Impact load damping unit

Abstract

The impact load damper includes a damper unit and an air spring. The damper unit includes a cylinder having a cylinder chamber and a fluid. The damper unit includes a piston rod. The piston rod includes a first end having an impact load surface and a second end having a piston head assembly. The piston rod includes a piston rod chamber containing the fluid. The damper unit includes an orifice pin. The orifice pin includes an orifice pin chamber containing the fluid. The orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin. The air spring is coupled to the damper unit and is in fluid communication with the damper unit.

Description

Technical Field

[0001] 0001. This disclosure generally relates to impact load attenuation units for energy absorption and vibration isolation.

Background Art

[0002] 0002. Unless otherwise indicated herein, the materials described in this section are not prior art to the claims of this application and are not admitted to be prior art by inclusion in this section.

[0003] 0003. Energy absorption and vibration isolation are important in the manufacturing, aerospace, defense, marine, and railway industries. Energy absorption and vibration isolation devices include shock absorbers, gas springs, speed controls, air springs, wire rope isolators, heavy industry buffers, and emergency stops. A shock absorber is a mechanical or hydraulic device that absorbs and attenuates energy by converting and dissipating the kinetic energy from an impact. Most shock absorbers include a damper that resists movement by friction.

Summary of the Invention

[0004] 0004. Existing problems related to those described above, as well as other problems, are overcome by the impact load dampers of the present disclosure. One embodiment of the present disclosure is an impact load damper comprising a damper unit and an air spring. The damper unit comprises a cylinder having a cylinder chamber and a fluid. The damper unit comprises a piston rod. The piston rod comprises a first end having an impact load surface and a second end having a piston head assembly. The piston rod comprises a piston rod chamber containing the fluid. The damper unit comprises an orifice pin. The orifice pin comprises an orifice pin chamber containing the fluid. The orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin. An air spring is coupled to the damper unit and is in fluid communication with the damper unit.

[0005] 0005. In one embodiment, the impact load damper unit is configured such that the damper unit is located above the air spring or parallel to the air spring.

[0006] 0006. In this embodiment, the orifice spin is a metering orifice spin.

[0007] 0007. In one embodiment, the orifice pin has a first diameter at a first end and a second diameter at a second end.

[0008] 0008. In one embodiment, the orifice is such that its cross-sectional area decreases or changes as a function of stroke to provide a required damping function when the piston rod is compressed into the cylinder chamber.

[0009] 0009. In one embodiment, the damping unit is configured to provide a nonlinear damping force.

[0010] 0010. In one embodiment, the air spring includes a gas chamber containing nitrogen.

[0011] 0011. In one embodiment, the air spring provides a driving force and preload to return the piston rod to a fully extended position when the impact load is removed.

[0012] 0012. In this embodiment, the impact load damper is configured to withstand a maximum load of approximately 35 kN applied to the impact load surface in the compression direction.

[0013] 0013. In one embodiment, the impact load damper further includes a fluid channel between the orifice pin chamber and the spring fluid chamber of the air spring.

[0014] 0014. In one embodiment, the impact load damper further includes a hydraulic fluid in a cylinder chamber, a piston rod chamber, an orifice pin chamber, a fluid channel, and a spring fluid chamber.

[0015] 0015. In one embodiment, the hydraulic fluid is a thermally stable silicone solution.

[0016] 0016. In this embodiment, the piston rod and orifice pin provide an impact damping effect with a damping coefficient as a function of the displacement and temperature of the hydraulic fluid.

[0017] 0017. Another embodiment of the present disclosure includes a method for damping an impact force. The method includes receiving an impact force on the impact load surface of the piston rod of a damper unit. The method includes compressing the piston rod into the cylinder of the damper unit by the impact force. Compressing the piston rod into the cylinder increases the pressure and temperature of the fluid in the cylinder chamber. The method includes passing at least a portion of the fluid, whose pressure and temperature have increased, through an orifice into the piston rod chamber, thereby increasing the pressure and temperature of the fluid in the piston rod chamber. The orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin. The method also includes moving at least a portion of the fluid in the piston rod chamber into a secondary cylinder chamber through a hole in the piston rod, thereby increasing the pressure and temperature of the fluid in the secondary cylinder chamber. The method also includes moving at least a portion of the fluid in the piston rod chamber into an orifice pin chamber, thereby increasing the pressure and temperature of the fluid in the orifice pin chamber. The method also includes moving at least a portion of the fluid in the orifice pin chamber into a fluid channel and increasing the pressure and temperature of the fluid in the fluid channel. The method also includes moving at least a portion of the fluid in the fluid channel into the fluid chamber of the air spring and increasing the pressure and temperature of the fluid in the fluid chamber of the air spring. The method also includes applying pressure to a spring separator and moving the spring separator toward the gas chamber of the air spring in order to compress the gas in the gas chamber of the air spring.

[0018] 0018. In one embodiment, the method further includes providing a driving force by an air spring to return the piston rod to a fully extended position once the impact load is removed.

[0019] 0019. In one embodiment, the method further includes providing a preload to the damper unit by an air spring before it is subjected to an impact load.

[0020] 0020. Another embodiment of the present disclosure is an impact load damper comprising a damper unit and an air spring. The damper unit comprises a cylinder having a cylinder chamber and a fluid. The damper unit comprises a piston rod. The piston rod comprises a first end having an impact load surface and a second end having a piston head assembly. The piston rod comprises a piston rod chamber containing the fluid. The damper unit comprises a metering orifice pin having a first diameter at the first end and a second diameter at the second end. The metering orifice pin comprises an orifice pin chamber containing the fluid. The orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin. The air spring comprises a spring fluid chamber containing the fluid, a separator and a gas chamber containing nitrogen. The spring fluid chamber of the air spring is in fluid communication with the orifice pin chamber through a fluid channel.

[0021] 0021. The above-mentioned overview is illustrative and not intended to be limiting. In addition to the exemplary aspects, embodiments, and features described above, further aspects, embodiments, and features will become apparent by reference to the drawings and the following detailed description.

[0022] 0022. The aforementioned and other features of this disclosure will become more fully apparent from the following description and the appended claims, together with the accompanying drawings. Understanding that these drawings illustrate only some embodiments of this disclosure and should not be considered to limit its scope, this disclosure will be described more specifically and in detail through the use of the accompanying drawings. [Brief explanation of the drawing]

[0023] [Figure 1] 0023. Figure 1 is a side perspective view of the impact load damper according to this disclosure. [Figure 2] 0024. Figure 2 is a side cross-sectional view of an enlarged impact load damper according to the present invention. [Figure 3] 0025. Figure 3 is a side cross-sectional view of a compressed impact load damper according to the present disclosure. [Figure 4] 0026. FIG. 4 is a top cross-sectional view of an enlarged impact load damper according to the present disclosure. [Figure 5] 0027. FIG. 5 is a front view of an impact load damper according to the present disclosure. [Figure 6] 0028. FIG. 6 is a rear view of an impact load damper according to the present disclosure. [Figure 7A] 0029. FIG. 7A is a rear view of a lock wire routing for an impact load damper according to the present disclosure. [Figure 7B] 0030. FIG. 7B is a perspective rear view of a lock wire routing for an impact load damper according to the present disclosure. [Figure 8A] 0031. FIG. 8A is a rear view of a lock wire routing for an impact load damper according to the present disclosure. [Figure 8B] 0032. FIG. 8B is a perspective rear view of a lock wire routing for an impact load damper according to the present disclosure. [Figure 9] 0033. FIG. 9 illustrates a flowchart of an example method for attenuating an impact force according to the present disclosure.

DETAILED DESCRIPTION OF THE INVENTION

[0024] 0034. In the following detailed description, reference is made to the accompanying drawings that form a part hereof. In the drawings, like symbols typically identify like components unless the context dictates otherwise. The illustrative embodiments described in the detailed description, the drawings, and the claims are not intended to be limiting. Other embodiments may be utilized and other changes may be made without departing from the spirit or scope of the subject matter presented herein. The aspects of the present disclosure generally described herein and illustrated in the drawings may be arranged, replaced, combined, separated, and designed in a variety of different configurations, all of which are explicitly contemplated herein.

[0025] 0035. An impact load damper may include a cylinder, piston assembly, bearing assembly, cylinder end, metering pin, hydraulic / gas separator, and filling valve. The impact load damper may include an orifice system comprising a metering orifice pin and an orifice ring, which may be designed to allow controlled transfer of viscous fluid from one side of the piston to the other. The orifice system may provide a damping coefficient as a function of displacement and temperature. An internal gas spring may provide the necessary preload and spring force as a function of displacement and temperature, and may also provide volume compensation for the piston rod, and may provide a driving force to return the damper to its fully extended position when the load is removed. A hydraulic / gas separator may prevent the gas from mixing with the hydraulic fluid and provide consistent damping regardless of the orientation of the damper unit.

[0026] 0036. Figure 1 is a side perspective view of an impact load damper arranged according to at least some embodiments described herein. The impact load damper 100 may include a damper unit 10 coupled to an air spring 40. The impact load damper 100 may be configured such that the damper unit 10 is above the air spring 40 or parallel to the air spring 40. The damper unit 10 may include a cylinder 20 and a piston rod 30. The piston rod 30 may be configured to extend outward from the cylinder 20 (as shown) and to be compressed toward the cylinder 20. The impact load interface 50 may be at the end of the piston rod 30. As will be described in more detail below, the damper unit 10 may be a viscous damper having a custom orifice and a progressive damping coefficient for dissipating impact energy at the impact load interface 50.

[0027] 0037. Figure 2 is an enlarged side cross-sectional view of an impact load damper according to at least some embodiments described herein. Components in Figure 2 that are given the same reference numerals as those in Figure 1 will not be described again for the sake of brevity.

[0028] 0038. The piston rod 30 may include a piston head assembly 250, which includes an impact load interface 50 at a first end and a wear ring and O-ring at a second end. The piston rod 30 is hollow and may define a piston rod chamber 205. The piston rod chamber 205 may contain a hydraulic fluid 210. The hydraulic fluid 210 may be a thermally stable silicone fluid, such as silicone 100 cSt (dimethylpolysiloxane) according to Federal Specification VV-D-1078. The cylinder 20 may define a cylinder chamber 220. The piston head assembly 250 may seal the piston rod 30 to the inner wall of the cylinder chamber 220 when an impact force is applied to the impact load interface 50 and the piston rod 30 is compressed within the cylinder 20. The cylinder chamber 220 may include an orifice pin 230 located in the center of the cylinder chamber 220. The orifice pin 230 may be hollow, and an orifice pin chamber 235 may be defined within the orifice pin 230. The cylinder chamber 220 and the orifice pin chamber 235 may contain hydraulic fluid 210. The piston rod 30 and piston head assembly 250 may be configured together with the orifice pin 230 to define a ring-shaped orifice 260 between the inner surface of the piston head assembly 250 and the outer surface of the orifice pin 230. The piston rod 30 and piston head assembly 250 may be configured to overlap around the orifice pin 230 and cover the orifice pin 230 when the piston rod 30 is compressed in the cylinder 20. The orifice pin 230 and the orifice 260 may define an orifice system configured to allow controlled transfer of hydraulic fluid 210 from the cylinder chamber 220 to the piston rod chamber 205. The cylinder chamber 220 may be in fluid communication with the piston rod chamber 205 through the orifice 260. The piston rod chamber 205 may also be in fluid communication with the orifice pin chamber 235. The orifice pin chamber 235 may be in fluid communication with the hydraulic fluid chamber 280 of the air spring 40 through the fluid channel 270.

[0029] 0039. The hydraulic fluid 210 in the cylinder chamber 220 can be compressed when the piston rod 30 is compressed within the cylinder chamber 220, causing the pressure and temperature of the hydraulic fluid 210 to rise. The hydraulic fluid 210 with increased pressure and temperature can pass through the orifice 260 into the piston rod chamber 205, causing the pressure and temperature of the hydraulic fluid 210 in the piston rod chamber 205 to rise. The hydraulic fluid 210 with increased pressure and temperature in the piston rod chamber 205 moves into the secondary cylinder chamber 221 (shown in Figure 3), which is formed between the outer surface of the piston rod 30 and the inner wall of the cylinder 20, when the piston rod 30 is compressed into the cylinder 20 of the damper unit 10, and interacts with the hydraulic fluid 210 in the secondary cylinder chamber 221, causing its pressure and temperature to rise. The hydraulic fluid 210, whose pressure and temperature increase in the piston rod chamber 205, moves into the orifice pin chamber 235, interacts with the hydraulic fluid 210 in the orifice pin chamber 235, and may increase its pressure and temperature. The hydraulic fluid 210, whose pressure and temperature increase in the orifice pin chamber 235, moves into the channel 270, interacts with the hydraulic fluid 210 in the channel 270, and may increase its pressure and temperature. The hydraulic fluid 210, whose pressure and temperature increase in the channel 270, moves into the hydraulic fluid chamber 280, interacts with the hydraulic fluid 210 in the hydraulic fluid chamber 280 of the air spring 40, and may increase its pressure and temperature. The hydraulic fluid 210 in the hydraulic fluid chamber 280 of the air spring 40 can pressurize the spring separator 285 to compress the gas 295 in the gas chamber 290, causing the spring separator 285 to move toward the gas chamber 290 of the air spring 40. The gas 295 may be nitrogen (N), and the air spring 40 may include a filling valve 297 for filling the gas chamber 290 with gas 295. The impact load damping unit 100, consisting of the damper unit 10 and the air spring 40, can dampen the impact load with the spring force from the air spring 40 and the nonlinear damping force from the damper unit 10.

[0030] 0040. The orifice pin 230 may have a first end 230A adjacent to the impact load interface 50 side of the impact load damper 100 and a second end 230B adjacent to the rear side of the impact load damper 100. The orifice pin 230 may be a metering orifice pin and may have a first diameter 240 at the first end 230A and a second diameter 245 at the second end 230B. The second diameter 245 may be larger than the first diameter 240, and both diameters 240 and 245 may be smaller than the inner diameter of the hollow piston rod 30. The orifice 260 may have a smaller cross-sectional area as the piston rod 30 moves along the orifice pin 230 when the piston rod 30 is compressed into the cylinder chamber 220, thereby resulting in higher pressure and temperature of the hydraulic fluid 210 in the cylinder chamber 220 as the piston rod 30 is compressed into the cylinder chamber 220. In another embodiment, the diameter of the metered orifice spin 230 may vary as a function of stroke to generate the required damping function.

[0031] 0041. The piston rod 30 and orifice pin 230 may form an orifice system configured to control the transfer of viscous hydraulic fluid 210 from one side of the piston head assembly 250 to the other side of the piston head assembly 250 into the cylinder chamber 220. The piston rod 30 and orifice pin 230 may provide a damping effect to impacts with a damping coefficient as a function of the displacement and temperature of the hydraulic fluid 210. The air spring 40 may provide preload and spring force to the damper unit 10 as a function of the displacement and temperature of the hydraulic fluid 210 and the temperature of the gas 295. The air spring 40 may also provide capacity compensation for the piston rod 30 and a driving force to return the piston 30 to its fully extended position when the impact load is removed.

[0032] 0042. The piston rod 30 may have a stroke from a minimum extension position of approximately 250 mm to a compressed position. The impact load damper 100 may consist of a minimum extension length of approximately 593.6 mm and a maximum extension length of approximately 596.6 mm. The impact load damper 100 may be configured to withstand a maximum impact velocity of 3.0 m / s (cable speed of 6.0 m / s). The impact load damper 100 may be configured to withstand a maximum impact weight of 303 kg. The impact load damper 100 may be configured to withstand a full load dump from a fully compressed position under any temperature conditions, without permanent deformation, and may continue to function normally.

[0033] 0043. Figure 3 is a side cross-sectional view of a compressed impact load damper arranged according to at least some embodiments described herein. Components in Figure 3 that are given the same reference numerals as those in Figures 1 and 2 will not be described again for the sake of brevity.

[0034] 0044. As shown in Figure 3, when an impact force is applied to the impact load interface 50, the piston rod 30 is subjected to the impact force and can be compressed within the cylinder 20. When the piston rod 30 is compressed within the cylinder chamber 220, the hydraulic fluid 210 in the cylinder chamber 220 can be compressed, and the hydraulic fluid 210 can pass through the orifice 260 into the piston rod chamber 205, and the hydraulic fluid 210 in the piston rod chamber 205 can flow through the flow holes. The hydraulic fluid 210 in the piston rod chamber 205 can communicate with the secondary cylinder chamber 221 through holes 261 and move into the secondary cylinder chamber 221 through holes 261. The hydraulic fluid 210 in the piston rod chamber 205 can also move into the orifice pin chamber 235. The hydraulic fluid 210 in the orifice pin chamber 235 can move into the channel 270. The hydraulic fluid 210 in the channel 270 can move into the hydraulic fluid chamber 280 of the air spring 40. The hydraulic fluid 210 in the hydraulic fluid chamber 280 can apply pressure to the spring separator 285 to compress the gas 295 in the gas chamber 290, causing the spring separator 285 to move toward the gas chamber 290 of the air spring 40. The impact load damping unit 100, composed of the damper unit 10 and the air spring 40, can dampen impact loads with the spring force from the air spring 40 and the nonlinear damping force from the damper unit 10. When the impact load is removed, the air spring 40 can provide capacity compensation for the piston rod 30 and a driving force to return the piston 30 to its fully extended position.

[0035] 0045. Figure 4 is a top cross-sectional view of an enlarged impact load damper arranged according to at least some embodiments described herein. Components of Figure 4 that are given the same reference numerals as those of Figures 1 to 3 will not be described again for brevity.

[0036] 0046. The damper unit 10 includes a cylinder 20 and a piston rod 30 configured to extend outward from the cylinder 20 (as shown in the figure) and to be compressed inward from the cylinder 20 in response to a force from an impact at the impact load interface 50 of the piston rod 30. The piston rod 30, piston head assembly 250, and orifice pin 230 define a ring-shaped orifice 260 between the inner surface of the piston head assembly 250 and the outer surface of the orifice pin 230. When an impact force is applied to the impact load interface 50, the piston rod 30 may be compressed inward from the cylinder 20, and the hydraulic fluid 210 in the cylinder chamber 220 may be compressed and move through the orifice 260 into the piston rod chamber 205. The hydraulic fluid 210 in the piston rod chamber 205 may move through the hole 261 into the secondary cylinder chamber 221. The hydraulic fluid 210 in the piston rod chamber 205 may also move into the orifice pin chamber 235, and the hydraulic fluid 210 in the orifice pin chamber 235 may move into the channel 270. The hydraulic fluid 210 in the channel 270 may interact with the air spring 40 (shown in Figures 1 to 3) and apply pressure to compress the gas in the air spring 40. The damper unit 10 can dampen impact loads with a nonlinear damping force.

[0037] 0047. The impact load damper unit 10 can generate a damping force output in the compression (load) direction within a specified output tolerance, according to the following theoretical damping force relationship: F damping =C(x,T)*V where F damping = Damping force output from the damper (N) x = Damper stroke position (mm) V = Relative velocity of the damper (m / s) C(x,T) = Damping coefficient as a function of stroke and temperature (N / m·s) 0048. The impact load damper unit 10 may be configured to withstand a maximum load of approximately 35 kN applied in the compression direction at any stroke position. The impact load damper unit 10 may be configured to have a nominal spring preload of approximately 8 kN. The impact load damper unit 10 may be configured to have a nominal spring end load of approximately 17.2 kN. The impact load damper unit 10 may be configured to maintain an electrostatic discharge between the helicopter and the ground having a potential of 300 kV.

[0038] 0049. The following table shows the simulation results for the damping coefficient as a function of stroke of the impact load damper unit 10 at 20°C, -45°C, and 55°C. [Table 1] [Table 2] [Table 3]

[0039] 0053. As shown in Tables 1-3, the impact load damper unit 10 may be configured with soft-start damping to eliminate force spikes during high-speed impacts. Tables 1-3 also illustrate that the damping coefficient of the impact load damper unit 10 is temperature-dependent.

[0040] 0054. Figure 5 is a front view of an impact load damper according to the present disclosure, arranged according to at least some embodiments described herein. Components in Figure 5 that are denoted by the same reference numerals as those in Figures 1 to 4 will not be described again for the sake of brevity.

[0041] 0055. The front view of the impact load damper 100 illustrates the damper unit 10 above the air spring 40. The front view of the damper unit 10 includes the cylinder 20, the piston rod 30, and the impact load interface 50. The front view of the air spring 40 includes the filling valve 297.

[0042] 0056. Figure 6 is a rear view of an impact load damper according to the present disclosure, arranged in at least some embodiments described herein. Components in Figure 6 that are denoted by the same reference numerals as those in Figures 1 to 5 will not be described again for brevity.

[0043] 0057. The rear view of the impact load damper 100 illustrates the damper unit 10 above the air spring 40. The damper unit 10 includes a temperature sensor 610, a pressure sensor 620, and a lock wire 630.

[0044] 0058. Figure 7A is a rear view of the lock wire routing for an impact load damper, and Figure 7B is a perspective rear view of the lock wire routing for an impact load damper, both arranged by at least some embodiments described herein. Components in Figures 7A and 7B that are denoted by the same reference numerals as those in Figures 1 to 6 will not be described again for the sake of brevity.

[0045] 0059. A rear view of the lock wire routing for the impact load damper shows the temperature sensor 610, pressure sensor 620, lock wire 630, lock nut 710, and lock nut hole 720. As shown in Figures 7A and 7B, in the first embodiment, the lock nut wire 630 can be threaded through the lock nut holes 720 on the upper and lower sides of the lock nut 710 around multiple sides of the fixing nut of the temperature sensor 610, and secured together on the back side of the lock nut 710.

[0046] 0060. Figure 8A is a rear view of an alternative lock wire routing for an impact load damper, and Figure 8B is a perspective rear view of an alternative lock wire routing for an impact load damper, both of which are arranged by at least some embodiments described herein. Components in Figures 8A and 8B that are given the same reference numerals as components in Figures 1 to 7B will not be described again for the sake of brevity.

[0047] 0061. A rear view of the lock wire routing for the impact load damper shows the temperature sensor 610, pressure sensor 620, lock wire 630, lock nut 710, and lock nut hole 720. As shown in Figures 8A and 8B, in the second embodiment, the lock nut wire 630 can be fixed together at the bottom of the lock nut 710, through the lock nut holes 720 at the front and rear of the lock nut 710, around multiple sides of the fixing nut of the temperature sensor 610.

[0048] 0062. The apparatus of this disclosure may provide an impact load damper having a nonlinear spring function and a nonlinear damping function. The apparatus of this disclosure may provide an impact load damper having a custom orifice-equipped viscous damper having a progressive damping coefficient coupled with an air spring that provides a specified preload and restoring force. The apparatus of this disclosure may provide an impact load damper that can maintain its set position when the impact load is below a designed threshold and absorbs and dissipates input energy when the impact load exceeds the designed threshold. The apparatus of this disclosure may provide an impact load damper that can provide a required damping coefficient as a function of displacement and temperature. The apparatus of this disclosure may provide a reduced-length impact load damper for applications requiring a smaller impact load damper footprint. The apparatus of this disclosure may provide an impact load damper that can provide impact load damping for use with a helicopter flight rescue system (HFRS) including an insertion and extraction tool that utilizes longlines and personnel transport system (PCDS) rescue lines.

[0049] 0063. Figure 9 illustrates a flowchart of an example method for attenuating an impact force, according to at least some embodiments presented herein. This example process may include one or more operations, actions, or functions, as illustrated by one or more of blocks S2, S4, S6, S8, S10, S12, S14, and / or S16. Although illustrated as separate blocks, various blocks may be divided into additional blocks, combined into fewer blocks, or deleted, depending on the desired implementation.

[0050] 0064. This method may be initiated in block S2, where "the piston rod of the damper unit receives an impact force on the impact load surface." In block S2, the impact force may be received by the piston rod of the damper unit. The impact force may be applied to the impact load surface of the piston rod.

[0051] 0065. This method can proceed from block S2 to block S4, and "compresses the piston rod into the cylinder of the damper unit by an impact force, and hereby compressing the piston rod into the cylinder increases the pressure and temperature of the fluid in the cylinder chamber." In block S4, the piston rod can be compressed into the cylinder of the damper unit by an impact force. Compressing the piston rod into the cylinder increases the pressure and temperature of the fluid in the cylinder chamber.

[0052] 0066. This method proceeds from block S4 to block S6, and involves "passing at least a portion of the fluid whose pressure and temperature have increased through the orifice into the piston rod chamber, thereby increasing the pressure and temperature of the fluid in the piston rod chamber, wherein the orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin." In block S6, at least a portion of the fluid whose pressure and temperature have increased passes through the orifice into the piston rod chamber, thereby increasing the pressure and temperature of the fluid in the piston rod chamber. The orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin.

[0053] 0067. This method proceeds from block S6 to block S8, and "at least a portion of the fluid in the piston rod chamber is moved into the secondary cylinder chamber through the flow holes in the piston rod, thereby increasing the pressure and temperature of the fluid in the secondary chamber." In block S8, at least a portion of the fluid in the piston rod chamber is moved into the secondary cylinder chamber through the flow holes in the piston rod, thereby increasing the pressure and temperature of the fluid in the secondary cylinder chamber.

[0054] 0068. This method proceeds from block S8 to block S10, and "at least a portion of the fluid in the piston rod chamber is moved into the orifice spin chamber within the orifice spin, thereby increasing the pressure and temperature of the fluid in the orifice spin chamber." In block S10, at least a portion of the fluid in the piston rod chamber is moved into the orifice spin chamber within the orifice spin, thereby increasing the pressure and temperature of the fluid in the orifice spin chamber.

[0055] 0069. This method proceeds from block S10 to block S12, and "moves at least a portion of the fluid in the orifice pin chamber into the fluid channel, and increases the pressure and temperature of the fluid in the fluid channel." In block S12, at least a portion of the fluid in the orifice pin chamber is moved into the fluid channel, and the pressure and temperature of the fluid in the fluid channel are increased.

[0056] 0070. This method proceeds from block S12 to block S14, "moving at least a portion of the fluid in the fluid channel into the fluid chamber of the air spring, and increasing the pressure and temperature of the fluid in the fluid chamber of the air spring." In block S14, at least a portion of the fluid in the fluid channel is moved into the fluid chamber of the air spring, and the pressure and temperature of the fluid in the fluid chamber of the air spring are increased.

[0057] 0071. This method can be continued from block S14 to block S16, "to compress the gas in the gas chamber of the air spring, pressure is applied to the spring separator, and the spring separator is moved toward the gas chamber of the air spring." In block S16, pressure is applied to the spring separator to compress the gas in the gas chamber of the air spring, and the spring separator is moved toward the gas chamber of the air spring.

[0058] 0072. Finally, the processes and techniques described herein are not inherently related to any apparatus and can be implemented by any suitable combination of components. Furthermore, various types of general-purpose apparatus can be used by the teachings described herein. It may also be found to be advantageous to construct specialized apparatus for performing the method steps described herein. This disclosure is described in relation to examples, which are intended in all respects to be illustrative rather than restrictive.

[0059] 0073. The foregoing description is merely illustrative of the present disclosure. Various alternatives and modifications can be devised by those skilled in the art without departing from the present disclosure. Accordingly, the present disclosure is intended to encompass all such alternatives, modifications, and variations. Embodiments described with reference to the accompanying drawings are presented solely to demonstrate specific examples of the present disclosure. Other elements, steps, methods, and techniques that are not substantially different from those described above and / or in the accompanying claims are also intended to be within the scope of the present disclosure.

Claims

1. It is an impact load damper, A cylinder including a cylinder chamber containing fluid, A piston rod, wherein the piston rod includes a first end having an impact load surface and a second end having a piston head assembly, and the piston rod includes a piston rod chamber containing fluid. An orifice spin including an orifice spin chamber containing fluid, An orifice defined between the inner surface of the piston head assembly and the outer surface of the orifice pin, A damper unit including, An air spring coupled to the damper unit and in fluid communication with the damper unit, An impact load damper equipped with this feature.

2. The impact load damper according to claim 1, wherein the damper unit is configured to be above or parallel to the air spring.

3. The impact load damper according to claim 1, wherein the orifice pin is a metered orifice pin.

4. The impact load damper according to claim 3, wherein the orifice pin has a first diameter at a first end and a second diameter at a second end.

5. The impact load damper according to claim 4, wherein the orifice has a cross-sectional area that decreases or changes as a function of stroke to provide a required damping function when the piston rod is compressed into the cylinder chamber.

6. The shock load damper according to claim 1, wherein the damper unit is configured to provide a nonlinear damping force.

7. The impact load damper according to claim 1, wherein the air spring includes a gas chamber containing nitrogen.

8. The impact load damper according to claim 1, wherein the air spring provides a driving force and preload to return the piston rod to a fully extended position when the impact load is removed.

9. The impact load damper according to claim 1, wherein the impact load damper is configured to withstand a maximum load of approximately 35 kN applied to the impact load surface in the compression direction.

10. The impact load damper according to claim 1, further comprising a fluid channel between the orifice pin chamber and the spring fluid chamber of the air spring.

11. The impact load damper according to claim 10, further comprising hydraulic fluid in the cylinder chamber, secondary cylinder chamber, piston rod chamber, orifice pin chamber, fluid channel, and spring fluid chamber.

12. The impact load damper according to claim 11, wherein the hydraulic fluid is a thermally stable silicone fluid.

13. The impact load damper according to claim 11, wherein the piston rod and orifice pin provide an impact damping effect with respect to the damping coefficient as a function of the displacement and temperature of the hydraulic fluid.

14. A method for dampening impact force, The impact force is received on the impact load surface of the piston rod of the damper unit, The impact force compresses the piston rod into the cylinder of the damper unit, and in this case, compressing the piston rod into the cylinder increases the pressure and temperature of the fluid in the cylinder chamber. To pass at least a portion of the fluid whose pressure and temperature have increased through the orifice into the piston rod chamber, thereby increasing the pressure and temperature of the fluid in the piston rod chamber, wherein the orifice is defined between the inner surface of the piston head assembly and the outer surface of the orifice pin, To move at least a portion of the fluid in the piston rod chamber into the secondary cylinder chamber through the flow holes in the piston rod, thereby increasing the pressure and temperature of the fluid in the secondary cylinder chamber, To move at least a portion of the fluid in the piston rod chamber into the orifice spin chamber within the orifice spin, thereby increasing the pressure and temperature of the fluid in the orifice spin chamber, To move at least a portion of the fluid in the orifice pin chamber into the fluid channel, and to increase the pressure and temperature of the fluid in the fluid channel, To move at least a portion of the fluid in the fluid channel into the fluid chamber of the air spring, thereby increasing the pressure and temperature of the fluid in the fluid chamber of the air spring, To compress the gas in the gas chamber of the air spring, pressure is applied to the spring separator, causing the spring separator to move toward the gas chamber of the air spring. A method for damping impact force, which includes the following features.

15. The method for damping an impact force according to claim 14, further comprising providing a driving force by the air spring to return the piston rod to a fully extended position when the impact load is removed.

16. The method for damping an impact force according to claim 14, further comprising applying a preload to the damper unit by the air spring before it is subjected to an impact load.

17. The method for damping an impact force according to claim 14, wherein the gas is nitrogen.

18. The damper unit provides a nonlinear damping force, as described in claim 14, for the method of damping an impact force.

19. The method for damping an impact force according to claim 14, wherein the fluid is a thermally stable silicone fluid.

20. It is an impact load damper, A cylinder including a cylinder chamber containing fluid, A piston rod, wherein the piston rod includes a first end having an impact load surface and a second end having a piston head assembly, and the piston rod includes a piston rod chamber containing fluid. A metering orifice spin having a first diameter at a first end and a second diameter at a second end, comprising a metering orifice spin chamber containing fluid, An orifice defined between the inner surface of the piston head assembly and the outer surface of the orifice pin, A damper unit including, An air spring comprising a spring fluid chamber containing fluid, a separator, and a gas chamber containing nitrogen, wherein the spring fluid chamber of the air spring is in fluid communication with the orifice pin chamber through a fluid channel, An impact load damper equipped with this feature.

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