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WO1990014532A1 - Transmission a billes - Google Patents

Transmission a billes Download PDF

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Publication number
WO1990014532A1
WO1990014532A1 PCT/EP1990/000802 EP9000802W WO9014532A1 WO 1990014532 A1 WO1990014532 A1 WO 1990014532A1 EP 9000802 W EP9000802 W EP 9000802W WO 9014532 A1 WO9014532 A1 WO 9014532A1
Authority
WO
WIPO (PCT)
Prior art keywords
balls
power transmission
ball
transmission according
radial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP1990/000802
Other languages
German (de)
English (en)
Inventor
Dieter Bollmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO1990014532A1 publication Critical patent/WO1990014532A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
    • F16H2025/063—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members the intermediate members being balls engaging on opposite cam discs

Definitions

  • the invention relates to a transmission of the type described in the preamble of claim 1.
  • the eccentric In a known transmission of this type (cyclo-transmission), the eccentric is provided with a number of drivers which engage in two disks provided with an edge toothing, which in turn interact with a ring provided with an internal toothing in such a way that the disk with the ring constantly are in engagement with each other on part of their circumference, so that on the one hand and the ring on the other hand a force or force due to the different number of teeth of the disks.
  • Path translation e follows.
  • the known gears allow a large power transmission due to the toothing, which is closely approximated to a wave, they make it possible to change the gear ratio. Reduction only within relatively narrow limits and are therefore primarily suitable as reductions for slow-running drives.
  • Ball roller tracks are subject to the same restrictions as e gear transmission, in particular the dependency of the selectable reduction ratio on a module - determined by the scope of the cycloid pitch circle - with the result that a selection of the reduction ratios is only possible - sometimes broken - jumps .
  • Another part of the known gearbox is caused by the cycloid shape d ball guideways, which each retard the circumferential ball when approaching a cycloid tip and - after reaching the cycloid tip - re-acceleration in the new curve path that was at an acute angle z previous movement direction.
  • the present invention has for its object to provide a Ge gearbox, the free choice of sub- or under wide limits with simple design and low wear. Translation ratio allowed.
  • the force transmission takes place by means of balls, with the guidance of the balls in a fre
  • the Kugelkraftge gearboxes according to the invention can be produced with any translation and reduction ratio, which can be chosen freely and without dependence on a given module. Reductions of less than 9: 1 are possible, which cannot be achieved with the help of conventional gear drives.
  • standard balls can be used, whereby the housing-side and output-side guideways can be manufactured by simple machining processes. The manufacturing effort is therefore low.
  • the transmission allows the transmission of large forces in view of the fact that all balls used are constantly in a force-transmitting engagement at the same time.
  • Fig. 1 shows a longitudinal section through a ball power transmission according to the invention
  • FIG. 2 shows a view from the left on FIG. 1
  • FIG. 3 shows a view from the inside of the drive-side housing wall d in FIG. 1.
  • Fig. 4 shows a longitudinal section through the drive part of an embodiment form of a multi-stage. multi-speed gearbox
  • Fig. 5 is a view from the right on FIG. 4
  • Fig. 6 shows a longitudinal section through the driven part of the transmission shown in FIGS. 5
  • Fig. 7 shows a longitudinal section through another embodiment of a multi-stage or multi-speed gearbox
  • Fig. 9 shows a ball race combination with an explanation of its calculation
  • Fig. 13 shows a section through a ball power transmission with ball-bearing power transmission balls.
  • Fig. 14 is a partial view of the ball ring of FIG. 8
  • Fig. 15 shows a section through a spherical power transmission with power transmission balls which are separate on the drive and output side and are mounted in a slide piece.
  • FIG. 16 shows a partial section through a slider which can be used in conjunction with the spherical power transmission according to FIG. 10 and has ball-supported power transmission balls.
  • FIG. 17 shows a partial section through a slide piece which can be used in conjunction with the spherical power transmission according to FIG. 10 and has ball-supported power transmission balls
  • Fig. 18 is a view of a slider
  • FIG. 19 is a side view of FIG. 14
  • FIG. 21 is a side view of FIG. 16
  • FIG. 22 is a top view of FIG. 16
  • FIG. 24 shows the view of another embodiment of a radial slotted disc 25 shows a section through a reduction gear with ball-supported force transmission balls.
  • a single-stage ball power transmission consists of a bearing in a housing 2a, 2b from the drive part 3 and a drive part 1 with an arranged thereon, surrounded by a bearing 5 for the force transmission elements eccentric.
  • the bearing 5 surrounding balls 6 are provided which are held by a freely rotatable bearing ring 7 in contact with the bearing.
  • the balls 6 are guided on the one hand in fixed radial ball guide grooves 10 formed in the housing and on the other hand in a shaft track 11a, 11b formed in the output part 3, the number of balls and corresponding radial guide grooves 10 relating to the number of corrugations of the shaft track 11 in the ratio between n : (n - 2) and n: (n + 2) stands.
  • the simplicity of the structural design of the gearbox can be readily recognized insofar as commercially available parts can be used for the balls and ball bearings used and the gearbox otherwise consists of simply designed elements which do not require complex machining.
  • S - as shown in FIG. 3 of the drawing - the radial guide groove can be produced by simply milling or grinding a continuous groove in a correspondingly stepped cover part, the ball bearings 5 and bearing ring 7 not serving for power transmission but only for guiding the ball 6 can be designed as a simple flat ring, ie the introduction of a guideway corresponding to the Kugelwölbu is not required.
  • Such a transmission can be used, for example, to transmit very large forces and or be used when the installation conditions require a particularly flat design.
  • the concentrically running corrugated ball guideways 11a, 11b can also be arranged in separate output parts 3a, 3b - see FIG. 6, in which case the power transmission lines also have different shapes, i.e. may have a different number of corrugations in the corrugated ball guide tracks and a different number of radial ball guide grooves in the two force transmission lines with a correspondingly different number of balls.
  • Such a gearbox is a multi-stage gearbox which can be designed as a gearbox with permanently assigned drives or as a gearbox, in which an output shaft is optionally coupled to one or the other output by means of a coupling and the non-coupled outputs are idle.
  • FIG. 7 Another embodiment of a manual transmission according to the invention is shown in FIG. 7.
  • the driven part of the downstream gear stage is mounted concentrically on the output shaft 21 of the upstream gear stage in such a way that with its annular shoulder 24 carrying the shaft path 23, it lies opposite an annular shoulder 28 formed in the housing 25, 26, which has an annular gap 29 with the downstream output part includes.
  • this embodiment is particularly suitable for the production of gearboxes with very large gear ratios, with - as a particular advantage - a power tap optionally being possible in each of the stages, so that the gearbox can also be used as a manual gearbox Manufacturing multi-stage or Multi-speed transmission in the manner described further output parts can be arranged after the last output part.
  • Fig. 7 of the drawing another particularly advantageous embodiment of a transmission according to the invention is shown in such a way that, instead of the radial ball guide grooves 27 used in the downstream power transmission line, a further wave track 36 is provided in the upstream power transmission line.
  • a ball power transmission has been created in which the balls are in two continuous, i.e. no sudden change in the direction of the ball causing and freely selectable, i.e. guided by the (mathematical) sinusoidal cycloid shape independent wave paths.
  • the reduction ratio can be freely selected in whole and half multiples, whereby optionally - advantageous for high-speed drives - a flat, i.e.
  • the inertial rings 37, 40 are advantageously provided with long slot guides 38, 39 which comprise the balls and which di balls without interference of the function-related slight pendulum u and their engagement position in a predetermined (middle) keep each other away and take them in the desired uniform direction of rotation.
  • Single-stage gear units can optionally be provided with a radial groove guide or with a double shaft groove guide.
  • multi-stage or multi-speed gearbox according to FIGS. 4 or 7 in the individual stage can be provided uniformly or differently with a radial groove guide or with a shaft groove guide in the housing.
  • the middle rolling circle with 41, the six-wave wave track with 42 and the four-wave wave track with 43 bezeic net.
  • the six-shaft shaft 42 in the housing and d four-shaft shaft 43 in the driven pulley there is a reduction ratio of 1: 2, with a reverse arrangement a reduction ratio of 1: 3.
  • the balls are arranged at the points where the two shaft paths 42, 43 and the rolling circle 41 have a common intersection. Denote in the equation representing the basis of the curve calculation
  • rx radius distance of a point of the wave center line from the axis of rotation
  • e eccentricity
  • Phix arc angle on the wave center line
  • ZI number of corrugations of the one wave or Z2 - number of corrugations of the other or.
  • Number of radial grooves rs radius distance of the eccentric in the point specified by rx.
  • FIGS. 13 to 25 further developments of the embodiments of a ball power transmission shown in FIGS. 1 to 1 are shown, in which, in contrast to the gears described above, power transmission has separate sets of balls between the drive unit and the fixed part - housing or radial slot - ben - on the one hand and between the drive part or the radial slide disc and the driven part are provided on the other hand, which are freely rotatably mounted on a spherical ring.
  • FIGS. 13 and 14 of the drawing show an essential gear corresponding to FIG. 1, in which the force from the drive part 41 provided with an eccentric disk 61 is exerted on the fixed housing 44 by means of two sets of balls 64, 65 on the driven part 51 is transmitted, which are freely rotatably mounted on two rows of balls 66, 67, such that each of the balls 66, 67 used for power transmission is supported on four balls of the two rows of balls 64, 65.
  • the support balls in turn are caught in an inertial ring 62, of which in particular the inner ring 63 instead of v
  • the power transmission takes place in a manner different from the embodiment shown in FIGS. 1 to 14 an axially acting inertial ring 68 mounted on the eccentric via a ball bearing instead of the radially acting inertial ring according to FIG. 14.
  • the power transmission also takes place via two sets of balls for the output part 51, in which case, in this case, a gear with an axially acting inertial ring, the balls are arranged individually or in pairs in sliders, which are slidably mounted in radial slots of a housing-fixed guide disk.
  • FIG. 15 which represents a simplified embodiment of the invention
  • the balls 55 serving for power transmission are mounted directly and without ball support in the slide pieces 57 and the slide piece in radial slots 58 of a disk 59 fixed to the housing, where additionally in FIGS. 16 to 22 different variants of slider with ball support systems and in FIGS. 23 and 24 two further execution forms of housing-fixed guide disks are shown.
  • FIG. 16 shows an embodiment of a slide 70, in which the balls 71, 72 serving for power transmission are each supported by a ball ring 73, 74 supported by ball guideways 75, in the embodiment shown in FIG. 17 the balls 76, 77 serving for power transmission are supported in pairs on a common ball ring.
  • the support balls 78 are guided in a ball guide 79 - see FIGS. 18 and 19 - of the slider 70, which is also provided with outer slideways 80 with which it engages around the edges of the slot 58 of the disk 59 - FIG. 15 fixed to the housing , in which under the effect of the force of the drive part 41 depending on d eccentricity of the eccentric 61 radially inward. slides on the outside.
  • the slide 81 shown in FIGS. 20 to 22 differ from the slide n shown in FIGS. 16 to 19 in that both variants shown in FIGS. 16 and 17 are combined into one slide. Sliders of this type can be used, for example, to increase the power transmission or to build up step transmissions according to FIG.
  • the sliders can be used in connection with any guide disk, for example d
  • the sliders can be formed in two parts and the parts can be screwed together after insertion in the radial lock.
  • Fig. 25 a step transmission using a double sliding piece according to Fig. 20 to 22 of the drawing, wherein the balls 91, 92, 93 in the inertial ring 68, which are guided in grooves in the housing 44 and in the driven part each serve to transmit power while the umla fenden only on the surface of the inertial ring 68, ie Do not perform balls 94 ledigli supporting function in ball guideways.
  • the guide disk 83 is rotatably guided in the middle of a ball bearing 84, so that the guide disk 83 d can follow predetermined rotary movements through the waveguide-guided balls 91, 92.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Friction Gearing (AREA)
  • Retarders (AREA)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

Transmission à billes comportant une partie de sortie (3) logée dans un carter ainsi qu'une partie d'entrée (1) au niveau de laquelle est disposé un excentrique (1a) entouré d'un coussinet (5) pour les éléments de transmission de puissance. Les billes (6) servant à la transmission de puissance sont maintenues, à l'aide d'une bague à inertie (7) guidée librement en rotation, en contact de transmission de puissance avec le coussinet (5) et sont en outre guidées dans les guidages prévus à cet effet d'une part directement dans le carter (2a) ainsi que d'autre part dans la partie de sortie (3). Certains de ces guidages sont formés soit de rainures de guidage radiales (10) soit d'une rainure cannelée continue et d'autres d'une glissière cannelée continue (11), le nombre de cannelures étant différent du nombre des rainures radiales (10) et du nombre de cannelures de la première glissière cannelée, et le nombre des billes correspond au nombre des rainures de guidage radiales (10) et au nombre des points d'intersection des deux glissières cannelées avec le cercle primitif. Dans une transmission avec guidage des billes (6) transmettant la puissance, d'un seul côté et dans des rainures radiales (10), le rapport entre le nombre des billes (6) et donc des rainures de guidage radiales (10) et le nombre des cannelures de la glissière cannelée (11) est compris entre n:(n-2) et n:(n+2), tandis que dans une transmission avec guidage des billes (6) des deux côtés dans des glissières cannelées (11), le rapport entre le nombre des billes (6) et donc des cannelures dans une glissière cannelée et le nombre des cannelures de l'autre glissière (11) est égal à au moins n:(n +/- 2).
PCT/EP1990/000802 1989-05-18 1990-05-18 Transmission a billes Ceased WO1990014532A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DEP3916108.0 1989-05-18
DE3916108 1989-05-18
DEP3920317.4 1989-06-21
DE19893920317 DE3920317A1 (de) 1989-05-18 1989-06-21 Kugelkraftgetriebe

Publications (1)

Publication Number Publication Date
WO1990014532A1 true WO1990014532A1 (fr) 1990-11-29

Family

ID=25880978

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1990/000802 Ceased WO1990014532A1 (fr) 1989-05-18 1990-05-18 Transmission a billes

Country Status (6)

Country Link
EP (1) EP0425657A1 (fr)
JP (1) JPH04500714A (fr)
AU (1) AU5810790A (fr)
CA (1) CA2033061A1 (fr)
DE (1) DE3920317A1 (fr)
WO (1) WO1990014532A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0492760A1 (fr) * 1990-12-27 1992-07-01 Kamoseiko Kabushiki Kaisha Dispositif réducteur de vitesse

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19757845B4 (de) * 1997-12-24 2006-12-14 Dieter Bollmann Kugelkraftgetriebe
DE102006006003A1 (de) 2006-02-08 2007-08-09 Auma Riester Gmbh & Co. Kg Überlagerungsgetriebe
JP6767244B2 (ja) * 2016-11-17 2020-10-14 株式会社エンプラス ボール減速機
JP2018115715A (ja) * 2017-01-19 2018-07-26 株式会社エンプラス ボール減速機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0090214A1 (fr) * 1982-03-26 1983-10-05 Advanced Energy Concepts '81 Ltd. Transmission épicycloidale ayant des éléments entraînant des rouleaux roulant librement
JPS60146954A (ja) * 1983-12-30 1985-08-02 Sanwa Tekki Corp ギアレス変速装置
EP0207206A2 (fr) * 1985-06-27 1987-01-07 Kamoseiko Kabushiki Kaisha Réducteur de vitesse sans engrenage

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1359655A (en) * 1970-08-01 1974-07-10 Leeson P G Speed changing mechanisms
US4643047A (en) * 1981-10-20 1987-02-17 Advanced Energy Concepts '81 Ltd. Speed reducing gearing mechanism employing trochoidally formed gear surfaces for rolling torque transmission
EP0107485A1 (fr) * 1982-10-22 1984-05-02 Quadrant Drive Bv Dispositif de transmission de mouvement

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0090214A1 (fr) * 1982-03-26 1983-10-05 Advanced Energy Concepts '81 Ltd. Transmission épicycloidale ayant des éléments entraînant des rouleaux roulant librement
JPS60146954A (ja) * 1983-12-30 1985-08-02 Sanwa Tekki Corp ギアレス変速装置
EP0207206A2 (fr) * 1985-06-27 1987-01-07 Kamoseiko Kabushiki Kaisha Réducteur de vitesse sans engrenage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 311 (M-436)(2034) 07 Dezember 1985, & JP-A-60 146954 (SANWA TETSUKI) 02 August 1985, siehe das ganze Dokument (in der Anmeldung erwähnt) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0492760A1 (fr) * 1990-12-27 1992-07-01 Kamoseiko Kabushiki Kaisha Dispositif réducteur de vitesse

Also Published As

Publication number Publication date
EP0425657A1 (fr) 1991-05-08
DE3920317A1 (de) 1990-11-22
CA2033061A1 (fr) 1990-11-19
JPH04500714A (ja) 1992-02-06
AU5810790A (en) 1990-12-18

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