 5 and the outer diameter of slider 3 have 0-0.2mm assembly tolerance.The inner diameter of silicone rubber ring 4 is equal to the outer diameter of positioning sleeve 5 and fits closely.
[0029] Specifically, the inner diameter of silicone rubber ring 4 is 20-26mm, the outer diameter is 15-40mm, and the length is 10-30mm.Slider 3 is cylindrical thin-walled part with length of 20-40mm, the outer diameter of slider 3 is 15-25mm, one end of slider 3 has radial mounting hole position matched with connecting rod 2, and the other end is connected with massage head.Crank 1 has mounting hole position connected with drive motor output end and mounting shaft position connected with connecting rod 2, the distance between mounting hole position of crank 1 and mounting shaft position of crank 1 is eccentric distance, and the eccentric distance is 4-10mm.Connecting rod 2 has mounting hole position connected with crank 1 and mounting hole position connected with slider 3, the distance between two mounting hole positions is hole distance of connecting rod 2, and the hole distance is 30-40mm, and one ball bearing is arranged at the connection of two mounting hole positions of connecting rod 2.Drive motor is motor with maximum speed of about 3600n / min, and the motor output end is connected with the mounting hole position of crank 1.
[0030] The embodiment also provides a calculation method of damping effect of silicone rubber ring of fascia gun, which is based on the mechanical structure of the above fascia gun and details the calculation method of damping effect.The calculation method includes: determining the eccentric distance of crank 1 and the length of connecting rod 2 (in this embodiment, the length of connecting rod 2 can also be regarded as the hole distance between two mounting hole positions), taking the eccentric distance of crank 1 and the length of connecting rod 2 as fixed values, and taking the damping ratio and collision frequency ratio of silicone rubber ring 4 as variables, calculating the vibration transmissibility after mounting silicone rubber ring 4 by the transmissibility formula in single degree of freedom system, and then calculating the damping effect of silicone rubber ring 4.
[0031] Further, the transmissibility formula of silicone rubber ring 4 as damping component is , and r= ω / ω n , ωn = , if the shock absorbing effect is to be satisfied and at the same time T < 1 is required. In the formula, r is the frequency ratio, ω is the system frequency, ω n is the natural frequency, k is the compression stiffness of the silicone rubber ring 4, M is the mass supported by the silicone rubber ring 4, and ζ is the damping ratio of the silicone rubber ring 4 (usually ζ ≈ 0.1-0.3).
[0032] Further, the compression stiffness k of the silicone rubber ring 4 is related to the shape factor S and the elastic modulus E, k = E × A × (1 + 2 × S²) / h, where A is the bearing area and h is the height of the silicone rubber ring 4; A = π(Ro²-Ri²), where Ro is the outer diameter of the silicone rubber ring 4 and Ri is the inner diameter of the silicone rubber ring 4; the shape factor S is the ratio of the bearing area to the free expansion area, = (Ro-Ri) / 2h; substituting each part can obtain the compression stiffness k value of the silicone rubber ring 4. In the embodiment, Ro = 0.0135 m, Ri = 0.0125 m, h = 0.0215 m, substituting to calculate the bearing area A = π(Ro²-Ri²) ≈ 8.168x10 -5 m², S = A / [2π × (Ro + Ri) × h], E ≈ 3G = 2.1MP, substituting to obtain k = 7987 N / m.
[0033] Further, since the deformation amount of the silicone rubber ring 4 is mainly caused by the reverse shock of the slider 3, it can be calculated equivalently, the equivalent mass M = F side / g, where F side is the forced vibration force, and g is the gravitational constant;
[0034] F side = F rod × sinφ ≈ F rod × sinθ × L1 / L2, where F rod is the driving link 2 thrust, θ is the swing angle of the crank 1, L1 is the eccentricity of the crank 1, and L2 is the length of the connecting rod 2 (in the embodiment, the length of the connecting rod 2 can also be regarded as the hole distance between the two mounting hole positions);
[0035] F rod = T n / [L1 (sinθ + L1 / L2 sinθ cosθ)], where T n is the motor output torque.
[0036] Substituting the calculation can obtain the forced vibration force F side and the equivalent mass M, substituting the equivalent mass M and the compression stiffness k of the silicone rubber ring 4 can obtain the natural frequency ω n , substituting the natural frequency ω n can obtain the system transmissibility T.
[0037] In this embodiment, based on the above, the parameters are taken within the specified range and the calculation is verified:
[0038] L2=0.033m, L1=0.004m, take θ=90 (maximum forced deformation), substitute into the calculation, F side = Tn / [L1sinθ×(1+0.121cosθ)]×sinθ×L1 / L2≈Tn / L2 =(30.3Tn) ,Motor torque Tn=0.25NM (maximum) (when the speed n=2500 rpm, Tn needs a compensation coefficient of 0.7), substituting into the equation, we get the equivalent mass M=30.3×Tn×0.7÷g =30.3×0.25×0.7 / 9.8 = 0.54 kg.
[0039] Substituting the equivalent mass M and compressive stiffness k obtained above into the equation...
[0040] Natural frequency ωn = = =121.6 rad / s,
[0041] The system frequency ω = 2πn / 60 = 2 × 3.1416 × 2500 / 60 = 261.8 rad / s, where n is the motor speed.
[0042] ωn satisfies ωn<ω / =261.8 / 1.414≈185.1 rad / s Vibration reduction conditions.
[0043] Substituting ζ≈0.2, ω=261.8 rad / s, ωn =121.6 rad / s into... The calculation yields T≈0.36, meaning that the silicone rubber system can only transmit 36% of the vibration, and can reduce vibration by 64%.
[0044] In summary, a method for calculating the shock absorption effect of silicone rubber rings in a fascia gun:
[0045] ,
[0046] r = ω / ω n , ωn = ,
[0047] k=E×A×(1+2×S²) / h, A = π(Ro²-Ri²), S=A / [2π×(Ro+Ri)×h]
[0048] M=F side / g=T n / [L1(sinθ+L1 / L2sinθcosθ)]×sinθ×L1 / L2≈Tn / (L2×g) (θ=90°),
[0049] Further, a method for calculating the shock absorption effect of a silicone rubber ring of a fascia gun, the design needs to protect the relevant dimensions:
[0050] First, the crank radius L1=3~16mm (0.003-0.016m) has no effect on the maximum transmission result. But the maximum value of L1 should not be greater than the rotation radius of the motor itself, and the minimum value should be a value with actual massage experience (L1=3mm is the smallest value with obvious massage effect). According to the experience design of traditional crank connecting rod structure, the ratio λ=L1 / L2 of crank radius L1 and connecting rod L2 is usually designed between λ=1 / 4 ~ 1 / 3, the minimum λ should not be less than 0.2, and the maximum λ should not be greater than 0.4, i.e. L2=15~40mm.
[0051] Second, the connecting rod L2=15~40mm (0.015-0.04m) affects M value, which indirectly affects the inverse ratio of ωn and the inverse ratio of ωn square. Replace L2=0.015-0.04m into the above example formula to recalculate T value: 0.015 = 0.17, T 0.04 = 0.43. It shows that L2=15~40mm has good shock absorption effect (more than 50%) under the same conditions.
[0052] Third, the outer diameter of the slider d=12~30mm, and the length is 20~50mm. The installation size of the massage head determines it: the installation outer diameter of the general massage head and the inner hole of the slider is usually 10~26mm, and the installation depth of the massage head and the slider is 15~30mm.
[0053] Fourth, the wall thickness of the positioning sleeve is 1~3mm, considering the minimum stiffness: the alloy wall thickness is about 1~2mm, and the injection molding part wall thickness is 1.5~3mm; the inner diameter and the outer diameter are equal to the outer diameter of the slider and the inner diameter of the silicone rubber ring, respectively.
[0054] Fifth, the inner diameter of the silicone rubber ring is 20~38mm (inner radius Ri=0.01~0.019m), the outer diameter is 22~40mm (outer radius R0=0.011~0.02m), and the length is 15~30mm (h=0.01~0.03m):
[0055] According to k=E×A×(1+2×S²) / h, A=π(Ro²-Ri²), S=A / [2π×(Ro+Ri)×h]
[0056] Replace Ri=0.01~0.013m, R0=0.011~0.02m, h=0.01~0.03m into the calculation
[0057] Obtained: k = 13923, (Ro = 0.011 m, Ri = 0.01 m, h = 0.01 m)
[0058] k = 4620, (Ro = 0.011 m, Ri = 0.01 m, h = 0.03 m)
[0059] k = 12342, (Ro = 0.015 m, Ri = 0.013 m, h = 0.03 m)
[0060] k = 8581, (Ro = 0.02 m, Ri = 0.019 m, h = 0.03 m)
[0061] k = 9578, (Ro = 0.15 m, Ri = 0.014 m, h = 0.02 m)
[0062] Substitute ωn = 261.8 rad / s, < ω = 261.8 rad / s, :
[0063] ωn = 160, T = 0.67, (k = 13923)
[0064] ωn = 92.4, T = 0.21, (k = 4620)
[0065] ωn = 151, T = 0.57, (k = 12342)
[0066] ωn = 126, T = 0.38, (k = 8581)
[0067] ωn = 133, T = 0.38, (k = 9578)
[0068] That is, the range size of the silicone rubber ring all has damping effect (T < 1).
[0069] Those skilled in the art should understand that the technical features of the above-described embodiments can be combined in any manner, and in order to make the description concise, all possible combinations of the technical features in the above-described embodiments are not described, however, as long as the combinations of the technical features do not contradict, they should be considered as the scope of the description.
[0070] The above-described embodiments only express several implementation manners of the present application, and the description is more specific and detailed, but it should not be understood as a limitation on the patent scope. It should be noted that for ordinary skilled in the art, without departing from the concept of the present application, a number of modifications and improvements can be made, which are all within the protection scope of the present application. Therefore, the protection scope of the patent of the present application should be subject to the appended claims.
Claims
1. A silicone rubber ring shock absorption system of a fascia gun, characterized in that: The massage head is connected with the driving motor through a transmission mechanism, the transmission mechanism comprises a crank, a connecting rod and a slider, one end of the crank is connected with the output end of the driving motor, the other end of the crank is connected with the connecting rod, one end of the slider is connected with the connecting rod, the other end of the slider is connected with the massage head, the crank drives the slider and the massage head to reciprocate through the connecting rod, a positioning sleeve is arranged outside the slider for limiting the reciprocating motion of the slider, and a silicone rubber ring is arranged outside the positioning sleeve for collision damping during the reciprocating motion.
2. The shock absorption system of the fascia gun according to claim 1, characterized in that: The crank has a mounting hole position connected with the output end of the driving motor and a mounting shaft position connected with the connecting rod, the distance between the mounting hole position of the crank and the mounting shaft position of the crank is the eccentric distance, and the eccentric distance is 4-10 mm.
3. The shock absorption system of the fascia gun according to claim 1, characterized in that: The connecting rod has a mounting hole position connected with the crank and a mounting hole position connected with the slider, the distance between the two mounting hole positions is the hole distance of the connecting rod, the hole distance is 30-40 mm, and one ball bearing is arranged at the connection position of the two mounting hole positions.
4. The shock absorption system of the fascia gun according to claim 1, characterized in that: The inner diameter of the silicone rubber ring is 20-38 mm, the outer diameter is 22-40 mm, and the length is 15-30 mm.
5. The shock absorption system of the fascia gun according to claim 1, characterized in that: The slider is a cylindrical thin-walled part with a length of 20-50 mm, the outer diameter of the slider is 12-30 mm, one end of the slider has a radial mounting hole position matched with the connecting rod, and the other end of the slider is connected with the massage head.
6. A method for calculating the shock absorption effect of a silicone rubber ring of a fascia gun, based on the shock absorption system of the silicone rubber ring of the fascia gun according to any one of claims 1-5, characterized in that, The eccentric distance of the crank and the length of the connecting rod are determined, the eccentric distance of the crank and the length of the connecting rod are taken as fixed values, the damping ratio and the collision frequency ratio of the silicone rubber ring are taken as variables, the vibration transmissibility after the silicone rubber ring is installed is calculated through the transmissibility formula in the single degree of freedom system, and then the damping effect of the silicone rubber ring is calculated. 7. The fascia gun silicone rubber ring shock absorption effect calculation method according to claim 6, characterized in that: The transmission rate formula of the silicone rubber ring as a damping component is , wherein r is a frequency ratio, and ζ is a damping ratio of the silicone rubber ring; the frequency ratio r = ω / ω n , ω = 2πn / 60, wherein ω is a system frequency, ω n is a natural frequency, and n is a motor rotating speed; the natural frequency ωn = , wherein k is a compression stiffness of the silicone rubber ring, and M is a mass supported by the silicone rubber ring.
8. The fascia gun silicone rubber ring shock absorption effect calculation method according to claim 7, characterized in that: The compression stiffness k of the silicone rubber ring is related to a shape factor S and an elastic modulus E, k=E×A×(1+2×S2) / h, wherein A is a bearing area, and h is a height of the silicone rubber ring; the bearing area A=π(Ro2-Ri2), wherein Ro is an outer diameter of the silicone rubber ring, and Ri is an inner diameter of the silicone rubber ring; the shape factor S is a ratio of the bearing area to a free expansion area, =(Ro-Ri) / 2h.
9. The method for calculating the shock absorption effect of the silicone rubber ring of the fascia gun according to claim 8, characterized in that: The deformation amount of the silicone rubber ring is mainly caused by the reverse vibration of the slider, so it can be calculated equivalently, and the equivalent mass M = F side / g, wherein F side is the forced vibration force, and g is the gravitational constant.
10. The method for calculating the shock absorption effect of the silicone rubber ring of the fascia gun according to claim 9, characterized in that: The forced vibration force F side = F rod ×sinφ ≈F rod ×sinθ×L1 / L2, where F rod is the driving link thrust, θ is the crank swing angle, L1 is the eccentricity of the crank, and L2 is the link length; the driving link thrust F rod = T n / [L1(sinθ+L1 / L2sinθcosθ)], where T n is the motor output torque.