FR2694060A1 - Speed Variator with expandable rotors and cams connected by belt and being hydraulically controlled - includes two rotors of variable diameters connected by belt with hydraulic double effect piston in circuit regulating control hydraulic pressure,this piston connected to independent circuit having pump, rotative distributor and another doub - Google Patents

Abstract

The variator consists of two rotors (Va.1,Va.2) whose diameters can be varied by the displacement of cams mounted round their periphery. They are connected by a flat pulley belt (41). This action is made by a double acting hydraulic jack (cyl.2) which feeds oil to or from the respected rotors in a closed circuit which is controlled by pressure regulators (Reg.1,Reg.2). This jack is connected to a double acting control jack (Cyl.2) which is controlled independently by a rotary distributor (Dist.) from a power source (45,46). A manual lever (32) is used to operate the distributor. Use/Advantage - Use as a variable speed drive in a wide range of vehicular transmissions where the flat belt transmission is an improvement over the conventional vee belt drive.

Description

 The present invention relates to a speed variator with cams, coupled in pairs and driven by a flat belt, as well as its entire hydraulic control system.

 The existing speed variators currently are not very powerful and do not have a large variation in speed at the variator output given their designs.

 The aim of the variator system invented and described below is to considerably improve the difference in rotation at the output of the driven variator, without displacement of the driving or driven shaft and to have greater driving power whatever the variator operating stages, this at low, medium or high engine speeds.

 The variators are controlled using a hydraulic system controlled by an independent manual circuit, and the possibility of automatic control depending on the use requested.

 The power of this variator can be increased by the diameter and the width of the rotor, as well as the diameter and the number of cams.

 Depending on use, the cams can be smooth or notched.

 The control of the closed hydraulic circuit can be done mechanically or electrically depending on the use, industrial or on land vehicles.

 Current variators with V-belts do not have a large drive power and do not provide large variations in speed at the output of the driven shaft relative to the drive shaft, despite all the devices invented to overcome these drawbacks.

 The present invention is made in order to remedy these problems. The design of the present variator being with cams (3) and having a hydraulic thrust on pistons (5), which has the aim of increasing or decreasing the circumference of the present variator, the drive being done by a flat belt (41) , smooth or notched which provides greater drive power, having a greater range of the belt. The cams are balanced between them by 2 regulating washers with oblong holes (4).

 The cylinder (Cyl. 1) being controlled by a rotary distributor (Dist) figure 8 which aims to act on the piston (19) and to maintain the pistons (21 and 19) at any position from the lever (32) of the dispenser released, the dispenser being very simple to build, light in weight and very compact, given the minimum of parts brought to its construction.

 A hydraulic pump (45) with gear or other supplying pressure to the distributor (Dist.) And driven itself by the same force whatever the drive variator (Va. 1).

 The hydraulic pressures of the variators being regulated by two regulators (Reg. 1) and (Reg. 2) figure 8 in order to allow a perfect balancing between the two hydraulic circuits of the two variators and to have a sufficient pressure to avoid a floating and a belt slippage.

 The variator present is coupled with another variator of the same type and driven together by belt figure 31. Both being hydraulically controlled in closed circuit, which allows to increase the circumference of the variator driver (Va. 1) and to decrease the circumference of the driven variator (Va. 2) or vice versa, results in a very large speed variation at the output of the driven variator.

 The simplicity of the present drive brings a very low manufacturing cost and minimal maintenance.

 The set of two variators is controlled by two cylinders with coupled pistons (Cyl. 1 and Cyl. 2) in figure 8 and ordered together but having two independent hydraulic circuits. The two variators (Va. 1 and Va. 2) are controlled by the piston (21) in a closed circuit, the latter itself being controlled by the piston (19) of the master cylinder (Cyl. 1).

The accompanying drawings illustrate the invention
With reference to these drawings, the invention relates to a speed variator device constituted by two expandable cam rotors, connected by belt, hydraulically controlled and each comprising:
A main rotor (1) by which are mounted cams (3) of a belt (41) sliding radially and uniformly guided in their movement by two regulating washers (4) with oblong holes (71) and maintained side by two guide flanges (2), the cams (3) each being actuated by a push piston
(5) guided by a bush (6) for carrying piston seals, tongues (81) ensuring the connection of a neighboring cam to the other, the displacement of the pistons (5) being obtained from a system hydraulic control (Cyl. 1: Cyl. 2: Dist: Reg. 1: Reg. 2) ensuring that oil is sent to one of the rotors and that the oil is returned correspondingly.

 Figure 1 shows an overview of the drive alone from above.

 Figure 2 represents the variator seen in section assembled with all its mechanical and hydraulic parts: main body or rotor (1), external crowns (2), drive cams (3), regulating washers with oblong holes offset from cam thrust (4), cam thrust pistons (5), screwed seals bearing seats (6) hydraulic oil inlet (7), bleed outlet (8). The oil pressure arriving at (7), the pistons (5) are pushed on the cams (3), the cams are balanced at the outlet and re-entered by the balancing washers (4).

 We will see later in the text the following more precise operating system, from plate 8/15 to plate 15/15.

In FIG. 3 is presented the sectional view and the front view in FIG. 4 of the two jacks coupled with double control effects of the two variators.
Body of the control cylinder (17), body of the controlled cylinder (20), bleed outlet of the closed circuit (9), oil pressure outlet and inlet to the variators (10), seals between the two pressure circuits oil (23), outlet and return of oil pressure to the distributor (24), piston control rod (22), piston (19), retaining nuts (12), piston guide (14), seals pistons (15), seals 4es two cylinders (it), seals (25) of the case (18) screwed, sealing gasket; between rod I order and pistons (1wgjt4tpiston (21), the step of fine pitch screw is for fixing the two cylinder bodies (16).

 View of the rotary distributor in two sections and a front view in Figures 5 - 6 and 7 (Plate 3/15).

 The gear lever (32) has a ball (40), a plunger (39) and a return spring (38) in the neutral position. In the current position (section view .B-B. Figure 5), no hydraulic pressure is exerted in the circuit, the variators remain in the position where they were previously controlled.

 The cavity (31) in the distributor body serves for the lever (32) to return to its neutral position, thus the rotor (30) returns to the same position.

 The lever can be an integral part of the rotor (30) or be fixed to the latter by screws or other methods.

 Arrival of the oil pressure (27) and the oil return (26) in neutral position, return (26 bis) of the cylinder in the running position towards the tank, (lever advanced or moved back), oil pressure outlet ( 27) to the control cylinder or oil return from the control cylinder depending on the rotor position.

 Regarding the fixing of the distributor (29) with two holes (28) several variants may be possible as a method of fixing this is depending on the usefulness and the installation of the system, the fixing shown in the sketch is the simplest .

 On the section .A-A. FIG. 7 shows the closure cover (34), as well as the seals (33), bolts passages (35) and leakage return (36) to the tank, the rotor is drilled and tapped (37), in order to receive the bolts (38) with hexagon socket heads. In front view we see the fixing system of the distributor sealing cover.

The seals (33) are a function of the rotating system.

 Figure 8 shows the entire mechanical and hydraulic system. The distributor (Dist.) Is in neutral position, the variator (Va. 1) is in the output cam position and the variator (Va. 2) is in the retracted cam position (sectional view) The cylinder (Cyl. 1) is controlled by the rotary distributor (Dist.). The piston (19) of the cylinder (Cyl.

1) having remained in thrust according to the position in which the lever (32) was previously placed, the piston (21) is likewise pushed by means of the rod (22), following this hydraulic movement the variator cams (Va. 1) are output and variator cams (Va. 2) are retracted, the pressure of two variators being regulated by two regulators (Reg. 1 and Reg. 2) as well as by the voltage of the flat belt 41), two valves (42) with pressure tap (43) being mounted at the regulator outlet and two purges (44) being installed on the two variator circuits and mounted on the body of the receiving cylinder (Cyl. 2 ).

Figure 9 shows the system in operation
The advancement of the lever (32) integral with the rotor (30) thus rotating this same rotor (30) of the distributor (Dist.) The return circuit (26) of neutral position is now closed, the oil pressure circuit going to the piston (19) is open as well as the circuit for retoupv6ssers the tank (46), the pressure pushing the piston (19) and at the same time the piston (21), the oil pressure separating the cams of the variator ( Va. 2) and bringing in the cams of the variator (Va. 1) which causes a reduction in the speed of rotation at the output of the driven variator (Va. 2).

 In Figure 10 the operation is reversed. The thrust of the lever is in the other direction, the distributor is open for a thrust on the piston (19) driving the piston (21) the direct return circuit is closed and the cylinder return circuit open, the cams of the drive variator (Va. 1) move apart and the variator cams (Va. 2) retract, the speed of rotation of the variator (Va. 2) increases, and the speed of the variator driven following its two functions, on figure (9) and (10) is more than doubled.

 The present control system is manual but an automatic system can be mounted on the distributor control which acts according to the engine speed driving the variators (Example: on land vehicle with 3 functions, economical driving, sporty driving or manual driving).

 In FIG. 11 we see in section the mechanical and schematic system of the two vanators driven by a flat and toothed belt with fine pitch.

 Central sections of the variator (Va. 1), retracted cams (3) and central sections of the variator (Va. 2) output cams (3), closed circuit oil line (47), flat belt (41), smooth or notched with very fine pitch depending on use.

 The very fine pitch of the belt is used in order to have a better grip and so that the change of pitch at each operating stage of the variators is done smoothly and smoothly, the little elasticity of the belt making the rest.

 The choice of the belt remains to be defined according to the use and the power requested from the variators.

 FIG. 12 represents a schematic example of the process mounted on a gearbox.

 Cutaway view of the gearbox housing (48), pinion with driving tail (49), intermediate reverse gear (50), driving pinion (51) of the variator (Va. 1), variator driver (Va. 2) gtgnon of the variator (52) driving the output shaft (53), the sliding pinion or synchro (51) controls the neutral and 1st gear, the sliding pinion or synchro (54) controls the reverse gear (Logging 055) the oil and the variator housing (56) being dry, the central bearings (57) being mounted on sealed rings on the variator side. The bearings (58) are lubricated by gearbox pump with internal circuit, the bearings (59) are lubricated by licking as are the bearings (57). Flat belt (41).

 This device allows a change of speed without dead time and better regulation of the engine speed therefore a gain of energy, a gain of power, less fatigue in town, or in a car race, less risk of getting bogged down on the forest or African tracks (zero dead time), less risk of losing grip of the wheels in a turn, more precise power and speed at the wheels, the power and speed will be exactly in the position desired by the driver or driver, either in manual or automatic control.

Another variant of the process:
The gearbox being driven by a torque converter and the reverse gear being a hermetic hydraulic inverter, in this case the gears are removed and more utility of gearbox oil, all gear changes will be done automatically at using the same hydraulic pump and controlled by an electronic system in relation to the engine speed.

 This process would be very useful for vehicles for the disabled.

Sectional view in Figure 13 of the body (1) of the drive following section .AA. in Figure 1. Oil pressure inlet (7), oil pressure regulator outlet (8), housing for cam guides (61), regulating washers with offset oblong holes for cam thrust (3), threads with fine pitch (63) for fixing the seal holder sockets and the passage / cam push pistons
IL3 /
The length of the output shafts is not defined as well as the splines or other used for mounting a pinion or other. At the end of the shaft, the sealing system for the hydraulic oil inlet remains to be defined by the user (Rotating joint, etc.).

 Cross-section view on figure 14 of the variator body (1) according to section .B-B. in figure 1. Body or rotor (1), location of the cams in the retracted position (64) fixing of the piston sealing bushings (63).

 Side view of the rotor (1) of the drive in Figure 15, face of the drive shaft side (65). Drilled and tapped location (66) for the passage of the fixing screws for the 2 outer rings (2) / inner cavity (62) for the passage of the 2 regulating washers with oblong holes (4), cam guide slides (61), oil inlets (7).

 View of an outer ring (2) in Figure 17 and sectional view in Figure 16. Adjustment cavity on the drive body (68), adjustment cavity on the drive shaft (69), location of the screws fixing the crown (70).

 The purpose of the two crowns is to hold the regulating washers of the cams in place, to serve as a slide on the outside of the cams and to guide the belt.

 The fixing can be done by socket head screws tucked into the crown so that they do not protrude, under these conditions a countersink is necessary in the crown at the location of the fixing screws.

 Front view in FIG. 18 and sectional view in FIG. 19 of one of the two regulating washers (4) with offset oblong holes (71) of cam thrust, that is to say arranged in an offset manner in inclination relative to a radial position. Passages (71) allowing the sliding cams fingers to slide, passage of the shaft (72) of the variator body.

 The regulating washers are made of treated steel and pivot in their housing by means of the cams in and out, the utility of this part is to keep the cams in the same position between them at all stages of operation of the variator. They can be mounted on balls, a groove being made on the periphery and inside the passage of the shaft, the balls have a rolling effect and the pivoting will be done without difficulty and without risk of seizing, their diameter and thickness may vary depending on the force and the speed of rotation required from the drive.

 Longitudinal section view (Figure 20) of a U-shaped cam (3) (upside down), with hooking grooves of the fine pitch belt (73), bore (74) of the fingers being housed in the balancing washer with oblong holes (4).

 Bottom view (Figure 21) of a cam (3), cam guides (75) with flat on the outside (76), housing (77) of the cam on the rotor (1) of the drive, the flats of the cam guides serve as a slide along the two balancing washers (4) as well as the two flanges (2).

 Top view (Figure 22) of a cam (3), the fine pitch grooves (73) allowing better adhesion of the flat belt, the holes (78) are used to fix the flexible steel tongue acting as spring and ensuring the connection between one cam and the other.

 Side view (figure 23) of the cam (3) the housing (74) or bore is used to force force or nitrogen the finger (93) (figure 30) in the cam guide, the fine pitch grooves (73) are off-center with respect to the cam guides (3), the holes (78) used for fixing screws or rivets in order to hold in place the cam connecting tongue (81), the housing (79) the tab on the top of the cam is deeper than the slide bearing surface (80), the tongue (81) is fixed on the cam (3) and the tongue of the neighboring cam slides on the bearing surface (80) cam, the tongue fixed on the cam being at the same level externally as the hollow of the grooves or serrations of the cam as well as the neighboring tongue coming to slide on the cam.

 The trapezoidal shape (77) of the underside of the cam (3) being made to match the cavities (64) of the variator rotor in the retracted cam position. The guides of each of the cams (75) are cylindrical with a flat (76). The cam guides can be in hexagonal, square, rectangular or cylindrical shape with flat surface and be attached by fixings on the cam (3) or be an integral part of the same part, this depending on the machining mode and the force required of the variator. , a cylindrical cavity can be made at the location of the piston outlet (5) under the underside of the cam (3) in order to have perfect alignment of the pistons at the outlet.

 The balancing fingers being force-fitted or with nitrogen and a groove can be made on the periphery in order to put balls to have a better sliding in the slides of the regulating washer, grooves can also be made on the guides cams in order to install balls for better sliding of the guides.

 The grooves on the outer periphery of the cam are off-center in order to use a larger sliding surface of the tongue, the holes being on the cam will depend on the placement of a rivet or screw; the radius of the external cam curve will be greater than the retracted cam radius and less than the output cam radius, the exact radius will be the intermediate radius in order to ensure maximum reach of the belt.

 The connecting tab (81) in figures 24 and 25 is presented as a thin steel blade acting as a spring towards the inside in order to provide perfect balance of the belt, the holes (82) are used to fix it on the cam and a recess will be made to prevent any overshoot, a greater thickness will be made on the tongue at the location of attachment to the cam, its outer bearing will be on the neighboring cam by acting as a slide.

 Sectional view (Figure 26) of a seal holder sleeve (6), seal (84) of the cam thrust piston, seal of the sleeve (85), location of the scraper seal (86), notch tightening of the sleeve (87), fine pitch thread (88) corresponding to the threaded cavity on figure 14 and the number of eight on the variator, scraper seal (89) on (figure 27), front view of the sleeve ( 6) (figure 28), passage of the piston (90), cavity of the surface of the scraper seal (91), clamping notches (87).

 The piston seals will depend on the force requested from the drive.

 The diameter, the length and the number of the push pistons (5) (figure 29) will depend on the force requested from the variator and they will be cylindrical. The cam fingers (93) in FIG. 30 are force-fitted or with nitrogen.

 All the main parts of the present invention are made of treated steel. The present variator is non-limiting in size, the current dimensions presented on board 1/15 and on (Figure 1 and 2) being 130 mm, rotor diameter, 142 mm rotor length and 40 mm the diameter of the shaft. , the length of the tree can only be defined according to use.

 Several recesses can be made on the rotor in order to reduce its weight.

 Grooves can be machined along or around the cam guides, in order to position the balls to have a better sliding of the part without risk of seizing.

 Grooves can be machined on the periphery and at the place of the passage of the shaft on the balancing washer of cams with oblong holes in order to position the balls to have a better pivoting of the washer without risk of seizing.

 The grooves on the periphery of the cams can be in the form of a very fine tooth and have the same pitch as the chosen belt, the shape of the teeth or grooves must be studied according to the type of belt to be used.

 Figure 31 shows schematically the entire hydraulically controlled system. The control valve is in neutral position, the variator (Va. 1) is driven by any force (internal combustion engine, electric or other) this same variator driving a second variator (Va. 2) of the same type and same power by a flat belt (41), smooth or notched with very small pitch.

 The two variators being controlled in closed hydraulic circuit using the piston (21), the pressure is regulated by two regulators (Reg. And Reg. 2), the regulators present are with mechanical adjustment, but can be with electric adjustment. Each regulator consists of a piston (94) with seals (95), a pressure spring (96), an adjustment screw (97) with nuts (98) The assembly is sealed by a cover (99). Two purges (44) are mounted on the circuit and two valves (42) are mounted for filling the circuit and the pressure tap (43), two pressure relief valves with valve (One on each circuit) in return for closing the cams can be mounted on the oil circuits between the control piston and the variators, to smoothly regulate the change in speed.

 The assembly is controlled by a rotary distributor (Dist.) With gear lever and by a hydraulic pump (45), (with gear or other), operating the assembly, the piston (19) is integral with the piston (21 , seals (23) are mounted between the two circuits so that no mixture of oil and pressure takes place between the two independent circuits, the two cylinder bodies being integral (17) and (20).

 In the current position of the distributor the latter is in neutral position, the circuit is carried out from the pump to the distributor and from the distributor on the return to the tank (46), the pistons (19) and (21) as well as the two variators remain in the same position to which they had previously been placed by the aid of the distributor (Dist.).

 The system presented from board 1/15 to board 15/15 is particularly intended for the automobile industry, agricultural machinist, public works, machine tools and vehicles for the disabled.

Claims (10)

 1) Variable speed drive device characterized in that it consists of two  variable diameter rotors (Va. 1) and (Va. 2) with variable diameter connected by pistEL44 belt) AND including each  A main rotor (1) by which drive cams (3) are mounted  sliding radially and uniformly guided in their displacement by two  regulating washers (4) with oblong holes (71) and held laterally by two flanges  guide (2), the cams (3) being actuated by guided piston pistons (5) and  watertight, by bearing seals of piston seals (6), of tongues (81) ensuring the  connection of a neighboring cam to the other, the displacement of the pistons (5) being obtained from  a hydraulic control system (Cyl. 1: Cyl. 2: Dist: Reg. 1: Reg. 2) ensuring  sending oil in one of the rotors and returning the oil in the other correspondingly.  2) Device according to claim 1, characterized in that the rotor (1) of the  variator (Va. 1) has a central cylindrical inlet (8), oil outlet (7) passage  and cylindrical passages of pistons (47) for pushing the cams, with their guides (61)  of cams, with two circular locations (62) for the passage of the two washers  regulators (4) with oblong holes allowing perfect regulation of the cams (3) at the outlet  and reentry, threaded passages (63) with fine pitch allowing the fixing of the seals carrier sockets (83) for sealing the pistons (5), threaded holes (66) for the fixing of the two  flanges (2) allowing the maintenance of the two regulating washers (4), {e GUIDE pf A  flat belt (41) smooth or notched with small steps and serve as a slide for the guides  cams (3).  3) Device according to claim 1, characterized in that the cams (3)  have an outer surface comprising grooves (73) or teeth depending on the  belt (41) used, a smooth part (80) serving as a slide and a pierced part  (79) of holes (78), with a smaller radius than the slide part in order to position the  connecting tongue (81), the underside of the cam consists of two guides (75)  cylindrical with flat (76) and bore (74) for the passage of sliding fingers (93)  in the oblong holes of the regulating washer (4).  4) Device according to claims 1 and 3, characterized in that the regulating washers (4) comprise oblong holes (71) decentered arranged in an offset manner in inclination relative to a radial position so that the fingers (93) slide in said oblong holes and maintain the cams (3) in the same position with each other at all stages of operation.  5) Device according to claims 1 and 3, characterized by the tabs (81) of cam connection representing two different thicknesses having holes (82) with recesses for fixing, and act as a spring to remain supported on the cam neighbor.  6) Device according to claim 1, characterized by a drive system mounted on the gearbox housing (48) with a first gear (51) and a reverse gear (54) a set of pinions and shafts (52). 50). (49). (51). (53) (54), mounted on bearings (59). (57). (58), driving a variator (Va. 1) and driving itself by a belt (41 ), a second variator (Va. 2) of the same type driving the output shaft (53) the gear housing (55) is in an oil bath and the variator housing (56) is dry, rings of seals are mounted on the bearings (57) on the drive side.  7) Device according to claim 1, characterized in that the hydraulic control system and consisting of a double-acting cylinder (Cyl. 1) twinned with another double-acting cylinder (Cyl. 2) and fixed together by thread ( 11) and sealed between the two bodies (17) and (20) by seals (23), the two pistons (19) and (21) are secured by a rod (22) and held by two nuts (12), the cylinder (Cyl. 1) is actuated by means of a rotary distributor (Dist.) and the cylinder (Cyl. 2) is actuated by means of cylinder (Cyl. 1), the (Cyl. 2) is in closed circuit to control the two drives.  8) Device according to claim 7, characterized by a rotary distributor (Dist) which comprises a pivoting rotor (30) controlled by a lever (32) and an automatic return system in neutral position (31). (40). 39). (38), oes oil passages (27). (26) and (26 bis) acting as input or output depending on the pivoting of the lever (32), one of the two outputs (27) sends the oil pressure in the cylinder (Cyl. 1) following the pivoting of the rotor (30) and one of the two outlets (27) causes the oil to return to the reservoir (46), this rotary distributor is double-acting.  9) Device according to claims 1 and 7, characterized by two identical regulators (Reg. 1) and (Reg. 2) intended to maintain a constant and defined pressure in the variator circuit (Va. 1) and (Va. 2) , they each consist of a piston (94) with seals, a spring (96), an adjusting screw (97) with a locking nut (98), a cover (99 ) screwed, two valves (42) mounted at the outlet with two pressure taps (43), two purges (44) being mounted on the receiver cylinder (Cyl. 2).  10) Device according to claims 1, 7, 8 and 9, characterized in that the hydraulic system has two independent circuits operates using a hydraulic pump (45) bringing the oil under pressure to the distributor (Dist.) which distributes the oil pressure in the cylinder (Cyl. 1) and at the same time effecting the oil return in the tank (46), the piston (19) acting on the piston (21) sends an oil pressure spreading the cams of the variator radially (Va. 2) and at the same time pushing back the oil from the variator (Va. 1) for retracting the cams, this being done inversely according to the positioning of the lever (32), the tension of the belt (41), acting in the same way, the two regulators (Reg. 1) and (Reg. 2) acting according to the variators in operation and balancing the oil pressures and the tension of the belt (41) at each operating stage of the drives.