WO2008040281A1 - Planetengetriebe mit kontinuierlich veränderbarer übersetzung - Google Patents
Planetengetriebe mit kontinuierlich veränderbarer übersetzung Download PDFInfo
- Publication number
- WO2008040281A1 WO2008040281A1 PCT/DE2007/001609 DE2007001609W WO2008040281A1 WO 2008040281 A1 WO2008040281 A1 WO 2008040281A1 DE 2007001609 W DE2007001609 W DE 2007001609W WO 2008040281 A1 WO2008040281 A1 WO 2008040281A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- planetary
- sun
- gears
- gear
- rotation
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
- F16H15/50—Gearings providing a continuous range of gear ratios
- F16H15/506—Gearings providing a continuous range of gear ratios in which two members of non-uniform effective diameter directly co-operate with one another
Definitions
- the invention relates to a planetary gear with continuously variable transmission.
- Transmissions with continuously variable transmission which are also called variator, are usually designed as a belt transmission in which the force is transmitted via traction means such as wide V-belts, disk chains or thrust belts, or as a friction gear such as toroidal or conical ring gear.
- a peculiarity of the friction gear is that the planet gears must be stored, tilted and pressed on separately provided components.
- An object of the invention is to provide a planetary gear continuously variable transmission with a simple structure.
- a planetary gear with continuously variable translation is provided, the two at mutual axial distance about the same axis of rotation at different speeds rotatable sun gears with Finmantelvidin a coaxially arranged to the sun gears ring gear with a radially inner inner peripheral surface and planetary gears with planetary surfaces in frictional contact with the inner circumferential surface and the Sonnenmantelvid are, wherein the Sonnenmantel vom, the planetary lateral surfaces and the inner peripheral surface are shaped such that at an axial displacement of the ring gear relative to the sun gears and associated tilting of the axes of rotation of the planet gears relative to the axis of rotation of the sun gears, the translations change in opposite directions between the ring gear and each of the sun gears.
- the planetary gear according to the invention is simple in construction and low wear or maintenance. Characterized in that each planetary surface is in frictional engagement with the two sun gears on different sides of a plane perpendicular to the axis of rotation of the associated planetary center plane and in at least one point with the inner peripheral surface of the ring gear in frictional contact, and the planetary mantle surfaces are shaped such that the planetary gears are held axially by the Reibberamung with the sun gears and the ring gear, a planet carrier is not mandatory.
- a sun gear is rigidly connected to a shaft and the other sun gear is rotatably mounted on the shaft and biased in the direction of a sun gear, whereby the necessary for a friction contact pressure is supported.
- the planetary lateral surfaces can taper to the end faces of the planet gears and the sun shell surfaces can taper towards the mutually facing end faces of the sun gears.
- the planetary lateral surfaces can taper in the direction away from the end faces of the planetary gears and the sun shell surfaces can taper to the opposite end faces of the sun gears.
- the planetary mantle surfaces between two lateral surfaces areas for a Reibberamung, each with a sun shell surface arranged mean lateral surface area for a Reibberamung with the inner peripheral surface of the ring gear, whereby the contact force necessary for the friction contact acts uniformly on the planetary gears.
- the middle lateral surface area is formed as a circumferential groove and the convex contour formed inner peripheral surface of the ring gear with each edge of the groove is in frictional contact, tilting of the planet gears for changing the ratio between the drive and output is particularly simplified.
- the planetary gears in the tilted state of the planetary gears intersect a line through the two points of Reibberamung the inner peripheral surface of the ring gear with the flanks of the groove, the axes of rotation of the planetary gears and the axis of rotation of the sun gears in one point, whereby the axis of rotation of the planetary gears undergoes a precession in oblique position.
- the planetary gears are held by a separator in substantially the same circumferential distance from each other, the planetary gear is stabilized.
- the planetary gear advantageously has a device for axially displacing the ring gear relative to the sun gears.
- the sun shell surfaces, the planetary lateral surfaces and the inner peripheral surface are shaped such that the distance between the sun gears does not change or only minimally increases upon tilting of the axis of rotation of the planet gears relative to the axis of rotation of the sun gears.
- the necessary for a friction transmission contact pressure is supported.
- the planetary gear has a tendency to automatically return to the ratio one, in which the axes of rotation are parallel to each other.
- the contours of the sun shell surfaces, the planetary shell surfaces and the inner peripheral surface are shaped such that when torque is transmitted from one sun gear to the other, the planetary gears a the contact pressure between the surfaces in frictional reinforcing Tiltmoment acts, whereby the necessary for a friction contact pressure without the addition of components such as hydraulic pressure piston is generated.
- Suitable materials include not only conventional steels but also special steels, tool steels or ceramic materials, as well as composite materials from which at least some of the components or their upper or effective surfaces can exist. In general, all materials with increased hardness and / or wear resistance are advantageous.
- FIG. 1 shows a side view of a planetary gear according to a first embodiment
- FIG. 2 is a sectional view, not to scale, of the planetary gear of FIG. 1 along the line A-A;
- Fig. 3 is an enlarged view of a planetary gear of the planetary gear of Fig. 1;
- Fig. 4 shows schematically the two sun gears, the ring gear and a planetary gear of the planetary gear drive of Figure 1, wherein the planet gear is tilted.
- Fig. 5 shows schematically the two sun gears, the ring gear and a planetary gear of the planetary gear drive of Figure 1, wherein the planet gear is tilted.
- Fig. 6 shows schematically a sun gear, a part of the ring gear and a planetary gear of the plane tengetriebes of Figure 1, wherein the planet gear is tilted.
- Fig. 7 shows schematically another possible embodiment of the essential components of the planetary gear, wherein the planet gear is tilted
- Fig. 8 shows schematically another possible embodiment of the essential components of the planetary gear, wherein the planet gear is tilted
- Fig. 9 shows schematically another possible embodiment of the essential components of the planetary gear, wherein the planetary gear is tilted.
- a planetary gear 10 with continuously variable transmission two sun gears 12a, 12b, three planet gears 14 and a ring gear 16.
- the sun gears 12a, 12b taper towards their mutually facing end sides, so that their sun shell surfaces 18a, 18b are circular-frustoconical.
- the contour line of the sun shell surfaces 18a, 18b is rectilinear in the illustrated example.
- the sun gears 12a, 12b are arranged axially spaced on a shaft 20 with a rotation axis 22.
- a sun gear 12 a is axially displaceable relative to the shaft 20 and rotatable relative to the shaft 20 by means of a bearing 24, for example a ball bearing.
- the other sun gear 12b is rigidly connected to the shaft 20.
- the side of the planetary gear 10 with the sun gear 12a rotatable relative to the shaft 20 is, for example, the drive side.
- the side of the planetary gear 10 with the sun gear 12b, which is rigidly connected to the shaft 20, is the output side.
- a spring 26 is supported between the sun gear 12a and a lug 28 of the shaft 20 and elastically biases the sun gear 12a in the axial direction to the sun gear 12b.
- the planet gears 14 each have an axis of rotation 30 and taper, starting from a central region towards their end faces, so that their planetary lateral surfaces 32 are substantially circular frustum-shaped. In the example shown, the contour lines of the planetary lateral surfaces 32 are convexly curved.
- the planet gears 14 have between the planetary lateral surfaces 32 on a circumferential groove 34 with rounded edges 36.
- the planetary gears 14 are arranged coaxially with the shaft 20 and each with one of its planetary lateral surfaces 32 in frictional contact with one of the sun shell surfaces 18a, 18b.
- the planetary gear 10 has a rotatably mounted on the shaft 20 star-shaped separator element 38 which is formed with lugs 40, the wheels in spaces between the planet 14 and project into the groove 34, so that the planet gears 14 are held at the same circumferential distance from each other ,
- the ring gear 16 advantageously has an annular shape and is formed on its inner peripheral surface 42 with a convex, convex, arcuate bead.
- the ring gear 16 is arranged concentrically with the shaft 20.
- the inner circumferential surface 42 is in frictional contact with each flank 36 of the groove 34.
- the planet gears 14 are held by the Reibberamung the planetary surface 32 with the sun shell surfaces 18 a, 18 b and the inner peripheral surface 42 axially.
- the planetary surface 32, the groove 34 and the inner peripheral surface 42 are advantageously shaped so that in the tilted state, the axes of rotation 30, the axis of rotation 22 and lines the two points of frictional contact of the inner circumferential surface 42 with the flanks 36 of the groove 34 intersect at one point (see Fig. 4). This leads to a well-defined precession of the planet gears 14.
- a displacement device 44 which is shown only in Fig. 2, arranged around the ring gear 16.
- the displacement device 44 is formed similar to a clutch operation and will therefore not be explained in detail.
- Fig. 3 shows for better understanding a planetary gear, as used in the planetary gear of FIGS. 1 and 2, in an enlarged view.
- rsi is the distance between the axis of rotation 20 and the point of Reibberamung the sun shell surface 18a with the planetary surface 32;
- rs2 is the distance between the axis of rotation 20 and the point of frictional contact of the sun shell surface 18b with the planetary surface 32;
- rpi is the distance between the axis of rotation 30 and the point of frictional contact of the planetary surface 32 with the sun shell surface 18a;
- rp2 is the distance between the axis of rotation 30 and the point of frictional contact of the planetary lateral surface 32 with the sunshield surface 18b;
- nsi is the speed of the sun gear 12a
- ns2 is the rotational speed of the sun gear 12b
- np is the rotational speed of the planet gears 14;
- ⁇ S is the axial distance of the sun gears 12a, 12b from each other.
- the planet gears 14 With an axial displacement of the ring gear 16 relative to the sun gears 12a, 12b, the planet gears 14 are taken along the flanks 36 of the grooves 34 and the axes of rotation 30 of the planet wheels 14 tilted relative to the axis of rotation 20 of the sun gears 12a, 12b. If, as can be seen in FIG. 4, the axis of rotation 30 is tilted towards the sun gear 12a, then rsi> r ⁇ 2 and rpi ⁇ rp2, i. nsi ⁇ ns2- If the axis of rotation 30 is tilted towards the sun gear 12b, the above-mentioned relationships change correspondingly inversely. The translation between nsi and ns2 thus changes according to the axial displacement. In this case, the translations between the ring gear 16 and each of the sun gears 12a, 12b change in opposite directions.
- the conical surface areas may be formed such that the distance .DELTA.S (FIG. 5) between the end faces of the sun gears 12a, 12b when tilting the axes of rotation 30 of the planet gears 14, i. with an adjustment of the translation, remains constant. A contact pressure between the sun gears 12a, 12b, the planetary gears 14 and the ring gear 16 is ensured by the spring 26.
- the contact pressure increases with increasing torque transmitted by the planetary gear 10, ie the planetary gear 10 is in some way self-pressing.
- the spring 26 could be omitted in this case, when the sun gears 12a, 12b are held axially relative to each other.
- the planetary gear according to the invention can be varied in many ways:
- the sun gears can be different in size.
- the contours of the lateral surfaces can be concave, convex or rectilinear in mutual agreement.
- the inner peripheral surface of the ring gear may be in frictional contact with the planetary peripheral surfaces at only one point.
- a planet, whose webs penetrate the planetary gears can be arranged so that at this another gear can be tapped.
- the spring 26 may be replaced by other biasing means.
- FIGS. 7 to 9 Further possible embodiments of the planetary gear are shown in FIGS. 7 to 9.
- Fig. 7 shows an embodiment in which the sun gears 12a, 12b are formed and arranged similarly to Figs.
- the planet gears 14 have a similar shape as the planet gears 14 in Figs. 1-4, but are formed without a groove.
- the ring gear 16 has on its inner circumferential surface 42 two convex inner circumferential surfaces forming a total of the flanks of a groove, which are each in frictional contact with one of the planetary lateral surfaces 32.
- Fig. 8 shows another embodiment in which the sun gears 12a, 12b are formed and arranged similarly to Figs. 1-4.
- the planet gears 14 taper towards their end faces, so that the planetary lateral surfaces 32 are substantially circular and have convexly curved contours. In a central region, the planetary lateral surfaces 32 have a smaller radius of curvature than at the side regions.
- the Ring gear 16 has on its inner peripheral surface 42 has a substantially concave cross-section, the radius of curvature advantageously slightly larger than the radius of curvature of the central region of the planetary surface 32, so that the inner peripheral surface 42 contacts the central region of the planetary surface 32 at one point.
- the planetary skirt surfaces 32 may alternatively comprise two parallel circumferential beads near the central region such that the inner peripheral surface 42 contacts the planetary lateral surfaces 32 at two points.
- FIG. 9 shows a further embodiment in which the axially narrow-shaped sun shell surfaces 18a, 18b are circular-frustoconical and have concavely curved contours.
- the sun gears 12a, 12b are arranged on their own, mutually equiaxial waves 46 so that the tapered end face facing away from the respective other sun gear 12a, 12b.
- the planetary lateral surfaces 32 are formed without embnut or-bead and have a concave contour.
- the inner circumferential surface 42 of the ring gear 16 is formed with two concave side portions, which are connected via a straight, axially parallel portion. Each concave side region of the inner circumferential surface 42 is in frictional contact with the conical surfaces of the planetary gears 14.
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112007002121T DE112007002121A5 (de) | 2006-09-28 | 2007-09-06 | Planetengetriebe mit kontinuierlich veränderbarer Übersetzung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006045854.0 | 2006-09-28 | ||
DE102006045854 | 2006-09-28 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008040281A1 true WO2008040281A1 (de) | 2008-04-10 |
Family
ID=38915610
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2007/001609 WO2008040281A1 (de) | 2006-09-28 | 2007-09-06 | Planetengetriebe mit kontinuierlich veränderbarer übersetzung |
Country Status (3)
Country | Link |
---|---|
US (1) | US20080090693A1 (de) |
DE (1) | DE112007002121A5 (de) |
WO (1) | WO2008040281A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3187751A1 (de) * | 2015-12-30 | 2017-07-05 | Wolfgang Rodi | Stufenloses planetengetriebe |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH265617A (de) * | 1941-06-30 | 1949-12-15 | Falk Corp | Stufenlos regelbares Getriebe. |
JPS63251656A (ja) * | 1987-04-08 | 1988-10-19 | Kazuichi Ito | 自動変速機 |
JPH02212651A (ja) * | 1989-02-10 | 1990-08-23 | Kazuichi Ito | 変速装置 |
-
2007
- 2007-09-06 DE DE112007002121T patent/DE112007002121A5/de not_active Withdrawn
- 2007-09-06 WO PCT/DE2007/001609 patent/WO2008040281A1/de active Application Filing
- 2007-09-28 US US11/906,145 patent/US20080090693A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH265617A (de) * | 1941-06-30 | 1949-12-15 | Falk Corp | Stufenlos regelbares Getriebe. |
JPS63251656A (ja) * | 1987-04-08 | 1988-10-19 | Kazuichi Ito | 自動変速機 |
JPH02212651A (ja) * | 1989-02-10 | 1990-08-23 | Kazuichi Ito | 変速装置 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3187751A1 (de) * | 2015-12-30 | 2017-07-05 | Wolfgang Rodi | Stufenloses planetengetriebe |
WO2017114691A1 (de) * | 2015-12-30 | 2017-07-06 | Wolfgang Rodi | Stufenloses planetengetriebe |
CN108431456A (zh) * | 2015-12-30 | 2018-08-21 | 罗列斯有限公司 | 无级行星变速器 |
US10876609B2 (en) | 2015-12-30 | 2020-12-29 | Rolless Gmbh | Continuously-variable planetary transmission |
CN108431456B (zh) * | 2015-12-30 | 2021-08-10 | 罗列斯有限公司 | 无级行星变速器 |
Also Published As
Publication number | Publication date |
---|---|
DE112007002121A5 (de) | 2009-06-10 |
US20080090693A1 (en) | 2008-04-17 |
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