shady wrote:gruntguru wrote:Axial and centrifugal compressors are "rotodynamic" machines. This means they work by accelerating the air to a high velocity (kinetic energy) then convert that KE to pressure by slowing it down again in a diffuser. In broad terms the PR of each stage is limited by the velocity ratio of the outlet to inlet of the rotating part (impeller).
It is obvious immediately that a centrifugal compressor impeller has a relatively slow inlet and much higher velocity outlet - being placed much further from the axis of rotation.
Axial compressors achieve a velocity difference through blade shape. At the intake side the blades are slicing through the air as it approaches roughly axially (small tangential velocity component). As the air passes along the blade, it is turned to rotate in the same direction as the rotating impeller so it now has a large tangential velocity component in addition to its axial (flow) component. It should be clear that the potential for achieving a large velocity ratio is much less for the axial compressor. If higher pressures are required, it is necessary to slow the air down in a diffuser (stationary vanes) and repeat the process in another stage.
Do you have an equation? Based on some of the schematics shared, that may not be the case if it is, a radial compressor still has waste gates, which is to say excess pressure.
Turbomachines follow Eulers turbomachine equation. That means that the enthalpy change over a compressor can be described as:
dh = U2*C2-U1*C1
Where U2 is the blade velocity at the outlet, U1 blade velocity at the inlet, C2 tangential fluid velocity at the outlet and C1 tangential fluid velocity at inlet.
Since the radius of the inlet is smaller than the outlet on a centrifugal compressor, the blade velocity U1 is always lower than U2.
The power required by the compressor is the enthalpy change multiplied with the massflow
P = m_dot*dh
A wastegate work by reducing the power output of the turbine driving the compressor.