Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
  • F02N15/062—Starter drives
• • 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
  • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
  • F16H55/02—Toothed members; Worms
  • F16H55/08—Profiling
  • F16H55/0873—Profiling for improving axial engagement, e.g. a chamfer at the end of the tooth flank
• • 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
  • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
  • F16H55/02—Toothed members; Worms
  • F16H55/08—Profiling
  • F16H55/088—Profiling with corrections on tip or foot of the teeth, e.g. addendum relief for better approach contact
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N11/00—Starting of engines by means of electric motors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
  • F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
  • F02N15/067—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement the starter comprising an electro-magnetically actuated lever
• • 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
  • F16H57/00—General details of gearing
  • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings

Definitions

• DE 10 2008 042 434.5 relates to a reduction gear and a starter device for an internal combustion engine.
• the reduction gear is a speed-reducing coupling between a drive shaft and a
• Output shaft by means of at least two gears which are engaged with each other.
• the gears are formed straight toothed, the toothing between them is designed as a high toothing.
• the formation of the toothing as a high toothing makes it possible to significantly increase the overlap of the mutually engaged toothed component.
• a high toothing is a toothing in which the overlap of the toothing
• a high gearing has the advantage that the used
• straight toothed gears can be produced by means of conventional manufacturing processes and thus existing assembly processes can be maintained.
• a spur gear is provided with a lower gear ratio. This measure improves the engagement conditions and reduces the
• gear ratio also means that the dynamics of the starting device is changed, so that starting operations at extremely low temperatures can be affected. This in turn has the consequence that requirements of the customer's liability booklet can no longer be met or an adaptation of the requirements must be taken into account.
• helical toothing is provided between the intermeshing tooth partners, starting pinion and ring gear. This measure improves the engagement conditions and prevents the occurrence of vibrations and the associated noise level. This will cause the acoustic
• a toothing between two meshing gears, in particular a Andrehritzels, a starter device and a ring gear of an internal combustion engine is proposed, characterized by the noise level and the vibration behavior of the toothing
• At least one of the intermeshing wheels is an asymmetric geometry of
• Gear profiles provided, which extends at least over part of the axial length of the toothing.
• Starter pinion and ring gear is provided with an optimized toothing, which has a special profile to reduce the noise level during a starting operation of the internal combustion engine with meshing sprocket of the internal combustion engine and Andrehritzel the starting device.
• the optimized design of the pairing starter pinion and ring gear has the advantage that the optimized toothing significantly improves the operation in acoustic Way is optimized, ie overall, the noise level drops significantly.
• a compact and cost-saving design is possible. The cost savings are achieved in particular by the fact that a spur toothing is still used. As a result, axial forces can be avoided, which would otherwise have to be absorbed by structural measures of the bearing and the housing of the starting device.
• the storage of the drive and the crankshaft or the gears can be designed following the solution proposed according to the invention such that no or only small axial forces are to be absorbed.
• the improvement of the acoustic properties is achieved in that the toothing is designed as a high toothing. This allows an increase in
• Vibration level also has a positive effect on the service life of the optimized toothing between starter pinion and ring gear.
• noise-optimized high-toothing is understood as meaning a toothing in which the overlapping of the toothing is increased by reducing the normal-engagement angle and reducing the geometry of a tooth
• Tooth head has a withdrawal of the tooth head profile. Furthermore, the high-toothing is designed such that in the region of the tooth root, a reinforcement of the Zahnfußprofils is shown. This results in steeper flanks, a larger profile coverage and lower radial forces acting on the bearing of the gears. Furthermore, by the withdrawal of the tooth head profile causing a reduction of a noise
• the tooth height should be designed so that the uncorrected involute area achieves an effective minimum profile coverage of> 1 between the starter gear and the ring gear.
• the profile coverage e a represents the ratio of the engagement distance g a to the preoperative pitch p et .
• Interference on the teeth can also be realized a load capacity optimization of the toothing.
• the requirements are met on the one hand optimal noise and vibration behavior, on the other hand to a sufficient strength of the meshing gears.
• the increase of the profile overlap occurs, among other things, through the use of a reduced module for a specific gear ratio on the gear pair, which is to be determined by the following design:
• the module used must be selected according to strength, so that the load capacity is given in the area of the teeth of the toothing.
• the minimum usable module is according to experience at 1, 0 mm. However, this value is to be understood only as an indicative value since, if necessary, a lower modulus can also be possible by using improved materials.
• the high-toothing has a normal engagement angle of 10 ° to 35 °, preferably about 15 ° or about 25 °.
• the reduction of the normal engagement angle of the high gear results in steeper flanks, greater profile coverage and lower radial forces.
• the high-toothing compared to a conventional geometry is less sensitive to axial spacing deviations and concentricity errors, even the smoothness is improved.
• the pressure angle can be reduced to approximately 10 °, in particular if the profile coverage is> 1, 0 is. If the toothing is hobbed off, the pressure angle can change
• An advantageous embodiment of the proposed solution according to the invention is given by the fact that the toothed feet of the high-toothing have a shape deviating from a Trochoidenform.
• the tooth root radius of the toothing is reduced by the use of a smaller module.
• the Zahnfußform is advantageously replaced by a corrected Zahnfußverrundung to improve the Zahnfußfestmaschine instead of a conventional rounding of the tooth root.
• the optimized Zahnfußform deviates from the previously formed Trochoidenform.
• the tooth heads of the high toothing have a modified head region.
• the flank can be formed, for example, by means of a slight head rounding adapted to the module used.
• a head cancellation may be provided.
• Head return is represented by three mutually tangential radii, which are different, connecting each tooth flank and tooth head together. This last measure allows a shock-free inlet of force-transmitting tooth flanks, so that the wear
• the inventively proposed high-toothing can be produced by means of a conventional manufacturing process. There are no additional manufacturing steps to make so that the teeth can be made relatively inexpensive.
• the output shaft of the starter device is associated with a freewheel.
• the freewheel can be prevented that the already started internal combustion engine applied to the drive shaft of the reducer with a high speed and thus, for example, a connected via this electric motor damaged.
• the freewheel unilateral torque transmission is realized, so that the torque can be transmitted only from the drive shaft to the output shaft and not in the reverse direction.
• High toothing with an asymmetric geometry on the tooth profile which runs at least over a limited length of the toothing together.
• the asymmetric geometry of the tooth profile can both in the frontal region of the ring gear of the internal combustion engine as well as in the frontal region of the sprocket of the
• the starter device Internal combustion engine to be inserted in the axial direction Andrehritzels the starter device be executed.
• the toothing is designed such that the tooth thickness of either the Andrehritzels or the ring gear of
• Tooth root stress can be maintained both in the range of reduced tooth thickness and on the configured in normal tooth thickness range.
• the procedure should be as follows: When designing a noise-optimized spur gear, a reduction of the backlash is sought. At the same time, a minimum backlash of 0.3 mm should be maintained to secure the meshing of the Andrehritzels in the outer teeth of the ring gear of the internal combustion engine.
• designing the gearing proceed as follows:
• Gear geometry designed to ensure that a specified minimum foot and a minimum edge safety is maintained.
• the backlash present in the optimized gearing geometry may be less than 0.3 mm.
• Profile displacement factor for example, be made at the starter pinion, the tip diameter is to be maintained.
• the optimized tooth geometry is permitted according to the first design step. If this is not the case, in the optimized gearing according to the first design step, a module increase should be made and the process according to the second design step and the third
• Designing step i. the evaluation, be repeated.
• a starter device of an internal combustion engine with a pair of intermeshing toothings of starter pinion and ring gear, a side view of a toothing pair of starter pinion and ring gear with noise-optimized high-gearing,
• Figure 3 is a side view of the noise-optimized high gear
• Figure 4 is a view of an asymmetrical design
• FIG. 1 shows a starter device 10 in a longitudinal section.
• Starter device 10 includes, for example, a starter motor 13 and a
• Vorspuraktuator 16 (for example, relay, starter relay) on.
• the starter motor 13 and the electric Vorspuraktuator 16 are connected to a common
• the starter motor 13 functions to drive a starting pinion 22 when it is meshed with a ring gear 25 of an internal combustion engine not shown in FIG.
• the starter motor 13 has as
• Power classes are here, instead of the pole piece 31 and field winding 34 and permanent magnets conceivable.
• the pole shoes 31 in turn bypass an armature 37, which has a built-up of lamellae 40 anchor packet 43 and in grooves 46 arranged armature winding 49 has.
• the armature package 43 is pressed onto a drive shaft 44.
• a commutator 52 is mounted, which among other things is made up of individual commutator bars 55.
• the commutator bars 55 are so electrically connected in a known manner with the armature winding 49, that upon energization of the commutator fins 55 by carbon brushes 58, a rotational movement of the armature 37 in the pole tube 28 results.
• a arranged between the electric drive 16 and the starter motor 13 power supply 61 supplies in the on state, both the carbon brushes 58 and the
• the drive shaft 44 is commutator side supported with a shaft journal 64 in a sliding bearing 67, which in turn is held stationary in a Kommutatorlagerdeckel 70.
• Commutator bearing cap 70 in turn is fastened by means of tie rods 73, which are distributed over the circumference of the pole tube 28, so for example screws, for example two, three or four pieces, in the drive end plate 19. It supports the pole tube 28 on the drive end plate 19 and the tie rods 73, which are distributed over the circumference of the pole tube 28, so for example screws, for example two, three or four pieces, in the drive end plate 19. It supports the pole tube 28 on the drive end plate 19 and the
• a sun gear 80 connects to the armature 37 of the starter device 10, the part of a planetary gear, such as a
• Planetary gear 83 is.
• the sun gear 80 is surrounded by a plurality of planetary gears 86, usually three planet wheels 86, which are supported by means of rolling bearings 89 or plain bearings on journals 92.
• the planet gears 86 roll in a ring gear 95, which is radially mounted in the pole tube 28 of the starter 10. Towards the output side closes to the planetary gears
• the planet carrier 98 is in turn stored in an intermediate storage 101 and a slide bearing 104 arranged therein.
• the intermediate bearing 101 is designed cup-shaped, that in this both the planetary carrier 98 and the planet gears 76 are added. Furthermore, in cup-shaped
• the ring gear 95 is arranged, which is ultimately closed by a lid 107 relative to the armature 37. Also, the intermediate bearing 101 is supported with its outer circumference on the inside of the pole tube 28.
• the armature 37 has on the end remote from the commutator 52 of the
• the output shaft 1 16 is divided into several sections: the section located in the sliding bearing 104 of the intermediate bearing 101 is followed by a section with a straight toothing 125 (internal toothing), which is part of a shaft-hub connection 128.
• the shaft-hub connection 128 in this case allows the axially straight sliding of a driver 131st The driver
• the freewheel 137 (Richtgesperre) further consists of the inner ring 140, which is radially within the
• Outer ring 132 is arranged. Between the inner ring 140 and the
• Outer ring 132 clamping body 138 are arranged.
• the clamp bodies 138 in cooperation with the inner ring 140 and the outer ring 132, prevent relative rotation between the outer ring 132 and the inner ring 140 in a second direction.
• the freewheel 137 allows a circumferential relative movement between the inner ring 140 and the outer ring
• the inner ring 140 is integral with the starter pinion 22 and its helical teeth 143
• the starter pinion 22 may alternatively be designed as a straight toothed pinion.
• electromagnetically excited pole pieces 31 with exciter winding 34 could also be used.
• the electric Vorspuraktuator 16 and the armature 168 also has the task of moving a tension member 187 in the drive bearing plate 19 rotatably mounted lever.
• This lever 190 is usually designed as a fork lever and engages with two "tines", not shown here, two disks 193, 194 on its outer circumference, thereby moving a pinched driving ring 197 between them against the resistance of the spring 200 and thus the starting pinion 22 in the sprocket 25 of the internal combustion engine, not shown in Figure 1kohlspurt.
• the electric Vorspuraktuator 16 has a bolt 150, a
• the lid 153 includes a housing 156 made of steel, which is fastened by means of a plurality of fastening elements 159 (screws) on the drive end plate 19.
• a pusher 160 for exerting a tensile force on the fork lever 190 and a switching device 161 is arranged.
• Pusher 160 has a winding 162, the switching device 161 has a winding 165 on.
• the winding 161 of the pusher 160 and the winding 165 of the switching device 161 each cause in the on state an electromagnetic field which flows through various components.
• the shaft-hub connection 128 may take place with a
• Spur gearing 125 may also be provided with a steep thread toothing.
• the combinations are possible, according to which a) the starting pinion 22 is helically toothed and the shaft-hub connection 128 has a straight toothing 125, b) the starting pinion 22 is helically toothed and the shaft-hub connection 128 has a helical toothing or c) the Andrehritzel 22 is spur-toothed and the shaft-hub connection 128 has a helical toothing.
• FIG. 2 shows, on the basis of a single tooth, the design according to the invention of an asymmetric toothing with a high toothing with a partially reduced tooth width in the front region of the toothing.
• an asymmetric toothing 214 will be described below with reference to a single tooth 202.
• the single tooth 202 may be a tooth of a toothing, which is preferably formed as a straight toothing.
• the single tooth 202 shown in FIG. 2 with an asymmetrical toothing 214 can be formed either on the outer toothing of a starting pinion 22 as shown in FIG. 1 or on an outer circumference of a toothed ring 25 which serves to turn on an internal combustion engine.
• a tooth flank 204 is formed in a tooth width 206. Following the solution according to the invention, it is proposed that on the tooth flank 204, as shown in FIG. 2, within a front region 228 extending from an end face 32 of FIG.
• Single tooth 202 extends along a reduced tooth width 208, a reduced tooth thickness 212 is formed.
• the reduced tooth thickness 212 extends from the end face 230 of the single tooth 202 along the reduced tooth width 208 up to a transition flank region 226. Within this transition flank region 226 on the tooth flank 204, the reduced tooth thickness 212 gradually transitions to an original tooth thickness 210. This means that the asymmetric toothing 214 is formed on the tooth flank 204.
• Gearing 214 is designed so that the tooth thickness 210 within the front portion 228 of the single tooth 202 - seen from the end face 230 of the Andrehritzels 22 or the ring gear 25 - on the reduced
• Tooth width 208 is performed only on one side of the tooth flank 204 of the single tooth 202, so that within this front portion 228 a tooth flank 204 of the single tooth 202 has a reduced tooth thickness 212.
• this front region 228, characterized by the reduced tooth thickness 212 along the reduced tooth width 208, is a desired backlash for example, 0.3 mm. This causes the gearing over the
• the remaining part of the tooth width 206 minus the reduced tooth width 208 can be designed with a significantly lower backlash, which is less than 0.3 mm.
• Toothed ring 25 ensured and on the other hand, the noise level
• asymmetric toothing 214 is a top circle of the single tooth 202 with the reference numeral 216, a partial circle of the single tooth 202 with the reference numeral 218 and the root circle with the reference numeral 220 is designated.
• Critical is one
• Reference numeral 226 designates the transition flank region within which the reduced tooth thickness 212 changes to the original tooth thickness 210.
• the edge-pressing security against the stress occurring in the region of the tooth root 220 is maintained both in the region of reduced tooth thickness 212 and in the region which is not reduced, i.e. in the region of reduced tooth thickness 212. the original tooth thickness 210 is formed.
• the following procedure is used to design the asymmetric toothing 214 proposed according to the invention: In the design of the noise-optimized, e.g. formed as a straight toothing asymmetrical teeth 214, the reduction of the backlash of the tooth flanks 204 of the individual teeth 202 is sought. At the same time it is used to secure the safe tracking of the
• Andrehritzels 22 in the teeth of the ring gear 25 at least one
• the backlash may be below 0.3 mm.
• a tooth geometry with a reduced tooth width 208 is derived from the optimized tooth geometry derived in the first step when the required backlash of 0.3 mm is reached.
• the same radius is to be used on the tooth root 222 as in the case of the optimized tooth geometry obtained according to the first method step.
• the reduced tooth width 208 can, starting from the original tooth width 206, by setting a smaller profile displacement factor, for example in the manufacture of
• the safety on the tooth root 222 of the tooth geometry is at least equal to that derived from a proven one
• gearing geometry specified minimum footing then the determined in the first step optimized gearing geometry is allowed. If, in the third method step representing an assessment, it is ensured that the safety in the tooth root 222 of the tooth geometry is at least equal to that of the reference toothing according to the present design step, then the optimized tooth thickness determined in the first method step
• Gear geometry are allowed. If, on the other hand, this is not fulfilled, then in the optimized method determined and designed in the first method step Gearing a module increase the interpretation of the gearing are made and the subsequent two process steps, ie the second and the third process step, be run through again.
• the tip diameter 216 is highlighted in Figure 2 with d a , the pitch diameter 218 d and the root diameter d f .
• FIG. 3 shows a side view of a toothed pairing of starting pinion and ring gear with noise-optimized high-toothing.
• FIG. 3 shows that individual teeth 202 of the toothed rim 25 of the internal combustion engine and of the starting pinion 22 of the starter device 10 mesh with one another. Both the ring gear 25 of the internal combustion engine and the starting pinion 22 of the starter device 10 are shown only partially in the illustration according to FIG. A
• External teeth of the ring gear 25 of the internal combustion engine is designed as a noise-optimized high gear 232, which meshes with individual teeth 202 and also designed as a noise-optimized high gear teeth 234 external teeth of the starter device.
• the starting pinion 22, which is mounted on the output shaft 16, is meshed with the ring gear 25 of the internal combustion engine.
• the illustration according to Figure 4 is a side view of the noise-optimized high toothing can be seen, both on the sprocket of the
• Internal combustion engine can be designed as well as to be wellpurenden Andrehritzel the starter device.
• FIG. 4 shows that a single tooth 202 of the noise-optimized high-toothing has tooth flanks 204, which in contrast to conventional ones
• Gearing profiles 238 have modified areas.
• the modified regions of the tooth flanks 204 of the noise-optimized toothing proposed according to the invention, ie the high toothing 232, 234, on the one hand have a reinforced tooth root 236 formed in comparison to the conventional tooth root profile 238 and one by reference numeral 240 in FIG Contrary to the conventional tooth profile trained tip retraction 240 below the tip diameter d a 216.
• An essential goal of the design of the high-toothing is to design the toothed sleeve such that the uncorrected involute region is an effective one
• the profile overlap ⁇ is defined as the ratio of the engagement distance to the (front) engagement pitch p et .
• the (front) engagement pitch p et m t * ⁇ * cosa t is the distance between two right or left flanks along the engagement line.
• the modulus used should be selected such that load-bearing tooth bases 222 are obtained.
• the minimum usable module is according to experience at 1, 0 mm. However, this value is to be understood only as an indicative value, since the use of improved materials also means a
• the inventively proposed noise-optimized teeth 232, 234, in particular formed as a high toothing, is provided with a Normal engagement angle of 10 ° to 35 °, preferably a little 15 ° or slightly 25 ° provided.
• the normal engagement angle can be reduced to about 10 °, especially if a profile coverage of> 1, 0 is given. If the toothing is hobbed off, the normal engagement angle can be reduced, for example, to 15 °. By increasing the strength, usually given by a different choice of material, the normal engagement angle can also assume values smaller than 10 °.
• the toothed feet 222 of the noise-optimized toothings 232, 234 have, in particular, a shape deviating from the trochoidal shape. Tooth root rounding 224 is significantly reduced by the use of the smaller module. For example, to improve tooth root strength, the tooth root mold can advantageously replace the conventional fillet 224 of the tooth root 222 with a corrected version. This is done while maintaining the engagement of the intermeshing
• the tooth heads of the noise-optimized toothing 232, 234 are provided with a modified head region.
• Tooth region the tooth edge 204, for example, by a module adapted to the module used each slightly rounded or
• Head return 240 may be modified. Both measures allow a shock-free inlet of the force-transmitting tooth flanks 204. This, on the one hand, reduces wear and, on the other hand, reduces the generation of noise.
• Torsional backlash may be less than 0.3 mm in this design.
• a gearing geometry is derived, which is a reduced
• Reduction of the tooth width can be achieved by setting a smaller one
• Profile displacement factor at the starter pinion 22 are made for example, the tip diameter 216 should not be changed.
• Gearing geometry according to the second method step is at least equal to the foot safety at a reference gearing, the optimized
• Gear geometry approved according to the first method step If the comparison is negative, the first method step for obtaining an optimized tooth geometry should be carried out by a module increase and the subsequent method steps 2) and 3) should be repeated.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Gears, Cams (AREA)
• Gear Transmission (AREA)
• Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (2)

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• 2010
  • 2010-03-26 DE DE201010003361 patent/DE102010003361A1/de not_active Ceased
• 2011
  • 2011-03-04 WO PCT/EP2011/053304 patent/WO2011117055A2/de active Application Filing
  • 2011-03-04 EP EP11709053A patent/EP2553258A2/de not_active Withdrawn
  • 2011-03-04 JP JP2013501711A patent/JP5787975B2/ja not_active Expired - Fee Related
  • 2011-03-04 CN CN201180026174.XA patent/CN102918257B/zh not_active Expired - Fee Related

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