HYDROKINETIC ENERGY CONVERTER AND VELOCITY AND TORQUE MULTIPLIER

Abstract: A hydrokinetic energy converter transforms the rotary output of a prime mover into progressively increasing hydrokinetic energy, which is blocked in a closed energy circuit including fluid coupled flywheels. The converter comprises a lighter flywheel (2) mounted to rotate within an in fluid coupled relationship with a heavier flywheel (1). The shaft (7) of the heavier flywheel (1) is suitably connected to the prime mover. The shaft (7) of the heavier flywheel (1) is also coupled to shaft (9) of the lighter flywheel by means of a velocity and torque multiplier (8).

Description: HYDROKINETIC ENERGY CONVERTER AND VELOCITY AND TORQUE MULTIPLIER The present invention refers to a hydrokinetic energy con¬ verter designed to transform the rotary output of a prime mover into continuous and progressively increasing hydro¬ kinetic energy of which the progressive increase in energy may be used to drive a machine, vehicle or the like. The remaining energy may be "blocked" in a closed circuit of energy including two fluid coupled flywheels rotating at different angular velocities. The invention likewise refers to a preferred form of velo¬ city and torque multiplier which may form part of the energy converter mentioned above. Attempts have previously been made to store part of the ex¬ cessive energy of a drive motor in a flywheel from which the energy may be used as necessary instead of requiring addition¬ al energy from the motor. Considerable fuel economy may be obtained in a motor vehicle by storing energy in the flywheel when the vehicle is going downhill and then using part of such energy to assist the motor when the vehicle goes uphill. The object of the present invention is to provide a greatly improved device using flywheels which permits not only even greater fuel economy but also creates great reserves of power with less engine wear and reduction in noice. In princi¬ pal the device of the present invention permits the engine to operate at a substantially constant speed. In accordance with the present invention a hydrokinetic energy converter comprises a first rotary shaft, a first heavier flywheel rotatable withsaid first shaft, a second lighter flywheel adapted to be fluid coupled with said first flywheel, a second rotary shaft rotatable with the second flywheel, a pressurized hydraulic fluid inlet in fluid communication with a space between said flywheel for providing the fluid coupling and a velocity and torque multiplier coupling said first and second rotary shafts. Preferably said first heavier flywheel is coaxial with and encloses therewithin the smaller second flywheel. In one practical arrangement, a motor is connected to drive the first rotary shaft which rotates the first heavier fly- wheel at a given velocity. At the same time the motor is connected to the velocity and torque multiplier whose in¬ creased velocity output drives the second shaft and thus the second lighter flywheel at an angular velocity greater than that of the first flywheel. When the latter has attained the given velocity, pressurised fluid supplied by a pump also driven by the motor is applied to the space between the flywheels to create the fluid coupling which tends to accelerate the first flywheel and decelerate the second. Power may then be taken from one of the shafts or even from the motor shaft itself to drive a load, which, allowing for mechanical losses and the like in the system, may utilize the progressive increase in energy obtained from the velocity and torque multiplier without any reduction in the motor velocity or increase in the fuel consumption or electrical power used to drive the motor. If less than such progres¬ sive increase in energy is being used it is necessary to regu¬ late the pressure of the fluid to increase the slip between the flywheels and thus prevent a progressive increase in the velocity of rotation of the motor. Further in accordance with the invention, a velocity and torque multiplier comprises a rotary input drive means, first and second velocity multiplier arrangements, each said arrange¬ ments comprising: a) first rotor means in driven relationship with said rotary input drive means; b) second rotor means coaxial with said first rotor means and ' having driven output means; c) rotary coupling means between said first and second rotor means, said coupling means having first follower means associated with said first rotor means and second follower means associated with said second rotor means, said coupling means being linearly reciprocable in a direction parallel to the common axis of said rotor means, and said second follower means being inclined with respect to said first follower means based on said direction of reciprocation, whereby reciprocation of said coupling means in a first direction driv- ingly rotates said second rotor means with respect to said first rotor means; and d) free wheel means eliminating any driving relation¬ ship between said input drive means and said second rotor means during reciprocation of said coupling means in a second opposite direction, said free wheel means operating in opposite directions for the two said velocity multiplier arrangements; and transmission means between said rotary input drive means and each said coupling means, said transmission means converting rotary movement of said input drive means to linear reciprocation of ea said coupling means so that, in operation, the torque applied by each said second follower means to each said second rotor means is greater than the torque applied by said rotary input drive means. In the preferred embodiment of the velocity and torque multiplier each first rotor means is a straight toothed gear, each second rotor means is a helical toothed gear and each coupling means comprises a reciprocating floating sleeve surrounding said gears in which each first follower means comprises at least one internal projection on the corresponding sleeve mating with a tooth space in the cor¬ responding straight toothed gear and each second follower means comprises at least one internal projection on the same sleeve mating with a tooth space in the corresponding heli- cal gear. The input drive means preferably comprise a pair of identical meshed gears and each said free wheel means is arranged between corresponding ones of said meshed gears and said straight toothed gears. The transmission means suitably comprises a gear train in¬ cluding a differential gear set, arranged between one of said identical meshed gears and a connecting rod arrangement connected to reciprocate said floating sleeves. It has been found as a result of theoretical calculations and proved in practice that in the case of preferred embodi¬ ment a tooth angle of 309 should be chosen for the helical gears in order to ensure that the theoretical progressive increase in energy in the system under no load conditions ex¬ ceeds the losses provoked by friction, general mechanical losses and slip in the hydraulic coupling between the flywheels. In such preferred embodiment such losses of energy are in the region of 35% of the energy in the system, but, as will be demonstrated later in the specific descrip¬ tion it still results in a progressive increase in overall energy under no load conditions. Such increase may be used by the load and its amount controlled by varying the hydrau¬ lic pressure. In order to permit a better understanding of the invention, a preferred embodiment thereof will now be described, by way of example, with reference to the accompanying drawing, in which: Figure 1 is a longitudinal section along line I - I of » Figure 2, with some parts cut away and others not sectioned, of a hydrokinetic energy converter constructed in accordance with the present invention; Figure 2 is a cross section of the converter of Figure 1 with some parts removed to facilitate comprehension; Figure 3 is a view of the turbine face of one of the fly¬ wheels shown in Figure 1; Figure 4 is a graphic representation of the results obtained with the energy converter shown in Figure 1 to 3; and Figure 5 is a sketch illustrating one application of the energy converter shown in Figures 1 to 3. Referring now to the drawings, an energy converter illus¬ trated in Figures 1 and 2 comprises a pair of flywheels 1 and 2 of which the larger outer flywheel 1 is driven by a motor (not shown) , gear wheels 3, 4 and 5 (Figure 2) , gear 5 being keyed by pins 6 to a sleeve 7 which, in its turn is keyed to flywheel 1. Apart from serving to drive flywheel 1, gear 5 is part of a velocity and torque multiplier generally indicated by reference number 8 and whose output is transmitted to a shaft 9 which passes through sleeve 7 and is keyed to the smaller inner flywheel 2. In order to facilitate understanding o'f the illustrated energy converter, a simplified description of its operation will be given prior to describing the device in greater detail. On starting the drive motor, flywheel 1 is positive¬ ly accelerated by means of gears 3, 4 and 5 and sleeve 7. At the same time the smaller flywheel 2 is positively driven at a greater velocity by means of the same motor, gears 3 and 4, velocity multiplier 8 and shaft 9. When the small flywheel 2 attains a given velocity a hydraulic pump driven by the same motor is permitted to pump oil under pressure to the space between flywheels 1 and 2 to define a fluid coupl¬ ing therebetween. This fluid coupling completes a feedback of energy which is blocked or stored in the system, the torque transmitted by the coupling tending to accelerate flywheel 1 and slow down flywheel 2 which, however, is further accelerated due to the increased speed of flywheel 1 which is amplified by velocity multiplier 8 and then transmitted to flywheel 2. The output of the device may be taken from any suitable point in the system and may even be from the other end of the shaft of the motor that drives (or is driven by) gear 3. Returning now to the device itself, the converter has a main housing 10 having bolted thereto end plates 11 and 12 with respective end caps 13 and 14 bolted thereto. Flywheel 1 is composed of two parts la and lb bolted together by bolts 15 ' and defining therebetween a space which receives inner flywheel 2. Part la of flywheel 1 is journaled to housing 10 by means of conical bearing 16. Inner flywheel 2, in its turn, is journaled within part la of flywheel 1 by bearing 17 which also serves as one end bearing for its shaft 9 the other end of which is journaled in a conical bearing 18 mounted in the other end plate 12. Needle bear¬ ings 19 are also provided between shaft 9 and sleeve 7, this latter also rotating within conical bearing 20. Shaft 9 is provided with an axial oil bore 21 in communica¬ tion at one end with an oil inlet 22 provided in end cap 14 and, at the other end, via radial bores 23 and inclined bores 24 in flywheel 2 with the fluid coupling turbine space or pockets 25 between the two flywheels 1 and 2. Figure 3 shows a view of one of the flywheel turbine faces (the turbine faces of the two flywheels are identical) . As seen from Figure 1, each flywheel is form¬ ed with a circular channel of semicircular cross section. As seen in Figure 3, the channel of each flywheel is provided with twenty-three semi-circular equally angular¬ ly spaced radial oil deflector plates 26 each having a semi-circular cutout 27. These deflector plates are held in position by inner and outer metal rings 28 and 29 riveted to the turbine face of the flywheel. A circular channel 30 of semi-circular cross section is then fitted into cutouts 27 and riveted to the deflector plates 26. Flywheels 1 and 2 with turbine faces as shown in Figure 3 » have been found to provide an excellent fluid coupling therebetween. The velocity multiplier 8 is shown partly in Figure 1 and partly in Figure 2. Gear 5 meshes with similar sized gear 31 so that they are driven in opposite directions by the drive motor (not shown) . Internally of gears 5 and 31 are the stub ends 32 of straight toothed gears 33 and 34, the stub ends 32 being coupled to gears 5 and 31 for rotation in one direction but free for rotation in the opposite direction, these directions being different for the two gears, by means of a free wheel type arrangement employing roller pins 35 (see Figure 2) . Straight toothed gear 33 is freely supported on main shaft 9 by needle bearings 19 and gear 34 is likewise supported on a shaft 36 having one end mounted in housing 10 by means of a conical bearing 37 and its other end mounted in end plate 12 by means of a similar bearing 38. The left hand faces of gears 33 and 34 are separated from gears 5 and 31 by bearing rings 39 and the right hand faces thereof are separated by similar bearing rings 40 from helical gears 41 and 42. These helical gears, however are internally fluted and received on external fluting provided in the corresponding regions of shafts 9 and 36. The right hand ends of shafts 9 and 36 carry meshing identical gears 44 and 45. Each pair of associated straight toothed and helical gears 33, 41 and 34, 42 is surrounded by a reciprocating float¬ ing sleeve 46 or 47, sleeves 46 and 47 being identical whereby only sleeve 47 will be described. As may be seen from Figure 1, sleeve 47 is provided with two groups of in¬ wardly protecting studs. The first group of studs 48 com¬ prises two rings of axially spaced studs whose ends enter the spaces between the straight teeth of gear 34. Conse¬ quently sleeve 47 will rotate together with gear 34 but may reciprocate axially. The second group of studs 49 comprises two rings of studs shifted with respect to each other at an angle corresponding to that of the teeth of helical gear 42. It will be understood from the above description that reci¬ procation of sleeve 47 in one direction will rotate helical gear 42 at an angular velocity exceeding that of straight toothed gear 34 by an amount depending on the angle of the helical teeth but that reciprocation in the other direction will have no effect due to the free wheel arrangement 35 (see Figure 2) . Due to the opposite directions of rotation of gears 5 and 31, reciprocation in such other direction will drive gear 41, whereas reciprocation in said one direction will have no effect. Reciprocation of floating sleeves 46 and 47 is effected by a double collar 50 driven by a pair of connecting rods 51 and 52, only one of which is visible in Figure 1. Double collar 50 is generally in the form of a figure of 8 so as completely to encircle each of sleeves 46 and 47. Coupling between .said collar and each of said sleeves includes two arrows of ball bearings 50' so as to permit rotation of the sleeves relevant to the collar but to permit the collar to transfer the axial reciprocating movement thereto. Rods 51 and 52 are driven by a toothed shaft 54 which is orthogonal to and passes between shafts 9 and 36. The drive arrangement is shown in Figure 2 where it is seen that gear 5 also meshes with a small gear 55, integrally associated with a pinion 56 which drives a crown ge 57. Crown gear 57 is mounted on a shaft together with a gear 5 which in turn drives a gear 59 keyed to connecting rod shaft 54 A counterweight W is provided at the end of shaft 54 to provid dynamic balance in view of the eccentricity of the connecting rod arrangement. Still with reference to Figure 2, it will be seen that gear 4 also drives a gear 60 mounted on a shaft 61 which can be used as an output shaft. Gear 60, in its turn, meshes with gear 62 which may be used to drive the oil pump whose oil outlet will be connected to oil inlet 22 in housing end cap 14 (Figure 1) . The embodiment of the invention that has been des¬ cribed above has been constructed and tested in practice. The relevant physical characteristics and the test results will be given as follows: Drive Motor - DC electric motor having 15 HP rating at 3000 rpm. fed by four 12v. batteries; Flywheel 1 - 85.900 kg; diameter 40 cm; Flywheel 2 - 29.200 kg; diameter 30 cm; Helical gears 41, 42 - tooth angle 309 providing velocity increase of 18%; Oil pump - Pressure 80 psi; Reciprocation stroke of sleeves 46 and 47 - 40 mm (a total of 29.28 cm per revolution) Speed reduction from gear 5 to shaft 54 - 32.61%. On starting up the drive motor, the hydraulic valve of the oil pump is closed so that no oil enters the system and the motor is allowed to run up to 3000 rpm at which time smaller flywheel 2 has a kinetic energy of 577.4 kgm and the larger flywheel 1 has 4204.4 kgm of kinetic energy giving a total of 4781.8 kgm. The hydraulic valve of the oil pump is then actuated and oil at 80 psi enters oil inlet 22, passes along axial bore 21 and radial bores 23 in shaft 9 and inclined bores 24 in flywheel 2 to fill the turbine pockets 25 from where it fills all gaps between the flywheels, bathes the bearings 16, 17, 18, 20, 37 and 38 and the needle bearings 19 and is generally spread throughout the mechanism to ensure permanent lubrication. The 4204.4 kgm of kinetic energy in flywheel i is equi¬ valent to 101,924.8 kgf. and is transferred through the free wheel type coupling 34 with 64.189.3 kgf to the crown and pinion arrangement 55, 56, there being a velocity reduction between sleeve 7 (or gear 5) and shaft 54 of 32.61% (from 3000 rpm to 2021.6 rpm) which increases the torque to 85,121.4 kgf. This torque is increased to 155,980 kgf. on being transferred via correcting rods 51 and 52 to the double collar 50. This is transferred to the helical gears 41 and 42 which increase the output velocity by 18% over the original 3000 rpm, i.e. to 3540 rpm. The velocity multiplier is operating at 3600 im¬ pulses per minute. At this stage, the smaller flywheel 2 now has 577.4 kgm (13,997.5 kgf) due to its mass relating at 3000 rpm plus 155.980 kgf resulting from the energy entered in the double collar 50, giving a total of 169,977.5 kgf at 3,540 rpm. A loss of energy of 35% as a result of mechanical resistance and resistance to accele¬ ration of the flywheels leaves 110,485.38 kgf which is transferred to the larger flywheel 1 due to the oil coupl¬ ing. Flywheel 1 then accelerates by 12% with respect to its original 3000 rpm forming an enormous fluid coupled, closed circuit store of hydrokinetic energy having a stored power of 121,693 kgf at 3,360 rpm or 5,019.96 kgm ? 76 = 66 HP. As operation continues, energy continues to be absorbed progressively by flywheel 2 from flywheel 1 and vice versa with a 16% increase in the stored energy, due to the reci¬ procating movement of the floating collar and sleeves which transfer the energy with 4% slip loss from one fly¬ wheel to the other in less than 0.08 second. Of the 5,019.56 kgm (66 HP) of energy blocked and stored in the system in this extremely short time, the progressive 16% (10.56 HP) may be used to drive a vehicle with a reserve of 66 HP at 3,360 rpm, 250 HP at 6,000 rpm, 1,006 HP at 12,000 rpm and 4,000 HP at 24,000 rpm. * This reserve may be used in moments of necessity or urgency to provide high acceleration. Figure 4 gives a graphic representation of these results. Figure 5 is a sketch showing an application of the energy converter illustrated in Figures 1 to 3 to a motor car. Thus the car 63 has a 15 HP electric motor 64 whose output shaft has one end in driving relationship with gear 3 (Figure 2) of the converter 65 and has its other end connec¬ ted directly to the clutch 66 following which these may be a conventional gearbox 67, cardan shaft 68 and rear wheel drive transmission 69. An oil pump provided with a pressure control valve is driven by gear 62 (Figure 2 ) and the velocity of the car may be controlled by means of such valve, in such a way that motor 64 rotates continuously at a general¬ ly constant velocity. It should be observed that device 8 is not only a velocity but also a torque multiplier. In the embodiment illustrated in Figures 1 and 2, the torque increase is obtained in the driving mechanism of connecting rods 51 and 52 where, as mentioned above, there is a velocity reduction between gear 5 and connecting rod shaft 54 which obviously results in an increase in the torque applied by the reciprocating movement of collars 46 and 47. Due to this torque increase, the device 8 increases both velocity and torque, whereby it is possible to obtain the incremental energy increase in the system, at 16% in the specific embodiment described, in which the tooth angle of helical gears 41 and 42 is 309. Naturally, any other type of multiplier could be used provided that multiplication of both velocity and torque be obtained. Although the invention has been described with respect to only one specific embodiment, it will be appreciated that many variations and alterations may be made provided that they do not go beyond the scope of the following claims.

Claims: CLAIM; 1. Hydrokinetic energy converter, characterized by comprising: a) a first rotary shaft (7) ; b) a first flywheel (1) rotatable with said first rotary shaft (7) ; c) a second flywheel (2 ) having a weight less than that of said first flywheel (1) , said first and second flywheels being adapted to be in fluid coupled re¬ lationship; ) a second rotary shaft (9) rotatable with said second flywheel (2) ; e) a pressurized hydraulic fluid inlet (22) in fluid communication with a space (25) between said first and second flywheels for providing said fluid coupled relationship; and f) a velocity and torque multiplier (8) coupling said first rotary shaft (7) to said second rotary shaft (9). 2. Hydrokinetic energy converter according to claim 1 characterized in that said second lighter flywheel (2) is enclosed coaxially within said first flywheel (1) and said first rotary shaft comprises a sleeve (7) mount¬ ing said first flywheel (1) and said second rotary shaft (9) passes coaxially through said sleeve (7) and has one end mounting said second flywheel (2) . 3. Hydrokinetic energy converter according to claim 2 characterized in that said fluid inlet (22) is in con¬ nection with an axial bore (21) along said second shaft (9) , said bore being in communication with fluid channels (23, 24) leading through said second flywheel (2) to said space (25) . 4. Hydrokinetic energy converter according to any one of claims 1, 2 or 3, characterized in that said velocity and torque multiplier (8) comprises a rotary input drive means (5, 31) , first and second velocity multiplier arrangements, each said arrangement comprising: a) first rotor means (33; 34) in driven relationship with said rotary input drive means (5; 31) ; b) second rotor means (41; 42) coaxial with said first rotor means (33;34) and having driven output means (9;36); c) rotary coupling means (46;47) between said first and second rotor means, said coupling means having first follower means (48) associated with said first rotor means and second follower means (49) associated with said second rotor means , said coupling means being linearly reciprocable in a direction parallel to the common axis of said rotor means, and said second followe means being inclined with respect to said first follower means based on said direction of reciprocation, whereby reciprocation of said coupling means (46; 47) in a first direction drivingly rotates said second rotor means (41;42) with respect to said first rotor means (33;34); and d) free wheel means (35) eliminating any driving re¬ lationship between said input drive means (5;31) and said second rotor means (41;42) during reciprocation of said coupling means in a second opposite direction, said free wheel means (35) operating in opposite directions for the two said velocity multiplier arrange ments; and transmission means (51,52,54,55,56,57,58,59) between said rotary input drive means (5;31) and said coupling means, said transmission means converting rotary movement of said input drive means to linear reciprocation of said coupling means (46;47) so that, in operation, the torque applied by each said second follower means (49) to each said second rotor means (41;42) is greater than the torque applied by said rotor input drive means (5;31). 5. Hydrokinetic energy converter according to claim 4, characterized in that each said first rotor means is a helical toothed gear (41;42) and each said coupling means comprises a reciprocating floating sleeve (46,47) surround¬ ing said gears of the corresponding arrangement, in which each first follower means comprises at least one internal projection (48) on the corresponding sleeve mating with a tooth space on the corresponding straight toothed gear and each said second follower means comprises at least one internal projection (49) on the same sleeve mating with a tooth space in the corresponding helical gear. 6. Hydrokinetic energy converter according to claim 5 charac¬ terized in that said input drive means comprises a pair of identical meshed gears (5,31) each associated with a respective one of said velocity multiplier arrangements and in that each said free wheel means (35) is arranged between corresponding ones of said meshed gears (5, 31) and said straight toothed gears (33,34) . 7. Hydrokinetic energy converter according to claim 6 charac¬ terized in that said transmission means comprises a gear crown (55,56,58,59) including a differential gear set (56,57) arranged between one (5) of said identical meshed gears and a connecting rod arrangement (51,52,54) connected to reciprocate said ' floating sleeves (46,47). 8. Hydrokinetic energy converter according to claim 7, charac¬ terized in that said connecting rod arrangement comprises a pair of parallel connecting rods (51,52) mounted on a shaft (54) on either side of said velocity multiplier arrangements, said connecting rods (51,52) having corres¬ ponding actuating ends carrying therebetween a collar (50) encircling said two floating sleeves (46,47) and coupled thereto in a manner to permit relative rotation of said sleeves with respect to said collar (50) but to transmit movement therebetween in the direction of their axes. 9. Hydrokinetic energy converter according to claim 8 charac¬ terized in that said collar is a double collar similar to a figure 8 so as completely to encircle each of said sleeves (46,47) . 10. Velocity and torque multiplier characterized by com¬ prising a rotary input drive means (5,31), first and second velocity multiplier arrangements, each said arrangement comprising: a) first rotor means (33;34) in driven relationship with said rotary input drive means (5;31); b) second rotor means (41;42) coaxial with said first rotor means (33;34) and having driving output means (9;36); c) rotary coupling means (46;47) between said first and second rotor means, said coupling means having first follower means (48) associated with said first rotor means and second follower means (49) associated with said second r.otor means, said coupling means being linearly reciprocable in a direction parallel to the common axis of said rotor means, and said second follower means being inclined with respect to said first follower means based on said direction of reci¬ procation, whereby reciprocation of said coupling means (46;47) in a first direction drivingly rotates said second rotor means (41;42) with respect to said first rotor means (33;34); and d) free wheel means (35) eliminating any driving relation ship between said input drive means (5;31) and said second rotor means (41;42) during reciprocation of said coupling means in a second opposite direction, said free wheel means (35) operating in opposite directions for the two said velocity multiplier arrangements; and transmission means (51,52,54,55,56,57,58,59) between said rotary input drive means (5;31) and said coupling means, said transmission means converting rotary movement of said input drive means to linear reciprocation of said coupling means (46;47) so that, in operation, the torque applied by each said second follower means (49) to each said second rotor means (41;42) is greater than the torque applied by said rotary input drive means (5;31) . 11. Velocity and torque multiplier according to claim 10, characterized in that each said first rotor means is a helical toothed gear (41;42) and each said coupling means comprises a reciprocating floating sleeve (46,47) surround¬ ing, -said gears of the corresponding arrangement, in which each first follower means comprises at least one internal projection (48) on the corresponding sleeve mating with a tooth space on the corresponding straight toothed gear and each said second follower means comprises at least one internal projection (49) on the same sleeve mating with a tooth space in the corresponding helical gear. 12. Velocity and torque multiplier according to claim 11, characterized in that said input drive means comprises a pair of identical meshed gears (5,31) each associated with a respective one of said velocity multiplier arrangements and in that each said free wheel means (35) is arranged between corresponding ones of said meshed gears (5,31) and said straight toothed gears (33,34). 13. Velocity and torque multiplier according to claim 12, characterized in that said transmission means com¬ prises a gear crown (55,56,58,59) including a differ¬ ential gear set (56,57) arranged between one (5) of said identical meshed gears and a connecting rod arrangement (51,52,54) connected to reciprocate said floating sleeves (46,47). 14. Velocity and torque multiplier according to claim 13, characterized in that said connecting rod arrangment comprises a pair of parallel connecting rods (51,52) mounted on a shaft (54) on either side of said velocity multiplier arrangements, said connecting rods (51,52) having corresponding actuating ends carrying therebetween a collar (50) encircling said two floating sleeves (46,47) and coupled thereto in a manner to permit relative rota¬ tion of said sleeves with respect to said collar (50) but to transmit movement therebetween in the direction of their axes. 15. Velocity and torque multiplier according to claim 14, characterized in that said collar is a double collar similar to a figure 8 so as completely to encircle each of said sleeves (46,47).

Inventors: SILVA SIMOES ADELINO DA, SILVA SIMOES, ADELINO DA
Applicants: GUIMARAES MOURAO OTO, SILVA SIMOES ADELINO DA, GUIMARAES MOURAO, OTO, SILVA SIMOES, ADELINO DA
Application year: 1986
Main classification: B60R9
IPC codes: B60K6, B60K8, F02B29, F02B61