MXPA99001795A - Step-down gear unit - Google Patents

Abstract

The invention concerns a step-down gear unit with a rigid support ring (1), comprising a substantially cylindrical support surface (1), and with a radially flexible rolling collet (5) which has an outer generated surface (7) with a smaller peripheral length than the support surface (2), one or a plurality of peripheral sections of the outer generated surface (7) being held in substantially slip-free engagement in continuous exchange with the support surface (2) of the support ring (1) by one or a plurality of parts lying on an enveloping circle of a drive core (20) which is rotatably disposed inside the rolling collet (5) and is rotated by a drive shaft (14). The enveloping circle (20) of the driven elliptical drive core (20) has a substantially smaller diameter (Dh) than the basically cylindrical rolling collet (5). The rolling collet (5) is supported on the drive core (20) by a plurality of substantially radial transmission elements (32) which are all of equal length.

Description

REDUCTION GEAR SYSTEM The invention relates to a reduction gear system according to the characteristics of the preamble of claim 1. Mechanisms of this kind are known in the technical field under the term "harmonic drive systems (Dubbel, Taschenbuch für Maschinenbau 15th Edition , page 1069, company publication by Harmonic drive System GmbH 63225 Langen / Hassen.) These mechanisms essentially comprise three basic units, namely: a) the so-called wave generator, which is the actual drive unit, which includes an elliptical core , in which a ball bearing is mounted and which is also provided with an input shaft, b) the so-called flexible tongue, which is a steel hub, essentially cylindrical, but radially flexible (bearing bush) having external teeth , in which the elliptical nucleus is arranged for rotation, and finally REF .: 29556 c) the so-called circular tongue. This part is a stationary support ring, with internal teeth, the teeth of which are constantly coupled with the tongue, flexible, elliptically deformable, that is, with the steel bushing, deformable. In this regard, the support ring with internal teeth has a large number of teeth than the flexible steel hub, two peripheral sectors, diametrically opposite of which are constantly coupled with the internal teeth of the stationary support ring. As a result of the rotation of the elliptical core in the flexible steel hub, all the teeth of the steel bushing are made to engage, one after the other, with the teeth of the internal teeth of the support ring, stationary, during each rotation, as a result of which a rotation of the steel bushing takes place by the difference in the number of teeth.

Using these mechanisms that have a very compact structure, it is possible to achieve considerable speed reduction ratios or reductions. The rotational directions of the drive and the output are, however, opposite directions. The formula to calculate the relations of the respective gear is: i = Zi where Zi is a number of steel bushing teeth, flexible, and Z2 is a number of teeth of the support ring, of internal teeth, stationary. According to the information received from the manufacturer of these drive mechanisms, harmonics, gear ratios from 1:72 to 1: 320 are possible. The mechanisms of this class are used mainly in special purpose machines and industrial robots. In a known design of this harmonic drive mechanism (EPO 514 829 A2), the radially flexible steel hub is designed to be pan-shaped and is provided with a terminal wall, stable to a spatial separation from its external teeth. The thin, basically cylindrical wall of the steel bushing is flexibly deformable, such that it is able to adapt, on the one hand, to the cylindrical shape of the end wall and on the other hand, which adapts flexibly to the elliptical rotating circumference of the core. of the mechanism, that is, the so-called wave generator. In other designs of these mechanisms, such as the transmission element between the flexible steel bushing, ie the flexible tongue, and a transmission wave (DE 39 06 053 C2 and EP 0 309 197 B2), in each case, a second toothed ring comprising an internal denture is provided and this is arranged coaxially relative to the first support ring, of internal teeth, stationary, and has, at least substantially the same inner diameter as the support ring, stationary, but a number of teeth that differ from that of the support ring, stationary. In this respect, the teeth of the flexible steel bushing engage both with the stationary support ring and with the rotating serrated ring, specifically in such a way that the rotation of the flexible steel bushing is transmitted directly to the serrated ring., rotating, in addition to a ratio of 1: 1, since the rotating, serrated ring has the same number of teeth as the flexible steel bushing which, of course, during the rotation of the elliptical drive core, rolls on the edge of the gear of the stationary support ring. The steel bushing subsequently herein will be referred to as a bearing bushing. In principle, the method for operating the generic reduction gear system resides in that the peripheral surfaces of different lengths roll with each other free of sliding, as a result of which during the bearing, the shorter peripheral surface rotates or rotates through the difference in length. Since all the individual parts of these known mechanisms are made of steel or a similar material, and the mechanisms are, as a rule, equipped with ball bearings, radially flexible, ie deformable, which are arranged between the peripheral surface of the core of Elliptical drive and flexible bearing bushing, these mechanisms involve considerable manufacturing costs, especially since a high degree of finishing accuracy is a prerequisite for trouble-free operation. The object underlying the invention is to design a gear reduction system of the kind mentioned at the beginning, such that it is possible for its individual components to be manufactured in a simpler and more economical way, but, in particular, to have small dimensions, and to be assembled in a completely easy manner and in particular, automatically, such that it is possible to achieve a high degree of efficiency, a free play coupling and higher gear reduction ratios and higher speed reduction ratios as long as Keep friction losses to a minimum. The object is satisfied by a reduction gear system having the features of claim 1. Further developments are set forth in the dependent claims. Compared to the known mechanisms of the generic type, the design according to the invention provides not only the means for a more economical production to date, but also for a larger range of design variations and in particular, a very compact construction and small. It is also possible to achieve the precision of the transmission of the rotational movement using a considerably simplified means. This is due to the fact that, in the design of the mechanisms according to the invention, a roller or ball bearing is not required in any case between the bearing hub and the driving core or the bearing hub surrounding the latter. A further important advantage is that the mechanism is self-securing, which means that no torque, or any magnitude thereof, exerted on the bearing hub is capable of rotating the drive shaft forward or backward. At the same time, this also means that the drive shaft, which is in transmission connection as a result of the bearing bushing, in each case assumes an angular pressure, exactly defined when the mechanism is idle or the drive is inactive, and is possible so that this angular position is changed in one or the other direction only by means of the drive, that is, by a corresponding rotation of the drive core. The known mechanisms of the generic type do not include a self-insuring characteristic. The driving core, by means of which the transmission elements can be deflected radially, conveniently comprises an individual part. However, it is within the scope of the invention that the driving core comprises a plurality of parts. The crucial factor here is that the multi-part drive core also causes one or more peripheral sectors of the peripheral, outer surface of the flexible bearing bushing to engage in it. continuous alternation with the supporting surface of the support ring. In order to reduce the friction between the transmission elements and the drive core, the design according to the rei indication 6 is ventaj oso. As a result of the design according to claim 7, it is possible to achieve very good or optimum force and torque ratios, and the means for providing high gear ratios or gear ratios. With the design according to claim 8, it is possible to ensure not only a very high degree of functional reliability, but also an operation that is very slow in wear and in particular, very precise.

A particularly economic embodiment is set forth in claim 9, while the design according to claim 10 and / or claim 11 ensures minimum losses by friction, and thus, a high degree of efficiency. While the designs according to claims 12, 13 and 14 are already provided, as such, in known mechanisms of the generic type, it is also advantageously possible to use these designs in the embodiment according to the invention. of claim 15 provides a means for selecting, within certain limits, any gear ratio, since the circular spacing in a friction coupling has the value of zero, and the gear ratio or mesh reduction ratio achieved it is determined exclusively by the differences in the length of the peripheral lengths of the friction surfaces that roll against each other.Therefore, it is also possible to select gear reduction ratios, the denominators in respect of which they are not a number integral, but that can also comprise a decimal fraction, instead of purely frictional coupling, it is also It is possible, of course, to provide very small or very fine, circular separations, which is possible, in certain cases in which an isogonal, precise impulse transmission is not a critical factor, for the irregular dentition to be provided, for example, in the form of grooves, lacing or the like. An advantageous design in this regard is set forth in claim 16 insofar as this design ensures that it is possible to transmit, isogonally and without loss, the rotational movement of the bearing bush. A very advantageous design of the invention is set forth in claim 17. As a result thereof, it is possible to ensure that the connection between the bearing bushing and the drive shaft is also produced very economically and in a functionally direct manner. . An alternative to the above is set forth in claim 18. As a result of this design, it is possible, by means of additional meshing parts, to gain additional gear reduction ratios. While the design according to claim 19 is known, in principle, in the prior art mechanisms of the generic type, the design according to claim 20 provides an additional alternative, which opens up additional possibilities for the use of relationships of additional gear. The design according to the claim 21 it is advantageous for the embodiments of the reduction gear system according to the invention, which are more exact to what performance is related, because it is possible that the transmission elements, which are designed to make rams, are produce a different material that has a load carrying capacity, higher, than that of the rays of a complete plastic part. In this way, it is also possible that larger radial forces are transmitted from the drive core to the bearing hub, which is an advantage and gives considerable functional significance in particular in the case of a very fine denture or irregular teeth for friction transmission of the strength.

The design according to claims 22 and 23 approved is the most appropriate in this respect. Claims 24 and 25 refer to two advantageous design options, so the shape and arrangement of the guide cage for the transmission elements, designed to be rams, are of interest. With the design according to claims 26 and 27, a simply produced means is provided to compensate for process tolerances in order to achieve an absolutely play-free engagement of the teeth between the bearing bush and the support ring. Instead of an elliptical drive core, comprising two eccentric cams, placed diametrically opposite, or protuberances, it may be advantageous and convenient for certain uses, in particular uses comprising high pairs of forces in the shaft, to provide the design according to claim 28, in the use of which, in each In this case, three circumferential sectors of the bearing bush are simultaneously in a force-securing or shape-assurance coupling with the inner surface or denture of the support ring. The design according to claim 29 serves to ensure the convenient and protective encapsulation of possibly highly accurate engagement parts. The invention will be described in more detail below with reference to the drawings, in which: Figure 1 shows a front view of the reduction gear system along the line I-I of Figure 2; . Figure 2 shows a section II-II of the Figure 1; Figure 3 shows the body of the plastic, comprising the bearing bushing, the spokes and the bearing hub, in the same frontal view as in Figure 1; Figure 4 is a side view of the reduction gear system in its actual size; Figure 5 shows a side view V-V of Figure 6 of the reduction gear system, which is provided with a different driven device; Figure 6 shows a section VI-VI of Figure 5; Figure 6a shows half of a sectional illustration of a variation of the embodiment of Figure 6 in which the support ring is provided with an internal, radially flexible denture; Figure 7 shows a cross section of an annular, driven gear; Figure 8 shows a view VIII of Figure 7; Figure 9 shows a sectional illustration of a different embodiment of the reduction gear system, in which the driven annular gear is in transmission connection with a drive shaft via additional gear members; Figure 10 shows a partial front view along the line XX of Figure 11 of an embodiment in which the inner surface of the support ring and the peripheral surface of the bearing bucket are, in each case, provided with friction bonds and in which the bearing hub of the bearing hub, as in the embodiment exemplified according to Figures 1 to 4, is coupled to a shaft of transmission via a flexible connecting member; Figure 11 shows a section XI-XI of Figure 10; Figure 12 shows an exemplified embodiment, in which the bearing bushing, which frictionally engages the support ring, engages an annular gear driven via a denture, in the same view, in Figure 10; Figure 13 shows a section XIII-XIII of Figure 12; Figure 14 shows the front view of a bearing bushing, comprising radial spokes and a bearing hub and the spokes of which are provided with metal inserts.

Figure 15 shows a partial section XV-XV of Figure 14; Figure 16 shows a section XVI-XVI of Figure 15; Figure 17 shows a section XVII-XVII of Figure 15; Figure 18 shows a front view of a different embodiment of the single piece bearing bushing comprising spokes and a bearing hub; Figure 19 shows a partial section XIX-XIX of Figure 18; • Figure 20 shows a front view of an external tooth bearing bushing with spokes, ram and bearing bushing; Figure 21 shows the bearing bushing of Figure 14 with a metal ring inserted; Figure 22 shows the open terminal view of a mode of the reduction gear system in which the transmission numbers between the drive core and the bearing hub comprise rams; Figure 23 shows an isometric view of a ram as a separate part; Figure 24 shows an isometric view of a ram that is provided with a widened support surface, as a separate part; Figure 25 shows a front view with a triangular drive core, that is, a drive core provided with three eccentric protuberances; Figure 25a shows a front view of a different embodiment of the drive core of Figure 25; Figure 26 shows a side view of Figure 25; Figure 26a shows the drive core of Figure 25a in a side view, partially sectioned; Figure 27 shows a front view of an annular, driven gear comprising a guide cage, inserted; Figure 28 shows a section XXVIII-XXVIII of Figure 27; Figure 29 shows a front view of a different, driven, annular gear comprising a guide cage that is molded into a single piece; Figure 30 shows a section XXX-XXX of Figure 29.

. The various embodiments of a reduction gear system, the basic components of which, are, in each case, a circular support ring 1, having a surface 2 of inner, circular support, a bearing bushing 7, having a outer peripheral surface 7, and a driving core 20 or 21/1, elliptical or triangular, respectively. It will be described later herein with reference to the figures discussed above. In the exemplified embodiment of Figures 1, 2 and 3, the cylindrical support ring 1 is provided with an internal denture 3 extending across its full width b. The support ring 1, like the stationary gear part, is not rotatably connected to any mechanism carrier or the like, which does not. It is illustrated in the drawing. At their two terminal, lateral surfaces, in each case, the end walls 43 and 44 are arranged and interconnected or connected to the support ring 1 by means of axial screws 42. In a central hole 61 of the end wall 44, a tree of drive 14 is supported for rotation, and for example, is in communication with a drive motor, by means of which it is designed to be driven in one or the other direction of rotation. The drive core 20 is secured for rotation in the drive shaft 14, such that the drive core 20 also rotates isogonally with the drive shaft 14, when the latter is driven. The basically circular bearing bushing 5 is provided to have an external dentition 9 which, in the embodiments exemplified according to FIGS. 1 to 3, has the same width b as the support ring 1 or its denture 3. As can be seen in FIG. Figure 1, this external denture 9 of the bearing bush engages with the internal teeth 3 of the support ring 1, via a plurality of teeth, in each case, in the region of two peripheral sectors, placed in a diametrically opposite manner. This is possible because the bearing bushing 5 is radially flexible and is connected integrally, via the radial transmission members which, in the present case, are designed to be spokes 32, to an outer bearing bushing 22 within the which drive core 20 is arranged for rotation.

In this regard, the inner diameter Dn, that is, the inner circumferential length, resulting from the bearing bushing 22, is selected such that, the mounted condition as shown in Figures 1 and 2, the elliptical drive core is encircled. 20 at least substantially free of play. The inner diameter Dn of the bearing hub 22, basically cylindrical, is smaller, by at least a quarter to a third, of outer diameter Da of the bearing hub 5, also, basically cylindrical. In the exemplified embodiment illustrated in Figures 1 to 3, the bearing bushing 5 and the bearing hub 22, together with the transmission elements designed to be spokes 32, form a structural part of a single piece of plastic material, which is economical for simple assembly production. As a result of the relatively high degree of flexibility that the bearing hub 22 can have in this respect, it is also very simple to insert the non-circular drive core 20 into the bearing hub 22. As a result of the rotating movement of the drive group, eccentric that is, elliptical, the driving core 20 in the bearing bushing 22, the latter being continuously deformed elliptically. This elliptical deformation is also transmitted to the bearing bushing 5 via the stripes 32, such that different teeth of the outer teeth 7 of the bearing bushing 5 are continuously coupled with the internal teeth 3 of the stationary support ring 1. In doing so, due since the tooth number Zi of the outer teeth 9 of the bearing bush 5 is smaller than the number Z2 of teeth of the internal teeth 3 of the support ring 1, a continuous rotation of the bearing bush 5 relative to the ring 1 of support, stationary takes place, the rotation being in a direction opposite to the direction of rotation of the drive shaft 14, ie the drive core 20. As mentioned, the resulting gear ratio between the number of shaft rotations of printing 14 and the number of revolutions of the bearing bush 5 is calculated according to the following formula: Z2 Z1-Z2 For example, when the bearing bushing 5 has the number_ of teeth Za = 98, and the support ring 1 has the number of teeth Z2 = 100, a gear ratio of i = 1:50 is calculated according to the formula previous. Instead of the number of teeth, it is also possible to use the circumferential lengths of the inner surface 2 as Z2, and the circumferential length of the outer peripheral surface 7 of the bearing bush 5 as Zi, producing the same result. The above is proposed to show that it is not absolutely essential to provide a tooth coupling between the support ring 1 and the bearing bush 5, but that it is actually possible that the mechanism is designed to be a pure friction gear, as will describe in more detail later in the present. As can be seen in Figure 2, the bearing hub 22 comprises, as a connecting member 25, a hollow shaft 26, flexibly deformable and also substantially thin-walled cylindrical, which is engaged, via an internal denture 27, to a pinion 31 of a transmission shaft 30. In this regard, the hollow shaft 26 is provided with suitable radial clearance and passes through a correspondingly wide axial central hole 34 in the terminal wall 43. As a result of this member of connection 25, the rotational movement of the bearing bushing 5, or bearing bushing 22, are transmitted to the drive shaft 30. The exemplified embodiment, illustrated in FIGS. 5 and 6, differs from the exemplified embodiment of FIGS. 1 to 3, described above essentially in that an annular, driven gear 40, comprising an internal denture 41, is provided as the connecting member between the bearing bush 5 and a transmission shaft 29, and forms a a structural part, single piece together with the drive shaft 29. In this respect, the internal teeth 3 of the support ring 1 has a smaller axial width bl than in the external teeth 9 of the bearing bush 5 having the width b . The inner annular gear 41, driven 40, has a number of teeth Z3 which corresponds, at least substantially, to the number of teeth Zi of the external teeth 9 of the bearing bush 5 which engages with the internal teeth 3 of the ring. support 1 However, in order to ensure that a rotational movement of the driven, annular gear 40 also occurs during a rotational movement of the bearing hub 5, the number of teeth Z3 of the internal teeth 41 of the driven annular gear 40 must differ from the number of teeth. teeth Z2 of the internal teeth 3 of the support ring 1. When the number of teeth Z3 of the internal teeth 41 corresponds to the number of teeth Zi of the external teeth 9 of the bearing bush 5, the gear ratio between these two sets of teeth teeth 41 and 9 will be 1: 1. When the number of teeth Z3 of the internal teeth 41 is greater than the number of teeth Zi of the bearing bush 5, there will be an additional speed reduction ratio; When the number of teeth Z3 is less than the number of teeth Zi, there will be an additional rate of increase, speed. When the internal teeth 41 has, for example, a tooth smaller than the outer teeth 9, then the driven annular gear 40 will rotate, during a complete rotation of the bearing bushing 5, upwards through an additional circular clearance that the bushing 5. When, in contrast, the internal dentition 41 has a tooth more than the bearing bush 5, then the driven annular gear 40, during a complete rotation of the bearing bush 5, will perform a rotational movement that is less , by a circular separation, that a complete rotation. Figure 9 shows a variation of the reduction gear system illustrated in Figures 5 and 6, in which the driven annular gear 40/1, with its internal teeth 41, is coupled in the same manner with the outer teeth 9 of the hub of bearing 5. In contrast to annular gear driven 40, however, the driven annular gear 40/1 does not comprise a drive shaft. Instead, it is connected in the form of a transmission to a transmission shaft 28 via additional gear members 60. The gear parts 60 comprise two planetary wheels 62 and 63, positioned diametrically opposite, which is supported for rotation on trunnions. bearing 64 and 65, arranged eccentrically, and which are coupled, on the one hand, with the internal teeth 41/1 of the annular gear, driven 40/1 and, on the other hand, with a gear 28 'which integrally connects to the shaft transmission 28. It is possible that the gear reduction ratio between the drive shaft 14 and the drive shaft 28 is further changed, by means of these additional meshing parts 60. In particular, in this way, it is possible to achieve greater gear reductions or higher speed reduction ratios. As is already the case in known reduction gear systems of the generic type, it is also very easily possible, in the reduction gear system according to the invention, to produce a completely play-free tooth coupling between the bushing teeth of the bearing 5 and the teeth of the support ring 1, especially since the additionally improved conditions are provided since the bearing hub tooth 5, which is made of a plastic material, are softer and thus also more flexible than the teeth. rigid teeth of the support ring 1 which is usually made of steel, brass, aluminum or other hard material. This combination of materials also contributes considerably to a completely silent operation of the mechanism according to the invention, while of course it is possible for certain applications to fields of application to produce the two coupling parts of plastic or metal material.

Depending on the proposed use and possible field of applications, the 40 or 40/1 driven annular gear is produced from plastic or metal material, the production using plastic material in an injection molding process obviously being more economical. Figures 10 and 11 show a mode that differs from the embodiment of Figures 1 and 2 only in that the inner surface 3 of the support ring 1 is provided with a friction name 4, and the peripheral surface 7 of the bearing bush 4 , comprising spokes 32 and a hub 22, is provided with n friction lining 11, and that, instead of a coupling with teeth, a frictional engagement between the support ring 1 and the bearing bush 5 occurs. the embodiment of figures 12 or 13, the basic design of which is similar to the embodiment according to figures 5 and 6, the inner surface 2 of the support ring 1 and the peripheral surface 7 of the bearing bush 5 are, in each case, provided with friction liners 4 and 11, respectively, extending across the width bl. Axially adjacent, an outer dentition 9 of the bearing bush 5 engages with the internal teeth 41 of an annular, driven gear 40. Figures 14 to 17 illustrate one embodiment of the bearing bushing 5, in which the spokes 32, which are integrally connected thereto, are each provided with metal inserts 37. These metal inserts 37, in each case, they comprise foot ends 38, which protrude inwardly freely from the bearing bushing and by means of which it is possible for the insert parts to be directly supported on the peripheral surface 52 of the drive core 20. (figure 22). In this regard, in order to ensure favorable frictional behavior, it is advisable to select the known combinations of materials, for example, brass and steel, brass and steel, or the like. As can be seen in figures 15 to 17, the metal inserts 37 are completely wrapped, in each case, with a plastic material, with the exception of their foot ends. Metal inserts 37 of this kind are convenient and advantageous, in particular in cases where considerable radial forces are to be transmitted, for example in order to achieve sliding frictional engagement between the peripheral surface 7 of the bearing bush 5. , peripheral surface which is optionally provided with a friction lining 11, and the inner surface 3 of the support ring 1. In this regard, it may also be advisable to equip the outer annular body of the bearing bush 5, by itself, with a piece of metallic incision, annular, that will cause an improved distribution of the force, in the peripheral direction. Metal insertion parts 37 of this class are, of course, also conveniently used in the bearing bushings 5 which are provided with an external denture 7. It may also be convenient and advantageous when the bearing hub 22 of a bearing bushing The bearing 5 is provided with a metal bearing sleeve 23, in order to reduce the wear resulting from the friction within the bearing hub 22 to a minimum. An exemplary embodiment of this nature is illustrated in FIGS. 18 and 19. In these figures, a bearing metal sleeve 23 is fitted in the bearing hub 22 such that its inner surface liza 23 ', which has characteristics that produce low friction, it surrounds the drive core 20 at least in a substantially play-free manner. In order to prevent a rotation of the bearing sleeve 23 in the hub of the bearing 22, and in order to secure it axially in its position, the bearing sleeve is provided at its front ends, in each case, with slots 24 in the form of a slot that they are filled from the outside with the plastic material of the bearing hub 22. In the finished state, the bearing bushings 5 of Fig. 14 and 18, in each case, they form a uniform structural part 35, which is simple to produce and is also simple and is installed in a technically correct manner in the mechanism. Figure 20 shows the front view of a bearing bushing 5/1 which, however, does not comprise any spoke or any bearing hub. Specifically, it comprises an annular body. 58 radially flexible having an external denture 9. In the embodiment of Figure 21, the bearing bush 5/1 is provided with a thin-walled, annular metal insert 39. When these bearing bushings 5/1 are used, the force transmission from the drive core 20, which, as a rule, is elliptical, takes place via a plurality of rams 33 or 33 ', respectively, which are guided for displacement. radial and are supported, via the rounded, interior, foot ends 38, directly on the peripheral surface 52 of the drive core 20, and the outer ends of which are provided with a curved support surface 36 and 36 ', respectively, which can optionally be widened in both directions. It is by means of these support surfaces 36 and 36 'that these rams 33 and 33', respectively, transmit the radial deformation forces and movements to the annular body 58 of the bearing bush, externally toothed 5/1, the denture 9 of the which, in this way, is coupled circumferentially with the teeth of the internal teeth 3 of the support ring 1. These rams 33 or 33 'are guided, in each case, in radial guides 47 in the form of a slot of a guide cage 45, cylindrical, hollow, and 45/1, respectively, which is arranged and centered within the bearing bush 5/1, concentrically with the internal teeth 3 of the support ring 1. It is possible that this guide cage 45, 45/1, for example, be of plastic material. In the exemplified embodiment, illustrated in FIGS. 27 and 28, their sectors 48, forming radial, slit-shaped guides 47, are provided with a common terminal wall 49 which is designed to be circular and centered in a depression cylindrical 49 'of an annular driven gear 40 which is made of metal. In this regard, the sectors 48 form a circular hollow space 48 'in which the drive core 20 freely rotates. The outer diameter of the connectors is also selected such that the radial, elliptical deformation of the bearing bush 5/1 , or the radial movement of the rams 33 ', which are provided with flared support surfaces 36', are not adversely affected. In the exemplified embodiment, illustrated in Figures 29 and 30, the guide cage 45/1 is integrally connected to an annular, driven gear 40, which is also made of plastic material. It is readily conceivable that, instead of an elliptical drive core 20, it is also possible to use a drive core 20/1 that is designed to be triangular, that is, provided to have three radial protuberances 55 to be deposited at a common circumscribed circle 56, and by means of which three peripheral sectors, in each case, misaligned by 120 ° relative to one another, of the bearing bush are coupled with the inner support surface 2, or its denture 3 (see figure) 25). An advantageous use of such a triangular drive core is, in particular, when a very thin denture, with a small height of the teeth, a with an inflectional coupling being used. In the chaos of the teeth used, care must be taken that the tooth differences between the denture 3 of the support ring 1 and the denture 9 of the bearing hub 5 or 5/1 must be a * integer that is divisible for three. For a frictional coupling, this is irrelevant. An additional design option with respect to the drive core is illustrated in Figures 25a and 26a. In this embodiment, the drive core is a triangular disc 20/2 which is provided, on the one hand, by the drive shaft 14, and on the side placed opposite, with three rollers 55/2 that are offset by 120 ° relative to each other. These rollers 55/2 are, in each case, supported for rotation in the cylindrical bearing journals 55/1 of the disc 20/2, and are otherwise arranged and designed such that their cylindrical peripheral surfaces are placed in the circle circumscribed, common 56 that is coaxial with the axis of the drive shaft 14, as is the case with respect to the protuberances 55 of the exemplified embodiment of FIGS. 25 and 26. This shows that it is also possible for the drive core to have a multi-part design. In order to ensure a completely play-free, reliable coupling position, even in the case of critical tooth profiles for the denture 9 of the bearing bushing 5 or 5/1, on the one hand, and the denture 3 of the support ring 1, on the other hand, as long as the minimum of friction-induced wear is ensured, it is advantageous and convenient to design the internal teeth 3 of the support ring 1 to be radially flexible. It is possible to provide this, for example, by means of the modality illustrated in figure ßa. In this regard, a thin, annular groove 70 is arranged between a relatively thin, annular, body part 68, in which the internal dentition 3 is joined, and the outer, thick-walled, outer wall body part 69. , the annular groove extending in a substantially axial manner across the full width b of the outer dentition 9 of the bearing bush 5. That part of the support ring 1 that is provided with the denture 3 is radially flexible since the two sets of dentures 3 and 9 are designed to be pressed together radially in a complete manner in play. In this way, it is possible to completely compensate the tolerances of the process.

It is noted that in relation to this date, the best method known by the applicant to carry out the present invention, is the conventional one for the manufacture of the objects to which it refers.

Having described the invention as above, the content of the following is claimed as property:

Claims (30)

1. The reduction gear system, comprising a support ring, having a substantially cylindrical support surface, and a radially flexible bearing hub having an outer peripheral surface having a circumferential length shorter than the surface of support, in which one or more peripheral sectors of the outer peripheral surface are maintained in a substantially sliding-free coupling with the outer surface of the support ring in continuous alternation by means of one or more parts that are placed in a encircling circle of a drive core that is arranged for rotation with the bearing bushing and rotated by a drive shaft, characterized in that the enclosing circle has a substantially smaller diameter than the roller bearing, basically cylindrical, and in that The bearing bushing is supported in the drive core by means of a plurality of transmission elements. ision that extend essentially radially, all of which have the same length.

2. The reduction gear system according to claim 1, characterized in that the bearing surface of the support ring is provided with an internal dentition, and the bearing bush, radially flexible with an external denture.

3. The reduction gear system according to claim 1 or claim 2, characterized in that the drive core has an eccentric shape, in particular, an elliptical shape.

4. The reduction gear system according to one of claims 1 to 3, characterized in that the bearing bushing is in, or is designed to be in contact with, a rotationally fixed connection with a drive shaft via a connecting member. .

5. The reduction gear system according to one of claims 1 to 4, characterized in that the transmission elements are designed to be spokes or rams.

6. The reduction gear system according to one of claims 1 to 5, characterized in that the radially inwardly positioned ends of the transmission elements are supported in a radially flexible bearing hub, in which the drive core is Supports for rotation.

7. The reduction gear system according to one of claims 1 to 6, characterized in that the inner diameter of the bearing hub, basically cylindrical, is smaller by at least one-quarter to one-third of the outer diameter of the bearing hub, basically cylindrical.

8. The reduction gear system according to claim 6, or claim 7, characterized in that the circumferential, inner length of the bearing hub conforms to the circumferential length of the drive core, such that the bearing hub encircles the core of drive at least substantially free of play.

9. The reduction gear system according to one of claims 6 to 8, characterized in that the bearing bushing and the bearing hub, together with the transmission elements designed to make spokes, form a structural part of an individual piece of plastic material.

10. The reduction gear system according to claim 9, characterized in that the bearing hub, which is made of plastic material, is provided with a bearing sleeve, also radially flexible, made of metal, which serves as a sliding bearing for the drive core and surrounds the drive core.

11. The reduction gear system according to claim 10, characterized in that the spokes comprise metal inserts that are completely covered in plastic material and the ends of the feet of which are supported in a sliding manner directly on the surface peripheral of the drive core.

12. The gear reduction system according to one of claims 9 to 11, characterized in that the bearing hub, which is connected to the bearing thrust by means of the spokes, comprises, as a connection member, a hollow shaft basically cylindrical to which the transmission shaft is coupled.

13. The reduction gear system according to one of claims 1 to 12, characterized in that the bearing bushing comprises an external denture which engages with an internal dentition of the support ring.

14. The reduction gear system according to claim 13, characterized in that the internal teeth of the support ring have a smaller axial width than the outer teeth of the bearing bush, and that an annular, driven, cylindrical gear is arranged , concentrically with the support ring and can be rotated relative to this, and with the internal teeth of which, in each case, at least substantially the same tooth of the rolling bearing engages as with the internal teeth of the support ring .

15. The reduction gear system according to one of claims 1 to 14, characterized in that the inner surface of the support ring and the outer surface of the rolling bearing are in frictional engagement.

16. The reduction gear system according to claim 15, characterized in that the bearing bushing comprises an external toothing axially adjacent to its peripheral surface sector, which is in frictional engagement with a friction surface, inside the support ring , external teeth which, in each case in the region of their peripheral sectors that frictionally engage the support ring, engages in a gear form the internal teeth of an annular, driven gear that is supported for rotation coaxially with the support ring.

17. The reduction gear system according to claim 15 or claim 16, characterized in that the driven, annular gear is provided with a drive shaft that is coaxial with the support ring.

18. The reduction gear system according to claim 15 or claim 16, characterized in that the driven annular gear is in a transmission connection with a drive shaft via the additional parts of the gear.

19. The reduction gear system according to claim 12, characterized in that the internal teeth of the driven annular gear engaging with the outer teeth of the bearing bush have the same number of teeth as the bearing bush, but at least substantially the same reference diameter and / or internal diameter as the internal teeth of the support ring.

20. The reduction gear system, according to claim 13 to claim 19, characterized in that the internal denture of the driven annular gear that engages with the outer denture of the bearing bush has a different number of teeth than the bushing. of bearing.

21. The gear reduction system according to one of claims 1 to 8, or 11 to 20, characterized in that the transmission elements, which are designed to be rams and are arranged between the bearing bush, on the one hand, the Drive core or bearing hub, on the other hand, are supported to be radially displaceable in a cylindrical guide cage surrounding the bearing hub or drive core, the outer ends of the butt-transmitting transmission elements loosely for the support against an inner surface of the bearing bush, which is an annular body, and the ends of the inner feet of which are butted loose to the support against the peripheral surface of the driving core.

22. The reduction gear system according to claim 21, characterized in that the rams are metal plate-shaped parts that are guided, in each case, in radial guides of the guide cage of the plastic material.

23. The reduction gear system according to one of claims 1 to 22, characterized in that the rams are provided, at their ends radially outwardly with enlarged support surfaces.

24. The reduction gear system according to claim 22 or claim 23, characterized in that the guide cage is guided and centered via a terminal wall on an annular surface that is concentric with the support ring.

25. The reduction gear system according to claim 22 or claim 23, characterized in that the guide cage is integrally molded in an annular driven gear which is also made of plastic material.

26. The reduction gear system according to one of claims 1 to 14, or claims 16 to 25, characterized in that the internal teeth of the support ring is designed to be radially flexible.

27. The reduction gear system according to claim 26, characterized in that the internal teeth of the support ring are joined to a thin-walled, annular body part which is separated from a thick-walled, annular body part. outside by an annular, circumferential groove that opens on a front side.

28. The reduction gear system according to one of claims 1 to 27, characterized in that the drive core comprises three protuberances that are misaligned by, in each case, 120 ° in relation to each other and placed in a circumscribed circle that It is concentric with the support ring.

29. The reduction gear system according to one of claims 1 to 28, characterized in that the support ring is part of a cylindrical housing that surrounds the bearing bush and the annular, driven, possibly proportioned gear, and is provided to the less on a terminal surface with a terminal wall.

30. The reduction gear system according to one of claims 1 to 29, characterized in that the drive core comprises three rollers that are supported for rotation in bearing journals, axially parallel, which are offset by 120 ° relative to each other. Yes, on a disc, the cylindrical peripheral surfaces of these rollers that are placed in a circumscribed, common circle that is coaxial with the shaft of the drive shaft.