Cushioning Performance of the Biomimetic Cobweb Cushioning Silicone Pad

At present, the packing method of “plastic bag–buffer packing–packing paper box” is adopted for bearing packaging. However, the common packing method has a poor packing effect and poor versatility. In this study, a new biomimetic cobweb cushion is proposed to solve the problem of insufficient cushioning capacity of high-precision bearing cushion packaging pads. First, according to the nature of cobweb form, the cobweb cushion structure configuration is determined. Next, based on the structure of the cushion and the relationship between the parameters of radial thread and spiral thread, a mechanical and target optimization model is established. The stress nephogram of bearing and the cobweb cushion are analyzed under three drop heights of 381, 610, and 700 mm, in the finite element simulation software to ensure that the maximum bearings stress is not beyond the material yield strength. Via the 3D printing technology, a cobweb cushion shell cast is made. Drop tests of the bearing were performed, and the results were verified with the finite element simulation analysis. This research can provide technical support for the protection of high-precision bearings from accidental drops during transportation.


Introduction
Bearing is an essential component in modern mechanical equipment, its primary function is to support the mechanical rotating body, to reduce the mechanical load friction coefficient of the equipment in the transmission process, and its precision determines the working accuracy of mechanical products [1][2][3]. Among them, high-precision bearings are widely used in aerospace, military equipment, high-precision equipment and other fields due to their excellent performance, and the demand for high-precision bearings has grown exponentially [4,5]. The surface quality of bearings is a crucial factor that determines the performance of mechanical equipment. At present, studies have focused on the manufacturing process of high-precision bearings and various applications of machinery and equipment. However, the impact of various external factors on the surface quality of bearings has not been studied comprehensively.
As a cushion carrier in the packaging structure, the cushioning material plays the main role of protecting high-precision bearings, which can decrease the influence of external shock and vibration, and absorb most of the energy of external shocks and vibrations suffered by high-precision bearings in the process of storage, transportation and turnover. Zhang Zhenyu proposed a cushion packing pad made of polydimethylsiloxane (PDMS) [6][7][8] for aviation bearings to improve the protection of bearings [9]. Yu Min et al. used 3D printing technology to fabricate thermoplastic polyurethane (TPU) cubic foam samples of different densities and sizes, and carried out mechanical compression tests, through comparative analysis, TPU materials have better cushioning performance [10,11], and medium-sized TPU cubic foam has the best mechanical properties [12]. Xu Ting et al.
testing and simulated transportation tests [18]. Bin Sun improved th tapered roller bearings by adding expanded polyethylene (EPE) [19, tween the outer ring and inner assembly and verified its protective e al. analyzed the impact of environmental factors on the cushioning p urethane (PU) [22,23] materials by observing the changes in appeara sion performance, compression set performance and infrared spectru under the influence of temperature, humidity and other external en [24]. Shijie Wang et al. developed a bionic-inspired honeycomb colum ture (BHTS) by the biological structure of beetle's elytra. Through the ergy absorption, maximum displacement and other parameters were a found that the BHTS buffer interlayer can effectively protect the rein structure from impact and explosion [25]. Taking advantage of the weight and high strength of honeycomb structure, Zhenglei Yu et al. lattice structure with memory alloy through the principle shape of str found that the bionic lattice structure has excellent impact resistance performance through quasi-static compression test and numerical sim At present, the packing method of "plastic bag-buffer packingis adopted for bearing packaging [27][28][29]. However, the common pa poor packing effect and poor versatility. In this paper, we propose a m structure-based cushion made of HL-1029 material. The cushion con designed by establishing and optimizing the mechanical model of th The shell was obtained, and the bionic cushion was cast using 3D p Through the analysis of experimental data, the cushioning performan ture cushion under three different drop heights were simulated in fini

Research on Cobweb Configuration
The forms of cobwebs in nature are very diverse and can be broa types: circular web with radial threads and spiral threads interwove web, and 3D irregular network. Among them, the flake web, containin area and robust wind resistance, is the most common, as shown in Fig   Figure 1. Flake web observed in nature.
A flaky regular polygon was deduced as the shape of the web c to the available literature and studying the shapes of different cobweb [30]. A simplified geometric structure containing only spiral threads, A flaky regular polygon was deduced as the shape of the web cushion by referring to the available literature and studying the shapes of different cobwebs observed in nature [30]. A simplified geometric structure containing only spiral threads, radial threads, and center was developed from the flaky regular polygon, as shown in Figure 2. As shown in Figure 3, a part of the simplified cobweb structure is taken as a micro element for the study.  Where R is the radius of the centerline of the web center, θ is the included angle between the center line and the centerline of the radial thread, d is the distance of the centerline of the adjacent spiral thread, t1 is the width of the radial thread, and t2 is the width of the spiral thread.

Mechanical Model of Cobweb Structure Cushion
The cobweb structure diagram in Figure 2 is converted to a 3D structure with a cer tain thickness, in which the internal force surface surface is the upper surface of the cob web structure, as shown in Figure 4a. Let the overall internal force applied to the cobweb structure be F and the upper surface area be S. For analysis, let us consider a micro-ele ment with the dimension dx, dy, and dz, x0, y0, and z0 be the changes in length after the micro-element is forced in the three directions of x, y, and z, dx0, dy0, and dz0 be the fina lengths after internal force deformation, respectively. Let dF be the internal force applied to the micro-element. The diagram of the micro-element is shown in Figure 4b. As shown in Figure 3, a part of the simplified cobweb structure is taken as a microelement for the study. As shown in Figure 3, a part of the simplified cobweb structure is taken as a element for the study.  Where R is the radius of the centerline of the web center, θ is the included between the center line and the centerline of the radial thread, d is the distance centerline of the adjacent spiral thread, t1 is the width of the radial thread, and t width of the spiral thread.

Mechanical Model of Cobweb Structure Cushion
The cobweb structure diagram in Figure 2 is converted to a 3D structure with tain thickness, in which the internal force surface surface is the upper surface of t web structure, as shown in Figure 4a. Let the overall internal force applied to the c structure be F and the upper surface area be S. For analysis, let us consider a mic ment with the dimension dx, dy, and dz, x0, y0, and z0 be the changes in length af micro-element is forced in the three directions of x, y, and z, dx0, dy0, and dz0 be th lengths after internal force deformation, respectively. Let dF be the internal force a to the micro-element. The diagram of the micro-element is shown in Figure 4b.  Where R is the radius of the centerline of the web center, θ is the included angle between the center line and the centerline of the radial thread, d is the distance of the centerline of the adjacent spiral thread, t 1 is the width of the radial thread, and t 2 is the width of the spiral thread.

Mechanical Model of Cobweb Structure Cushion
The cobweb structure diagram in Figure 2 is converted to a 3D structure with a certain thickness, in which the internal force surface surface is the upper surface of the cobweb structure, as shown in Figure 4a. Let the overall internal force applied to the cobweb structure be F and the upper surface area be S. For analysis, let us consider a micro-element with the dimension dx, dy, and dz, x 0 , y 0 , and z 0 be the changes in length after the microelement is forced in the three directions of x, y, and z, dx 0 , dy 0 , and dz 0 be the final lengths after internal force deformation, respectively. Let dF be the internal force applied to the micro-element. The diagram of the micro-element is shown in Figure 4b.  According to the micro-element analysis, the overall normal stress of the cobweb structure is given by: According to Equation (1), the larger the contact area, the smaller the stress. Therefore, the stress on the cobweb structure is smaller when the upper surface is larger. Further, shortening the total length of the cobweb structure cushion aids in reducing the waste of raw materials and overall costs. Therefore, maximizing the surface area and minimizing the total length are considered the optimization objectives.
Therefore, the optimization objectives can be formulated as: where C is the total length of cobweb structure, S is the surface area of cobweb structure, n1 is the number of radial threads, and n2 is the number of the spiral threads. We have: The cobweb cushion plays a protective role at the bottom of the bearing. Therefore, the inner connection radius of the outermost ring spiral thread of the cobweb structure cushion should be larger than the outer ring radius of the bearing.
where r is the outer ring radius of the bearing, the value of r is 90 mm.
The total width of all radial threads of the cobweb structure should be less than the length of the center of the web structure, and the width of the radial threads must be less than the side length of the outermost regular polygon of the outermost ring of the cobweb structure.
( ) (6) Considering the actual situation, the distance between the two adjacent spiral threads of the cobweb in nature is 5-15 mm. Therefore, the distance between the two spiral threads of the cobweb structure cushion is 5-15 mm [31]. According to the micro-element analysis, the overall normal stress of the cobweb structure is given by: According to Equation (1), the larger the contact area, the smaller the stress. Therefore, the stress on the cobweb structure is smaller when the upper surface is larger. Further, shortening the total length of the cobweb structure cushion aids in reducing the waste of raw materials and overall costs. Therefore, maximizing the surface area and minimizing the total length are considered the optimization objectives.
Therefore, the optimization objectives can be formulated as: minC = n 1 n 2 d(n 2 sin θ + sin θ + 1) + 2R(n 1 n 2 sin θ + π) + 1 2 cos θ (n 1 d − 2n 1 n 2 t 1 ) − n 1 t 2 2 (2) maxS = n 1 n 2 t 2 d sin θ(n 2 + 1) + n 1 t 1 t 2 2 cos θ (1 − cos θ − 2n 2 ) + n 1 n 2 (t 1 d + 2Rt 2 sin θ) + 2πRt 2 where C is the total length of cobweb structure, S is the surface area of cobweb structure, n 1 is the number of radial threads, and n 2 is the number of the spiral threads. We have: The cobweb cushion plays a protective role at the bottom of the bearing. Therefore, the inner connection radius of the outermost ring spiral thread of the cobweb structure cushion should be larger than the outer ring radius of the bearing.
[R + n 2 d + t 2 /(2 cos θ)] cos θ > r where r is the outer ring radius of the bearing, the value of r is 90 mm. The total width of all radial threads of the cobweb structure should be less than the length of the center of the web structure, and the width of the radial threads must be less than the side length of the outermost regular polygon of the outermost ring of the cobweb structure.
2(R + t 2 /2) sin θ > t 1 (6) Considering the actual situation, the distance between the two adjacent spiral threads of the cobweb in nature is 5-15 mm. Therefore, the distance between the two spiral threads of the cobweb structure cushion is 5-15 mm [31].
According to the literature [32], when the stiffness hg (stiffness refers to the ability of a material or structure to resist elastic deformation when subjected to force) ratio between the spiral thread and the radial thread is 1:10, the cushioning capacity is excellent. The height of the spiral thread and radial thread is the same in the cobweb cushion structure. Therefore, the width ratio between spiral and radial threads is 1: 10, written as follows: The structure of a cobweb is a network structure, so the number of radial threads must be greater than or equal to three. Therefore, we get: The centerline of the cobweb structure cushion passes through the inner ring of the bearing and the radial threads bear the cobweb structure cushion. To save material cost, the spiral thread width must be less than 1 mm.

Optimization of Structural Parameters of Cobweb Bionic Cushion
We introduced the above optimization objectives and constraints into the mathematical modeling software and solved the structure parameters using the max-min method. The solution process is illustrated in Figure 5 below. According to the literature [32], when the stiffness hg (stiffness refers to the ability of a material or structure to resist elastic deformation when subjected to force) ratio between the spiral thread and the radial thread is 1:10, the cushioning capacity is excellent. The height of the spiral thread and radial thread is the same in the cobweb cushion structure. Therefore, the width ratio between spiral and radial threads is 1: 10, written as follows: The structure of a cobweb is a network structure, so the number of radial threads must be greater than or equal to three. Therefore, we get: The centerline of the cobweb structure cushion passes through the inner ring of the bearing and the radial threads bear the cobweb structure cushion. To save material cost, the spiral thread width must be less than 1 mm.

Optimization of Structural Parameters of Cobweb Bionic Cushion
We introduced the above optimization objectives and constraints into the mathematical modeling software and solved the structure parameters using the max-min method. The solution process is illustrated in Figure 5 below.  Figure 5. Flow chart of structure parameter solution.
In this study, the outer ring diameter was 90 mm, and the inner ring diameter was 65 mm. To save the material cost, the radius of the centerline of the cobweb was equal to the radius of the inner ring of the test bearing, and the radius R of the centerline of the cobweb was 65 mm. The value of radial thread number n1, spiral thread number n2, spiral thread centerline spacing d, radial thread width t1, and spiral thread width t2 are 7, 2, 17, 20, and 2 mm, respectively.

Calculation of Cushion Thickness of Cobweb Structure
The mass of the test aero bearing was 2.2 kg, and its brittleness value Gc was 120 G [33]. Based on the product drop test height standard in ASTM D 4169 (Standard of American Society for Material Testing) [34], the drop height H was determined to be 381 mm. In this study, the outer ring diameter was 90 mm, and the inner ring diameter was 65 mm. To save the material cost, the radius of the centerline of the cobweb was equal to the radius of the inner ring of the test bearing, and the radius R of the centerline of the cobweb was 65 mm. The value of radial thread number n 1 , spiral thread number n 2 , spiral thread centerline spacing d, radial thread width t 1 , and spiral thread width t 2 are 7, 2, 17, 20, and 2 mm, respectively.

Calculation of Cushion Thickness of Cobweb Structure
The mass of the test aero bearing was 2.2 kg, and its brittleness value Gc was 120 G [33]. Based on the product drop test height standard in ASTM D 4169 (Standard of American Society for Material Testing) [34], the drop height H was determined to be 381 mm.
HL-1029 is a low-viscosity, two-component, and highly transparent silicone potting adhesive that can be cured at room temperature. It is widely employed in the potting and sealing of precision electronic components and can be used as a raw material for bearing cushions. In the experiment, the test aviation bearing is placed flat on the HL-1029 silicone rubber cushion pad. The cushioned area A received by the aviation bearing is the contact area between the annular part between the outer ring and the inner ring and the cushion pad. By the software simulation, the value of A is found to be 0.0034 m 2 . The maximum stress acting on the cushion pad is given by: where W is the bearing mass. The stress-buffer coefficient curve of the HL-1029 silica gel material is shown in Figure 6. HL-1029 is a low-viscosity, two-component, and highly transparent silicone potting adhesive that can be cured at room temperature. It is widely employed in the potting and sealing of precision electronic components and can be used as a raw material for bearing cushions. In the experiment, the test aviation bearing is placed flat on the HL-1029 silicone rubber cushion pad. The cushioned area A received by the aviation bearing is the contact area between the annular part between the outer ring and the inner ring and the cushion pad. By the software simulation, the value of A is found to be 0.0034 m 2 . The maximum stress acting on the cushion pad is given by: where W is the bearing mass.  By fitting the curve in Figure 6, when the stress is 0.777 MPa, the corresponding buffer coefficient is 0.556 MPa. Using Equation (12) the thickness of the cobweb cushion is calculated to be 2 mm.
Therefore, the minimum thickness of the cobweb cushion was 2 mm to meet the buffering requirement. To more intuitively observe the damaged state of the cobweb cushion after the drop, prevent the bearing from causing greater damage due to the error of theoretical calculation and practical test, and improve the safety protection ability of the cobweb cushion structure for the bearing. We finally determined a safety factor is 9, and the thickness of the cobweb cushion structure is finally determined to be 18 mm.

Simulation
Using the structural parameters obtained from the above analysis, we can draw a 3D model of the cobweb structure cushion in the 3D software (2018 X 64), as shown in Figure  7. By fitting the curve in Figure 6, when the stress is 0.777 MPa, the corresponding buffer coefficient is 0.556 MPa. Using Equation (12) the thickness of the cobweb cushion is calculated to be 2 mm.
Therefore, the minimum thickness of the cobweb cushion was 2 mm to meet the buffering requirement. To more intuitively observe the damaged state of the cobweb cushion after the drop, prevent the bearing from causing greater damage due to the error of theoretical calculation and practical test, and improve the safety protection ability of the cobweb cushion structure for the bearing. We finally determined a safety factor is 9, and the thickness of the cobweb cushion structure is finally determined to be 18 mm.

Simulation
Using the structural parameters obtained from the above analysis, we can draw a 3D model of the cobweb structure cushion in the 3D software (2018 X 64), as shown in Figure 7. Based on the international drop test standards, the drop test heights was 381 mm. In addition, we also selected two drop test heights, 610 mm and 700 mm, as comparison groups. Therefore, the initial speeds were 2.773 m/s, 3.458 m/s, and 3.704 m/s, respectively, and the contact type of the bearing and the cobweb cushion were bonded. Bearing steel Based on the international drop test standards, the drop test heights was 381 mm. In addition, we also selected two drop test heights, 610 mm and 700 mm, as comparison groups. Therefore, the initial speeds were 2.773 m/s, 3.458 m/s, and 3.704 m/s, respectively, and the contact type of the bearing and the cobweb cushion were bonded. Bearing steel had a density of 7800 kg/m 3 , Young's modulus of 210 GPa, and Poisson's ratio of 0.3. The cobweb structure cushion was made of silicone HL-1029, with a density of 970 kg/m 3 and a time length of 0.05 s. These were the parameters chosen for the tests.
Therefore, the display dynamics module was chosen as the solver of the simulation experiment. The entire test model included three parts: bearing, cobweb structure cushion, and rigid ground. To shorten the simulation solution time and simplify the simulation solution process, we adopt the simulation software to automatically divide the mesh, and the number of nodes divided is 9834 and the number of elements is 9496. In addition, the maximum factor of element quality is 0.99, which is very close to 1, indicating that the meshing meets the requirements. The drop state of the test bearing and cobweb structure cushion in the finite element environment is shown in Figure 8. Based on the international drop test standards, the drop test heights was 381 mm. In addition, we also selected two drop test heights, 610 mm and 700 mm, as comparison groups. Therefore, the initial speeds were 2.773 m/s, 3.458 m/s, and 3.704 m/s, respectively, and the contact type of the bearing and the cobweb cushion were bonded. Bearing steel had a density of 7800 kg/m 3 , Young's modulus of 210 GPa, and Poisson's ratio of 0.3. The cobweb structure cushion was made of silicone HL-1029, with a density of 970 kg/m 3 and a time length of 0.05 s. These were the parameters chosen for the tests.
Therefore, the display dynamics module was chosen as the solver of the simulation experiment. The entire test model included three parts: bearing, cobweb structure cushion, and rigid ground. To shorten the simulation solution time and simplify the simulation solution process, we adopt the simulation software to automatically divide the mesh, and the number of nodes divided is 9834 and the number of elements is 9496. In addition, the maximum factor of element quality is 0.99, which is very close to 1, indicating that the meshing meets the requirements. The drop state of the test bearing and cobweb structure cushion in the finite element environment is shown in Figure 8. The equivalent stress nephogram of the three drop heights is shown in Figure 9. From Figure 9, the largest equivalent stress appears at the bottom of the bearing outer ring. With an increase in the distance from the ground, the stress on the bearing gradually increases, and the bearing has no plastic deformation and damage even at maximum stress, as shown in Figure 10. The equivalent stress nephogram of the three drop heights is shown in Figure 9. From Figure 9, the largest equivalent stress appears at the bottom of the bearing outer ring. With an increase in the distance from the ground, the stress on the bearing gradually increases, and the bearing has no plastic deformation and damage even at maximum stress, as shown in Figure 10.  With an increase in the drop height, the maximum stress on the bearing gradually increases. Because the limit range of the annealed yield strength of the test bearing materials is 353-382 MPa, the maximum stress at the three drop heights is far less than the yield strength. Figure 12 shows the cloud map of the equivalent stress on the cobweb cushion at the three drop heights. It can be seen from these images that the cobweb structure cushion is damaged, and the maximum equivalent stress occurs at the bottom of the cushion. The enlarged nephogram of maximum equivalent stress is shown in Figure 13. With an increase in the drop height, the maximum stress on the bearing gradually increases. Because the limit range of the annealed yield strength of the test bearing ma- terials is 353-382 MPa, the maximum stress at the three drop heights is far less than the yield strength. Figure 12 shows the cloud map of the equivalent stress on the cobweb cushion at the three drop heights. It can be seen from these images that the cobweb structure cushion is damaged, and the maximum equivalent stress occurs at the bottom of the cushion. The enlarged nephogram of maximum equivalent stress is shown in Figure 13. The equivalent stress curve of the cobweb structure cushion is shown in Figure 14. For the drop height of 381 mm, the maximum equivalent stress was 0.668 MPa at 0.015 s. For the drop height of 610 mm, the maximum equivalent stress was 0.950 MPa at 0.015 s. For the drop height of 700 mm, the maximum equivalent stress was 2.063 MPa at 0.01 s. Figure 13. Enlarged nephogram of maximum equivalent stress when cobweb cushion is dropped from the three drop heights: (a) Enlarged nephogram of maximum equivalent stress when cobweb cushion is dropped from 381 mm; (b) Enlarged nephogram of maximum equivalent stress when cobweb cushion is dropped from 610 mm; (c) Enlarged nephogram of maximum equivalent stress when the cobweb cushion is dropped from 700 mm.
The equivalent stress curve of the cobweb structure cushion is shown in Figure 14. Accordingly, with an increase in the dropping height, the maximum stress of the cobweb structure cushion increases gradually, and the yield strength limit of HL-1029, which is used for the cobweb cushion, is 0.265 MPa, according to the constitutive relation, which is beyond the yield strength of the cobweb structure cushion. Therefore, the cushion was damaged.
Through the analysis of the simulation results, we believe that when the cobweb cushion structure is impacted, the radial threads will be squeezed out to both sides due to the action of the impact force, resulting in the phenomenon of "Bulging", as shown in Figure 15, due to the deformation of the radial threads, the spiral threads is subjected to pressure from the radial threads on both sides pointing to the center of the spiral threads which may cause the spiral threads to break due to too much extrusion force and absorb energy, as shown in Figure 16. Accordingly, with an increase in the dropping height, the maximum stress of the cobweb structure cushion increases gradually, and the yield strength limit of HL-1029, which is used for the cobweb cushion, is 0.265 MPa, according to the constitutive relation, which is beyond the yield strength of the cobweb structure cushion. Therefore, the cushion was damaged.
Through the analysis of the simulation results, we believe that when the cobweb cushion structure is impacted, the radial threads will be squeezed out to both sides due to the action of the impact force, resulting in the phenomenon of "Bulging", as shown in Figure 15, due to the deformation of the radial threads, the spiral threads is subjected to pressure from the radial threads on both sides pointing to the center of the spiral threads which may cause the spiral threads to break due to too much extrusion force and absorb energy, as shown in Figure 16.

Preparation of the Cobweb Structure Cushion Material Cast
To obtain the cobweb cushion, we must make the shell of the cushion, develop the 3D model of the shell in 3D software, and print it using 3D printing technology [35,36]. The shell is now divided into three parts for convenience in printing and stripping. It is then assembled into a cast of HL-1029, as shown in Figure 17. During casting, materials A and B were mixed evenly with a mass ratio of 1:1. The mixed material was slowly injected into the shell to prevent any bubbles. After allowing it to rest at room temperature for 24 h, it was unmolded to obtain the cobweb structure cushion, as shown in Figure 18. The casting conditions of the HL-1029 silicone are listed in Table 1.

Preparation of the Cobweb Structure Cushion Material Cast
To obtain the cobweb cushion, we must make the shell of the cushion, develop th 3D model of the shell in 3D software, and print it using 3D printing technology [35,36 The shell is now divided into three parts for convenience in printing and stripping. It then assembled into a cast of HL-1029, as shown in Figure 17. During casting, materials A and B were mixed evenly with a mass ratio of 1:1. Th mixed material was slowly injected into the shell to prevent any bubbles. After allowin it to rest at room temperature for 24 h, it was unmolded to obtain the cobweb structur cushion, as shown in Figure 18. The casting conditions of the HL-1029 silicone are liste in Table 1.

Preparation of the Cobweb Structure Cushion Material Cast
To obtain the cobweb cushion, we must make the shell of the cushion, develop the 3D model of the shell in 3D software, and print it using 3D printing technology [35,36]. The shell is now divided into three parts for convenience in printing and stripping. It is then assembled into a cast of HL-1029, as shown in Figure 17.

Preparation of the Cobweb Structure Cushion Material Cast
To obtain the cobweb cushion, we must make the shell of the cushio 3D model of the shell in 3D software, and print it using 3D printing tech The shell is now divided into three parts for convenience in printing and then assembled into a cast of HL-1029, as shown in Figure 17. During casting, materials A and B were mixed evenly with a mass r mixed material was slowly injected into the shell to prevent any bubbles. it to rest at room temperature for 24 h, it was unmolded to obtain the cob cushion, as shown in Figure 18. The casting conditions of the HL-1029 sili in Table 1. During casting, materials A and B were mixed evenly with a mass ratio of 1:1. The mixed material was slowly injected into the shell to prevent any bubbles. After allowing it to rest at room temperature for 24 h, it was unmolded to obtain the cobweb structure cushion, as shown in Figure 18. The casting conditions of the HL-1029 silicone are listed in Table 1.

Test Methods and Equipment Required
The standard drop height was obtained according to the relevant provisions in ASTM D 4169 (Standard of American Society for Material Testing). The bearing was placed above the cushion and glued to it. An acceleration sensor was placed on the surface of the test samples. Then, the bearing was placed on the table of the drop-testing machine and fixed with a fixed rod. The test table was raised to the set height to make the test piece drop freely. The impact acceleration of the bearing was recorded as it touched the ground. Next, the drop height was re-adjusted, and the test was repeated. Finally, the impact acceleration of the bearing at different drop heights was compared.
The equipment required for the drop test includes a data collector, acceleration sensor, and DJ-100B single-arm drop machine, as shown in Figure 19. The bearing and cobweb structure cushion is shown in Figure 20.

Test Methods and Equipment Required
The standard drop height was obtained according to the relevant provisions in ASTM D 4169 (Standard of American Society for Material Testing). The bearing was placed above the cushion and glued to it. An acceleration sensor was placed on the surface of the test samples. Then, the bearing was placed on the table of the drop-testing machine and fixed with a fixed rod. The test table was raised to the set height to make the test piece drop freely. The impact acceleration of the bearing was recorded as it touched the ground. Next, the drop height was re-adjusted, and the test was repeated. Finally, the impact acceleration of the bearing at different drop heights was compared.
The equipment required for the drop test includes a data collector, acceleration sensor, and DJ-100B single-arm drop machine, as shown in Figure 19. The bearing and cobweb structure cushion is shown in Figure 20.

Test Methods and Equipment Required
The standard drop height was obtained according to the relevant provisions in ASTM D 4169 (Standard of American Society for Material Testing). The bearing was placed above the cushion and glued to it. An acceleration sensor was placed on the surface of the test samples. Then, the bearing was placed on the table of the drop-testing machine and fixed with a fixed rod. The test table was raised to the set height to make the test piece drop freely. The impact acceleration of the bearing was recorded as it touched the ground. Next, the drop height was re-adjusted, and the test was repeated. Finally, the impact acceleration of the bearing at different drop heights was compared.
The equipment required for the drop test includes a data collector, acceleration sensor, and DJ-100B single-arm drop machine, as shown in Figure 19. The bearing and cobweb structure cushion is shown in Figure 20.

Analysis of the Test Results
The test was divided into three groups according to the drop height of the test. Each group was tested several times. Finally, the most representative four data of each group from tests were considered for analysis. The bearing with and without the HL-1029 cushion package was tested for drop heights of 381 mm, 610 mm, and 700 mm, respectively. The thickness of the cobweb structure cushion was 18 mm. The impact acceleration curves with and without the cushion for the drop height of 610 mm are shown in Figure 21 and Figure 22, respectively.

Analysis of the Test Results
The test was divided into three groups according to the drop height of the test. Each group was tested several times. Finally, the most representative four data of each group from tests were considered for analysis. The bearing with and without the HL-1029 cushion package was tested for drop heights of 381 mm, 610 mm, and 700 mm, respectively. The thickness of the cobweb structure cushion was 18 mm. The impact acceleration curves with and without the cushion for the drop height of 610 mm are shown in Figures 21 and 22, respectively.

Analysis of the Test Results
The test was divided into three groups according to the drop height of the test. Each group was tested several times. Finally, the most representative four data of each group from tests were considered for analysis. The bearing with and without the HL-1029 cushion package was tested for drop heights of 381 mm, 610 mm, and 700 mm, respectively. The thickness of the cobweb structure cushion was 18 mm. The impact acceleration curves with and without the cushion for the drop height of 610 mm are shown in Figure 21 and Figure 22, respectively.

Analysis of the Test Results
The test was divided into three groups according to the drop height of the test. Each group was tested several times. Finally, the most representative four data of each group from tests were considered for analysis. The bearing with and without the HL-1029 cushion package was tested for drop heights of 381 mm, 610 mm, and 700 mm, respectively. The thickness of the cobweb structure cushion was 18 mm. The impact acceleration curves with and without the cushion for the drop height of 610 mm are shown in Figure 21 and Figure 22, respectively.   Because the impact acceleration generated by a 700 mm drop height is beyond the sensor range when there is no cushion, it cannot be tested. The bearing drop test data without a cushion, histogram of the bearing drop impact acceleration and histogram of average impact acceleration are shown in Table 2, Figures 23 and 24, respectively. As shown in Figure 23, the maximum impact accelerations of the two drop heights without cushion are 1546.326 m/s 2 and 2147.737 m/s 2 , respectively. It can be seen from the table that the average impact acceleration of the two drop heights without cushion is 1356.675 m/s 2 and 1880.545 m/s 2 , respectively. All the above values exceed the brittle value of 120 G of the bearing. Therefore, the bearing is easily damaged without a cushion. Because the impact acceleration generated by a 700 mm drop height is bey sensor range when there is no cushion, it cannot be tested. The bearing drop without a cushion, histogram of the bearing drop impact acceleration and histo average impact acceleration are shown in Table 2, Figure 23 and Figure 24, resp As shown in Figure 23, the maximum impact accelerations of the two drop heigh out cushion are 1546.326 m/s 2 and 2147.737 m/s 2 , respectively. It can be seen from that the average impact acceleration of the two drop heights without cushion is m/s 2 and 1880.545 m/s 2 , respectively. All the above values exceed the brittle value of the bearing. Therefore, the bearing is easily damaged without a cushion.  The bearing drop test data with the cobweb cushion, histogram of the bear impact acceleration and histogram of average impact acceleration are shown in Because the impact acceleration generated by a 700 mm drop height is bey sensor range when there is no cushion, it cannot be tested. The bearing drop t without a cushion, histogram of the bearing drop impact acceleration and histo average impact acceleration are shown in Table 2, Figure 23 and Figure 24, resp As shown in Figure 23, the maximum impact accelerations of the two drop heigh out cushion are 1546.326 m/s 2 and 2147.737 m/s 2 , respectively. It can be seen from t that the average impact acceleration of the two drop heights without cushion is 1 m/s 2 and 1880.545 m/s 2 , respectively. All the above values exceed the brittle value of the bearing. Therefore, the bearing is easily damaged without a cushion.  The bearing drop test data with the cobweb cushion, histogram of the beari impact acceleration and histogram of average impact acceleration are shown in Figure 25 and Figure 26, respectively. It can be seen that the impact acceler The bearing drop test data with the cobweb cushion, histogram of the bearing drop impact acceleration and histogram of average impact acceleration are shown in Table 3, Figures 25 and 26, respectively. It can be seen that the impact acceleration of bearings with a cobweb structure cushion at three drop heights of 381, 610, and 700 mm is less than the brittleness value of 120 G. bearings with a cobweb structure cushion at three drop heights of 381, 610, and is less than the brittleness value of 120 G.  A histogram comparing the impact acceleration with and without the cobwe ion at the same drop height is shown in Figure 27. The cobweb cushion can eff reduce the impact acceleration of the bearing whenever it is dropped. Biomimetics 2023, 8, x FOR PEER REVIEW bearings with a cobweb structure cushion at three drop heights of 381, 610, and 7 is less than the brittleness value of 120 G.   A histogram comparing the impact acceleration with and without the cobwe ion at the same drop height is shown in Figure 27. The cobweb cushion can eff reduce the impact acceleration of the bearing whenever it is dropped. A histogram comparing the impact acceleration with and without the cobweb cushion at the same drop height is shown in Figure 27. The cobweb cushion can effectively reduce the impact acceleration of the bearing whenever it is dropped. The impact acceleration of different materials cushions at a drop height of 700 mm is shown in Table 4 and Figure 28. It can be seen that the impact acceleration of the bearing with the cobweb structure cushion is 678.375 m/s 2 , the impact acceleration of the bearing with the expanded polyurethane (EPU) cushion is 948.555 m/s 2 , and the impact acceleration of the bearing with the Polydimethylsiloxane (PDMS) cushion is 810.953 m/s 2 . It can be seen from the histogram that the impact acceleration of the bearing is quite different when the three materials are cushioned, and the cobweb cushion with HL-1029 has the best cushioning performance.   The impact acceleration of different materials cushions at a drop height of 700 mm is shown in Table 4 and Figure 28. It can be seen that the impact acceleration of the bearing with the cobweb structure cushion is 678.375 m/s 2 , the impact acceleration of the bearing with the expanded polyurethane (EPU) cushion is 948.555 m/s 2 , and the impact acceleration of the bearing with the Polydimethylsiloxane (PDMS) cushion is 810.953 m/s 2 . It can be seen from the histogram that the impact acceleration of the bearing is quite different when the three materials are cushioned, and the cobweb cushion with HL-1029 has the best cushioning performance.  The impact acceleration of different materials cushions at a drop height of 700 mm is shown in Table 4 and Figure 28. It can be seen that the impact acceleration of the bearing with the cobweb structure cushion is 678.375 m/s 2 , the impact acceleration of the bearing with the expanded polyurethane (EPU) cushion is 948.555 m/s 2 , and the impact acceleration of the bearing with the Polydimethylsiloxane (PDMS) cushion is 810.953 m/s 2 . It can be seen from the histogram that the impact acceleration of the bearing is quite different when the three materials are cushioned, and the cobweb cushion with HL-1029 has the best cushioning performance.

Methods
In this paper, we analyze the cobweb structure cushion theoretically and experimentally, and the method's process is as follows: (1) A method of using organic silica gel as a cushion for aviation precision bearing packaging is proposed, and the structure of the cushion is designed based on a cobweb configuration.
(2) By increasing the structural parameters of the radial thread as a bearing force carrier, the minimum cushion thickness was calculated and designed. The theoretical calculation accuracy was verified by conducting simulation analysis. (3) Using finite element software, drop simulations were carried out on a high-precision bearing packed with a biomimetic cobweb structure cushion, and stress cloud maps of the bearing and cushion were obtained. (4) The biomimetic cobweb structure cushion casting was carried out using a 3D printed cobweb cushion shell. The impact acceleration of the bearing was obtained using a drop test.

Conclusions
A new biomimetic cobweb cushion is proposed to solve the problem of insufficient cushioning capacity of high-precision bearing cushion packaging pads. the results can be summarized as follows: (1) The structural parameters of the cobweb structure cushion were solved by the optimization equation, and then the thickness is 18 mm according to the actual situation. (2) Analysis and processing of the drop test results show that at a drop height of 381 mm and 610 mm, the impact acceleration of the bearing with a cobweb structure cushion is reduced by 86% and 78%, respectively, compared with the without cobweb structure cushion. At a drop height of 700 mm, the impact acceleration of the bearing with the HL-1029 cushion is reduced by 28% and 16% compared with the EPU cushion and PDMS cushion, respectively. (3) The test results showed that the biomimetic cobweb structure cushion could provide robust protection for high-precision bearings.