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The drawing for the seal shows a clearance of .065" - .070". I believe this is per side. As I mentioned earlier, the seal was pushed all the way to the left and the gap measured .160". This leaves .080" per side, which is close.

Not really worried about the ID. We do clearance checks to ensure we have sufficient clearance there. We just found an unusual gap at the horizontal split line, that's why I was asking the question. See picture:

Yes you are correct, I was thinking a little too hot for that area of the turbine. It is more like 120F. My question reall was; do I treat it like a straight piece of aluminum? Or do I take into account the curvature?

measurement of .140" taken - this should be .160". Don't know how to edit threads.

All, Question about thermal expansion of oil seals. I have seal with a clearance between the top and bottom at the horizontal joint of .160". This measurement was taken with the seal pushed all the way to one side as to close up the left horizontal joint and measurement of .140" taken at the...

So if I was to look at this print to determine the maximum run out on the vertical face of that flange, I would use .0005" because of the perpendicularity reference there. That's fine, I used .0005" as my tolerance and we got the vertical run out on the face down to .0004". However, I don't...

It's for a GE frame gast turbine. Yes it probably was made somewhere around 1960-1970. Can't really see any dates on the drawing. The coupling I am referring to is the marriage coupling between the compressor and turbine rotor. I have set the tolerance for the axial run out on this face to...

The attached drawing clip is from a rotor machine drawing and I have the following questions about the run out on this rotor: 1) Which symbol represents the run out on the vertical face? Which symbol represents run out on the rim? Is perpendicularity the same as runout on the face? My machinery...

Copper wire bar, cake, slab, billets, ingot and Ingot bar ASTM B5

Can you elaborate a litte on this? A polytropic process is one that is reversible, the process that goes on inside the compressor is not reversible. There is always heat loss due to friction. Therefore, I can not assume that the process is reversible. I thought that comparing real enthalpy and...

Actual enthalpy out is always more than isentropic enthalpy out in a compressor. Enthalpy increases due temperature increase caused by friction. Isentropic enthalpy assumes no change in entropy due friction. If the numerator and denominator were switched, this would cause efficiency to be over...

I know that this subject has been covered before on this site. However, I was interested in learning more about tracking compressor efficiency using enthalpy. I have access to an excel add-in that will calculate enthalpies and entropies based on pressure, temperature, and humidity. This excel...