40 is in the form of a ball bearing 42 alternatively the rolling bearing may be in the form of a tapered roller bearing not shown the arrangement of a ball bearing 42 or a tapered roller bearing in place of the needle roller bearing 33 is especially advantageous since ball and tapered roller bearings 42 inherently make possible a lower coefficient of friction needle roller bearings 33 inherently have a higher coefficient of friction in particular when loaded with axial forces the use of a ball or tapered roller bearing 42 therefore has the advantage that in the event of failure of the electromechanically actuated service brake the residual clamping force to be set can be reduced to a minimum above all a ball bearing 42 has the further advantage of being very cost effective in production through their construction ball and tapered roller bearings 42 have a larger space requirement than needle roller bearings 33 in order to reduce the space requirement the force measuring device is advantageously configured in such a way that a part of the ball or tapered roller bearing or the ball or tapered roller bearing itself forms the deformable element 43 of the force measuring device 40 in the second exemplary embodiment represented in fig3 the ball bearing 42 is arranged between the threaded spindle 17 and the force measuring device 40 the ball bearing 42 serving to transmit force between threaded spindle 17 and force measuring device 40 the force measuring device.