Hi people,

I am doing a convective heat transfer analysis in engine - SimScale & SimScale - cooling jacket.

The main idea was to specify a fixed power heat flux [W] on few faces, others to keep adiabatic and see, how much heat would be absorbed by the water flowing through the channels. Results should provide input for pressure drop calculation and wall temperature load determination.

Boundary conditions could be seen in the mentioned projects, and also on the pictures below:

– INLET

– OUTLET

– HEAT FLUX

– ADIABATIC

.I have some troubles during simulations

and

.I don’t know if the problem really lays in geometry or maybe in B.C. conditions.

I did offline calculations in OF23x (using buoyantBoussinesqSimpleFoam solver) on my local machine and didn’t see the problem, that occurs here, but I had a problem concering the overall temperature difference of water.

My problem was, that I followed basic physics, that means

power_heat_flux[W]=mass_flow[kg/s]*termal_capacity[J/kgK]*temperature_difference[K]

but when I integrated phi on inlet and outlet and multiplied by density to get the mass_flow and also averaged temperature on inlet and outlet and put in the equation above, I got much bigger temperature difference from simulation, then by hand.

This was the main reason, I came here. I wanted to verify that I did some mistakes locally, but a whole lot different problem occured.

Kind regards,

Sergej