EP4013979A1 - Transmission à rapport de réduction élevé - Google Patents

Transmission à rapport de réduction élevé

Info

Publication number
EP4013979A1
EP4013979A1 EP20757852.7A EP20757852A EP4013979A1 EP 4013979 A1 EP4013979 A1 EP 4013979A1 EP 20757852 A EP20757852 A EP 20757852A EP 4013979 A1 EP4013979 A1 EP 4013979A1
Authority
EP
European Patent Office
Prior art keywords
segments
tooth
transmission
gear
recess
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.)
Pending
Application number
EP20757852.7A
Other languages
German (de)
English (en)
Inventor
Ernst Von Lehmann
Astrid Zimmermann
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.)
Maxon International AG
Original Assignee
Maxon International AG
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 Maxon International AG filed Critical Maxon International AG
Publication of EP4013979A1 publication Critical patent/EP4013979A1/fr
Pending 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
    • F16H49/00—Other gearings
    • F16H49/001—Wave gearings, e.g. harmonic drive transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • 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
    • F16H55/17—Toothed wheels
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F01L2001/3521—Harmonic drive of flexspline type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/02—Formulas
    • 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
    • F16H49/00—Other gearings
    • F16H49/001—Wave gearings, e.g. harmonic drive transmissions
    • F16H2049/003—Features of the flexsplines therefor

Definitions

  • the present invention relates to a transmission with a ring gear in which a flexible gear is arranged, wherein the flexible gear is connected to a wave generator and the wave generator deforms the flexible gear so that it is partially in engagement with the ring gear and the flexible Gear comprises at least two tooth segments which are connected to one another by means of spring segments and at least one of the Zahnseg elements has a recess in which a pin element is arranged.
  • WO 2016/165684 A2 shows an adjusting gear for adjusting two components with a ring gear, a driver gear, a wave generator and an elastic spur gear.
  • the elastic spur gear consists of several identically structured tooth elements. Each tooth element has a head area facing the ring gear and a foot area facing the wave generator. The head areas of the tooth elements are seen ver with teeth that can come into contact with the ring gear.
  • each tooth element has an outwardly open recess in its head segment, which breaks the toothing and is in contact with a drive pin of a drive wheel. Tooth elements lying next to one another are connected to one another by means of elastic connecting elements.
  • the wave generator is essentially elliptical and also brings the elastic spur gear into an elliptical shape, so that two opposing areas of the elastic spur gear are in engagement with the ring gear.
  • each of the spring segments has a central plane which contains a central central axis of the transmission and divides the respective spring segment into two areas of equal length and each recess has a central plane which contains the central central axis of the transmission and the recess into two divided equally large areas and the central plane of each spring segment has a different distance from the central plane of the recess lying next to it on each side of the central plane of the spring segment.
  • a gear can be made very short and still has the desired high torsional rigidity.
  • the structure of the transmission according to the invention opens up the possibility of increasing the flexibility of the flexible gear, so that sufficient elastic deformations of the gear can still be achieved, especially with small diameters of the transmission.
  • At least one of the tooth segments has a waist in the radial direction of the flexible gear and the spring segments act on this tooth segment in the region of the waist.
  • the spring segments can be made larger or longer, which further increases the flexibility of the gear, which is particularly advantageous with small gear diameters.
  • the spring elements should advantageously be designed in such a way that they have elasticity in the radial direction and are rigid in the tangential direction. Deformation of the flexible gear is thus only permitted in the radial direction. In the tangential direction, forces can be transmitted from one tooth segment to the adjacent tooth segment in the tangential direction without deforming the flexible gear. As a result, a gear play between the gear input and output is kept as small as possible.
  • a particularly simple configuration of the flexible gearwheel can be made possible by the fact that the spring segments are formed in one piece with the toothed segments.
  • the spring segments are advantageously designed as webs that connect adjacent Zahnseg elements to one another. These webs are preferably arcuate and ge ensure the desired elasticity in the radial direction, whereas they are stiff in the tangential direction.
  • the webs are preferably arranged at a distance from the head area of the tooth segments, where they come into engagement with the ring gear, and at a distance from the foot areas, where the tooth segments come into contact with the wave generator.
  • the arcuate webs preferably extend along a circular line, the center of which lies in the area or on the central central axis of the gear. As an alternative, straight webs are also possible.
  • the flexible gear has at least one first tooth segment that is provided with a recess, and at least one second tooth segment that has no recess.
  • the tooth segments provided with a waist preferably have no recess. This allows the spring segments extending between the toothed segments are designed to be longer, and a good combination of flexibility and strength of the toothed segments is achieved.
  • the toothing force of the at least one second tooth segment is transmitted to the at least one first tooth segment via the spring segments.
  • the spring segments engage the at least one first tooth segment at the level of the recesses in the at least one first tooth segment. This results in a good transmission of the toothing forces of the at least one second tooth segment to the at least one first tooth segment.
  • the spring segments are in the area in which they are connected to the at least one first Tooth segment are in contact, have an undercut.
  • a plurality of tooth segments in particular at least four tooth segments, are provided.
  • a flexible gear with four or more tooth segments which are accordingly connected to one another with four or more spring segments, sufficient flexibility of the gear can easily be ensured.
  • a good compromise between the flexibility of the flexible gear and sufficient strength can be made possible in that half of the tooth segments have a recess. So there are the same number of first and second tooth segments.
  • the second tooth segments which do not have a recess, transmit the toothing forces via the spring segments to the tooth segments with a recess.
  • the flexible connections can be made larger, whereby the flexibility of the flexible gear is Gestei Gert and you can still ensure sufficient elastic deformations even with a small diameter of the gear.
  • the recess in the first tooth segments is arranged in the interior of the respective tooth segment.
  • the recess in these tooth segments therefore has a closed peripheral contour on which the pin element rolls.
  • the recesses are advantageously substantially executed elliptically.
  • the tooth segments can then have a continuous toothing in a head region facing the ring gear.
  • each of the tooth segments can be supported in two support points on the wave generator.
  • a base area facing the wave generator is then concave so that it only comes into contact with the wave generator at two points.
  • the angle between the two support points is preferably approximately 170 °. The alignment of the tooth segments normal to the outer contour of the wave generator can be improved.
  • the wave generator has at least one cam which is in contact with the flexible gear and the cam is designed such that the tooth segments are deformed in the area in which they are in engagement with the ring gear be that they form a portion of an imaginary gear with egg nem constant radius that rotates about an axis that was at a specified distance from the central axis of the transmission is arranged.
  • the section of the imaginary gear with a constant radius comprises an angular range of preferably 45 ° -100 ° or 55 ° -85 ° and in particular 60 ° -80 °.
  • the constant radius of the imaginary gear has an aspect ratio to the radius of the ring gear of preferably 75-99%, or 82-97% and in particular 85-95%.
  • the number of tooth segments can be independent of the number of teeth of the entire flexible gear.
  • the number of teeth on the gear is therefore not an integral multiple of the number of tooth segments.
  • the arrangement of the teeth on the tooth segments does not necessarily have to be uniform.
  • the design of the wave generator described above ensures that each tooth on the tooth segments has the same shape.
  • the only boundary condition here is that the distance between the two outer teeth, which are on adjacent tooth segments, is an integral multiple of the tooth width S within this range. With tooth width S, the double distance between two adjacent teeth is meant.
  • the wave generator preferably has two corresponding cams which are arranged on the circumference of the wave generator in such a way that the wave generator has a section with a constant radius in the area where the flexible gear comes into contact with the ring gear.
  • the section with a constant radius comprises an angular range of preferably 45 ° -100 °, or 55 ° -85 ° and in particular 60 ° -80 °.
  • the wave generator can also have an elliptical section shape in the area in which the flexible gear comes into contact with the ring gear.
  • the teeth of the flexible gear can be preferably be adapted accordingly and can have at least two different tooth shapes. Designs of the wave generator with, for example, three, four or more cams are also possible.
  • the cams are preferably arranged symmetrically around the circumference of the wave generator.
  • the pin elements are designed as bolts that are connected to an output shaft. As a result, the movement of the flexible gear via the bolts is transferred to a uniform rotary movement of the output.
  • a sleeve is preferably arranged on each bolt, so that a sliding bearing with the associated advantages is formed.
  • an elastic sleeve or elastic O-rings can be arranged on each bolt.
  • the associated recesses can alternatively be made with a round cross section.
  • the pin elements are fixed and the ring gear is designed to be rotatable.
  • the ring gear is driven by the engagement of the flexible gear and accordingly serves as an output element in this embodiment variant.
  • Fig. 2 Front view of the transmission from Fig. 1,
  • Fig. 3 Cross section through the transmission from Fig. 2 along the line III-III,
  • Fig. 4 flexible gear from the transmission from Fig. 1,
  • Fig. 5 Detail of the flexible gear from Fig. 4,
  • Fig. 6 Representation of the area of engagement between the flexible gear and the ring gear of the transmission from Fig. 1,
  • Fig. 7 simplified representation of the engagement area shown in Fig. 6 between the flexible len gear and the ring gear
  • the transmission 1 comprises a housing 10 in which a wave generator 2, a flexible gear 6, a stationary ring gear 9 and a pin element 11 are arranged.
  • the cover of the housing 10 is removed to allow a view into the interior of the transmission.
  • the transmission 1 is essentially disk-shaped with a central central axis M.
  • the wave generator 2 comprises a base body 3 which has an approximately elliptical cross section. Due to the approximately elliptical cross section, the base body 3 has two sections with elevations. The elevations on the base body 3 generate cams on the wave generator 2.
  • the flexible gear 6 is brought into contact with the ring gear 9 by the cams.
  • the base body 3 can have a section with a constant radius, the center point Ms of this constant radius being offset from the central axis M by the distance e.
  • Rolling bodies 4, which are surrounded by a deformable sleeve 5, are arranged on the base body 3.
  • the flexible gear 6 is arranged on the wave generator 2. The flexible gear 6 is therefore in contact with the base body 3 via the deformable sleeve 5 and the rolling elements 4.
  • the flexible gear 6 comprises a plurality of tooth segments 7.1, 7.2, which segments 8 are connected to one another by means of flexible spring.
  • the flexible gear 6 is provided with an external toothing 14 which can be brought into engagement with an internal toothing 15 of the fixed ring gear 9.
  • the flexible gear 6 comprises twelve tooth segments 7.1, 7.2, which are divided into six first tooth segments 7.1 and six second tooth segments 7.2.
  • the first tooth segments 7.1 each have a recess 17 which is designed as a continuous opening in the interior of the respective first tooth segment 7.1.
  • a bolt 12 of the pin element 11 is received in each recess 17.
  • Each bolt 12 is surrounded by a sleeve 13 so that a sliding bearing is formed.
  • the elliptical shape of the base body 3 of the wave generator 2 is transferred to the flexible gearwheel 6 via the rolling elements 4 and the deformable sleeve 5.
  • the external toothing 14 of the flexible gear 6 is at two opposite points with the internal toothing 15 of the ring gear 9 in engagement.
  • the wave generator 2 is preferably connected to a drive shaft. A rotation of the drive shaft causes the wave generator 2 to rotate. This rotary movement is transmitted to the flexible gear 6.
  • the external toothing 14 of the flexible gear 6 therefore runs off the internal toothing 15 of the ring gear 9.
  • the spring segments 8 arranged between the toothed segments 7.1, 7.2 enable the flexible or elastic deformation of the flexible gear 6.
  • the movement of the flexible gear 6 is transmitted via the bolts 12 to a uniform rotary movement of the output.
  • the transmission 1 from FIG. 1 is shown in a front view.
  • the elliptical cross-sectional shape of the wave generator 2 or of the base body 3 of the wave generator 2 can be clearly seen here.
  • the center of the ellipse is always on the central axis M of the transmission 1.
  • the main axis 16 of the elliptical base body 3 is aligned exactly horizontally. Due to the elliptical shape of the wave generator 2, the flexible gear 6 is deformed in two areas, in the case shown in FIG. 2 on the right and left side of the transmission 1, in such a way that the external toothing 14 of the flexible gear 6 engages with the Internal toothing 15 of the fixed ring gear 9 comes. Furthermore, in the other two areas, which are shown on the upper and lower sides in FIG. 2, the external toothing 14 of the flexible gear 6 is not in engagement with the internal toothing 15 of the ring gear 9.
  • FIG. 3 shows a cross section through the transmission 1 along the line III-III from FIG. 2.
  • the transmission 1 comprises the housing 10 which is closed by a housing cover 10.1.
  • the ring gear 9 is fastened in the housing 10.
  • the ring gear 9 is partially in engagement with the flexible gear 6, for which purpose the ring gear 9 has the internal toothing 15 and the flexible gear 6 has the external toothing 14.
  • the flexible gear 6 comprises the first tooth segments 7.1.
  • Each of the first tooth segments 7.1 comprises a recess 17.
  • One of the bolts 12 is arranged in each recess 17.
  • One of the sleeves 13 can be attached to each of the bolts 12, so that a sliding bearing is formed.
  • the recesses 17 are somewhat larger than the sleeves 13. In the illustrated case, the recesses 17 have an elliptical cross section.
  • the cross-section of the bolts 12 and the sleeves 13 is round.
  • the diameter of the recesses 17 is somewhat larger than the outer diameter of the sleeves 13.
  • the flexible gear wheel 6 rests on the deformable sleeve 5.
  • the deformable sleeve 5 is connected to the base body 3 via the rolling bodies 4.
  • the base body 3, the rolling bodies 4 and the deformable sleeve 5 form the wave generator 2.
  • the transmission 1 has a very short overall length L G and is therefore very short in relation to the diameter. Nevertheless, a high torsional stiffness is given.
  • a transmission as described above has a high reduction ratio.
  • the flexible gear 6 comprises first and second tooth segments 7.1, 7.2, the segments 8 are connected to each other via spring.
  • the flexible gear 6 comprises twelve tooth segments 7.1, 7.2. Every second of the tooth segments, that is to say the first tooth segments 7.1, have the recess 17.
  • the first tooth segments 7.1 are all configured identically to one another.
  • the two tooth segments 7.2 are arranged between the first tooth segments 7.1.
  • the second tooth segments 7.2 have no recess.
  • Adjacent tooth segments 7.1, 7.2 are connected to one another via the spring segments 8.
  • the spring segments 8 are designed as arcuate webs which extend along a circular line, the center of which lies on the central axis of the transmission 1 in this embodiment.
  • first tooth segments 7.1 and the second tooth segments 7.2 are described in more detail below:
  • Each first tooth segment 7.1 has a foot area 18 with which it comes into contact with the wave generator 2. Starting from the foot region 18 radially outward, there is a body region 19 in which the recess 17 is arranged.
  • the recess 17 thus has a closed contour lying in the interior of the tooth segment 7.1.
  • the bolt 12 or the sleeve 13 rolls on this contour.
  • This trunk area 19 is followed by a head area 20 in the radial direction.
  • the external toothing 14 is formed on the outwardly facing peripheral surface of the head region 20 of each first tooth segment 7.1.
  • the external toothing 14 extends over the entire outwardly facing peripheral surface of the first tooth segment 7.1. If the width of the first tooth segment 7.1 is now being considered in the circumferential direction U of the flexible gear 6, the first tooth segment 7.1 in the foot area 18 has a first width that tapers in the trunk area and increases again towards the outside so that the first tooth segment 7.1 have the greatest width on the outer circumference.
  • the second tooth segments 7.2 also have a foot region 21 which comes into contact with the wave generator 2. This foot area 21 is also connected to the second tooth Segments 7.2 in the radial direction outward a trunk area 22, which merges into a head area 23 rich.
  • the second tooth segments 7.2 have no recess. Instead, the second tooth segments 7.2 are strongly constricted in the trunk area 22 and thus have a waist 24.
  • the external toothing 14 is also formed on the outwardly facing peripheral surface of the head regions 23 of the second tooth segments 7.2.
  • Each of the tooth segments 7.1, 7.2 is connected via spring segments 8 with the adjacent tooth segments 7.2, 7.1.
  • the spring segments 8 are Dodgebil det as arcuate webs that extend on a circular line in the circumferential direction of the flexible gear 6.
  • the spring segments 8 engage approximately at the level of the middle of the recess 17 on the first Zahnseg elements 7.1.
  • the connection between the spring segments 8 and the second Zahnseg elements 7.2 is at the level of the waist 24.
  • the flexible gear 6 is formed in one piece.
  • the second tooth segments 7.2 which do not have a recess, transmit the toothing forces via the spring elements 8 to the first tooth segments 7.1 with the recess 17. This allows the spring segments 8 to be made larger, which increases flexibility and you can use a smaller diameter of the gear 1 can still achieve sufficient elastic deformation.
  • the illustrated shape of the spring elements 8 ensures that, as far as possible, they have no elasticity in the tangential direction, but only in the radial direction.
  • Each of the spring segments 8 has a central plane MFS which contains the central central axis of the transmission 1 and divides the respective spring segment 8 into two areas of equal length. Since the spring segments 8 are formed by arcuate webs, this length corresponds to an arc length.
  • Each of the recesses 17 also has a central plane M A which contains the central central axis of the transmission 1 and divides the respective recess 17 into two equally large areas.
  • the spring segments 8 between the toothed segments 7.1, 7.2 are designed asymmetrically in such a way that the center plane MFS of each spring segment 8 is at a different distance from the two adjacent center planes MA of the recesses 17.
  • FIG. 5 the detail V from FIG. 4 is shown enlarged.
  • a first tooth segment 7.1 and a second tooth segment 7.2 are shown.
  • the first tooth segment 7.1 has a foot region 18, a trunk region 19 and a head region 20.
  • the recess 17 lies in the trunk area 19 of the first tooth segment 7.1.
  • the external toothing 14 is formed in the head region 20.
  • the second tooth segment 7.2 also has a foot region 21, a trunk region 22 which has a waist 24 and a head region 23.
  • both the foot area 21 of the second tooth segments 7.2 and the foot area 18 of the first tooth segments 7.1 have a concave recess so that each of the tooth segments 7.1, 7.2 is supported on the wave generator 2 with two support points. This improves the alignment of the tooth segments 7.1, 7.2 normal to the outer contour of the wave generator 2.
  • This concave depression has an opening angle ⁇ of approximately 170 °.
  • the spring segments 8 engage approximately at the level of the recesses 17 on the first Zahnseg elements 7.1. In the area where the spring segments 8 merge into the first toothed segments 7.1, the spring segments 8 have an undercut 25. This undercut 25 can increase the flexibility of the flexible gear 6 in the transition area from the spring segments 8 to the first toothed segments 7.1.
  • the spring segments 8 engage the second toothed segments 7.2 at the level of the waist 24. Since the second tooth segments 7.2 have a very small width in this area, there is sufficient flexibility there.
  • the tooth segments 7.1, 7.2 lying next to one another are spaced apart from one another both in the head area and in the foot area.
  • the first tooth segments 7.1 can have a different number of teeth than the second tooth segments 7.2.
  • the number of teeth of the flexible gear 6 is therefore not an integral multiple of the number of tooth segments 7.1, 7.2.
  • the number of tooth segments 7.1, 7.2 is not determined by the number of teeth of the entire flexible gear 6.
  • the number and / or the arrangement of the teeth on the tooth segments 7.1, 7.2 is not necessarily uniform. So that each tooth on the tooth segments 7.1, 7.2 has the same shape, the geometry of the wave generator 2, i.e.
  • the elliptical cross-sectional shape with two opposing cams can be selected so that a constant radius R extends over in the area of the upper high point (elevation) extends an angle a within which the tooth engagement takes place.
  • the angle ⁇ is 72 °.
  • FIGS. 6-8 This means that all result within this section, i.e. the win- kels a, located tooth segments 7.1, 7.2 an imaginary gear with the radius R, wel Ches rotates around an axis Ms.
  • This axis Ms is at a certain distance e from the central center axis M of the transmission 1.
  • the distance e here has a length ratio of less than 10% to the radius of the ring gear.
  • the only boundary condition is that the stand of the two outer teeth, which are located on adjacent gear elements 7.1, 7.2, is an integral multiple of the tooth width S within this range.
  • the tooth width S is defined here as twice the distance between two adjacent teeth of the external toothing 14. This is shown in FIG.
  • the advantage of the gear unit according to the invention with a high reduction ratio is that the length of the gear unit is very short and the torsional rigidity is high.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

La présente invention concerne une transmission comprenant une couronne dentée, dans laquelle est disposée une roue dentée flexible, la roue dentée flexible étant reliée à un générateur d'ondes et le générateur d'ondes déformant la roue dentée flexible de sorte que ladite roue dentée est engrenée dans certaines régions avec la couronne dentée, et la roue dentée flexible comprenant au moins deux segments de dent qui sont reliés l'un à l'autre au moyen de segments de ressort et au moins l'un des segments de dent comporte un évidement dans lequel est disposé un élément de broche. La présente invention aborde le problème de la fourniture d'une transmission qui, même dans le cas particulier de diamètres de transmission plus petits, permet une déformation élastique suffisante de la roue dentée flexible et présente une longueur globale très courte tout en ayant une rigidité de torsion élevée. La solution selon l'invention est caractérisée en ce que chacun des segments de ressort possède un plan médian qui contient un axe médian central de la transmission et divise le segment de ressort correspondant en deux régions de longueur égale, et chaque évidement possède un plan médian qui inclut l'axe médian central de la transmission et divise l'évidement en deux régions de taille égale, et le plan médian de chaque segment de ressort est disposé à une distance différente du plan médian de l'évidement situé de chaque côté du plan médian du segment de ressort, de manière adjacente au segment de ressort.
EP20757852.7A 2019-08-13 2020-08-12 Transmission à rapport de réduction élevé Pending EP4013979A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP19191460.5A EP3779239B1 (fr) 2019-08-13 2019-08-13 Engrenage à grande démultiplication
PCT/EP2020/072556 WO2021028451A1 (fr) 2019-08-13 2020-08-12 Transmission à rapport de réduction élevé

Publications (1)

Publication Number Publication Date
EP4013979A1 true EP4013979A1 (fr) 2022-06-22

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP19191460.5A Active EP3779239B1 (fr) 2019-08-13 2019-08-13 Engrenage à grande démultiplication
EP20757852.7A Pending EP4013979A1 (fr) 2019-08-13 2020-08-12 Transmission à rapport de réduction élevé

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP19191460.5A Active EP3779239B1 (fr) 2019-08-13 2019-08-13 Engrenage à grande démultiplication

Country Status (6)

Country Link
US (1) US11994199B2 (fr)
EP (2) EP3779239B1 (fr)
JP (1) JP2022544458A (fr)
KR (1) KR20220042231A (fr)
CN (1) CN114207324B (fr)
WO (1) WO2021028451A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3828442A1 (fr) * 2019-11-26 2021-06-02 Maxon International AG Roue dentée souple et boîte de vitesses dotée d'une telle roue dentée souple
DE102022000408A1 (de) 2022-02-03 2023-08-03 Jan Klindworth Stellgetriebe
WO2024055866A1 (fr) * 2022-09-16 2024-03-21 美的集团股份有限公司 Dispositif satellite à engrènement interne
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US11994199B2 (en) 2024-05-28
CN114207324A (zh) 2022-03-18
JP2022544458A (ja) 2022-10-19
US20220316573A1 (en) 2022-10-06
CN114207324B (zh) 2024-05-28

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