connection ve leading from the friction clutch ktr to the ring gear hu the two embodiments of fig5 and 7 have in common that on the planetary gear carrier pte auxiliary planetary gears npe are rotatably supported so as to be in engagement with the planetary gears pe and also with an auxiliary ring gear nhe which is connected to an engageable and disengageable friction brake bn fig1 as shown in the table of fig2 the brakes b 1 and b 2 as well as the clutches k 3 and ktr are engaged in this state the three transmission structures te ta and tu are set in a standard transmission ratio wherein the reaction member u2014 sun gear se or sa or su respectively u2014 are locked in position and with respect to the power flow through the transmission disposed in series so that the transmission ratio is given by a multiplication of individual transmission ratios fig3 the state of the transmission corresponds to that of fig1 as indicated in the table fig4 since the clutch ktr and the brakes b 1 and b 2 are engaged and also the sun gear su is locked by way of the connection vuf with the brake b 2 fig5 here the state of the transmission is also such that in accordance with the table of fig6 the brake b 2 and the clutch k 3 are engaged whereby the two transmission structures ta and tu are in a standard setting u2014 with locked sun gears sa and su serving as reaction members u2014 and are arranged in series for the power flow through the transmission this is also true for the input transmission structure te but in this case the standard.