WO2017190727A1 - Transmission - Google Patents

Transmission Download PDF

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Publication number
WO2017190727A1
WO2017190727A1 PCT/DE2017/100309 DE2017100309W WO2017190727A1 WO 2017190727 A1 WO2017190727 A1 WO 2017190727A1 DE 2017100309 W DE2017100309 W DE 2017100309W WO 2017190727 A1 WO2017190727 A1 WO 2017190727A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
transmission
pinion
shift
gears
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE2017/100309
Other languages
German (de)
English (en)
Inventor
Daniel Schlereth
Adam Peter Fros
Sascha Haase
Jakob Glück
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Universitaet Kassel
Original Assignee
Universitaet Kassel
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Universitaet Kassel filed Critical Universitaet Kassel
Publication of WO2017190727A1 publication Critical patent/WO2017190727A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/36—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with a single gear meshable with any of a set of coaxial gears of different diameters
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears

Definitions

  • the invention relates to a transmission, in particular for arrangement on an internal combustion engine of a vehicle, comprising a first gear stage with a first gear of a smaller diameter and at least a second gear stage with a second gear of a larger diameter, wherein between the gears a non-circular gear is arranged, and wherein a shift pinion is provided which is adapted to engage in the first gear or in the second gear, wherein the shift pinion is engageable with the non-circular gear, to switch between the engagement with the first gear and the engagement with the second gear , STATE OF THE ART
  • CN 10 17 37461 A discloses a transmission with multiple gear stages, and it is a first gear stage with a first
  • a still further gear in turn has a larger diameter than the second gear, and with the three gears of different diameters, a shift pinion can be brought into engagement by an axial displacement, so that different gear ratios between, for example, a drive shaft and an output shaft can be achieved.
  • the distance between the drive shaft and the output shaft must vary in order to compensate for the different diameters of the gears.
  • the object of the invention is an improvement of a transmission with at least two gear stages, with a traction interruption-free switching between two gear stages is possible.
  • a drive shaft and an output shaft of the transmission gear cross-over a structurally fixed distance from each other may have. This object is based on a transmission according to the
  • the invention includes the technical teaching that the switching pinion is accommodated on a pivoting element, wherein with a pivoting of the pivoting element, the position of the switching pinion to the
  • the core idea of the invention is the inclusion of the switching pinion on a pivotable pivot member, so that the pivot member can assume various pivotal positions to the
  • a drive shaft and an output shaft can be integrated in the transmission, which for all
  • Gear stages have a structurally constant distance from each other.
  • the pivot member pivots the shift pinion precisely so that the shift pinion can be arranged with a required distance to the gears of different diameters and the non-circular gear.
  • means are provided with particular advantage, which are adapted to pivot the pivoting element such that the toothing between the shift pinion and the various
  • an output shaft is provided around which the pivoting element is pivotally received.
  • the output shaft has a longitudinal axis in which the output shaft is rotatable, and a
  • Pivot axis of the pivot element coincides with the longitudinal axis of the output shaft.
  • Transmission pinion transmits the torque through the rotationally fixed receptacle on the output shaft to this.
  • a Kraftftuss be built on different gears, and it can be brought into engagement with the shift pinion gears of different sizes, without the distance of the axis of rotation of the gears must be changed with the longitudinal axis of the output shaft.
  • the pivot member is movably received on the shift pinion and the transmission pinion in the longitudinal axis of the output shaft on this.
  • the pivot member with the shift pinion and with the transmission pinion can thus be moved along the longitudinal axis of the output shaft to be engaged with the various gears arranged parallel to each other.
  • the shift pinion over all
  • Gears are moved away by this is moved along the longitudinal axis on the output shaft.
  • the distance of the switching pinion to the common axis of rotation of the gears is corresponding to the
  • Transmission pinion be formed.
  • guide flanks are formed between the gears, which adapt to the Position of the shift pinion to the different diameters of the gears interact with the pivot member.
  • Guide flanks have a respective guide contour over which a leading edge of the pivoting element can slide.
  • Guide contours of the guide flanks are shaped so that there is always a technically correct distance between the axis of rotation of the shift sprocket and the axis of rotation of the gears and thus also the non-circular gear even when engaging the shift pinion in the non-circular gear.
  • there is always a technically correct engagement of the teeth with each other regardless of whether the shift pinion is engaged with a round gear of the first or second gear stage or with the non-circular gear between the two gear stages.
  • the non-circular gears have circumferential segments that communicate with the adjacent smaller gear on a first side and with the adjacent larger gear on a second side, respectively
  • the non-circular gear has a first circumferential segment, which is adapted to the first gear with the smaller diameter and that the non-circular gear has a second circumferential segment, which is adapted to the second gear with the larger diameter.
  • the adaptation of the diameter is such that the teeth of the respective circumferential segments in
  • Matching with the smaller or larger gear may be formed in a continuous manner, so that the
  • Transmission pinion is moved in the longitudinal axis of the output shaft. For example, a first leading edge is in the region of the first
  • the two guide flanks face about 180 ° and enclose the gear on a segment of slightly more than 180 °.
  • the transmission may comprise at least a third gear having a larger diameter than the second gear, wherein another un round gear between the second gear and the third gear is arranged.
  • the transmission may have more than two, more than three or even more than four gear stages. All gears are preferably arranged adjacent to each other in the package and have a common axis of rotation.
  • the gears are formed as cylindrical wheels with an outer toothing, wherein the pivoting element with the shift pinion from the outside of the
  • Gears is in operative connection with these.
  • the gears may be formed as ring gears and have an internal toothing, wherein the pivot member with the shift pinion from the inside of the gears with these in
  • the gears may be both an external toothing and a
  • first pivot member with a first shift pinion is located on the outside of the gears and a second pivot member with a second shift pinion is located inside the gears.
  • the pivot member may be received for receiving the shift pinion in operative connection with the external teeth on the output shaft, so that a torque flow can take place from the drive shaft to the output shaft.
  • the axis which forms the axis of rotation of the gears is used as the input or output axis.
  • retaining elements are provided for holding the at least one pivoting element when it is in engagement with the round toothed wheels. This can be done on the
  • Pivoting element to be formed on the pivot elements holding Anne, which engage in the holding elements, wherein the engagement is generated by the axial displacement of the pivoting element on the output shaft or on the drive shaft.
  • the transmission has a shift control with a shift drum, which interacts with a tapping element for the axial adjustment of the pivoting element with the shift pinion.
  • the shift drum has groove guides, wherein intersecting groove guides a shift pin is arranged at an intersection, which is rotatable with a rack, which is formed on a shaft traversing the shift drum.
  • Figure 1 is a view of a first embodiment of the
  • Figure 2 shows the embodiment of the transmission according to Figure 1 in a second switching position
  • FIG. 3 shows the embodiment of the transmission according to FIG. 1 in a third switching position
  • Figure 5 is a side view of the transmission according to the
  • FIG. 6 is a perspective view of a non-circular gear
  • FIG. 7 shows the view of a shift control with a shift drum in a first shift position
  • Figure 8 shows the shift drum of Figure 7 in a second switching position
  • Figure 9 is a view of a shaft with a rack extending through the shift drum.
  • Figures 1, 2 and 3 show in a respective perspective view of a first possible embodiment of the transmission 1 according to the invention with three gear stages.
  • the first gear stage is formed by a first gear 10 of a small diameter, and the second
  • Gear stage is formed by a second gear 11 of a larger diameter
  • the third gear stage is formed by a third even larger gear 20.
  • Between the small gear 10 and the larger gear 11 is a non-circular gear 12, and between the larger gear 11 and The largest gear 20 is another non-circular gear 21.
  • the embodiment of the transmission 1 a total of five gears 10, 11, 12, 20 and 21, wherein the gears 10, 11 and 20 are designed to be round and wherein the intervening gears 12 and 21 have a non-circular shape. All
  • gears for example, forms a drive axle.
  • the gears are arranged in a package to each other, wherein the smallest round gear 10 and the largest round gear 20 complete the package of gears in the axial direction. All gears are designed according to the embodiment as spur gears with external teeth.
  • Switching pinion 13.1 in arrangement on a pivoting element 14.1.
  • the pivoting element 14.1 is pivotable about an output shaft 15th
  • the pivoting element 14.1 is on the output shaft 15th
  • guide flanks 18 are formed, which cooperate with the pivoting element 14.1 to adapt the position of the Wegritzels 13.1 to the different diameters of the gears 10, 11 and 20.
  • the guide flanks 18 each have a guide contour via which a leading edge 19 of the
  • Swivel element 14.1 can slide off.
  • Figure 1 shows the transmission 1 in a state in which the switching pinion 13.1 is in engagement with the smallest gear 10.
  • the pivoting element 14.1 is pivoted about the longitudinal axis 17 of the output shaft 15 such that the shifting pinion 13.1 has the technically necessary distance to the first gear 10, so that the teeth mesh cleanly.
  • the Gear set rotates thereby about the axis 31 counterclockwise, so that a peripheral portion of the first gear 10 is achieved with the non-circular gear 12 by the teeth of the first gear 10 and the non-circular gear 12 extend in respective extension to each other. In this circumferential position can be shifted axially up to a next gear stage, the pivot element 14.1 with the switching pinion 13.1 and the transmission pinion 16.1 in
  • Figure 2 shows an operating situation of the transmission 1, in which the switching pinion 13.1 is in engagement with the non-circular gear 12, so that the switching pinion 13.1 coming from the smaller gear 10 in a sense on the non-circular gear 12 runs up to the larger diameter of the second gear 11th The leading edge 19 of the slides
  • Figure 3 shows an operating situation of the transmission 1, in which the
  • Shift pinion 13.1 is just in engagement with the second gear 11, until finally a further displacement of the pivot member 14 takes place in the longitudinal axis direction 17, so that the shift pinion 13.1 can finally engage with the further non-circular gear 21 into engagement.
  • the switching pinion 13.1 is in a circumferential position in engagement with the other non-circular gear 21 in which the teeth coincide with the teeth of the next largest non-circular gear 21, so a further displacement of the pivot member 14.1 in
  • pivoting element 14.1 For locking the pivoting element 14.1 holding elements 23 are provided which serve to hold receiving the pivot member 14.1 when this is in engagement with the round gears 10, 11, 20. In FIG. 3, the pivoting element 14.1 is in a holding arrangement in the middle holding element 23.
  • Figures 4 and 5 show in a perspective view and in a side view of another embodiment of the transmission 1 with a first gear 10 of a smaller diameter and with a second gear 11 of a larger diameter, wherein between the
  • Gears 10 and 11 a non-circular gear 12 is arranged.
  • the embodiment thus shows a transmission 1 with two gear stages.
  • the gears 10, 11 and 12 are formed so that they have both an external toothing and an internal toothing. Outside the external toothing is a first pivot member 14.1 with a first shift pinion 13.1, and within the gears 10, 11 and 12 is a second pivot member 14.2 with a second
  • the outer pivot member 14.1 is on a
  • the embodiment shows a development of the transmission 1 according to Figures 1, 2 and 3, wherein the spatial distance between the output shaft 15 and the drive shaft 22 does not have to be changed to each other in the different switching positions of the transmission 1.
  • two holding elements 23 are shown, wherein the pivoting element 14.1 is seated in a holding arrangement in a first holding element 23.
  • Figure 5 shows by the side view, the guide edge 18 between the first gear 10 and the non-circular gear 12.
  • the gears 10, 11 and 12 have both an outer toothing and an inner toothing, so that the torque transmission between the drive shaft 22 and the output shaft 15 via the respective gears 10, 11 and 12 takes place.
  • Figure 6 shows a perspective view of a non-circular gear 12 with a first transmission area 32 for upshifting and a second transmission area 23 for downshifting.
  • the transfer area 32 for upshift coincides with the adjacent smaller gear, so that the teeth of the non-round
  • Gear 12 form a respective extension
  • Transmission range 33 for downshifting coincides in sections with the toothing of the adjacent larger gearwheel.
  • the contour of the guide flanks 18 is determined so that the teeth of the non-circular gear 12 can take place in any circumferential position of the teeth with the shift pinion.
  • a shift control 24 is shown with a shift drum 25, and in the outer peripheral surface of the shift drum 25 are located
  • Tapping element 26 which can be moved in the groove guides 27.
  • the tapping element 26 is coupled to the pivoting element 14.1, 14.2, so that it can be displaced axially by means of an activation of the shunt control 24 on the output shaft 15 or the drive shaft 22.
  • the shift control 24 serves for the axial displacement of the
  • the leadership of the tapping element 26 is realized by the shaft 30 through which the shift control 24 is driven.
  • the tapping element 26 forms a pin which is guided in the groove guides 27.
  • the pivoting element 14.1, 14.2 is positively connected in a manner not shown with the tapping element 26, thus the pivoting element 14.1, 14.2 including the shift pinion 13.1, 13.2 each according to the shape of the groove guide 27 of the shift drum 25 a defined
  • the shift drum 25 is axially displaced by a defined path to guide the pick-off element 26 in a parallel groove. This movement of the shift drum 25 does not change the position of the tapping element 26 and thus of the
  • a switching pin 28 is provided, as shown in Figures 7 and 8 in different switching positions.
  • Shift pin 28 are brought into the various switching positions.
  • Figure 9 shows with a double arrow, the axial displacement of the shaft 30 and thus the rack 29, so that the switching pin 28 rotate can.
  • the rotation of the shift pin is achieved by the
  • Shift drum 25 is fixed axially, and by the inclusion of the
  • Shift pin 28 in the shift drum 25 rotates this at axial

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une transmission (1), en particulier destinée à être agencée sur un moteur à combustion interne d'un véhicule, comprenant un premier étage de transmission doté d'une première roue dentée (10) d'un plus petit diamètre et au moins un deuxième étage de transmission doté d'une deuxième roue dentée (11) d'un plus grand diamètre, une roue dentée (12) ovalisée étant disposée entre les roues dentées (10, 11), et un pignon de commande (13.1, 13.2) étant prévu, lequel est conçu pour s'engrener avec la première roue dentée (10) ou avec la deuxième roue dentée (11), le pignon de commande (13.1, 13.2) pouvant être amené à s'engrener avec la roue dentée ovalisée (12) afin de commuter entre l'engrènement avec la première roue dentée (10) et l'engrènement avec la deuxième roue dentée (11). Selon l'invention, le pignon de commande (13,1, 13.2) est logé sur un élément de pivotement (14.1, 14.2), la position du pignon de commande (13.1, 13.2) pouvant être adaptée aux différents diamètres des roues dentées (10, 11) par un pivotement de l'élément de pivotement (14.1, 14.2).
PCT/DE2017/100309 2016-05-04 2017-04-19 Transmission Ceased WO2017190727A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016005391.7A DE102016005391B3 (de) 2016-05-04 2016-05-04 Getriebe
DE102016005391.7 2016-05-04

Publications (1)

Publication Number Publication Date
WO2017190727A1 true WO2017190727A1 (fr) 2017-11-09

Family

ID=59061743

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2017/100309 Ceased WO2017190727A1 (fr) 2016-05-04 2017-04-19 Transmission

Country Status (2)

Country Link
DE (1) DE102016005391B3 (fr)
WO (1) WO2017190727A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110107658A (zh) * 2019-04-29 2019-08-09 黎李韦 齿盘联动变速机构及齿盘联动变速器
WO2020032893A1 (fr) * 2018-08-07 2020-02-13 Tusas- Turk Havacilik Ve Uzay Sanayii Anonim Sirketi Mécanisme de mouvement

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202100019985A1 (it) 2021-07-27 2023-01-27 Denso Thermal Systems Spa Cinematismo con settore dentato ribassato

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB343832A (en) * 1929-06-27 1931-02-26 Wilhelm Brase Improvements in variable speed gears
WO1993001427A1 (fr) * 1991-07-11 1993-01-21 Luigi Celani Boite de vitesses continue a engrenages helicoidaux
CN101737461A (zh) 2010-03-04 2010-06-16 北京邮电大学 基于非圆齿轮的变速传动机构

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB270696A (en) * 1926-05-06 1928-01-26 Joseph Destree Improvements in change speed power-transmission mechanisms

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB343832A (en) * 1929-06-27 1931-02-26 Wilhelm Brase Improvements in variable speed gears
WO1993001427A1 (fr) * 1991-07-11 1993-01-21 Luigi Celani Boite de vitesses continue a engrenages helicoidaux
CN101737461A (zh) 2010-03-04 2010-06-16 北京邮电大学 基于非圆齿轮的变速传动机构

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020032893A1 (fr) * 2018-08-07 2020-02-13 Tusas- Turk Havacilik Ve Uzay Sanayii Anonim Sirketi Mécanisme de mouvement
CN110107658A (zh) * 2019-04-29 2019-08-09 黎李韦 齿盘联动变速机构及齿盘联动变速器
WO2020220791A1 (fr) * 2019-04-29 2020-11-05 黎李韦 Mécanisme de changement de vitesse à liaison à disques et engrenages et transmission à liaison à disques et engrenages

Also Published As

Publication number Publication date
DE102016005391B3 (de) 2017-07-13

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