A vibration isolator includes a first conical disc spring member having a first end and a second end. A first-end spacer in contact with the first spring member first end, and a second-end spacer in contact with the first spring member second end. A second conical disc spring member has a first end and a second end. The second spring member first end is in contact with the first-end spacer. Another second-end spacer is in contact with the second spring member second end. A flexible housing of the isolator defines an interior. The housing is in contact with and extends between the second-end spacer and the other second-end spacer so that the first-end spacer and the first and second spring members are received in the housing interior. The housing includes a plurality of spaced-apart through holes formed therealong between the second-end spacer and the other second-end spacer.

Systems and methods for limiting transmission of vibrations and forces causing vibrations from one element to another are provided. A vibration isolator may include a compressible inner member and an outer member compressible with the inner member. The outer member may be positioned at least partially around the inner member to provide lateral support to the inner member. The outer member may maintain a consistent diameter and compression force when in a compressed state. The outer member may include a tube with a zero or near-zero Poisson's ratio.

In one embodiment, a vibration control apparatus is provided having a pair of face sheets with a core material in between. The core material comprising a positive stiffness material. A stack comprising a positive stiffness structure in series with a negative stiffness structure is located between the pair of face sheets, in parallel with the core material. The stack may be embedded in the core material. Various embodiments may include multiple stacks in parallel with each other. In some embodiments, the stack may include multiple positive stiffness structures in series with multiple negative stiffness structures. The multiple positive stiffness structures and negative stiffness structures may be interleaved.

A rotating machine system include a rotating machine. The rotating machine system can include a housing. The housing can include an inner surface. The housing can surround at least a portion of the rotating machine. The inner surface of the housing can be spaced from the rotating machine such that a space is defined therebetween. The rotating machine system can include a plurality of vibration isolators. The vibration isolators can be positioned in the space and can be operatively connected to the rotating machine and to the inner surface of the housing. The vibration isolators can be compression-type vibration isolators.

A zero-stiffness impact isolation device includes a shell, a half-hourglass-shaped boss, a sliding block, a spring, a motion guide assembly, and an inner core. Where the motion guide assembly includes a linear bearing fixed to the shell and the inner core and a corresponding sliding rod, and is divided into a transverse guide assembly and a longitudinal guide assembly. The spring is sleeved outside the sliding rod of the transverse motion guide assembly, and two ends of the spring are in contact with the sliding block and the inner core, respectively. When the device suffers from external impact load, the inner core and the separated object carry out a reciprocating motion, the sliding block is extruded by the half-hourglass-shaped boss to move side to side with respect to the inner core, and the spring provides elastic force to the sliding block in the process.

A vehicle seat assembly includes a seat frame, a seat pan, and a plurality of vibration isolators interposed between the seat frame and the seat pan for limiting transmission of vibrations from the seat frame to the seat pan.

Systems and methods for limiting transmission of vibrations and forces causing vibrations from one element to another are provided. A vibration isolator may include a compressible inner member and an outer member compressible with the inner member. The outer member may be positioned at least partially around the inner member to provide lateral support to the inner member. The outer member may maintain a consistent diameter and compression force when in a compressed state. The outer member may include a tube with a zero or near-zero Poisson's ratio.

A vibration isolator includes a first conical disc spring member having a first end and a second end. A first-end spacer in contact with the first spring member first end, and a second-end spacer in contact with the first spring member second end. A second conical disc spring member has a first end and a second end. The second spring member first end is in contact with the first-end spacer. Another second-end spacer is in contact with the second spring member second end. A flexible housing of the isolator defines an interior. The housing is in contact with and extends between the second-end spacer and the other second-end spacer so that the first-end spacer and the first and second spring members are received in the housing interior. The housing includes a plurality of spaced-apart through holes formed therealong between the second-end spacer and the other second-end spacer.

The present invention discloses a quasi-zero-stiffness (QZS) based six-degree-of-freedom (6-DOF) absolute displacement and attitude measurement device. A lower end coil and an upper end coil are respectively charged with currents in the opposite directions; The electromagnetic field and the magnetic fields of an upper magnet and a lower magnet per se are mutually acted to produce an electromagnetic stiffness opposite to the stiffness of a spring. The stiffness of the whole leg is close to zero stiffness. When the to-be-measured platform generates space motion, the reference platform is in the stationary state. At this point, the deformation amounts of the six legs can be measured by laser displacement sensors. The six deformation amounts are respectively inputted into the displacement and attitude resolver, and by forward kinematic solution of the 6-DOF device, the displacement and the attitude of the to-be-measured platform can be obtained.

A zero-stiffness impact isolation device includes a shell, a half-hourglass-shaped boss, a sliding block, a spring, a motion guide assembly, and an inner core. Where the motion guide assembly includes a linear bearing fixed to the shell and the inner core and a corresponding sliding rod, and is divided into a transverse guide assembly and a longitudinal guide assembly. The spring is sleeved outside the sliding rod of the transverse motion guide assembly, and two ends of the spring are in contact with the sliding block and the inner core, respectively. When the device suffers from external impact load, the inner core and the separated object carry out a reciprocating motion, the sliding block is extruded by the half-hourglass-shaped boss to move side to side with respect to the inner core, and the spring provides elastic force to the sliding block in the process.