Cantilever Vent Line Vibration - Mass Addition_ - Topic
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electricpete posted 05 May 2010 04:13 PM
We have a 1" vent line that extends straight up from a LARGE pipe
in a cantilever fashion.
We see varying high vibration on the pipe up to 4 ips at a
subsynchronous frequency approx 1500 cpm (machine operates at
5200). I think it is flow noise. Other similar sister machine pipes
vibrate at 0.5 ips or less.
We added 5-7 pounds weight and magnitude came down as well asfrequency. Details attached.
I think we are just lowering the resonant frequency below the range
where the flow-induced excitation is highest. I realize lowering
resonant frequency is a more logical strategy for fixed-frequency
excitation rather than broadband, but it seems to have worked in
thise case.
Does it make sense to permatize weights similar to this?
SGFP23_VentlLineSmall.ppt (958 Kb, 91 downloads)
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
Ron
Brookposted 05 May 2010 04:28 PM Hide Post
EP,
Go ahead and add more weight and test it. You are adding inertia
which will lower the displacement, but it would appear that there isalso a natural frequency involved that you are moving away from.
Ron
Posts: 916 | Location: Philadelphia,PA | Registered: 18 July2006
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WaltStrong
posted 05 May 2010 05:28 PM Hide Post
El'Pete,
That was a good start. A true rigid weight of 10-12 lbs might give a
frequency redct ion over 20% (now 17%) and reduce vibration levels
further. More weight would be needed if it was installed closer to
valve body, so keep elevation high on stub pipe, as possible.
Walt
Posts: 2147 | Location: Massachusetts | Registered: 27 April2005
electricpete posted 05 May 2010 09:14 PM Hide Post
Thanks. We are going to clamp weight onto the pipe cap using
device shown attached. The clamp weight around 6 pounds with
provisions for additional weight in 3 pound increments, following
Walt's comment. Our machinist says he will figure out the exact
dimensions needed to get good clamping action on the pipe cap.
We didn't try stiffening. My thought is that the initial directionwould be increase in vibration with small amount of stiffening
(based on weight addition results), but certainly could turn back
down as we get stiffen farther. There is not a lot to brace off of as
you can see it sits in the air. The adjacent blue structure isremoved (during outages), so it would not be good to clamp to. If I
had more time, I might investigate that further but we're far enough
into weight addition that I'm going to stick with it (unless there are
some obvious problems with this design anyone can think of).
One the thing that makes me a little uneasy is the idea of tuning
away from broadband flow noise. We are now a little less than full
flow. Would frequency of flow noise be expected to change withchange in flow? How about change in fluid temperature?
Another interesting thing is that the magnitude of the vibration
wanders up and down. Would this type magnitude variation be atypical expected behavior for a resonance excited by broadband
flow noise?
This message has been edited. Last edited by: electricpete,
05 May 2010 09:24 PM
Clamp4a.ppt (1,136 Kb, 64 downloads)
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
Ron
Brookposted 06 May 2010 06:58 AM Hide Post
EP,The response of a component at resonance is always dependent on
the amount of energy in the forcing function. The amplification factor
doesn't change.
If the 'broadband' energy you describe in this pipe doesn't have a
defined flow resonance, then the amplitude of the response with
change with % of flow.
My guess is that there is a fluid resonance and the amount of energy
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at the resonance could be affected by small changes in flow day to
day.
I like the design of the weights.
Posts: 916 | Location: Philadelphia,PA | Registered: 18 July2006
Walt
Strongposted 06 May 2010 08:58 AM Hide Post
El'Pete,
An increase in flow velocity generally raises turbulence peak frequency
and amplitude. Temperature change would probably have insignificant
effect on structual natural frequency. I think that the add-on weight
will be as good or better at higher flow/turbulence. The only negative
about the weight design is that the additional weights are attached
by bolts in shear, and this is not the strongest clamping direction. If
you do add one or more plates to get to "magic weight" status, then
weld the plates together and to one of the clamp halves. This would
prevent loosening over time and reduce risk of losing parts should it be
removed for any reason.
Walt
Posts: 2147 | Location: Massachusetts | Registered: 27 April2005
electricpete posted 06 May 2010 11:08 AM Hide Post
Thanks. Good comments.
Now a crucially important aspect I have to describe this thing on
paper. Everyone wants to call it a dynamic absorber, but that's not
what it is. We all know it is a weight added to reduce resonant
frequency. What is the short/quick catchy name for that?
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
Walt
Strongposted 06 May 2010 11:45 AM Hide Post
El'Pete,
"Tuning Mass"
"Detuning Mass"
"NF Modifier"
"Stubby the pacifier mass"
"Magic Mass"
Be aware that the valve and stub pipe may be acting like a "dynamic
absorber" if the large pipe has a similar natural frequency. It would be
worthwhile to inspect and/or measure vibrations at other locations in
the pipe system to be sure that no new high vibration problems werecreated.
Tip: Use thin SS shim stock to be sure there is a tight 2-point (each
clamp half) contact to stub pipe.
Walt
Posts: 2147 | Location: Massachusetts | Registered: 27 April2005
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William_C._Foiles posted 06 May 2010 12:57 PM Hide Post
Should the goal be to eliminate the branch pipe vibration or to
just follow the pipe vibration?
One can address the main pipe vibration separately.
Mass can not only de-tune; it can change the mode shape.
Regards,
Bill
Posts: 2545 | Location: Houston, TX USA | Registered:23 February 2005
electricpete posted 07 May 2010 11:48 AM Hide Post
The small pipe has enough access we could measure bottom, middle
and top. Levels highest at top, lowest at bottm, in the middle
between. The pattern stayed the same with our initial 5 pounds
added mass. So I think it is 1st mode shape of cantilever beam andthe main pipe is not vibrating excessively.
LOL - I would have liked to seen my bosses face if I wrote "magic
mass" in my paperwork. I like "Detuning mass" - it is very short and
descriptive, and I would've used that if I'd have thought of it or
read it in time, but I ended up using "vibration-reducing weight"(pretty lame).
Operations wouldn't let us attach anything to the pipe cap since
they have to remove it for fluid system venting during every plant
startup. So we have to clamp to the pipe below the cap rather
than to the cap. Also we have to keep enough clearance to
operate the valves. I had to get agreement from a pipe stress guy.He wanted to restrict the total weight added to 15 pounds and
ensure it was symmetric about the pipe (no moment). All of this
forced the design to evolve to what is shown in attached. It has
minimum 5 pounds (clamp) plus provisions to add additional weightin 1.8 pound increments. Our machinists built the device yesterday.
It may be installed today or over the weekend or Monday. Will let
you know results.
FinalVibrationReducingWeight.ppt (1,224 Kb, 52 downloads)
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
Steve
Cieslaposted 07 May 2010 02:42 PM Hide Post
At least the name you picked meets the nuclear criteria for TLA
(Three Letter Acronymn).
Posts: 442 | Location: Southern California | Registered: 23February 2005
electricpete posted 08 May 2010 09:09 PM Hide Post
lol - good point Steve.
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The "VRW" was installed today. I was not there, but the report is
that the full 14.5 pounds was installed all at once (didnt try any
intermediate mass level) . The vibration reduced to 0.20 0.23 ips
on top of the pipe in both directions at a frequency of 1145 cpm.
Vibration remained approx 0.20 at bottom of the pipe. I have no
report of vibration level in the middle of the pipe (will check Monday
to try to get an idea of the shape).
Fitting this data against SDOF model:f = C / sqrt(M0+Madded)
Madded = 0 pounds => we had 1555 cpmMadded = 5.5 pounds => we had 1290 cpm.
From above first two datapoints we solve C=5418 cpm*lbm^0.5 ,
M0 = 12.14 lbm
From the above we would predict:
Madded = 14.5 pounds => 1050 cpm resonant freq (SDOF
prediction)
But we actually had
Madded = 14.5 pounds => 1145 cpm resonant freq (actualmeasured)
So a SDOF model does not fit very well accross this range of
attached masses.
This message has been edited. Last edited by: electricpete,
08 May 2010 09:28 PM
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
William_C._Foiles posted 09 May 2010 05:08 PM Hide Post
Often one can brace the smaller pipe to the larger one. Could
this not be done?
When the frequency changes a great deal and when the
added mass is a considerable fraction of the total mass it ispossible that the mode shape has changed. The frequency
reduction for this mode could be close to reaching a limit, i.e.
close to the point where it would be with infinite mass
(probably some room to go further if desired).
Regards,
Bill
Posts: 2545 | Location: Houston, TX USA | Registered:23 February 2005
roughrider posted 09 May 2010 05:44 PM Hide Post
Reminds me of using a stabilizer on a bow, the longer the stabilizer
the less weight required to prevent torque.
Posts: 12 | Location: alaska | Registered: 01 March 2010
Walt
Strongposted 09 May 2010 07:44 PM Hide Post
El'Pete,
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4 ips down to 0.2 ips is fantastic! The deviation from SDOF may be
nonlinear effect of clamping the weight to the pipe as opposed to
welding it. I think you had the right solution with the weight instead of
bracing to the main pipe, and an infinite mass was not needed either.
Paint it and file the results of the Case History"!
Walt
Posts: 2147 | Location: Massachusetts | Registered: 27 April
2005
William_C._Foiles posted 10 May 2010 07:58 AM Hide Post
If you got a similar reduction in acceleration, did the force at
the tip from inertia go down, remain the same, or go up? How
about the dynamic moment at the intersection with the big
pipe?
Regards,
Bill
Posts: 2545 | Location: Houston, TX USA | Registered:23 February 2005
electricpete posted 10 May 2010 10:29 AM Hide Post
We did get a chance to take a closer look today. Vibration at
bottom/middle/top in both direction was no more than 0.23 ips and
no less than 0.17 ips (0.2 0.23 ips at top and 0.17 0.2 at
bottom). We dont have a 2-channel analyser to take phase, but
even if we did, Im not sure we would get a stable phase reading
given the flow excitation.
I summarized comparison of 4 configurations in attachment:
Slide 1 original configuration 1555 cpm (1 4 ips)Slide 2 5.5 pounds weight (clamps added) 1290 cpm (0.6 1.4
ips)
Slide 3 [NEW] 14.5 pounds permanent weight 1145 cpm (0.17
0.23 ips)
Slide 4 [NEW] Sister units with different (smaller) valve style
2300 to 2700 cpm frequency. 0.2 0.45 ips among 5 sister units
with smaller valve (we only have one with the larger valves... the
one that originally had the 1-4 ips vibration)
So, I conclude the sister valves likely have 1st resonance above
the excitation frequency, and that the flow excitation falls of
rapidly outside of a narrow frequency band somewhere in theneighborhood of 1550 cpm to somewhere below 2300 cpm. (I would
have thunk it would be a wider range).
I tend to agree with Walt that the only thing left to do is the
painting. But certainly willing to discuss and learn what we can from
this.
Bill as I mentioned earlier there is nothing handy to easily stiffen
against. Certainly would be more work to try to build something like
that. What advantage would it have been to stiffen instead of
adding weight?
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I dont think stresses from shear forces will be relevant since this
resembles a long thin beam and bending stresses (from moment) are
typically much greater than shear stresses (from shear force) in a
long thin beam. It was our objective to reduce bending stresses
from moment near the bottom (as Bill mentioned) where this vent
line is welded to the main pipe which should be much larger. I tend
to think we have accomplished that objective simply because we
tuned obvious resonance away from the excitation, although I dont
have means to calculate any stresses to provide proof. In the initialconfiguration we had what I believe is excitation near first resonant
frequency where 1st mode shape is cantilever beam 1st modeshapewith highest moment and bending stresses at the base. Im not
positive what the final mode shape looks like after weight addition,
but my suspicion is we cannot get anywhere near the 2nd resonant
frequency based on trying some preliminary calcs. The piping is 1
schedule 160, i.e. 0.815 id and 1.35 od. The length from big pipe
to tip of vent line is 23. The 1st valve is attached 8 from main
pipe, 2nd valve is attached 19.5 from main pipe, and permanent
14.5 weight is attached 22 from main pipe. The valves I estimated
in the neighborhood 10-30 pounds. Thats a big range
(uncertaintly), but anything within that range still gives us apredicted 1st resonant frequency in the very rough ballpark of our
measurements, and predicts 2nd resonant frequency way up in theneighborhood above 6000cpm. If in fac t the 2nd mode is that high
in frequency, then we must still be seeing a first mode shape whose
shape is not tremendously different than the original and I dont
think there can be enough increase in curvature to overcome the
dramatic decrease in peak vibration magnitude (4.0 ips down to
0.23 ips). My preliminary calcs considered the main pipe stationary.
Will try again sometime with main pipe movement allowed (forcing
function)... I imagine that will have some effect on the conclusion
of how high the 2nd resonant frequency is.
Always open to further discussion and comments.
This message has been edited. Last edited by: electricpete,10 May 2010 11:13 AM
PhotoComparison.ppt (3,934 Kb, 33 downloads)
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
electricpete posted 10 May 2010 07:31 PM Hide Post
One thing you guys may have noticed... there is a gap between the
clamp halves. We did not shim as Walt had suggested. It certainlydoesn't look right to the eye. My first thought is to wonder whether
it will increase susceptibility of the bolts to fatigue (thinking aboutbolt joint diagram, where compression of the joint plays an
important role). My 2nd thought, maybe the stretch in the clamp
halves plays a similar role for this device as joint compression does
for a typical bolted joint. What do you guys think?
Note - if this device should fall off, there is nothing fragile below it
and also it's not a place where people would be.
This message has been edited. Last edited by: electricpete,
10 May 2010 07:43 PM
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Reply
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
electricpete posted 12 May 2010 07:44 AM Hide Post
Heres a related quest ion. Would you consider this fix as
permanent ?
We require 2 barriers for the high-temperature water in the main
pipe. The pipe cap counts as one barrier while installed. The pipecap is only removed for system venting when the system is cool
during plant outage/startup. So we only need one of those two
valves. We could remove one of the vent valves during the next
plant outage (we cant do it on-line because the system is hot andwe wouldnt have isolation to cut out the valve out, short of using
freeze seal).
As I said, the consequence of weight falling off is not a problem.
The consequence of vent pipe breaking at the bottom weld from
vibration fatigue would be big problem.
Any opinions on whether this weight should be considered
permanent, or whether we should go to the expense/effort ofcutting out the extra valve (and updating drawings) instead?
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
electricpete posted 13 May 2010 10:19 AM Hide Post
Thanks Sam. What are your reasons?
fwiw - I tend to agree. There is of course one selfish reason - If
the thing works fine forever, no-one will ever think about the
weight or my involvement in it again. But if something goes wrong
many years from now (lets say the year before I retire!), they willlook up the paperwork and come straight back to me.
If I were to champion a request for design change and work order
to cut the valve off, I would need a little more justification.
I could say the flow excitation might change over time which could
eventually make the weight ineffective... but if that's a concern
than it applies to both solutions (the weight and cutting the valve).
Although I do tend to think we would have a lot more margin above
the existing flow excitation frequency band before we get to
resonance with one valve cut off than we have below the existing
flow excitation band before we get to resonance with the weight
installed.
Posts: 5545 | Location: Texas Gulf Coast | Registered: 20February 2005
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