WO2004068000A1

WO2004068000A1 - Bevel friction ring gearing

Info

Publication number: WO2004068000A1
Application number: PCT/DE2003/004164
Authority: WO
Inventors: Ulrich Rohs; Christoph DRAGËR; Werner Brandwitte
Original assignee: Ulrich Rohs; Drager Christoph; Werner Brandwitte
Priority date: 2003-01-17
Filing date: 2003-12-17
Publication date: 2004-08-12
Also published as: BR0307163A2; JP2006513384A; KR101098151B1; BR0307163B1; AU2003298065A1; KR20050101181A; DE10394040D2; CN1602397A

Abstract

A bevel friction ring gearing comprises a reverse gear, which is provided behind the output of the bevel friction ring gearing and which is connected in series to said bevel friction ring gearing.

Description

Kegeheibringgetriebe

The invention relates to a bevel friction ring gear in connection with a reverse run.

It is becoming more and more possible to make continuously variable transmissions (CVT) suitable for use in motor vehicles, in particular also in large series. Such a continuously variable transmission is also a bevel friction ring transmission, and it is an object of the present invention to provide a bevel friction transmission with a reverse gear.

As a solution, the invention proposes a bevel friction ring gear with a reverse gear provided behind the abrasion in a row with the bevel ring gear. Such an arrangement has the advantage, on the one hand, that the bevel friction ring gear can be operated with a constant direction of rotation, which is advantageous for the bevel friction gear with regard to its control or with regard to the adjustment of the friction ring. In addition, this arrangement also allows the reverse gear to be varied continuously.

In the sense of the present invention, the terms “in series”, “front” or “rear” refer to the flow of force in the drive train comprising a conical friction ring. In this respect, according to the invention, reverse gear in series on the side of the key facing away from the engine in the drive train. be drive ring gear provided. The reverse gear preferably comprises an epicyclic gear with at least one revolving gear frame, which supports at least one gear member of the epicyclic gear and can optionally be fixed with a housing or with a revolving gear member. Such an arrangement provides a reverse gear which, depending on requirements, can also be shifted during the rotation of the drive, that is to say also during the rotation of the bevel ring gear, in which the rotating gear member is optionally set accordingly, such a setting being made by suitable ones Couplings or synchronizations can be carried out carefully. Such a switchover option is particularly adapted to the requirements of a bevel friction ring gear, which in turn can only be varied in its gear ratio in a rotating state.

The reverse gear can in particular comprise a planetary gear with a planet, sun gear and outer gear, of which a first gear member is operatively connected to the output of the bevel friction ring gear and a second gear member is operatively connected to the output of the overall arrangement of bevel friction ring gear and reverse gear, while the third gear member with respect to a housing is at least one Degree of freedom can be determined. A planetary gear has the advantageous property that when one of the gear members - outer wheel, sun gear, planet, the latter should advantageously retain their self-rotating ability - the other gear members can continue to rotate and interact with one another in accordance with the resulting gear ratios. In particular, a corresponding determination of a transmission link requires a substantial change in the relative speeds between the remaining two transmission links, at least in terms of a degree of freedom, so that this change in the relative speed can be used to control the reverse gear.

The latter can be ensured in particular by the fact that the third gear element is the planet. If, in a planetary gear, the planets are fixed in terms of their rotational degree of freedom around the corresponding sun gear, then a direction of rotation between the outer gear and the sun gear follows immediately, whereby a corresponding reverse gear can be implemented if the respective forward gear is realized with a correspondingly moving planet, where - if necessary - through the planetary gear ratio ratios can be selected in a suitable manner.

The overall arrangement of the bevel friction ring gear and reverse gear is particularly compact if the first gear member is driven by a pinion rotating with the output cone of the bevel friction ring gear. Such an arrangement ensures a direct and direct flow of force or torque between the conical friction ring gear and the reverse gear, so that the overall arrangement is extremely compact and therefore extremely economical, particularly for modern power tools.

With regard to the latter requirement, it can be cumulatively or alternatively advantageous if the second gear member with the rotating frame one Differentials connected revolves. In particular in connection with the use in a motor vehicle, the main differential can be used advantageously, so that the reverse gear can be integrated directly into the differential, a compact design resulting in particular in connection with a bevel friction ring transmission regardless of the drive-side configuration of the reverse gear.

In particular with regard to normal operation, it is advantageous if the first and the second gear member can be fixed together. Depending on the specific configuration of the shifting processes with regard to the reverse gear, such an adjustment can also be advantageously used in other ways in order to fix a desired operating state of the planetary gear. The fact that the first and the second transmission element can be fixed with one another ensures a direct flow of force via the planetary gear, so that in this operating state the planetary gear works essentially without loss and the overall arrangement operates with an extremely high efficiency, in particular with regard to a pre-shift. Preferably, the optional fixing of the third gear and the first two gear members is coupled accordingly, so that the planetary gear rotates in a reliable manner in its states. In this regard, it is particularly advantageous if the first or second gear member is formed by the outer gear or sun gear of the planetary gear and the third gear member by the planets, since this enables the necessary interaction between the gear members to be implemented in a very simple and compact manner. This applies in particular if the second gear member is directly connected to the mating frame of a differential or is formed integrally therewith and / or the first gear member is driven directly by a pinion running with the output cone. With such a configuration, the overall arrangement, particularly in the case of conventional motor vehicle drives, which, owing to the large numbers and variations in the complementary motor vehicle classes, are each designed with drives in the same direction, can lead to an extraordinarily compact and therefore inexpensive transmission which can also be used in the case of very small vehicles.

To determine, for example, the rotating gear frame or the planet or the third gear member with respect to the housing with respect to a degree of freedom, the most varied types, such as friction or film connections, can advantageously be used for such a setting. In particular, friction connection connections have proven to be advantageous which enable a smooth transition which, depending on the specific embodiment, even enables the reverse gear to be switched on during the rotation. However, the latter is not advantageous in every application because of the relatively high forces and friction losses, so that in particular a starting clutch between the motor and the bevel friction ring gear can be advantageous in such cases. Depending on the specific application, clutches, overrunning brakes, synchromeshings and similar arrangements are suitable for fixing, as are common in connection with well-known transmissions. Further advantages, aims and properties of the present invention are explained with reference to the attached drawing, in which is shown in

Figure 1 shows a first arrangement of bevel friction ring gear and reverse gear

Figure 2 shows a second arrangement of bevel friction gear and reverse gear.

The arrangements shown in FIGS. 1 and 2 each comprise a bevel friction ring gear 1 and a reverse gear 2 connected herewith in a row. In these exemplary embodiments, the bevel friction ring gear 1 are essentially identical in construction and each have an input cone 3 and an output cone 4 that are axial are arranged parallel to one another and between which a friction ring 5 can be displaced in a gap 6, so that a variable transmission ratio can be set as a function of the position of the friction ring 5. The friction ring 5 encompasses the drive cone 3 in these exemplary embodiments, while the output cone 4 carries an output pinion 7. It is adjusted that, depending on the specific configuration, the conical friction ring gear can also be designed differently.

In the exemplary embodiment according to FIG. 1, the output pinion 7 meshes directly with an assembly 8 which carries the sun gear 9 of a planetary gear 10. The arrangement shown in FIG. 2 also includes a planetary gear 11 with a sun gear 12 which is driven by the output pinion 7 is driven. This takes place via a belt 13 and a wheel 14 rotating with the sun wheel 12. All known belt or chain arrangements, by means of which a sufficiently reliable power transmission can be permanently guaranteed, can be used as the belt 13.

Both planetary gears 10 and 11 each have planet gears 15 and 16, which mesh on the one hand with the respective sun gear 9 and 12 and on the other hand with a respective outer gear 17 and 18.

In the embodiment according to FIG. 1, the outer wheel 17 is connected to the rotating frame 19 of a differential 20 so that it can be directly cut. In this respect, the planetary gear 10 and thus the reverse gear 2 are located directly on the differential 20 in this arrangement. For this reason, this arrangement proves to be extremely compact in construction and extremely high in efficiency, since the number of transmission members and drive train is minimized , It goes without saying that a reverse gear 2 arranged on the differential 20 is also advantageous because of the compact design, independently of the other features of the present invention. Otherwise, an arrangement in which the output pinion 7 meshes directly with an input gear of a reverse gear and the output gear of the reverse gear is directly connected to the rotating frame of a differential, because of the direction caused by a bevel friction ring gear nkelrr advantageous for common motor vehicle engines, because such an arrangement requires only a minimal number of transmission links and is therefore extremely efficient.

In the embodiment according to FIG. 2, on the other hand, the outer wheel 18 is connected to and rotates with an output wheel 21, which in turn meshes with the rotating frame 22 of a differential 23. The resulting reversal of direction is compensated for by the belt arrangement 13, the reverse gear being arranged on or around an intermediate shaft 24 in the exemplary embodiment according to FIG. 2. An arrangement on the intermediate shaft 24 has the advantage, compared to the arrangement proposed in FIG. 1, directly on the differential 20 that the overall arrangement according to FIG. 2 can be made more flexible in its spatial arrangement. This is particularly advantageous for environments in which the spatial conditions are limited in the vicinity of the differential by third assemblies. It turns out that the arrangement of the reverse gear on an intermediate shaft 24 - in particular also because of the change of direction caused by this - is also advantageous independently of the other features of the present invention. The latter applies in particular if conical friction ring gearboxes are to be used in conjunction with foreign motors that have an opposite direction of rotation. In such cases, the belt arrangement 13 can be dispensed with and the pinion 7 can be meshed with the ring 14. Furthermore, it can be advantageous if the output cone 4 is arranged on the shaft 24 so that a separate output pinion 7 and the belt arrangement 13 can be dispensed with entirely. It is also immediately apparent to the person skilled in the art that the drive from the conical friction ring gear 1 can take place via the outer wheels 17 or 18 or via other gear elements of the reverse gear instead of via the sun gears 9 or 12. Likewise, the output of the reverse gear does not necessarily have to take place via the outer wheels 17 or 18. Rather, the sun gears or other transmission elements can also be used for this purpose.

In order that the exemplary embodiments shown in FIGS. 1 and 2 can reliably maintain their “forward” or “backward” states, fixing systems are provided with which a gear link, in these exemplary embodiments a frame 25 or 26 rotating with the planets, on which the planets 15 and 16 are mounted, can be fixed rigidly. Furthermore, fixing systems are available which allow two gear elements of the respective planetary gear 10 or 11 to be fixed to one another. Here, in the embodiment according to FIG. 1, sun gear 9 and outer gear 17 and in the embodiment according to FIG. 2, outer gear 18 and rotating frame 26 of planets 16 are optionally fixed to one another.

Various fixing systems, such as clutches, running brakes or synchronizations, can be used to fix the gear links on the housing or with each other. Three of these are provided by way of example in the illustrated examples, which, depending on the specific requirements, can be easily replaced. In the exemplary embodiment according to FIG. 1, the frame 25 of the planet 15 is by means of an electromagnetic brake 27, which can optionally brake a brake pinion 28, which in turn meshes with the frame 25 of the planet 15. If, in this arrangement, the Drelrrichtimg is to be changed, the brake is activated, so that to the extent that the frame 25 is slowed in relation to the sun gear 9 and the outer gear 17, the drive or speed of the output decreases until it finally comes to a standstill comes and then changes direction.

The outer wheel 17 and the sun wheel 9 are fixed by means of a brake 29, whereby the planet wheels 15 are also fixed with respect to the outer wheel 17 and the sun wheel 9. Since in this state the planetary gear 10 runs with very little loss, this state is preferably selected as a forward gear, whereby it can be seen directly that a brake corresponding to the brake 29 can also be provided, for example, between the frame 25 and the sun wheel 9 and / or outer wheel 17 , Likewise, it may be sufficient to merely prevent the planet 15 from rotating with respect to the frame 25 in order to appropriately shut down the planetary gear 10 and allow it to revolve as a whole.

In the exemplary embodiment according to FIG. 2, the optional fixing takes place via a synchronization 30, by means of which the frame 26 carrying and rotating with the planets 16 can optionally be attached to the outer wheel 18 or with respect to a fixed wheel 31, which is fixed to the housing 32 in this exemplary embodiment. can be synchronized. This one- when mechanisms occur, they correspond to the mechanisms already explained for the exemplary embodiment in FIG. 1, it being understood that the frame 26 can also be synchronized with the sun wheel 12 instead of the outer wheel 18.

Claims

claims:

1. bevel ring gear (1) with a reverse gear (2) provided behind the output (4) in series with the bevel ring gear (1).

2. bevel key ring gear according to claim 1, characterized in that the reverse gear mnfasst a planetary gear with at least one mnlaufende gear rack (25, 26), which supports at least one gear member (15, 16) of the epicyclic gear and optionally with a fixed frame (27, 32) or a revolving gear member (9, 17; 12, 18) can be fixed.

3. cone ring gear according to claim 1 or 2, characterized in that the reverse gear (2) a planetary gear (10, 11) with planet (15, 16), sun gear (9, 12) and outer wheel (17, 18) mnfasst, of which a first gear member (9, 12) with the output (7) of the pinion ring gear (1) and a second gear member (17, 18) with the output (20, 23) of the overall arrangement of pinion ring gear (1) and reverse gear (2) w kconnected is, while the third gear member (15, 16) with respect to a frame or housing (27, 32) can be fixed at least in terms of a degree of freedom.

4. cone ring gear according to spoke 3, characterized in that the third gear member are the planets.

5. bevel ring gear according to claim 3 or 4, characterized in that the first gear member wkd driven by a rotating with the driven cone pinion (7).

6. cone ring gear according to one of claims 3 to 5, characterized in that the second gear member with the rotating

Frame (19) of a differential (20) connected running.

7. cone ring gear according to one of claims 3 to 6, characterized in that two of the gear members, preferably the first and the second gear member, can be fixed together.

8. cone ring gear according to one of claims 2 to 8, characterized in that for fixing a clutch (29), an overrun brake (27, 28), and / or synchronization (30) used wkd.