Shock absorber with high shock absorption performance

Abstract

The invention discloses a shock absorber with high shock absorption performance, and relates to the technical field of shock absorbers, a piston rod module comprises a piston rod body and a main piston valve system, the piston rod body is hollow, and hydraulic oil in an oil storage barrel module can enter a nitrogen barrel module through an internal flow channel of the piston rod body and an oil passing hole in a connecting seat; the piston rod body comprises a first connecting section, a middle section and a second connecting section, the first connecting section and the second connecting section are located at the two ends of the middle section correspondingly, and the first connecting section, the middle section and the second connecting section are hollow and sequentially communicate with one another; the two quenching transition sections are integrally connected to the two ends of the quenching section respectively, the first connecting section is used for being connected with a main piston valve system, the first connecting section is subjected to flash plating treatment, and an anti-rust oil coating is arranged on the periphery of the second connecting section. The rigidity of the piston rod body can be improved, the service life is prolonged, and safety is improved.

Description

Technical Field

[0001] This invention relates to the field of vibration damper technology, and in particular to a vibration damper with high vibration damping performance. Background Technology

[0002] Existing shock absorbers typically cannot adaptively adjust the fluid flow resistance according to actual operating conditions, resulting in poor vehicle adaptability and an inability to adapt to different operating conditions. Furthermore, the piston rod stiffness of existing shock absorbers is insufficient, which means that under extreme driving conditions, they cannot provide enough strength to ensure vehicle stability and safety. This not only affects vehicle handling and ride comfort but may also lead to premature shock absorber failure, increasing vehicle maintenance costs and safety hazards.

[0003] Especially in racing and high-performance vehicle applications, insufficient piston rod stiffness can severely impact the reliability of shock absorbers and the overall vehicle dynamics. When a vehicle is subjected to high-frequency impacts, severe lateral loads, or continuous high-intensity compression and rebound under extreme conditions, a piston rod with insufficient stiffness is prone to bending and deformation, leading to uneven wear of seals, oil leakage, and even inducing resonance, accelerating the risk of fatigue fracture. This not only weakens the damping stability of the shock absorber, causing inaccurate vehicle attitude control, but also reduces tire contact performance, affecting driver feedback. Furthermore, seal failures and fluctuations in support force due to piston rod deformation or fracture significantly shorten the shock absorber's lifespan, forcing teams to frequently replace components, increasing maintenance costs and safety hazards. Summary of the Invention

[0004] The purpose of this invention is to provide a vibration damper with high vibration reduction performance to solve the problems existing in the prior art, improve the stiffness of the piston rod body, extend its service life, and improve safety.

[0005] To achieve the above objectives, the present invention provides the following solution: This invention provides a high-performance vibration damper, comprising a nitrogen cylinder module, an oil reservoir module, a piston rod module, and a connecting seat. The piston rod module includes a piston rod body and a main piston valve system. The piston rod body is hollow, and hydraulic oil in the oil reservoir module can enter the nitrogen cylinder module through the internal flow channel of the piston rod body and the oil passage hole on the connecting seat. The piston rod body includes a first connecting section, an intermediate section, and a second connecting section. The first connecting section and the second connecting section are located at opposite ends of the intermediate section, and all three sections are hollow and sequentially connected. The intermediate section includes a quenching section and two quenching transition sections, which are integrally connected to the opposite ends of the quenching section. The first connecting section is used to connect the main piston valve system and is flash-plated. The outer periphery of the second connecting section is coated with an anti-rust oil coating.

[0006] Preferably, the system further includes a buffer elastic module. The first end of the nitrogen cylinder module is connected to the first end of the connecting seat, and the second end of the connecting seat is connected to the first end of the piston rod module. The nitrogen cylinder module contains a floating piston assembly, and the nitrogen cylinder module is used to store nitrogen on one side corresponding to the floating piston assembly. The nitrogen cylinder module is used to introduce hydraulic oil on the other side corresponding to the floating piston assembly. The first end of the piston rod module is used to connect to the suspension, and the second end of the piston rod module extends through the first end of the oil reservoir module into the oil reservoir module and connects to the buffer elastic module. The buffer elastic module includes a mounting seat, a first elastic element, and a buffer sleeve disposed within the oil reservoir module. The first elastic element is located between the second end of the oil reservoir module and the mounting seat. Both the mounting seat and the buffer sleeve are slidably connected to the inner wall of the oil reservoir module. The buffer sleeve is connected to the second end of the piston rod module. A fluid flow channel can be formed between the mounting seat and the buffer sleeve. Under the action of the piston rod module, the buffer sleeve contacts the mounting seat and can close the fluid flow channel.

[0007] Preferably, the nitrogen cylinder module includes a nitrogen cylinder and the floating piston assembly. The nitrogen cylinder is a hollow cylindrical shell. The floating piston assembly is slidably connected inside the nitrogen cylinder, and the outer side wall of the floating piston assembly can contact the inner side wall of the nitrogen cylinder. The first end of the nitrogen cylinder is threadedly connected to the connecting seat.

[0008] Preferably, the oil reservoir module includes an oil reservoir, a lower spring, an upper spring, and a spring transition seat. The oil reservoir is used to store hydraulic oil. The spring transition seat is installed on the outer periphery of the oil reservoir and is located near the first end of the oil reservoir module. The lower spring is sleeved on the outer periphery of the oil reservoir, and the first end of the lower spring abuts against one side of the spring transition seat. The second end of the lower spring abuts against a protrusion on the outer wall of the oil reservoir. The upper spring is sleeved on the outer periphery of the piston rod module, and the first end of the upper spring abuts against one side of the connecting seat. The second end of the upper spring abuts against the other side of the spring transition seat.

[0009] Preferably, the second end of the oil reservoir is detachably connected to a fixing cap, and the fixing cap is coaxially arranged with the oil reservoir. The fixing cap is provided with a first limiting protrusion, and the first limiting protrusion and the second end of the oil reservoir form a first limiting groove. One end of the first elastic element is located in the first limiting groove. The first limiting protrusion is used to limit the axial position of the first elastic element, and the first limiting groove is used to limit the radial position of the first elastic element. The mounting base is provided with a second limiting protrusion, and the second limiting protrusion forms a second limiting groove. The other end of the first elastic element is located in the second limiting groove. The second limiting protrusion is used to limit the axial position of the first elastic element, and the second limiting groove is used to limit the radial position of the first elastic element.

[0010] Preferably, the oil reservoir, the first elastic element, the mounting base, and the buffer sleeve are all coaxially arranged, and a sealing structure is provided between the mounting base and the oil reservoir, and between the buffer sleeve and the oil reservoir; the end of the buffer sleeve facing the mounting base is also provided with a conical sealing surface, and under the action of the piston rod module, the cross-sectional size of the fluid flow channel gradually decreases during the movement of the buffer sleeve toward the mounting base.

[0011] Preferably, the buffer elastic module further includes at least two second elastic elements, each of which is located between the mounting base and the buffer sleeve, and the plurality of second elastic elements are evenly distributed along the circumference of the mounting base.

[0012] Preferably, the main piston valve system is located inside the oil reservoir module and is installed at the second end of the piston rod body. The buffer sleeve is located on one side of the main piston valve system. The piston rod body is provided with an oil passage for the passage of hydraulic oil.

[0013] Preferably, the flash coating thickness on the outer surface of the first connecting section is 3µm-5µm; the intermediate section is made of 45# steel, and the quenched section is induction hardened and tempered during processing. The surface hardness of the induction hardened section is 50HRC~55HRC, the depth of the hardened layer is 1.2mm~1.6mm, and the depth of the hardened layer is up to 350HV1. The outer surface of the intermediate section is hard chrome plated, and the hardness of the hard chrome plating layer is in the range of 900HV-1200HV. The number of microcracks in the plating layer is 800fsi / cm²-1300fsi / cm², and the microcracks are distributed in a network. After chrome plating, the plating layer is held at 200℃-220℃ for 2 hours, and the thickness of the polished plating layer is 45±5µm.

[0014] Preferably, the connecting seat is further provided with a compression regulating valve, which is used to regulate the flow resistance of hydraulic oil passing through the oil passage. A spherical bearing is provided at the second end of the connecting seat, and the connecting seat is used to connect the suspension through the spherical bearing. A springback regulating valve is also provided on one side of the connecting seat, and the hydraulic oil inside the piston rod module can flow into the oil passage of the connecting seat through the springback regulating valve. The connecting seat is made of 7075 aluminum alloy, and the mass percentage of each component in the 7075 aluminum alloy is Si (0~0.4%), Fe (0~0.5%), Cu (1.2%~2.0%), Mn (0~0.3%), Mg (2.1%~2.9%), Cr (0.18%~0.28%), Zn (5.1%~6.1%), Ti (0~0.2%), with the remainder being Al and impurities.

[0015] Compared with the prior art, the present invention has achieved the following technical effects: The present invention provides a high-performance vibration damper, comprising a nitrogen cylinder module, an oil reservoir module, a piston rod module, and a connecting seat. The piston rod body is hollow, and the hydraulic oil in the oil reservoir module can enter the nitrogen cylinder module through the internal flow channel of the piston rod body and the oil passage hole on the connecting seat. The flow of hydraulic oil achieves gas elastic energy storage and oil-gas separation, resulting in smoother shock absorption. The nitrogen pressure can be adjusted as needed to adapt to different road conditions, exhibiting good adaptability and vibration damping effect. Furthermore, the hollow design of the piston rod body reduces weight while maintaining necessary strength and rigidity, extending service life and improving safety. It also reduces the overall mass of the high-performance vibration damper, minimizing unnecessary material costs. The piston rod body includes a first connecting section, an intermediate section, and a second connecting section, located at opposite ends of the intermediate section. The first section and the second connecting section are both hollow and connected sequentially. The second section includes a quenched section and two quenched transition sections, which are integrally connected to both ends of the quenched section. The quenching process improves the material's hardness and wear resistance, thereby ensuring that the piston rod body can withstand repeated stretching, compression, and friction during vibration damping, extending the service life of the piston rod body and preventing deformation or wear due to excessive force. At the same time, the quenched transition sections avoid stress concentration caused by direct connection between the quenched and unquenched sections, thus eliminating stress differences and ensuring the structural stability of the entire piston rod body. The first connecting section is used to connect the main piston valve system and is flash-plated, which provides corrosion protection without affecting the assembly accuracy with other components. The outer periphery of the second connecting section is coated with an anti-rust oil coating to reduce friction between the second connecting section and other components, serving both anti-rust and lubrication purposes. Attached Figure Description

[0016] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0017] Figure 1 This is a partial cross-sectional view of the high-damping-performance vibration damper of the present invention; Figure 2 This is a schematic diagram of the internal structure of the oil storage cylinder in this invention; Figure 3 for Figure 2 Enlarged view of point A; Figure 4 for Figure 2 Enlarged view of point B; Figure 5 This is a schematic diagram of the piston rod body in this invention; In the diagram: 1-Buffer elastic module, 10-Conical sealing surface, 11-Mounting seat, 12-First elastic element, 13-Buffer sleeve, 14-Liquid flow channel, 15-Fixing cover, 16-First limiting protrusion, 17-Second limiting protrusion, 18-Sealing structure, 19-Second elastic element, 2-Oil reservoir module, 21-Oil reservoir, 22-Lower end spring, 23-Spring transition seat, 24-Upper end spring, 3-Piston rod module, 31-Piston rod body, 32-Main piston valve system, 4-Connecting seat, 5-Compression regulating valve, 6-Spherical bearing, 7-Rebound regulating valve. Detailed Implementation

[0018] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0019] The purpose of this invention is to provide a vibration damper with high vibration reduction performance to solve the problems existing in the prior art, improve the stiffness of the piston rod body, extend its service life, and improve safety.

[0020] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0021] like Figures 1-5As shown, this embodiment provides a high-performance vibration damper, including a nitrogen cylinder module, an oil reservoir module 2, a piston rod module 3, and a connecting seat 4. The piston rod body 31 is hollow, and the hydraulic oil in the oil reservoir module 2 can enter the nitrogen cylinder module through the oil passage holes on the piston rod module 3 and the connecting seat 4. The flow of hydraulic oil achieves gas elastic energy storage and oil-gas separation, resulting in smoother shock absorption. The nitrogen pressure can be adjusted as needed to adapt to different road conditions, offering good adaptability and vibration damping effect. Furthermore, the hollow design of the piston rod body 31 reduces weight while maintaining necessary strength and rigidity, extending service life and improving safety. It also reduces the overall mass of the high-performance vibration damper, minimizing unnecessary material costs. The piston rod body 31 includes a first connecting section, an intermediate section, and a second connecting section, located at opposite ends of the intermediate section. The connecting section, intermediate section, and second connecting section are all hollow inside and connected sequentially. The intermediate section includes a quenching section and two quenching transition sections, which are integrally connected to both ends of the quenching section. The quenching process improves the hardness and wear resistance of the material, thereby ensuring that the piston rod body 31 can withstand repeated tension, compression, and friction during vibration reduction, extending the service life of the piston rod body 31 and preventing deformation or wear due to excessive force. At the same time, the quenching transition sections can avoid stress concentration caused by direct connection between the quenching section and the unquenched section, thereby eliminating stress difference and ensuring the structural stability of the entire piston rod body 31. The first connecting section is used to connect the main piston valve system 32, and the first connecting section is flash-plated, which can achieve corrosion resistance without affecting the assembly accuracy with other components. The outer periphery of the second connecting section is provided with an anti-rust oil coating to reduce friction between the second connecting section and other components, taking into account both anti-rust and lubrication functions.

[0022] Specifically, this embodiment also includes a buffer elastic module 1. The first end of the nitrogen cylinder module is connected to the first end of the connecting seat 4, and the second end of the connecting seat 4 is connected to the first end of the piston rod module 3. The nitrogen cylinder module has a floating piston assembly inside, and the nitrogen cylinder module is used to store nitrogen on one side of the floating piston assembly, and to introduce hydraulic oil on the other side of the floating piston assembly. The floating piston assembly slides inside the nitrogen cylinder module, so that one side of the floating piston assembly is filled with nitrogen and the other side is connected to hydraulic oil. The gas volume is adjusted by the movement of the floating piston assembly. The first end of the piston rod module 3 is used to connect to the suspension to transmit the suspension impact force. The second end of the piston rod module 3 extends into the oil reservoir module 2 through the first end of the oil reservoir module 2 and is connected to the buffer elastic module 1. Thus, when the piston rod module 3 moves back and forth, it can act on the inside of the oil reservoir module 2. At the same time, the setting of the buffer elastic module 1 can also significantly increase the buffer stroke of the high-damping-performance shock absorber, thereby making the change of the buffer force value smoother and more linear. To improve vibration damping performance and road condition adaptability, the buffer elastic module 1 includes a mounting base 11, a first elastic element 12, and a buffer sleeve 13 disposed within the oil reservoir module 2. The first elastic element 12 is located between the second end of the oil reservoir module 2 and the mounting base 11. Both the mounting base 11 and the buffer sleeve 13 are slidably connected to the inner wall of the oil reservoir module 2. The buffer sleeve 13 is connected to the second end of the piston rod module 3. A fluid flow channel 14 can be formed between the mounting base 11 and the buffer sleeve 13, which significantly increases the oil chamber pressure formed by the oil reservoir module 2, the mounting base 11, and the buffer sleeve 13, forming a high-pressure chamber. This design greatly improves the buffering effect. When subjected to external impact, under the action of the piston rod module 3, the first elastic element 12 can compress or rebound accordingly according to the applied pressure. This characteristic allows the buffer elastic module 1 to evenly distribute impact energy over a long stroke. Compared with traditional buffer designs, this improved method can effectively reduce the occurrence of peak forces, avoid the risk of potential damage to the high-vibration-damping vibration damper, and improve structural stability and safety.

[0023] The nitrogen cylinder module includes a nitrogen cylinder and a floating piston assembly. The floating piston assembly is slidably connected inside the nitrogen cylinder, and its outer wall can contact the inner wall of the nitrogen cylinder, thereby isolating the spaces on both sides of the floating piston assembly and preventing nitrogen from mixing with hydraulic oil. The first end of the nitrogen cylinder is connected to the connecting seat 4 via a thread. The nitrogen cylinder is a hollow cylindrical shell with a smooth and high-pressure resistant inner wall to ensure no nitrogen leakage and to withstand the internal gas pressure. The nitrogen cylinder is made of a high-strength metal material (such as aluminum alloy or steel).

[0024] The oil reservoir module 2 is mainly used to store hydraulic oil, compensate for changes in oil volume, and assist in heat dissipation. It includes an oil reservoir 21, a lower spring 22, an upper spring 24, and a spring transition seat 23. The oil reservoir 21 stores hydraulic oil. The spring transition seat 23 is installed on the outer periphery of the oil reservoir 21, and is positioned close to the first end of the oil reservoir module 2. The lower spring 22 is sleeved on the outer periphery of the oil reservoir 21, with its first end abutting against one side of the spring transition seat 23, and its second end abutting against a protrusion on the outer wall of the oil reservoir 21. The upper spring 24 is sleeved on the outer periphery of the piston rod module 3, and the upper spring 24... The first end abuts against one side of the connecting seat 4, and the connecting seat 4 is provided with a groove for abutting the upper spring 24. The second end of the upper spring 24 abuts against the other side of the spring transition seat 23. Through the above design, the oil reservoir module 2 realizes volume compensation + heat dissipation + filtration, which solves the problems of oil volume change, high temperature and impurity contamination during the operation of the high vibration damper. Together with the nitrogen cylinder and other structures, it ensures the reliability and damping stability of the high vibration damper in high-frequency reciprocating motion. Its structure is simple but its function is critical. Especially under harsh working conditions such as off-road and heavy load, it can play a decisive role in the long-term performance of the high vibration damper.

[0025] The second end of the oil reservoir 21 is detachably connected to a fixing cover 15, and the fixing cover 15 is coaxially arranged with the oil reservoir 21. The fixing cover 15 is provided with a first limiting protrusion 16, and the first limiting protrusion 16 and the second end of the oil reservoir 21 form a first limiting groove. One end of the first elastic element 12 is located in the first limiting groove. The inner wall of the first limiting groove is arc-shaped and matches the shape of the first elastic element 12. The first limiting protrusion 16 is used to limit the axial position of the first elastic element 12, and the first limiting groove is used to limit the radial position of the first elastic element 12. The mounting base 11 is provided with a second limiting protrusion 17, and the second limiting protrusion 17 forms a second limiting groove. The other end of the first elastic element 12 is located in the second limiting groove. The inner wall of the second limiting groove is arc-shaped and matches the shape of the first elastic element 12. The second limiting protrusion 17 is used to limit the axial position of the first elastic element 12, and the second limiting groove is used to limit the radial position of the first elastic element 12. Mounting base 11 serves as the supporting foundation for the first elastic element 12, participating in the transmission and distribution of force. By optimizing the shape of mounting base 11, pressure can be effectively dispersed, reducing localized wear. The fluid flow channel 14 formed by mounting base 11 and buffer sleeve 13 reduces compressive damping force and increases rebound damping force, making the high-performance shock absorber operate more smoothly, avoiding rebound impact, and making vehicle driving more comfortable.

[0026] As a preferred embodiment, the fixing cover 15 is detachably connected to the closed end of the oil reservoir 21 by bolts. The fixing cover 15 is an important structure during installation, which can ensure a stable connection between the first elastic element 12 and the oil reservoir 21.

[0027] The oil reservoir 21, the first elastic element 12, the mounting base 11 and the buffer sleeve 13 are all coaxially arranged, and a sealing structure 18 is provided between the mounting base 11 and the oil reservoir 21, and between the buffer sleeve 13 and the oil reservoir 21, to ensure that the mounting base 11 and the buffer sleeve 13 can seal with the oil reservoir 21 when sliding, so as to avoid oil leakage.

[0028] The buffer sleeve 13 is also provided with a conical sealing surface 10 at the end facing the mounting base 11. Under the action of the piston rod module 3, during the movement of the buffer sleeve 13 toward the mounting base 11, the cross-sectional size of the liquid flow channel 14 gradually decreases, thereby achieving gradual closure. During the movement of the piston rod body 31 in the opposite direction, that is, during the movement of the buffer sleeve 13 away from the mounting base 11, the cross-sectional size of the liquid flow channel 14 gradually increases, thereby achieving gradual opening.

[0029] The buffer elastic module 1 also includes at least two second elastic elements 19, each of which is located between the mounting base 11 and the buffer sleeve 13. The second elastic elements 19 can play a buffering role when the buffer sleeve 13 moves toward the mounting base 11, and can provide elastic force when the buffer sleeve 13 moves away from the mounting base 11, so that the liquid flow channel 14 is opened. The multiple second elastic elements 19 are evenly distributed along the circumference of the mounting base 11, which can provide uniform buffering force and elastic force.

[0030] The main piston valve system 32 is located inside the oil reservoir module 2 and is installed at the second end of the piston rod body 31. The buffer sleeve 13 is located on one side of the main piston valve system 32. The piston rod body 31 has an oil passage for hydraulic oil to pass through. The core function of the piston rod module 3 is to transmit the suspension impact force and ensure the reciprocating motion accuracy of the main piston valve system 32 in the oil reservoir 21. The piston rod module 3 is designed with a high-strength piston rod body 31 and a precision sealing guide as its core design. It serves as a mechanical carrier for force transmission and solves friction, leakage and fatigue problems through surface treatment and structural optimization. Its performance directly affects the response speed (e.g., the lighter the piston rod body 31, the smaller the motion inertia) and service life of the high-damping-performance shock absorber (seal failure will lead to oil leakage and damping force attenuation). It is a key guarantee for the reliability of high-damping-performance shock absorbers under harsh conditions such as off-road and racing.

[0031] The flash coating thickness on the outer surface of the first connecting section is 3µm-5µm; the middle section is made of 45# steel, and the quenched section is induction hardened and tempered during processing. As a preferred embodiment, the surface hardness of the induction hardened section is 50HRC~55HRC, the depth of the hardened layer is 1.2mm~1.6mm, and the depth of the hardened layer is up to 350HV1. The outer surface of the middle section is hard chrome plated, and the hardness of the hard chrome plating layer is in the range of 900HV-1200HV. The number of microcracks in the plating layer is 800fsi / cm²-1300fsi / cm², and the microcracks are distributed in a network. After chrome plating, it is held at 200℃-220℃ for 2 hours (to remove hydrogen), and the thickness of the plating layer after polishing is 45±5µm. This embodiment employs a "micro-cracked chromium" process, combined with a dehydrogenation treatment (baking to remove hydrogen), which improves corrosion resistance, enhances bonding strength, and prevents hydrogen embrittlement failure, thereby ensuring the reliability of the high-damping-performance vibration damper under long-term vibration, humidity, and salt spray environments. See Table 1 below for a comparison between the micro-cracked chromium plating process and the ordinary chromium plating process in this embodiment.

[0032] Table 1 Comparison between micro-crack chrome plating process and ordinary chrome plating process The connecting seat 4 is also equipped with a compression regulating valve 5. The compression regulating valve 5 is used to adjust the flow resistance of the hydraulic oil passing through the oil passage, and then adjust the damping force by controlling the flow resistance of the hydraulic oil in the compression stroke. When the throttling area is smaller, the oil flow resistance is greater and the compression damping force is stronger, which can be used for off-road and other application scenarios that require strong damping to suppress vehicle body sinking. When the throttling area is larger, the damping force is weaker, which can be used for highway driving and other application scenarios that require gentle buffering, thus improving the applicability range.

[0033] A spherical bearing 6 is provided at the second end of the connecting seat 4. The connecting seat 4 is used to connect the suspension through the spherical bearing 6. A springback regulating valve 7 is also provided on one side of the connecting seat 4. The hydraulic oil inside the piston rod module 3 can flow into the oil passage hole of the connecting seat 4 through the springback regulating valve 7. Preferably, there are multiple oil passage holes. Furthermore, in this embodiment, for the connection design between the connecting seat 4 and other structures, the optimal locking torque value at the joint between the connecting seat 4 and other components needs to be accurately calculated and set to ensure a tight fit between the components and reduce the risk of loosening or slippage. The locking torque is calibrated using special tools to ensure the consistency and reliability of the assembly quality. By constructing a global locking torque collaborative calculation, the locking torque rectangle at each joint point is made into a self-consistent stress field, which improves the overall strength by 20% to 40% and extends the fatigue life to 2.5 times that of the traditional method.

[0034] The connecting seat 4 is made of 7075 aluminum alloy (Al-Zn-Mg-Cu system). The mass percentages of each component in the 7075 aluminum alloy are Si (0~0.4%), Fe (0~0.5%), Cu (1.2%~2.0%), Mn (0~0.3%), Mg (2.1%~2.9%), Cr (0.18%~0.28%), Zn (5.1%~6.1%), Ti (0~0.2%), with the remainder being Al and impurities. In this embodiment, by using 7075-T651 aluminum alloy, the strength is significantly improved, with the yield strength increased by 75% and the tensile strength increased by 90.4%. This indicates that the load-bearing capacity of 7075-T651 aluminum alloy is far greater than that of 6061-T6 aluminum alloy. Under the same cross-sectional area, the ultimate load that 7075-T651 aluminum alloy can withstand is 1.9 times that of 6061-T6 aluminum alloy.

[0035] The design of the piston rod body 31 in this embodiment is particularly suitable for the high-frequency vibration suppression requirements of racing cars under extreme track conditions (such as F1, rally racing, Baja 1000). It is suitable for transient vibration environments with high-frequency impacts of 20Hz~50Hz and amplitudes of ±10~30mm, while meeting the requirements of lightweight (60% weight reduction compared to traditional solid rods) and fatigue life (≥1×10). 7 The system achieves a dual objective (secondary cycle). Engineering verification has shown that under dual-track shifting conditions, it can increase the vibration energy attenuation rate by 18%-22%, without exhibiting buckling failure of the piston rod body 31. Compared to traditional solid rod structures, the dynamic response advantage resulting from the reduced moment of inertia is particularly significant under transient acceleration conditions above 8 m / s². The technical solution is explained below from three aspects: the principle of lightweight structure, the mechanism of mechanical performance enhancement, and the multifunctional integrated design. (1) Principle of lightweight structure (optimization of mass moment of inertia) The piston rod body 31 adopts a hollow tubular structure instead of the traditional solid rod. While maintaining the same outer diameter, the mass can be reduced by decreasing the cross-sectional area. According to the formula for calculating the mass of a hollow cylinder, m = ρπ(R² - r²)L, the mass m decreases quadratically as the inner diameter r increases. Experimental data shows that when the wall thickness is 30% of the outer diameter, the weight can be reduced by approximately 40%, while still maintaining over 90% of the bending stiffness. In the formula, ρ is the material density of the piston rod body 31 (unit: kg / m³), R is the outer radius of the piston rod body 31 (unit: m), r is the inner radius of the piston rod body 31 (unit: m), and L is the length of the piston rod body 31 (unit: m).

[0036] (2) Mechanism for enhancing mechanical properties (compensation for cross-sectional moment of inertia) Traditional solid rods are prone to bending stress concentration (stress amplitude at the root fillet reaches the material fatigue limit) and resonance risk (the natural frequency falls into the operating frequency band of high vibration damping performance, such as 15Hz~25Hz, causing resonance fracture) under alternating loads due to their large mass (high inertia force) and abrupt change in cross-sectional stress gradient.

[0037] In this embodiment, the hollow piston rod body 31 achieves optimized mechanical properties through material distribution on its outer edge, according to the formula for the moment of inertia of a cross section, I=π(R). 4 -r 4 As shown in 4, compared to traditional solid bar structures, the stress concentration factor is greatly reduced, and sufficient bending stiffness can be maintained within a reasonable wall thickness range. Finite element analysis also verifies that when r / R = 0.7, the moment of inertia of the section can still reach 75% of that of a solid structure, while the mass is only 51%. This results in a significant reduction in both mass and moment of inertia compared to a solid bar.

[0038] (3) Multifunctional integrated design Built-in flow channel integration: The hollow cavity inside the piston rod body 31 can serve as an oil passage, achieving structural-functional integration; Improved dynamic characteristics: The reduced reciprocating mass of the piston rod body 31 increases the system's natural frequency by 12%-18%, which can reduce the accumulation of vibration energy; Thermal deformation control: The symmetrical hollow structure of the piston rod body 31, due to the low hardness of the inner wall of the piston rod body 31, can improve the uniformity of the cross-sectional temperature field, and actual measurements show that it can reduce thermal bending deformation by up to 35%; A high-frequency quenching process is introduced: 45# steel is used, and the quenching section in the middle is heat-treated by induction hardening and tempering. The surface hardness of the induction hardened layer is 50HRC~55HRC, and the depth of the hardened layer is 1.2mm~1.6mm. This makes the exterior of the piston rod body 31 hard, resulting in a stronger damper with high vibration damping performance. The interior is left untreated, allowing for better internal bending and reducing the risk of breakage. The depth of the hardened layer reaches 350HV1, specifically referring to the vertical distance from the surface to the point where the Vickers hardness (HV) drops to 350 after surface hardening treatment. "HV1" indicates that the load used during testing is 1 kgf (9.81 N). Simultaneously, the middle section is hard chrome plated with a thickness of 900HV0.05-1200HV0.05, specifically indicating a hardness range of 900HV~1200HV (Vickers hardness). The test load is 0.05. kgf, the chromium layer thickness after polishing is 45±5um, which improves wear resistance and corrosion resistance, thereby increasing its service life.

[0039] This design overcomes the bulkiness of traditional solid rods, achieving a balance between lightweight and high performance through an innovative hollow design, making it particularly suitable for applications with stringent power density requirements. The specific application principle of this embodiment is as follows: As the core carrier of the high-performance vibration damper, the connecting seat 4, when in use, when the high-performance vibration damper is under compression, the main piston valve system 32 moves away from the connecting seat 4, and part of the oil in the oil reservoir 21 flows to the connecting seat 4 through the inside of the piston rod body 31, passes through the oil passage in the connecting seat 4 and the compression regulating valve 5, and finally enters the nitrogen cylinder. At the same time, the floating piston assembly in the nitrogen cylinder moves towards the second end of the nitrogen cylinder module and compresses the nitrogen. Simultaneously, when the piston rod body 31 moves, it can push the buffer sleeve 13 to move closer to the mounting base 11. As the buffer sleeve 13 compresses the second elastic element 19, the conical sealing surface 10 of the buffer sleeve 13 gradually closes the fluid flow channel 14. When the fluid flow channel 14 is completely closed, the pressure of the oil chamber formed by the oil reservoir 21, the mounting base 11, and the buffer sleeve 13 increases significantly, forming a high-pressure chamber. At this time, the piston rod body 31 continues to move, compressing the first elastic element 12. The pressure of the oil chamber formed by the oil reservoir 21, the mounting base 11, and the buffer sleeve 13 rises sharply, and the hydraulic resistance increases significantly, achieving a stepwise absorption of impact energy.

[0040] When the external load is removed, the device is in the recovery state. At this time, the piston rod body 31 moves away from the mounting base 11, the first elastic element 12 releases its stored energy, and pushes the mounting base 11 to reset the direction of the piston rod body 31. The second elastic element 19 provides auxiliary rebound force. The second elastic element 19 pushes the buffer sleeve 13 to move away from the mounting base 11, opening the fluid flow channel. As the buffer sleeve 13 moves, the fluid flow channel 14 gradually increases in size, and the oil flows back to the low-pressure chamber (i.e., the chamber where the piston rod body 31 is located) through the fluid flow channel 14. At the same time, the piston rod body 31 drives the main piston valve system 32 to move in the opposite direction. The high-pressure nitrogen pushes the floating piston assembly to move in the opposite direction, thereby pushing the oil into the oil passage of the connecting seat 4, and then through the compression regulating valve 5 assembly, through the piston rod body 31, and back into the oil storage tank 21. At this time, the device returns to the standby state.

[0041] A portion of the oil in the oil reservoir 21 can enter the lower chamber of the main piston valve system 32 through the rebound regulating valve 7. Therefore, the compression damping force of the device can be controlled by adjusting the compression regulating valve 5 to control the flow rate of the oil through the compression regulating valve 5 during the compression condition. Similarly, adjusting the rebound regulating valve 7 can control the flow rate of the oil through the main piston valve system 32 during the recovery condition, thereby controlling the rebound damping force.

[0042] This embodiment achieves both weight reduction and necessary strength by designing the piston rod body 31 as hollow; advanced coating technology is applied to enhance the surface hardness of the piston rod body 31, improving wear resistance and corrosion resistance, thereby increasing its service life; high-strength alloy steel is selected as the main material of the connecting seat 4, which has good mechanical properties and effectively resists deformation under high stress; rigorous material screening and testing are conducted to ensure that the selected material can maintain excellent performance under extreme conditions; the optimal locking torque value at the junction of the connecting seat 4 and other components is accurately calculated and set to ensure tight fit between components and reduce the risk of loosening or slippage; special tools are used for locking torque calibration to ensure the consistency and reliability of assembly quality; high-frequency quenching process is introduced during the manufacturing process to achieve local hardening treatment of key parts to meet the rigidity requirements.

[0043] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only intended to help understand the method and core concept of the present invention. At the same time, those skilled in the art will find that the specific implementation methods and application scopes may vary based on the concept of the present invention. In summary, the contents of this specification should not be construed as limiting the present invention.

Claims

1. A high-performance vibration damper, comprising a nitrogen cylinder module, an oil reservoir module, a piston rod module, and a connecting seat, wherein the piston rod module comprises a piston rod body and a main piston valve system, characterized in that: The piston rod body is hollow inside, and the hydraulic oil in the oil reservoir module can enter the nitrogen cylinder module through the internal flow channel of the piston rod body and the oil passage on the connecting seat; the piston rod body includes a first connecting section, an intermediate section and a second connecting section, the first connecting section and the second connecting section are respectively located at both ends of the intermediate section, and the first connecting section, the intermediate section and the second connecting section are all hollow inside and connected in sequence, the intermediate section includes a quenching section and two quenching transition sections, the two quenching transition sections are integrally connected to both ends of the quenching section, the first connecting section is used to connect the main piston valve system, and the first connecting section is flash plated, and the outer periphery of the second connecting section is provided with an anti-rust oil coating.

2. The high vibration damping performance damper according to claim 1, characterized in that: It also includes a buffer elastic module. The first end of the nitrogen cylinder module is connected to the first end of the connecting seat, and the second end of the connecting seat is connected to the first end of the piston rod module. The nitrogen cylinder module has a floating piston assembly inside, and the nitrogen cylinder module is used to store nitrogen on one side corresponding to the floating piston assembly. The nitrogen cylinder module is used to introduce hydraulic oil on the other side corresponding to the floating piston assembly. The first end of the piston rod module is used to connect to the suspension, and the second end of the piston rod module extends into the oil reservoir module through the first end of the oil reservoir module and connects to the buffer elastic module. The buffer elastic module includes a mounting seat, a first elastic element, and a buffer sleeve disposed in the oil reservoir module. The first elastic element is located between the second end of the oil reservoir module and the mounting seat. The mounting seat and the buffer sleeve are both slidably connected to the inner wall of the oil reservoir module. The buffer sleeve is connected to the second end of the piston rod module. A fluid flow channel can be formed between the mounting seat and the buffer sleeve. Under the action of the piston rod module, the buffer sleeve contacts the mounting seat and can close the fluid flow channel.

3. The high vibration damping performance vibration damper according to claim 2, characterized in that: The nitrogen cylinder module includes a nitrogen cylinder and the floating piston assembly. The nitrogen cylinder is a hollow cylindrical shell. The floating piston assembly is slidably connected inside the nitrogen cylinder, and the outer side wall of the floating piston assembly can contact the inner side wall of the nitrogen cylinder. The first end of the nitrogen cylinder is threadedly connected to the connecting seat.

4. The high vibration damping performance vibration damper according to claim 2, characterized in that: The oil reservoir module includes an oil reservoir, a lower spring, an upper spring, and a spring transition seat. The oil reservoir is used to store hydraulic oil. The spring transition seat is installed on the outer periphery of the oil reservoir and is located near the first end of the oil reservoir module. The lower spring is sleeved on the outer periphery of the oil reservoir, and the first end of the lower spring abuts against one side of the spring transition seat. The second end of the lower spring abuts against a protrusion on the outer wall of the oil reservoir. The upper spring is sleeved on the outer periphery of the piston rod module, and the first end of the upper spring abuts against one side of the connecting seat. The second end of the upper spring abuts against the other side of the spring transition seat.

5. The high vibration damping performance damper according to claim 4, characterized in that: The second end of the oil reservoir is detachably connected to a fixing cap, and the fixing cap is coaxially arranged with the oil reservoir. The fixing cap is provided with a first limiting protrusion, which and the second end of the oil reservoir form a first limiting groove. One end of the first elastic element is located in the first limiting groove. The first limiting protrusion is used to limit the axial position of the first elastic element, and the first limiting groove is used to limit the radial position of the first elastic element. The mounting base is provided with a second limiting protrusion, which forms a second limiting groove. The other end of the first elastic element is located in the second limiting groove. The second limiting protrusion is used to limit the axial position of the first elastic element, and the second limiting groove is used to limit the radial position of the first elastic element.

6. The high vibration damping performance vibration damper according to claim 4, characterized in that: The oil reservoir, the first elastic element, the mounting base, and the buffer sleeve are all coaxially arranged, and a sealing structure is provided between the mounting base and the oil reservoir, and between the buffer sleeve and the oil reservoir. The end of the buffer sleeve facing the mounting base is also provided with a conical sealing surface. Under the action of the piston rod module, the cross-sectional size of the fluid flow channel gradually decreases as the buffer sleeve moves toward the mounting base.

7. The high vibration damping performance vibration damper according to claim 2, characterized in that: The buffer elastic module further includes at least two second elastic elements, each of which is located between the mounting base and the buffer sleeve, and the plurality of second elastic elements are evenly distributed along the circumference of the mounting base.

8. The high vibration damping performance vibration damper according to claim 2, characterized in that: The main piston valve system is located inside the oil reservoir module and is installed at the second end of the piston rod body. The buffer sleeve is located on one side of the main piston valve system. The piston rod body is provided with an oil passage for the passage of hydraulic oil.

9. The high vibration damping performance vibration damper according to claim 1, characterized in that: The flash coating thickness on the outer surface of the first connecting section is 3µm-5µm; the intermediate section is made of 45# steel, and the quenched section is induction hardened and tempered during processing. The surface hardness of the induction hardened section is 50HRC~55HRC, the depth of the hardened layer is 1.2mm~1.6mm, and the depth of the hardened layer is up to 350HV1. The outer surface of the intermediate section is hard chrome plated. The hard chrome plating hardness ranges from 900HV to 1200HV, the number of microcracks in the plating is 800fsi / cm²-1300fsi / cm², and the microcracks are distributed in a network. After chrome plating, it is held at 200℃-220℃ for 2 hours, and the thickness of the plating after polishing is 45±5µm.

10. The high vibration damping performance vibration damper according to claim 2, characterized in that: The connecting seat is also equipped with a compression regulating valve, which is used to regulate the flow resistance of hydraulic oil passing through the oil passage. A spherical bearing is provided at the second end of the connecting seat, and the connecting seat is used to connect the suspension through the spherical bearing. A springback regulating valve is also provided on one side of the connecting seat, and the hydraulic oil inside the piston rod module can flow into the oil passage of the connecting seat through the springback regulating valve. The connecting seat is made of 7075 aluminum alloy, and the mass percentage of each component in the 7075 aluminum alloy is Si (0~0.4%), Fe (0~0.5%), Cu (1.2%~2.0%), Mn (0~0.3%), Mg (2.1%~2.9%), Cr (0.18%~0.28%), Zn (5.1%~6.1%), Ti (0~0.2%), with the remainder being Al and impurities.

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