USRE43315E1 - Multi-step gear - Google Patents

Multi-step gear Download PDF

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Publication number
USRE43315E1
USRE43315E1 US11/529,692 US52969202A USRE43315E US RE43315 E1 USRE43315 E1 US RE43315E1 US 52969202 A US52969202 A US 52969202A US RE43315 E USRE43315 E US RE43315E
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gear set
planetary gear
carrier
input
output
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Peter Ziemer
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ZF Friedrichshafen AG
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ZF Friedrichshafen AG
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    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2015—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with five sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight engaging means
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears

Definitions

  • the present invention concerns a multi-step transmission.
  • EP 0 434 525 A1 which encompasses, essentially, an input drive shaft and an output drive shaft, which are arranged coaxial to one another, a double planetary gear set placed concentric to the output drive shaft and five shifting elements in the form of three shift elements and two brakes, the selective blocking of which respectively determine, pairwise, the different gear ratios between the input drive shaft and the output drive shaft.
  • the known transmission possesses two power paths, wherein a first element of the double planetary gear set is connected by means of a first shift element with the first power path.
  • a second element of the double planetary gear set is connected to the output drive shaft and a third element is connected with the second power path by means of a third shift element and is braked by means of a first brake.
  • a fourth element of the double planetary gear set is connected with the first power path by means of a second shift element and is braked by a second brake, so that a selective shifting pairwise between the shifting organs assures that six forward gear positions are available.
  • This arrangement then comprises a first gear through the first shift element and the first brake, a second gear through the first shift element and the second brake, a third gear through the first shift element and the second shift element, a fourth gear through the first shift element and the third shift element, a fifth gear through the second shift element and the third shift element a sixth gear through the third shift element and the second brake, and finally, a reverse gear position through the second shift element and the first brake.
  • the purpose of the present invention is to be found in the creating of a multi-step transmission, which encompasses at least seven forward gear positions with a favorable gear step and ample spread, and is relatively economical to manufacture.
  • the invented multi-step transmission offers at least seven forward gear positions with a reduced number of gear sets and shift elements.
  • each gear into which a shift is made, only two shift elements are actuated.
  • FIGS. 1A and 1B a first embodiment form of a multi-step transmission with seven forward gear positions and one reverse gear position;
  • FIGS. 2A and 2B a second embodiment form of a multi-step transmission with seven forward gear positions and one reverse gear position;
  • FIGS. 3A and 3B a third embodiment form of a multi-step transmission with seven forward gear positions and one reverse gear position;
  • FIGS. 4A and 4B a fourth embodiment form of a multi-step transmission with seven forward gear positions and one reverse gear position;
  • FIGS. 5A and 5B a fifth embodiment form of a multi-step transmission with seven forward gear positions and one reverse gear position;
  • FIGS. 6A and 6B a sixth embodiment form of a multi-step transmission with ten forward gear positions and one reverse gear position;
  • FIGS. 7A and 7B a seventh embodiment form of a multi-step transmission with nine forward gear positions and two reverse gear positions;
  • FIGS. 8A and 8B an eighth embodiment form of a multi-step transmission with nine forward gear positions and one reverse gear position;
  • FIGS. 9A and 9B a ninth embodiment form of a multi-step transmission with eight forward gear positions and two reverse gear positions;
  • FIGS. 10A and 10B a third embodiment form of a multi-step transmission with thirteen forward gear positions and one reverse gear position;
  • FIGS. 11A and 11B an eleventh embodiment form of a multi-step transmission with sixteen forward gear positions and one reverse gear position;
  • FIGS. 12A and 12B a twelfth embodiment form of a multi-step transmission with eight forward gear positions and no reverse gear position;
  • FIGS. 13A and 13B a thirteenth embodiment form of a multi-step transmission with eight forward gear positions and no reverse gear position;
  • FIGS. 14A and 14B a fourteenth embodiment form of a multi-step transmission with eight forward gear positions and no reverse gear position;
  • FIGS. 15A and 15B a fifteenth embodiment form of a multi-step transmission with eleven forward gear positions and no reverse gear position;
  • FIGS. 16A and 16B a sixteenth embodiment form of a multi-step transmission with seventeen forward gear positions and no reverse gear position.
  • FIGS. 1A to 16A the power flow schematic chart
  • FIGS. 1B to 16B the shifting-logic accompanied by the assigned gear ratios of the individual gears, the gear staging, the transmission range, and the transmission ratio of the individual planetary gear sets. From the individual planetary gear set ratios, it becomes evident to the expert from the Kutzbach-plan, that group shifting is avoided in all the embodiments here presented.
  • the speeds of rotation n 1 , n 2 and the input speed of rotation n are transferred to the output drive shaft.
  • additional shift elements it becomes possible, utilizing the invented multi-step transmission with seven forward gear positions and one reverse gear position, to conceive of various multi-step transmissions with more than seven forward gear positions and at least one reverse gear position. This is true especially in the case of passenger motor vehicles, busses and trucks.
  • a cross-country reduction gear can be designed with special gear staging.
  • multi-gear drives without a reverse gear position can be made available.
  • the input drive shaft is designated with 1
  • the shift elements are respectively denoted as A, B, C, D, and E.
  • the first planetary gear set of the input-side gear set VS is designated with RS 1
  • the second planetary gear set of that input-side gear set is RS 2 .
  • the first and second gear sets of the shiftable output-side gear set NS are designated RS 3 and RS 4 .
  • the input-side gear sets comprise a non-shiftable two carrier, 4-shaft drive, wherein at least one shaft, and as a maximum one shaft per input-side gear set runs with the speed of rotation of n of the input drive shaft and at least one shaft, and at a maximum, one shaft per input-side gear set is immobile.
  • the gear set RS 1 possesses a sun gear 11 , planet gears 12 and an internal gear 13 .
  • the gear set RS 2 shows a sun gear 21 , planet gears 22 and an internal gear 23 .
  • the planetary carrier designated as 15 is common to the planet gears 12 and the carrier designated with 25 is common to the planetary gear sets 22 .
  • the arrangement is a shiftable two carrier, four shaft drive, which includes the planetary gear sets RS 3 and RS 4 .
  • the gear set RS 3 has a sun gear 31 , planet gears 32 and an internal gear 33 .
  • the gear set RS 4 of the output-side drive NS comprises a sun gear 41 , planet gears 42 , and an internal gear 43 .
  • the common carrier of the planet gears 32 is designated as 35 and the common carrier of the planet gears 42 is designated with 45 .
  • the carrier 45 of the gear set RS 4 is connected with one shaft of the gear set RS 3 . Onto this coupling shaft, the shift elements E and D are affixed.
  • the shift elements B and C are connected to a central gear of the gear set RS 4 , wherein, by the term “central gear”, either a sun gear or an internal gear of the gear set is to be understood.
  • the shift element A is connected to one central gear of the gear set RS 3 .
  • FIG. 1A shows a first embodiment of the invented multi-step transmission with two coupled, non-shiftable input-side gear sets.
  • the input drive shaft 1 is connected with the sun gears 11 and 21 of the input-side gear sets RS 1 and RS 2 .
  • the internal gear 13 of the first input-side gear set RS 1 is stationarily fixed.
  • the planetary carriers 15 and 25 of the two input-side gear sets RS 1 and RS 2 are connected together.
  • the internal gear 23 (speed of rotation n 2 ) of the second input-side gear set RS 2 can be connected by means of the shift element D to the internal gear 33 of the first output-side gear set RS 3 and the carrier 45 of the second output-side gear set RS 4 .
  • the planetary carriers 15 and 25 (speed of rotation n 1 ) can be connected by means of the shift element A with the sun gear 31 of the first output-side gear set RS 3 , as well as by means of the shift element C with the sun gear 41 of the second output-side gear set RS 4 .
  • the input drive 1 is connectable by means of the shift element B to the sun gear 41 and to the carrier 45 by means of the shift element E.
  • the carrier 35 of the gear set RS 3 is connected with the internal gear 43 of the gear set RS 4 and with the output drive shaft 2 .
  • the internal gear 33 of the gear set RS 3 is connected with the carrier of the gear set RS 4 .
  • the forward gear positions 1 to 7 and the reverse gear position R with the aid of the control of the output-side gear set NS, i.e., the gear sets RS 3 and RS 4 , which respectively have the speeds of revolution of n, n 1 and n 2 , can be attained by means of selective shifting of the five shift elements A to E, in accord with the shift sketch of the FIG. 1B .
  • it is an essential advantage that by the shift change from one gear to the next gear, principally one shift element is open and only one shift element in need be closed. In this way, shifting of questionable quality, with a simultaneous engagement of a plurality of shift elements (group shifting), is avoided.
  • the large spread (greater than 9) in the case of similar more favorable gear steps, which are described in the introductory passages as being state of the technology for 6-gear automatic transmissions.
  • the normally installed torque converter serving as a startup element, could be substituted for by a hydraulic shift element and/or a lamellar shift element integrated into the transmission without having to dispense with a high startup power.
  • a possible embodiment is shown as an example in the FIG. 1A . With the depicted arrangement, the advantages gained are a lesser weight, favorable dimensioning for installation in the vehicle tunnel space giving a reduced length of construction, as well as achieving a reduction in manufacturing costs.
  • FIG. 2A Details of the FIG. 2A , which have already been explained in FIG. 1A , still carry the same reference numbers.
  • the embodiment form 2 A has, contrary to the embodiment in FIG. 1A a generally more simply controlled brake serving as a fifth shifting element instead of a clutch element.
  • both sun gears 11 and 21 are connected with the input drive shaft 1 .
  • the input drive shaft 1 can be connected with the sun gear 31 and by means of the shift element E, also connected with the planetary carrier 45 .
  • the planetary carrier 15 (speed of rotation n 1 ) can be connected by means of the shift element B with the sun gear 41 .
  • the internal gear 13 is connected with the carrier 25 , wherein the carrier 25 is rigidly affixed to the housing.
  • the internal gear 23 (speed of rotation n 2 ) can be connected with the sun gear 41 by means of the shift element C.
  • the carrier 45 can be connected to the housing by means of brake D.
  • the internal gear 33 is connected with the carrier 45 .
  • the internal gear 43 is connected with the carrier 35 and with the output drive shaft 2 .
  • Advantageous in the embodiment 2 of the invented multi-step transmission is especially the overdrive characteristic of the two upper gears, in regard to the reduction of fuel consumption and running noise.
  • a further advantage is the designed simple formulation possibility of having a brake D instead of a shift element, for instance in regard to the delivery of pressurized oil for the activation.
  • FIG. 3A shows a further embodiment of the invented multi-step transmission with two coupled, non-shiftable input-side gear sets.
  • Input-side gear set VS and output-side gear set NS are here constructed as Ravigneaux-gear sets.
  • the input drive shaft 1 is connected with the sun gear 11 of the gear set RS 1 , by means of the shift element E with the carriers 35 ′. 35 ′′ of the inner and out planet gears 32 ′, 32 ′′ of the gear set RS 2 , and can be connected with the carrier 45 of the gear set RS 4 . Further the input drive shaft 1 can be connected with sun gear 31 of the gear set RS 3 by means of the shift element A.
  • the planet gears 12 of the gear set RS 1 and the outer planet gears 22 ′′ of the gear set RS 2 are joined to one another.
  • the sun gear 21 (speed of rotation n 2 ) of the gear set RS 2 can be connected with the sun gear 41 of the gear set RS 4 by means of the shift element C.
  • the internal gear 13 of the gear set RS 1 is immobilized.
  • the carriers 35 ′, 35 ′′ and 45 may be made stationary.
  • the planet gears 42 of the gear set RS 4 and the outer planet gears 32 ′′ of the gear set RS 3 are coupled together.
  • the output drive shaft 2 is rigidly bound to double internal gears 33 and 43 .
  • Advantageous in the embodiment 3 of the invented multi-step transmission is especially the favorable cost formulation of the four planetary gear sets with only two internal gears. Beyond this, the over-drive characteristic of the two upper gears can be employed for the saving of fuel and for a lessening of the noise emission.
  • FIG. 4A shows yet another embodiment of the invented multi-step transmission with two coupled , non-shiftable input-side gear sets.
  • the additional speeds of rotation n 1 and n 2 are produced through the input-side gear sets RS 1 and RS 2 ., whereby the carriers 15 and 25 of the planet gears 12 and 22 of this gear set are connected together.
  • the input-side shaft 1 is connected with the internal gears 13 and 23 of the gear sets RS 1 and RS 2 , and by means of the shift element E can be connected with the internal gear 33 of the third gear set RS 3 , as well as being connectable by means of the shift element B with the internal gear 43 of the fourth gear set RS 4 .
  • the sun gear 11 of the first gear set RS 1 is affixed to the housing.
  • the sun gear 21 (speed of rotation n 2 ) of the second gear set RS 2 can be connected by means of the shift element D to the carrier 45 of the gear set RS 4 , whereby the said carrier 45 is connected to the internal gear 33 of the gear set RS 3 .
  • the carriers 15 and 25 (speed of rotation n 1 ) of the planet gears 12 and 22 of the gear sets RS 1 and RS 2 can be connected by the shift element C with the internal gear 43 of the gear set RS 4 .
  • the sun gears 31 and 41 of the gear set RS 3 and RS 4 can be blocked in common by the brake A.
  • the carrier 35 of the gear set RS 3 is connected with the output drive shaft 2 .
  • the design 4 of the invented multi-step transmission is particularly favorable for use in off-road vehicles, since in this case, because of the stall-gear ratios of the gear sets, as shown in FIG. 4B , a creep gear with a high ratio such as i (first gear) >8, is available upon simultaneous favorable gear ratio in the upper travel speed areas. Further, the use of a stepped planet gear provides, in the case of the simultaneous drop-out of a fourth internal gear, a saving in the manufacturing costs.
  • the internal gear 13 is made immobile.
  • the carrier 15 (speed of rotation n 1 ) is connected with the carrier 25 and can be connected with the internal gear 43 by means of the shift element B.
  • the internal gear 23 (speed of rotation n 2 ) can be connected with the carrier 45 by means of the shift element D, and thus to the therewith connected internal gear 33 .
  • the input drive shaft 1 is connected with the sun gears 11 and 21 and can be connected with the sun gears 41 and 31 by means of the shift element A, and further by the shift element E, can be connected with the carrier 45 and the internal gear 33 .
  • the internal gear 43 can be adjusted to the speed of rotation zero.
  • the carrier 35 is connected to the output drive 2 .
  • FIG. 6A shows an invented multi-step transmission with two coupled, non-shiftable, input-side gear sets, in the case of which shifting can be carried out with six shift elements and one reverse gear position to obtain ten forward gear positions along with the said one reverse gear position.
  • an additional shift element F On the shaft with the shift elements B and C of the shiftable output-side gear set is provided an additional shift element F.
  • the input drive shaft 1 (speed of rotation n) is connected with the internal gear 13 and the internal gear 23 .
  • the said input drive shaft 1 can also be connected, by use of the shift element E, with combined carriers 45 of the gear set RS 4 , carrier 35 ′′ of the outer planet gears 32 ′′ of gear set RS 3 and carrier 35 ′ of the inner planet gears 32 ′ of the gear set RS 3 .
  • the planet gears 32 and 42 are coupled together.
  • the carrier 25 is connected with the carrier 15 (speed of rotation n 1 ) and can be connected with the sun gear 41 by the shift element B.
  • the sun gear 41 upon the activation of the brake C, can be blocked, that is, connected to the housing.
  • the carriers 15 and 25 (speed of rotation n 1 ) can be connected with the sun gear 31 by the shift element A.
  • the sun gear 21 (speed of rotation n 2 ) can be connected by the shift element D with the carrier 35 ′ of the inner planet gears 32 ′ of the gear set RS 3 and can be connected by the shift element F with the sun gear 41 of the gear set RS 4 .
  • the internal gears 33 and 43 are joined together and also are connected to the output drive shaft 2 .
  • the gear steps can be designed to fit in a close space, which makes this particular arrangement particularly favorable for a vehicle with a diesel motor.
  • the input drive shaft 1 is connected to the internal gear 13 of the input-side gear set RS 1 and the thereto connected internal gear 23 of the input-side gear set RS 2 . Further, the input drive shaft can be connected to the carrier 45 by means of the shift element E and by means of the shift element B, can be connected with the sun gear 41 .
  • the carrier 25 of the planet gears 22 is connected with the carrier 15 (speed of rotation n 1 ) as well as with the sun gear 31 by means of the shift element A. In addition, by the activation of the shift element F, the carrier 25 and the carrier 15 can be connected to the sun gear 41 .
  • the sun gear 21 (speed of rotation n 2 ) is connectable by the shift element C with the sun gear 41 as well as connectable with the carrier 45 by means of the shift element D.
  • the carrier 45 is connected to the internal gear 33 .
  • the internal gear 43 is connected with the carrier 35 and with the output drive shaft 2 .
  • FIG. 8A shows an invented multi-step transmission with two coupled, non-shiftable input-side gear sets, whereby, for the activation of this transmission, a total of six shift elements A to F are provided for shifting into nine forward gear positions and one reverse gear position.
  • the multi-step transmission outlined in FIG. 8A possesses four shift elements and two brakes, whereby the number of the forward gear positions is reduced by one gear from the number of forward gear positions as shown in FIG. 6A .
  • the gear set RS 2 is minus one gear set
  • the gear set RS 1 is plus one gear set.
  • the input drive shaft 1 is connected with the sun gear 21 as well as with the carrier 15 ′′ or the outer planet gears 22 ′′ of the gear set RS 1 , and by means of the shift element A can be connected with the sun gear 31 and by means of the shift element E, can be connected with the carrier 45 .
  • the carrier 25 is, on the one hand, bound to the housing, and on the other side, connected with the sun gear 11 of the gear set RS 1 .
  • the carrier 15 ′ of the inner planet gear 12 ′ is connected with the carrier 15 ′′ of the outer planet gears 12 ′′ of the gear set RS 1 .
  • the internal gear 13 of the gear set RS 1 (speed of rotation n 1 ) can be connected with the sun gear 41 by means of the shift element B.
  • the internal gear 23 (speed of rotation n 2 ) can be connected with the sun gear 41 through the shift element C.
  • the carrier 45 upon the activation of the brake D, can be connected with the housing. Beyond this, the carrier 45 is connected to the internal gear 33 .
  • the internal gear 43 connects with the carrier 35 and with the output drive shaft 2 .
  • the shifting logic for the six shift elements A to F for the shifting to the nine forward gears and the reverse gear position of the multi-step transmission in accord with FIG. 8 is shown in the tables of FIG. 8B .
  • the special point of this transmission is, that only one, non-shiftable, input-side gear set RS 1 is present instead of two input-side gear sets as have been described up to this time.
  • the input drive shaft 1 (speed of rotation n) is connected with the sun gear 11 of the gear set RS 1 (Plus-gear set), and can be connected with the carrier 45 by means of the shift element E, as well as being connectable by shift element B with the sun gear 41 .
  • the carrier 15 ′ of the inner planet gears 12 ′ of the gear set RS 1 and the carrier 15 ′′ of the outer planet gears 12 ′′ of the gear set RS 1 are connected together and affixed to the housing.
  • the carrier 15 ′ and the carrier 15 ′′ by means of the shift element C, can be connected with the sun gear 41 .
  • the internal gear 13 (speed of rotation n 1 ) can be connected with the sun gear 41 by the shift element F and also connected to the sun gear 31 by means of the shift element A.
  • the internal gear 43 is connected to the internal gear 33 and connected to the output drive shaft 2 .
  • the carrier 45 (of the planet gears 42 ), carrier 35 ′(of the inner planet gears 32 ′) and carrier 35 ′′ (of the outer planet gears 32 ′′) are bound together and can be blocked by the brake D.
  • the planet gears 32 ′′ and 42 are, in this case, also coupled.
  • FIG. 10A shows a multi-step transmission with three, coupled, non-shiftable input-side gear sets RS 1 , RS 2 a and RS 2 b, by means of seven shift elements A to G, shifting is available through thirteen forward gear positions and one reverse gear position.
  • the valid relationship is NF>nG>Nb.
  • In input speeds of rotation are produced through a non-shiftable three carrier, five shaft gear arrangement.
  • the input drive shaft 1 (speed of rotation n) is bound to the sun gear 11 of the first input-side gear set RS 1 and can be connected by means of the shift element A with the sun gear 31 of the first output-side gear set RS 3 and the thereto connected sun gear 41 of the second output-side gear set RS 4 and can be connected further by means of the shift element E with the carrier 45 of the second output-side gear set RS- 4 .
  • the gear set RS 2 which has been installed in the described transmissions up to this point, is now replaced by the gear sets RS 2 a and RS 2 b, whereby, the carriers 25 a and 25 b′′ of the planet gears 22 a of the gear set RS 2 a and the outer planet gears 22 b′′ of the plus-transmission constructed gear set RS 2 b are all connected together.
  • the planet gears 22 a and 22 b′′ are coupled together.
  • the carrier 15 is connected to the carriers 25 b′ of the inner planet gears 22 b′ and to the carrier 25 b′′ of the outer planet gears 22 b′′. Beyond this the carrier 25 b′′ can be connected with the internal gear 43 (speed of rotation n 2 a) by means of the shift element G.
  • the internal gear 43 can be blocked by the brake C.
  • the sun gear 21 a of the gear set RS 2 a (speed of rotation n 1 ) can be connected with the internal gear 43 by means of the shift element B.
  • the internal gear 23 a of the gear set RS 2 a and the internal gear 23 b of the gear set RS 2 b are connected together (speed of rotation n 2 b) and can be connected with the internal gear 43 by means of the shift element F, and by the shift element D can be connected with the carrier 45 and the therewith attached internal gear 33 .
  • the carrier 35 is connected to the output drive shaft 2 .
  • the sun gear 21 b of the gear set RS 2 b and the internal gear 13 of the gear set RS 1 are connected with the housing.
  • this embodiment 10 of the invented multi-step transmission lie thus in the high number of gear changes along with a very compact installation space with only five planetary gear sets and seven shift elements.
  • a multi-step transmission with two reverse gear positions can be developed, but then with only twelve forward gear positions.
  • the input-side gear set VS comprises, in total, four connected, non-shiftable planet gear sets.
  • the input-side gear set RS 1 consists of a gear set RS 1 a and a gearset RS 1 b, wherein the planet gears 12 a of the gear set RS 1 a and the outer planet gears 12 b′′ of the gear set RS 1 b are coupled together and the carrier 15 b′′ of the outer planet gears 12 b′′ is connected with the carrier 15 b′ of the inner planet gears 12 b′.
  • the gear set RS 2 encompasses two gears sets RS 2 a and RS 2 b, whereby the planet gears 22 a of the gear set RS 2 a and the outer planet gears 22 b′′ of the gear set RS 2 b are coupled together.
  • the input drive shaft 1 (speed of rotation 1 ) is connected with the sun gear 11 b of the gear set RS 1 b and the sun gear 21 a of the gear set RS 2 a and by means of the shift element A can be connected with the sun gear 31 and by means of the shift element E is connectable with the internal gear 33 .
  • the sun gear 11 a of the gear set RS 1 a is connected with the housing.
  • the internal gear 13 a of the gear set RS 1 a and 13 b of the gear set RS 1 b are connected to one another (speed of rotation, n 1 a) and by means of the shift element B can be connected to the sun gear 41 of the second output-side gear set RS 4 .
  • the sun gear 41 is blockable by the brake C.
  • the sun gear 21 b of the gear set RS 2 b (speed of rotation n 2 B) can be connected to the internal gear 33 by means of the shift element D, as well as with the sun gear 41 by means of the shift element F.
  • the internal gear 33 is connected to the carrier 45 .
  • the carrier 25 b′ of the inner planet gears 22 b′ and 25 b′′ of the outer planet gears 22 b′′ of the gear set RS 2 b and the carrier 25 a of the gear set RS 2 a are bound to one another (speed of rotation n 1 b) and can be connected to the sun gear 41 by means of the shift element H.
  • the coupled internal gears 23 a and 23 b (speed of rotation n 2 a) of the gear sets RS 2 a and RS 2 b can, likewise, be connected to the sun gear 41 by means of the shift element G.
  • the sun gear 43 is connected with the carrier 35 and with the output drive shaft 2 .
  • a multi-step transmission which transmission possesses eight forward gear positions which are accessible through five shift elements and only one input-side gear set RS 1 , which is achieved in that the previously mentioned kinematic condition “speed of rotation on the shift element D is less than, or equal to the speed of rotation on the shift element B” is limited by the change, “speed of rotation on the shift element D is equal to the speed of rotation on the shift element B”.
  • the internal gear 13 of the input-side gear set RS 1 is rigidly connected by means of an axle with the housing of the multi-step transmission.
  • the input drive shaft 1 (speed of rotation n) is connected with the sun gear 11 of the input-side gear set RS 1 .
  • the said input drive shaft 1 is connectable by means of the shift element E with the internal gear 33 of the first output-side gear set RS 3 as well as with the therewith connected carrier 45 of the second output-side gear set RS 4 . Additionally, by means of the shift element A the input drive shaft 1 can be connected to the sun gear 31 of the gear set RS 3 .
  • the carrier 15 (speed of rotation n 1 ) of the gear set RS 1 is connectable with the sun gear 41 of the gear set RS 4 through the shift element B and can further be connected with the internal gear 33 of the gear set RS 3 by means of the shift element D.
  • the sun gear 41 of the gear set RS 4 can be immobilized.
  • the internal gear 43 of the gear set RS 4 and the therewith connected carrier 35 of the gear set RS 3 are connected with the output-side shaft 2 .
  • a single input-side gear set RS 1 is provided, which produces the necessary speed of rotation for the regulation of the output-side gear sets RS 3 and RS 4 .
  • the input-side gear set RS 1 possesses, besides a sun gear 11 and an internal gear 13 , inner planet gears 12 ′ and outer planet gears 12 ′′, the carriers of which ( 15 ′ and 15 ′′) are connected together.
  • the input drive shaft 1 (speed of rotation n) is connected to the sun gear 11 of the input-side gear set RS 1 and can be connected with the carrier 35 ′′ of the outer planet gears 32 ′′ of the first output-side gear set RS 3 by means of the shift element E, as well as connectable through the shift element A with the sun gear 31 of the gear set RS 3 .
  • the carriers 15 ′ and 15 ′′ of the gear set RS 1 are affixed to the housing of the multi-step transmission.
  • the sun gear 41 of the gear set RS 4 can be blocked by the brake C.
  • the internal gear 13 (speed of rotation n 1 ) of the gear set RS 1 is connectable with the sun gear 41 and by means of the shift element D also connectable with the carrier 35 ′ of the inner planet gears 32 ′ of the gear set RS 3 .
  • the carrier 35 ′ is connected to the carrier 35 ′′ of the outer planet gears 32 ′′ of the gear set RS 3 and connected also with the carrier 45 of the gear set RS 4 .
  • the planet gears 32 ′′ and 42 are, in this arrangement, coupled with one another.
  • the internal gears 33 and 43 of gear sets RS 3 and RS 4 are connected with the output drive shaft 2 .
  • the sun gear 11 of the input-side gear set RS 1 is affixed to the housing of the multi-step transmission.
  • the input drive shaft 1 (speed of rotation n) is connected with the internal gear 13 of the gear set RS 1 and by means of the shift element E can be brought into connection with carrier 45 of the second output-side gear set RS 4 along with the therewith connected sun gear 31 of the first output-side gear set RS 3 .
  • the input drive shaft 1 (speed of rotation n) can be brought into connection with the internal gear 33 of the gear set RS 3 and the therewith connected internal gear 43 of the gear set RS 4 .
  • the carrier 15 (speed of rotation n 1 ) of the gear set RS 1 by means of the shift element B, can be connected with the sun gear 41 , and by means of the shift element B, can be connected with the sun gear 41 and by means of the shift element D connectable with the carrier 45 of the gear set RS 4 .
  • Use of the brake C permits the sun gear 41 of the gear set RS 4 to be made immobile.
  • the carrier 35 of the gear set RS 3 is connected to the output drive shaft 2 .
  • This embodiment possesses two, coupled, non-shiftable input-side gear sets, which enable shifting through a total of eleven forward gear positions by the selective activation of six shift elements A to F.
  • the second input-side gear set RS 2 is designed as a plus-gear set and the first input-side gear set RS 1 is designed as a minus-gear set, wherein the outer planet gears 22 ′′ of the gear set RS 2 are rigidly coupled to planet gears 12 of the gear set RS 1 .
  • the input drive shaft 1 (speed of rotation n) is connected to the sun gear 21 of the gear set RS 2 , as well as, connectable to the sun gear 41 through the shift element B and can further be connected by the shift element E to the carrier 45 of the second output-side gear set RS 4 , wherein the carrier 45 is connected with the internal gear 33 of the first output-side gear set RS 3 .
  • the carrier 15 (speed of rotation n 1 ) common to the outer planet gears 22 ′′ of the gear set RS 2 and the planet gears 12 of the gear set RS 1 , can be connected to the sun gear 31 of the gear set RS 3 by means of shift element A and can be connected to the sun gear 41 of the gear set RS 4 through shift element F. Beyond this, the carrier 15 is connected with the carriers 25 ′′ of the outer planet gears 22 ′′ and 25 ′ of the inner planet gears 22 ′ of the gear set RS 2 .
  • the coupled internal gears 13 and 23 (speed of rotation n 2 ) of the gear sets RS 1 and RS 2 can be connected through the shift element D with the carrier 45 as well as being connected to the sun gear 41 of the gear set RS 4 by means of the shift element C.
  • the carrier 35 of the gear set RS 3 is connected to the internal gear 43 of the of the gear set RS 4 and with the output drive shaft 2 .
  • the input-side gear set RS 1 comprises in this arrangement, a gear set RS 1 a and a gear set RS 1 b, the input-side gear set RS 2 is made up of a gear set RS 2 a and a gear set RS 2 b.
  • the input drive shaft 1 is connected with the sun gear 11 a of the first input-side gear set RS 1 a (plus-gear set) and can be connected to the sun gear 31 of the first output-side gear set RS 3 by means of activating shift element A.
  • Shift element E can connect the input drive shaft 1 to the carriers 35 ′ of the inner planet gears 32 ′ and 35 ′′ of the outer planet gears 32 ′′ of the gear set RS 3 (plus-gear set).
  • the carrier 15 a′ of the inner planet gears 12 a′′ of the gear set RS 1 a and the carrier 15 ′′ of the outer planet gears 12 ′′ of the gear set RS 1 are joined together.
  • the gear set RS 1 b is designed as a minus gear train.
  • the sun gear 11 b of the second input-side gear set RS 1 b corresponds to the sun gear 21 a of the third input-side gear set RS 2 A.
  • the internal gear 13 b of the second gear set RS 1 b corresponds to the internal gear 23 b of the fourth input-side gear set RS 2 b.
  • the outer planet gears 12 a′′ of the gear set RS 1 a, the planet gears 12 b of the gear set RS 1 b, the planet gears 22 a of the gear set RS 2 a and the planet gears 22 b of the gear set RS 2 b are coupled together as stepping planetary gears.
  • the carrier 15 a′′ is assigned in common.
  • the carrier 15 a′′ (speed of rotation n 1 b) is, upon activation of the shift element G, connectable with the sun gear 41 of the second output-side gear set RS 4 (minus gear train) as well as, upon activation of the shift element D, connectable to the carrier 35 ′ of the inner planet gears 32 ′ of the first output-side gear set RS 3 .
  • the gear set RS 3 is designed as a plus gear train.
  • the outer planet gears 32 ′′ of the gear set RS 3 are coupled with the planet gears 42 of the gear set RS 4 .
  • the carrier 35 ′ of the inner planet gears 32 ′ is connected to the carrier 35 ′′ of the outer planet gears 32 ′′ of the gear set RS 3 .
  • the sun gear 11 b of the gear set RS 1 b is affixed to the housing.
  • the sun gear 21 b of the gear set RS 2 b (speed of rotation n 2 b) is, by activation of the shift element F, connectable with the sun gear 41 , which, by means of the brake C is likewise affixed to the housing.
  • the internal gear 13 a of the gear set RS 1 and 13 b of the gear set RS 1 b are connected together and, upon activation of the shift element B (speed of rotation n 1 a) are connectable to the sun gear 41 .
  • the carrier 35 ′′ and the carrier 35 ′ are connected together with the carrier 45 .
  • the internal gear 23 a of the, gear set,RS 2 a (speed of rotation n 2 a) is, through the shift element H, connectable with the sun gear 41 of the gear set RS 4 . Finally, the internal gears 33 and 43 are connected with the output drive shaft 2 .
  • the described embodiments 15 and 16 of the multi-step transmissions are particularly adaptable to motorcycles and especially well suited for hub shifting for bicycles, with a corresponding high number of shift positions.
US11/529,692 1999-10-14 2000-10-11 Multi-step gear Expired - Lifetime USRE43315E1 (en)

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DE19949507 1999-10-14
US11/529,692 USRE43315E1 (en) 1999-10-14 2000-10-11 Multi-step gear
US10/089,808 US6634980B1 (en) 1999-10-14 2000-10-11 Multi-step gear
PCT/EP2000/009993 WO2001027496A1 (de) 1999-10-14 2000-10-11 Mehrstufengetriebe

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DE19949507B4 (de) 2014-10-23
JP5898291B2 (ja) 2016-04-06
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JP2012189220A (ja) 2012-10-04
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US6634980B1 (en) 2003-10-21
JP5898290B2 (ja) 2016-04-06

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