Self-tuned mass damper and system comprising the same

Patent metadata

Field	Value
Publication number	US-10655699-B2
Application number	US-201414895504-A
Country	US
Kind code	B2
Filing date	Jun 2, 2014
Priority date	Jun 3, 2013
Publication date	May 19, 2020
Grant date	May 19, 2020

Abstract

A simple self-tuned mass damper is hereby proposed for a broadened frequency band and which can be adapted to large and expensive structures as well as small and inexpensive structures alike. The novel self-tuned mass damper includes an auxiliary mass and a non-linear suspension, which is configured to connect the auxiliary mass to a vibrating structure. The mass of the auxiliary mass and the stiffness of the non-linear suspension are selected such that the natural frequency is at least 6 Hz and that the amplitude of the relative displacement of the auxiliary mass in respect to the vibrating structure is at most 12 mm.

First claim

The invention claimed is:

1. A self-tuned mass damper comprising:
an auxiliary mass and
a wire rope isolator acting as a non-linear suspension, which is configured to connect the auxiliary mass to a vibrating structure,

wherein:
the mass of the auxiliary mass and the stiffness of the non-linear suspension are configured to yield an appropriate natural frequency for the resulting structure,
the mass of the auxiliary mass and the stiffness of the non-linear suspension are selected such that said natural frequency is at least 10 Hz and that the amplitude of the relative displacement of the auxiliary mass in respect to the vibrating structure is at most 4 mm, and the stiffness to mass ratio is at least 4 kN/(m·kg) using static stiffness.

2. The self-tuned mass damper according to claim 1 , wherein said natural frequency is at least 14 Hz.

3. The self-tuned tuned-mass damper according to claim 2 , wherein the stiffness to mass ratio is at least 7 kN/(m·kg) using static stiffness.

4. The self-tuned mass damper according to claim 1 , wherein the amplitude of the relative displacement of the auxiliary mass in respect to the vibrating structure is at most 2 mm.

5. The self-tuned mass damper according to claim 1 , wherein the amplitude of the relative displacement of the auxiliary mass in respect to the vibrating structure is at most 1 mm.

6. The self-tuned mass damper according to claim 1 , wherein the auxiliary mass is in the range of 40 to 80 kg.

7. The self-tuned mass damper according to claim 1 , wherein the stiffness of the wire rope isolator has been selected to be in the slope of the amplitude-stiffness curve of the wire rope isolator that is closer to a second or higher order function than a linear equation.

8. The self-tuned mass damper according to claim 1 , wherein the stiffness of the wire rope isolator, in conjunction with the other properties of the self-tuned mass damper, has been selected to be in the slope of the amplitude-stiffness curve of the wire rope isolator that is closer to a second or higher order function than a linear equation.

9. The self-tuned mass damper according to claim 1 , wherein the wire rope isolator has been selected such that, at the maximum relative displacement of the auxiliary mass, the derivative of the amplitude-stiffness curve of the wire rope isolator is greater than 1.

10. The self-tuned mass damper according to claim 1 , wherein the wire rope isolator has been selected such that, in conjunction with the other properties of the self-tuned mass damper, at the maximum relative displacement of the auxiliary mass, the derivative of the amplitude-stiffness curve of the wire rope isolator is greater than 1.

11. A vibrating system comprising:
a vibrating structure and
a self-tuned mass damper, which includes:
an auxiliary mass and
a non-linear suspension, formed by a wire rope isolator, which is configured to connect the auxiliary mass to the vibrating structure,

wherein:
the mass of the auxiliary mass and the stiffness of the non-linear suspension are configured to yield an appropriate natural frequency for the resulting structure, and wherein
said mass of the auxiliary mass and the stiffness of the non-linear suspension are selected such that:
said natural frequency is at least 10 Hz and that
the amplitude of the relative displacement of the auxiliary mass in respect to the vibrating structure is at most 4 mm
wherein the mass damper is self-tuned and wherein the stiffness to mass ratio is at least 4 kN/(m·kg) using static stiffness.

12. The vibrating system according to claim 11 , wherein the auxiliary mass is in the range of 40 to 80 kg.

13. The vibrating system according to claim 11 , wherein the stiffness of the wire rope isolator has been selected to be in the slope of the amplitude-stiffness curve of the wire rope isolator that is closer to a second or higher order function than a linear equation.

14. A self-tuned mass damper comprising:
an auxiliary mass and
a wire rope isolator acting as a non-linear suspension, which is configured to connect the auxiliary mass to a vibrating structure,

wherein:
the mass of the auxiliary mass and the stiffness of the non-linear suspension are configured to yield an appropriate natural frequency for the resulting structure,
the mass of the auxiliary mass and the stiffness of the non-linear suspension are selected such that said natural frequency is at least 10 Hz and that the amplitude of the relative displacement of the auxiliary mass in respect to the vibrating structure is at most 4 mm under normal loading, and the stiffness to mass ratio is at least 4 kN/(m·kg) using static stiffness.

Assignees

• Teknologian Tutkimuskeskus Vtt Oy

Inventors

• Keinänen Jarkko
• Vehviläinen Kalle

Classifications

• F16F7/104 Primary

  the inertia member being resiliently mounted {(F16F7/1022 takes precedence)} · CPC title

• F16F7/116 Primary

  on metal springs · CPC title

• F16F7/14 Primary

  of cable support type, i.e. frictionally-engaged loop-forming cables · CPC title

• F16F15/067

  using only wound springs · CPC title