Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
  • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
  • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
  • F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
  • F16H15/04—Gearings providing a continuous range of gear ratios
  • F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members

Definitions

• the invention relates to a bevel friction ring gear in connection with a reverse run.
• CVT continuously variable transmissions
• 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.
• 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.
• this arrangement also allows the reverse gear to be varied continuously.
• 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.
• 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 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.
• the second gear member with the rotating frame one Differentials connected revolves.
• 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.
• first and the second gear member can be fixed together.
• 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.
• 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.
• 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.
• 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.
• 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.
• 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.
• clutches, overrunning brakes, synchromeshings and similar arrangements are suitable for fixing, as are common in connection with well-known transmissions.
• 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.
• FIGS. 1 and 2 each comprise a bevel friction ring gear 1 and a reverse gear 2 connected herewith in a row.
• 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.
• 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.
• the outer wheel 17 is connected to the rotating frame 19 of a differential 20 so that it can be directly cut.
• the planetary gear 10 and thus the reverse gear 2 are located directly on the differential 20 in this arrangement.
• 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 .
• 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.
• 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.
• 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.
• 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.
• 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.
• 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.
• 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.
• 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.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Transmission Devices (AREA)
• Retarders (AREA)
• Friction Gearing (AREA)
• Structure Of Transmissions (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

Family

ID=32797262

Family Applications (1)

Country Status (7)

Cited By (2)

Families Citing this family (2)

Citations (7)

Family Cites Families (5)

• 2003
  • 2003-12-17 BR BRPI0307163-4A patent/BR0307163B1/pt not_active IP Right Cessation
  • 2003-12-17 DE DE10394040T patent/DE10394040D2/de not_active Expired - Fee Related
  • 2003-12-17 JP JP2004567257A patent/JP2006513384A/ja active Pending
  • 2003-12-17 WO PCT/DE2003/004164 patent/WO2004068000A1/de active Application Filing
  • 2003-12-17 KR KR1020057013221A patent/KR101098151B1/ko not_active IP Right Cessation
  • 2003-12-17 AU AU2003298065A patent/AU2003298065A1/en not_active Abandoned
  • 2003-12-17 CN CNA038011891A patent/CN1602397A/zh active Pending

Patent Citations (7)

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