A conical surface friction type overrunning clutch, comprising: an inner ring, an outer ring, a first intermediate ring, a second intermediate ring, and an elastic pre-tightening member; wherein, the inner ring, the outer ring, the first intermediate ring and the second intermediate ring have a common rotation axis; the first intermediate ring and the second intermediate ring are both located between the inner ring and the outer ring; the first intermediate ring and the second intermediate ring each cooperates with one of the inner ring and the outer ring via conical surfaces, to respectively form at least one first working friction pair and at least one second working friction pair which are both axially engageable and disengageable; and a first force amplifying transmission mechanism and a second force amplifying transmission mechanism are respectively formed between the first intermediate ring and the other one of the inner ring and the outer ring and between the second intermediate ring and the other one of the inner ring and the outer ring, and the first intermediate ring and the second intermediate ring are respectively connected to the other one of the inner ring and the outer ring via the first force amplifying transmission mechanism and the second force amplifying transmission mechanism; the elastic pre-tightening member has one end arranged on the first intermediate ring or the second intermediate ring, to allow all the working friction pairs to maintain an elastic pressing force which meets a working requirement when the working friction pairs are not working; the first working friction pair and the second working friction pair have a common rotation axis, and two conical surfaces of each working friction pair that cooperate with each other have equal cone apex angles; and, at least one of the force amplifying transmission mechanisms is configured to convert a relative rotation arc length between the respective intermediate ring and the inner ring or the outer ring which is connected to the force amplifying transmission mechanism to an axial relative displacement, characterized in that for the cone apex angle of any one of the working friction pairs, the cone apex angle referred to as θ and a friction coefficient of the friction pair referred to as μ 0 must satisfy a condition of 2arctan(μ 0)<θ≤180°, wherein arctan () in the formula represents arctangent function, and the condition is to ensure that self lock of the working friction pair will not occur; and in a case that the relative rotation arc length is Φ, and the generated axial relative displacement is λ, and the friction coefficient of the force amplifying transmission mechanism is μ 1, a condition of arctan(dλ/dΦ)>arctan(μ 1) must be satisfied, wherein arctan() in the formula represents arctangent function, and d represents differential, and the condition is to ensure that self lock of the force amplifying transmission mechanism will not occur, and each of the force amplifying transmission mechanisms is constituted by a structural shape directly formed on the respective intermediate ring directly engaging with a structural shape directly formed on the inner ring or the outer ring which is connected to the force amplifying transmission mechanism; each of the structural shapes is any one of the following structural shapes, comprising screw threads having a standard cross section or a nonstandard cross section, an axial helical surface, and an axial inclined wedge surface; and while converting the movement, the force amplifying transmission mechanism divides a tangential force between the intermediate ring and the inner ring or the outer ring to generate an axial component force between the intermediate ring and the inner ring or the outer ring.