HIGH-TEMPERATURE, HIGH-TORQUE, POLYMER TWIST DAMPER

Abstract

Torsion spring damper (200), comprising: - a core (210) which has an opening (212) leading through it; - a first solid component (220) having a first set of projections (222); - a second fixed component (230) having a second set of projections (232); and - a tension element (240) positioned between the first fixed component (220) and the second fixed component (230), and wherein the tensile element (240) comprises a solid silicone polymer, characterized by the fact that the tension element (240) has a plurality of elongated bands, wherein the tension element (240) has a plurality of cavities (244) extending through it.

Description

CROSS-REFERENCE TO RELATED REGISTRATIONS

[0001] This application claims priority over preliminary US patent application No. 63 / 311,306, filed on February 17, 2022, and preliminary US patent application No. 63 / 313,510, filed on February 24, 2022. AREA OF REVELATION

[0002] Embodiments of the present disclosure provide a torsion spring damper comprising a compression limiter, a first disk, and a second disk. The first disk is arranged at a first end of the compression limiter, and the second disk is arranged at a second end of the compression limiter, the second end being opposite the first end. The torsion spring damper also comprises a tension element. The tension element is connected to the first disk and the second disk. The tension element is made of a solid silicone polymer. BACKGROUND

[0003] Various components, such as cables and pipes, can be attached to surfaces like walls, ceilings, or the like using guide clamp assemblies. For example, a cylindrical pipe can be attached to a wall by a guide clamp assembly that includes a pipe retaining channel which snaps, locks, or otherwise secures a portion of the pipe. The guide clamp itself is then fixed within an opening in the object by means of an anchoring element, such as a pintle fastener or a threaded bolt, which may be integrally formed with the guide clamp. Optionally, the guide clamp may not include an integral anchoring element or any other component that can be used to anchor the guide clamp assembly to a vehicle component.

[0004] Torsion springs can be used in a wide variety of applications. In some applications, it is desirable to combine a torsion spring with a damper. Dampers can reduce the activation speed of a loaded torsion spring after it has been released. Some dampers can be particularly useful in combination with certain types of torsion springs. For example, common silicone dampers offer only low resistance torque and may only be suitable for use with low-torque torsion springs, not with high-torque springs. Furthermore, certain dampers are not well-suited for all situations, such as extreme temperatures.

[0005] The publication DE 10 2013 010 418 A1 relates to a torsion spring element with at least two axially spaced spring element mounts that are rotatable relative to each other, and at least one elastic spring element that is radially spaced from the axis of rotation and connects the spring element mounts.

[0006] The publication DE 602 17 744 T2 concerns an elastic tension cable made of polysiloxane. BRIEF SUMMARY OF THE INVENTION

[0007] The present invention relates to a torsion spring damper according to independent claim 1, wherein advantageous embodiments of the torsion spring damper according to the invention are specified in the dependent claims. The invention further relates to a torsion spring damper according to dependent claim 6.

[0008] The present disclosure provides a torsion spring damper comprising a compression limiter, a first disk, and a second disk. The first disk is arranged at a first end of the compression limiter, and the second disk is arranged at a second end of the compression limiter, the second end being opposite the first end. The torsion spring damper also comprises a tension element. The tension element is connected to the first disk and the second disk. The tension element is made of a solid silicone polymer.

[0009] In some embodiments, a torsion spring damper comprises a core, a first solid component, a second solid component, and a tension element. The core has an opening through it. The first solid component has a first set of projections, and the second solid component has a second set of projections. The tension element is positioned between the first and second solid components and is made of a solid silicone polymer.

[0010] In some embodiments, a torsion spring damper assembly comprises a cap, a base plate, and a damper. The cap includes a cap opening, and the base plate includes a base plate opening. The damper is positioned between the cap and the base plate and comprises a first disk, a second disk, a tension element, and an opening. The first disk and the second disk are located at the first end and second end, respectively, of a compression limiter. The tension element extends between the first disk and the second disk and surrounds the compression limiter about a longitudinal axis. The cap opening, the damper opening, and the base plate opening are arranged concentrically about a longitudinal axis.

[0011] In a further embodiment, a torsion spring damper assembly comprises a first fixed component, a second fixed component, a tension element, and at least one longitudinal cap. The first fixed component includes a plurality of fixed modular subcomponents, the fixed modular components comprising a plurality of first projections and a central opening. The second fixed component comprises a body and a plurality of second projections extending outward from an outer surface of the body. The tension element comprises a plurality of cavities arranged between a plurality of bands. The at least one longitudinal cap is arranged at one end of the tension element. The plurality of second projections are received by the plurality of cavities of the tension element to form a first subassembly, and the first subassembly is inserted through a central opening of the first fixed component. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] The invention will be better understood, and features, aspects, and advantages other than those mentioned above will become apparent, when the following detailed description is taken into account. This detailed description is given with reference to the following drawings. Fig. Figure 1A is a perspective view of a basic design form of a damper in a pre-tensioned starting position from above, front and right; Fig. 1B is a perspective view of the damper of Fig. 1A in a position rotated by 30 degrees from above, front and right; Fig. 1C is a perspective view of the damper of Fig. 1A in a position rotated by 240 degrees from above, front and right; Fig. Figure 2A is a cross-sectional view of a preferred embodiment of a damper in a pre-tensioned rest / start position; Fig. 2B is a front cross-sectional view of the preferred embodiment of a damper of Fig. 2A in a position after a slight rotation has been applied; Fig. 2C is a front cross-sectional view of the preferred embodiment of a damper of Fig. 2A in a position after a larger rotation has been applied; Fig. 3A is a front top view of a tension element for a damper of Fig. 2A; Fig. 3B is a front top view of an outer section of an alternative tension element, similar to the one in Fig. 3A shown; Fig. 3C is a front cross-sectional view of the damper of the preferred embodiment of the Fig. 2A-2C in close-up; Fig. Figure 4A is a perspective front view of a damper of an alternative embodiment with an approach angle of zero degrees; Fig. 4B is a perspective front view of the damper from Fig. 4A with an approach angle of 20 degrees; Fig. Figure 5 is a calculated stress-strain curve for a low-modulus silicone polymer; Fig. 6A is a perspective front view of an embodiment of a damper, which corresponds to the damper in Fig. 2A resembles the damper shown and has a first depth, from above and right; Fig. 6B is a perspective front view of an embodiment of a damper corresponding to that of Fig. 6A is similar, but has a greater depth, from above and right; Fig. 6C is a perspective front view of an embodiment of a damper corresponding to that of Fig. 6B is similar, but has a greater depth, from above and right; Fig. Figure 7 is a close-up front view of an outer section of the tension element; Fig. 8A is a fully exploded isometric view of a damper assembly similar to the one shown in the Fig. Dampers shown in 2A-2C; Fig. 8B is an isometric view of the damper assembly of Fig. 8A, wherein a cylinder was inserted into a housing; Fig. 8C is an isometric view of the damper assembly of Fig. 8B with a pulling element positioned on the cylinder; Fig. 8D is an isometric view of the damper assembly of Fig. 8C with a disc component positioned on the housing; Fig. 9A is a perspective front view of the damper similar to the dampers of 2A-2C and 8A-8D in single view from above and left; Fig. 9B is a perspective front view of the damper positioned between unassembled parts of an assembly, from above and left; Fig. 9C is a perspective front view of the damper positioned between unassembled parts of an assembly, from above; Fig. 9D is a perspective front view of the damper positioned in the assembled unit, from above; Fig. 10A is an exploded view of a first fixed component of the damper assembly; Fig. 10B is a perspective front view of a first fixed component of the damper assembly in an assembled state from the right; Fig. 10C is a perspective front view of a second fixed component of the damper assembly from the right; Fig. 10D is a perspective front view of a tension element mounted on the second fixed component, from the right; Fig. 10E is a perspective front view of both the first fixed component and the second fixed component, separated from each other, from the right; Fig. 10F is a perspective front view of the first fixed component, the second fixed component and the tension element of the damper assembly in an assembled state from the right; Fig. Figure 11 is a perspective view of a side shield of a motor vehicle seat, using an embodiment of a damper, from the right; Fig. Figure 12A illustrates a torsion spring-driven movement of a motor vehicle seat with a torsion spring damper; Fig. 12B illustrates a torsion spring-driven movement of a motor vehicle seat without a torsion spring damper; Fig. 13A is an illustration of the movement of a possible application for dampers of embodiments that are in the for the Fig. 13C-13F tests have been replicated; Fig. 13B is a representative diagram for “torque vs. angle of rotation” under loading and unloading conditions; Fig. 13C is a representation of test data for “torque vs. angle of rotation” of certain example dampers; Fig. 13D is a representation of test data for "torque vs. angle of rotation" of certain example dampers; Fig. 13E is a representation of test data for “torque vs. angle of rotation” of certain example dampers; Fig. 13F is a representation of test data for "torque vs. angle of rotation" of certain example dampers; and In Fig. Figure 14 is a flowchart showing a method for manufacturing dampers according to embodiments.

[0013] Before the embodiments of the disclosure are explained in detail, it is understood that the disclosure, in its application, is not limited to the details of the structure and arrangement of the components set forth in the following description or illustrated in the drawings. The disclosure permits other embodiments and can be exercised in various ways. It is understood that the formulations and terminology used herein serve the purpose of description and are not to be considered limiting. The use of "including" and "featuring" and variations thereof is intended to include the elements and equivalents listed below, as well as additional elements and equivalents thereof. DETAILED DESCRIPTION OF THE DRAWINGS

[0014] The present disclosure provides for a damper that can be combined with a torsion spring to improve spring performance. The term torsion spring is interchangeable with the term "torsion spring" as used herein. Torsion springs are often coupled with a damper so that the spring can drive a mechanical movement in a clockwise or counterclockwise direction while simultaneously being damped to control the rotational speed and / or resonance jump of the spring. Such springs are often metallic coil springs or clock springs.

[0015] For some applications, low-mass, low-torque metal springs may suffice. However, when metal springs are used in applications with high torque requirements, the specifications often necessitate the use of heavier-gauge wires to achieve the desired torque. This increases product mass and size / volume, which is often undesirable. In some applications, for example, the torsion spring and damper packaging must be small to fit in a designated storage space and must be aesthetically pleasing, while remaining unchanged over time, withstanding temperature variations, and operating quietly. Furthermore, certain materials may not be suitable for use in a damper in some applications. For instance, in high-temperature applications (such as temperatures above 60°C (140°F)), certain polymer materials may exhibit excessive orientation (e.g., tungsten carbide).B. melting or becoming more pliable), which can lead to undesirable deformation (e.g., annealing or warping) of the polymer material. Embodiments of the present disclosure discussed herein remedy some of these shortcomings.

[0016] Some existing damping devices known for use with hinge rotation of heavy vehicle components (e.g., vehicle doors, seats, tailgates, trunks, and tailgate latches) may include: (1) linearly moving gas springs; (2) silicone gel viscous dampers; (3) steel clock / coil springs; (4) friction dampers, such as those that use surface-to-surface friction to generate kinetic energy absorption (e.g., a Reell friction damper); and (5) steel torsion bar dampers, often designed as a viscous damper with a steel rod twisting within a viscous material. However, these known damping devices have several problems and limitations.

[0017] For example, common gas spring solutions are typically manufactured and designed using a metal tubular cylinder and a piston that holds high-pressure gas. The piston's motion control is limited to linear (e.g., straight-line) and / or non-rotating / swivel motion. The gas structure may also include a linear gas spring, which usually supports, but is not limited to, a separate, simple joint, such as a four-rod double-lever hinge. Furthermore, the structural packaging required for gas springs and their associated solutions typically occupies more space than is available in many applications (e.g., a vehicle seat). Additionally, the seals used in piston and cylinder designs tend to leak over time, resulting in gas pressure loss.Pressure loss can cause gas spring solutions to fail or significantly reduce the performance of the gas structure over a short period. Furthermore, gas springs are associated with high costs due to their complex design and manufacturing processes.

[0018] Silicone gel or viscosity dampers rely on the relatively high viscosity of the liquid or gel silicone to provide fluidic friction (e.g., resistance) for damping. Damping in rotary motion is typically limited to less than 1 Nm when silicone fluid housings are manufactured using thermoplastic construction, as is common practice in the industry.

[0019] When torque values ​​above 1 Nm are required, a metallic housing is generally necessary to absorb the resulting pressure. Silicone gel or viscosity dampers also require fluidic seals positioned to prevent the gel from leaking over time and during cyclic operation. The problem here is that metallic housings are typically made of die-cast aluminum or zinc, which significantly increases the mass of the solution and makes them unsuitable for many applications. Furthermore, high-torque applications (such as vehicle seats, tailgates, and doors) require the use of multiple silicone gel or viscosity dampers to provide the necessary damping effect in all positions. The problematic addition of mass associated with silicone gel or viscosity dampers would therefore be multiplied in these applications, making such dampers particularly unsuitable.Furthermore, the silicone gel used in common rotary dampers is highly temperature-dependent. In particular, the resistance torque of the silicone gel is measured at extreme temperatures, which determines the performance of the silicone gel dampers at these temperatures. For example, at cold temperatures (e.g., below -40 °C (-40 °F)), the viscosity of the silicone gel increases significantly, and at hot temperatures (e.g., above 85 °C (185 °F)), the viscosity of the silicone gel is greatly reduced.

[0020] As another example of the disadvantages of known damping devices, steel springs are sometimes used to counteract movement induced by a spring force or gravity acting on a solid closure or backrest. The counter-spring may be tuned to partially engage with the moving application through its movement, exerting a negative force on the application that slows its velocity or rotational inertia (e.g., moment of inertia). While this is a common solution, it has significant drawbacks. The performance of such damping springs deteriorates over time due to material fatigue during cyclic operation. It should also be noted that the hardening of the steel springs increases the brittleness of the steel material over time, which can lead to spring failure.As with other unsuitable dampers, the use of metallic components generally results in packaging that takes up more space than is available in many applications (e.g., in a vehicle seat) and a device whose weight is more than is feasible in many applications.

[0021] Additionally, steel springs are necessarily metallic, which can lead to disturbances and problems related to buzzing, squeaking and rattling noises (BSR noises) when used in the vehicle interior.

[0022] As a further example of the disadvantages of known damping devices, friction dampers typically utilize forces applied perpendicular to opposing surfaces, generating friction when the damper is rotated or moved linearly. These forces are usually induced by a metallic coil spring. Stress and wear on internal components can be a significant problem with these dampers, depending on the materials used to form the friction surfaces. This is especially true when less dense materials (e.g., viscoelastic and / or compressible rubber-like materials) are used for the friction surfaces. Alternatively, using denser materials can result in a damping device that is heavier than is practical for many applications.Furthermore, it is difficult to design friction dampers with "freewheel damping" (as described below), and any such design is likely to result in excessive size, complexity, and cost. Friction dampers typically provide little to no torque in at least one direction (usually counterclockwise) and may provide insufficient torque (e.g., 0.2 Nm torque damping) in the other direction (usually clockwise). Additionally, friction dampers offer little to no spring damping or torque assistance. Moreover, the engaging components of friction dampers tend to lose torque over time when subjected to multiple heating / cooling cycles, rendering the dampers completely unusable in applications with significant temperature fluctuations. This wear also reduces the service life of these dampers, often to unacceptable levels.Another problem with friction dampers is that the resins used in their damping tend to overheat and creep over time, causing the dampers to lose their initial resistance friction. Friction dampers are also known to generate noise, particularly squeaking, and are therefore undesirable for use in vehicle interiors.

[0023] The dampers of the present disclosure, discussed herein, remedy some of these shortcomings. The dampers mitigate the shortcomings by (1) providing a torsional damping device consisting entirely of polymeric materials (i.e., it contains no metallic components); (2) providing a torsional damping device capable of utilizing the viscosity / friction of the polymer material from which it is formed; (3) providing a torsional damping device capable of repeatedly withstanding torsional loads at 100% of the rotation for at least 1000 hours at extreme temperatures (e.g.,(4) to withstand temperatures below -40 °C (-40 °F) and above 85 °C (185 °F); (5) to provide a torsional damping device with a low mass sufficient for use in vehicle seats; (6) to provide a torsional damping device with a 3D volume and packaging size sufficiently small for use in vehicle seats; (7) to provide a torsional damping device that is sufficiently quiet during operation for use in a vehicle interior; (8) to provide a torsional damping device that is sufficiently independent for shipping and installation as part of an equipment variant; (9) to provide a torsional damping device that is highly scalable so that it may be suitable for use in particularly high-torque applications (e.g.in vehicle seats, vehicle tailgates and / or vehicle doors); (9) providing a rotation damping device capable of rotating and damping the movement of an application both clockwise and counterclockwise; (10) providing a rotation damping device easily configurable to include a 'freewheel' or 'idle' feature; (11) providing a rotation damping device capable of repeatedly returning to its home position (or 'zero position') after operation; and (12) providing a rotation damping device easily configurable to operate as a 'lift assist' device.

[0024] The Fig. Figures 1A-1C show a basic embodiment of a damper, illustrating the underlying concepts as used herein. Fig. Figures 2A-2C show a damper according to a preferred embodiment. Fig. Figures 10A-10F show a damper according to a further preferred embodiment. Dampers according to other preferred embodiments are also possible.

[0025] The Fig. Figures 1A-1C illustrate a basic embodiment of a damper 100 and the underlying concepts of the damper as used herein. The damper 100 includes a solid core 110, which can also be referred to as a compression limiter 110. The damper 100 also includes a first disk 120, which is located at a first end 112 of the compression limiter 110, and a second disk 130, which is located at a second end 114 of the compression limiter 110. The second end 114 is opposite the first end 112 with respect to the axial length of the compression limiter 110. The damper 100 also has a tension element 140.

[0026] Furthermore, the compression limiter 110 is arranged between the first disk 120 and the second disk 130, so that the first disk 120 and the second disk 130 are prevented from contacting each other by the compression limiter 110. The compression limiter 110 can have a cylindrical shape, as shown in Fig. Figures 1A-1C show the compression limiter 110. However, the compression limiter 110 can alternatively be designed in other shapes, such as a rectangular prism, a hexagonal prism, an octagonal prism, or the like. The compression limiter 110 can be elongated, such that its axial length AL in an axial direction AD is greater than a diameter D1 of the compression limiter 110. Alternatively, the compression limiter 110 can also have a wide shape, such that its diameter D is greater than its axial length AL in the axial direction AD. In one embodiment, the compression limiter 110 can be a cylinder. The compression limiter 110 can be composed of any suitable material for separating the first disk 120 and the second disk 130. In a particular embodiment, the compression limiter 110 consists of a hard polymer material, such as...Polyvinyl chloride (PVC), high-density polyethylene (HDPE), fluoropolymers (such as Teflon), polyamides (such as nylons, in particular nylon 6, nylon 66, nylon 12, nylon 13 and nylon 11), polyethylene terephthalate (PET), polybutylene terephthalate (PBT) or polyoxymethylene (POM). The compression limiter 110 composed of such materials can be advantageous because it has a relatively low mass, is inexpensive to manufacture and can also offer advantages with regard to the amount of friction generated between the compression limiter 110 and the tensile element 140.

[0027] The first disc 120 and the second disc 130 can be formed in any shape suitable for the application in which they are used.

[0028] For example, as in Fig. As illustrated in Figure 1A, the first disk 120 and the second disk 130 are both circular. In some embodiments, the disks 120, 130 can be rectangular, hexagonal, octagonal, or the like. The disks 120, 130 can be any size suitable for the application. In some embodiments, the first disk 120 and the second disk 130 can have a diameter D2 that is larger than the diameter D1 of the compression limiter 110. In alternative embodiments, the diameter D2 of the disks 120, 130 can be the same as or smaller than the diameter D1 of the compression limiter 110. The disks 120, 130 can be made of a hard polymer material, such as...The components may be made of polyvinyl chloride (PVC), high-density polyethylene (HDPE), fluoropolymers (such as Teflon), polyamides (such as nylons, in particular nylon 6, nylon 66, nylon 12, nylon 13, and nylon 11), polyethylene terephthalate (PET), polybutylene terephthalate (PBT), polyoxymethylene (POM), or other suitable materials. Furthermore, it is considered that the first disc 120 may be made of a different material than the second disc 130. It is also conceivable that the discs 120 and 130 may be made of the same material as the compression limiter 110. In some embodiments, it may be advantageous if the discs 120 and 130 are made of the same material as the tension element 140. In such embodiments, the tension element 140 and the discs 120 and 130 may be formed integrally as a single unitary component.

[0029] With renewed reference to Fig. In embodiment 1A, the tension element 140 is connected to the first disc 120 and the second disc 130 about a central axis CA. The tension element 140 can be a single band or a plurality of bands. For example, the tension element 140 can be configured to have three bands, five bands, ten bands, or more. In some embodiments, the plurality of bands of the tension element 140 can be evenly spaced about the central axis CA. In some embodiments, the tension element 140 can be a belt. In some embodiments, the tension element 140 is twisted about the central axis CA, so that the tension element 140 is elastically deformed and exerts a compressive force on the first disc 120 and the second disc 130, causing the discs 120 and 130 to engage with the compression limiter 110 at the first end 112 and the second end 114, respectively.In addition to the damping effects through elastic deformation and compression of the tension element 140, friction or resistance can be generated between the tension element 140 and an outer axial surface 142 of the compression limiter 110 and / or the disks 120, 130.

[0030] The materials suitable for the tensile element 140 must be able to withstand repeated torsional loading (from 100% to 600%) for at least 1000 hours at extreme temperatures (e.g., below -40°C (-40°F) and above 85°C (185°F)). Furthermore, suitable materials for a lightweight, compact torsional damper must meet certain material property restrictions. Non-restrictive examples of materials suitable for use in the tensile element 140 include thermosetting silicone elastomers, thermosetting fluorinated elastomers, and hybrids thereof. In some embodiments, the tensile element 140 may be composed of a solid silicone polymer.

[0031] The term "solid silicone polymer," as used herein, may refer to polymers composed mainly of silicone-containing monomer units, such as siloxane. As such, solid silicone polymer may also be referred to as solid polysiloxane. In some embodiments, solid silicone polymers may preferably be formed exclusively from silicone-containing monomer units. In some embodiments, solid silicone polymers may be copolymers formed from one or more silicone-containing monomer units and one or more other comonomer units (i.e., a solid silicone copolymer). In some embodiments, solid silicone polymer may be internally cross-linked. In some embodiments, solid silicone polymers may be thermosetting polymers. Solid silicone polymers, as used herein, are more likely to undergo elastic deformation than viscous flow.In particular, the tensile elements 140 formed using the solid silicone polymers can have a degree of polymerization of at least 100, or at least 200, or at least 500, or at least 1000. In some embodiments, a solid silicone polymer polymer polymer polymerised by polymerization with fluorine-containing functional groups and / or copolymerised with fluorine-containing comonomers may be particularly well suited for use in certain dampers.

[0032] The tensile element 140 can be composed of a solid silicone polymer, a solid silicone polymer grafted with fluorine-containing functional groups, mixtures, or any other combination thereof. In some embodiments, the solid silicone polymer can be a high-consistency silicone polymer, such as a high-consistency rubber (“HCR”), which is typically a thick gel. Because HCR silicone is in gel form, it is important that the molecular weight of the silicone polymer is high. For example, even before crosslinking, the HCR silicone polymer has a very high molecular weight compared to a “hand-mixed” two-component silicone resin or liquid silicone resin. Hot-vulcanized rubber produced via high-temperature vulcanization (HTV) or HCR contains polymers with high molecular weights and long polymer chains.HCR silicone possesses a number of important material properties, such as high viscosity, elasticity, recovery after stretching or compression, resistance to extreme temperature conditions, electrical properties and consistent viscosity similar to a putty.

[0033] Solid silicone polymer can be combined with certain additives to modify its physical properties. The solid silicone polymer can be combined with any additive that may be suitable for a particular application. For example, the solid silicone polymer can be combined with certain additives to increase or decrease its elasticity, tensile strength, heat resistance, creep resistance, lubricity, and / or other target properties. Non-restrictive examples of additives suitable for certain applications include fluoroelastomers such as PTFE or Teflon, or siloxane oil. In some embodiments, the tensile element 140 can be composed of a solid resin containing the solid silicone polymer and one or more additives. In some embodiments, the additives can be applied to the solid silicone polymer as a coating after polymerization and cooling of the polymer.The resin can be formed as a melt mixture of the solid silicone polymer and one or more additives.

[0034] Without relying on any specific theory, it is assumed that the very high molecular weight of the cross-linked HCR silicone polymer can withstand at least 1000 hours of continuous torsional stress (400 to 1200% torsional stress), with the resin being continuously exposed to 85 °C throughout the entire 1000-hour stress period, without suffering any unacceptable creep or annealing. This property is important for the functionality of dampers, considering the high stresses present in vehicle interiors.

[0035] The solid silicone polymer used in the tensile element 140 can have a yield strength of approximately 1 MPa to approximately 15 MPa, or of approximately 2 MPa to approximately 12 MPa, or of approximately 5 MPa to approximately 9 MPa, or of approximately 7 MPa, as measured according to ASTM D638. The solid silicone polymer used in the tensile element 140 can have an elongation at break of approximately 100% to approximately 2000%, or of approximately 200% to approximately 1800%, or of approximately 300% to approximately 1500%, or of approximately 400% to approximately 1200%, as measured according to ASTM D638. The solid silicone polymer used in the tensile element 140 can have an elongation at break of at least 200%, measured at -40 °C, or of at least 300%, measured at -40 °C, or of at least 400%, measured at -40 °C. The solid silicone polymer used in the tensile element 140 can also exhibit good creep resistance when subjected to continuous and / or repeated stress at 85 °C.A solid silicone polymer that exhibits good creep resistance can show less than 30% performance loss after 200 hours at 60°C (140°F) under 100% peak load.

[0036] The tensile element 140, made of solid silicone polymer, offers numerous advantages over tensile elements 140 made of other materials, particularly metallic materials. The solid silicone polymer provides high torsional strength while maintaining low mass and the ability to generate significant friction between itself and other components of the damper 100 (such as the compression limiter and / or the discs). Additionally, a tensile element 140 made of solid silicone polymer can be suitable for use in high-temperature environments (i.e., at temperatures above 60 °C (140 °F)).Without relying on any specific theory, the chemical structure of the HCR silicone polymer may prevent the solid silicone polymer from becoming excessively oriented in high-temperature situations, thus avoiding undesirable annealing of solid silicone polymers under such high-temperature conditions. Additionally, a tensile element 140 made of solid silicone polymer may be more cost-effective to produce and manufacture. These advantages allow the damper 100 with a tensile element 140 made of solid silicone polymer to be smaller, lighter, more versatile, less conspicuous, and less expensive, while also being capable of providing greater torque resistance, which may make the damper 100 particularly suitable for certain applications.

[0037] The tensile element 140 can be connected to the first disk 120 and the second disk 130 in any suitable manner. For example, the tensile element 140 can be mechanically attached or glued to the disks 120 and 130. In some embodiments, the tensile element 140 and the disks 120 and 130 can be formed in one piece as a unitary component made of a single material. For example, the tensile element 140 and the disks 120 and 130 can be simultaneously overmolded onto the compression limiter 110 in a one-shot injection molding process. In particular, the solid silicone polymer can be polymerized in the mold itself. Alternatively, the solid silicone polymer can be polymerized in a barrel of an extruder and extruded onto a mold.

[0038] With further reference to the Fig. In 1A-1C, the damper 100 can be twisted about its central axis CA. In some embodiments, the force that causes the damper 100 to twist about its central axis CA can be generated by a separate torsion spring with which the damper 100 is combined. When the damper 100 is twisted, the tension element 140 is loaded and expands, wrapping itself around the compression limiter 110, as shown in Fig. 1B and Fig. Figure 1C illustrates this. As the tension element 140 wraps around the compression limiter 110, it defines an angle 144 relative to an inner plane 146 defined by the first disk 120. The tension element 140 can be designed and arranged such that the angle 144 defined by the tension element 140 and the first disk 120 has any value less than 90°. For example, the angle 144 defined by the tension element 140 and the first disk 120 can have a value of more than 0° to less than 90°, or from 10° to 80°, or from 20° to 70°, or from 30° to 60°. In one embodiment, the angle 144 defined by the tension element 140 and the first disk 120 can have a value of approximately 45°. Since the tension element 140 continues to wrap around the compression limiter 110, the angle 144 defined by the tension element 140 and the first disc 120 can also change continuously.In particular, the angle 144 defined by the tension element 140 and the first disk 120 can be continuously reduced (towards an angle approaching 0°) as the tension element 140 continues to wrap around the compression limiter 110. When the damper 100 is twisted, the tension elements 140 also exert a compression force on the first disk 120 and the second disk 130, pulling the disks 120 and 130 towards each other, with the first disk 120 moving towards the first end 112 of the compression limiter 110 and the second disk 130 moving towards the second end 114 of the compression limiter 110. In some embodiments, the stretching (and eventual relaxation) of the tension element 140 can dissipate energy and reduce the rotational speed. In some embodiments, the compression force can generate friction, which can dissipate energy and reduce the rotational speed.

[0039] In some embodiments, sections of the compression limiter 110, the first disk 120, the second disk 130, and the tension elements 140 come into contact with one another and generate friction. The friction between the compression limiter 110 and the tension elements 140 slows down the rotational movement provided by the damper 100 and any torsion spring (not shown) with which it is combined. Additional friction can also be added to control the rotational speed of the torsion spring's return stroke. This friction / interference can be partially controlled by the design and composition of the tension element 140, the disks 120 and 130, and the compression limiter 110. The tension elements 140 also provide tensile resistance, which is converted into rotational resistance. In many applications (e.g.,In the case of a torsion spring used in a seat or a locking door of a motor vehicle, a torsional damping function is required to prevent jolting or sudden movement of the torsion spring at high speeds. Alternatively, the tension elements 140 can be designed to provide a torsional moment and thus act as a torsion spring, which may also be referred to here as a lifting support feature or lifting support device.

[0040] The speed-damping friction can be provided in several directions and at several locations. One is located axially between the tension element 140 and the axial surfaces of the compression limiter 110 and / or other fixed components. A second is located between the tension element 140 and the radial surface of the compression limiter 110 or a core (not shown). Another is located between sections of the tension element 140, in particular the plurality of bands that may be in contact while the tension element 140 is deformed. There are numerous factors that can be used to control or modify the friction that dampens the rotational speed of the damper 100 and any torsion spring with which it may be combined.

[0041] Characteristics such as the size, shape, construction, and spacing of the components of a damper 100 can influence the magnitude of the damping effect. For example, the diameter D2 of the discs 120, 130 relative to the diameter D1 of the compression limiter 110, and the presence or absence of features that increase the surface area of ​​the discs 120, 130 or axial surfaces of the compression limiter 110 (e.g., shafts, grooves, or knurling) also affect the magnitude of the generated damping effect. The cross-sectional area of ​​the tension element 140 also influences the magnitude of the generated damping effect, since a greater width of the tension element 140 increases the contact area between the tension element 140 and the compression limiter 110, thereby increasing the damping effect.Additionally, the polish or surface finish of the mold cavity in which the compression limiter 110 or the tension element 140 is formed, and thus the smoothness of these components, influences the magnitude of the damping effect. The choice of material / resin for the compression limiter 110 also affects the damping effect. Furthermore, the axial length AL of the compression limiter 110 can influence the damping effect. For example, a longer compression limiter 110 can generate a greater damping effect. The radial spacing of the tension elements 140, which can decrease or increase the interference with the compression limiter 110, also affects the damping effect.

[0042] Furthermore, the composition and properties of the solid silicone polymer and any resin in which it is incorporated also influence the damping effect produced. For example, the durometer of the solid silicone polymer used in the tensile element 140 can affect the degree of damping effect produced. Solid silicone polymers with a specific desired Shore A hardness exhibit ideal tackiness. Thus, the tackier the polymer, the greater the damping effect produced. Additionally, the final composition of the resin containing the solid silicone polymer, including the presence or absence of friction-modifying additives such as siloxane, polytetrafluoroethylene, fluorocarbons (derivatives of Teflon™), and / or other fluorine-based resins, can influence the degree of friction and damping effect produced.In this context, it should be mentioned that the coefficient of friction of the solid silicone polymer of the tensile element 140 and the material used in the compression limiter 110 affects the amount of friction generated, thereby influencing the torque of the device. The percentage of the resin's orientation used in the tensile elements 140 also affects their modulus of elasticity and thus the degree of damping effect. Specifically, the damping effect of the solid silicone polymer resin relates to the tensile stress and the release of tension in the tensile elements 140, as well as the return speed of the tensile elements 140 to their initial position. These properties can be controlled by incorporating additives that reduce the durometer of the polymer and thus influence the damping of the damper 100.In some embodiments, it may be advantageous to design the silicone polymer of the tensile element 140 with a durometer of 10 to 90, 20 to 80, 30 to 70, 40 to 60, or 40 to 50 Shore A hardness. As used herein, the term "low-modulus silicone polymer" may refer to a solid silicone polymer with a Shore A hardness of about 30 to about 45, the term "medium-modulus silicone polymer" may refer to a solid silicone polymer with a Shore A hardness of about 46 to about 60, and the term "high-modulus silicone polymer" may refer to a solid silicone polymer with a Shore A hardness of about 61 to about 75. The orientation of the stress-strain curve for the solid silicone polymer is also important, since a curved stress-strain curve facilitates energy dissipation.

[0043] The magnitude of the linear spring force in the axial direction AD acting on the compression limiter 110, the number of preloaded rotational turns on the damper 100 relative to the initial position (see Fig. 2A), the torque in relation to the rotational revolutions at the damper 100 relative to the starting position and the restoring speed of the tensioned polymer resin also influence the magnitude of the damping effect produced.

[0044] The solid silicone polymer can be modified to adjust its elongation or yield strength. Non-restrictive examples of modifications include varying the curing process for the solid silicone polymer (e.g., varying the process used to induce crosslinking within the solid silicone polymer). The solid silicone polymer can be cured and / or crosslinked with peroxide (such as Varox peroxide), or the crosslinking can be catalyzed with a catalyst such as platinum. The elongation strength of the solid silicone polymer can also be controlled by varying the molecular weight of the solid silicone polymer before curing / crosslinking (and subsequent curing of the solid silicone polymer).The solid silicone polymer with high molecular weight (and therefore low viscosity) before curing / crosslinking may have a lower modulus after crosslinking, in contrast to a solid silicone polymer with low molecular weight (and therefore high viscosity) before curing, which may have a high modulus after crosslinking.

[0045] Modifications to the solid silicone polymer that reduce elongation tend to increase the yield strength, which in turn tends to increase the torsional stiffness of the damper 100. Modifications that reduce the coefficient of friction between the tension element 140 and the compression limiter 110 (or between moving parts of the tension element itself) can improve the wear characteristics of the damper 100. Furthermore, a harder polymer resin reduces the friction between the compression limiter 110 and the tension element 140 (e.g., multiple bands), thereby reducing the damping effect and thus increasing the speed.

[0046] The plastic deformation of the solid silicone polymer can act as a damping agent through energy loss. The movement of the tensile element 140 made of solid silicone polymer can be damped by the energy loss during loading and unloading. In some embodiments, the plastic deformation of the tensile element 140 can be the primary damping force provided by the damper 100, which can contribute a greater damping effect than any friction that can be generated by the damper 100. In some embodiments, friction can be minimized so that the plastic deformation of the tensile element 140 is essentially the only damping effect provided by the damper 100. The dampers 100 can minimize internal friction by coating the tensile element 140 with a lubricant (e.g., grease or oil). Additionally or alternatively, other solid components of the damper 100 can be coated with a lubricant to minimize friction.

[0047] Advantageously, the dampers with tension elements 140 made of solid silicone polymer can be used in combination with tension springs that have a large torque range. Conventional liquid silicone dampers offer a resistance torque of only up to 70 Ncm, while high-torque dampers can provide resistance of up to 2000 Ncm. However, the dampers 100 of this disclosure incorporate tension elements 140 made of solid silicone polymer, which can offer high torque resistance values ​​between 2000 Ncm and 10,000 Ncm. Importantly, the dampers 100 of this disclosure offer this high torque resistance while maintaining a low weight and / or low mass and small volume, which is due to the use of a solid silicone polymer and the omission of heavy metallic components. For example, the damper 100 of this disclosure can advantageously be metal-free.Furthermore, the damper 100 of the present disclosure can advantageously be fluid-free, e.g., without silicone fluid. Typically, metallic and liquid silicone components increase the weight / mass and volume of the dampers 100. The aforementioned dampers 100 with high torque resistance, combined with low mass and small volume, are uniquely well suited for a range of applications, including use in automotive seats, doors, and tailgates.

[0048] One challenge in using silicone polymers in certain mechanical applications concerns their sliding properties. Silicone polymers are so slippery that conventional methods typically used to attach elastomeric parts to components (e.g., dovetails, snap fasteners, barbs, or arrowheads, as used in conventional plastic designs) may not be suitable for use with some silicone polymers. This necessitates alternative structures to incorporate some solid silicone polymers into specific applications. With reference to Fig. 2A takes these problems into account in a damper 200 according to a preferred embodiment.

[0049] The Fig. Figures 2A-2C show a damper 200 according to a preferred embodiment, which is capable of containing at least one tensile element formed from an HCR silicone polymer resin. The damper 200 has a core or cylinder 210 with a central opening 212 through it. The damper 200 also has a first set of projections 222 (each projection therein being a first projection 222), which may be part of a first solid component (in Fig. 2 not shown, but in the Fig. 8A-8D with 220 represented), and a second set of projections 232 (where each projection therein is a second projection 232) which forms part of a second fixed component (in Fig. 2 not shown, but in the Fig. 8A-8D with 230 shown). As in the Fig. As shown in Figures 2A-2C, the first set of projections 222 is configured as a smaller ring or a first diameter 224 surrounding the core 210, and the second set of projections 232 is configured as a larger ring or a second diameter 234 surrounding the first set of projections 222. As shown in Fig. As illustrated in Figure 2A, for example, the first set of projections 222 can be spaced at a first distance 224 from a center 236 of the central opening 212 and circularly surround the core 210. Additionally, the second set of projections 232 can be spaced at a second distance 234 from a center 236 of the central opening 212 and circularly surround the core 210. The damper 200 also has a tension element 240. The tension element 240 has bands 242 and internal cavities 244, as well as an inner section 246 and an outer section 248. The tension element 240, the first set of projections 222, and the second set of projections 232 are designed and positioned such that at least one first projection 222 and at least one second projection 232 with at least one cavity 244 of the tension element 240 are positioned. In the Fig. In the embodiment shown in Figures 2A-2C, a first projection 222 and a second projection 232 are positioned within each cavity 244 of the tension element 240. The bands 242 separate the cavities 244 from one another along the lateral sides of each cavity 244. The bands 242 also extend between the inner section 246 and the outer section 248 of the tension element 240. In some embodiments, the bands 242 extend tangentially between the first circle 224 and the second circle 234.

[0050] In the Fig. In the embodiment shown in Figures 2A-2C, the first projections 222 are configured to have a substantially cylindrical shape and an upper distal surface that is substantially flat. The first projections 222 can have a first diameter 224 of about 2 mm to about 12 mm or of about 3 mm to about 10 mm. In a particular embodiment, the first projections 222 can have a diameter of about 3 mm to about 8 mm or of about 4 mm. In the embodiment shown in the Fig. In the embodiment shown in Figures 2A-2C, the second projections 232 are also configured to have a substantially cylindrical shape and an upper distal surface that is substantially flat. The second projections 232 can have a second diameter 234 of about 2 mm to about 12 mm or of about 3 mm to about 10 mm. In a particular embodiment, the second projections 232 can have a diameter of about 3 mm to about 8 mm or of about 4 mm. In the embodiment shown in the Fig. In the embodiment shown in Figures 2A-2C, the first diameter 224 differs from the second diameter 234. In an alternative embodiment, however, the first diameter 224 can be the same as the second diameter 234. In another embodiment, the first diameter 224 can be larger than the second diameter 234.

[0051] As in the Fig. As shown in Figures 2A-2C, the first projections 222 are arranged in an inner circular row around the core 210. Each of the first projections 222 is connected to a common part, which is called the first solid component (not shown, but in the Fig. (Figures 9A-9D with 220 shown). The first solid component can be a plate arranged at a distal end of the first projections 222. In one embodiment, the first projections 222 can form a single, one-piece, unitary part with the first solid component. The first solid component can, for example, be a larger component that includes the first projections 222. In one embodiment, the first solid component (including the first projections 222) can be formed from a polymer material. The first solid component (including the first projections 222) can be formed from any suitable polymer material. Non-restrictive examples of suitable polymer materials are: PET (polyethylene terephthalate), PBT (polybutylene terephthalate), nylon, polyacrylates, and polycarbonates.An example of an alternative embodiment of a damper 200 with a first fixed component that includes the first projections is in the . Fig. 9A-9D shown.

[0052] Likewise, each of the second projections 232 is connected to a common part, which is referred to as the second fixed component (not shown, but in the Fig. (Figures 9A-9D with 230 shown). The second solid component is a separate part from the first solid component. The second solid component may be a plate arranged at a distal end of the second projections 232. In one embodiment, the second projections 232 may form a single, one-piece, unitary part with the second solid component. The second solid component may, for example, be a larger component that includes the second projections 232. In one embodiment, the second solid component (including the second projections 232) may be formed from a polymeric material. The second solid component (including the second projections 232) may be formed from any suitable polymeric material. Non-limiting examples of suitable polymeric materials are: PET (polyethylene terephthalate), PBT (polybutylene terephthalate), nylon, polyacrylates, and polycarbonates.In one embodiment, the second solid component can be made of a different polymeric material than the first solid component. An example of a damper according to one embodiment with a second solid component that includes the second projections is shown in the [reference]. Fig. 9A-9D shown.

[0053] It will now be referred to the in the Fig. Reference is made to the tension element 240 shown in Figures 2A-2C, wherein the tension element 240 is designed as a plate-like component with a cylindrical shape, the cross-sectional diameter of which (measured in the radial direction R) is greater than its depth (measured in the axial direction, which runs orthogonally to the radial direction R through the opening 212 of the core 210). The three-dimensional shape of the element shown in the Fig. The tensile element 240 shown in 2A-2C can be described as a cylindrical disk.

[0054] As from the Fig. 3A and Fig. As shown in Figure 3B, the tension element 240 of the damper 200 has an overall diameter OD (or outermost diameter), measured around the outermost circumference of the outer section 248 of the tension element 240 when the belt is in its rest / start position. The tension element 240 can have any overall diameter OD suitable for a particular application. In some embodiments, the tension element 240 can have an overall diameter OD of about 10 mm to about 200 mm, or of about 20 mm to about 200 mm, or of about 25 mm to about 150 mm. In a particular embodiment, the tension element 240 can have an overall diameter OD of about 30 mm to about 100 mm, or of about 30 mm to about 80 mm. Additionally, an outer edge 241 of the tension element 240 (i.e., the outer edge of the outer section 248 of the tension element 240) can be designed in a variety of different shapes. As in Fig. As shown in Figure 3A, the outer edge of the tension element 240 can, for example, be designed as a circle. Alternatively, as shown in Fig. As shown in Figure 3B, an outer section 248 of the tension element 240 may be configured to have an arc wave shape (i.e., a shape substantially similar to that of a series of sine waves), or it may be configured to have an substantially compartmentalized shape. Advantageously, a tension element 240 having an outer section 248 with an outer edge 241, which according to Fig. 3B, which is shaped, requires less material for formation and therefore contains less mass in the outer section 248, which can be advantageous in terms of cost savings and applications with weight restrictions. Fig. 3A and Fig. Figure 3B shows only two possible shapes for the outer edge of the outer section 248 of the tensile element 240, wherein the outer edge in embodiments may have any shape suitable for use in a particular application.

[0055] The tension element 240 of the damper 200 has an inner diameter ID, measured around the outermost circumference of the inner section 246 of the tension element 240 when the belt is in its rest / start position. The tension element 240 can have an inner diameter ID of approximately 1 mm to approximately 100 mm or of approximately 5 mm to approximately 50 mm. In a particular embodiment, the tension element 240 can have an inner diameter ID of approximately 10 mm to approximately 25 mm or of approximately 20 mm.

[0056] The tension element 240 of the damper 200 has a plurality of bands 242. In one embodiment, a single tension element 240 can have 1 to 75 bands, or 1 to 60 bands, or 2 to 50 bands, or 5 to about 50 bands, or about 10 to about 45 bands, or about 15 to about 40 bands, or 20 to 35 bands. In a particular embodiment, a single tension element 240 can have 20 to 30 bands, or about 25 bands. In one embodiment, the tension element 240 can have approximately the same number of bands 242 and cavities 244. Dampers according to some embodiments can include two or more tension elements 140. In dampers according to some embodiments, two or more tension elements 140 can be stacked on top of each other to increase the torque and / or change the spring rate by coupling a low-durometer disk with a high-modulus silicon disk.

[0057] The tension element 240 of the damper 200 has a plurality of cavities 244. In one embodiment, the tension element 240 can have approximately 2 to approximately 500 cavities, or approximately 2 to approximately 251 cavities, or approximately 2 to approximately 100 cavities, or approximately 2 to approximately 50 cavities, or approximately 5 to approximately 50 cavities, or approximately 10 to approximately 50 cavities, or approximately 20 to approximately 50 cavities. In a particular embodiment, the tension element 240 can have approximately 20 to approximately 30 cavities, or approximately 25 cavities. In one embodiment, the tension element 240 can have approximately the same number of cavities 244 and bands 242.

[0058] With renewed reference to the Fig. In 2A-2C, a damper 200 has a tension element 240 comprising a plurality of bands 242 and cavities 244, with a set of first projections 222 and a set of second projections 232, configured such that a first projection 222 and a second projection 232 are positioned in each cavity 244 of the tension element 240. Regarding the function of the damper 200 and the tension element 240, the tension element 240 (especially the bands 242) functions similarly to the tension element 140 of the damper 100, as described above. In particular, it shows Fig. 2A the damper 200 in a rest position or a starting position. Fig. Figure 2B shows the same damper 200 after it has undergone a relatively small rotation in radial degrees. Fig. 2C shows the same damper 200 after it has undergone a relatively large rotation in radial degrees. As in the Fig. 2B and Fig. As shown in Figure 2C, the bands 242 of the tension element 240 are stretched and / or deformed when the damper 200 rotates. The force required to stretch the bands 242 contributes at least partially to the torque required to rotate the damper 200 (i.e., it contributes to the damping effect of the damper 200). Additionally, as shown in Figure 2C, the bands 242 of the tension element 240 are stretched and / or deformed when the damper 200 rotates. The force required to stretch the bands 242 contributes at least partially to the torque required to rotate the damper 200 (i.e., it contributes to the damping effect of the damper 200). Fig. Figure 2C shows that sufficiently large rotations of the damper 200 cause the bands 242 to be stretched / deformed such that each band 242 directly contacts one or more other bands 242. In addition to the force required to stretch the bands 242, mutually contacting bands 242 also generate frictional and compression forces, which also contribute to the torque required to rotate the damper 200 and thus to the damping effect of the damper 200.

[0059] It will now be on Fig. Reference is made to Figure 3C, wherein the bands 242 of the tension element 240 have an hourglass or isthmus shape, although in other embodiments the bands may have any suitable shape. The bands 242 are configured to have a lower section 242A (i.e., the section of the band 242 near the inner section 246 of the tension element 240). As shown in Fig. As illustrated in Figure 3C, the lower section 242A of the band 242 is substantially wedge-shaped or substantially triangular. Likewise, the bands 242 are configured to have an upper section 242C (i.e., the section of the band 242 near the outer section 248 of the tension element 240), which may also be substantially wedge-shaped or substantially triangular. In other embodiments, the projections 222, 232, and the cavities 244 may be configured such that the lower section 242A and the upper section 242C may have any suitable shapes. Between the lower section 242A and the upper section 242C, the band is configured to have a middle section 242B (which may also be referred to as the leg 242B of the band 242). In the embodiment shown in the Fig. 2A--2C and the Fig. In the embodiment shown in 3A-3C, the central sections 242B of the bands 242 are essentially rectangular, as shown in Fig. 3C is most clearly visible.

[0060] As in Fig. 3A and in Fig. As shown in Figure 3C, the belts 242 of the tensioning element 240 have a belt thickness BT and a belt length BL. The belt thickness BT is the thickness as measured at the center of the middle section 242B of the belt 242 when the belt is in its rest / start position. The belts 242 of the tensioning element 240 can have any thickness suitable for a particular application. In some embodiments, the belts 242 of the tensioning element 240 can have a belt thickness BT of about 0.5 mm to about 20 mm, or of about 1 mm to about 15 mm, or of about 1.5 mm to about 12 mm. In a particular embodiment, the belts 242 of the tensioning element 240 can have a belt thickness of about 2.5 mm to about 4 mm, or of about 3 mm.A band length BL is measured from the uppermost edge of the middle section 242B of the band 242, i.e., the edge of the middle section 242B that is closest to the upper section 242C of the band 242 but still has a uniform band thickness BT (i.e., the lateral edges of the band are not substantially arcuate at this point), to the lowest section of the middle section 242B of the band 242 (i.e., the edge of the middle section 242B of the band 242 that is closest to the lower section 242A) but still has a uniform band thickness BT (i.e., the lateral edges of the band are not substantially arcuate at this point), when the band 242 is in its rest / start position. The bands 242 of the tension element 240 can have any band length BL suitable for a particular application.In some embodiments, the bands 242 of the tension element 240 can have a band length BL of about 1 mm to about 100 mm, or of about 1 mm to about 50 mm, or of about 2 mm to about 25 mm, or of about 3 mm to about 20 mm, or of about 4 mm to about 15 mm. In a particular embodiment, the bands 242 of the tension element 240 can have a band length of about 3 mm to about 8 mm, or of about 5 mm.

[0061] As in Fig. As can be seen in Figure 2A, the tension element 240 is designed such that the straps 242 are arranged at an angle relative to the core 210. As shown in the Fig. 4A and Fig. As shown in Figure 4B, an alternative configuration of the tension element can be designed such that the straps 242 are not angled with respect to the core 210 (or have a 0° angle to the core), as shown in Fig. 4A shown, or at an angle as shown in Fig. 2A and Fig. 4B is shown. As in Fig. As shown in Figure 4A, for example, the center of the first projection 222 and the center of the second projection 232 can be aligned along an imaginary line IL extending from the center C of the central opening 212. An approach angle of the bands 242 can alter the performance of the tension element and thus of the damper. For example, a tension element 240 configured such that the bands 242 are arranged at an angle of zero degrees may require substantially the same torque to stretch / extend its bands via a clockwise rotation of the damper 200 as it does via a counterclockwise rotation of the damper 200.

[0062] Fig. Figure 5 shows a stress-strain curve for a silicone polymer that can be used in tension elements of dampers according to embodiments. As can be seen, the first 50% of the stress-strain curve is relatively flat. Stretching / extending the tension element through this section of the curve therefore requires relatively little force and thus results in a relatively low torque / damping effect for the damper according to the embodiment during stretching. A damper according to an embodiment with a tension element designed such that the bands stretch / deform over a large part of this section of the stress-strain curve during rotation of the damper can be useful to initially provide a rotational movement with less damping for the early phase of the spring / application's rotation and subsequently an increased damping effect as the spring / application approaches its end of movement.

[0063] Alternatively, a damper according to one embodiment can be configured with a tension element 240 whose bands are arranged at an angle relative to the core. The tension element 240 can, for example, have bands 242 arranged at an angle of approximately 0° to approximately 85° or of approximately 0° to approximately 75° relative to the core 210. In the Fig. In the embodiment shown in 4B, the tensile element has 240 bands which are designed at an angle of approximately 20° relative to the core. Fig. Figure 4B thus shows a pre-stressed tension element 240. A pre-stressed tension element 240 can be useful in dampers according to one embodiment that are intended to dampen rotational movement in only one direction (i.e., only counterclockwise or only clockwise). The larger the approach angle of the bands, the faster the bands are stressed during rotation, since the silicone strain-stress curve has a steeper slope from positions of higher stress, as shown in Figure 4B. Fig. 5 shown. Alternatively, the tension element 240 can be used with bands 242, which replace the ones shown in the Fig. 2A-2C, Fig. 3A-3C and Fig. The straight bands shown in Figures 4A-4B are actually curved bands. The curved bands experience a small amount of torque during the early part of the damper's movement because straightening the curved bands would result in nearly zero torque. Therefore, the damper would only experience significant torque once it has rotated far enough for the bands to straighten. This band curvature and subsequent zero-torque rotation is an example of a "freewheel rotation" or "freewheel feature," which is described in more detail below.

[0064] With reference to the Fig. Figures 6A-6C show further three-dimensional shapes for tension elements that can be used in dampers according to embodiments. Fig. Figure 6A shows a tension element with a three-dimensional shape similar to that of the damper 200 according to an embodiment described in the Fig. 2A-2C is shown. Fig. Figure 6B shows a tensile element with a three-dimensional shape and a depth (measured in axial direction A) that is greater than the depth of the tensile element that is in Fig. 6A is shown. Fig. Figure 6C shows a tensile element with a three-dimensional shape and an even greater depth (measured in axial direction A) than the one in Fig. Figure 6B shows the tension element. It is important to note that the depth of the tension element correlates positively with the total amount of torque required to deform / tighten the tension element (especially the bands of the tension element) when the damper rotates. Therefore, as the depth of the tension element increases, the total amount of torque (e.g., the total damping effect) of a damper according to one embodiment also increases.

[0065] With reference to Fig. 7. The cavities 244 of the tension element 240 are configured to have a teardrop shape (e.g., two circles with two outer tangents). In other embodiments, however, the cavities 244 can have any suitable shape. For example, the cavities 244 can have a substantially elliptical shape or a substantially rectangular shape. As in Fig. As can be seen in Figure 7, the cavities 244 of the tension element 240 also have a cavity length, measured from the center point of the first projection 222, which is positioned inside the cavity 244, to the center point of the second projection 232, which is positioned inside the cavity 244 when the belt is in its rest / start position. This distance can also be referred to as the form length of the first projections 222 and the second projections 232. The cavity 244 can have a form length of approximately 1 mm to approximately 75 mm, or of approximately 2 mm to approximately 60 mm, or of approximately 3 mm to approximately 50 mm, or of approximately 3 mm to approximately 25 mm, of approximately 5 mm to approximately 15 mm, or of approximately 8 mm to approximately 12 mm.

[0066] It will now be referred to as Fig. Reference is made to 8A-8D, wherein an embodiment of a damper assembly 250 is shown, comprising a damper similar to the damper of the Fig. 2A-2C and the Fig. Includes 3A-3C. Fig. Figure 8A shows a complete exploded view of the damper assembly 250. The damper assembly 250 includes the damper 200, which is composed of a first fixed component 220 with a first set of projections 222 and a second component 230 with a second set of projections 232, wherein the first and second fixed components 220, 230 are configured such that the side of the first set of projections 222 extends towards the second fixed component 230 and the second set of projections 232 extends towards the first fixed component 220. As shown in Fig. As shown in Figure 8A, the damper assembly 250, including the damper 200, also has a tension element 240, which is positioned between the first fixed component 220 and the second fixed component 230. Fig. 8B shows the damper assembly 250 from Fig. 8A, wherein the first fixed component 220 is positioned on the housing 251.

[0067] Fig. 8C shows the damper assembly 250 of the Fig. 8A and Fig. 8B, wherein the tension element 240 is arranged on the first fixed component 220, which in turn is arranged on the housing 251. The tension element 240 is designed and positioned such that each projection in the first set of projections 222 extends through a cavity 244 of the tension element 240 and is thereby separated from each other projection of the first set of projections 222 by at least one band 242 of the tension element 240.

[0068] Fig. 8D shows the damper assembly 250 of the Fig. 8A-8C, wherein the second fixed component 230 is positioned on the housing 251, together with the tension element 240 and the first fixed component 220. The second fixed component 230 is designed and positioned such that each projection in the second set of projections 232 extends through a cavity 244 of the tension element 240 and is thereby separated from each other projection of the second set of projections 232 by at least one band 242 of the tension element 240. In the Fig. In the damper assembly 250 shown in Figure 8D according to the embodiment, a first projection 222 and a second projection 232 extend through each cavity 244 in the tension element 240. Alternatively, in some embodiments, one or more cavities 244 may not have a first projection and / or a second projection 222, 232 extending through them. After assembly, the damper assembly 250 is clamped. In the embodiment shown in Fig. In the embodiment shown in Figure 8D, the damper assembly 250 is clamped by securing the second fixed component 230 to the housing 251 via locking openings 254 on the housing 251 and complementary locking openings 234 on the second fixed component 230. The damper assembly 250 can then be attached to an application, for example a vehicle seat or a vehicle lock, using mounting means 256.

[0069] It will now be referred to as Fig. Reference is made to 9A-9D, wherein an alternative embodiment of a damper assembly similar to the damper of the Fig. 8A-8D is shown, which Fig. However, 9A-9D show the damper 200, which is designed to include a "freewheel" or "idle" feature. It is first applied to Fig. 9A is referenced, whereby a damper 900 has a compression limiter (not from the one in Fig. The angle shown in 9A is evident, but as in Fig. 9B with 910 shown). The damper 900 also has a first disc 920 and a second disc 930, which are arranged at a first and second end of the compression limiter respectively, as well as a tension element (not visible from this angle). The tension element of the damper 900 is essentially the same as the tension element of the damper 100, shown in Fig. 8A-8C. In particular, the tension element of the damper 900 is connected to the first disc 920 and the second disc 930. Similar to the tension element 240 of the damper 200, the tension element of the damper 900 is designed to wrap around the compression limiter when the damper 900 is twisted about a longitudinal axis LA. In this way, the tension element of the damper 900 provides essentially the same advantages to the damper 900 as the tension element 240 provides to the damper 200. The damper 900 has a hexagonal opening 916. This opening 916 is designed to receive a fastening mechanism (e.g., a bolt) that can be used to fasten the damper 900 to an application, such as a motor vehicle seat. The opening 916 can be rotated by the application while the application is operating / moving.For example, the opening 916 can be rotated by a motor vehicle seat when the seat is folded in and out via a hinge. In another embodiment, the opening 916 can have a different shape.

[0070] Next, we will look at Fig. Reference is made to Figure 9B, where the damper 900 is shown in the bottom view as part of the damper assembly 940. In particular, the damper 900 is arranged between a cap 950 and a base plate 960. Together, the damper 900, the cap 950, and the base plate 960 form the damper assembly 940. The cap 950 has a cap opening 956, which is arranged approximately in the center of the cap 950 and through which a section of the first disk 920 and the opening 916 of the damper 900 are visible and accessible in their entirety. The cap opening 956 is in Fig. 9B is shown as a circle. However, the cap opening 956 can also form any other suitable shape, including, but not limited to, an ellipse, square, rectangle, hexagon, or octagon. The cap 950 also has a plurality of peripheral cap openings (not visible from this angle, see Fig. 9C, designated with 954), which are arranged circumferentially around the circumference of the cap 950. The base plate 960 has a base plate opening 966, which is located approximately in the center of the base plate 260 and through which at least a section of the opening 916 of the damper 900 is visible / accessible. At least a section of the opening 916 can be simultaneously aligned with both the cap opening 956 and the base plate opening 966 about the longitudinal axis LA, so that an object and / or a fastening mechanism (e.g., a bolt) can extend simultaneously through each of the opening 916, the cap opening 956, and the base plate opening 966. The base plate 960 also has a plurality of peripheral base plate openings 964, which are arranged circumferentially around the circumference of the base plate 960. The peripheral cap openings 954 can be aligned with the peripheral base plate openings 964, so that objects (e.g.bolts) can simultaneously extend through each pair of peripheral cap openings 954 and one peripheral base plate opening 964 to fasten the cap 950 to the base plate 960. The cap 950 and / or the base plate 960 are shaped such that the entire damper 900 can be enclosed between the cap 950 and the base plate 960 when the cap 950 is fastened to the base plate 960 via the pairs of peripheral cap openings 954 and peripheral base plate openings 964 (i.e., when the assembly is in an assembled state). For example, in the in . Fig. In the embodiment shown in 9B-9D, the cap 950 provides a cavity 958 in which the entire damper 900 can be enclosed when the damper assembly 940 is in an assembled state.

[0071] Additionally, the damper 900 has a plurality of locking elements 932 arranged on the lower surface of the second disc 930. The locking elements 932 protrude from the lower surface of the second disc 930. In the Fig. In the embodiment shown in Figure 9B, the locking elements 932 are essentially T-shaped or cross-shaped. In other embodiments, the locking elements 932 can have any suitable shape, including square, rectangular, hexagonal, or octagonal.

[0072] It will now be on Fig. 9C is referenced, with the damper assembly 940 being of Fig. Figure 9B shows a top view. In particular, a plurality of locking openings 962 are visibly arranged on the upper surface of the base plate 960. The locking openings 962 have essentially the same shape and size as the locking elements 932. The locking openings 962 can extend over the entire thickness of the base plate 960, thereby forming a plurality of openings in the base plate 960. Alternatively, the locking openings 962 can extend only over a portion of the thickness of the base plate 960, thereby forming a plurality of indentations / recesses in the base plate 960. The locking openings 962 can be aligned with the locking elements 932, so that the locking elements 932 can be positioned within the locking openings 962.

[0073] With reference to Fig. Figure 9D shows the damper assembly 940 (i.e., the damper 900, the cap 950, and the base plate 960) in its assembled state. The locking elements 932 of the damper 900 are positioned in the locking openings 962 of the base plate 960, and the second disc 930 of the damper 900 is thereby secured / held in a fixed position by the base plate 960 (i.e., the second disc 930 is prevented from rotating when the damper 900 is twisted). Thus, at least a portion of the first disc 920 and / or the compression limiter 910 can move relative to the second disc 930 when the damper 900 is driven (i.e., twisted about its longitudinal axis) by an application, such as a motor vehicle seat. This movement stretches the tension element and causes the tension element to touch the compression limiter 910 and wrap around it, which at least partially enhances the damping effect of the damper 900.

[0074] With renewed reference to the Fig. 9A and Fig. 9C has the first disc 920 slots 922 and has the compression limiter 910 posts 942. As in Fig. As shown in Figure 9A, the compression limiter 910 includes posts 942 arranged to align with and pass through the slots 922 of the first disk. When the damper 900 is twisted about its longitudinal axis LA such that the posts 942 move along the slots 922, the damper 900 is not subjected to load until it has been twisted to the point where the posts 942 meet the opposite end of the slots 922 (i.e., the first object / obstacle the posts 942 encounter is the edge of the slots 922). This unloaded portion of the twisting by the damper 900 is referred to herein as the "freewheeling". During the freewheeling, the rotational speed of the damper 900 and any torsion spring with which it may be combined is undamped.Once the damper 900 is sufficiently twisted so that the posts 942 meet the ends of the slots 922, any further twisting of the damper 900 will subject the damper 900 to a load similar to that described above with reference to . Fig. 8A-8C described. The length of the free play can be modulated by varying the length of the slots 922, with a longer slot length allowing for more free play. In some embodiments, the damper 900 can have any number of pairs of posts 942 and slots 922. This is illustrated by the damper 900 shown in Fig. 9A is shown as having two pairs of posts 942 and slots 922, while the damper 900 is in Fig. Figure 9C is shown as having three pairs of posts 942 and slots 922, both embodiments being valid for the damper 900. It is also conceivable that the damper 900 has any number of pairs of posts 942 and slots 922, such as 1 pair, 4 pairs, 5 pairs, or more. This has the advantage that the damper 900 allows the torsion spring to move freely over a certain length of travel before exerting a damping effect on the movement of the torsion spring.

[0075] It will now be referred to as Fig. Reference is made to 10A-10F, where an alternative embodiment of a damper 1000 is shown. First, reference is made to the Fig. 10A and Fig. Reference is made to Figure 10B, where a first fixed component 1020 for the damper 1000 is shown. The first fixed component 1020 is designed as a holy cylindrical structure or holy cylindrical tube. The first fixed component 1020 has a plurality of first projections 1022 extending inwards from the outer cylindrical wall 1024 (i.e., towards the radial central first fixed component 1020 in each radial direction R perpendicular to the axial direction AD).

[0076] The first solid component 1020 is formed from a plurality of first solid modular subcomponents (1022A, 102B, 102C, 1022D, 1022E and 1022F). Each of the first solid modular subcomponents 1022A-1022F is designed as a cylindrical ring with substantially the same shape as the larger first solid component 1020, except that it has a shorter length in the axial direction AD. Each of the first fixed modular subcomponents 1022A-1022F contains a plurality of first projections 1022. Each of the first fixed modular subcomponents 1022A-1022F also contains a linking feature 1026 and a receiving feature 1028 for coupling each first fixed modular subcomponent (such as 1022A) with another first fixed modular subcomponent (such as 1022B) to form the larger and / or longer first fixed component 1020.

[0077] During the Fig. In the embodiment shown in Figures 10A-10F, all first fixed modular subcomponents 1022A-1022F are essentially identical. In some embodiments, each of the first fixed modular subcomponents 1022A-1022F can be formed in a manner that is essentially identical, such as using the same shape. An advantage of this modularity of the first fixed modular subcomponents 1022A-1022F is that a larger first fixed component 1020 of virtually any length can be formed without varying the manufacturing processes used to form the first fixed modular subcomponents 1022A-1022F.

[0078] It will be specifically addressed Fig. Reference is made to 10A, where the first fixed component is 1020, with most of the first fixed modular subcomponents (1022C, 1022D, 1022E, and 1022F) being separate from each other. However, the first fixed modular subcomponents 1022A and 1022B are shown as being connected to each other via the linking feature 1026 of the first fixed modular subcomponent 1022B and the receiving feature 1028 of the first fixed modular subcomponent 1022A. In Fig. In contrast, 10B shows that all first modular subcomponents (1022A, 1022B, 1022C, 1022D, 1022E, 1022F) are connected to each other via their linking features 1026 and receiving features 1028.

[0079] With reference to Fig. Figure 10C shows a second fixed component 1030 for the damper 1000. Like the first fixed component 1020, the second fixed component 1030 includes a body 1031 designed as a hollow cylindrical structure or hollow cylindrical tube. The second fixed component 1030 has a plurality of second projections 1032 extending outwards from the outer cylindrical wall 1024 (from the radial central second fixed component 1030 in each radial direction R). In the Fig. In the embodiment shown in Figure 10C, the second set of projections 1032 is configured such that the second projections 1032 are arranged in a plurality of rows extending along the length of the second fixed component 1030 in the axial direction AD. The second fixed component 1030 also includes an opening 1034 extending longitudinally through the length of the second fixed component 1030 along the axial direction AD.

[0080] It will now be on Fig. Reference is made to Figure 10D, which shows the tension element 1040 and the second fixed component 1030. The tension element 1040 is coupled to the second fixed component 1030. The tension element 1040 has bands 1042 extending along the length of the second fixed component 1030 in the axial direction AD. Each row of second projections 1032 is supported on the right side by at least one band 1042 and / or on the left side by at least one band 1042. In the Fig. In the embodiment shown in Figure 10C, each row of second projections 1032 is supported on the right side by a band 1042 and on the left side by a band 1042. In the embodiment shown in Fig. In the embodiment shown in 10C, the tensile element 1040 thus has two bands 1042 for each row of projections of the second set of projections 1032.

[0081] The tension element 1040 can also include one or more longitudinal caps 1046. The straps 1042 of the tension element 1040 are connected to the longitudinal caps 1046. In some embodiments, the tension element 1040 is a single, one-piece, unitary element, and therefore the straps 1042 are formed integrally with the longitudinal caps 1046. In alternative embodiments, the straps 1042 can be attached to the longitudinal caps 1046. In embodiments without longitudinal caps 1046, the tension element 1040 can be attached directly to the first fixed component 1020 and / or the second fixed component 1030 using any suitable fastening method. The tension element 1040 of the in Fig. The embodiment shown in Figure 10C has two longitudinal caps 1046 positioned at each longitudinal end of the second fixed component 1030, with a plurality of bands 1042 extending between the longitudinal caps 1046. The tension element 1040 is designed as a single, one-piece, unitary element comprising the bands 1042 and the longitudinal caps 1046 arranged at each end of the bands 1042.

[0082] The tension element 1040 has a plurality of cavities 1044 between the bands 1042. The second fixed component 1030 and the tension element 1040 are designed such that the rows of the second projections 1032 are positioned within some of the cavities 1044 of the tension element. In the Fig. In the embodiment shown in Figure 10D, not all cavities 1044 have a second projection 1032 extending through them. However, in alternative embodiments, each cavity 1044 can have a second projection 1032 extending through it.

[0083] It will now be referred to as Fig. 10E and Fig. Reference is made to 10F, where the first fixed component is 1020, the second fixed component is 1030, and the tensile element is 1040. In Fig. Figure 10E shows the second fixed component 1030 with the tension element 1040 mounted on it, positioned longitudinally behind and in line with the first fixed component 1020. Fig. 10F is the second fixed component 1030 with the tension element 1040 mounted on it, shown as provided within the first fixed component 1020. As in Fig. As shown in Figure 10F, the first projections 1022 of the first fixed component 1020 extend radially inward toward the second fixed component 1030, while the second projections 1032 of the second fixed component 1030 extend radially outward toward the first fixed component 1020. The tension element 1040 is positioned between the second fixed component 1030 and the first fixed component. The first fixed component 1020 and the second fixed component 1030 are designed and positioned such that the first projections 1022 of the first fixed component 1020 extend into at least some of the cavities 1044 of the tension element 1040. The first projections 1022 of the first fixed component 1020 can extend into at least some of the cavities 1044 of the tension element 1040 that do not have a second projection 1032 of the second fixed component 1030 extending through them. In the embodiment described in Fig. As shown in Figure 10F, first projections 1022 of the first fixed component 1020 extend into all cavities 1044 of the tension element 1040 that do not have a second projection 1032 of the second fixed component extending through them. In some embodiments, however, a damper 1000 may have a plurality of first projections 1022 and a plurality of second projections 1032 extending into each cavity 1044 of the tension element 1040.

[0084] In Fig. Figure 11 shows a side guard 1100 for a motor vehicle seat. A damper 1110 is installed in the side guard. The damper 1110 can be used to slow down the speed of movement of the motor vehicle seat, the movement of which is driven by a torsion spring. Fig. Figures 12A-B illustrate the movement of a motor vehicle seat both with and without a tension spring damper. Fig. Figure 12A illustrates that a damper of the present disclosure can slow down the speed of the rotational movement of the motor vehicle seat, which has a beneficial effect on a safer, smoother and more luxurious feeling of movement. Fig. Figure 12B illustrates the vehicle seat without the tension spring damper at a high speed of rotation of the vehicle seat, which can lead to a jerking motion.

[0085] With reference to the Fig. Sections 13A-13F present descriptions and diagrams of test data relating to "torque vs. angle of rotation" for specific example dampers. In these test examples, certain damper parameters are varied according to a given embodiment, and different silicone polymers, as described herein, are used. Fig. Figure 13A shows a representation of various movements of a potential application for the dampers, which were used in the tests for the Fig. 13C-13F were performed, and it has been replicated. Fig. Figure 13A, for example, illustrates the motor vehicle seat in a starting position, moving to a folded position and back to the starting position.

[0086] Fig. Figure 13B shows an example of a "torque vs. angle of rotation" curve for a low-modulus HCR silicone polymer to illustrate the concept of energy dissipation (e.g., damping) achieved using the silicone polymer. The curve is shown in the diagram. Fig. The exemplary curve shown in Figure 13B is the actual calculated curve for a low-modulus HCR silicone polymer, as described in the Fig. Figures 13C-13F are shown similarly. Because the stress-strain modulus section of the curve is curved (rather than straight), the solid silicone polymer dissipates energy through plastic deformation. This dissipated energy is represented by the colored area between the curves. In this way, the damper can be designed to utilize either the slowly rising section of the curve (low modulus) or the steep section of the curve (high modulus). The result is different spring rates per unit length. The curve in Fig. Figure 13B illustrates how the torque in the loading direction is not the same as in the unloading direction, as demonstrated by the example in the Fig. 2A-2C and Fig. This can be demonstrated using the damper shown in Figures 3A-3C. Therefore, the total work (W = FD) required to unload the tension element is less than the work required to load it. The difference in work due to plastic deformation leads to an energy loss or damping of the kinetic energy. Furthermore, the normal force of the tension element on the rotor, which may be a torsion spring, causes a frictional force that contributes to the overall damping rate.

[0087] Fig. Figure 13C shows a torque-versus-rotation curve for a low-durometer silicone polymer for a damper according to an embodiment with a mold length of approximately 8 millimeters. Due in part to the low durometer of the silicone polymer, the curve exhibits a peak torque of 26-30 Nm, measured at three different temperatures (-40 °C, 23 °C, and 85 °C). The damper was continuously rotated at 1 rpm at each temperature. The resulting torque was measured and plotted. As can be seen from the graph, there is minimal performance variation (i.e., torque) even between the extreme temperatures. This temperature independence is novel for the field of torsional spring damping and is advantageous in a number of applications where a damper may be exposed to a wide range of temperatures during operation (e.g.,in motor vehicle seats, motor vehicle doors, motor vehicle tailgate locks, etc.).

[0088] Fig. Figure 13D shows a torque-versus-angle curve for a medium-durometer silicone polymer incorporated into a damper according to an embodiment with a mold length of approximately 8 millimeters. The curve exhibits a higher peak torque of 32–45 Nm, measured at three different temperatures (-40 °C, 23 °C, and 85 °C), partly due to the slightly increased durometer hardness of the silicone polymer. The curve of Fig. 13C also shows minimal deviations in the polymer's performance at extreme temperatures, with the exception that Fig. 13C shows a slightly larger deviation towards the end of the movement. Without relying on any specific theory, this may be related to the tendency of silicones with higher durometer hardness to exhibit more plastic and less elastic behavior compared to silicones with lower durometer hardness. This can make the performance of silicones with higher durometer hardness somewhat non-Newtonian at high temperature and higher torque, since high-temperature materials generally have lower tensile strength. Friction factors can also influence this phenomenon.

[0089] Fig. Figure 13E shows a torque-versus-angle curve for a low-durometer silicone polymer for a damper according to an embodiment with a mold length of approximately 12 millimeters. The curve exhibits a peak torque of 10-11 Nm, measured at three different temperatures (-40 °C, 23 °C, and 85 °C), partly due to the medium durometer hardness of the silicone polymer and the longer 12-mm mold length. The damper was rotated continuously at 1 rpm at each temperature. The resulting torque was measured and plotted. As can be seen from the graph, there is a minimal performance variation (i.e., torque) even between the extreme temperatures. Without relying on any specific theory, the longer mold length (12 mm) and the resulting percentage resin elongation during rotation may contribute to this improved temperature independence of medium-durometer silicone.

[0090] Fig. Figure 13F shows a torque-versus-angle curve for a medium-durometer silicone polymer incorporated into a damper according to an embodiment with a mold length of approximately 12 millimeters. The curve exhibits a peak torque of 15-18 Nm, measured at three different temperatures (-40 °C, 23 °C, and 85 °C), partly due to the low durometer of the silicone polymer and the longer 12-mm mold length. The damper was continuously rotated at 1 rpm at each temperature. The resulting torque was measured and plotted. As can be seen from the graph, there is a minimal variation in performance (i.e., torque) even between the extreme temperatures. Without relying on any specific theory, the in Fig. In the diagrammatically represented tests (13F), the material with low durometer hardness used exhibited the highest coefficient of friction, which is related to the stress and relaxation sides of the curve (e.g., the "X-scale gap") and can be described as frictional damping. The longer mold length (12 mm) and the resulting percentage resin elongation during rotation may contribute to this improved temperature independence of silicone with medium durometer hardness.

[0091] With reference to Fig. Figure 14 is a non-limiting example of a possible method for manufacturing a damper according to one embodiment. As shown in Fig. As shown in Figure 14, the tension element can be molded onto one or more other components of the damper. As also shown in Figure 14. Fig. As shown in Figure 14, one or more solid components can be formed separately from the tension element, with the tension element being overmolded onto one or more of these components. The silicone polymer of the tension element can be cross-linked or otherwise cured after it has initially been overmolded or extruded onto a solid component of the damper.

[0092] With further reference to Fig. 14 are different types of polymers for the manufacture of various components of the in the Fig. 9A-9D or Fig.The damper assembly shown in Figures 10A-10F is illustrated. A first step, 1410, may involve, for example, preparing various polymer materials and premixing them in a cylinder before extruding them into a mold. A second step, 1420, may involve molding various components of the damper assembly. A third step, 1430, may involve assembling various components to form the damper assembly. A fourth step, 1440, may involve checking the desired torque of the damper assembly.

[0093] The technical features of the present invention can be summarized as follows: Torsion spring damper, featuring: a core which has an opening through it; a first fixed component having a first set of projections; a second fixed component having a second set of projections; and a tension element positioned between the first fixed component and the second fixed component, and the tensile element comprises a solid silicone polymer.

[0094] The tensioning element consists of a solid silicone polymer.

[0095] The tension element is separated from and not connected to the first fixed component, wherein the tension element is separated from and not connected to the second fixed component, and wherein the tension element is in direct and simultaneous contact with both the first fixed component and the second fixed component.

[0096] The tension element has a plurality of elongated bands.

[0097] The tension element has a plurality of cavities extending through it.

[0098] The first fixed component is designed such that at least one projection of the first set of projections extends through at least one cavity of the tensile element.

[0099] The second fixed component is designed such that at least one projection of the second set of projections extends through at least one cavity of the tensile element.

[0100] The first fixed component is designed such that at least one projection of the first set of projections extends through at least one cavity of the tension element, and wherein the second fixed component is designed such that at least one projection of the second set of projections extends through the same cavity of the tension element as at least one projection of the first set of projections.

[0101] The first fixed component is designed such that each projection of the first set of projections extends through a cavity of the tensile element, and wherein the second fixed component is designed such that each projection of the second set of projections extends through the same cavity of the pulling element as each projection of the first set of projections.

[0102] Each cavity of the pulling element has at least one projection of the first set of projections and at least one projection of the second set of projections extending through it.

[0103] The first solid component is a single, unitary element that features every projection of the first set of projections, and where the second fixed component is a single, unitary element that features each projection of the second set of projections.

[0104] The first solid component and the second solid component each consist of a hard polymer material selected from the group consisting of polyvinyl chloride (PVC), high-density polyethylene (HDPE), fluoropolymers, polyamides, polyethylene terephthalate (PET), polybutylene terephthalate (PBT) and polyoxymethylene (POM).

[0105] The torsion spring damper has a torque resistance of 2,000 Ncm to 10,000 Ncm.

[0106] The solid silicone polymer has a yield strength of approximately 2 MPa to approximately 15 MPa, measured according to ASTM D638.

[0107] The solid silicone polymer exhibits a percentage elongation at break of approximately 100% to approximately 2000%, measured according to ASTM D638.

[0108] The torsion spring damper also features a freewheel function.

[0109] A torsion spring damper assembly comprising: a cap that includes a cap opening; a base plate that includes a base plate opening; and a damper, wherein the damper is placed between the cap and the base plate, wherein the damper has: a first disk and a second disk, each at a first end and are arranged at a second end of a compression limiter; a tension element extending between the first disk and the second disk, wherein the tension element encloses the compression limiter around a longitudinal axis; and an opening, wherein the cap opening, the opening and the base plate opening are arranged concentrically around a longitudinal axis.

[0110] The base plate includes a plurality of locking openings and the second disc includes a plurality of locking elements that project outwards from the second disc, the plurality of locking elements being received by the plurality of locking openings.

[0111] A torsion spring damper assembly comprising: a first fixed component, wherein the first fixed component includes a plurality of fixed modular subcomponents, wherein the fixed modular components include a plurality of first projections and a central opening; a second solid component, wherein the second solid component comprises a body and a plurality of second projections extending outwards from an outer surface of the body; a tension element, wherein the tension element includes a plurality of cavities arranged between a plurality of bands; and at least one longitudinal cap arranged at one end of the tension element, wherein the plurality of second projections are received by the plurality of cavities of the tension element to form a first subassembly, and wherein the first subassembly is inserted through the central opening of the first fixed component.

[0112] The majority of cavities accommodate at least one of the majority of first projections.

[0113] It will be welcomed by those skilled in the field that, while the invention has been described above in connection with certain embodiments and examples, the invention is not necessarily limited to these, and that numerous other embodiments, examples, uses, modifications, and variations from the embodiments, examples, and uses are intended to be included in the appended claims. The entire disclosure of each patent and publication cited herein is incorporated by reference as if each of these patents or publications were individually incorporated herein by reference. Various features and advantages of the invention are set forth in the following claims.

[0114] Although various spatial and directional terms such as upper, lower, middle, lateral, horizontal, vertical, front, and the like may be used to describe embodiments of the present disclosure, it is understood that such terms are used only in relation to the orientations shown in the drawings. The orientations may be reversed, rotated, or otherwise changed so that an upper region becomes a lower region, and vice versa, horizontal becomes vertical, and so on.

[0115] Although the device disclosed herein may be implemented in many different forms, several specific embodiments are described herein with the understanding that the embodiments described in the present disclosure are only to be considered as examples of the principles described herein and that the disclosure is not intended to be limited to the illustrated embodiments. Throughout the disclosure, the terms "about" and "approximately" mean plus or minus 5% of the number preceding the respective term.

[0116] Variations and modifications of the foregoing are within the scope of this disclosure. It is understood that the embodiments disclosed and defined herein extend to all alternative combinations of two or more of the individual features mentioned or apparent from the text and / or the drawings. All such different combinations constitute different alternative embodiments of this disclosure.

Claims

[1] Torsion spring damper (200), comprising: - a core (210) which has an opening (212) leading through it; - a first solid component (220) having a first set of projections (222); - a second fixed component (230) having a second set of projections (232); and - a tension element (240) positioned between the first fixed component (220) and the second fixed component (230), and wherein the tensile element (240) comprises a solid silicone polymer, characterized by , that the tension element (240) has a plurality of elongated bands, wherein the tension element (240) has a plurality of cavities (244) extending through it. [2] Torsion spring damper (200) according to claim 1, wherein the tension element (240) consists of the solid silicone polymer. [3] Torsion spring damper (200) according to claim 2, wherein the tension element (240) is separate from the first fixed component (220) and is not connected to it, wherein the tension element (240) is separate from the second fixed component (230) and not connected to it, and wherein the tensile element (240) is in direct and simultaneous contact with both the first fixed component (220) and the second fixed component (230). [4] Torsion spring damper (200) according to one of claims 1 to 3, wherein the first fixed component (220) is configured such that at least one projection of the first set of projections (222) extends through at least one cavity (244) of the tension element (240), and / or wherein the second fixed component (230) is configured such that at least one projection of the second set of projections (232) extends through at least one cavity (244) of the tension element (240), and / or wherein the first fixed component (220) is configured such that at least one projection of the first set of projections (222) extends through at least one cavity (244) of the tension element (240), and wherein the second fixed component (230) is configured such that at least one projection of the second set of projections (232) extends through the same cavity (244) of the tension element (240) as at least one projection of the first set of projections (222), and / or wherein the first fixed component (220) is configured such that each projection of the first set of projections (222) extends through a cavity (244) of the tension element (240), and wherein the second fixed component (230) is configured such that each projection of the second set of projections (232) extends through the same cavity (244) of the pull element (240) as each projection of the first set of projections (222), and / or wherein each cavity (244) of the pull element (240) has at least one projection of the first set of projections (222) and at least one projection of the second set of projections (232) extending through it, and / or wherein the first component (220) is a single, unitary element having each projection of the first set of projections (222), and wherein the second fixed component (230) is a single, unitary element that has each projection of the second set of projections (232). [5] Torsion spring damper (200) according to any one of claims 1 to 4, wherein the first solid component (220) and the second solid component (230) each consist of a polymer material selected from the group consisting of polyvinyl chloride (PVC), high-density polyethylene (HDPE), fluoropolymers, polyamides, polyethylene terephthalate (PET), polybutylene terephthalate (PBT) and polyoxymethylene (POM), and / or wherein the torsion spring damper (200) has a torque resistance of 2000 Ncm to 10000 Ncm, and / or wherein the solid silicone polymer has a yield strength of about 2 MPa to about 15 MPa, as measured according to ASTM D638, and / or wherein the solid silicone polymer has a percentage elongation at break of about 100% to about 2000%, as measured according to ASTM D638. [6] Torsion spring damper (200), comprising: - a core (210) which has an opening (212) leading through it; - a first solid component (220) having a first set of projections (222); - a second fixed component (230) having a second set of projections (232); and - a tension element (240) positioned between the first fixed component (220) and the second fixed component (230), and wherein the tensile element (240) comprises a solid silicone polymer, characterized by , that the torsion spring damper (200) also has a freewheel feature.

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