BillA
12-17-2004, 01:27 PM
am in the midst of rad testing, and as usual I'm daily reminded of what miserable work this is
much of the difficulty has to do with maintaining steady state conditions, w/o which intelligible data cannot be collected
the question has been raised as to the suitability/appropriateness/necessity of the LMTD characterization of the rad's wet side temp, and upon reflection it would seem appropriate to make the same characterization of the dry side
- for this it would be necessary to know the mean velocity, atmospheric pressure, humidity, inlet and outlet temps, and the pressure drop - but this info requires very sophisticated equipment not at hand
-> the solution would seem to be the continued use of what is standard practice,
using the inlet air and inlet coolant temps to characterize the temp difference, "C"
opinions solicited
the heat dissipated is measured with a defined temp difference between the air and the coolant, this is an arbitrary amount as a very good WCing system with substantial radiator overcapacity could have a temperature differential of 5°C whereas a more typical system would see a 10°C rise in the coolant temp over ambient
this has caused a bit of confusion, my initial testing had a 10° differential, the ThermoChill rads were done with a 5° difference (presumably reflecting 'better' systems), and my present testing is again with a 10° difference (as does JoeC's)
- whatever the differential is, it causes extreme difficulty in testing as both the coolant and air temps respond differently yet must be maintained at a fixed interval
-> I am considering allowing the differential to 'float' within a range of ±1°, calculating the actual C/W, then back calculating the W dissipated with a 10°C differential
this will have the effect of removing the error of the temp differential measurement/control from the dissipation calculation
comments are solicited
the reason behind both of the above changes is the variation in air temps across the inlets of a dual fan rad, and while the phrase "in an environmental chamber" sounds impressive - achieving uniform temps across the dual inlets is not possible
- but knowing what the air temp actually is is not so difficult (4 RTDs, 1 in each quadrant, avg temp = inlet air temp for that fan; same setup for each fan)
one has to speculate as to how others control/quantify the inlet air temp
pH is going to be very unhappy, this is a vexing problem
much of the difficulty has to do with maintaining steady state conditions, w/o which intelligible data cannot be collected
the question has been raised as to the suitability/appropriateness/necessity of the LMTD characterization of the rad's wet side temp, and upon reflection it would seem appropriate to make the same characterization of the dry side
- for this it would be necessary to know the mean velocity, atmospheric pressure, humidity, inlet and outlet temps, and the pressure drop - but this info requires very sophisticated equipment not at hand
-> the solution would seem to be the continued use of what is standard practice,
using the inlet air and inlet coolant temps to characterize the temp difference, "C"
opinions solicited
the heat dissipated is measured with a defined temp difference between the air and the coolant, this is an arbitrary amount as a very good WCing system with substantial radiator overcapacity could have a temperature differential of 5°C whereas a more typical system would see a 10°C rise in the coolant temp over ambient
this has caused a bit of confusion, my initial testing had a 10° differential, the ThermoChill rads were done with a 5° difference (presumably reflecting 'better' systems), and my present testing is again with a 10° difference (as does JoeC's)
- whatever the differential is, it causes extreme difficulty in testing as both the coolant and air temps respond differently yet must be maintained at a fixed interval
-> I am considering allowing the differential to 'float' within a range of ±1°, calculating the actual C/W, then back calculating the W dissipated with a 10°C differential
this will have the effect of removing the error of the temp differential measurement/control from the dissipation calculation
comments are solicited
the reason behind both of the above changes is the variation in air temps across the inlets of a dual fan rad, and while the phrase "in an environmental chamber" sounds impressive - achieving uniform temps across the dual inlets is not possible
- but knowing what the air temp actually is is not so difficult (4 RTDs, 1 in each quadrant, avg temp = inlet air temp for that fan; same setup for each fan)
one has to speculate as to how others control/quantify the inlet air temp
pH is going to be very unhappy, this is a vexing problem