Traction mechanism with internal and external teeth and transmission with traction mechanism

Abstract

To realize a toothed belt with internal toothing and external toothing, and a transmission with such a toothed belt.SOLUTION: Tooth crests of the internal toothing comprise a rounded region, and tooth crests of the external toothing comprise a rounded region. The tooth crests of the internal toothing are arranged radially oppositely to respective tooth bases of the external toothing so that the toothed belt forms an offset gap arrangement where the teeth of the internal and external toothing are offset from one another. An inner side of the toothed belt comprises a smooth central bearing region.SELECTED DRAWING: Figure 12

Description

[Background technology]

[0001] The subject matter of patent application PCT / IB2017 / 057452 is hereby incorporated by reference. Specifically, Figures 1 to 9 and the corresponding text from page 28, line 11 to page 34, line 14 of the specification relate to a harmonic pin and ring transmission, and Figure 10 relates to a mounting scheme for the transmission of Figures 1 to 9. Figures 11 to 14 and 20 and the corresponding text from line 14 on page 36 to line 21 on page 40 and from line 41 to line 30 on page 42 of the specification relate to a harmonic pin ring transmission with an eccentric disc, and Figures 15 to 19 and the corresponding text from line 32 on page 40 to line 35 on page 41 relate to the pin ring for the transmission of Figures 11 to 14. 21 to 29 and the corresponding text from line 8 on page 48 to line 24 on page 50, and FIG. 30, FIG. 31 and the corresponding text from line 62 on page 50 to line 10 on page 53 relate to load cells. Figures 43 and 44 refer to an HPD transmission with a load cell, and the corresponding text from page 57, line 36 to page 58, line 38, while Figures 32 and 34 and the corresponding text from page 55, line 8 to page 56, line 9, relate to fastening and mounting concepts for the load cell. Figures 35 to 40 and the corresponding text from line 11 on page 56 to line 35 on page 57, and Figures 41 and 42 and the corresponding text from line 30 to 35 on page 57 relate to the indirect measurement of pedal shaft torque using a strain gauge. Figures 45 to 59 and the corresponding text from line 1 on page 59 to line 26 on page 63 relate to a freewheel assembly, and Figure 60 and the corresponding text from lines 28 to 34 on page 63 relate to a harmonic pin ring transmission with a clamp roller freewheel. 61 to 66 and the corresponding sentences on page 64, line 1 to page 67, line 27 relate to a geared motor. Figures 67 to 76 and the corresponding text from line 29 on page 67 to line 31 on page 69 relate to a harmonic pin-ring transmission having a planetary gear as the crank gear. Figures 77 to 81 and the corresponding text from page 69, line 33 to page 73, line 21 relate to cycloidal gears. Figures 82 to 88 and the corresponding text from line 23 on page 73 to line 16 on page 75 relate to tension shaft transmission. 89 to 93 and the corresponding text on page 76, line 23 to page 78, line 24 relate to a two-part pin ring and a high reduction gear having a two-part pin ring. Figures 94 to 118 and the corresponding text from page 78, line 26 to page 105, line 4 relate to tooth structure, particularly the epicycle structure and the bi-epicycle structure. Figures 119 to 123 in general and the corresponding text from page 105, line 34 to page 107, line 12 relate to the transmission of this specification, Figures 124 to 126 and the corresponding text from page 107, line 14 to page 107, line 21 relate to the tension shaft transmission, similar to Figures 82 to 88 above, and in addition, further text in the specification of PCT / IB2017 / 057452 relates to the above-mentioned embodiment examples.

[0002] The following terms used herein correspond to the terms listed below in the specification of PCT / IB2017 / 057452:

[0003] The inner central bearing area of ​​the toothed belt corresponds to the "inner bearing surface" of the pin ring, particularly the single-piece pin ring, and the outer central bearing area of ​​the toothed belt corresponds to the "outer bearing surface" of the pin ring, particularly the single-piece pin ring.

[0004] The "rotor transmitter unit" corresponds to the inner rotor shaft 27 and the cam disc 28 or the inner rotor shaft 27 and the eccentric disc 28', and the "internal gear driven shaft unit" corresponds to the inner gear 7 having the hollow shaft portion 234. The "external gear assembly" corresponds to the support ring 36 on which the first external gear 8 is mounted or inserted and on which the second external gear 8' is mounted or inserted.

[0005] A "single epicyclic toothing" corresponds to a toothing based on a gear orbit with one epicycle, as defined, for example, in item 1 of the first list at the end of this specification. A "double epicyclic toothing" corresponds to a toothing based on an epicyclic gear orbit with two epicycles, as defined, for example, in item 12 or 13 of the first list at the end of this specification. Summary of the Invention

[0006] The present specification discloses a toothed belt having internal and external teeth, wherein the tips of the internal teeth have rounded regions with fan-shaped cross sections, the tips of the external teeth have rounded regions with fan-shaped cross sections, and the area between two adjacent tips of the internal teeth is at least as wide as the tooth thickness of the internal teeth, and the area between two adjacent tips of the external teeth is at least as wide as the tooth thickness of the external teeth.

[0007] In particular, the area between the tooth tips may be at least as wide as the width of the tooth tips of each tooth section plus an area determined by the shape of the teeth of the external or internal gear of the transmission that fits each tooth section of the toothed ring.

[0008] In particular, the tips of the internal teeth may be arranged radially opposite the tips of the external teeth in a symmetrical arrangement, or alternatively, the tips of the internal teeth may be arranged radially opposite the roots of the external teeth in an offset arrangement.

[0009] Furthermore, the tooth roots of the internal teeth may be formed as flat tooth roots corresponding to the surface of a right cylinder, which can be easily produced, for example by molding from a cylindrical workpiece, and which is sufficient to achieve good engagement of the toothed belt with a properly designed mating toothing of an internal or external gear engaging the toothed belt.

[0010] According to a further embodiment, the toothed belt has the form of a corrugated sheet of constant thickness, forming a right cylinder, the internal teeth being formed by the backsides of the external teeth, and the external teeth being formed by the backsides of the internal teeth.

[0011] According to a further embodiment, a smooth central bearing area is provided inside the toothed belt in the shape of a right cylinder, such that the internal teeth contact the central bearing area in both axially opposite areas, where smooth does not mean in comparison on a microscopic scale but on a scale that can be observed without aids.

[0012] Furthermore, a central bearing region formed in the shape of a right cylinder may be provided on the outside of the toothed belt so that the external teeth contact the central bearing region in both axially opposing regions.

[0013] In particular, the toothed belt may be made in a single piece, for example cast, rolled or stamped, which allows for efficient manufacturing and improved stability.

[0014] According to one embodiment, the toothed belt comprises plastic, and may comprise more than 90 weight percent plastic or may be made entirely of plastic.

[0015] According to a further embodiment, the toothed belt comprises a steel alloy, in particular it may comprise more than 90 weight percent of a steel alloy or may be made entirely of a steel alloy.

[0016] In particular, the toothed belt may comprise a cobalt manganese steel alloy, may comprise more than 90 weight percent of the cobalt manganese steel alloy, or may be made entirely of the cobalt manganese steel alloy.

[0017] Further, the present specification discloses a transmission having an input shaft and an output shaft, an outer gear and an inner gear disposed inside the outer gear and coaxially with the outer gear, and a traction mechanism extending between the outer gear and the inner gear.

[0018] The transmission comprises at least one rotary transmitter for lifting the traction mechanism from the outer periphery of the inner gear and pressing it against the inner periphery of the outer gear, the traction mechanism being provided as a toothed belt according to the above specifications.

[0019] In the transmission, the input shaft may be connected in particular to the transmitter, the outer gear, or the inner gear, and the output shaft may be connected to the transmitter, the outer gear, or the inner gear if the input shaft is not already connected.

[0020] Furthermore, the present specification discloses a transmission according to one of items 1, 15, 34, 37, 46, 52, 57 or 59 of the second list of the present specification, wherein said traction mechanism is provided as a toothed belt as described above.

[0021] Furthermore, the present specification discloses a harmonic pin-ring transmission according to item 1 of the first list of the present specification, wherein said pin-ring is provided as a toothed belt as described above.

[0022] Furthermore, the present specification discloses a harmonic pin-ring transmission according to item 14 of the first list of the present specification, wherein said pin-ring is provided as a toothed belt as described above.

[0023] In particular, an electric motor may be provided, the rotor of which is connected to the input shaft of the transmission, or alternatively, an internal combustion engine may be provided, the output shaft of which is connected to the input shaft of the transmission.

[0024] Furthermore, the present specification discloses a vehicle, in particular a two-wheeled or three-wheeled vehicle, having the above-mentioned motor transmission unit, at least one running wheel of the vehicle being connected to the output shaft of the transmission.

[0025] Furthermore, the present specification discloses a generator having a drive unit, a power generation unit for generating electricity, and the above-mentioned transmission, wherein an input shaft of the transmission is connected to the drive unit and an output shaft of the transmission is connected to an input shaft of the generator. [Brief explanation of the drawings]

[0026] The subject matter of this specification will now be described with reference to the following drawings:

[0027] [Figure 1] 1 shows a perspective view of a first embodiment of a pin ring with spaced pins. FIG. [Figure 2] 2 shows an enlarged detail of the pin ring of FIG. 1; [Figure 3] 2 shows a side view of the pin ring of FIG. 1. [Figure 4] 4 shows a cross section of the pin ring taken along section line AA in FIG. 3. [Figure 5] FIG. 2 shows a front view of the pin ring of FIG. 1. [Figure 6] 10 shows a perspective view of a second embodiment of a pin ring with spaced pins. FIG. [Figure 7] FIG. 7 shows a front view of the pin ring of FIG. 6. [Figure 8] FIG. 7 shows a side view of the pin ring of FIG. 6. [Figure 9] 8A shows a cross-sectional view of the pin ring of FIG. 6 taken along section line AA of FIG. 8. [Figure 10] 1 shows a perspective view of an offset-spaced pin ring or toothed belt in which the internal and external pins or teeth are offset from one another. [Figure 11] 10 shows a perspective view of another offset-spacing pin ring with inner and outer central bearing areas. FIG. [Figure 12] FIG. 10 shows a perspective view of another offset-spacing pin ring with an inner central bearing area. [Figure 13] 10 shows a perspective view of another pin ring with symmetrical spacing of inner and outer teeth or pins facing each other. FIG. [Figure 14] FIG. 10 shows a perspective view of another pin ring with symmetrical spacing, with radial spacing between the pins. [Figure 15] 1 shows a perspective view of another pin ring or toothed belt in which the tooth roots form the tips of diametrically opposite toothings; [Figure 16] 15 shows an enlarged detail of FIG. 14. [Figure 17] 16 shows an enlarged detail of FIG. 15. [Figure 18] FIG. 1 shows a front view of the driven side of a harmonic pin ring transmission. [Figure 19] 19 shows a cross section taken along the line AA in FIG. 18. [Figure 20] 19 shows an exploded view of the transmission of FIG. 18. [Figure 21] 1 shows a transmission with a three-pole stator that uses electromagnetic force to move a pin ring. [Figure 22] 1 shows a transmission with a six-pole stator that uses electromagnetic force to move the pin ring. [Figure 23] 1 shows a transmission having a three-pole stator in which a pin ring is deformed by electromagnetic force. [Figure 24] 1 shows a transmission with a six-pole stator that deforms a pin ring using electromagnetic force. [Figure 25] 1 shows a transmission with a six-pole stator that uses electromagnetic force to move the internal teeth. [Figure 26] 1 shows a transmission with a six-pole stator that uses electromagnetic force to move the internal teeth. [Figure 27] 22 shows energization of the stator windings of the transmission of FIG. 21. [Figure 28] 1 shows a cross section through a symmetrically spaced pin ring. [Figure 29] 1 shows a cross section through the pin ring with shifted spacing. [Figure 30] 1 shows a cross section through a pin ring with shifted spacing where the backside of the internal teeth form the external teeth. DETAILED DESCRIPTION OF THE INVENTION

[0028] Details are provided below to describe the embodiments herein, but it will be apparent to one skilled in the art that the embodiments may be practiced without such details.

[0029] FIG. 1 shows a perspective view of a first embodiment of a pin ring 201 with pins 101 spaced apart. Pin or tooth spacing provides a gap between two pins or teeth that is at least as wide as the pin or tooth itself. For example, the tooth thickness can be considered to be the circumferential extension of a tooth at the midpoint between the tooth root and tip. Another definition of tooth thickness is the width at the height of the pitch circle.

[0030] When the spaced pin ring is installed in the transmission, the pins or teeth of the traction mechanism engage every other root of each external or internal tooth of the transmission, but do not engage the root of any adjacent circumferentially adjacent teeth. This applies to the engagement area where the pins engage with each internal or external tooth. Preferably, the teeth and / or pins are configured so that every pin or tooth of the traction mechanism contacts or engages with an opposing tooth of each internal or external tooth, so that the engagement area extends around the entire circumference or 360 degrees, as shown in FIG. 18. In a broader sense, engagement also refers to when two opposing tips of an external tooth overlap each other, as shown in the center of FIG. 18.

[0031] This spaced engagement is shown in Figure 18. The spaced engagement for the external teeth is particularly evident at the top and bottom of Figure 18 for the external teeth, and particularly evident in the center of Figure 18 for the internal teeth.

[0032] Figure 2 shows an enlarged detail of the pin ring 102 of Figure 1, showing the transition region between the pins 101 and the central bearing ring. According to the embodiment of Figures 1-5, the pin ring is made as a single piece. For example, the laterally protruding pins may be rolled or stamped from the workpiece.

[0033] 1 and other pin rings or toothed belts disclosed herein, is an alloy steel characterized by excellent stampability and formability, specifically, a manganese chromium alloy steel such as 16MnCr5, material designation 1.7131.

[0034] Figure 3 shows a side view of the pin ring 102 of Figure 1, depicting the angular distance between the pins, which depends on the radius of the pin ring and the number of pins evenly distributed around the circumference, and is 4.8 degrees in the example of Figure 3.

[0035] Figure 4 shows a cross section of the pin ring 102 taken along section line AA in Figure 3. As can be seen in Figure 4, the diameter of the pin is approximately the same size as the thickness of the central bearing ring.

[0036] FIG. 5 shows a front view of the pin ring 102 of FIG. 1, showing the central bearing ring and the pins protruding axially to the left and right of the central bearing ring.

[0037] Figure 6 shows a perspective view of a second embodiment of a pin ring 102' spacing the pins 101'. This embodiment differs from the embodiment of Figure 1 in that the diameter of the pins is smaller than the thickness of the central bearing ring.

[0038] FIG. 7 shows a front view of the pin ring 102' of FIG.

[0039] FIG. 8 shows a side view of the pin ring 102' of FIG.

[0040] Figure 9 shows a cross-sectional view of the pin ring 102' of Figure 6 taken along section line AA in Figure 8. The pin ring 102' is manufactured such that the diameter of the workpiece tapers axially outward in the transition region, and the pin diameter here is approximately two-thirds the thickness of the central bearing ring.

[0041] 10 to 13, 15, and 17 show pin rings configured in the style of a toothed belt and having external and internal teeth, where the number of teeth on the external teeth corresponds to the number of teeth on the internal teeth. The teeth may be considered pins, and the pin rings in FIGS. 10 to 13, 15, and 17 are also called double pin rings or double toothed rings.

[0042] The pin rings of Figures 10 to 17 may be made of an elastic material and / or may be suitably dimensioned to be particularly suitable for deformation into an oval or elliptical shape, the position of which is rotated on a circular path by a rotary transmitter located radially inside the respective pin ring.

[0043] The pin rings of Figures 10 to 17 can also be made of a non-elastic or low-elasticity material and / or can be dimensioned accordingly to be suitable for being guided on a circular path by an eccentrically arranged cylindrical cam disc of the transmitter.

[0044] In particular, the cross section of the tooth may resemble the cross section of a half pin, i.e. approximately semicircular, or, except for the transition region, may be fan-shaped, with at least the upper region of the tooth tip preferably being rounded to the fan shape.

[0045] This fan-shaped rounded upper region may, for example, extend over at least 30% or at least 40% of the tooth height measured from the center between the root and the tip, when viewed from the tip, so that on the one hand a wider transition area is available between the tip and the root, while on the other hand the tooth shape still sufficiently resembles that of a pin.

[0046] The transition area provides elasticity and design freedom for the dimensioning of the tooth structure of the toothed belt to accommodate the external teeth of the internal gear or the internal teeth of the external gear.

[0047] According to other exemplary embodiments, the fan-shaped rounded upper region may extend over at least 70%, at least 80%, or at least 90% of the tooth depth measured from the center between the root and the tip, as viewed from the tip, so as to resemble as closely as possible a pin shape. The similarity between the tooth shape and the pin shape allows for as good a fit as possible with, for example, the one or two epicyclic toothings of the external and / or internal gears as disclosed in PCT / IB2017 / 057452.

[0048] According to other example embodiments, the fan-shaped rounded upper region, when viewed from the tip, may extend over at least 50%, at least 60% of the tooth height measured from the center between the root and the tip, thereby achieving a compromise between a pin-like tooth shape and a sufficiently wide transition region.

[0049] On the other hand, the tooth bottoms of the internal and external teeth may be flat, for example, as shown in FIGS. 10 to 13, that is, may form cylindrical surfaces.

[0050] In particular, the tooth profile of the internal gear teeth can be adapted or structurally matched to the tooth profile of the external gear teeth. The tooth profiles of the internal and external gear teeth preferably correspond to straight tooth profiles or to the tooth profile of spur gears, which can be easily produced, for example, by rolling. Although not shown, helical teeth are also possible.

[0051] In particular, the double toothed ring may comprise one epicyclic toothing or two epicyclic toothings as described in PCT / IB2017 / 057452.

[0052] 10 shows a perspective view of an offset-spaced pin ring 102'' or toothed belt 102'', in which the pins or teeth of the internal teeth 106 and external teeth 105 are offset relative to each other, i.e., the teeth or pins of the external teeth 105 face the roots or pins of the internal teeth 106, respectively.

[0053] FIG. 11 shows a perspective view of an alternative offset-spacing pin ring 102''' having inner and outer central bearing areas 107, 108, with the internal teeth 105' offset relative to the external teeth 106'.

[0054] FIG. 12 shows an alternative offset-spaced pin ring 102 with an inner central bearing area 107. (IV) 1 shows a perspective view of a toothed wheel having internal teeth 105'' offset relative to external teeth 106''.

[0055] The inner central bearing area 107 may serve, inter alia, to improve contact with the cam disc or outer surface of the transmitter, and the outer central bearing area 108 may serve, inter alia, to improve contact with the cylindrical bearing surface of the transmission housing facing the outer surface of the transmitter.

[0056] With respect to the toothed belt example of Figure 12, if there is no central bearing area inside the toothed belt, external teeth matching the internal teeth of the toothed belt may be located radially inside the toothed belt to improve support for the transmitter. In particular, in the case of a transmission with a driven internal gear, the external teeth may be located on ball bearings, while in the case of a non-driven fixed internal gear, the external teeth may be attached to the transmission housing.

[0057] With respect to the example of the toothed belt of Figure 12, if there is no central bearing area on the outside of the toothed belt, external teeth matching those of the toothed belt may be located radially outside the toothed belt to improve support. In particular, in the case of a transmission with a driven outer gear, the external teeth may be located on ball bearings, while in a transmission with a fixed, non-driven outer gear, such as the transmissions of Figures 18-20, the external teeth may be mounted on the transmission housing.

[0058] However, the external gear teeth may extend across the entire width of the toothed belt, which also provides good contact.

[0059] FIG. 13 shows another pin ring 102 with symmetrical spacing in which the teeth or pins of the internal 106''' and external 105''' faces each other. (V) 1 shows a perspective view of the

[0060] Even in the case of a symmetrically spaced toothed belt as in FIG. 13, the central bearing area may be provided on the inside of the toothed belt or on the outside of the toothed belt.

[0061] FIG. 14 shows another pin ring 102 with symmetrical spacing between the pins 101'''. (VI) 1 shows a perspective view of the

[0062] In the pin ring of Figure 14, the pins 101''' are formed so that their cross section forms an elongated oval, which can be seen particularly clearly in the enlarged detail of Figure 16. That is, the cross section of the pins 101'' forms a rectangle with two semicircular ends on the short side, which may each be identical.

[0063] FIG. 15 shows another pin ring 102 in which the tooth roots form the tips of the teeth on the diametrically opposite sides. (VII) , toothed belt, or double toothed ring 102 (VII) Therefore, the external teeth 105 (IV) The back side has 106 internal teeth. (IV) and vice versa.

[0064] The shape of the double toothed ring resembles a cylindrical piece of corrugated metal, which can be seen particularly well in the enlarged detail of Figure 17.

[0065] The double toothed ring design according to FIG. 15 provides good elasticity while being simple and material-saving to manufacture.

[0066] FIG. 16 shows an enlarged detail of FIG.

[0067] FIG. 17 shows an enlarged detail of FIG.

[0068] FIG. 18 shows a front view of the driven side of a harmonic pin ring transmission with an oval cam disc, in which the pin ring 102″ according to FIG. 10 is installed as a traction mechanism, and shows, from inside to outside, the inner area of ​​the rotor transmitter unit 109 of the internal rotor motor (not shown), the inner gear driven shaft unit 110, the pin ring 102″ according to FIG. 10, and the outer gear assembly 111.

[0069] Figure 19 shows a cross section along the section line AA in Figure 18. The inner gear driven shaft unit 110 is attached to the rotor transmitter unit via a driven shaft ball bearing. A deformable ball bearing is attached to the cam disc of the rotor transmitter unit 109, and the pin ring according to Figure 12 is placed on this deformable ball bearing. The outer gear assembly 111 is placed radially outside the pin ring and consists of a drive side outer ring or outer gear, an outer gear holder, and a driven side outer ring or outer gear. The outer gear assembly is attached to the transmission housing, which is not shown in Figures 18 to 20.

[0070] FIG. 20 shows an exploded view of the transmission of FIG. 18, showing from left to right the drive outer ring or driven outer gear, outer gear holder, driven outer ring or driven outer gear, pin ring according to FIG. 13, rotor transmitter unit 109, deformable ball bearing, driven shaft ball bearing, and inner gear driven shaft unit 110.

[0071] Further components (not shown in Figure 20) of the transmission or motor-transmission unit according to Figure 20 may be configured in the same way as the transmission shown in PCT / IB2017 / 057452, in particular the transmission shown in Figures 1 to 10 and 11 to 20 of PCT / IB2017 / 057452. Similarly, further details of the transmission of Figure 20 not described here may be implemented in the same way as the transmission of Figures 1 to 10 of PCT / IB2017 / 057452.

[0072] The transmission of Figure 18 is only one example of a potential use of the pin ring of Figure 13 as a traction mechanism in a transmission. Rather, the pin ring of Figure 13 and the other pin rings shown in Figures 1-17 can also be used as traction mechanisms in other transmissions. In particular, these pin rings can also be used in the transmissions disclosed in PCT / IB2017 / 057452, which is incorporated herein by reference, with the shape of the pins or the shape of the internal or external teeth appropriately adapted as needed.

[0073] 1 to 17 are suitable for use as a traction mechanism between internal and external teeth of a reduction gear, with each pin ring engaging with the internal and external teeth of the reduction gear. Specifically, this may be a transmission having a transmitter that lifts the pin ring from the internal teeth and presses it against the external teeth.

[0074] 21 to 27 show transmission components of a transmission with a rotorless motor, each of which is driven by the deformation or displacement of the traction mechanism or the displacement of the internal or external teeth due to the electromagnetic force of the stator. The electromagnetic force sets the first tooth or pin in rotational motion by moving along the second tooth, and the electromagnetic force acts predominantly in the radial direction.

[0075] This is in contrast to transmissions with rotors, in which the rotational motion of the rotor occurs first, and radial motion only follows therefrom, as in the case of tension shaft transmissions with steel bushings mounted on deformable ball bearings.

[0076] The transmission components of Figures 21 to 27 can be used to reduce or change gear speeds, in particular in eccentric transmissions, cycloidal gears, or harmonic chain or pin-ring transmissions. The transmission components of Figures 21 to 27 may also be used, in particular, in the transmission disclosed in PCT / IB2017 / 057452, in which case the components located in the torque curve between the stator and the inner and outer gears are replaced or suitably modified by the components shown schematically in Figures 21 to 27.

[0077] In order to generate forces on the pins or teeth by the electromagnetic field of the stator, the teeth or pins may be provided with magnetic regions or permanent magnets or may consist of a magnetic material. In particular, if the entire toothing or pin ring is guided on a predetermined path, for example an eccentric circular path, the teeth or pins may be guided by a mechanical guide in addition to being guided by electromagnetic forces.

[0078] 21 and 22 show a transmission in which the traction mechanism, in particular the pin ring, is moved along the internal and external teeth by the electromagnetic force of the motor.

[0079] In Figures 21 and 22, the downward arrows indicate that the pin ring is moved away from the external teeth and pressed against the internal teeth in a first region, and is pushed away from the internal teeth and pressed against the external teeth in a second, diametrically opposite region.

[0080] The first region is the region of least contact or engagement with the external teeth and most contact or engagement with the internal teeth. The second region is the region of most contact or engagement with the external teeth and least contact or engagement with the internal teeth. The stator windings of the stator are controlled or energized to rotate the first region and the opposite second region about the central axis.

[0081] 23 and 24 show a transmission in which the traction mechanism, in particular the pin ring, is moved along the internal and external teeth by being deformed into an elliptical shape by the electromagnetic force of the motor.

[0082] 23 and 24, a pair of arrows, one above the other, indicates the pin ring being expanded in a first region and a radially opposite second region, and a pair of arrows, one to the left and right, indicates the pin ring being pulled in a third region and a radially opposite fourth region. In this case, the expanding, contracting, or both is caused by electromagnetic forces exerted by the stator, which may in particular be electrostatic forces. The third and fourth regions are offset by 90 degrees from the first and second regions.

[0083] The first and second regions are regions of least contact or engagement with the internal teeth and most contact or engagement with the internal teeth. The third and fourth regions are regions of most contact or engagement with the internal teeth and least contact or engagement with the external teeth. The stator windings of the stator are controlled or energized so that the first, second, third, and fourth regions rotate about the central axis.

[0084] Figures 25 and 26 show transmissions in which the internal teeth are driven along the external teeth by the electromagnetic forces of the stator, similar to those with cycloidal gears. In these transmission variants, no traction mechanism is located between the internal and external teeth. Instead, the internal teeth directly engage with or roll off onto the external teeth.

[0085] In Figures 25 and 26, the downward arrows indicate that the internal teeth are moved away from the external teeth in a first region and pressed against the external teeth in a second, diametrically opposite region.

[0086] The first region is the region of least contact or engagement with the external teeth. The second region is the region of greatest contact or engagement with the external teeth. The stator windings of the stator are controlled or energized such that the first region and the opposite second region rotate about the central axis.

[0087] Figures 21-26 show three-pole or six-pole electric motors or stators. However, electric motors having four pole pieces or more than six pole pieces may also be used. For clarity, the windings of a three-pole motor are not shown in Figures 21-26, and the winding connections of a six-pole motor are not shown in Figures 21-26.

[0088] The pole pieces of the electric motors described herein may each have their own winding and be controlled separately, or the pole pieces may be connected in series and controlled together. The pole pieces connected in series may have the same or different numbers of windings, which may be wound in the same or opposite directions. In particular, opposing pole pieces may be connected in series and wound in opposite directions to generate opposing forces of equal magnitude, which may be advantageous, for example, for deforming the pin ring into an oval shape.

[0089] Furthermore, rather than all pole pieces having windings, for example only every other pole piece can be wound. If the pole pieces can be controlled individually, for example by power electronics, or pairs of opposing pole pieces can be controlled individually, this results in finer control.

[0090] Figure 27 shows an example of a simple control of a three-pole motor, where the pole pieces of the three-pole motor are separately energized and a predetermined signal is used. The current supply I3(t) of the third pole piece is inverse to the current supply I1(t) of the first pole piece, and the current supply I2(t) of the second pole piece is phase shifted relative to the current supply of the first pole piece by the duration of the steady signal of I1(t). The inverse current supplies can be achieved, for example, by reverse windings or even by separate current supplies.

[0091] More complex control is possible depending on the requirements. For example, the amplitude may vary instead of being constant over multiple intervals as shown in Figure 27. Furthermore, a control loop such as a PID controller may be used instead of the feedforward control shown in Figure 27 to improve control of the stator coils.

[0092] The current signal in the stator coil may be used as a sensor signal for the control loop, thereby avoiding the need for a separate sensor such as a Hall sensor. For example, the current signal may be measured during control rest, when the respective stator winding is not energized. The parameters of the control loop can be varied as required, for example to generate a predetermined torque or to generate a predetermined rotational speed.

[0093] FIG. 28 shows a symmetrically spaced toothed belt 102 (V) A cross section passing through is shown.

[0094] FIG. 29 shows shift-type spacing toothed belts 102'', 102''', 102 (IV) The cross section passing through

[0095] FIG. 30 shows a shift-type interval toothed belt 102 in which the backside of the internal teeth forms external teeth. (VII) 28 to 30, the thickness of the toothed belt is not drawn in accurate proportion to the height of the tooth portion.

[0096] The above example embodiments and further example embodiments herein are also disclosed in the following first list of features, which may be combined with other features herein.

[0097] The dimensioning of the opposing toothings and of any intermediate transmission means, if present, may be selected in accordance with this specification so that the teeth are fully engaged both in the pin and ring transmission and in the tension shaft transmission or cycloidal gear, which may be assembled in a configuration with an eccentric transmitter or in a configuration with an oval transmitter.

[0098] [Item 1] A harmonic pin-ring transmission, a first gear having a first tooth portion; a second gear having a second toothed portion; a pin ring having a rounded engagement area; a rotation transmitter for drawing the engagement region of the pin ring into the first teeth of the first gear and the second teeth of the second gear; the first gear, the transmitter, and the second gear are concentrically arranged, the transmitter is arranged radially inside the pin ring, the pin ring is arranged between the first gear and the second gear, the transmitter has a transmitter disk arranged eccentrically with respect to a transmission central axis, and the first tooth portion of the first gear and the second tooth portion of the second gear are formed according to an epicycle structure; the positions of the first tooth portion and the second tooth portion on their respective tooth surfaces are determined by their radial distance from the transmission central axis as a function of rotation angle; Furthermore, the radial distance is determined by an equidistance line relative to the gear orbit; A harmonic pin ring transmission, wherein each position on the gear orbit is determined by the vector sum of a rotation vector and an epicycle vector, the rear end of the rotation vector is on the transmission central axis, the rear end of the epicycle vector is on the front end of the rotation vector, the epicycle angle of the epicycle vector is n times the rotation angle, the length of the rotation vector is longer than the length of the epicycle vector, and n is the number of rounded engagement areas of the harmonic pin ring transmission and is at least 3.

[0099] [Item 2] Item 1 is a harmonic pin ring transmission, wherein the first gear is an internal gear having external teeth, the second gear is an external gear having internal teeth, and with respect to the external teeth of the internal gear, the epicycle angle is measured in the same direction as the rotation angle, and the equidistant line is an internal equidistant line; 10. A harmonic pin and ring transmission, wherein, with respect to the internal teeth of the external gear, the epicycle angle is measured in the opposite direction to the rotation angle, and the equidistance lines are external equidistance lines.

[0100] [Item 3] Item 1: The harmonic pin ring transmission according to item 1, wherein the first gear and the second gear are each an external gear having internal teeth, 10. A harmonic pin-ring transmission, wherein, for the internal teeth of the two outer gears, the epicycle angle is measured in the opposite direction to the rotation angle, and the equidistance lines are outer equidistance lines.

[0101] [Item 4] Item 4. The harmonic pin ring transmission according to item 3, wherein each of the equidistance lines is an equidistance line at a distance equal to the sum of the radius of the rounded engagement region and a correction value, and the correction value depends on the backlash.

[0102] [Item 5] 5. The harmonic pin ring transmission according to item 3 or 4, wherein the harmonic pin ring transmission comprises a rolling bearing abutting the transmitter disc, and the rolling radius is equal to half the diameter of the rolling bearing.

[0103] [Item 6] 5. The harmonic pin ring transmission according to item 3 or 4, wherein the turning radius is equal to half the diameter of the transmitter disc.

[0104] [Item 7] 7. The harmonic pin ring transmission according to any one of items 3 to 6, wherein the epicycle radius is equal to half of an eccentric offset by which the transmitter disc is offset from the transmission central axis.

[0105] [Item 8] 8. The harmonic pin ring transmission according to any one of items 3 to 7, wherein a drive shaft is connected to the transmitter.

[0106] [Item 9] Item 9. The harmonic pin ring transmission according to item 8, wherein a driven shaft is connected to the first gear.

[0107] [Item 10] Item 9. The harmonic pin ring transmission according to item 8, wherein a driven shaft is connected to the second gear.

[0108] [Item 11] 9. The harmonic pin ring transmission according to item 8, wherein a driven shaft is connected to the pin ring.

[0109] [Item 12] An internal gear having external teeth for a harmonic pin ring transmission, wherein the tooth flanks of the external teeth are determined by radial distance from a central axis of the internal gear as a function of rotation angle, and further wherein the radial distance from the central axis is determined by an internal equidistance line relative to a gear orbit, and a position on the gear orbit is determined by a vector sum of a rotation vector, a first epicycle vector, and a second epicycle vector, wherein a trailing end of the rotation vector is on the central axis, a trailing end of the first epicycle vector is at a leading end of the rotation vector, and a trailing end of the second epicycle vector is at a leading end of the first epicycle vector; an epicycle angle of the first epicycle vector is n-1 times as large as the rotation angle, and an epicycle angle of the second epicycle vector is n-3 times as large as the rotation angle, where n is a number of pins in the harmonic pin ring transmission and is at least 4; the first epicycle angle is measured in the same direction as the rotation angle and the second epicycle angle is measured in the opposite direction to the rotation angle; a length of the rotation vector is longer than the sum of the lengths of the first epicycle vector and the second epicycle vector, and the length of the first epicycle vector is longer than the length of the second epicycle vector.

[0110] [Item 13] An external gear having internal teeth for a harmonic pin ring transmission, wherein the positions of the internal teeth on the tooth flanks are each determined by their radial distance from a central axis of the external gear as a function of rotation angle; Furthermore, the radial distance is defined by an outer equidistant line relative to the gear orbit, and the position on the gear orbit is determined by a vector sum of a rotation vector, a first epicycle vector, and a second epicycle vector, respectively, the rear end of the rotation vector is on the central axis, the rear end of the first epicycle vector is at the leading end of the rotation vector, and the rear end of the second epicycle vector is at the leading end of the first epicycle vector; an epicycle angle of the first epicycle vector is (n+1) times as large as the rotation angle, and an epicycle angle of the second epicycle vector is (n+3) times as large as the rotation angle, where n is a number of pins in the harmonic pin ring transmission and is at least 4; the first epicycle angle is measured in the opposite direction to the rotation angle and the second epicycle angle is measured in the same direction as the rotation angle; a length of the rotation vector is longer than the sum of the lengths of the first epicycle vector and the second epicycle vector, and the length of the first epicycle vector is longer than the length of the second epicycle vector.

[0111] [Item 14] A harmonic pin-ring transmission, an internal gear according to item 12; An outer gear according to item 13; a pin ring having a rounded engagement area; a rotation transmitter for drawing the engagement region of the pin ring into the internal teeth of the external gear and the external teeth of the internal gear; wherein the inner gear, the transmitter, and the outer gear are concentrically arranged with respect to one another, the transmitter is arranged radially inside the pin ring, and the pin ring is arranged between the inner gear and the outer gear.

[0112] [Item 15] A harmonic pin-ring transmission, A first outer gear according to item 13; A second external gear according to item 13; a pin ring having a rounded engagement area; a rotation transmitter for drawing the engagement region of the pin ring into the internal teeth of the first external gear and the internal teeth of the second external gear; wherein the transmitter, the first external gear, and the second external gear are concentrically arranged, the transmitter is arranged radially inside the pin ring, and the pin ring is arranged axially between the first external gear and the second external gear.

[0113] [Item 16] 16. The harmonic pin and ring transmission according to item 14 or 15, A harmonic pin ring transmission, wherein a drive shaft is connected to said transmitter.

[0114] [Item 17] Item 17. The harmonic pin ring transmission according to item 16, wherein a driven shaft is connected to the pin ring.

[0115] [Item 18] Item 15. The harmonic pin ring transmission according to item 14, wherein a drive shaft is connected to the transmitter and a driven shaft is connected to the inner gear.

[0116] [Item 19] Item 15. The harmonic pin ring transmission according to item 14, wherein a drive shaft is connected to the transmitter and a driven shaft is connected to the outer gear.

[0117] [Item 20] Item 16. The harmonic pin ring transmission according to item 15, wherein a drive shaft is connected to the transmitter and a driven shaft is connected to one of the two outer gears.

[0118] [Item 21] 21. The harmonic pin ring transmission according to any one of items 14 to 20, wherein each of the equidistance lines is an equidistance line at a distance equal to the sum of the radius of the rounded engagement region and a correction value, and the correction value is determined by backlash.

[0119] [Item 22] 22. The harmonic pin ring transmission according to any one of items 14 to 21, wherein the transmitter comprises an oval cam disc and a flexible rolling bearing in contact with the oval cam disc, and the turning radius is equal to the sum of half the diameter of the flexible rolling bearing and a correction value.

[0120] [Item 23] 22. A harmonic pin ring transmission according to any one of items 14 to 21, wherein the transmitter comprises a first circular disc arranged eccentrically with respect to a transmission central axis, and a second circular disc arranged eccentrically with respect to the transmission central axis, A harmonic pin-ring transmission, wherein the radius of rotation is equal to the sum of the average radius of the envelope of the two eccentrically arranged circular discs and a correction value.

[0121] [Item 24] 24. The harmonic pin and ring transmission according to any one of items 14 to 23, wherein the first epicycle radius is equal to or less than the sum of half the pin and ring stroke and a second correction value, and the second correction value is equal to or less than zero.

[0122] [Item 25] 25. The harmonic pin ring transmission according to any one of items 14 to 24, wherein the length of the second epicycle vector is 1 / 3 of the length of the first epicycle vector.

[0123] The above-mentioned embodiments and further embodiments herein are also disclosed in the following second list of features, which may be combined with other features herein.

[0124] [Item 1] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear; a rotation transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc; The cam disc is disposed in a third axial plane located between the first axial plane and the second axial plane, and the cam disc is formed as a single piece with the hollow drive shaft.

[0125] [Item 2] Item 1 is a harmonic pin ring transmission according to the present invention, wherein the traction mechanism is formed as a pin ring, with pins protruding from a central portion at two opposing sides, the central portion being disposed in the third axial plane, and the rotation transmitter lifts the pins from the outer periphery of the inner gear and presses them against the inner periphery of the first outer gear.

[0126] [Item 3] 3. The harmonic pin ring transmission according to item 1 or 2, wherein the outer periphery of the cam disc has an elliptical shape.

[0127] [Item 4] 3. The harmonic pin ring transmission according to item 1 or 2, wherein the outer periphery of the cam disc has a circular shape and is disposed eccentrically with respect to the transmission central axis.

[0128] [Item 5] 5. The harmonic pin ring transmission according to any one of items 1 to 4, wherein a rolling bearing is disposed between the cam disc and the traction mechanism.

[0129] [Item 6] 6. The harmonic pin ring transmission according to any one of items 1 to 5, wherein the transmitter 5 is made essentially of aluminum.

[0130] [Item 7] 7. The harmonic pin ring transmission according to any one of items 1 to 6, wherein the transmitter comprises a ring connected to the hollow drive shaft via a connecting strut.

[0131] [Item 8] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear; a rotation transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc, the cam disc is disposed in a third axial plane located between the first axial plane and the second axial plane, the first outer gear is formed by a first outer ring, the second outer gear is formed by a second outer ring, and the first ring and the second ring are inserted into a support ring, a harmonic pin ring transmission.

[0132] [Item 9] Item 9. The harmonic pin ring transmission according to item 8, wherein the first outer ring and the second outer ring are each made of plastic.

[0133] [Item 10] 10. The harmonic pin ring transmission according to item 8 or 9, wherein the first outer ring and the second outer ring each include a radially outwardly protruding journal distributed over the outer periphery of the respective outer ring, and the support ring includes matching recesses into which the journals are inserted.

[0134] [Item 11] 11. The harmonic pin ring transmission according to any one of items 8 to 10, wherein the support ring is made of aluminum.

[0135] [Item 12] 12. The harmonic pin ring transmission according to any one of items 8 to 11, wherein the support ring includes two partial rings adjacent to each other in the axial direction.

[0136] [Item 13] 13. The harmonic pin ring transmission according to any one of items 8 to 12, wherein the first outer ring, the second outer ring, and the support ring have threaded holes that fit together.

[0137] [Item 14] Item 14. The harmonic pin ring transmission according to item 13, wherein screws pass through threaded holes in the transmission cover and the matching threaded holes in the first outer ring, the support ring, and the second outer ring to threadably engage with threads in a transmission housing of the harmonic pin ring transmission.

[0138] [Item 15] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear; a rotation transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc, the cam disc being disposed in a third axial plane located between the first axial plane and the second axial plane; The harmonic pin ring transmission includes a hollow output shaft attached to the inner gear via a motor freewheel and a pedal shaft attached to the hollow output shaft via a pedal shaft freewheel, the pedal shaft having a receiving area for the motor freewheel on its outer periphery and a receiving area for the pedal shaft freewheel on its inner periphery.

[0139] [Item 16] Item 16. The harmonic pin ring transmission according to item 15, wherein the motor freewheel is configured as a clamp roller freewheel and the pedal shaft freewheel is configured as a pawl freewheel.

[0140] [Item 17] 17. The harmonic pin and ring transmission according to item 15 or 16, The driven shaft extends axially on the output side of the hollow drive shaft, a ball bearing is arranged between the hollow output shaft and the pedal shaft, and the hollow output shaft is provided with a fastening area for an output element.

[0141] [Item 18] 1. A freewheel assembly having an outer clamp roller freewheel and an inner pawl freewheel, a hollow drive shaft; a hollow output shaft; Pedal shaft and the pedal shaft, the hollow output shaft, and the hollow drive shaft are arranged concentrically with one another, the hollow output shaft is arranged radially inward of the hollow drive shaft, and the pedal shaft is arranged radially inward of the hollow output shaft; the hollow output shaft has an inner periphery with a stepped pawl engagement area and an outer periphery with a stepped clamp roller rolling area; the pedal shaft is provided with a star-shaped receiving area for a pawl; The star-shaped receiving area includes a pawl seat and a spring seat disposed adjacent the pawl seat.

[0142] [Item 19] Item 19. The freewheel assembly of item 18, wherein the stepped clamp body rolling area on the outer periphery of the hollow output shaft and the stepped pawl engagement area on the inner periphery of the hollow output shaft lie in essentially the same axial plane.

[0143] [Item 20] 20. The freewheel assembly according to claim 18 or 19, wherein the hollow drive shaft comprises a disk-shaped region having external teeth; The external teeth are provided on the outer periphery of the disc-shaped region.

[0144] [Item 21] 21. The freewheel assembly according to any one of items 18 to 20, wherein the hollow output shaft has an annular thickened portion at a first end and a fastening region for an output means at a second end opposite the first end.

[0145] [Item 22] 22. The freewheel assembly according to any one of items 18 to 21, wherein the outer periphery of the hollow output shaft is provided with a bearing area for a ball bearing.

[0146] [Item 23] 23. The freewheel assembly according to any one of items 18 to 22, wherein the inner circumference of the hollow output shaft is provided with a bearing area for a ball bearing.

[0147] [Item 24] 24. The freewheel assembly according to any one of items 18 to 23, wherein the inner circumference of the hollow output shaft is provided with an internal thread at one end.

[0148] [Item 25] 25. A freewheel assembly according to any one of the preceding five items 18 to 24, a pawl rotatably mounted on the pawl seat; and a spring element disposed on the spring seat and connected to the pawl. a freewheel cage having a plurality of webs and clamp rollers disposed between the plurality of webs; wherein the freewheel cage and the clamp roller are radially disposed between the clamp roller rolling area of ​​the hollow output shaft and an inner circumference of the hollow drive shaft.

[0149] [Item 26] 26. The freewheel assembly according to any one of items 18 to 25, wherein the pawl seat is cylindrical, one end of which is closed by a wall, and the opposite end of which is open.

[0150] [Item 27] 27. The freewheel assembly according to any one of items 18 to 26, wherein the stepped clamping body rolling area and the freewheel cage each comprise at least two receiving areas for a spring element, and in each case a spring element is arranged between the receiving area of ​​the clamping body rolling area and the receiving area of ​​the freewheel cage.

[0151] [Item 28] 28. The freewheel assembly according to any one of items 18 to 27, wherein the pedal shaft includes a force sensor unit, the force sensor unit includes a load cell and a pedal shaft ball bearing, and the load cell is disposed in the pedal shaft ball bearing.

[0152] [Item 29] Item 29. The freewheel assembly according to item 28, wherein the load cell comprises an inner annular portion attached to an outer annular portion via a plurality of fastening projections, and the pedal shaft ball bearing is inserted into the inner annular portion.

[0153] [Item 30] 30. The freewheel assembly of claim 29, wherein the inner and outer portions of the load cell are radially offset relative to one another, the plurality of fastening projections are laterally bounded by radial slots, and at least two of the plurality of fastening projections comprise strain gauges.

[0154] [Item 31] 31. The freewheel assembly according to item 29 or 30, wherein the axial thickness of the outer ring decreases in the region of the plurality of fastening projections.

[0155] [Item 32] a pedal shaft for a freewheel assembly, said pedal shaft having a first fastening area for a pedal crank at a first end and a second fastening area for a pedal crank at an opposite second end; The pedal shaft includes a star-shaped receiving area for a pawl near the first end.

[0156] [Item 33] Item 33. The pedal shaft according to item 32, wherein the star-shaped receiving area includes a plurality of steps, each of the steps including a first side surface, a second side surface, a pawl support area inclined in a predetermined direction relative to the circumferential direction and including a spring seat, an upper surface essentially parallel to the outer periphery, and an end area having a pawl seat, the pawl seat having a cylindrical shape, open on one axial side and closed on the opposite axial side.

[0157] [Item 34] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear; a rotation transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc, the cam disc being disposed in a third axial plane located between the first axial plane and the second axial plane; The harmonic pin ring transmission includes a hollow output shaft attached to the inner gear via a motor freewheel and a pedal shaft attached to the hollow output shaft via a pedal shaft freewheel, the pedal shaft having a receiving area for the motor freewheel on its outer periphery and a receiving area for the pedal shaft freewheel on its inner periphery.

[0158] [Item 35] 35. The harmonic pin ring transmission according to item 34, wherein the motor freewheel is configured as a clamp roller freewheel and the pedal shaft freewheel is configured as a pawl freewheel.

[0159] [Item 36] Item 36. The harmonic pin and ring transmission according to item 34 or 35, The driven shaft extends axially on the output side of the hollow drive shaft, a ball bearing is arranged between the hollow output shaft and the pedal shaft, and the hollow output shaft is provided with a fastening area for an output element.

[0160] [Item 37] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a pin ring having pins extending between the first outer gear and the inner gear; a rotation transmitter that lifts the pin of the pin ring from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc, the cam disc being disposed in a third axial plane located between the first axial plane and the second axial plane; A harmonic pin ring transmission, wherein the pin ring is formed as a single piece and is made of metal, the pins are formed by protrusions protruding from two opposite sides of a central region of the pin ring, and the central region is provided with an inner bearing surface for abutting a bearing.

[0161] [Item 38] Item 38. The harmonic pin ring transmission according to item 37, wherein the protrusion is cylindrical on a first of the two opposing sides and the protrusion is partially cylindrical on a second of the two opposing sides, the cylindrical region being located radially on the outside of the pin ring.

[0162] [Item 39] Item 38. The harmonic pin ring transmission according to item 37, wherein the protrusion has a rounded inner engagement region and a rounded outer engagement region on a first side of the two opposing sides, and the protrusion has a rounded outer engagement region on a second side of the two opposing sides.

[0163] [Item 40] 40. The harmonic pin ring transmission according to any one of items 37 to 39, wherein a bearing is disposed between the cam disc and the pin ring, and the pin ring has a shoulder on the inside for supporting the bearing.

[0164] [Item 41] A pin ring for a harmonic pin ring transmission formed as a single piece and made of metal, said pin ring comprising pins formed by protrusions protruding from two opposite sides of a central region of said pin ring, said central region comprising an inner bearing surface for abutting an outer bearing surface of a bearing.

[0165] [Item 42] Item 42. The pin ring according to item 41, wherein the protrusion is cylindrical on a first of the two opposing sides, and the protrusion is partially cylindrical on a second of the two opposing sides; A pin ring, wherein a cylindrical region is located radially outside the pin ring.

[0166] [Item 43] Item 42. The pin ring according to item 41, wherein the protrusion comprises a rounded inner engagement region and a rounded outer engagement region on a first side of the two opposing sides; The protrusion includes a rounded outer engagement area on a second of the two opposing sides.

[0167] [Item 44] Item 42. The pin ring according to item 41, wherein a web is in each case located between the protrusions on the first of the two opposing sides, and the outer boundary of the protrusions merges smoothly with the outer boundary of the web.

[0168] [Item 45] 45. The harmonic pin and ring transmission according to any one of items 41 to 44, A harmonic pin and ring transmission, wherein a bearing is disposed between the cam disc and the pin ring, and the pin ring has an inner shoulder for supporting the bearing.

[0169] [Item 46] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear;

[0170] [Item 37] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a pin ring having pins extending between the first outer gear and the inner gear; a rotation transmitter that lifts the pin of the pin ring from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc, the cam disc being disposed in a third axial plane located between the first axial plane and the second axial plane; A harmonic pin ring transmission, wherein the pin ring is formed as a single piece and is made of metal, the pins are formed by protrusions protruding from two opposite sides of a central region of the pin ring, and the central region is provided with an inner bearing surface for abutting a bearing.

[0171] [Item 38] Item 38. The harmonic pin ring transmission according to item 37, wherein the protrusion is cylindrical on a first of the two opposing sides and the protrusion is partially cylindrical on a second of the two opposing sides, the cylindrical region being located radially on the outside of the pin ring.

[0172] [Item 39] Item 38. The harmonic pin and ring transmission according to item 37, wherein the protrusion includes a rounded inner engagement region and a rounded outer engagement region on a first side of the two opposing sides; The protrusion includes a rounded outer engagement area on a second of the two opposing sides.

[0173] [Item 40] 40. The harmonic pin ring transmission according to any one of items 37 to 39, wherein a bearing is disposed between the cam disc and the pin ring, and the pin ring has a shoulder on the inside for supporting the bearing.

[0174] [Item 41] A pin ring for a harmonic pin ring transmission formed as a single piece and made of metal, said pin ring comprising pins formed by protrusions protruding from two opposite sides of a central region of said pin ring, said central region comprising an inner bearing surface for abutting an outer bearing surface of a bearing.

[0175] [Item 42] Item 42. The pin ring according to item 41, wherein the protrusion is cylindrical on a first of the two opposing sides and the protrusion is partially cylindrical on a second of the two opposing sides, the cylindrical region being located radially on the outside of the pin ring.

[0176] [Item 43] Item 42. The pin ring according to item 41, wherein the protrusion comprises a rounded inner engagement region and a rounded outer engagement region on a first side of the two opposing sides; The protrusion includes a rounded outer engagement area on a second of the two opposing sides.

[0177] [Item 44] Item 42. The pin ring according to item 41, wherein a web is in each case located between the protrusions on the first of the two opposing sides, and the outer boundary of the protrusions merges smoothly with the outer boundary of the web.

[0178] [Item 45] 45. The harmonic pin ring transmission according to any one of items 41 to 44, wherein a bearing is disposed between the cam disc and the pin ring, and the pin ring has a shoulder on the inside for supporting the bearing.

[0179] [Item 46] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear; a rotation transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter comprises a hollow drive shaft and a cam disc, the cam disc being disposed in a third axial plane located between the first axial plane and the second axial plane; A harmonic pin ring transmission, wherein a pedal shaft is disposed radially inside the driven shaft, and the pedal shaft is mounted within the motor housing via a drive-side pedal shaft ball bearing and a load cell.

[0180] [Item 47] Item 47. The harmonic pin ring transmission according to item 46, wherein the load cell comprises an inner annular portion attached to an outer annular portion via a fastening protrusion, the pedal shaft ball bearing is inserted into the inner annular portion, and the outer annular portion is inserted into a cylindrical region of the motor housing.

[0181] [Item 48] 48. The harmonic pin ring transmission according to any one of items 46 to 47, wherein a wave spring is disposed between the load cell and the drive-side rotor ball bearing.

[0182] [Item 49] 1. A harmonic pin and ring transmission having an input shaft and an output shaft, the transmission comprising: a first external gear and an internal gear arranged concentrically with respect to the first external gear in a first axial plane; a second external gear disposed in a second axial plane; a traction mechanism extending between the first outer gear and the inner gear; a rotation transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear; the transmitter includes a hollow drive shaft and a cam disc, the cam disc is disposed in a third axial plane located between the first axial plane and the second axial plane, a pedal shaft is disposed radially inside the output shaft, and a planetary gear and a pedal shaft freewheel are disposed in the force flow between the pedal shaft and the output shaft.

[0183] [Item 50] Item 49 is a harmonic pin ring transmission, wherein a planet carrier of the planetary gear is connected to the pedal shaft, a ring gear of the planetary gear is provided with a connection region for connection with a transmission housing, a sun gear of the planetary gear is attached to the pedal shaft, and the pedal shaft freewheel is disposed between a hollow shaft connected to the sun gear and the output shaft.

[0184] [Item 51] Item 49: The harmonic pin and ring transmission according to item 49, A harmonic pin ring transmission, wherein the pedal shaft freewheel is disposed between the crankshaft and a planet carrier of the planetary gear, the ring gear of the planetary gear is rotatably mounted within the harmonic transmission, and the sun gear of the planetary gear is adapted for mounting to a fixed housing portion.

[0185] [Item 52] A tension shaft transmission, the tension shaft transmission comprising: an external gear having internal teeth, said external gear comprising a fastening area for attachment to a transmission housing; a tension shaft having external teeth, the tension shaft being arranged concentrically with respect to the external gear in an axial plane; a rotation transmitter that presses the tension shaft against the internal teeth of the outer gear; the transmitter comprises a hollow drive shaft and a cam disc, a ball bearing being disposed on the outer periphery of the cam disc; the cross section of the tooth tips of the external teeth of the tension shaft essentially corresponds to a sector; 10. A tension shaft transmission, wherein the internal toothing of the external gear is essentially defined, relative to the axis of the external gear, by external equidistant lines to the gear raceways defined by the equations x(t)=r1*cost(t)+r2*cos((n+1)*t)+r3*cos((n+3)*t) and y(t)=r1*sin(t)-r2*sin((n+1)*t)+r3*sin((n+3)*t), where n+1 is the number of teeth in the internal toothing of the external gear, and the radii r1, r2, and r3 are greater than zero, with the following magnitudes of the radii applying: r2>r3 and r1>r2+r3.

[0186] [Item 53] Item 53. A tension shaft transmission according to item 52, wherein the tension shaft is formed in a cup shape, and a fastening area for fastening a driven shaft is formed at the bottom of the cup shape.

[0187] [Item 54] Item 54. The tension shaft transmission according to item 53, wherein a central circular opening is formed in the bottom of the cup shape, and the fastening region of the tension shaft comprises fastening holes arranged around the central circular opening.

[0188] [Item 55] Item 53. A tension shaft transmission according to item 52, wherein the tension shaft has a cylindrical shape, and the transmission comprises a second external gear having a fastening region for fastening a driven shaft, the internal teeth of the external gear being determined by the same structure as the internal teeth of the first external gear.

[0189] [Item 56] A tension shaft transmission, the tension shaft transmission comprising: an external gear having internal teeth, said external gear comprising a fastening area for attachment to a transmission housing; a tension shaft having external teeth, the tension shaft being arranged concentrically with the external gear in an axial plane, the cross section of the tips of the external teeth of the tension shaft essentially corresponding to a sector; a rotation transmitter that presses the tension shaft against the internal teeth of the outer gear; the transmitter comprises a hollow drive shaft and a cam disc; the tooth flanks of the internal teeth of the external gear are determined by radial distance from a central axis of the internal gear as a function of rotation angle; Furthermore, the radial distance from the central axis is determined by an inner equidistance line relative to the gear orbit, and the position on the gear orbit is determined by a vector sum of a rotation vector, a first epicycle vector, and a second epicycle vector, respectively, the rear end of the rotation vector is on the central axis, the rear end of the first epicycle vector is at the leading end of the rotation vector, and the rear end of the second epicycle vector is at the leading end of the first epicycle vector; A tension shaft transmission, wherein the epicycle angle of the first epicycle vector is (n+1) times the rotation angle, the epicycle angle of the second epicycle vector is (n+3) times the rotation angle, n is the number of pins in the harmonic pin ring transmission and is at least 4, the length of the rotation vector is longer than the sum of the lengths of the first epicycle vector and the second epicycle vector, and the length of the first epicycle vector is longer than the length of the second epicycle vector.

[0190] [Item 57] A two-stage reduction gear, the two-stage reduction gear comprising: a fixed external gear having a first internal toothing, the external gear comprising a fastening area for attachment to a transmission housing; a rotatable external gear having a second internal toothing, said external gear comprising a fastening area for attachment to a driven shaft; a two-piece, single-piece pin ring, the two-piece, single-piece pin ring having first and second external teeth, the first external teeth of the two-piece, single-piece pin ring engaging the internal teeth of the fixed external gear and the second external teeth of the two-piece, single-piece pin ring engaging the internal teeth of the rotatable external gear; a rotation transmitter for pressing the two-part single-piece pin ring against the internal teeth of the fixed external gear and the internal teeth of the rotatable external gear; A two-stage reduction gear.

[0191] [Item 58] Item 57 is a two-stage reduction gear according to item 57, wherein the number of teeth of the internal teeth of the fixed external gear is greater than the number of teeth of the first external teeth, and the number of teeth of the internal teeth of the rotatable external gear is greater than the number of teeth of the second external teeth, A two-stage reduction gear, wherein the number of teeth of the fixed external gear is greater than the number of teeth of the rotatable external gear, and the number of teeth of the first external gear is greater than the number of teeth of the second external gear.

[0192] [Item 59] 59. A two-stage reduction gear according to item 57 or 58, wherein the transmitter comprises a circular ring eccentric to the axis of the fixed outer gear.

[0193] [Item 60] Item 57. A two-stage reduction gear according to any one of Items 57 to 59, wherein a cross section of the tooth tips of the first external teeth and a cross section of the tooth tips of the second external teeth essentially correspond to a sector shape.

[0194] [Item 61] 61. A two-stage reduction gear according to any one of items 57 to 60, wherein a cross section of the tooth tips of the first external teeth and a cross section of the tooth tips of the second external teeth essentially correspond to equidistant lines with respect to the gear orbits defined by the equations x(t)=r1*cos(t)+r2*cos(nt) and y(t)=r1*sin(t)+r2*sin(nt), and wherein r1>0, r2>0 and r1>r2 apply to the radii r1 and r2.

[0195] [Item 62] 62. A two-stage reduction gear according to any one of items 57 to 61, wherein a cross section of the tooth tips of the first external teeth and a cross section of the tooth tips of the second external teeth essentially correspond to equidistant lines with respect to the gear orbits defined by the equations x(t)=r1*cos(t)+r2*cos(nt) and y(t)=r1*sin(t)-r2*sin(nt), and wherein r1>0, r2>0 and r1>r2 apply to the radii r1 and r2.

[0196] [Item 63] 1. A load cell for determining a radial force acting on a crankshaft, said load cell comprising: a receiving sleeve for receiving a ring of the bearing; a fastening ring for mounting the load cell within a transmission housing; an axial support portion provided on the fastening ring for axially supporting the ring of the bearing; measuring areas for receiving radial forces of the receiving sleeve, the measuring areas connecting the receiving sleeve to the fastening ring, and strain sensors attached to at least two of the measuring areas; A load cell comprising:

[0197] [Item 64] A freewheel assembly having an outer transmission freewheel and an inner pedal shaft freewheel, said freewheel assembly comprising: a hollow drive shaft; a hollow output shaft; Pedal shaft and the pedal shaft, the hollow output shaft, and the hollow drive shaft are arranged concentrically with one another, the hollow output shaft is arranged radially inside the hollow drive shaft, the pedal shaft is arranged radially inside the hollow output shaft, the pedal shaft freewheel is arranged between the pedal shaft and the hollow output shaft, the transmission freewheel is arranged on the opposite side of the hollow output shaft from the pedal shaft freewheel, and the hollow output shaft has adaptation portions on the inside and outside of the area of ​​each of the freewheels.

[0198] [Item 65] A single-piece pin ring made of metal, wherein a pin retaining ring and an arrangement of multiple pins projecting axially from said pin retaining ring on two opposite sides are made as a single piece.

[0199] [Item 66] Item 66. The single-piece pin ring according to item 65, wherein the plurality of pins are connected to one another in a circumferential direction.

[0200] [Item 67] 67. The single-piece pin ring according to item 65 or 66, wherein on a first of the two opposing sides the pin is formed as a half pin suitable for engagement with an internal toothing, and on a second of the opposing sides the pin is formed as a whole pin suitable for engagement with an internal toothing and with an external toothing opposite the internal toothing.

[0201] [Item 68] 1. A single-piece pin ring made of metal, the single-piece pin retaining ring having an inner smooth circumference and an outer rounded ridge, the ridges being fabricated as a single piece with the pin retaining ring.

[0202] [Item 69] Item 69. The single-piece pin retaining ring of item 68, wherein a head region of at least one of the plurality of rounded ridges comprises a semicircular cross-section.

[0203] [Item 70] A support ring assembly for a reduction gear having a first external gear and a second external gear, the support ring assembly comprising a support ring, a first external gear having first internal teeth, and a second external gear having second internal teeth, the first external gear and the second external gear being inserted into the support ring on opposite sides, and the support ring comprising a fastening area for attachment to a transmission housing.

[0204] [Item 71] Item 71. A support ring assembly according to item 70, A support ring assembly, wherein at least the first external gear and the second external gear are made of plastic.

[0205] [Item 72] Item 73. A support ring assembly according to any one of items 71 to 72, wherein the first external gear and the second external gear are each connected to the support wheel via a pin-and-groove connection.

[0206] [Item 73] A single-piece rotor-transmitter element for a reduction gear with a hollow shaft, the hollow shaft having a fastening area for fastening a rotor package on a first side thereof and a cam disc on a second side opposite the first side thereof, the outer periphery of the cam disc being configured as a receiving portion for a ball bearing.

[0207] [Item 74] Item 74. The single-piece rotor-transmitter element according to item 73, wherein the single-piece rotor-transmitter element is made of aluminum.

[0208] [Item 75] 75. A single-piece rotor-transmitter element according to item 73 or 74, wherein the hollow shaft is dimensioned to allow a pedal shaft to pass through the hollow shaft.

[0209] [Item 76] 76. A single-piece rotor-transmitter element according to any one of items 73 to 75, wherein the cam disc has a circular outer periphery arranged eccentrically with respect to the central axis of the hollow shaft.

[0210] [Item 77] 76. A single-piece rotor-transmitter element according to any one of items 73 to 75, wherein the cam disc has an outer periphery that is oval relative to the central axis of the hollow shaft.

[0211] [Item 78] 1. A drive shaft with planetary gears arranged on the drive shaft, wherein a planet carrier of the planetary gears is fixedly connected to the drive shaft, a ring gear of the planetary gears comprises a fastening area for attachment to a transmission housing and a receiving area for a torque sensor, a sun gear of the planetary gears configured as a ring gear and arranged concentrically with respect to the drive shaft, and the sun gear is connected to a hollow output shaft of the planetary gears rotatably mounted on the drive shaft.

[0212] [Item 79] 1. A drive shaft with planetary gears arranged on the drive shaft, wherein a planet carrier of the planetary gears is attached to the drive shaft via a freewheel, a sun gear of the planetary gears comprises a fastening area for attachment to a transmission housing and a receiving area for a torque sensor, and a ring gear of the planetary gears comprises a receiving area for a ball bearing for support in the transmission housing.

[0213] [Item 80] A drive shaft having planetary gears arranged thereon, wherein a planet carrier of the planetary gears is provided with a fastening area for attachment to a transmission housing, a hollow shaft of the planetary gears is fixedly connected to the drive shaft, and a sun gear of the planetary gears is configured as a hollow shaft arranged concentrically with respect to the drive shaft and rotatably attached to the drive shaft.

[0214] [Item 81] A cycloidal gear, the cycloidal gear comprising: A transmission housing; an external gear having internal teeth fixed to the transmission housing; an input shaft arranged concentrically with the external gear, the input shaft including a drive-side eccentric disk on which a first ball bearing is arranged and an output-side eccentric disk on which a second ball bearing is arranged; a drive-side inner gear attached to the first ball bearing and having external teeth; and an output-side inner gear attached to the second ball bearing and having external teeth. wherein the drive-side inner gear and the output-side inner gear are disposed inside the external gear, and the external teeth of the drive-side inner gear and the output-side outer gear are engaged with the internal teeth of the external gear, respectively.

[0215] [Item 82] Item 81: A cycloidal gear according to item 81, comprising a crankshaft mounted within the input shaft and a load cell according to item 63 mounted on the crankshaft on the drive side.

[0216] [Item 83] Item 83. A cycloidal gear according to any one of items 81 or 82, wherein the input shaft is configured as a single-piece rotor-transmitter element according to any one of items 73 to 77.

[0217] [Item 84] A cycloidal gear according to any one of items 81 to 83, The cycloidal gear comprises a crankshaft mounted within the input shaft, the crankshaft comprising the planetary gears according to items 78 to 80, the crankshaft forming the drive shaft of the planetary gears.

[0218] [Item 85] A cycloidal gear according to any one of items 81 to 84, a third ball bearing is disposed on the input shaft on the output side of the output side eccentric disk, a driven pulley is disposed on the third ball bearing, the driven pulley has a carrier pin, the carrier pin engages with openings in the drive side inner gear and the output side inner gear, and an output shaft is formed radially inside the driven pulley.

[0219] [Item 86] Item 86. The cycloid gear according to item 85, wherein an output shaft is formed radially inside the driven pulley, the third ball bearing is disposed on an inner shoulder of the output shaft, and an inner gear ball bearing is disposed on an outer shoulder of the output shaft diagonally opposite the third ball bearing, and the inner gear ball bearing is supported by the transmission housing.

[0220] [Item 87] A cycloidal gear according to any one of claims 81 to 83, 1. A cycloidal gear, wherein at least one of the internal gears comprises a first toothing and a second external toothing, and the cycloidal gear comprises a rotatable external gear having internal toothing, the second external toothing engaging the internal toothing of the rotatable external gear, the rotatable external gear comprising a fastening region for attaching a driven shaft.

Claims

1. A toothed belt having internal teeth and external teeth, wherein the tooth tips of the internal teeth have a rounded region, the tooth tips of the external teeth have a rounded region, wherein the tooth tips of the internal teeth are arranged on the radially opposite side of each tooth root of the external teeth such that the toothed belt forms an offset-type interval arrangement in which the teeth of the internal teeth and the external teeth are offset from each other, the toothed belt is characterized in that it has a smooth central bearing region on the inner side and does not have a smooth central bearing region on the outer side.

2. The toothed belt according to Claim 1, wherein the tooth roots of the external teeth and the tooth roots of the internal teeth are formed as flat tooth roots corresponding to the surface of a straight cylinder.

3. The toothed belt according to Claim 1 or 2, comprising the inner central bearing region provided in a straight cylindrical shape such that the internal teeth contact the central bearing region in one region facing axially.

4. The toothed belt according to any one of Claims 1 to 3, wherein the toothed belt is manufactured as a single component.

5. The toothed belt according to any one of Claims 1 to 4, wherein the toothed belt contains plastic.

6. The toothed belt according to any one of Claims 1 to 5, wherein the toothed belt contains alloy steel.

7. A transmission having an input shaft and an output shaft, an outer gear, an inner gear arranged coaxially with the outer gear inside the outer gear, and a traction mechanism extending between the outer gear and the inner gear, at least one rotary transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the outer gear, wherein the traction mechanism is the toothed belt according to any one of Claims 1 to 6.

8. The transmission according to Claim 7, wherein the input shaft is connected to the rotary transmitter. This is the characteristic of the transmission.

9. The transmission according to Claim 7, wherein the input shaft is connected to the outer gear. This is the characteristic of the transmission.

10. The transmission according to Claim 7, wherein the input shaft is connected to the inner gear. This is the characteristic of the transmission.

11. The transmission according to claim 8 or 9, wherein the output shaft is connected to the inner gear characterized in that it is a transmission.

12. The transmission according to any one of claims 9 or 10, wherein the output shaft is connected to the rotary transmitter characterized in that it is a transmission.

13. The transmission according to claim 8 or 10, wherein the output shaft is connected to the outer gear characterized in that it is a transmission.

14. A transmission having an input shaft and an output shaft, wherein the transmission comprises a first outer gear, an inner gear arranged concentrically with the first outer gear in a first axial plane, a second outer gear arranged in a second axial plane, a traction mechanism extending between the first outer gear and the inner gear, a rotary transmitter that lifts the traction mechanism from the outer periphery of the inner gear and presses it against the inner periphery of the first outer gear, and the rotary transmitter includes a hollow drive shaft and a cam disk, the cam disk is arranged in a third axial plane located between the first axial plane and the second axial plane, and the cam disk is formed as a single part with the hollow drive shaft, the traction mechanism is provided as a toothed belt according to any one of claims 1 to 6, a transmission.

15. a first gear having a first tooth portion, a second gear having a second tooth portion, a pin ring having a rounded engagement region, a rotary transmitter for pulling the engagement region of the pin ring into the first tooth portion of the first gear and the second tooth portion of the second gear, and the first gear, the rotary transmitter, and the second gear are arranged concentrically with each other, the rotary transmitter is arranged radially inside the pin ring, the pin ring is arranged between the first gear and the second gear, the rotary transmitter includes a transmitter disk arranged eccentrically with respect to the transmission central axis, and the first tooth portion of the first gear and the second tooth portion of the second gear are formed according to an epicyclic structure The positions on the tooth surfaces of the first tooth part and the second tooth part are each determined by the radial distance from the transmission central axis as a function of the rotation angle. Furthermore, the radial distance is determined by an equidistant line with respect to the gear orbit. The positions on the gear orbit are each determined by the vector sum of the rotation vector and the circumferential rotation vector. The rear end of the rotation vector is on the transmission central axis. The rear end of the circumferential rotation vector is at the tip of the rotation vector. The circumferential rotation angle of the circumferential rotation vector is n times the magnitude of the rotation angle. The length of the rotation vector is longer than the length of the circumferential rotation vector. n is the number of rounded engagement regions and is at least 3. The pin ring is provided as the toothed belt according to any one of claims 1 to 6, a harmonic pin ring transmission.

16. An inner gear having external teeth, An outer gear having internal teeth, A pin ring having a rounded engagement region, A rotary transmitter for drawing the engagement region of the pin ring into the internal teeth of the outer gear and the external teeth of the inner gear. The inner gear, the rotary transmitter, and the outer gear are arranged concentrically with each other. The rotary transmitter is arranged radially inside the pin ring. The pin ring is arranged between the inner gear and the outer gear. The tooth surface of the external teeth is determined by the radial distance from the central axis of the inner gear as a function of the rotation angle. Furthermore, the radial distance from the central axis is determined by an inner equidistant line with respect to the gear orbit. The position on the gear orbit is determined by the vector sum of the rotation vector, the first circumferential rotation vector, and the second circumferential rotation vector. The rear end of the rotation vector is on the central axis. The rear end of the first circumferential rotation vector is at the tip of the rotation vector. The rear end of the second circumferential rotation vector is at the tip of the first circumferential rotation vector. The rotation circle angle of the first rotation circle vector is of a magnitude that is n - 1 times the rotation angle, the rotation circle angle of the second rotation circle vector is of a magnitude that is n - 3 times the rotation angle, n is the number of pins of the harmonic pin ring transmission and is at least 4, the rotation circle angle of the first rotation circle vector is measured in the same direction as the rotation angle, the rotation circle angle of the second rotation circle vector is measured in the opposite direction to the rotation angle, the length of the rotation vector is longer than the sum of the lengths of the first rotation circle vector and the second rotation circle vector, and the length of the first rotation circle vector is longer than the length of the second rotation circle vector. The positions on the tooth surfaces of the internal teeth are each determined by the radial distance from the central axis of the outer gear as a function of the rotation angle. Furthermore, the radial distance is defined by an outer equidistant line with respect to the gear orbit, the positions on the gear orbit are each determined by the vector sum of the rotation vector, the first rotation circle vector, and the second rotation circle vector, the rear end of the rotation vector is on the central axis, the rear end of the first rotation circle vector is at the tip of the rotation vector, and the rear end of the second rotation circle vector is at the tip of the first rotation circle vector. The rotation circle angle of the first rotation circle vector is of a magnitude that is (n + 1) times the rotation angle, the rotation circle angle of the second rotation circle vector is of a magnitude that is (n + 3) times the rotation angle, n is the number of pins of the harmonic pin ring transmission and is at least 4, the rotation circle angle of the first rotation circle vector is measured in the opposite direction to the rotation angle, the rotation circle angle of the second rotation circle vector is measured in the same direction as the rotation angle, the length of the rotation vector is longer than the sum of the lengths of the first rotation circle vector and the second rotation circle vector, and the length of the first rotation circle vector is longer than the length of the second rotation circle vector. The pin ring is provided as a toothed belt according to any one of claims 1 to 6, harmonic pin ring transmission.

17. A motor transmission unit having a transmission according to any one of claims 7 to 14, where an electric motor is provided and its rotor is connected to the input shaft of the transmission. A transmission, characterized by this.

18. A motor transmission unit having the transmission according to any one of claims 7 to 14, wherein an internal combustion engine is provided, and the output shaft is connected to the input shaft of the transmission Characterized by a transmission.

19. A vehicle having the motor transmission unit according to claim 17 or 18, wherein at least one running wheel of the vehicle is connected to the output shaft of the transmission Characterized by a transmission.

20. A generator having a drive unit, a power generation unit for generating power, and the transmission according to any one of claims 7 to 14, wherein the input shaft of the transmission is connected to the drive unit, and the output shaft of the transmission is connected to the input shaft of the generator.

Images