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
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
  • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
• • 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 present invention has no role model since the invention of the gear transmission, which is likely to be displaced in the near future by the transmission according to the invention from wide areas of technology. It is based on the task of creating a transmission, which is compared to the conventional gear transmissions, including the b known harmonic drive gear and cyclo subsidence another Ov 'and in particular the reduction area BEZW. the transmission of larger forces.
• FIG. 1 shows a view of a transmission according to the invention.
• FIG. 2 shows a section according to II - II through FIG. 1
• FIG. 6 shows another embodiment of a manual transmission in section.
• FIG. 7 shows a section according to VII - VII through FIG. 6.
• FIG. 8 shows a section according to VIII - VIII through FIG. 6
• FIG. 9 shows another embodiment of a manual transmission in Schn.
• FIG. 10 shows a schematic illustration of an angular drive in Schn.
• FIG. 11 shows a transmission with a different design of the drive disk.
• FIG. 12 shows a further development of the transmission shown in FIG. 11 with simultaneous kinematic reversal of the Functional part Fig. 13 Examples of the formation of the shaft grooves of the embodiments of a gear shown in F 11 and 12.
• Fig. 14 shows another embodiment of an axial gear with a direct drive
• FIG. 15 is an exploded view of the transmission of FIG. 14 in 16 shows an exploded view corresponding to FIG. 15 of a transmission with a kinematically reversed arrangement of the parts.
• FIG. 17 shows a modification of the transmission shown in FIG. 12
• FIGS. 1, 6, 11 and 14 of the drawing are transmissions with mutually aligned drive or Output rotation axes with - see in particular FIGS. 1 and 2 - a housing 1 in which d the drive part having the shape of an essentially annular disc 2 and the drive part also having the shape of an annular disc 3 are mounted.
• the balls 11 used for power transmission a housing-fixed flange 6 is provided between the drive plate 2 and the driven plate 3, which with a basically any number A radial, the eccentric deflection of the ball guide groove 9 d drive plate 2 overlapping slot guides 10 is provided, the help of which the balls 11 are secured against rotation about the central axis of the transmission.
• the transmission can thus - based on the Transmission equal torques - can be built much smaller than the conventional gear transmission, in which the power transmission takes place via only a few teeth that are in mesh with each other.
• the gearboxes according to the invention in comparison with conventional gearboxes of a comparable installation size - allow the transmission of substantially larger torques, which are basically unlimited. If a force transmission line (eccentric groove-slot-guided ball set shaft track) is not sufficient for the forces required for transmission, only the arrangement is required another power transmission line or several power transmission lines of the same division in the same - possibly correspondingly larger - drive or Output parts.
• a force transmission line eccentric groove-slot-guided ball set shaft track
• the gearbox is simple to manufacture, which is limited to the milling of the ball guide grooves and slot guides for Einsa commercially available and therefore inexpensive balls, which - unlike the toughness of gear drives - do not require any special machining.
• Bet * "inevitable elaborations of the ball tracks can not Schwi culties be compensated by replacing the balls by balls a drafting m correspondingly larger diameter.
• the gearbox h also has a significantly longer service life than conventional gearboxes.
• the gear ratio of the gearbox can be freely selected as an integer ratio. His relationship to the number of - in a transmission line - balls 11 used on the one hand and waves in the shaft groove on the other hand is determined by the equation
• W is the number of corrugations in the output-side guide groove 14 and K is the - according to current knowledge at least between 1 and (W + 1 - number of force-transmitting balls or radial guide slots. This results from the constant force-transmitting Intervention of all balls used resulting special feature - D -
• the transmission is calculated in such a way that - for reduction gears - first by multiplying the length of the base circle - this is the length of the circle circumscribing the shaft groove 14 of the output part 3 - with the desired transmission ratio, the gear division, i.e. the length of a corrugation in the groove 1
• each gear ratio can be determined directly as an integer ratio, with the possibility of production of gears also m
• a straight-line zigzag shape 14a and a sharp-breaking wave shape 14b In Fig. 5B - preferred - guide grooves with regular waveforms 14c and 14d of different ripple speed are shown, which, with a further reduction in ripple i, the shape shown in Fig. 5C of a polygon 15a, 15b, 15c from three circular sections centered on the central axis or - go further - turns into an ellipse.
• the transmission can be designed as a single-stage or simply as a multi-stage transmission or - in different, fundamentally different embodiments - as a multi-speed manual transmission.
• Such a manual gearbox is the output of a number of gearboxes corresponding to the number of gearboxes of output disks 21, 22, 23, 24, 25 g which are rotationally coupled to one another by means of the balls, each of which, in relation to the output disk above in the drive assembly, has a shaft groove with a desired amount Have a reduction ratio of coordinated wavenumber.
• a hollow shaft 26 extends through the inner bores d driven disks and flanges 6, which cages for the planes of the driven disks - see in particular FIG.
• a drive part , 24a, 25a is formed in which, as a switching element, a cam slide 27 with cam beads 21b, 22b, 23b, 24b extending all around in stepped spacing is guided by the axial displacement of one of the driven disks - example case of the bead 24b with the output disk acting as a reverse gear 25 - is connected in a rotationally fixed manner to the hollow shaft 26 in such a way that d balls of the relevant ball set 25a are released into ball sockets 24c of the associated driven pulley 24 and released in this position and the balls of all other ball sets 21a, 22a, 23a, 24a are released.
• the A drive pulleys are supported in the example shown by a support bearing 28 in the housing 1, which is only required for transmissions to transmit larger forces, but can be dispensed with only a small force transmission bearing.
• a gear designed in this way is simple in construction allows a simple circuit by simply linear adjustment of a cam spool by hand or by program control. It e is particularly suitable for use in application cases in which the external conditions permit the installation of only an elongated, small-diameter gear.
• the gearbox can be designed as a multi-stage gearbox with any number of opposing direction force-transmitting gearboxes.
• the direct rotationally fixed coupling of any one is sufficient for this Number of output disks with each other with the interposition of a go fixed with radial guide slots for power transmission balls v see flange, the output disks each having an eccentric groove on their drive-side end face and a Wcllennut on their drive-side end face.
• the driven output disks 21, 22, 23, 24 u different transmission ratios - see also Fig. 8 - upstream of a reversing disk, each of which concentrates a ring disk 31, each with a concentr, to determine a direction of rotation
• Ball guide groove 32 formed in its two end faces and one side by means of an eccentric bearing from an eccentric disk 35 guided between ball rings 33, in the housing 1 and, on the other hand, means of the balls 11 via the flange 6 downstream of it, indirectly with d on its drive-side end face, a concentric ball guides 36 having subordinate driven pulley 22 and via a further ball set 37 directly with the upstream, on the output side gene end face with a concentric ball guide groove 38
• Output disk 21 are engaged in power transmission.
• the Reversie disc does not allow direct power to be used for drive purposes, however, it enables a reversal of the direction of rotation of the above driven disc in a ratio of 1: 1
• the cam slide 27 is designed as a shaft which is rotatably mounted in the hollow shaft 26 and is connected to a slide switch 41 by means of a rotary bearing which is fastened on a link axially guided in the hollow shaft.
• the hollow shaft 26 is provided with radially overlapping slot guides 44 and the link 43 is provided with a guide pin 45 projecting through the slot guide.
• the cam slide 27 rotates due to the connection with the guide pin n in the same way, without this having a reaction to the slide switch 41 in view of the connection via the rotary bearing 42
• the further gears are engaged by simply further axially shifting the slide switch 41, whereby, with simultaneous release of the ball power coupling 24a, 24b, the next ball power coupling 23a, 2 is engaged in the same manner as described, whereupon the shaft is driven with the reduction ratio specified by the driven pulley 23 becomes.
• the driven pulley 25 differs from the driven log. 21 to 24 only in that - as a reverse gear - no reversing disk is connected upstream.
• the individual output rings have a different reduction ratio compared to the common drive and can be coupled in a known manner to the driven unit, for example in a manner corresponding to the output according to FIG. 6, by means of a magnetic coupling or the like Regarding space requirements, gear ratio and power transmission around a gearbox of hard to estimate performance.
• the drive pulley 50 can be divided analogously to the driven parts 61, 62, 63, the resulting drive washers can be connected to the motor, for example, via an electromagnetically controlled cam slider.
• This embodiment is suitable for example for the production of automatic transmissions and has the further advantages that both the drive and the output side are always only one of the ring disks i circulation and the need for the connection of a clutch is eliminated, with the usual flywheel simultaneously being the on drive pulley of the transmission can be used.
• the gearbox according to the invention also allows the embodiment as an angle drive, for which purpose - see FIG. 10 - the output part from a ball head 75 having at least one rotatably mounted output pin 72 and with at least one endless ball guide groove 73 and di • ___ »15 drive disc from an annular disc 76 is formed, the inner opening of which corresponds to the contour of the spherical surface and ball sockets 77 for receiving at least one ball 78 guided in the ball guide groove 73 of the ball head 75.
• two ball guide grooves 73, 73a extend concentrically around the center of the ball head 75, 20 two synchronously coupled drive parts 76, 76a leading a corresponding number of balls 78.
• a ball guide groove extending eccentrically in the surface of the ball head can also be provided to create gearboxes with an output angle that deviates from a right angle.
• the guide groove 9 can - as in the case of that in FIGS. 1 to 9 again given embodiments - be worked directly into the drive pulley 2, which leads to excellent results, particularly for slow-speed drives.
• the guide groove for the ball 11 is advantageously arranged in a compensating ring 16, which is in the drive disk 2 on a compensating ring 16 in the axial direction, supporting it - see FIG. 11 Ball cage 17 is mounted. It is achieved in this way that although the radial movement of the balls i responsible for the power transmission takes place at a frequency corresponding to the speed of the drive, the rotation of the compensating ring 16 and thus the groove 9 itself is reduced on the drive side to the speed of the output.
• the compensating ring 16 in the embodiment shown in FIG. 11 can also have a shape similar to the ring 91 in FIG. 12, ie it may be provided with a shaft for guiding the force-transmitting balls 11 instead of a circular groove.
• the corrugations have both the shaft groove 96 of the compensating ring 91 and the shaft groove 97 of the flange having a pointed shape, the shaft groove 96 being curved and the shaft groove 97 being convex.
• a both shaft grooves have a concavely curved Fo corresponding to the shaft groove 96.
• a transmission with mutually aligned drive or. Is output axes see Figures 14 and 15, -.
• the output part of a wool 81 and ⁇ * .. driving part of a shaft 81 comprising sleeve 83 formed primarily the sleeve 83 on the shaft 81 facing surface with an endless obliquely across their
• the circumferentially extending guide groove 82 and the di shaft 81 are provided with an endless guide groove 84 made of curved sections for guiding the balls 85 used for power transmission and between the sleeve 83 and the shaft 81
• a sleeve 86 is provided which is fixed to the housing and which can have any number of axially parallel, the axial stroke height of the Ku gel Entrysnut 82 of the sleeve 81 covering
• Lan hole guides 87 provide »_-, with the help of which the balls 85 are secured against rotation about the axis of rotation of the gearbox.
• FIGS. 14 and 15 In the exploded view of the kinematic reversal of the transmission shown in FIGS. 14 and 15 forms in FIG Shaft part 81a, the drive part containing the oblique guide groove 82 and the sleeve 83a, the shaft part 84, the axial end drive part.
• FIG. 17 shows a modification of the guide guide according to FIG. 13, in which case two force transmission lines consisting of two oblique grooves 82, two shaft grooves and two sets of balls 85 with rows of slots 87 with the same part are provided to double the force-transmitting spherical cross section. In a corresponding manner, the number of power transmission lines can be increased as desired.
• the mode of operation of this embodiment corresponds to the mode of operation of the embodiment according to FIGS. 1 to 5, with the direct attraction of the shaft as a drive part for certain applications making it possible to achieve an even more compact design.
• Incidentally, can be produced in a corresponding manner to the embodiments described in FIGS. 11 to 17 - with analog application of the features described in connection with FIGS.

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

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

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ID=6345848

Family Applications (1)

Country Status (13)

Cited By (2)

Families Citing this family (7)

Citations (9)

Family Cites Families (4)

• 1988
  • 1988-11-21 ZA ZA888713A patent/ZA888713B/xx unknown
  • 1988-11-24 BR BR888807551A patent/BR8807551A/pt not_active IP Right Cessation
  • 1988-11-24 KR KR1019890701734A patent/KR900700796A/ko not_active Application Discontinuation
  • 1988-11-24 JP JP1500320A patent/JPH02503709A/ja not_active Expired - Lifetime
  • 1988-11-24 WO PCT/EP1988/001071 patent/WO1989007214A1/de not_active Application Discontinuation
  • 1988-11-24 AU AU28207/89A patent/AU2820789A/en not_active Abandoned
  • 1988-11-24 EP EP89900601A patent/EP0356467A1/de not_active Withdrawn
  • 1988-11-24 HU HU89477A patent/HUT55513A/hu unknown
  • 1988-12-24 CN CN88108872A patent/CN1036253A/zh active Pending
  • 1988-12-29 YU YU02380/88A patent/YU238088A/xx unknown
• 1989
  • 1989-01-20 PL PL27728489A patent/PL277284A1/xx unknown
  • 1989-09-05 DK DK440089A patent/DK440089A/da not_active Application Discontinuation
  • 1989-09-21 FI FI894468A patent/FI894468A/fi not_active IP Right Cessation

Patent Citations (9)

Non-Patent Citations (2)

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