WO1980001596A1 - Gear train with compensated action - Google Patents

Abstract

A gear train with compensated action is provided with a direct self repartition on the resistant work axis (O', O) according to two opposed resultants, so as to counterbalance the leading member in order to reduce the resistance opposed by the work to the motor without the reverse being so. It is characterized in that the mechanical energy acts according a second mode of operation, indirect, compatible with the displacements in application according to the first mode of operation due to the freedom of motion, in virtual or effective rotation, that is provided to the satellite member on its axis (6', 6). The invention applies to compensate any resistant work: whether it be the reaction of a dynamo, a blowing machine, a centrifugal machine coupled to the device, the inertia (in the driving or braking mode) of a body in motion, the weight of an elevator cabin, since it is not limited in practice, by a mass, a cable, a bearing point like in a counterload device.

Description

GEAR TRAIN

The present invention relates to a gear train device, intended in particular to supplement the use of counter-load devices, hoists, winches, by the advantages which the device according to the invention brings, and allowing in besides doing without various torque adapters such as reducer, reduction gear, speed variator.

The proposed device makes it possible to obtain partial compensation for the reaction of the resistant work by distributing it on either side of the tax of a driving gear therefore on the motor shaft of the device. The device thus assists part of the motor work as one does. counter-charge device. In use and without being modified, the device can still be used as an engine brake by simply acting on the direction of engine rotation.

Winch or reducer devices are limited in their application to optimally adapt the effort of motor work to that of resistant work.

The counter-load system makes it possible to reduce the effort of motor work by compensating for the reaction of useful work by the opposite work of a mass. However, as the mass is evaluated according to a predetermined useful work, the compensation is for use only approximate hence the need to provide an engine which can produce a significant torque. In principle, this system is still doubly limited in its applications by a travel imposed by the length of the cable and by the need to have a lift point external to the system.

The device according to the invention makes it possible to avoid these drawbacks. The device has, compared to a counter-load system, the advantage of not being limited by the place of use or by any movement, which allows the extension of the possible uses of the device to prohibited areas â a counter-charge system. It is possible with this device to partially compensate for the reaction of any useful work and thus reduce the value of motor work accordingly. The placing in series of several of these devices makes it possible to reduce the share of engine work in large proportions and at the same time allows the need to dispense with torque adapters of the reducer, reduction gear, speed variator and other types mentioned above. In addition, the compensation factor is almost constant (it varies according to the value of the resistive torque), which makes it possible to precisely assess the necessary torque of the motor to be used for each use and to calculate it non-oversized. Another object of the invention is to provide a device which makes it possible to assist part of the motor force or to be assimilated to a motor brake mechanism, depending on whether the action exerted on the leading point of the device is negative or possitive, and this at will, control of the leading point is always possible by the direction of rotation of the motor shaft. The device according to the invention comprises a driving gear rotating around a first axis and in engagement with two gears each ensuring the drive of a planetary gear of which it is secured by a common shaft, the two common shafts being aligned on the same second axis perpendicular to said first axis and the two drive gears being diametrically opposite with respect to the driving member, at least one satellite gear being engaged both with each of the planetary gears and driving in rotation a member driven around of said second axis.

In one embodiment, this device is characterized in that the planetary gears are engaged with a satel-lite gear with double toothing of axis perpendicular to the second axis and mounted in a casing containing this satellite and the planetary.

This casing can be rotatably mounted around the second axis and is then secured to the driven member, or it can be fixed, a crankshaft secured to the driven member ensuring the rotation of the satellite.

In another embodiment, the device according to the invention is characterized in that the planetary gears are substantially coplanar, the second being a ring with internal toothing.

The characteristics of the invention will moreover be better explained by the following description, given only by way of example, with reference to the accompanying drawings, of which Figures 1 and 2 schematically illustrate two embodiments of the device according to the invention.

The device which is the subject of the invention in the embodiment of Figure 1 comprises a differential, the satellite member of which is a pair of gears 4 'and 4 of different radius, centered in 6', 6. Gears 5 and 6 mesh respectively with 4 'and 4. A driving gear 8 is in relation to the gears 5, 6, by means of two gears 7', 7, or any other connecting means. The drive unit (not shown) is at 11. The housing 3 drives, via a crown 2, the transmission gear 1. The structure elements and the bearings are represented by 9, the bearings and stops are represented by 10.

The motor and transmission inputs are reversed for the assembly considered compared to the conventional use of the differential.

This device does not replace the differential, it cannot compensate for the difference in resistance of the wheels of a vehicle during a turn. We will first consider rotations due to TR work (reaction of useful work) directly or indirectly active.

By way of example, reference is made to the device of FIG. 1, in which the various elements have the following characteristics:

1 ... .. Training weight 500g

2 ... .. Pulley 0 100 mm

3 ... .. Differential housing

4 ', 4 ... .. Couple of satellites 0 35 mm and 70 mm 5, 6 ..... Output gears 0 70 mm

7 ', 7, 8 ... .. Gears 0 140 mm

9 ... .. Frame

10 ... . . Bearings and thrust bearings

11 .. ... Training weight 250 g. We see that the ratio of the satellite 4 'is worth two rays of 4, that of 5 and 5 is worth two rays of 4, that of 7' and 7, four rays of 4, finally, the ratio of the leading gear 8 is four rays of 4. The satellite pair 4 ', 4 is in free rotation according to Tax 6', 5 and in effective rotation according to Tax 0 ', 0. If we had the same radius on each side of the Tax of a single satellite, the moment of 4 'out of 5 would exactly compensate the moment of 4 out of 6 on Tengrenage 8, but then it would be impossible to obtain a useful displacement of said satellite according to Tax 0 ', 0 from the actual motor rotation on Tengrenage 8, the satellite can only be rotated on itself (free rotation according to Tax 6', 6). This is why it is essential that a couple of satellites of different radius be included in the differential. In this example, we have on Tengrenage 6 a work double that received by Tengrenage 5 if a work is carried out on Tax 6 ', 5 of the couple of satellites since the radius of satellite 4' is half that of 4. The torque of Tengrenage 5 and Tengrenage 5 is fully transferred to Tengrenage 8 via the gears 7 'and 7.

We obtain schematically on Tengrenage 8 the equivalent of a double lever, focused on T motor shaft, where they oppose each other according to a compensation of 50% the above moments, since their actions are opposite on both sides of l 'engine shaft. Indeed, the rotations of the couple of satellites 4 ', 4 being free on 6', 6, the rotation on Tax 6 ', 6 is impossible if the state of equilibrium is verified, it follows that the couple of satellites is only rotated during active TR work until on Tax 0 ', 0. On the other hand, the pair of satellites receives from 5 and 6 reactive work which is opposed to it. There is 2F on 4 when there is F on 4 ', the force displacement equivalence principle makes it possible to verify that the couple of satellites is in equilibrium on Tax 6', 5, taking into account the fact that the radius of 4 'is double that of 4. This concerns the self-balance property of the couple of satellites 4', 4 on their axis 6 ', 6, and we will see later that it is not modified during rotation device motor. To demonstrate the properties of the device as simply as possible, it is advantageous to start from the hypothesis that a defined TR work (for example that of a load on a keyed pulley on the transmission shaft) represents the basis of the calculations; it is enough to know its active resultant on the motor shaft of the device to assess the value of the compensation. This remains valid whether or not there is actual engine work on the engine stamp. It should also be specified that the initial work TR applied in transmission can be considered as an active force that said work actively or passively opposes motor work. This allows with a single calculation to consider the possible hypotheses in practice and always know the value of this compensation. The results are not modified during rotation due to Tisotropy of the device.

For a better demonstration, we take an example in which we double the terms F. L. not. to make multiplication effective. Calculation of the compensation that Ton obtains on the driving gear 8 from an effective work TR on the transmission gear - For example, the reaction of a useful work of 48 MT, distributed on the satellites 4 'and 4 according to:

4 'out of 5: F. 2L. n, or 2F. 4L. 2n = 16 MT 4 of 6: 2F. 2L. n, i.e. 4F .4L. 2n = 32 MT When the actual TU work on Tax 6 ', 6 of the pair of satellites is: (F + 2F). 2L. n, i.e. 6F .4L. 2n = 48 MT Verification: total moment of forces on 5 and 6:

32 MT + 16 MT = 48 MT MT after compensation on Tengrenage 8:

32 MT - 16 MT = 16 MT The initial work ratio is one third of the actual work, since:

48/16 = 3. This result is expressed as a ratio. To know the balance of forces on this system, it is necessary to verify that a motor work, TM, effective on Tengreneur leader 8, produces a work in transmission in identical does not exercise the same moment depending on whether it is applied to the leading point or to the led point. Indeed we have seen that the reaction of any useful work produces 2 resultants which act simultaneously on both sides of the satellite organ and consequently, on both sides of the motor shaft which is thus in a state of partial dynamic equilibrium. An equivalent work, is no longer transmitted except by an output if it is active from the leading point via 1 planetary, since it brings into rσtation T organ driven by means of the difference in ratio which exists between these 2 outputs. Thus the work of the leading Tarbre is fully transmitted to the driven point of the device. But this does not question the above. The work on the point carried out acts independently of that exerted on the leading point, in particular by leaving free in rotation, on Tax 6 ', 6, T satellite organ, at least with regard to the virtual displacements. It is this property which is taken advantage of and this is what makes it possible to separate the 2 operating modes into 2 parts.

2nd operating mode: calculation of the successive conversions of the total moment (MT) of a work, TM, of 48 MT, effective on Tengrenage driving 8: 1,5F. 4L. n, or 3F. 8L. 2n = 48 MT, (once the terms are doubled). In 8 out of 7, we have:

*Ce calcul posé permet d'éliminer les rotations de 7' et les rotations non effectives de 7; en effet, en raison de la différence de diamètre des satellites 4 'et 4, le satellite 4' fait un tour quand le satellite 4 fait deux tours. Si Ton retranche mentalement la rotation de 4' à celles de 4, Tengrenage 7' peut être considéré cornue fixe. Il est ainsi possible de simplifier les calculs. Chaque rotation de Tengrenage 8 entraîne une demirotation active de Tengrenage 7. Le moment exercé sur 6 est de: 3F . 2L . (0,5n), soit 6F . 4L . n = 24 MT.1.5F. 4L. or 3F. 8L. n = 24 MT.

* This calculation made it possible to eliminate the rotations of 7 'and the non-effective rotations of 7; in fact, due to the difference in diameter of the satellites 4 'and 4, the satellite 4' makes one turn when the satellite 4 makes two turns. If you mentally subtract the rotation from 4 'to those of 4, Tengrenage 7' can be considered fixed retort. It is thus possible to simplify the calculations. Each rotation of Tengrenage 8 results in an active demirotation of Tengrenage 7. The moment exerted on 6 is: 3F. 2L. (0.5n), i.e. 6F. 4L. n = 24 MT.

The ineffective moment in transmission, exerted on satellite 4, according to Tax 6 ', 6, is: 3F. L. n (0.5n. 2), that is: 6F. 2L. 2n = 24 MT.

On Tax 6 ', 6 of the couple of satellites according to the active rotation on Tax 0', 0, we have the work of 6 on 4 + the reaction work of 5 on 4 ':

With this in mind, it is possible to envisage a more compact version of the device, as shown in FIG. 2. This variant consists in aligning the gears 5 and 6 with a single satellite 4.

The gears 4 and 5 can have a straight toothing, Tun being an inner toothed crown 6. The satellite 4 is driven indirectly, the motor rotation of the device, by the difference in diameter of the pinion of the crown. The respective radius of the gears 4, 5 and 6 of this example being 1, 1 and 3, the crown drives the satellite according to Tax 6 ', 6 over three turns when the pinion 5 only drives it over one turn. The pinion 5 can be considered as fixed when one mentally subtracts the rotation from 5 to that of 6. The satellite is then usefully driven on Tax 0 ', 0 according to 2/3 of the useful travel of the crown.

Useful work TU directly drives the satellite, therefore gears 5 and 6, according to Tax 0 ', 0. The work TU is therefore divided into 6 according to: F. 3L. n, the doubled terms give: 2F. 6L. 2n = 24 MT. When it is divided into 5 according to:

F. L. n, or 2F. 2L. 2n = 8 MT.

For useful work of:

2 F . 2L. n is 4F. 4L. 2n = 32 MT.

The distribution on Tengrenage 8 is therefore: (24 - 8) = 16 MT.

Or a MT report leading from 1 to 2 since:

32/16 = 2. The embodiments described and shown, in particular, may include the following modifications: a dynamo can be connected to the driven point, and supply Ténérgie at the point leading to an electric motor. The MT leading / led ratio is then 1 if we take the last example, or 1 to 2 if we take the previous example. If several of these devices are connected in series, the MT ratio of the resistant work is divided by the ratio of the following device. The output of Tun of the gears (5 or 6) can be reversed. For example, Tax of the pinion 5 can pass through the crown 6, in particular if the crown is kept in rotation by an external bearing. Finally, all modifications relating to the ratios of the various gears of the device remain within the scope of this invention. For mechanical reasons, the addition of one or more satellites symmetrically arranged with respect to that of the examples described is preferable for the distribution of the forces. Similarly, to reduce static stresses, can use nylon gears and insert a semi-elastic material between the bearing and the bearing. The transmission member 2 and 1 can be any. Using the above, we can consider a 3rd version, shown schematically in Figure 3, whose originality comes from the means used to obtain the useful movement of the driven member from a motor rotation. This means, which can moreover be used in conjunction with those of Texmple 1 or of Example 2, consists in taking advantage of the difference in ratio between one of the outputs with the drive gear and possibly, the planetary gear of the other. output (2nd operating mode). This version is characterized in that the planetary gear and the drive gear are, for each of the outputs, equidistant respectively with respect to the tax of the satellite organ and of the leading shaft, with for each output a different ratio and in that the the driving member is composed of two tuned gears Tun behind the other (at a distance "D" equal to the difference in ratio of the two outputs). This arrangement makes it possible to distribute equitably over each of the outputs the reaction of any useful work exerted on the satellite member, according to rotation tax 0 ′, 0, and consequently, makes it possible to compensate equitably on the driving member of the dispos sitive, this work in two resultants opposite in force and in displacement, (1st mode of operation). This result is obtained from the fact that, by definition, the satellite organ and the leading organ meshing at equal distance from their respective axis on said gears and despite the fact that, for our example, Tengrenage 7 is equal to 2 radii of 7 ', it receives of the satellite (and opposes it by reaction) a work equivalent to that received on Tengrenage 7 '. Likewise, the leading gear receives, via the 2 outputs, 2 opposite resultants of any TR work, equivalent to each other since Taxe de Tengrenage 8 is equidistant from the gears 7 'and 7.

The satellite gear 4 is therefore in equilibrium, which does not mean that the work of 7 'is distributed like that of 7, in fact we have:

F. L. 2n out of 7 'when we have F. 2L. n out of 7. The work of 7 'is subtracted from that of 7 on Torgane leading, Torgane leading is in equilibrium which assumes that "n" is virtual. The compatibility of movement with the second operating mode being ensured by the freedom of rotation available to the satellite on Tax 6 ', 6, (differential effect). It is however possible to have an intermediate version with any of the previous versions. The larger of the 2 planets, so as not to come into contact with the first of the 2 driving Torgane gears, may have a recess. Each of the driving gears, in rotation on the first axis, is in engagement with the drive gear of each output, as it was said previously, or, according to a variant (not shown), a single driving gear is disposed at an angle such that it engages both the drive gear of the respective planetai of each output.

A version (not drawn), directly inspired by the initial version can still be considered; it consists in transposing the double gear from Torgane satellite to Torgane leading. It is characterized in that the driving shaft, in rotation on the first axis, is integral with a corner gear with double teeth, as an indication of radius R and R / 2, engaged as above with the gears 7 ', 7. Consequently, it appears that each version is characterized by a double operating mode; an effective work of the led point being active at the same time on the two planets, while an effective work of Torgane carrying out Test, via a single planetary, leaving in both cases Torgane free satellite in virtual rotation, which is the necessary condition to obtain the self-distribution of a resistant work on the two planets and consequently, a self-compensation of this work on both sides of T, driving tree - so as to reduce the resistance that this work opposes the engine - while obtaining, in use, a unitary transmission of useful work, via the active rotation of a single sun gear, causing the indirect rotation of the satellite body. Hence the need to provide a difference in ratio of one or more gears, according to said variations, or alternatively, according to a partial implementation of one or more of said means used jointly.

Whatever its embodiment, the device is still characterized by its application which is to compensate for active or passive resistant work, whether it is due to the reaction of a dynamo, a blower, a centrifuge coupled to the device, inertia when driving or braking a mobile, to the weight of an elevator car; by distributing said resistant work on either side of Tarbre leading along 2 opposite resultants, with a view to producing useful work with minimum motor work, like a counter-load device, without it having autonomy limited by the travel of a cable, a mass, a fulcrum dependent on the system.

In the spirit of the invention, it can also be annexed to the shaft leading from the device to different braking systems taking advantage of friction, viscosity or any magnetic process such as that of reversing the polarity of an electric motor or passively use this engine, power off.

Of course, the invention is in no way limited to the embodiments tion described and shown which have been given only by way of example.

In particular, it is susceptible to numerous variants accessible to those skilled in the art and includes all the means constituting technical equivalents of the means described, used in this context and in the context of the claims which follow.

Claims

1. - Gear train device comprising at least one driving gear rotating around a first axis and in engagement with two gears each ensuring the drive of a planetary gear of which it is integral by a common axis, the two shafts common being aligned on the same second axis perpendicular to said first axis and the two drive gears being diametrically opposite with respect to the driving gear, at least one satellite gear being engaged at the same time with each of the planetary gears and driving in rotation a member carried out around the second axis, characterized, in the integrity of a version, in that the resistant work, effective from the point carried out, acts according to a 1st mode of operation while a motor work, effective from the leading Torgan, acts according to a second operating mode. 2. - Means according to claim 1, characterized in that the planetary ges are engaged with a satellite gear with double teeth as an indication of radius R / 2 and R / 4, axis perpendicular to the second axis and mounted in a housing containing this satellite and the planets. 3. - Device according to claim 2, characterized in that the housing is rotatably mounted about the second axis, driving the Torgane satellite driven. This contributes, in the integrity of a version, in that an effective work of the point carried out is active at the same time on the 2 planets, while an effective work of Torgane conducting Test via a single planetary, leaving in the 2 cases Torgane free satellite in virtual rotation, which is the necessary condition for T self-distribution of the resistant work on the 2 planetary ones and consequently, on T driving shaft. 4. - Or, according to claim 2, characterized in that the casing is fixed, a crankshaft integral with the driven Torgane ensuring the rotation of the satellite. 5. - Means 2 according to claim 1 and according to any of claims 3 or 4, characterized in. that the planetary gears are substantially coplanar, the second being an inner gear ring By way of indication, the respective radii of the gears of the satellite, of the first planet and of the second planet are in the ratios 1, 1 and 3. This contributes like the claims 2, 6, 7 or according to a partial implementation of one or more of said means used together, to obtain in use the unitary transmission of useful work via the active rotation of a single sun gear causing that, indirect, of the satellite body. 6. - means 3 according to claim 1, according to any one of claims 3 or 4, characterized in that the planetary gear and the drive gear are, for each of the outputs, respectively equidistant from the tax of the satellite torgan and the leading shaft. , with a different ratio for each output, and in that the driving Torgan is composed of two keyed gears Tun behind the other on the shaft leading to a distance D, equal to the difference in ratio of the drive gears of the respective planetary of each output. 7. - Or, according to claims 1 and 6, a single driving gear is arranged at an angle such that it is engaged both with the drive gear of the respective planet of each output. 8. - Means 4 according to claim 1, according to any one of claims 3 or 4, characterized in that the leading shaft, in rotation on the first axis, is integral with a double-angle angle gear, as an indication of radius R and R / 2, engaged as before with the drive gears. 9. - The device according to claim 1 is characterized, in the integrity of a version, by its mode of operation and by its application; the implementation of the fundamental elements cited, makes it possible to compensate for the resistant work by opposing this work on either side of Tarbre leading so as to reduce the resistance as much as this work opposes the engine. From which it follows that the device has the application of compensating for active or passive resistant work, whether it is due to the reaction of a dynamo, a blower, a centrifuge coupled to the device, with T inertia at driving or braking a mobile, the weight of an elevator car; by distributing said resistant work on either side of Tarbre leading along 2 opposite resultants, with a view to producing useful work with minimum motor work, like a counter-load device, without this having a autonomy limited by the movement of a cable, a mass, a fulcrum depending on the system. 10. - Device according to claim 1, characterized, according to 9, in that Tarbre leading can be provided with one or more braking system (s) taking advantage of friction, viscosity or any magnetic process such as that consisting to reverse the polarity of an electric motor or to passively use this motor, power cut.