WO2016029907A1

WO2016029907A1 - Cone friction-ring transmission, use of a reduction transmission, and method for setting the friction ring of a conical friction ring transmission

Info

Publication number: WO2016029907A1
Application number: PCT/DE2015/100359
Authority: WO
Inventors: Ulrich Rohs
Original assignee: Ulrich Rohs
Priority date: 2014-08-28
Filing date: 2015-08-28
Publication date: 2016-03-03

Abstract

The invention relates to a cone friction-ring transmission, comprising an input cone and an output cone, which are oriented in relation to each other with parallel cone axes in such a way that the input cone and the output cone are spaced apart by a gap, wherein a friction ring rotates in the gap, which friction ring is supported in an adjusting bridge in such a way that the friction ring can be displaced axially along the gap, which adjusting bridge can be axially displaced freely along a guide bar, which can be set in the setting angle thereof in relation to the cones by an adjusting drive via a reduction transmission by means of an attachment. According to the invention, high reduction ratios can be enabled in a structurally simple and compact manner if the reduction transmission comprises a driven planet carrier bearing at least one planet, an outputting ring gear or sun gear, and a housing-fixed ring gear or sun gear, if both the outputting ring gear or sun gear and the housing-fixed ring gear or sun gear mesh with the at least one planet, and if the number of teeth of both ring or sun gears differs by less than 3 teeth.

Description

Bevel friction ring gear, use of a reduction gear and method for adjusting the friction ring of a conical-friction ring gear

The invention relates to a conical friction ring transmission, a use of a

Reduction gear and a method for adjusting the friction ring of a conical friction ring gear. In particular, the invention relates to a conical friction ring gear comprising an input cone and an output cone, which are aligned with a gap with parallel cone axes aligned with each other, wherein in the gap a friction ring rotates axially along the gap is mounted displaceably in a Verstellbrücke axially free along a Guide rod is displaced, which can be made by means of an approach via a reduction gear by an adjusting drive in their angle of attack with respect to the cone. The invention also relates to the use of a reduction gear for the employment of a friction ring of a conical friction ring gear. In particular, the invention further relates to a method for adjusting the friction ring of a conical-friction ring transmission.

[02] Reduction gears in general, and in particular planetary gear, as

Serving reduction gear, on the one hand sufficiently well known from the prior art. On the other hand, reduction gears are also known per se, in which the reduction ratio is 30: 1 or more, in this regard, in particular worm gear enable compact reduction gear with a very high reduction ratio. However, such worm gears, as they are known, for example, from WO 2004/033934 A2 or from WO 2009/068012 A2, prove to be relatively expensive, in particular for fine actuations, in particular by conical friction ring gears, for example, as described in these publications or also in US Pat WO 2006/012892 A2 are known, with respect to the position of the friction ring and in particular with respect to its angular position, especially when this friction ring can be positioned only about its angular position and otherwise freely axially position.

It is therefore an object of the present invention, a conical friction ring gear, a

Use of a reduction gear and a method for employment of the friction ring of a conical-friction ring gear to provide, in which the reduction gear structurally simple and compact high reduction ratios possible.

The object of the invention is by conical friction ring, uses a

Reduction gear and method for adjusting the friction ring of a Conical friction ring gear with the features of the independent claims solved. Further, possibly also independent thereof, advantageous embodiments can be found in the subclaims and the following description.

Thus, in a conical friction ring transmission comprising an input cone and an output cone, which are aligned at a gap with parallel cone axes aligned with each other, wherein in the gap a friction ring rotates axially along the gap displaceably mounted in a Verstellbrücke axially is freely displaceable along a guide rod, which can be made by means of an approach via a reduction gear of an adjustment in their angle of attack with respect to the cone, structurally simple and compact designed the reduction gear, if this a driven, at least one planet carrying planet carrier, an abortive Hollow or sun gear and a housing-fixed hollow or sun includes, if both the abortive hollow or sun gear and the housing-fixed hollow or sun gear mesh with the at least one planet and if the number of teeth of both hollow or sun gears by three or less Teeth is different. In such a reduction gear designed the abortive hollow or sun gear is rotated at every complete revolution of the planet carrier by exactly the difference of the teeth relative to the housing, which accordingly structurally simple and compact high reduction ratios possible. Accordingly, a method for employment of the friction ring of a conical-friction ring transmission, if this is characterized in that for the reduction of a rotational movement by means of a planetary gear at least one planet is driven by a planet carrier and with a housing-fixed hollow or sun gear and with an abortive hollow or sun meshes, the number of teeth of both hollow or sun wheels differing by three or fewer teeth, according to advantageous. The same applies to the use of a reduction gear for the employment of the friction ring of a conical-friction ring gear, which includes a driven planetary carrier supporting at least one planet, an abortive hollow or sun gear and a housing fixed hollow or sun gear, if both the driven hollow or sun gear as well the housing-fixed hollow or sun gear mesh with the at least one planet and when the number of teeth of both hollow or sun gears differs by three or fewer teeth

Although such reduction gear, for example, from DE 317 153, DE 40 26 886 AI, DE 10 2005 048 179 AI or from Meier, Bruno "arrangement of several epicyclic gears in planetary gears" (construction 13, 1961, Heft 2, pp. 67 to 69) are well known and are clearly Wolfromgetrieben, for example, in Klein, Bernd "The Wolfromgetriebe - a planetary gear design for high ratios (Feinwerktechnik & Messtechnik, 89, 1981, 4, 177-184) are set forth and have by definition an idler co-rotating web or planet carrier, to distinguish. However, for example, from DE 317 153, DE 40 26 886 AI, DE 10 2005 048 179 AI or from Meier, Bruno "arrangement of several epicyclic gears in planetary gears" (construction 13, 1961, No. 2, p. 67 to 69) known reduction gear for high torque or long travel paths, which plays no role in the employment of friction rings in conical friction ring gears, in which only the angular position of the friction ring is adjusted, here a few degrees, in particular less than 10 ° sufficient.

[07] Preferably, the number of teeth is at least one of the two hollow or

Sun gears more than 30, which then requires correspondingly high gear ratios. Likewise, even higher gear ratios, such as 40 teeth or more, can also be implemented thereby. It is understood that the aforementioned conditions preferably of both hollow or sun gears, so both of the driving hollow or sun gears and the housing-fixed hollow or sun gear can be met.

As immediately understood, the reduction ratio is particularly large, the smaller the difference in the number of teeth of both hollow or sun gears. In this respect, a difference of 1 results in particularly high reduction ratios, which may possibly result in balancing or stability problems which may make a difference between two teeth or even three teeth appear to be advantageous. With more than three teeth difference, however, causes the consequent reduction of the reduction that the number of teeth of the hollow and sun gears must be so large as compensation that it is likely that a corresponding reduction gear is not sufficiently compact builds.

For reasons of stability of the arrangement, it is particularly advantageous if the

Difference in the number of teeth corresponds to the number of planets. The planets are then positioned according to the number of teeth and the resulting positional overlap of the respective teeth of the two hollow or sun gears.

In a structurally simple and compact manner can cumulative or alternatively by a method for employment of the friction ring (10) of a conical-friction ring transmission enable a reduction of rotational movement by means of a planetary gear, if at least one planet is driven by a planet carrier and with a fixed housing Hollow or Sun gear with a reduction ratio of x: y and with a driven hollow or sun gear with a reduction ratio of (x ± z): y interacts, where x is the value 30 more and z is 3 or less. Likewise, accordingly, a conical friction ring transmission comprising an input cone and an output cone aligned with a gap with parallel cone axes aligned with each other, wherein in the gap a friction ring rotates axially along the gap displaceably mounted in a Verstellbrücke axially free along a guide rod is displaceable, which can be made by means of an approach via a reduction gear of an adjustment in their angle of attack with respect to the cone, a planetary gear or a reduction gear, which can provide high reduction ratios in a structurally simple and compact manner, if the corresponding planetary or Reduction gear comprises a driven, at least one planet bearing planet carrier, a driven hollow or sun gear and a housing-fixed hollow or sun gear, if both the driven hollow or sun gear and the housing-fixed hollow or sun gear interacts with the at least one planet and when the planet interacts with the housing fixed hollow or sun gear with a reduction ratio of x: y and with the driven hollow or sun gear with a reduction ratio of (x ± z): y, where x is the Value is 30 or more and z is 3 or less.

[11] In this context, x or (x ± z) denote the contribution of the hollow and

Sun gears to the reduction ratio, while y denotes the contribution of the planet (s). This contribution can be made, for example, by the number of teeth, for example in the case of a positive connection, or by the radii, for example in the case of a frictional connection. It is understood that by the fact that the planet interacts with both hollow or sun gears, the amount y of the planet or auszuschürzt from the total translation, unless it interacts with the two hollow or sun gears with different amount y. Accordingly, the number of teeth or the radius of the planet initially only play a secondary role.

It is understood that the interaction between the two hollow or

On the other hand, sun gears on the one hand and the planet on the other hand can not necessarily be form-fitting but may also be non-positive, as long as there are appropriate reduction or transmission ratios between the planets on the one hand and the hollow or sun gears on the other hand. It is understood that a good controllable force and torque flow can be ensured by the transmission by a positive connection or by a combing and thus by a configuration of the transmission as a gear transmission. In particular, you can Also, the reduction ratios in the desired manner can be defined precisely precisely by the respective number of teeth easily.

It is understood that preferably z has a value of 1, wherein - in the case of a frictional interaction between the planet and the two hollow or sun gears - z can also assume values closer to zero. This then has a corresponding effect on the reduction ratio increasing.

Preferably, the value y of the planet is more than 6. Accordingly, it is advantageous if the planet has more than 6 teeth, so that the interaction between the planet and the elevation or sun gears or the concrete shape of the gears or Teeth must not be too extreme in the respective design or physical requirements must be configured.

If the number of teeth of the planet less than 20 or y has a value of less than 20, so the planet and thus also the overall planetary gear can be structurally relatively compact, since the planet does not have to be designed too large.

The at least one planet can with both hollow or sun wheels with the same

Comb module, which structurally allows easy implementation, since possibly on a shared structure of the planet, whose first planetary part specifically for one of the two hollow or sun gears and the second planetary part for the other of the two hollow or sun gears are specially designed can be omitted, with a correspondingly divided configuration, if necessary, for other reasons, for example, for reasons of a particularly low-loss and very play-free connection, may be advantageous.

Combines the planet with the same module with two hollow or sun gears, it may be advantageous if the planet meshes with two hollow or sun gears each with different profile displacement, so that the different number of teeth or the different reduction ratios account can be worn, which is immediately understandable that the different profile shift with increasing number of teeth of the two hollow or sun wheels possibly less important, since the differences between the two hollow and sun gears are getting smaller.

The at least one planet, apart from the difference in the number of teeth between the two hollow or sun gears with the same under- or gear ratio with two hollow or sun gears comb, which is a particularly simple constructive Design of the overall arrangement allows. On the other hand, it goes without saying that, if necessary, an additional reduction or transmission can also be implemented in the transmission via the planet by the planet meshing with different reduction ratios or gear ratios with both hollow or sun gears.

[19] In particular, the solutions described above are suitable for the

Angular position of the friction ring of a conical-friction ring gear, in particular when the friction ring is guided freely axially displaceable per se and therefore can move independently by the angular adjustment along the friction cone.

[20] It is understood that the features of the solutions described above or in the claims can optionally also be combined in order to implement the advantages in a cumulative manner.

[21] Further advantages, objects and features of the present invention will be explained with reference to the following description of exemplary embodiments, which are also illustrated in particular in the appended drawing. In the drawing show:

Figure 1 shows the adjusting device of a conical-friction ring transmission in a perspective plan view; Figure 2 is a schematic side view of the conical friction ring gear for the adjusting device of Figure 1;

3 shows a schematic section through a suitable for the adjusting device of Figure 1 reduction or planetary gear;

Figure 4 shows a schematic section through the arrangement of Figure 3 perpendicular to

Drawing plane in Figure 3;

FIG. 5 shows a second reduction or adjustment device suitable for the adjusting device according to FIG.

Planetary gear in a similar representation as Figure 3;

Figure 6 shows the arrangement of Figure 5 in a similar representation as Figure 4;

7 shows a third suitable for the adjusting device of Figure 1 reduction or

Planetary gear in a similar representation as Figures 3 and 5;

Figure 8 shows the arrangement of Figure 7 in a similar representation as Figures 4 and 6;

9 is a fourth for the adjusting device of Figure 1 suitable reduction or

Planetary gear in a similar representation as Figures 3, 5 and 7;

Figure 10 shows the arrangement of Figure 9 in a similar representation as Figures 4, 6 and 8;

11 is a fifth for the adjusting device of Figure 1 suitable reduction or

Planetary gear in a similar representation as Figures 3, 5, 7 and 9;

Figure 12 shows the arrangement of Figure 11 in a similar representation as Figures 4, 6, 8 and 10; 13 is a sixth used for the adjusting device of Figure 1 reduction or

Planetary gear in a similar representation as Figures 3, 5, 7, 9 and 11; and

14 shows the arrangement according to FIG. 13 in a representation similar to FIGS. 4, 6, 8, 10 and 12.

The conical friction ring gear 11 shown in Figures 1 and 2 comprises an input cone 12 and an output cone 13, which are aligned around a gap 36 spaced parallel cone axes to each other, wherein in the gap 36 of the friction ring 10 surrounds the input cone 12 encompassing.

The friction ring 10 is mounted axially displaceable along the gap in an adjustment bridge 14, which in turn is axially displaceably mounted in a cage 16 via a guide 15, wherein the guide 15 along two guide rods 17 which are arranged parallel to the gap 36 and are fixed to a support 18 of the cage 16, is axially displaceable. It is understood that in different embodiments, for example, only one guide rod can be provided, so that can be dispensed with a suitably designed support 18, if necessary, entirely. Possibly, in such an embodiment, then the guide 15 is designed such that it comprises a rotation of the Verstellbrücke 14 to the individual guide rod 17, which - depending on the concrete implementation - by the interaction between the guide 15 and the guide rod 17 or by a structurally provided elsewhere rotation lock can be realized.

The cage 16 is mounted via a pivot bearing 20 in a housing 19 of the conical-friction ring gear 11, so that the angle of the Verstellbrücke 14 with respect to the cones 12, 13 are changed and incidentally, the friction ring 10 itself can move freely along the cone axes , This arrangement has the advantage that over the angle of incidence of the cage 16, the friction ring 10 can be made at an angle to a vertical plane on both cone axes, the friction ring 10 then depending on the size and direction of the angle independently by the cones 12, 13th driven axially along the gap 36 migrates. Under certain circumstances, this migration takes place very rapidly, since it has been shown that the friction ring 10 is able to migrate from one axial end of the conical-friction ring transmission 11 to the other axial end of the conical-friction ring transmission 11 at seven conical revolutions. This requires an extremely rapid adjustment of the friction ring 10 and thus the transmission ratio of the conical friction ring 11, which is extremely difficult to achieve with other methods. However, this requires a very accurate employment of the angle. For this purpose, the conical-friction ring gear 11 on the support 18 on a lug 21 on which a Anstellstange 22 engages, which in turn via an eccentric sleeve 23 which is connected to the eccentric 24, is controlled. This eccentric 24 is located on a reduction gear 1 and planetary gear 9, as shown in Figures 3 to 14, said reduction gear 1 or planetary gear 9 via an adjusting drive 31, which is designed as a rotating motor and on the drive shaft 6 attacks, can be hired. In the present embodiment, the reduction gear 1 and planetary gear 9 of Figures 13 and 14 are used. In a different embodiment, if the carrier 18 is dispensed with, the lug 21 may also attach to another location of the cage 16, which may then no longer look like a cage; For example, on a guide rod itself. It is understood that the projection 21 may also be formed in one piece with the assembly to which it is attached. Also, if necessary, the projection 21 may be connected directly to the eccentric bushing 23.

The reduction gear 1 or planetary gear 9 shown in Figures 3 to 14 each comprise a driven via a drive shaft 6 planet carrier 3, which carries a planet 2, which with both a driven hollow or sun gear 4 and a housing-fixed hollow or sun gear 5 meshes.

Here, the reduction gear 1 and planetary gear 9 each comprise a

Housing 28, which is pierced by the drive shaft 6 and an output shaft 7 and within which the planet carrier 3, the planet 2 and the hollow or sun gears 4, 5 are arranged.

In this case, the abortive hollow or sun gear 4 is connected to the output shaft 7, so that a drive on the drive shaft 6 or a corresponding rotational movement on this drive shaft 6 cause a corresponding output or a corresponding rotational movement on the output shaft 7.

[29] In the embodiments illustrated in FIGS. 3 to 14, the hollow or sun wheels 4, 5 differ by the number of their teeth 8, whereby in all these exemplary embodiments this difference amounts to exactly one tooth 8. This requires that the two hollow or sun gears 4, 5 - as can be seen in particular in Figures 4, 6, 8, 10, 12 and 14 - in one area almost exactly superimposed teeth 8, while the teeth 8 in the opposite Then overlap area. It is understood that with a difference in teeth 8 of two teeth 8 or three teeth 8 corresponding to two or three areas occur in which the teeth 8 are aligned almost identically. In these areas can then be arranged without further planet 2.

In two or three planets or at tooth number differences of 2 or 3, it can be assumed that the planet 2 and the planet carrier 3 can be balanced without further ado, while this is initially not the case with only one planet 2 per se. For this reason, the arrangements according to Figures 3 to 14 each have a counterweight 27 on the planet carrier 3, so that the latter is balanced in a suitable manner or can be balanced.

[31] Moreover, in all embodiments, the planet 2 is over one

Planet shaft 26 mounted on the planet carrier 3, it being understood that in other embodiments, if appropriate, other bearings of the planet 2 or the planet on the planet carrier 3 are conceivable.

In the embodiment shown in Figures 3 and 4 are both hollow or

Sun wheels 4, 5 configured as sun gears. Here, the housing-fixed hollow or sun gear 5 has 60 teeth and the abortive hollow or sun gear 4 61 teeth. The planet 2 meshes with two hollow or sun gears 4, 5 with the same module and substantially the same ratio, but it with two hollow or sun gears 4, 5 meshes with different profile shift to compensate for the difference of a tooth accordingly. It goes without saying that the number of teeth can correspondingly also be less than 60 and, in particular, moreover, whereby the question of the profile shift possibly loses significance, especially with higher numbers.

In addition, in this embodiment, the housing-fixed hollow or

Sun gear 5 via a spacer 25 by means not unnumbered screws on the housing 28 of the reduction gear 1 and planetary gear 9 attached.

Also, in the embodiment shown in Figures 3 and 4, the counterweight 27 is relatively slim and narrow, so that in this way the space for the entire reduction gear 1 and planetary gear 9 is not unnecessarily increased.

[35] In the embodiment shown in Figures 5 and 6, the housing is fixed

Hollow or sun gear 5 designed as a ring gear and formed directly in the housing 28. The abortive hollow or sun gear 4, however, is also formed in this embodiment as a sun gear. In addition, in this embodiment, the counterweight 27 designed axially shorter, so it does not appear in the schematic sectional view of Figure 6. However, the counterweight 27 extends over a much larger angular range in order to be able to provide mass in this way. Otherwise, the embodiment illustrated in FIGS. 5 and 6 corresponds to the exemplary embodiment according to FIGS. 3 and 4, so that further explanations in this regard are dispensed with.

[36] In the embodiment shown in FIGS. 5 and 6, the abortive is

Hollow or sun gear 4 provided with 61 teeth, while the housing-fixed hollow or sun gear 5 has 60 teeth. The planet 20 meshes with two hollow or sun gears 4, 5 with the same module and with substantially the same reduction ratio, a different profile displacement is also provided here, compared to the embodiment of Figures 3 and 4 in view of the very different radii of the two hollow - or sun gears 4, 5 correspondingly larger fails.

In the embodiment shown in Figures 7 and 8 are both hollow or

Sun wheels 4, 5 designed as ring gears, so that the planet 2 and also designed as a substantially circular mass counterweight 27 rotates within both ring gears.

In deviation from the two embodiments according to Figures 3 to 6 in the embodiment shown in Figures 7 and 8, the abortive hollow or sun gear 4, which is provided with 60 teeth 8, axial output s side and the housing fixed hollow or sun gear 5, which is provided with 61 teeth 8, arranged axially on the drive side.

[39] In addition, in this embodiment, the planet 2 meshes with the same module with two hollow or sun gears 4, 5 also with substantially the same reduction ratio. Again, a slightly different profile shift is provided.

[40] Similar to the arrangement of Figures 5 and 6 is in the embodiment according to

Figures 9 and 10, the housing-fixed hollow or sun gear 5 is formed as a ring gear, while the abortive hollow or sun gear 4 is formed as a sun gear.

[41] In deviation from the embodiment of Figures 5 and 6 and similar to the embodiment of Figures 7 and 8, the abortive hollow or sun gear 4 is provided on the axial output side and the housing fixed Hohloder sun gear 5 axially on the drive side in the embodiment of Figures 9 and 10 , Also, the planet carrier 3 enters Counterweight 27, which approximately corresponds to the shape of the counterweight 27 of the embodiment of Figures 5 and 6.

[42] Unlike the embodiments described above, in the exemplary embodiment according to FIGS. 9 and 10, the planet 2 is formed in two parts with a planetary part 29 and a planetary part 30 which are respectively adapted to the particular configurations of the hollow or sun wheels 4, 5. Thus, the planetary part 29 meshes with the abortive hollow or sun gear 4, which has 61 teeth in this embodiment, while the planetary part 30 meshes with the housing-fixed hollow or sun gear 5, which has 60 teeth in this embodiment. Due to the corresponding division of the planet 2, it is possible that the planet 2 meshes with each of the hollow or sun gears 4, 5 adapted module and possibly with the same profile shift.

[43] In this embodiment, the combing is done with substantially the same

Reduction ratio, since ultimately the number of teeth of the planetary part 29 corresponds to the number of teeth of the planetary part 30. However, it is immediately understandable that in different embodiments here also on the planet 2 and its two planetary parts 29, 30, a change in the number of teeth and thus an adapted translation or reduction ratio can be selected.

[44] The fifth reduction gear 1 shown in Figures 11 and 12, respectively

Planetary gear 9 is similar in construction mainly to the reduction gear 1 and planetary gear 9 shown in Figures 3 and 4, but directly to the drive shaft 6, a drive gear 35 is placed, in which a driven by a drive motor 33 driving pinion 34 engages.

The drive motor 33 is on the housing 28 of the reduction gear 1 and

Planet gear 9 attached, so that the arrangement is relatively compact.

As can be seen immediately, the reduction ratio of the reduction gear 1 or planetary gear 9 is still influenced and in particular by the number of teeth of the drive pinion 34 and the drive gear 35 and by the choice of the gear ratio between the drive pinion 34 and the drive gear 35 be increased even without a considerable space loss is associated with this.

[47] Even more compact, especially in the axial direction - ie parallel to the drive shaft

6 or to the output shaft 7 - builds the reduction gear 1 and planetary gear 9 after Figures 13 and 14, which in the present case in the conical friction ring 11 according to Figurl and 2 is used, with only minor structural deviations and the reduction gear 1 or planetary gear 9 of the other embodiments can be used here without further ado, and in which the drive gear 35th is arranged on or on the planet carrier 3, so that the drive pinion 34 meshes directly with the planet carrier 3. Thus, the drive motor 33 can be at least partially disposed in the housing 28 of the reduction gear 1 and planetary gear 9, which reduces the number of movable assemblies passing through housing breakthroughs to a minimum, especially since the drive shaft 6 only serves to support the planet carrier 3 , where appropriate, a different form of storage or additional storage types may be provided here.

[48] In this sixth reduction gear 1 or planetary gear 9 according to figures

13 and 14, the housing 28 is selected for reasons of a shapely and compact appearance in the axial section around, but eccentric to the output shaft 7 and the drive shaft 6. It is also conceivable, a corresponding circular in axial section housing to the output shaft 7 and the To select drive shaft 6, however, which leads to a correspondingly larger housing, where appropriate, the additional space for other modules, such as an electronic control unit, a battery or a battery or the like can be used. On the other hand, the housing in axial section can also substantially follow the shape of the planetary carrier 3 and only have a bulge for the drive motor 33, which then leads in axial section to a bulge, as can be seen in the region of the drive motor 33 in FIG.

[49] The three embodiments, which are shown in Figures 3, 4, 9, 10 and 13, 14, have an eccentric 24, which, however, need not necessarily be provided. However, these eccentrics 24 shown by way of example in FIGS. 3, 4, 9, 10 and 13, 14 serve for the angular adjustment of a friction ring 10 of a conical-friction ring transmission 11, as illustrated by way of example in FIGS. 1 and 12. For such use, the eccentric 24 is advantageous. For other uses, accordingly, another connection element may be provided, which is adapted accordingly. This may, for example, as exemplified in the embodiment of Figures 5 and 6, a corresponding flange 32, while omitted in the embodiments shown in Figures 7 and 8, 11 and 12 on an already attached separate connection element, wherein such a connecting element in particular, for example, a flange 32 or an eccentric 24, if necessary Of course, it can be supplemented or a connection of an acting with the reduction gear 1 change assembly with the abortive hollow or sun gear 4 and with the output shaft 7 can be done in other ways. It is understood that, if appropriate, corresponding connections or connecting elements can also be selected on the drive shaft 6 or, with regard to the driving planet carrier 3, as required, with slightly different embodiments.

[50] This arrangement allows a particularly compact design with excellent reduction ratios and a very precise control.

It is understood that corresponding reduction gear 1 or planetary gear

9 can also be used advantageously in congruently designed conical friction drives, if appropriate reduction ratios are desired. Likewise, it goes without saying that corresponding transmissions can also be used advantageously in other contexts for these reasons.

LIST OF REFERENCE NUMBERS

Reduction gear 20 pivot bearing

Planet 21 approach

Planet carrier 22 Anstellstange

abortive hollow or sun gear 25 23 eccentric bushing fixed to the housing hollow or sun gear 24 eccentric

Drive shaft 25 spacers

Output shaft 26 planetary axis

Tooth 27 counterweight

Planetary gear 30 28 Housing of the reduction gear

Friction ring planetary gear 1, 9

Bevel friction ring gear 29 planetary part

Input cone 30 planetary part

Output cone 31 Adjustment drive

Adjustment bridge 35 32 flange

Guide 33 Drive motor

Cage 34 drive pinion

Guide rod 35 Drive gear

Carrier 36 gap

Housing of conical friction ring gear

11

Claims

Claims:

A conical friction ring gear (11) comprising an input cone (12) and an output cone (13) spaced around a gap (36) with parallel cone axes aligned with each other, wherein in the gap (36) a friction ring (10) rotates axially along the gap (36) displaceable in an adjustment bridge (14) is mounted axially freely along a guide rod (17) is displaceable, which by means of a projection (21) via a reduction gear (1) by an adjusting drive (31) in its angle of attack with respect to the cones (12, 13), characterized in that the reduction gear (1) comprises a driven planet carrier (3) carrying at least one planet (2), a driven hollow or sun wheel

(4) and a housing-fixed hollow or sun gear (5), wherein both the driving hollow or sun gear (4) and the housing fixed hollow or sun gear

(5) with the at least one planet (2) mesh, wherein the number of teeth (8) of both hollow or sun gears (4, 5) differs by three or fewer teeth (8).

2. Use of a reduction gear for the employment of the friction ring (10) of a conical-friction ring transmission (11), characterized in that the reduction gear (1) has a driven, at least one planet (2) bearing planet carrier (3), an abortive hollow or sun gear ( 4) and a housing-fixed hollow or sun gear (5), wherein both the driven hollow or sun gear (4) and the housing-fixed hollow or sun gear (5) with the at least one planet (2) mesh, the number of Teeth (8) of both hollow or sun gears (4, 5) differs by three or fewer teeth (8).

3. Use according to claim 2 for the angular adjustment of the friction ring (10) of a conical-friction ring transmission (11).

4. conical friction ring gear (11) or use according to one of claims 1 to 3, characterized in that the number of teeth at least one of the two, preferably both, hollow or sun gears (4, 5) 30, preferably 40, or more ,

5. conical friction ring gear (11) or use according to one of claims 1 to 4, characterized in that the difference of the number of teeth (8) corresponds to the number of planets (2).

6. A method for adjusting the friction ring (10) of a conical-friction ring transmission (11), characterized in that for reducing a rotational movement of an adjusting drive (31) by means of a planetary gear (9) at least one planet (2) via a planet carrier (3) is driven and with a housing-fixed hollow or sun gear (5) with a reduction ratio of x: y and with a driven hollow or sun gear (4) with a reduction ratio of (x ± z): y interacts, where x is 30 or more and z 3 or less.

7. Anstellverfahren according to claim 6, characterized in that it serves the angular adjustment of the friction ring (10) of a conical-friction ring transmission (11).

8. Anstellverfahren according to claim 6 or 7, characterized in that at least one of the two hollow or sun gears (4, 5) meshes with the planet (2).

9. conical friction ring gear (11), use or Anstellverfahren according to one of claims 1 to 5 and 8, characterized in that the at least one planet (2) with the same module with two hollow or sun gears (4, 5) meshes.

10. conical friction ring (11), use or Anstellverfahren according to claim 9, characterized in that the at least one planet (2) with two hollow or sun gears (4, 5) meshes with different profile displacement.

11 conical friction ring gear (11), use or Anstellverfahren according to one of claims 1 to 5 and 8 to 10, characterized in that the at least one planet (2) apart from the difference in the number of teeth between the two Hohloder sun gears (4, 5) with the same reduction ratio with two hollow or sun gears (4, 5) meshes.

12. conical friction ring gear (11), use or adjusting method according to one of claims 1 to 5 and 8 to 10, characterized in that the at least one Planet (2) with different reduction ratio with two hollow or sun gears (4, 5) meshes.