A gear box comprising a stationary gear component having a plurality of teeth (116a,..., 116n) formed along a tooth trace, at least some of said plurality of teeth (116a,..., 116n) differing in their tooth flank profiles at least at an initial phase of an operational lifetime of said gear box, and at least one rotary gear (121a, 121b, 121c) mechanically coupled to a subset of said teeth, wherein said at least one rotary gear (121 a, 121b, 121c) is connected to a mechanical load so as to cause compressive forces to act on said teeth flank (116a,.., 116n) of said stationary gear component that vary along said tooth trace during movement of said at least one rotary gear (121a, 121b, 121c), wherein a difference in tooth flank profiles of said at least some of said plurality of teeth (116a,..., 116n) is correlated to said variation of said compressive forces, and wherein said tooth flank profiles are individually adjusted as a function of the following formula: Δf_ φ = sinφ * f_γ * sinα_wt + cosφ * f_γ * cosα_wt wherein φ = angle of the position of the tooth to be adjusted along said tooth trace, wherein the angle is preferably measured in clockwise direction in relation to the center axis of the stationary gear component as seen from the load input side (side 0) of the gearbox, wherein the position representing an angle φ of 0° is most preferably a position which is offset by 90° in clockwise direction from a load-side intersecting position of a plane spanned by the axis of said rotary gear (121a, 121b, 121c) and by the axis of said stationary gear component when intersecting, and said stationary gear component, as seen from the load input side (side 0) of the gearbox; f_γ = amount of the effective flank line angular deviation by virtue of the influence of the tilt (γ) the axis of said rotary gear (121a, 121b, 121c) when intersecting the axis of said stationary gear component, wherein f_γ = b * tan (γ) and b corresponds to the width of the tooth along an axial direction of said stationary gear component; α_wt = working pressure angle of the gear engagement between said rotary gear (121a, 121b, 121c) and said stationary gear component; and Δf_(φ) = overall tooth flank compensation amount by virtue of the influence of the parameters φ, f_γ and α_wt. φ = angle of the position of the tooth to be adjusted along said tooth trace, wherein the angle is preferably measured in clockwise direction in relation to the center axis of the stationary gear component as seen from the load input side (side 0) of the gearbox, wherein the position representing an angle φ of 0° is most preferably a position which is offset by 90° in clockwise direction from a load-side intersecting position of a plane spanned by the axis of said rotary gear (121a, 121b, 121c) and by the axis of said stationary gear component when intersecting, and said stationary gear component, as seen from the load input side (side 0) of the gearbox; f_γ = amount of the effective flank line angular deviation by virtue of the influence of the tilt (γ) the axis of said rotary gear (121a, 121b, 121c) when intersecting the axis of said stationary gear component, wherein f_γ = b * tan (γ) and b corresponds to the width of the tooth along an axial direction of said stationary gear component; α_wt = working pressure angle of the gear engagement between said rotary gear (121a, 121b, 121c) and said stationary gear component; and Δf_(φ) = overall tooth flank compensation amount by virtue of the influence of the parameters φ, f_γ and α_wt.