Tire testing machine with vibration damper

Abstract

In one embodiment, the vibration dampers 26, 26a, 26b comprise first diaphragm bends 48a, 48b, 48c and second diaphragm bends 48a, 48b, 48c defining a cavity 76 between them, damping materials 50, 50a, 50b disposed within the cavity 76, and mass bodies 46, 46b, 46c connecting the first diaphragm bends 48a, 48b, 48c and the second diaphragm bends 48a, 48b, 48c. In another embodiment, the assembly comprises a load cell body 32 having two opposing sides, first vibration dampers 26a, 26b operably connected to the load cell body 32 on the first side, and a second vibration damper 26b operably connected to the load cell body 32. In yet another embodiment, a machine 20 and method are used to test a tire wheel assembly 24, the machine 20 comprising a road surface simulator 14, a spindle hub 34, a spindle housing 28, a frame 52, a spindle support 56, and damper assemblies 26, 26a, 26b, 60. The damper assemblies 26, 26a, 26b, 26c, 60 are bonded to the spindle housing 28 or the spindle support 56 and are configured to dampen forces or motions of the spindle hub 34 or the spindle support 56.

Description

Technical Field

[0001] The following discussion is provided merely as general background information and is not intended to be used as an aid in determining the scope of the claimed subject matter. Aspects of the present disclosure relate to a tire wheel tester having a vibration damping assembly.

Background Art

[0002] For testing a tire wheel assembly on a machine having a simulated road, the force between the contact patch of the tire and the road surface can be measured by a load cell mounted on the machine near the spindle hub to which the tire and wheel are attached. The load cell transmits and measures linear forces along up to three orthogonal axes and moments about the orthogonal axes.

[0003] Two such load cells are disclosed in U.S. Patent No. 4,640,138, titled “Multiple axis load sensitive transducer,” and U.S. Patent No. 4,821,582, titled “Load transducer,” by the same applicant, which are incorporated herein by reference. U.S. Patent No. 4,640,138 describes a multi-axis load-sensitive transducer having an inner member and an outer member joined by a pair of axially spaced spiders. The spiders have arms integral with the inner member and connected to the outer member by a flexible strap having a longitudinal link, the ends of which are fixed to the outer member. The arms of the spiders are fixed to the center of the associated strap. The load is detected as a function of the bending of the spider arms. U.S. Patent No. 4,821,582 describes a load transducer that measures linear forces in three axes and moments around two of these axes. The transducer has an inner and outer structure connected by a load-sensing spider arm or shear beam. The outer end of the spider is connected to an outer link that is rigid when the inner structure is loaded in a direction along an axis perpendicular to the plane of the spider. Each of the load cells described above may be adversely affected by vibrations and other forces transmitted to the load cell by a tire wheel assembly on a simulated road. Excessive vibration may affect the accuracy and / or lifespan of the load cell. [Prior art document] [Patent] [Patent Document 1] U.S. Patent No. 4,640,138 [Patent Document 2] U.S. Patent No. 4,821,582 [Patent Document 3] U.S. Patent No. 6,584,835 [Patent Document 4] U.S. Patent No. 6,845,675 [Overview of the project]

[0004] In one embodiment, the vibration damper comprises a first diaphragm bend and a second diaphragm bend defining a cavity between them, a damping material disposed within the cavity, and a mass body connecting the first diaphragm bend and the second diaphragm bend.

[0005] In another embodiment, the assembly comprises a load cell body having two opposing sides, a first vibration damper operably connected to the load cell body on the first side, and a second vibration damper operably connected to the load cell body.

[0006] In yet another embodiment, the machine is configured to test a tire wheel assembly and comprises a road simulator, a spindle hub, a spindle housing, a frame, a spindle support, and a damper assembly. In one exemplary embodiment, the spindle hub is configured to support the tire wheel assembly on the road simulator. In one exemplary embodiment, the spindle housing supports the spindle hub for rotation around an axis. In one exemplary embodiment, the spindle support is bonded to the frame and the spindle housing. In one exemplary embodiment, the damper assembly is bonded to the spindle housing or spindle support and is configured to dampen forces or motions of the spindle hub or spindle support.

[0007] An exemplary method for testing a tire-wheel assembly is described. The exemplary method involves mounting the tire-wheel assembly on a spindle hub configured to support the tire-wheel assembly on a road simulator, wherein the spindle housing supports the spindle hub for rotation around an axis, and the spindle support is joined to the spindle housing. The exemplary method involves operating the spindle hub to rotate the tire-wheel assembly relative to the road simulator. The exemplary method involves attaching a damper to the spindle housing or spindle support to dampen the forces or motion of the tire-wheel assembly on the road simulator.

[0008] This summary is provided to provide a simplified introduction to concepts that will be further explained in the detailed description below. This summary is not intended to identify any major or essential features of the subject matter disclosed or claimed, nor is it intended to describe each or all embodiments of the disclosed or claimed subject matter. Specifically, features disclosed herein with respect to one embodiment are similarly applicable to another embodiment. Furthermore, this summary is not intended to be used as an aid in determining the scope of the claimed subject matter. Many other novel advantages, features, and relationships will become apparent as this description progresses. The following drawings and descriptions illustrate illustrative embodiments in more detail.

[0009] The subject matter disclosed is further described with reference to the accompanying drawings, and similar structural or system elements are referred to by the same reference numerals throughout some of the drawings. Unless otherwise specified, all descriptions are applicable to similar and analogous structures throughout some of the embodiments. [Brief explanation of the drawing]

[0010] [Figure 1] This is a front perspective view of a tire testing machine having one exemplary embodiment of a synchronized mass damper assembly.

[0011] [Figure 2] It is a rear perspective view of the tire testing machine of FIG. 1.

[0012] [Figure 3] It is a front view of a tire testing machine without a tire, showing a first exemplary embodiment of a passive damper.

[0013] [Figure 4] It is a front perspective view of a tire testing machine with a tire wheel assembly attached, showing a first exemplary embodiment of a passive damper.

[0014] [Figure 5] It is a partial rear side perspective view of the hub end of a spindle drive assembly, showing a first exemplary embodiment of a passive damper attached to a spindle housing that holds a load cell body.

[0015] [Figure 6A] It is a front view of a vertical cross-section of a first exemplary embodiment of a passive damper.

[0016] [Figure 6B] It is a side view of a vertical cross-section of a first embodiment of a passive damper.

[0017] [Figure 6C] It is a front view of a vertical cross-section of a second embodiment of a passive damper.

[0018] [Figure 7A] It is a front view of a tire testing machine having a third exemplary embodiment of a passive damper.

[0019] [Figure 7B] It is a side view of a tire testing machine having a third exemplary embodiment of a passive damper (the front of the machine is on the left side and the rear of the machine is on the right side).

[0020] [Figure 8] A partial cross-sectional view of the structure of the constraint layer laminated structure part of a third exemplary embodiment of a passive damper.

[0021] [Figure 9] A rear perspective view of a tire testing machine similar to FIG. 2, having an additional exemplary embodiment of an active damper.

[0022] [Figure 10] A side view of a tire testing machine having an exemplary embodiment of an active damper (the rear of the machine is on the left side and the front of the machine is on the right side).

[0023] [Figure 11A] A schematic view of a passive damper attached to a testing machine.

[0024] [Figure 11B] A schematic view of a passive damper attached to a load cell.

[0025] [Figure 11C] A schematic view of an active damper attached to a testing machine.

Mode for Carrying Out the Invention

[0026] Although one or more embodiments of a load transducer are shown in the above-described drawings, other embodiments are also contemplated. This disclosure is presented by representing the disclosed subject matter in a representative manner and is not limiting. It should be understood that numerous other variations and embodiments can be devised by those skilled in the art that fall within the scope of the principles of this disclosure.

[0027] The diagrams may not be drawn to scale. In particular, some features may be enlarged relative to others for clarity. Furthermore, please understand that when terms such as top, bottom, up, down, apex, bottom, side, right, left, vertical, and horizontal are used, they are used solely to facilitate understanding of the explanation. It is intended that the structure may be in other orientations.

[0028] The terminology used in this application is for the purpose of describing embodiments and is not intended to be limiting. Unless otherwise indicated, ordinal numbers (e.g., 1st, 2nd, 3rd, etc.) are used to distinguish or identify different elements or processes within a group of elements or processes and do not impose a serial or numerical limitation on the elements or processes of the embodiment. For example, the “1st,” “2nd,” and “3rd” elements or processes do not necessarily have to appear in this order, and the embodiment does not necessarily have to be limited to three elements or processes. Unless otherwise indicated, notations such as “left,” “right,” “front,” “back,” “top,” “bottom,” “forward,” “backward,” “clockwise,” “counterclockwise,” “up,” “down,” or other similar terms such as “upward,” “downward,” “back,” “before,” “vertical,” “horizontal,” “proximal,” “distal,” and “intermediate” are used for convenience and do not, for example, mean any specific fixed position, orientation, or direction. Instead, such notations are used to reflect, for example, relative position, orientation, or direction. The singular forms "a," "an," and "the" also include the plural form, unless otherwise clearly determined by the context.

[0029] This disclosure describes exemplary embodiments of synchronized mass damper assemblies particularly suitable for use with load cells in the context of tire testing machines. One particularly suitable machine is the FlatTrac® tire force and moment measuring system, commercially available from MTS Systems, Inc., Eden Prairie, Minnesota. Another suitable system is described in U.S. Patent No. 6,584,835, titled “Spindle Assembly for a Tire or Wheel Testing Machine,” by the same applicant, which is incorporated herein by reference. The synchronized mass damper assemblies described may also be used with other systems and with load cells in other applications. In one exemplary embodiment, the synchronized mass damper assembly comprises one or more passive and active dampers.

[0030] Figures 1 and 2 are a front and rear perspective view, respectively, of a tire wheel testing machine 20 suitable for use with the described synchronized mass damper assembly. The illustrated tire wheel testing machine 20 comprises a spindle drive assembly 12 and a road simulator 14 having an endless belt 16 forming a circumferential surface. The endless belt 16 is supported on a pair of rollers 18 and rotates around the pair of rollers 18. The belt drive assembly 22 moves the endless belt 16 on which the tire wheel assembly 24 is being tested. As will be understood by those skilled in the art, other forms of circumferential surfaces, such as a rotatable drum, may be used instead of the illustrated road simulator 14.

[0031] In one exemplary embodiment, the spindle drive assembly 12 comprises a driven spindle shaft coupled to a spindle hub 34. The spindle hub 34 is adapted to support a tire wheel assembly 24 for rotation around a spindle axis 36. A drive motor 44 rotates the tire wheel assembly 24 around the spindle axis 36.

[0032] In the illustrated embodiment, the frame 37 of the machine 20 includes a frame member 52 pivotably mounted to a base 54 at a swivel connection 64, allowing adjustment of the camber of the tire wheel assembly 24 relative to the road simulator 14. In one exemplary embodiment, a camber actuator 58 is coupled to the frame member 52 and displaces the frame member 52 and the spindle drive assembly 12 around a camber axis 62 extending through the swivel connection 64.

[0033] In one exemplary embodiment, the frame 37 of the machine 20 includes a support member 38 that rotates the spindle hub 34 and spindle drive assembly 12 around a steering axis 42, typically oriented perpendicular to the spindle axis 36. In one exemplary embodiment, a linear steering actuator 55 is coupled to a frame member 52 and a strongback or spindle support 56 that is pivotably mounted to the frame member 52 to move around the steering axis 42. The spindle support 56 is attached to and supports the spindle drive assembly 12 and spindle hub 34 in order to rotate the tire wheel assembly 24 around the steering axis 42. In other embodiments, a rotary actuator can be used to rotate the support member 38 around the steering axis 42. In one exemplary embodiment, a vertically positioned linear actuator 59 is coupled to the support member 38 and raises and lowers the tire wheel assembly 24 relative to an endless belt 16 (and also transmits a load simulating the vehicle weight).

[0034] The structure of the frame member 52, the pivot connection portion 64 of the frame member 52 to the base 54, and the means for supporting the spindle drive assembly 12 and pivoting the spindle drive assembly 12 around the steering axis 42 and the camber axis 62, as relating to exemplary embodiments, should not be considered limiting. In one exemplary embodiment, actuators 55, 58 and 59 displace the spindle hub 34 and the spindle support 56 directly or indirectly through other support structures, displacing the tire and applying a load to it as the tire rotates on the circumferential surface (e.g., the endless belt 16). The spindle 34 and the circumferential surface may be equipped with independent drive devices. The actuators and support structures can take many forms to support the spindle 34 on the circumferential surface and may include mechanical assemblies utilizing gears and / or electric, hydraulic and / or pneumatic actuators. One or more damping assemblies are provided to dampen the forces on the spindle 34 resulting from the forces generated between the tire and the circumferential surface. The damping assembly is preferably configured to provide damping along the rotation axis of the spindle 34 and / or perpendicular to the rotation axis of the spindle 34 (generally in the longitudinal direction 40 parallel to the surface 16 of the road simulator 14 that contacts the tire under test).

[0035] Figure 3 is a front view of the test machine 20 with the tire wheel assembly 24 removed so that the spindle hub 34 is visible. Two left and right passive dampers 26 dampen vibrations in the longitudinal direction 40. These dampers 26 are preferably positioned in close proximity to the spindle hub 34, for example, mounted on the spindle housing 28 or spindle support 56 to absorb vibrations and other forces transmitted from the tire wheel assembly 24 to the components of the test machine 20. In exemplary ways for the use of the passive dampers 26, two such passive dampers 26 are mounted on the left and right sides of the spindle housing 28 that holds the load cell 32, examples of which are described in the background art but should not be considered limiting. Exemplary load cells are disclosed in U.S. Patent No. 6,845,675, titled “Multi-Axis Load Cell,” by the same applicant, as well as in U.S. Patents No. 4,640,138, 4,821,582, and 6,845,675, which are incorporated herein by reference in whole.

[0036] As shown in Figures 4 and 9, in one exemplary embodiment, two (front and rear) passive dampers 26 are positioned on the spindle support 56 to dampen forces along the rotation axis of the spindle 34 in the direction 41 between the tire contact patch and the road simulator 14. In other embodiments, any of the dampers described in this disclosure of a synchronous mass damper assembly may be positioned elsewhere in the machine 20, for example, on the spindle drive assembly 12, or on components attached to the drive assembly 12, such as the spindle support 56. By absorbing or otherwise damping vibrational forces and other forces, the disclosed synchronous mass dampers protect components of the machine 20 from excessive loads that could contribute to wear of the machine 20.

[0037] In some cases, several embodiments of an element are shown. Elements in general may be indicated by a reference number, and specific embodiments of an element may be indicated by a lowercase code along with its reference number. In all cases, any discussion relating to an element refers to all other similarly numbered elements unless otherwise specified.

[0038] As shown in Figure 11A, a schematicly drawn passive damper 26 is mounted on a tire wheel testing machine 20. As shown in Figure 11B, a schematicly drawn passive damper 26 is mounted on a load cell 32, which can be used in embodiments other than the tire wheel testing machine. Such a passive damper 26 comprises a mass body 46 attached to a spring 48 (having a spring constant k) and a damper element 50 such as a damping material. A passive damper 26 having these components in any configuration can be used in a tuned mass damper assembly described together with the testing machine 20. This disclosure also includes specific structures such as, for example, a drum-shaped passive damper 26a, a drum-shaped constrained passive damper 26b, and a constrained layer laminated passive damper 26c. These specific embodiments are not limiting and are merely specific structures suitable as passive dampers.

[0039] The composition of the damping material 50 affects its behavior and performance. For example, referring to Figures 6A to 6C, when the particulate damping material 50a is formed as granular pellets (e.g., lead shot), vibrations are damped by friction as the particles rub against each other, thereby generating heat as a form of energy dissipation. In contrast, referring to Figure 6C, the solid elastomer damping material 50b relies on its inherent elastic properties for damping effect. Layered or laminated structures can exhibit Coulomb damping, in which kinetic energy is absorbed by sliding friction generated by the relative motion of two surfaces pushing against each other. The spring 48 can take many different forms, and the constraining layer structure 66 can perform both spring and damping functions.

[0040] As shown in Figures 1 to 6C, in exemplary embodiments, the passive dampers 26a, 26b are configured in a drum shape, and each substantially cylindrical unit is attached to the spindle housing 28 of the spindle 34 by fasteners such as bolts 30. In one exemplary embodiment, as shown in Figures 6A and 6B, the drum passive dampers 26A, 26B are formed together with a central shaft spacer mass 46a having a bore 68 through which the fasteners 30 pass. A concentric cylindrical mass 46b surrounds the shaft mass 46a. These elements are connected on opposing sides (sides) by a pair of circular diaphragm bends 48a. In one exemplary embodiment, the cavity 76 between the two masses 46a, 46b and the circular diaphragm bends 48a is at least partially filled with particulate damping material 50a such as lead shot.

[0041] Figure 6C shows a modified example of a drum-shaped passive damper 26b, in which each of the circular diaphragm bends 48a is adjacent to a constrained layer damping laminated section 66 (described below in relation to Figure 8) and comprises a laminated diaphragm 48b exhibiting Coulomb damping capability. The Coulomb damping laminated diaphragm 48b has multiple layers, such as a metal layer 48c.

[0042] Figures 7A and 7B are a front and side view, respectively, of a tire wheel testing machine 20 which has a third exemplary embodiment of a passive damper, namely configured as a constrained layer passive damper 26c, on top of it. In the illustrated embodiment, a bar mass 46c is attached to the left and right sides of the spindle housing 28 by two laminated constrained layer structures 66. In one exemplary embodiment, each of the constrained layer damping laminates 66 is composed of several material layers, a cross-sectional view of which is shown in Figure 8. In one exemplary embodiment, the laminate 66 includes a solid elastomer 50b (or other viscoelastic material) sandwiched between two flat metal springs 48c.

[0043] Figure 9 is a side and rear perspective view of a tire testing machine 20 with several drum passive dampers 26 and active dampers 60a, 60b mounted on top. Figure 10 shows a side view of the machine 20 with active damper 60a mounted on a spindle support 56 and active damper 60b mounted on a spindle drive assembly 12. As shown in Figures 9 and 10, in one exemplary embodiment, the active damper 60a is mounted on the spindle support 56 of the machine 20 and is oriented so that the operation of the mass body 46d is achieved in a generally horizontal direction perpendicular to the rotation axis of the spindle 34 and calibrated to reduce vibrations in a generally longitudinal direction 40. Another active damper 60b is mounted on the spindle drive assembly 12 and is oriented so that the operation is achieved along the rotation axis of the spindle 34 and calibrated to reduce vibrations along the rotation axis of the spindle 34 (generally, lateral motion 41 across the endless belt 16).

[0044] Figure 11C shows a schematic diagram of an active damper 60 configured to be attached to a portion of a test machine 20. In one exemplary embodiment, the active damper 60 comprises an actuator 70 attached to a mass 46d. The active damper 60 includes a sensor 72 for detecting the motion of the mass 46d, and a sensor 73 for detecting the motion of a portion of the test machine 20. Signals from sensors 72 and 73 are used by a controller 75. As schematically shown, the controller 75 controls the operation of the actuator 70 in phase with the detected vibration of the portion of the test machine 20, thereby moving the mass 46d and controlling the resonant frequency of the portion of the machine 20 to which the active damper 60 is attached. Sensors 72 and 73 can be any type of motion sensor capable of detecting the motion of the mass 46d and the portion of the test machine 20, respectively. Typically, each motion sensor 72, 73 is one of a displacement sensor, a velocity sensor, or an accelerometer. It should be understood that motion sensors 72 and 73 are shown schematically and do not necessarily represent their connection to the test machine 20 or any part of the actuator 70. For example, if embodied as accelerometers, motion sensors 72 and 73 are coupled to the moving part of the test machine 20, actuator 70, or mass body 46d to detect acceleration. If sensors 72 or 73 are embodied as displacement sensors or velocity sensors, they are configured to measure the displacement or velocity of a part of the test machine 20, mass body 46d, or moving part of the actuator 70. Output signals from motion sensors 72 and 73 are provided to a controller 75, which may include a processing circuit that provides displacement, velocity, and / or acceleration values ​​to control the operation of the actuator 70 and move the mass body 46d to dampen the force and / or displacement of a part of the test machine 20. The actuator 70 can be any active part configured to move the mass body 46d to counteract motion, such as an electric actuator or a hydraulic or pneumatic cylinder.

[0045] By arranging two passive dampers 26 on the left and right sides of the spindle housing 28 as shown in the figure, forces in the longitudinal direction, mainly indicated by arrow 40, perpendicular to the rotation axis of the spindle 34, are damped. By arranging two passive dampers 26 on the front and rear of the spindle support 56 as shown in the figure, forces in the lateral direction, mainly indicated by arrow 41, along the rotation axis of the spindle 34, are damped. By arranging an active damper 60a on the spindle support 56 as shown in the figure and directing the mass body 46c to move in the longitudinal direction, as indicated by arrow 40, vibrations perpendicular to the rotation axis of the spindle 34 are also damped. By arranging an active damper 60b on the spindle assembly 12 as shown in the figure and directing the mass body 46c to move in the lateral direction, as indicated by arrow 41, along the rotation axis of the spindle 34, vibrations in that direction are also damped. It should be understood that dampers 26, 60 can be positioned in other locations and orientations, particularly on the spindle drive assembly 12 and / or spindle support 56, to dampen forces in other directions (e.g., along the steer axis) to the test machine 20, load cell 32, or another object to which the synchronized mass damper assembly is attached.

[0046] The vibration frequency of the passive damper 26 is tuned to be similar to the resonant frequency experienced by the part of the machine 20 to which the passive damper 26 is attached during tire testing, in order to effectively cancel out such frequencies. Such tuning can be achieved by various factors such as the quantity, composition and arrangement of the mass body 46, the spring constant and composition of the spring 48, and the volume, arrangement, composition and structural configuration of the damping material 50. Furthermore, when two dampers 26, 60 are used in pairs, they do not need to be identical. For example, two passive dampers 26 on the left and right sides (or two passive dampers 26 at the front and rear) can be tuned to different frequencies to have different effects, for example, depending on whether the tire wheel assembly is accelerating or decelerating.

[0047] By reducing the mechanical vibrations experienced by the machine 20 through the use of the disclosed synchronized mass damper assembly, damage to the components of the machine 20 and structural failure can be prevented. Controlling such vibrations is particularly important for protecting highly sensitive components such as the load cell 32 and its transducer, which measure the forces experienced by the tire wheel assembly 24 during testing. With advances in vehicle technology, tires are expected to withstand higher radial forces and torques than before. For example, electric vehicles in particular have heavy battery components and higher weight loads. Cars are more powerful than ever, drivers demand higher levels of responsiveness and control, and tires generally have higher grip performance. The synchronized mass damper assembly of this disclosure may comprise only a single damper 26, 60, or any number, combinations, and arrangements of the disclosed dampers 26, 60, to reduce the effects of vibrations experienced by the test machine 20 or the load cell 32.

[0048] Non-limiting exemplary embodiments of vibration dampers, assemblies, and machines are described. As shown in Figures 5 to 6C, an exemplary embodiment of a vibration damper 26 comprises a first diaphragm bend 48 and a second diaphragm bend 48 defining a cavity 76 between them, a damping material 50 disposed within the cavity 76, and a mass body 46 connecting the first diaphragm bend 48 and the second diaphragm bend 48. In one exemplary embodiment, the damping material 50a is particulate or in particulate form. In one exemplary embodiment, at least one of the first diaphragm bend 48 and the second diaphragm bend 48 comprises a stack 48b, 66 including a plurality of layers. In one exemplary embodiment, the plurality of layers include a first metal layer 48c, a viscoelastic intermediate layer 50b, and a second metal layer 48c disposed on the opposite side of the intermediate layer 50b from the first metal layer 48c.

[0049] In one exemplary embodiment, the mass body 46b is configured as a cylinder, and the first diaphragm bend 48 and the second diaphragm bend 48 each constitute a disk attached to the opposing ends of the cylinder, and the cavity 76 is defined within the cylinder. In one exemplary embodiment, the central shaft 46a is located inside the cylinder mass body 46b.

[0050] In one exemplary embodiment, the assembly shown in Figure 5 comprises a load cell body 32 having two opposing sides, and first vibration dampers 26, 60 operably connected to the load cell body 32 on the first side. In one exemplary embodiment, the vibration damper 26 comprises a spring 48, a damping material 50, and a first mass body 46. In one exemplary embodiment, the assembly also comprises second vibration dampers 26, 60 operably connected to the load cell body 32.

[0051] In one exemplary embodiment of the assembly, the damping material 50 is in the form of particles. In one exemplary embodiment of the assembly, the spring 48 includes diaphragm bends 48a and 48b. In one exemplary embodiment of the assembly, the second vibration damper 60 includes an actuator 70, a speed sensor 72, and a second mass body 46d.

[0052] An exemplary machine 20 configured to test a tire wheel assembly 24 comprises a road simulator 14, a spindle drive assembly 12, and a spindle support 56 or first dampers 26, 60 positioned on the spindle drive assembly 12. In one exemplary embodiment, the spindle drive assembly 12 comprises a spindle hub 34 configured on which the tire wheel assembly 24 is mounted so as to contact the road simulator 14. In one exemplary embodiment, the first damper 26 comprises a first damping material 50, a first spring 48, and a first mass body 46.

[0053] In the exemplary machine 20, the motion of the tire wheel assembly 24 relative to the road surface simulator 14 is configured to occur primarily in opposing longitudinal linear directions 40. The exemplary machine includes second dampers 26, 60, the first dampers 26, 60 being located on the front side of the hub 34 and the second dampers 26, 60 being located on the rear side of the hub 34. In the exemplary machine, the spring 48 of the damper 26 includes a pair of diaphragm bends 48a, 48b that are spaced apart in the longitudinal linear direction 40.

[0054] The exemplary machine 20 comprises a frame member 52 movably mounted to the road surface simulator 14. The exemplary machine 20 comprises a spindle support 56 connected to the spindle drive assembly 12 and pivotally connected to the frame 52. The exemplary machine 20 comprises second dampers 26, 60 positioned on the spindle support 56. In the exemplary machine 20, the second damper 26 comprises a second damping material 50, a second spring 48, and a second The second damper 60 comprises an actuator 70, motion sensors 72 and / or 73, a controller 75, and a second mass body 46d. In an exemplary machine 20, the spindle support 56 has opposing front and rear surfaces, and the machine 20 comprises a third damper 26, 60 located on the spindle support opposite the second dampers 26, 60.

[0055] As shown in Figures 9 and 10, the exemplary machine 20 includes second dampers 26, 60 positioned adjacent to the end of the spindle drive assembly 12 and opposite the hub 34. In the illustrated embodiment, the second damper 60 positioned on the spindle drive assembly 12 includes an actuator 70, motion sensors 72 and / or 73, a controller 75, and a second mass body 46d.

[0056] While the subject matter has been described using terminology specific to structural features and / or methodological actions, it should be understood that the subject matter as defined in the attached claims is not necessarily limited to the specific features or actions described above, as has been determined by the courts. Rather, the specific features and actions described above are disclosed as exemplary forms for carrying out the claims. Furthermore, features disclosed in relation to one embodiment may be included in another embodiment, and vice versa. All references cited in this disclosure constitute part of this specification by reference.

Claims

1. It is a vibration damper, A first diaphragm bend and a second diaphragm bend, wherein a cavity is defined between the first diaphragm bend and the second diaphragm bend, A damping material placed within the cavity, A mass body connecting the first diaphragm bending portion and the second diaphragm bending portion, A vibration damper equipped with this feature.

2. The vibration damper according to claim 1, wherein the damping material is in the form of particles.

3. The vibration damper according to claim 1, wherein at least one of the first diaphragm bend portion and the second diaphragm bend portion comprises a stack including a plurality of layers.

4. The aforementioned multiple layers are, The first layer and, A viscoelastic intermediate layer, A second layer is disposed on one side of the viscoelastic intermediate layer opposite to the first layer, The vibration damper according to claim 3, including the following:

5. The aforementioned mass is configured as a cylinder, The first diaphragm bend and the second diaphragm bend are each configured as discs attached to the opposing ends of the cylinder, The cavity is defined within the cylinder, The vibration damper according to claim 1.

6. The vibration damper according to claim 5, further comprising a central shaft disposed within the cylinder.

7. It is an assembly, The load cell body and A first vibration damper operably connected to the load cell body on the first side of the load cell body, spring and, Damping material and, The first mass body and A first vibration damper equipped with, A second vibration damper is operably connected to the load cell body, An assembly comprising:

8. The assembly according to claim 7, wherein the damping material is in the form of particles.

9. The assembly according to claim 7, wherein the spring comprises a diaphragm bend.

10. The second vibration damper is, Actuator and Speed ​​sensor and The second mass body and, The assembly according to claim 7, comprising:

11. A machine configured to test tire wheel assemblies, Road surface simulator and, A spindle hub configured to support the tire wheel assembly on the road surface simulator, A spindle housing that supports the spindle hub for rotation around an axis, Frame and, The frame and the spindle housing are joined to a spindle support, A damper assembly bonded to the spindle housing or the spindle support, configured to dampen the force or motion of the spindle hub or the spindle support, A machine equipped with [the necessary components].

12. The damper assembly comprises a first passive damper, and the first passive damper is The first damping material and The first spring and, The first mass body and The machine according to claim 11, comprising:

13. The damper assembly comprises a first active damper, and the first active damper is A first motion sensor configured to detect the movement of the spindle housing or the spindle support, A mass body and, An actuator configured to move the aforementioned mass, A second motion sensor configured to detect the motion of the aforementioned mass, A controller that receives output signals from the first motion sensor and the second motion sensor, and is configured to provide control signals for operating the actuator, The machine according to claim 11, comprising:

14. The machine according to claim 11, wherein the damper assembly is configured to dampen the force of rotation of the spindle hub along the axis.

15. The machine according to claim 11, wherein the damper assembly is configured to dampen the force of rotation of the spindle hub in a direction perpendicular to the axis.

16. The machine according to claim 15, wherein the direction of rotation of the spindle hub perpendicular to the axis is parallel to the surface of the road simulator supporting the tire.

17. The motion of the tire wheel assembly relative to the road surface simulator is configured to occur primarily in the longitudinal linear direction opposite to each other, and the damper assembly is, A first damper positioned in front of the spindle hub, A second damper positioned on the rear side of the spindle hub, The machine according to claim 11, comprising:

18. The machine according to claim 17, wherein at least one of the first damper and the second damper is provided with a pair of diaphragm bends spaced apart from each other in the linear direction between the front and rear.

19. A method for testing a tire wheel assembly, Mounting the tire wheel assembly onto a spindle hub configured to support the tire wheel assembly on a road simulator, wherein the spindle housing supports the spindle hub for rotation around an axis, and the spindle support is joined to the spindle housing, The spindle hub is operated to rotate the tire wheel assembly relative to the road surface simulator, A damper is attached to the spindle housing or the spindle support to dampen the force or motion of the tire wheel assembly on the road surface simulator, Methods that include...

20. The method according to claim 19, wherein the damper includes a passive damper, and the method includes acting a separate active damper.

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