SK46295A3 - Epicyclic roller gear with two round bodies provided with teeth and segments which may be successively pressed on the teeth - Google Patents

Abstract

An epicyclic roller gear (10) has two round bodies, in particular rings (1) and (4), provided with a profile or teeth at their inner or outer circumference, and a driving shaft (2), by means of which pressing elements, in particular epicyclic rollers (3), bring individual segments (6), which have complementary profiles and are radially adjustable independently from each other, into engagement with above said profiles of the round bodies. Since these round bodies or rings (1 and 4) have different numbers of teeth and one ring (1) is fixed, whereas the other ring (4) rotates, a relative displacement is achieved, and thus also a high reduction ratio between input and output. In order to guide the segments (6) in a reliable but mutually independent manner without axial guiding rings or mutually coupling the individual segments (6) into a segment chain, the individual segments (6) which are directly adjacent to each other in the circumferential direction are mounted individually and independently from each other in a deflectable manner against the restoring force of two parallel bar or preferably leaf springs (7) fixed to each other. The springs (7) are arranged behind each other in the radial direction but their larger width extends in the circumferential direction. The segments (6) may thus be individually deflected parallel to their own direction, so that a precise engagement and thus a displacement on the rotary round bodies or ring (4) may take place with a high efficiency.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gearbox having impellers, two spherical bodies having a toothing, and successively for toothing in the pressable segments.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an impeller having two spherical bodies or rings provided on the outer or inner circumference with profiling or toothing, wherein the fixed and second spherical bodies are coaxial to the first spherical body and mounted relative to this rotatable. , with successive segments for toothing or profiling of the spheres which have an associated toothing for this profiling or spherical toothing and thus always engage in the toothing of the fixed and rotatable spherical body, and with at least one segment facing away from the circumferential side and parallel to one another, on their spherical body in a radial direction, towards the spherical bodies which, due to the different number of teeth on the two spherical bodies, the rotatable body relative to the fixed body can move while the restoring force releases the segments again.

More current melts

Such a gearbox is known, for example, from DE-AS1. 182 011. Here, the individual segments are guided axially by the two faces so as to prevent lateral bending movements during their radial movement. In addition, an example of an embodiment in which the individual segments are interconnected transversely is described in this print

-2-pins to create a segment's orbiting chain to better manage and hold each segment. In both cases, this results in a mechanically demanding transmission, which requires high production and assembly costs for the mutual placement and fixing of the individual segments, as well as a large space requirement for both sides of the segments.

Although a comparable gearbox is known from LIS-A-2 943 513, in which it does not use segments but a continuously circulating toothed belt, it may carry it. it is subjected to considerable wear due to its constant deformation during the circulation of the thrust or thrust elements which press it into the inner toothing of the rings and on the other hand pull it out at adjacent points.

In these previously known gears, an oval bearing is always required for the thrust elements so that the segments or the toothed belt are always pressed in sections into the inner ring teeth and the adjacent sections are held out or pulled out. Such oval holding also requires high production costs and very accurate production.

SUMMARY OF THE INVENTION

It is therefore an object of the invention to provide. The gear units of the type mentioned above, in which the toothed segments are individually adjustable parallel to one another without the need for a double-sided guide or interconnection, are therefore independent of the double-sided guide and / or the interconnection precisely movable thereby avoiding at the same time. oval bearing or design of the thrust element.

In order to solve this problem, an impeller-defined impeller is characterized by the fact that the segments are arranged side by side - possibly touching - the segments are mounted individually and independently of each other on two parallel rigidly connected spring or leaf springs and can be deflected the springs are arranged one behind the other in the radial direction and can deflect when the respective segment is pressed so that the respective segment is adjustable parallel to itself. This follows the arrangement

For each segment, precise and precise fixation of its position, while at the same time retaining the segment also provides a restoring force so that the segments can be adjusted in a radial direction independently of adjacent segments, adjusting themselves parallel and after engagement due to the two parallel springs. automatically returns to the out-of-range starting position. Parallel adjustment by means of a double-spring bearing ensures the required engagement along the entire axial length of the teeth in the associated toothing and thus the best transmission of force with the lowest possible wear. There is no need to convert two-way segment management to create a chain of segments because the segments are hinged individually and thus have a precise position and maintain it.

As a rule, such an impeller has two rings as spherical bodies with different internal toothing, one of which is rotatably mounted, further provided with a rigidly connected carrier fitted with thrust elements or roller elements. 11 of such a gearbox, it may be envisaged in the embodiment of the invention that the internal profiled rings have at least one point of contact with the profiled segment, for example, gear-fixing segments of pulleys having on their external toothing which may be provided with one, two, three or more teeth and that with the help of a parallel system of springs mounted on the ring, it has also proved to be particularly suitable for running with rings such as round bodies, internal profiling or toothing. Here, the invention can be applied particularly advantageously since the individual segments can be pushed by their own. by means of the teeth of the internal toothing of the rings independently of each other in order to set in motion a rotating ring with a different number of teeth and achieve a correspondingly large gear ratio in comparison with the drive shaft moving the thrust element in the circumferential direction.

The segment may be disposed approximately midway between the two springs or continuing one of them approximately parallel to the central axis of the spreading spring, in particular a continuation of the spring lying most outward in the radial direction. This allows space saving design because

-4 can get. In such a gearbox with such a gear with rings with internal toothing in the radial direction further inwardly lying leaf spring is the area where the thrust element -axially and needs space. Typically, the teeth of the rotating bodies or rings, and the teeth of the segments are approximately parallel to the central axis of the drive and output shafts or the rotating bodies or rings.

In order to be able to be simply shaped as a circulating sliding element, or to be able to roll a rolling pulley during the circulation during rotation and to be able to circulate on just radially displaced segments without impact and with little friction, even between the pressed and the adjacent segment produces a graduation, it can be a cross-sectional element and from the rotating bodies and 1 or a segment. an elastic contact ring between the rings facing away from the segments. This creates an uninterrupted bonded surface for the circulating thrust element, even though the tooth elements relative to one another move in a radial direction and thus continuously form a graduation. This is bridged and attenuated by the contact ring.

It should be noted that the number of teeth on each individual segment may be. the greater the number of teeth on the rotating bodies or rings. A particularly useful embodiment of the invention of the importance of suitable protection may be that along the circumference of the rotatable rotary body or rotary ring the number of teeth is the same as that over the same portion of the periphery of the fixed rotary body or ring and adjacent parts of the circumference of the rotatable rotary body or ring have different numbers of teeth. As a result, when the thrust element is circulated, the drive shaft continues to rotate for a certain period of time during which the tooth segments are pushed into the two rotary bodies or rings in the same number of teeth on the same circumferential length, while the output shaft is running. the shaft does not rotate and starts to run as soon as adjacent parts of the perimeter with different tooth numbers or tooth spacing are applied. In doing so, it may be. the siner of rotation optionally in one or the other direction, depending on whether the number of teeth or the pitch of the teeth in the adjacent portion of the circumference of the rotary ring is greater or lesser than that of the respective portion of the circumference of the ring. Thus, the transmission can also be designed, used as a stepping transmission or, alternatively, for various areas such as a reversing device, or possibly also for oscillating movements. Depending on the choice of the number and length of these parts of the circuit with alternating numbers, teeth or tooth pitches, it is possible here to choose rocking movements with greater or lesser amplitudes. This arrangement can also be used with gear units with interconnected segments, toothed belts and the like. However, it is particularly advantageous if the segments are hinged individually on parallel springs in order to allow precise movement with low wear and space saving, which is particularly advantageous when they occur in the transmission, on the basis of said measure with alternating tooth numbers or tooth pitches, acceleration and delay on the output shaft.

Another embodiment may be when the movable rotary body or ring has more teeth in certain angular ranges of its circumference and in other angular ranges less teeth than the opposite circumference of the fixed rotary body or ring. This causes the aforementioned reciprocating movement in the direction of rotation on the output shaft, with the drive always rotating in the same direction.

In the transition area of the circumferentially toothed portion of such different tooth counts or in the transition areas of the circumferentially toothed portion of different tooth counts, a transition function of the tooth transition that at least in the first derivative has a value different from zero or does not cause shocks can be predicted. Thus, a smooth transition from the idle state to a rotational motion or from one direction of rotation to another direction of rotation of the output shaft can be achieved.

As the thrust element, at least one circulating pulley (as already mentioned) or at least one pressure medium nozzle, in particular a pressurized air nozzle, which orbits the segments and introduces them successively by their projecting beam against the spring suspension, can be foreseen. This basically achieves control of individual segments without

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Further control of the gearbox without friction can be achieved if an electromagnetic device is provided in which the segments are magnets which can be repelled from their rotating body facing away from the rotating body and acting on the thrust element acting as a thrust element. It is also operated without friction.

A structurally advantageous arrangement, also suitable for assembly, can be achieved in that the parallel springs or leaf springs are clamped in their region. i and individual? joined by a ring. For example, the initially wide double-wall ring could be divided by axial slots into individual leaf springs, but the slots would not completely split the ring. This results in a single part, but in which the individual segments can deviate independently of one another, in the radial direction against their supporting double springs. Accordingly, relatively many segments.

It is also worth mentioning having a toothing that engages the segments with a suitable fact during the toothing on it is also easy to assemble these that the pressure rollers can bypass and push the segments. In this case, the segments are toothed on both sides of the perimeter. As a result, there is a degree of soft passage and softer circulation when the pressure roller or pressure rollers are circulated, although there is a step between the pushed and unpressed segments.

If necessary: or ed n ot. .1 even more substantially axially required that the spring without requiring length, the spring springs can be shaped by two directional changes approximately as S or Z, and in particular by their directional changes, they can be arranged mirror-like and ends connected to the segment or to each other may be closer to each other than the clamped ends. With approximately the same axial length of the springs, the effective spring length can thus be increased, thus providing a softer suspension.

For a well-balanced rotation without radial runout, it is expedient to provide at least two diametrically opposite or i.e. circumferentially distributed pressure elements which are fixed or mounted in particular on common, drive shaft of pivot bars or similar carriers and rotate therewith and with the drive shaft.

The altered impeller gearbox could be converted so that the rotary body or ring or disc had external toothing, that the individual segments could be pressed from outside and had internal toothing, and that the outer side of the segment circulated] pressure element or pressure roller. Thus, rotary bodies with external toothing could be produced, which is easier than manufacturing internal toothing a.

Overview of the figures in the drawing

In the following, examples of embodiments of the invention are described in more detail with reference to the drawings.

In a partially schematic representation, Fig. 1 shows a cross-section of a planetary gearing according to the invention along the line in Fig. 2, with a view of three thrust elements carried by the pulleys and loaded by individual segments having a single tooth in this case; 1, FIG. 3 shows a representation corresponding to FIG. 1 with a gear sectioned along the line A-A in FIG. 2, with the segments having two teeth, FIG. 4 a representation corresponding to FIG. 3, having the segments Fig. 5 to Figs. 1, 3 and 4, an analogous representation of the transmission according to section line A-A in Fig. 6, wherein a contact ring is inserted between the rotating pulleys and the individual tooth segments, so that the thrust movements are transferred from the pressure rollers to the tooth segments 6, a half-longitudinal sectional side view of a gearbox with impellers according to FIG. Fig. 7c is a front view of the toothed segment with two teeth; Fig. 7c is a rear view of the clamping ends of the springs and the springs facing the springs firmly connecting the toothed segment side; Fig. 7b side view of the toothed segment with its supporting springs.

Fig. -8d-7d is a plan view of the toothed segment and its spring system in a radial direction.

FIG. 8 is a schematic representation of a ring gear according to the invention having internal toothing with three areas in which an equal number of teeth is assumed, with corresponding angular ranges of the second ring, and the remaining three ranges with a different number of teeth; 10 shows a representation analogous to FIGS. 1a to 5 along the cross-sectional line A-n in FIG. 11, wherein the orbiting rollers configured as thrust elements have external the toothing and the segments engaging their outwardly arranged teeth in the inner toothing of the rings furthermore have an internal toothing with which the toothing on the outer circumference of the pressure rollers engages, FIG. 11 is a half cross-sectional side elevation view of the impeller gear of FIG. gearbox with 13 is a cross-sectional view and FIG. 14 is a cross-sectional view of a modified rotary-wheel transmission according to the invention, in which the thrust rollers run on the outside of the toothed rings or discs and push the radially located segments therein inside.

Examples of embodiments of the invention (also described in the embodiments below) and substantially identical reference numerals will also be used for parts having the same function in their different shaping.

The whole of the gearbox 10, which is referred to as the gearbox 10, hereinafter referred to as the gearbox 10, has two rings 1 and 4 provided on its inner circumference with a ring 1 and 4, the first ring X being fixed and the second ring 4 arranged parallel and coaxial to the number of teeth per

This is different or different.

The ring gear transmission of the toothing of the two rings 1a and 4 is that segments 6.1 to 6.3 or 6, respectively, which have an associated toothing to fit the toothing of the rings 4 and 4 can be pressed against the profiling or 1 and 4 respectively. can be simultaneously pushed into the toothed fixed ring 4 and the rotary ring 4, so that due to the different number of teeth of the two rings 1 and 4, the rotary ring 4 is pivoted at a slow speed compared to the drive shaft 2.

By segments 6.1. 2.6 6.3 and 6.D the at least one thrust element, in the exemplary embodiment of the pulley 3, circulates at least one of the toothing of the rings 1 and 4, in which case the individual segments, in this case in parallel radial direction, adjust themselves to engage the toothing of the rings 1 and 4. The drive shaft 2 causes the pulley 3 to circulate. The restoring force, which will be explained further, is released from the toothing three and ensures that the segments 6 are returned. It will be noted that in the exemplary embodiment the thrust elements of the acting roller 3 are spaced equally apart on the inside of the segments

6, so that there is still a positive connection in the three zones in the gearbox 10.

According to Figures 2,6,7 and 11, segments 6-1 can be arranged side by side in the circumferential direction. 6.2, 6.3 and 6.D can be moved independently of one another in the radial direction into and from the internal toothing of the rings 4 and 4 and are movably mounted on two parallel for this purpose and against the restoring force.

The springs 7 are arranged in a radial direction behind or side by side and can be adjusted when the segment is pressed so that the respective segment swings itself towards the desired way. parallel. This is achieved by the quadrilateral formed by the springs 7, their clamping point and their fixed connection, both long sides of which are formed by the springs 7. By this simple and expedient refitting, the unnecessary minimum wiring and 1 e 1: · connecting individual segments with each other.

In all cases, two are assumed

-.10para 1 e 1 no breast t.ence i think anyway! Fig. 13 prints externally.

and 4 provided with internal toothing. It would not be possible to use other spherical bodies, such as provided with discs, wheels or rings or .1.4, where the segments are analogous. in that the segments G are securely held by springs 7, in which case the outer side of the corresponding spherical bodies can also be supported without the need for a costly retaining measure and that the engagement side would now have to be closed now; ii or 1 or more similar elements.

As the thrust elements of the serving pulley 3, they are fixedly connected to the pulley carrier 5, subsequently shortly referred to as the carrier 5, on the shaft 2 such that rotation of the shaft by means of drive drives the carrier 5 or carriers 5 so that the pulleys 3 roll on the inner side of the segment G, and in the manner outlined above, these are parallel to each other, whereby the adjusted segments 6 are always disengaged after the pulley 3 has been driven by the return force of the springs.

They have at least one point of contact with the outside toothed segment, which can be provided with one (figure 1), two (figure 3), three (figure 4) or more teeth, according to various figures. In this case, the segments are supported by a parallel spring system on the fastening ring, in the exemplary embodiment on the fixed ring 1.

The arrangement of the two springs 7 is also particularly noticeable in Figure 12. It is clear that the two springs 7 arranged in the radial direction next to each other for holding the segment 6 are connected by a cross bar 7B or the segment body itself. 6 extends in the radial direction and the toothing comprising the segment G is arranged or fixed in the axial direction next to the cross bar 7B or next to the connection of the two springs 7. The segment G is then formed from the outboard rectangle formed by the clamping point 7fl, the two springs 7 and their connection, so that the segment G is deflected parallel to itself against the leaf springs 7 and their restoring force. In this case, an apparent deflection path is sufficient to engage the segments 6

-11 with the internal profiling of the leaf spring system and 4. The deformation is shown in Fig. 2, 6 and 11 in a slightly exaggerated manner.

According to Figures 2, 6, 7b and 11, the segment may be. 6 arranged approximately-? in the middle between the two springs 7, according to Figure 12, as a continuation of one of approximately parallel to the central axis with the springs of the ester springs. preferably in parallel in the radial direction furthest from the outwardly extending spring

According to FIG. 12, the latter arrangement has the advantage that the spring 7 lying radially inward can lie at the height of the axis of rotation of the pressure roller 3, so that the entire gearbox 10 obtains the smallest possible radial dimension than the teeth of the rotary bodies or rings 1 and 4. the teeth of the segments 6 are also approximately parallel to the central axis of the drive shaft 2 and the output shaft 12 (cf. FIG. 12), which is fixedly connected to the rotary ring 4, for example by a bell or a disc 11.

Thus, in the gearbox 10, instead of the planet wheels, the toothed segments 6 are predicted. The roller carrier 5 is fixedly connected to the shaft 2, thus rotating with this shaft. As the shaft 2 is driven, the profiled segments 6 insert the profiled segments 6 into the rings 4 and 4 by means of the roller 3.1 to 3.3. By the spring force of the leaf springs 7, the profiled segments 6 are then returned to the training from j to 1 bend. with several teeth both the fixed ring 4 and after one turn of the pulley carrier 5 around the ring 1, all the teeth are pushed by the pulleys 3 into the toothing of the rings 1 and 4, this against the return force of the springs 7. tooth difference compared to ring 1. 11 of the three pulleys 3, for example, three extra teeth are provided in the movable ring 4 in FIGS. Movement of the output ring 4 occurs as the ring 4 outstrips the fixed ring with each rotation of the pulleys 3.

If the outlet ring 4 were provided with the same number of completely identical profiles or teeth as the ring 1, there would be no relative movement when the pulleys 3 were circulating between the two rings 4 and 4. Output ring 4

-12 which has a profile match with a fixed ring

i. stops. If the number of teeth is smaller, there is a reverse rotation. Because of the rotation of the pressure rollers 3, the individual segments move in a radial direction, while adjacent segments are arranged more inwardly, small graduations occur between these segments located in different radial positions. This is hardly noticeable in the exemplary embodiment in the circumferential direction of the narrow segments 6-1 of Figure 1 having only one tooth. Also in the relatively narrow segments 6.2 according to Figure 3, this graduation is only slightly noticeable, since the roller 3 still moves more or less radially than in Figure 1 at the same time more segments 6. However, which is wider in the circumferential direction, individual scales and approximately the magnitude of radial displacement of individual segments 6.3. In order to reduce or compensate for any resulting shock and noise, it is envisaged in the exemplary embodiment according to FIGS. 4 and 5 that a contact ring 8 is arranged between the pressure element, i.e. between the rollers 3 and the ring 4 facing away from the segments 6. contact surface for deflecting the pulley 3.

E> ude mentioned that count. The number of teeth on a single segment is all the greater the greater the number of teeth on the rotary body or the ring 11 and 4.

A very special embodiment of the gearbox 10 according to the invention is indicated schematically in Figures 8 and 9. This embodiment foresees that for a portion of the circumference of the rotary ring 4 the number of teeth equals the number of teeth on the same part of the circumference of the fixed rotary body or ring 1 and the circumference of the rotatable rotary body or ring 4 have different numbers of teeth. In FIG. 8, a rotating ring 4 is shown in which the parts Z 11, Z 13 and Z 15 have the same or identical number of profiles or teeth as the same angular ranges of the fixed ring 1. that is, when the pulley 3 runs these parts, there is no rotational movement on the output shaft 1 and 12.

-13 is as if in a delayed phase. Thus, at a constant speed of the drive shaft 2, a step rotation of the output shaft occurs

12th

Z 14 and Z of the ring with the greater help of Figure 9. Parts Z 12 of the tooth less and parts Z 11, Z 13 of the same angular ranges of fixed e circumference of the movable outlet with a smaller number of teeth with parts of fixed ring χ. The team is formed

The variation is shown from 16 to have. half a half of the tooth more than the ring 1, so that in direction 4 the number of teeth alternates with the number of teeth relative to the oscillating movement on the output shaft 12 or other output device because the movable ring 4 rotates alternately in different direction while the drive shaft and driven the movable rotary body or ring 4 may thus have. in a certain angular range, fewer teeth than the opposite circumference of the fixed rotary body or ring

1 to achieve some modified output movement.

Here, it is expedient to foresee circumferential ones with different circumferential ones with several rings 1. in the transition portion with an equal number of teeth by the number of teeth, or in the transition portion with the number of teeth. To some parts with less teeth than for the fixed transmission function of the tooth transitions, which has or will produce a value different from zero in the first derivative. The transfer function can ensure that the coefficients of the axis change from one to the other. This occurs when the profile difference is divided by sine to maximum or again to zero. number of teeth or function deviation, for example, for the entire number of teeth of a region. This creates a uniformity in the vicinity of the transition between the drive ring and the output ring. Thus, for the continuous movement introduced on the drive shaft 2, a continuous transmission of the axes of 11 y b is obtained at the output 4 by changing the ring.

1a _: internal toothing 4 Bending Sh. art - stop or

Bo 1 foreseeing segments 6 has also been mentioned more or less that a co. It is possible to anticipate the circulation. of the nozzles for the pressure in the examples of the lid design for radial adjustment

3. For non-contact control, as a pressing element one medium, in particular compressed air,

14 which rotate around the segments 6 and which, with their media beam, transfer the segments against their mounting on the springs to the engagement position. Once the nozzle has passed through the segments 6 to be pushed in, the segments 6 are adjusted by the springs 7 again. back, i.e. out of shot.

Also, a non-contacting and thus low or no friction design arises when an electromagnetic compression device is contemplated in which the magnets, for example, form only the segments 6, which can be moved by a magnet circulating as a pressing element on their side facing away from the rotating body. repel the ring when aligned with the same poles against the resilient fit and deflect. from the normal position and thereby bringing into engagement with the rings.

For simple assembly by rotary bodies or a relatively large number of segments 6, it is advantageous if the parallel springs or leaf springs 7 are connected together, in particular in the clamping region 7 napríklad, for example they are in one piece, i.e. they have a connecting ring or connection ring

Thereby, the springs 7 and the segments 6 supported by them can be adjusted. independently of one another, however, they are joined together at the clamping point 7fi and can therefore be a ring.

In Figures 1.0 and 11, an example of a gearbox 10 is shown as a variation i at least v, in which the pressure rollers 3 also have a toothing which engages a corresponding toothing on the segments 6 during the circulation and during shaking and the segments 6. This can be achieved the soft and smoother circulation of the pulleys 3, although there is always a degree of separation between the pushed and unloaded segments 6. This is mitigated by the toothing and greatly compensates.

A particular embodiment of a spring system with two leaf springs 7 is shown in FIG. 7. It can be seen that the two springs 7 are shaped at least two meters 7C approximately into S-shape, with portions of their length running parallel to each other. According to FIG. 7b, they are arranged in a mirror-symmetrical manner with their measurements and towards each other, the ends of these springs 7 connected to each other and to the respective segment 6 being closer to each other than the clamping ends. This causes a relatively small

The axial length of the springs 7 has doubled them, thus producing a softer effective spring length. P r is a th e axial length of the gearbox 1 1 or a reduction in the deflection resistance of the segments. 6, and in particular with reduced spatial ratios, efficiency improvements. In the embodiments, three equally distributed circumferential pulleys 3 are provided as pressure elements. It would also be possible to provide such a gearbox 10 also with one such pressure element or at least two diametrically opposed elements. In all these cases they may be. these thrust elements mounted or supported on a driving shaft 2 of rotating uprights or carriers 5.

If these thrust elements or pulleys 3 have an external toothing, as discussed above with reference to FIG. 10, the accuracy, the displacement of the individual segments 6 and thus their introduction into the toothed rings χ and 4 will be improved simultaneously. will support. The transmission 10 with two, on the periphery profiling or bodies, in particular rings, by means of which the pressing elements by this toothing still have internal or external toothing having round spheres 1 and 4, has a drive shaft 2.

in particular the pulleys 3, each of the radially adjustable segments 6, which are independent of one another, are brought into engagement with the associated first-mentioned round-shaped profiling. Because these spherical bodies or these rings 1 and 4 have teeth and one ring is a relative displacement

each other from l i dream count you fixed and second diam puppy is a rotary or big at the same time conversion to poiii or 1 a For good led by e and before s

independent movement of the segments 6 without axially arranged guide rings or without an individual connection of the individual segments 6 into the chain of segments it is provided that in the circumferential direction, the adjacent segments 6 are arranged individually and independently of each other on two parallel, firmly mutually streaky or The springs 7 are able to deflect the return force of the springs in which they are arranged in a radial direction in succession, but their greater width is directed in the circumferential direction. That may be. segments 6 biased to or against the spring 7

-16 parallel to each other and the lacquer to convert precise movement into engagement and thus adjusting movement on the rotating spherical body or ring 4 with high efficiency-17-

Claims (3)

PATENT P RENT -.1.8 the connection of both springs (7) is arranged or fixed segment (6) provided with toothing. Gearbox according to one of Claims 1 to 2, characterized in that the segment (6) is both springs (7) or extends approximately parallel to the central one axis, in particular the spring, which in the radial direction u 1 is moved to the outside. u s po r i a d d i d i n i n i n i n i s, 4. Gearbox with impellers 3, characterized by t or rings (1, 4) and teeth approximately parallel to the center and output shaft (12). according to one of claims 1 to 1, characterized in that? the teeth of the rotary bodies of the segments (6) are arranged on the axis of the drive shaft (2) Gearbox according to one of Claims 1 to 4, characterized in that between the thrust element, in particular during the starving and revolving motion, the rolling roller (3) and the rotating bodies or rings (1,4) facing away of the segments (6), a resilient contact ring is provided. 6. An impeller according to one of claims 1 to 4, characterized in that the number of teeth on each segment is all the greater the number of teeth on the rotating bodies or rings / 1. 4 /. 7. Gearbox having the preceding claims, characterized in that in a certain part of the ring (4), the number of teeth in the corresponding ring (1) and the pulleys is in particular according to one characteristic of the circumference of the body or equal to the number of teeth of the portion of the periphery of the fixed rotary body, or that the adjacent portions of the circumference of the rotary rotary body or the ring have different numbers of teeth or pitch. u py z u bov. -19-: and · :. 8. A gearbox having a circumferential ring or more. i ¾ h 1 č s s ¾. circulatory i s c and s and f; ý m / 4 / m or v / 1 /. in particular according to claims 1 to 7, that the movement in the rotary body determines in its angular ranges its teeth in other angular ranges less teeth than the circumference of the fixed rotary body or ring 9. Gearbox with rotating pulleys 8, characterized in that it is from part of the circuit to the part of the circuit according to claim 1, characterized in that in the transition area with the same number of teeth with different numbers of teeth or in the transition For example, in the regions of parts of circuits with different numbers of teeth, the transition function of the gear transition is envisaged, which at least in the first derivative has a value different from zero or does not cause shocks. 10. The impeller gear according to claims 1 to 9, characterized in that at least one circulating roller or at least one nozzle for the pressure medium, in particular a jet of compressed air flowing around the segments, is envisaged as the pressure medium. and these in turn push the successively extending nozzle therethrough against their resilient suspension into the engagement position. 11. The gearbox 10 is characterized by a magnetic roller with a roller, in particular according to one or more of the claims 1 to be considered in a shaking device in which the segments (6) are designed as magnets with a magnet. circulating as a thrust element on their side facing away from the rotating body at opposing poles, it repels and deflects against its resilient yoke. 12- A rotary-roller gear unit, in particular according to claims 1 to 11, characterized in that the gearbox is equipped with a roller. characterized in that the parallel springs or leaf springs (7) are joined together in one clamping ring (7A) in their clamping region (7A). -2013. Gear units with rotary pulleys, in particular according to claims 1 to 12, characterized in that the thrust rollers (3) have a toothing, engage the boring during the circulation and at the same time of the segments (6) with corresponding toothing on the segments. / 6 /. Gearbox with impellers in particular according to claims 1 to 14 13, characterized in that the springs (7) are shaped approximately in the shape of an S or in a direction aligned to each other from the interconnected ends at 15. Gearbox with running gear 14, characterized in that the two rods have at least two changes of direction (7C / Z), which are changed in a symmetrical manner and with a segment (6) closer than the clamped ends. By means of rollers, in particular according to claims 1 to 2, at least two circumferentially disposed circumferentially distributed pressing elements are provided or mounted or mounted in particular by a rotatable drive shaft (2) rotated one hundred times or three evenly onto the rollers (3). which are stored on the common and / or nose i coe h / 5/16. In particular, according to one of the preceding claims, pulleys according to one s y n and c n j u c Art rings / 1, 4 / alto or blades they are sweeping from out P r i 1.1 a č t toothing i that smoldered outdoors element and 1 ebo accessory k 1adka. íí / ^ - tr o ΙοζϊΓ. 2 J 1. The gearbox 1, with the smallest diameter of the first spherical body fixed by impellers (10) with two spherical rings (1/4) having on the inner circumference a profi 1 toothing, pr wherein the second spherical body is arranged parallel and coaxial to the first spherical body and is mounted relative to this rotational and number. toothing is different in the profiling of the two spheres, with successively profiling or toothing of the spheres in the printable segments (6.1, 6.2, 6.3, 6.D), which have a serration-matching toothing or toothing and thus act simultaneously on the toothing of the fixed and rotatable spherical body and with at least one of the segments (6) facing away from the spherical bodies and at the same time facing each other in a radial direction parallel to the spherical bodies constituting the thrust element, whereby the spherical spheres can be rotated return force segments again. releases from gearing, s and t and t. 6.1) (a) independently of each other on two parallel fixed or intermittent spring or leaf springs (7) and can be deflected against their restoring force, the two springs (7) being movable and in which direction 6.2 6th side-by-side arrangement is arranged in radial order in a row. whether or not the respective segment (6) can be deflected such that the respective segment (6) can be deflected. parallel to each other. 2. The impeller gear unit according to claim 1, characterized in that the impeller is equipped with an impeller. characterized in that the two springs (7) arranged in the radial direction for holding the segments (6) are connected at a distance from the clamping points (7J) by a rigid transverse rod (7B) or by the actual body of the segment (6). (7R) extends in particular in the radial direction and that in the axial direction next to the transverse rod of the incis (7E ') or 3 / ο ο CC ι QC Cľ> Ο ~ υ ~ 2Χ <2 £ θ Γ% 6έ- «Γ f  oktr ¾ ε e