The calculation for determining where to cut the intake manifold is based upon wave theory. When the valve opens it will create a negative pressure wave. This causes air to rush inwards and displace leaving a small amount of negative pressure in their wake which pulls the molecule behind it. This wave is more of a pulse due to the vacuum source not being constant, as the piston travels it does so in a non-linear acceleration curve. Once the valve shuts it will create a relative high pressure front. If you plot out the pressure you will have a sine curve. Apply this over time and you have a resonance model. When you achieve pressure front speeds that are in tune with the opening of the next valve you will achieve the desired effect, increased airflow. Read up on Helmholtz resonance, it will explain this further.
The volume of the plenum, the length of the runner, the area of the runner, piston speeds, valve timing, and alot of other aspects go into designing the intake manifold. Plenum volume should be designed first, once you have decided upon a camshaft, you need to plot it out in a 360 diagram of valve timing and overlap. This will give you the Delta P moments you need to determine optimal timing. After figuring the optimal timing for the pulse per a given RPM (where you want peak power, typically cam dictated) you can design the runners. The length of the runners is the easiest thing to modify. It allows you to run a gradual venturi flow and dictate the geometry of the flow inside the runner via radiusing. Lastly you will modify the area and geometry of the inlets. This is restricted in large part due to port design.
One of the many things people do not look at is the geometry of the internal flow. Once the air enters the intake manifold it will be traveling at a certain vector and velocity. The vacuum causes this vector to adjust towards the low pressure source. The flow at this point is fluous and the port radii will cause variations in the flow velocity and vector direction. Running the flow at too high of a velocity can cause turbulance as the flow grades against the wall of the port, this is typically an issue on high port heads with narrow radius turns. Likewise if you slow the flow too much with a sharp radius you will reduce the mass flow. The objective is to increase flow velocity as much as possible without exceeding about 0.98 Mach at the valve (lift, valve sizing, and volume dictate this number). Exceeding 1 Mach will create a turbulent flow and will decrease mass flow. Typically the KA will not have this issue (the valves are adequate), although you could possibly achieve it running a small lift cam.
Another mistake people commonly make is assuming that a forced induction car requires less intake manifold design. While this might be true in practice (due to N/a engines requiring additional engineering to make power), it doesn't make it correct in theory. In theory you simply are looking at delta P. Increasing manifold pressure just alters the atmosphere in which the engine runs. An N/a engine runs up to about 14.5 PSI of atmospheric pressure in the intake manifold, aka 1 BAR absolute. A turbo engine simply runs as if you could raise atmospheric pressure. The physical principles of the flow remain the same in relation to the application of laws [of physics].
All of this is worthless if you are running a sub-par exhaust manifold. Just something to remember.
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Data? It's all in how volumetric efficiency works.Edub1 wrote:Wow, all that. Well perhaps I spoke too soon. I must admit you have sparked my interest a little.
How much does one of these cost & do you have any data that might demonstrate these things?
Here it is plotted out.
Assume an engine VE increase of 5% roughly, and a 0.15 - 0.20 BAR drop in pressure to maintain equal engine flow.
Notice how the green line (with intake manifold) is not only flowing the same amount of air, but the compressor is turning at a slower RPM. This in turn allows the turbine (typically) to be more efficient, reducing backpressure and increasing engine output further.
Reducing the shaft RPM at the turbo will cool the oil temps to a small degree and that will help to reduce coolant temps, as will removing the restrictive passages in the old intake manifold.
Nevermind the fact that it is a lighter manifold with less crap on it and you stand to make more power at the limit since you are at a wider point in the compressor map.
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Because it's engine efficiency.Edub1 wrote:How much benefit would such a manifold be over stock?
Say a guy has a T3/T4, is he going from 400HP to 500HP at the same boost level?
What is the actual HP gain and how is it so much better than another few lbs? By the way, manifolds are specifically tuned to the motor based on tubal resonance and many other factors so you would probably have to do a lot of monkying before you get it right.
Like I said, if you want sick power that is a different matter. How much does a good aftermarket one cost?
With an intake manifold properly designed to make power you will see less exhaust backpressure, lower boost temps, greater turbo life, lower oil temps, lower coolant temps, and you can more accurately take advantage of a turbochargers mapping (maps are widest at lower pressures).
It's not about the power, it's about the efficiency and doing it right. You could make 600whp on a stock manifold thats been hogged out, but the powerband will not be ideal, and you will be pushing the turbocharger hard.
Feel free to critique