spongebob007
Military
- Sep 14, 2007
- 265
Let me start by saying I have zero practical experience with random vibration and only a very fuzzy knowledge of the theory. I have successfully designed isolated systems to attenuate shock and harmonic vibratory loads.
What I am dealing with is one of our current products that consists of commercial electronics that are mounted using vibration mounts. The assembly has successfully passed vibration testing so the isolated system has proven itself acceptable for harmonic excitation. Recently we have sold this equipment to a new customer and they require it to pass random vibration. The equipment failed. I examined the equipment and determined that the most likely cause of failure was the vibration mounts bottomed durning testing and generated enough force to cause damage to the isolated equipment.
For harmonic motion, design of an isolated system is as simple as selecting isolators such that the driving frequency is greater than 1.4 times the isolated system frequency (2X or more ideally) and that there is sufficient excursion space for the isolated system to move under load. The isolated structure also needs to be stiff to avoid unwanted amplifications. But how does one go about selecting an isolator stiffness when frequency content between 1Hz and 100Hz is going to be hitting the sturcutre essentially all at the same time?
One of the lessons learned from harmonic motion is that sometimes a poorly designed isolated system is worse than no isolation at all. Along those lines, I was also considering just removing the isolators altogether and trying to harden the equipment to withstand the full force of the vibration.
What I am dealing with is one of our current products that consists of commercial electronics that are mounted using vibration mounts. The assembly has successfully passed vibration testing so the isolated system has proven itself acceptable for harmonic excitation. Recently we have sold this equipment to a new customer and they require it to pass random vibration. The equipment failed. I examined the equipment and determined that the most likely cause of failure was the vibration mounts bottomed durning testing and generated enough force to cause damage to the isolated equipment.
For harmonic motion, design of an isolated system is as simple as selecting isolators such that the driving frequency is greater than 1.4 times the isolated system frequency (2X or more ideally) and that there is sufficient excursion space for the isolated system to move under load. The isolated structure also needs to be stiff to avoid unwanted amplifications. But how does one go about selecting an isolator stiffness when frequency content between 1Hz and 100Hz is going to be hitting the sturcutre essentially all at the same time?
One of the lessons learned from harmonic motion is that sometimes a poorly designed isolated system is worse than no isolation at all. Along those lines, I was also considering just removing the isolators altogether and trying to harden the equipment to withstand the full force of the vibration.
