Number_Cruncher
Active Member
As you may know, I'm extremely sceptical about the way losses are estimated by dyno operators, and I'm also fairly sceptical about the measuring technique many of them use to begin with.
What Steve's plot shows is that the gradients where the torque lines cross, especially for the higher gears, isn't large. This means that small errors in local road gradient can cause problems for the inclinometer method.
An interesting point in Steve's first graph (which is in the spreadsheet too) is that the tractive effort curves all fit together under the smooth curve you would get with a CVT operated at maximum power - the individual curves are tangent to this ideal curve at the maximum power engine speed.
>>Losses are exponential to the power supplied.
Really? I usually work with the assumption that they are proportional, or, in the case of frictional losses for lip seals or bearing pre-loads, a simple constant torque.
What Steve's plot shows is that the gradients where the torque lines cross, especially for the higher gears, isn't large. This means that small errors in local road gradient can cause problems for the inclinometer method.
An interesting point in Steve's first graph (which is in the spreadsheet too) is that the tractive effort curves all fit together under the smooth curve you would get with a CVT operated at maximum power - the individual curves are tangent to this ideal curve at the maximum power engine speed.
>>Losses are exponential to the power supplied.
Really? I usually work with the assumption that they are proportional, or, in the case of frictional losses for lip seals or bearing pre-loads, a simple constant torque.
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