Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
  • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
  • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
  • B62M11/06—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with spur gear wheels

Definitions

• the invention relates to a multiple transmission for a bicycle with bearing in a transmission housing input shaft and output shaft, wherein the input shaft designed to accommodate cranks and led out with its two ends from the gear housing and the Aus ⁇ output shaft leads out with one of its ends from the gear housing and is configured at this end for receiving a drive pinion.
• Such a transmission is known for example from US 5,553,510.
• Gearwheels are arranged on both shafts, each of which can be connected in a rotationally fixed manner to the respective shaft via a free passage.
• pivotable Verbtndungsritzel are provided, which can each mesh with two opposing gears.
• a rotatable bottom bracket with one or more chainrings is mounted on the frame, which forms the main component of the bicycle with all its mounting points for the front fork, the seat post and the rear wheel.
• a cassette consisting of up to ten pinions of different sizes, at a dropout located directly on the rear axle attached a rear derailleur whose task is to lead the chain on the Rit ⁇ tent the cassette and to enable switching operations.
• a derailleur usually mounted on the seat tube can be changed at the bottom bracket between the different chainrings.
• the possibility of shifting allows the driver to adapt the ratio of his drive to the particular driving situation.
• Bicycles with a shifting system as described above are generally referred to as derailleur bicycles.
• the so-called “platform strategy” can be used with the aid of the gearbox integrated in the frame.It was customary in bicycle construction initially to build a frame and then retrofit it with its components, it is integrated with the integrated concept
• the gearbox housing as a platform, for example components such as circuit, suspension, the complete power transmission, as well as brakes, dynamo and lighting are fixedly mounted on the thus-equipped Gearboxes are then assembled the custom parts that complete the bike according to customer requirements.
• the transmission consists of a planetary gear and a prime mover.
• the primary drive is necessary because the planetary gear developed for use in a gear hub does not withstand the high torque acting in the bottom bracket.
• the planetary gear is brought by the primary drive to a higher speed to withstand the forces acting.
• this design reduces the efficiency of the drive.
• the generic multiple transmission is characterized by the following features:
• the at least one Eisenwel ⁇ le (44, 45, 62) and the output shaft (93) are each arranged at least two gears (200, 201, 202, 203),
• the coupling means may be freewheels and / or externally controllable clutches.
• each one of the gears by means of a freewheel and the other of the gears by means of the switchable coupling mos ⁇ firmly connected to the respective shaft. This ensures that both the input shaft and the output shaft are positively connected to a gear.
• the arranged on the intermediate shaft gears can be firmly (rigidly) connected to this, whereby the manufacturing costs are reduced.
• It can be gela ⁇ siege several parallel intermediate shafts in the gear housing, if a plurality of gears and / or the lowest possible gradation of the transmission is desired.
• the waves are hollow.
• the gears may be perforated to reduce weight.
• the switchable coupling preferably has an internal toothing and a spur toothing, via which the rotationally fixed connection between the shaft and the associated toothed wheel is produced.
• the coupling can be arranged axially displaceably on the shaft. Preferably, it is connected to two axially acting bearings and the bearings are fixed or connected by a spring to a shift finger.
• the shift finger can constantly be in contact with a shift gate and be rotatably mounted.
• the shift finger is also guided in the axial direction.
• the shift gate of the clutch is arranged on a rotatable, rotationally symmetrical shift gate body.
• the shift gate body has on its front or lateral surface elevations and depressions.
• the axis of rotation of the shift gate body preferably runs parallel or at right angles to the axes of rotation of the shafts.
• shift gates can be connected to one another in a rotatable manner, whereby the connection can take place via gears.
• the shift gates can be connected simultaneously with more than one clutch and perform several axial movements simultaneously.
• the position of the shift finger relative to the clutch is preferably variable.
• the rotatable mounting of the shift gate body takes place on or in the gearbox.
• a + 1 gears have a spur gear teeth.
• the spur toothing is preferably sawtooth-shaped in profile section.
• At least two shafts are provided with external teeth on which the components can be pushed. It is advantageous if the coupling is always held in an axial state by means of a spring. To reduce friction and improve the guidance of the guide, the axial movement of the shift finger is preferably guided via a linear ball bearing.
• the gears may preferably be formed in several parts, with annular serrations can be applied to the body.
• an overload protection in the transmission is preferably arranged in front of the drive pinion.
• a particularly compact design of the transmission is possible if the axes of rotation of the waves lie in at least two different planes.
• At least two gears have the same axis of rotation and are always connected to each other.
• a plurality of shift gate bodies are provided, their rotational movement is preferably controlled via a separate connecting shaft.
• the angular position of a plurality of shift gate bodies relative to one another is preferably adjustable by means of clamping components.
• FIG. 1 shows a bicycle with a multiple transmission integrated in the frame
• FIG. 2b is an exploded view of the assembled transmission with the transmission housing
• Figure 2c the multiple transmission in its housing in perspective view
• Figure 3 different assemblies of the multiple transmission in its arrangement in a perspective view
• FIG. 3b various assemblies of the multiple transmission in their
• FIG. 4 a shows the bottom bracket shaft assembly in a perspective view
• Figure 5a shows the central shaft assembly in perspective view
• FIG. 6a shows the connecting shaft assembly in perspective view
• FIG. 7a the drive shaft assembly in a perspective view
• FIG. 7b shows the drive shaft assembly in an exploded view
• FIG. 8 shows the coupling assembly in an exploded view
• Figure 9 shows the shift finger assembly in an exploded view
• FIG. 10 shows the mechanical control unit of the coupling assembly according to FIG. 8
• FIG. 12a shows the construction of the connecting shaft assembly in perspective view
• FIG. 12b shows the construction of the connecting shaft assembly in an exploded view
• FIG. 13 shows the structure of the main shift axle assembly in perspective view
• FIG. 14 shows the arrangement of the shift gate body according to FIG. 11 and its activation via the connecting shaft assembly according to FIG. 12 and the main shift axle assembly according to FIG. 13.
• Figure 15 shows the position of the Wegfingerbaumaschine of Figure 9 and the drive unit according to Figure 10 and their proceedingss ⁇ axes within the housing in an exploded view.
• 16 shows the positioning of the shift gate body according to FIG. 10, the connecting shaft assembly according to FIG. 12 and the main shift axle assembly according to FIG. 13 in exploded view;
• Figure 17 is a switching handle in an exploded view
• Figure 18 shows the concept sketch of a 4-speed transmission in section
• Figure 19 shows the concept sketch of a 15-speed transmission in section.
• FIG. 1 shows the side view of a bicycle, in the frame 1, the multiple transmission 4 is integrated with the cranks 5. Via a joint 2a and a spring-damper element 3, a Hinderrad ⁇ rocker 2 is arranged on the frame 1.
• the transmission is housed in a multi-part housing H, which, as Figure 2a shows, carrying housing parts 9, 10, 11, 12, 13, which has the function of bearing support and Positions ⁇ fixing the shafts and axles of the transmission, and from De - disgusting 6, 7, 8, which cover the housing H to the outside.
• screw caps 14, 15 are provided to fasten the bearings of the gear shafts.
• screw caps 14, 15 are provided about the cover 7, 8, the gear H with the frame 1 ver ⁇ prevented.
• the 4-speed transmission consists of the input shaft 22, the intermediate shaft 45 and the output shaft 93 provided with an Arbitriebsritzel 111.
• the drive pinion 111 is mounted on the Aus ⁇ output shaft 93.
• the input shaft 22 is on both sides of the Ge led housing H and provided at their ends with cranks 5.
• the drive shaft 22 has two gear wheels 200, 201 and the output shaft 93 has two gear wheels 204, 205.
• the intermediate shaft 45 is integrally provided with two gears 202, 203.
• the bearing of the shafts 22, 45, 93 via roller bearings 27 in the housing H.
• the torque introduced via the pedal cranks 5 is transmitted from the input shaft 22 via an intermediate shaft 45 to the output shaft 93. From the output shaft 93, the torque is transmitted to the auxiliary wheel HR via a drive pinion 111 and a chain, not shown here.
• the gearbox is connected via two externally controllable couplings 32, 104th , and two freewheels 29, 102.
• the clutch 32 and the freewheel 29 cooperate with the gears 200, 201 rotatably mounted on the input shaft 22 and the clutch 104 and the freewheel 102 interact with the gears 204 rotatably mounted on the output shaft 93 , 205 together.
• the storage preferably takes place via ball or needle roller bearings. In the axial direction Rich ⁇ the gears 200, 201, 204, 205 are secured against displacement.
• the gears 200 and 205 rotatably connected to the input shaft 22 and the output shaft 93 are connected.
• the outer parts of the clutches 29, 102 are connected to the gears 201, 204 and the inner parts with the shafts 22, 93.
• the gears 201, 204 rotate faster in the same direction as the shaft 22, 93, the freewheel rotates freely and without load at a torque transmission from the shaft 22, 93 to the respective gear 201, 204.
• the freewheels 29, 102 then run free when the gearwheel 201, 102 slows down rotates as the shaft 22, 93.
• the freewheels 29, 102 are secured by means of feather keys or a toothing on the shafts 22, 93.
• the gears 200, 201, 202, 203, 204, 205 must be selected such that the most uniform gradation of the individual gears is present.
• the determination of which of the gears of a shaft 22, 93 via a coupling 32, 104 or a freewheel 29, 102 to the shaft 22, 93 rotatably coupled, is dependent on the rotational speed difference of the gears on a shaft and the direction of torque transmission, ie, whether the moment is transferred from the gear to the shaft or from the shaft to the gear.
• the torque transmission from the shaft 22 takes place on the gears 200, 201.
• the clutch 104 If the clutch 104 is engaged on the gear 205, the torque is transmitted from the Intermediate shaft 45 with a ratio of 36 to 11 teeth on the output shaft 93.
• the gear 204 is driven by the intermediate shaft 45 in the ratio 17:30 and rotates so slower than the Aus ⁇ output shaft 93. Thereby, no moment of the insectslie 45 over the gear 204 transmitted to the output shaft 93.
• the freewheel 102 is disengaged. If the clutch 104 is disengaged, the shaft 93 tries to stop and the torque is then transferred automatically via the freewheel 102, since now the gear 204 rotates faster than the shaft 93.
• the coupling means 29, 32; 102, 104 are arranged within the transmission (viewed in the direction of travel F) to the left of the gear 200, 201, 204, 205, so that the actuation of the clutches 32, 104 can take place from an outer side of the housing H. It must be noted that switching operations may require more than one clutch to be operated at the same time. This has the consequence that a time-synchronous engagement or disengagement is necessary.
• Both clutches 32, 104 are disengaged and both freewheels 32, 102 transmit the torque via the gear wheels 201, 203 to the intermediate shaft 45 and from there via the gearwheels 202, 204 to the output shaft 93.
• the ratio is 1.47 fast.
• the clutch 32 on the input shaft 22 is engaged and the coupling 104 disengaged on the output shaft 93.
• the clutch 32 on the input shaft 22 is disengaged and the clutch 104 is engaged on the output shaft 93. Dö's moment is transmitted via the gears 201, 203 to the intermediate shaft 45 and from there via the gears 203, 205 to the output shaft. The translation is 2.73 in the fast.
• Both clutches 32, 104 are engaged.
• the torque is transmitted via the gears 200, 202 to the intermediate shaft 45 and from there via the gears 203, 205 to the output shaft 93.
• the transmission is 3.93 in the fast.
• This 4-speed transmission offers a good transmission bandwidth.
• the individual gradations between the courses are very rough and therefore only suitable for very simple types of bicycles.
• One way to realize this is to connect in series two identical 4-speed gearbox in series, resulting in 16 theoretically possible switching combinations. So that the cyclist can not perceive any large differences in treadmill frequency between the adjacent aisles, which can lead to a loss of driving comfort and acceleration capacity, the size and gradation of the 16-speed gears must be sensibly selected.
• the translation jumps between the individual courses should not be too large and relatively gleich ⁇ moderate.
• the translation width should correspond approximately to that of a commercially available chain circuit.
• the aisles are realized as follows:
• the clutch 32 is engaged, the clutch 69 is disengaged, the clutch 70 is disengaged, and the clutch 104 is disengaged.
• the torque passes from the gear 200 to the gear 202 of the intermediate shaft 45, from here via the gear 202 to the gear 79 of the intermediate shaft 42 and via the gear 80 to the gear 41 of the intermediate shaft 44 and from here via the gear 40 on the gear 31 of the output shaft 93. This results in a ratio of 0.67 ratio.
• 4th gear In 4th gear, the clutch 32 is disengaged, the clutch 69 is disengaged, the clutch 70 disengaged, and the clutch 104 is engaged.
• the moment runs from the toothed wheel 201 to the toothed wheel 203 of the intermediate shaft 45, from here via the toothed wheel 42 to the toothed wheel 79 of the intermediate shaft 62, then via the toothed wheels 80, 41 to the intermediate shaft 44 and from here via the toothed wheels 41 205 to the output shaft 93. This results in a ratio of 0.88.
• the clutch 32 is disengaged, the clutch 69 ein ⁇ coupled, disengaged the clutch 70 and the clutch 104 Scheme ⁇ coupled.
• the torque passes through the gears 201, 203 to the intermediate shaft 45, from here via the gears 203, 71 to the intermediate shaft 62, via the gears 80, 41 on the intermediate shaft 44 and from here via the gears 41, 205 on the Output shaft 93. This results in a ratio of the ratio 1, 44th
• the clutch 32 In the 9th gear, the clutch 32 is disengaged, the clutch 69 Wegkup ⁇ pelt, coupled the clutch 70 and the clutch 104 disengaged.
• the torque extends via the gears 200, 202 to the intermediate shaft 45, from here via the gears 203, 71 to the intermediate shaft 62, then via the gears 72, 40 to the intermediate shaft 44 and from here via the gears 40, 31 the output shaft 93. This results in a ratio of the ratio 1, 63.
• the clutch 32 In the 11th gear, the clutch 32 is engaged, the clutch 69 Solutionskup ⁇ pelt, the clutch 70 disengaged and the clutch 104 engaged
• the moment passes through the gears 201, 203 on the intermediate shaft 45, then on the gears 203, 71 on the intermediate shaft 62, from here via the gears 80, 41 to the intermediate shaft 44 and then via the gears 41, 205 to the output shaft 93.
• the gear ratio here is 2.06.
• the clutch 32 In the 14th gear, the clutch 32 is disengaged, the clutch 69 is engaged, the clutch 70 is engaged and the clutch 104 is engaged.
• the torque curve takes place via the gears 201, 203 on the intermediate shaft 45, from here via the gears 203, 71 on the sept ⁇ shaft 62, then on the gears 72, 40 on the intermediate shaft 44 and via the gears 40, 31 on the output shaft 93. This results in a transmission ratio of 3.30.
• the torque transmission is always on the Frei ⁇ run of the partner gear, when a clutch is disengaged.
• the translations must be increased in the embodiments described above. This is done by the gear ratio of the drive pinion 111 to the pinion 63 on the rear wheel HR.
• the resulting total translation with its sorbents can be taken from the following table:
• N be an arbitrary course between 1 and 14.
• the ratio of the gear N + 1 is divided by the gear ratio N. From the quotient subtract 1 and multiply the result by 100. The result is the jump between gears N and N + 1 in%.
• the total translation is calculated from the quotients of the last and the first gear.
• the sealing takes place via two on the dowel sleeves 23, 24 shaft seal rings 25, 26.
• the inner part of the freewheel 29 is rotationally connected to the input shaft 22.
• the outer part is rotationally connected to the gear 201.
• the gear 27 is fixedly connected to a coupling 30 and mounted on the needle bearing 31 on the input shaft 22.
• the clutch 32 is rotationally fixed but axially displaceable on the input shaft 22 applied. Between the freewheel 29 and the clutch 32 be ⁇ there is a thrust washer 33.Um to ensure independent turning both ' gears 200 and 201, between them a Pass ⁇ disc 34 and an axial needle bearing 35 with two thrust washers 36 and 37 attached. In order to ensure independent operation of the freewheel 29 and the ball bearing 20, a thrust washer 38 is mounted between them.
• the central shaft assembly 17 is shown.
• the central shaft 39 is rigidly secured in the housing parts 9, 10 and 11.
• On this central shaft 39 are a total of four gears 40, 41, 202 and 203 of which two are each mounted on a connecting piece 44 and 45 rotationally.
• the connecting pieces 44 and 45 are mounted on the central shaft 39 via the needle bearings 46, 47, 48 and 49.
• On the side of the gears, towards the housing clamps, are each an axial needle bearing 50, 51, 52, 53, each with two thrust washers 54, 55, 56, 57, 58, 59, 60, 61.
• FIG. 6b shows the structure of the connecting shaft assembly 18.
• a coupling shaft component 65, 66 is fixedly mounted.
• the coupling shaft components 65, 66 have external teeth.
• On the outer piece of the coupling shaft components 65, 66 is in each case a ball bearing 67, 68 applied, which is mounted in the housing parts 9 and 10.
• On each coupling shaft component 65 and 66 are each a Kupp ⁇ ment 69, 70.
• the gears 71, 72 are fixedly mounted on the coupling elements 73, 74 which are mounted on the needle bearings 75, 76 on the shaft parts 63 and 64.
• the clutches 69, 70 are rotationally and axially displaceable on the clutch shaft components 65, 66 designed to a rotationally fixed connection between the coupling shaft components 65, 66 and the gears 71, 72 to produce.
• the gear wheels 79, 80 are connected to the freewheel 83, 84 via a respective connecting element 81, 82.
• the outer part of the freewheels 83, 84 is in each case connected to the connecting element 81, 82 in a rotationally fixed manner.
• the inner part is in each case rotationally connected to the Welleneducations ⁇ piece 61.
• the gear wheels 79, 80 are mounted on the needle bearings 85, 86 via the connecting elements 81, 82.
• On the kaus ⁇ elements 81, 82 is ever a ball bearing 87, 88, which is axially secured by two respective retaining rings 89, 90, 91, 92.
• the connecting shaft assembly is mounted in the housing part 11.
• FIGS. 7a, 7b show the output shaft assembly 19.
• the output shaft 93 is mounted in the housing parts 9, 10 via two ball bearings 94, 95 and sealed to the outside with shaft seals 98, 99 lying on dowel sleeves 96, 97.
• the toothed wheel 204 is connected to the freewheel 102.
• the inner part of the freewheel 102 is connected in a rotationally fixed manner to the bottom bracket shaft 93.
• the outer part is rotationally connected to the gear 204.
• the gear 205 is fixedly connected to a coupling 103.
• the clutch 104 is rotationally fixed but axially displaceable on the output shaft 93 applied.
• the coupling component 103 and the gear 205 are mounted on the output shaft 93 via the needle bearing 105.
• a thrust washer 106 Between the clutch assembly 104 and the clutch component 103 is a thrust washer 106.
• an axial bearing 107 with two thrust washers 108, 109 is mounted between them.
• a thrust washer 110 is also mounted between them.
• a pinion 111 via a pinion holder 112 is rotationally fixed on the Wel ⁇ le 93 outside of the housing H applied.
• 8 shows an embodiment of a coupling assembly 32.
• a coupling element 114 is applied to the not shown here Druckfingerbauffle 121. This coupling element 114 is to ensure a loss-less possible rotation with two thrust bearings 115, 116 stored. The arrangement is secured axially against slipping with a securing ring 117.
• FIG. 9 shows the mechanical control of a clutch assembly.
• the coupling assembly is fixedly connected via coupling elements 118, 119, 120 with a switching finger assembly 121.
• This shift finger assembly 121 runs on a Wegkulis ⁇ sen redesign 122 provided with an external toothing, which is mounted on a ball bearing 173.
• the coupling component 113 is a coupling component 124 on which a toothed wheel 200 is mounted.
• a thrust washer 126 Between the Kupplungsbauele ⁇ element 124 and the coupling component 113 is a thrust washer 126, the components 116, 117, 114, 115, 113, 124 together form the coupling 32nd
• Figures 10 and 11 show the Heidelbergfingerbaurie 121.
• a Heidelbergfin ⁇ gerbaueria consists of the two Heidelbergfingergephaseusen 127, 128, in which a shift finger 129 via two ball bearings 130, 131 is mounted.
• the bearings 130, 131 lie in a connecting component 132.
• the shift finger 129 is secured against slipping by means of three securing rings 133, 134, 135.
• a linear ball bearing 136 is located between the finger housings 127, 128.
• the shift finger 129 of the shift finger assembly 114 runs on a shift gate body 122.
• the shift finger assembly 114 is connected to the clutch assembly of FIG.
• the shift finger 129 is pulled over the coupling elements 118, 119, 120, the coupling assembly and a Switzerlandfe ⁇ 136 against the frontally waved Heidelbergkulissenisson 122 .
• the tension spring 136 is an eye screw 137 with the Koppel ⁇ element 114 of the coupling assembly and a further eyesight screw 135 with a housing part 9, 10, 11, connected.
• the gear 200, which is applied to the clutch component 124 is concentric with the clutch component 113.
• the position of the shift finger 129 on the front side of the shift gate body 122 (shaft or shaft) determines whether the clutch 32 is engaged or disengaged.
• the tension spring 136 keeps the clutch 32 engaged.
• Figure 12 shows the structure of a connecting shaft assembly.
• the connecting shaft 140 is supported by two ball bearings 141, 142 in the housing parts 12, 13.
• the bearings 141, 142 run on two gears 143, 144 with hub 143a and 144a against each thrust washer 145, 146.
• Centered on the connecting shaft 140 are two further ball bearings 147, 148 auf ⁇ brought, which support the connecting shaft 140 in the housing part 11.
• the bearings are secured by a further gear 149, two dowel sleeves 150, 151 and a collar 152 against slipping.
• FIG 13 shows the structure of the shift driver assembly.
• the flange-shaped Wegan horrungswelle153 has on its front side a plurality of recesses 153a and a hexagon piece 153b. It is mounted on the ball bearings 154, 155 in the housing parts 9, 12. On the Heidelbergan horrungswelle 153 two gears 156, 157 are fixed by means of four screws 158, 159, 160, 161 and held with a Dis ⁇ tanzular 162 at a distance.
• the ball bearing 154 is applied via a spacer sleeve 163 on the Heidelbergan horrungswelle 153. About the wells on the Heidelbergan tenuungswelle 153 runs an Index- pressure piece 164.
• the cable drum 165 On the hexagonal piece (153b) of the Heidelbergansteue ⁇ tion shaft 153 is the cable drum 165. This is the Auf ⁇ acceptance of the switching cable 166 and for passing the switching pulse.
• the cable drum 165 is located in a housing, consisting of a Weg- housing 167 and a switch housing cover 168th
• FIG. 15 shows the structure and the positioning of the shift finger assemblies 179, 180, 181, 182 and their shift finger axes 183, 184, 185 in the transmission. Furthermore, the coupling elements 186, 187, 188, 189, 190, 191 are also shown here. By way of example, the eyebolts 192, 193 fastened to the housings 9, 10 are shown.
• Figure 16 shows the structure and positioning of the parts shown in Figure 14 in the transmission.
• the shift gate body 171, 172 are mounted on the housing part 9 via the bearings 175, 176 and secured axially with the housing parts 12, 14.
• the Heidelbergan horrungsbauffle 178 of Figure 13 is mounted on the bearings 154, 155 in the housing parts 12, 14. Laterally on the shift driver assembly 178, the cable drum assembly 194 is attached.
• the shift gate body 169, 170 are mounted on the housing part 10 via the bearings 173, 174 and secured axially by the housing parts 13, 15.
• the connecting shaft assembly 177 is located above the bearings 148, 147 in the housing part 11 and via the bearings 141, 142 in the housing parts 12, 13th
• FIG. 17 illustrates an exemplary embodiment of a rotary handle assembly.
• This assembly consists of a Weg Bach- inner part 195 which can be fixedly mounted on the handlebar 18, a handle rotary body 196 in which the cables 197, 198 inserted the was ⁇ , and a shift handle rubber grip portion 199.
• Thrust Washer 56 Thrust Washer 57 Thrust Washer
• Shift finger axis 183 Shift finger axis 184 Shift finger axis

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Mechanical Engineering (AREA)
• Structure Of Transmissions (AREA)
• Gear Transmission (AREA)
• Transmission Devices (AREA)

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• 2004
  • 2004-09-15 DE DE102004045364A patent/DE102004045364B4/de not_active Expired - Fee Related
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  • 2005-08-30 TW TW094129647A patent/TW200616830A/zh not_active IP Right Cessation
  • 2005-09-09 WO PCT/DE2005/001580 patent/WO2006039880A1/de not_active Ceased
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