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Anonymous Poster

Run-Out Criterion

03/03/2010 8:52 AM

In any rotating machine, let us say a gear box, what is the acceptance criterion on radial and axial run-out on output flange?

It is a low speed gearbox (1000 RPM / 40 RPM), quite large (power transmission 500KW-700KW)

There are good vibration acceptance levels - VDI, DIN.. have them.

I tried to search the run-out data but every where- say AGMA, API, DIN,... it is usually related to coupling, alignment, etc.

However in this case there are none of these in picture. The flange rotates a otherwise unsupported table (located both axially and radially by the gearbox bearings) - on the low speed flange.

Is there any general standard where like the vibration standards (these are also application independent) there is a standard that limits the Run-out, say based on certain grades/ classes A,B,C,D,... (like the vibration) ?

For our high speed machines we have them say turbine journal run-out but what about the outlet flanges of low speed machines?

Any-one come across a standard?

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Join Date: Aug 2009
Posts: 53
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#1

Re: Run-Out Criterion

03/04/2010 8:45 AM

Checkout ISO 5753-1 Rolling bearings-internal clearnance, part 1: radial internal clearance for radial bearings.

This should get you started. I suspect the runout will be a function of bearings you use in your machine. However i also suspect runout is a derived value. Usually other criterea drive runout in machines, so there probably isn't any 'standard' to go by. Weight, RPM, life expectancy, etc. all a considerations to how much radial runout you allow.

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Anonymous Poster
#2
In reply to #1

Re: Run-Out Criterion

03/04/2010 9:03 AM

All that aspects are taken care of (in fact the bearing clearance (at some other bearings) are chosen to control this after preload.

This is a bit complex bearing arrangement and the location is by a spherical bearing with the arrangement that ideally the bearing will retain the shaft at center. The radial endplay exists for the floating shaft (it is a fixed ring planetary).

The endplay at the shaft stage is OK. On this shaft the output circular flange is shrunk in. The problem is that once it is shrunk, the shaft is un-approachable and you can only see the r/o on the flange OD.

The type of loading on the table is very highly unbalanced. Exactly for that reasons I am unable to count the balancing of the rotating mass also into my logic.

The problem is here while doing the no-load test when the unbalance does not exist what should be the run-out. The design fails due to the basic requirement which should constrain the run-out in actual operation are non-existent here

- constraint on the coupled component- freely supported (of course stud tensioned to it, but no guide or constraints at least within few milimeters)

- On a weight of rotating mass of 20T, the unbalanced load (peak) is 35T.

- Totally undefinable low cycle fatigue loaded.

Designer has given a value of 0.1mm on a diameter of 2.5 meters. But no justification from any of them (just given a close value I guess to keep us on our toes )

So I wanted to know like normal bearing standards or vibration standards where based on approximate machine characteristics they give a recommended value is there some sort of value for Run-Out too?

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