V-BELT PULLEY AND VARIATOR

Abstract: The object of the invention is a pulley and variator, or a transmission being adjustable or self-adjusting, where the transmitting element is a V-belt or a like flexible link and the pulleys consist of two disklike sheaves (2, 3) being pressed together. The aim is to reduce the power losses between the belt and sheaves even under the rate being possible with the same belt in the non-variable transmissions. The mean is to modify the bearings (6, 7, 9, 10) and the structures (11, 12, 13, 14) by such a way, that the sheaves (2, 3) are neither non-loaded nor loaded parallel, but so inclined, that the groove between sheaves has its maximum width at the points, where the belt leaves the driving pulley and comes onto the driven pulley.

Description: V-BELT PULLEY AND VARIATOR The invention concerns transmissions having a variable ratio and being adjustable or automatically self-adjusting by means of pulleys consisting of sheaves being axially movable to each other and contacting on flanks of a V-belt or a like flexible link transmitting the power. The objects of the invention are pulleys and variators including them. The basis of the invention is an observation that power losses between the belt and the pulleys are mainly caused by lateral clearances and resiliences of the sheaves and belt and dominating in relation to the bearing losses. For this reason the V-belt variators have generally a clearly lower efficiency rate than non-variable transmissions. The basic idea of the invention is to modify the bearings of the sheaves by such a way, that the sheaves are not parallel when they are non-loaded or the belt is missing between them, but so inclined that bending load caused by the belt makes them approximately parallel. In itself it is not a new idea to make the sheave halves of a variable pulley non-parallel. It is known for example in the patent publications ' USP 3757594 (F 16 H 55/52) and GB 2041116 A (F 16 H 9/12). The solution according to this . invention is deviating from both devices mentioned afore by such a way that the distance of the contact rings on the sheaves is not smallest at the middle point of the touching areas, but deviates from it approximately 45° to the direction of rotation in the driven pulley and to the opposite direction in the driving pulley. This improvement, which seems little and easy to be found, when valued ' afterwards, is however important, since without it no effect can be born reducing losses of the power and improving the efficiency. The pulleys made according to the prior known inventions are functioning right only without loading torque moment. When the belt is loaded, the problems caused by its wedging and jamming can become even worse than in pulleys, where the sheaves are parallel before loading. Particularly when the V-belt is wide or else laterally compressible the inclination of the sheaves shall be greater than required to compensate only the clearances and resil¬ iences. In other words the- distance between the sheaves shall be greatest approximately at the points, where the belt leaves the driving pulley and comes onto the driven pulley. The sufficient total inclination is 0,1...0,4 grades or 0,0017...0,007 radians and the main means to accomplish it is to make the radial bearings eccentric and substitude the axial bearings partly or fully by rollers pushing and rolling against the rear sides of the sheaves. More in detail the characteristic features of the invention are represented in the enclosed patent claims. The invention is described in the following with the aid of examples referring to the drawing attached, in which: Fig. 1 presents in rear view a longitudinal section of a driving pulley of a bicycle variator according to the invention. Fig. 2 presents a section of such a driving pulley, where the axial force pressing the sheaves together is produced as a sum effect of a notched cup spring, a multiple- end ball screw and a roller pressing on the outer rim of the cup spring. Fig. 3 presents in cross view the driving pulley as described afore and a quarter of the notched cup spring, which can be similar also in the construction as presented in fig. 1. Fig. 4 presents schematically a V-belt variator, where the inclination of the sheaves is accomplished by support rollers substituding the axial bearings. Fig. 5 presents schematically a V-belt variator, where the support rollers are flat disks pressed radially between the rear sides of the sheaves and the par¬ ticular supporting rings. Fig. 6 presents an arrangement having less friction as before, where a wedgeshaped ring is pressed between two conical surfaces each by means of two cylindrical support rollers. Fig. 7 presents a construction, which is modified from the variator described afore, by such a way, that the function remains correct despite of changing direction of the loading torque moment. The supporting rollers are symmetrically located and idle rotating fixed into levers, which are steered by the tension rollers of the belt, by such a way that the roller on the tight side is going deeper and the roller on the slack side is coming outwords. Fig. 8...10 present the longitudinal views on planes attached with axes of the pulleys corresponding the sections described afore. In the construction presented in fig. 1 the effect according to the invention or the inclination of the sheaves (2 and 3) is caused by a bearing system consisting of the needle bearings (6 and 7) between the frame (1) and the axially moving tubular shaft (4), a sliding bearing (9) between the pedal shaft (5) and tubular shaft (4), and the ball bearing (10), which supports the left end of the pedal axle to the frame (1) by such a way that it can be regulated eccentric to every direction by means of two eccentric bushings (11 and 12). The inclination can be increased by means of the roller (18), the pressing force of which can easy be regulated according to variations of the pedal force. Another alternative for adjusting of the axial force is to lead pressurized oil into the space between the tubular shaft (4) and pedal axle (5). In the construction presented in fig. 2 the only mean causing the inclination is the support roller (18), the number of which can also be greater than one. The greatness of the inclination can also be affected by the clearance of the ball screw (19). This construction is fit to be made lighter and to be easier attached to normal bicycles as an auxiliary device. In a normal construction, where the joints of the axle and pedal cranks are scuare-formed only the right crank shall be modified. The section under the axis presents an adaptation to such a construction, where the axle and cranks normally consist of only one piece. In relation to the former this construction has the disadvantage, that the production in small series would be more expensive because of the multiple-end ball screw, which must be made accurately. Fig. 3 is aimed to visualize both constructions described afore. The cup springs and support rollers can be similar in both. The schematic figures 4...7 and the corresponding sections 8...10 give intimations at the possibilities to adapt this invention made in the development of bicycle variators to the normal V-belt variators used in vehicles and industry. The possibilities are however not confined to them, but within the scope of the claims many other variations and combina- tions can be developed as well for bicycles as for other applications. Also the constructions according to the schematic figures 4 and 5 can be modified by using two or three rollers so, that changing direction of the loading torque moment does not disturb the control function. It is the simplest but not the only way to verify these changes by tasting the belt tension.

Claims: CLAIMS 1. V-belt pulley with a variable effective radius, designed for use as a component in a variable transmission or variator based on the use of a V-belt or the like, which pulley consists of a pair of sheaves (2,3) pressing the V-belt laterally between them and has such a construc¬ tion and such bearings (6,7,9,10) that, in the non- loaded state, the axes of the treads contacting the flanks of the V-belt do not coincide but intersect or are crosswise, c h a r a c t e r i z e d in that the plane or the two parallel planes formed by the axes of revolution of the sheaves (2,3) are rotatable in the direction of rotation of the pulley. 2. V-belt pulley according to claim 1, c h a r a c ¬ t e r i z e d in that the degree of divergence of the sheaves can be varied. 3. Variable transmission or variator based on the use of a V-belt or the like, in which at least the driving pulley has a variable effective radius and consists of a pair of sheaves (2,3) pressing the V-belt laterally between them and has such a construction and such bearings (6,7,9,10) that, in the non-loaded state, the axes of the treads contacting the flanks of the V-belt do not coincide, c h a r a c t e r i z e d in that the belt groove between the sheaves is wider at the point of exit than at the point of entry of the belt. 4. Variable transmission or variator based on the use of a V-belt or the like, in which at least the driven pulley has a variable effective radius and consists of a pair of sheaves (2,3) pressing the V-belt laterally between them and has such a construction and such bearings (6,7,9,10) that, in the non-loaded state, the axes of the treads contacting the flanks of the V-belt do not coincide, c h a r a c t e r i z e d in that the belt groove between the sheaves is narrower at the point of exit than at the point of entry of the belt. Variable transmission according to claim 3, c h a r ¬ a c t e r i z e d in that the belt touches the driving pulley at a point at least 10 degrees or 0.17 radians before the point where the groove between the sheaves is narrowest. Variable transmission according to claim 4, c h a r ¬ a c t e r i z e d in that the belt leaves the driven pulley at a point at least 10 degrees or 0.17 radians after the point where the groove between the sheaves is narrowest. Driving pulley according to claim 1, 2 or 3 for a bicy¬ cle variator, in which one (2) of the sheaves is axially movable while the other (3) is fixed, c h a r a c ¬ t e r i z e d in that the movable sheave (2) is sup¬ ported by needle bearings (6,7) on the bicycle frame (1) while the fixed sheave (3) is supported on the movable sheave (2) by at least one sliding bearing (9) and on the bicycle frame 1 by a grooved ball bearing (10) with eccentrical mountings (11 , 12) securing its outer ring. V-belt pulley according to claim 7, in which part of the axial force acting between the sheaves (2,3) is produced by a notched cup spring (17), c h a r a c t e r ¬ i z e d in that an eccentric pinpoint force is exerted on the movable sheave (2) by a roller (18) rolling against the rim of the cup spring. Driving pulley according to claim 1 , 2 or 3 for a bicy¬ cle variator, in which the axial force acting between the sheaves (2,3) is produced by means of a multi-end thread (19) and at least one pressure spring (17), c h a r a c t e r i z e d in that an eccentric variable spring force is exerted on the movable sheave (2) by a roller (18) rolling against the rear side of the sheave. 10. V-belt variator with at least one variable pulley as claimed in claim 2, 3 or 4, c h a r a c t e r i z e d in that the divergence of the sheaves is caused by a freely rotating disc (Figs. 5 and 9) or ring (Figs. 6 and 10) wedging radially between a specific auxiliary ring and the rear side of at least one of the sheaves. 11. V-belt variator according to claim 10, c h a r a c ¬ t e r i z e d in that, the rollers adjusting the wedge ring determining the divergence of the sheaves are sym¬ metrically placed and mounted with bearings on levers controlled by the belt tensioning rollers (Fig. 7). 12. V-belt variator according to claim 10, c h a r a c ¬ t e r i z e d in that the action of the mechanism pro¬ ducing the divergence of the sheaves is independent of the direction of the loading torque (Fig. 7).

Inventors: MANTOVAARA URPO, MANTOVAARA, URPO
Applicants: MANTOVAARA URPO, MANTOVAARA, URPO
Application year: 1989
Main classification: F16H55
IPC codes: F16H55