WO1989009351A1 - Commande a cames - Google Patents

Commande a cames Download PDF

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Publication number
WO1989009351A1
WO1989009351A1 PCT/DE1989/000189 DE8900189W WO8909351A1 WO 1989009351 A1 WO1989009351 A1 WO 1989009351A1 DE 8900189 W DE8900189 W DE 8900189W WO 8909351 A1 WO8909351 A1 WO 8909351A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
shaft
gear
speed
output shaft
Prior art date
Application number
PCT/DE1989/000189
Other languages
German (de)
English (en)
Inventor
Peter Graf Von Ingelheim
Original Assignee
Peter Graf Von Ingelheim
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 Peter Graf Von Ingelheim filed Critical Peter Graf Von Ingelheim
Priority to DE19893924548 priority Critical patent/DE3924548A1/de
Publication of WO1989009351A1 publication Critical patent/WO1989009351A1/fr

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
    • F16H48/00—Differential gearings
    • F16H48/12—Differential gearings without gears having orbital motion
    • F16H48/14—Differential gearings without gears having orbital motion with cams
    • F16H48/147—Differential gearings without gears having orbital motion with cams with driven cam followers or balls engaging two opposite cams
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/10—Couplings with means for varying the angular relationship of two coaxial shafts during motion
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D5/00—Impulse couplings, i.e. couplings that alternately accelerate and decelerate the driven member
    • 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
    • F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
    • F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal or cams
    • 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the invention relates to a device for the positive transmission or conversion of forces and movements.
  • Such mechanical devices can be used as gears, clutches, differentials (differential) and brakes.
  • Positive gears for the transmission of uniform rotary movements are generally designed as toothed gears. Their disadvantages are the comparatively large installation space and certain basic conditions that apply to all previous gear transmissions.
  • Another possibility is to transmit forces and movements with the aid of cam mechanisms.
  • a disadvantage of this transmission is that the link on which the controlled force is applied is non-rotatably connected to the reciprocating lifting bodies and therefore rotates with them. Such a control can therefore only be implemented with great effort.
  • a second disadvantage of this transmission is that it does not make it possible to translate the torque.
  • the torque on the output shaft is always the same as the torque on the drive shaft.
  • a third transmission element would be necessary for torque transmission in order to be able to initiate a supporting torque Ms; see. the above equation (2).
  • the invention provides a remedy here. On the one hand, it enables a controlled application of force to non-rotating ones
  • gear elements which enables easy control.
  • the invention makes it possible to implement controllable transmissions with three torque shafts for real torque transmission.
  • These gears can be built both as conventional epicyclic gears, which can even be designed without play, and as epicyclic gears, which have a different main speed equation than conventional planetary gears, or can be used in gear-planet gears for speed control of the planet gear.
  • the transmission contains three coaxial or parallel-axis transmission elements, one of which is provided with axial slots, in which engagement members can be moved axially back and forth, and the engagement members act in such a way that (self-locking) transmissions which can be fixed in the power flow can be realized are and / or permit control of the torques transmitted by the transmission or change in the speed ratios of the transmission shafts.
  • FIG. 1 shows a transmission in perspective
  • FIG. 2 shows a clutch with recovery of the previous clutch losses due to springs
  • FIG. 3 shows the same coupling principle in a different embodiment
  • FIGS. 2 and 3 shows an arrangement with clutches according to FIGS. 2 and 3 to compensate for different speeds of the input and output shaft
  • FIG. 5 shows an arrangement which can be used as a clutch or gearbox and has a directed power flow
  • FIG. 6 shows a transmission circuit with a transmission according to FIG. 5
  • FIG. 8 another gear arrangement with the new main speed equation
  • FIG. 9 shows a gear arrangement for a controllable locking differential
  • FIG. 10 shows a gear arrangement for a continuously variable gear
  • FIG. 11 shows a gear arrangement for an actively controllable differential
  • FIG. 12 shows a gear arrangement for a starting clutch.
  • the two output shafts 1, 2 of the differential are provided with oppositely oscillating bead curves 3, 4 of the same number of phases.
  • the drive shaft 5 of the differential Around the two output shafts 1, 2 is the drive shaft 5 of the differential, which has a slot 6.
  • an engagement body 7 can be moved back and forth, which rolls with wheels 8 on the bead curves 3, 4 of the output shafts 1, 2.
  • the engaging body 7 remains stationary in the slot 6.
  • the two output shafts 1, 2 then have the rotational speed of the drive shaft 5. If one of the two output shafts has a greater torque than the other, it has the tendency to rotate more slowly.
  • the engaging body 7 is then moved back and forth in the slot 6 and thus rotates the shaft with the lower torque forward. It should be noted that if the engagement body 7 is guided without play in the slot 6 and the wheels 8 along the bead curves 3, 4, the transmission becomes free of play.
  • FIG. 2 shows the principle for a clutch according to the invention with recovery of the previous clutch losses.
  • the drive shaft 40 contains an oscillating groove 41 in which a ball 46 is located as the engagement body.
  • the output shaft 42 is coaxial with the drive shaft 40 and engages with a tube around it. In the tube there is a slot 43 in which the ball 46 can roll back and forth.
  • the tube 44 can be moved axially back and forth against the force of springs.
  • the spring force can be changed by axially adjusting adjustment rings 48 which are otherwise fixed to the housing.
  • FIG. 3 shows the same coupling principle with an input shaft 50, in which sinusoidal grooves 51 are formed, and an output shaft 52, which surrounds the input shaft 50.
  • the engagement body 53 is a ring with spikes 54 which engage in the grooves 51.
  • the engagement body 53 slides back and forth in a slot of the output shaft 52. Furthermore, it slidably engages with an annular bead 55 in an annular groove 56 of a third gear element 57.
  • This gear element 57 is supported by springs 49 with respect to a component that can be axially displaced in the housing 60 and engages with spikes 58 in axial grooves 59 in the housing 60; it is therefore only axially movable.
  • FIG. 3 is primarily used to understand the following gear arrangements.
  • Previous safety clutches slip clutches
  • the mechanical drive power Pan Man. nan.
  • the mechanical output power Pab -Man stands 2 ⁇ . nab. 2 ⁇ opposite.
  • the differential power Pan - Pab is converted into thermal energy in the coupling.
  • the previous "loss energy” is stored by springs 47 and 49, respectively, and is returned when the springs relax.
  • the power flow can be outlined as follows. If M is the average torque that is needed to compress the springs, then it acts as a brake on the input shaft and accelerates on the output shaft. When relaxing, it works the other way round. If the time for pressing together and relaxing were the same, no power could be transferred from the input shaft to the output shaft. If tl is the time for compressing and t2 is the time for relaxing the springs, then the pulse M acts on the output shaft. tl accelerating and M. t2 wide. The average torque Md acting on the output shaft during a sine phase is then calculated
  • This time difference can additionally be influenced positively by different steepnesses of the sinus curves for the compression and relaxation phase.
  • a flywheel with periodic change in the moment of inertia is shown in FIG. 4 as an energy store and explained further below.
  • FIG. 4 shows an application of the coupling according to the invention.
  • a number of auxiliary units are driven by the motor shaft (lubricating oil pump, alternator, auxiliary pumps, etc.). That is, even though they have to do their job at the lowest engine speed, their speed increases linearly with the engine speed. So they take up power that would not be necessary for their satisfactory work in the engine.
  • a centrifugal pump is used in conjunction with a coupling according to the invention, the lubricating oil pump could be made very small and economical.
  • the power consumption curve of a centrifugal pump increases exponentially with the pump speed. So far, it has not been suitable for an internal combustion engine with large differences in speed.
  • a flywheel 65 acts as an energy store, which is fixed to the pump shaft 64 and in which the masses 66 are moved radially inwards or outwards depending on the clutch or spring position, as a result of which the moment of inertia of the flywheel 65 is changed.
  • Figure 5 shows the principle of a transmission with directed power flow.
  • Such mechanical transmissions have so far only been known as worm gear transmissions and other high-ratio transmissions with self-locking.
  • This self-locking can be easily realized by different steepness (ratio of amplitude to phase length) of two sine curves. With the same wavelength range, sine curves with different number of phases and the same amplitude have different slopes.
  • With the gearbox according to the invention it is also possible to realize clutches (1: 1 ratios) with self-locking. This serves for safety and precision.
  • a sinusoidal groove 71 is formed on a large cylinder circumference. The steepness of this sine curve is therefore low.
  • a sinusoidal groove 73 is provided on the output shaft 72 on a small cylinder circumference. The steepness of this sine curve is great.
  • Engagement bodies 75 engage in the input and output shafts 70, 72, which can be moved back and forth in slots 77 in the housing 76 and bridge the difference in diameter.
  • the axial force on the engagement body 75 is a multiple of the peripheral force on the drive shaft 70.
  • the peripheral force is a multiple of the axial force.
  • the output shaft 72 is therefore rotated. In the opposite direction, no power flow is possible because the transmission stops due to friction.
  • Such a transmission can also be designed without play. It is therefore very well suited for precision drives (leaving a precisely approached position only through active adjustment).
  • Figure 6 shows the circuit of such a clutch in Connection with a hydraulic motor.
  • the transmission 81 of FIG. 5 is arranged between the hydraulic motor 80 and the working machine 82. Leakage losses of the hydraulic motor 80 and the compressibility of the hydraulic oil cannot lead to the shaft of the working machine 82 adjusting itself.
  • the drive shaft 90 has two single-phase sinusoidal grooves 91, 92 (oblique ring grooves) into which spikes 93 of an engagement body 94 engage.
  • the engagement body 94 slides in slots 95 of the output shaft 96.
  • An annular bead 97 can be rotated in an annular sleeve 98 of the third gear element, an annular sleeve 99.
  • the back and forth movement of the sleeve 99 at unequal speeds of the input and output shafts is used to drive a further shaft.
  • a wheel 101 is rotated at the speed ns via a crankshaft drive 100.
  • FIG. 8 shows a similar gear, in which the engagement body 115 engages in an oscillating groove 119 in the drive shaft 113. Furthermore, a sleeve 110 with spikes engages in an oscillating curve 111 in the housing 112. By reciprocating the engagement body 115 with relative rotation of the drive shaft 113 and the output shaft 114, the sleeve 110 is moved along in the oscillating curve 111 and therefore rotated. The sleeve 110 in turn engages with engagement bodies 116 in slots 117 of the support shaft 118 rotating at the speed ns. Thus, only the engagement body 115 and the sleeve 110 execute oscillating and rotating movements. The three shafts 113, 114, 118 of the transmission are exclusively rotated.
  • FIG. 9 shows the use of the transmission according to the invention for controlling a locking differential.
  • the drive shaft 121 of the differential which is driven by the cardan shaft 120, is connected to the drive shaft 122 of the transmission 123 according to the invention, and the one output shaft 124 of the differential is the output shaft of the transmission 123.
  • the support wheel 125 is stored in the housing 126. At the same speed of the input and output shafts 121, 122 of the differential, the support wheel 125 stands still. If the input and output shafts 121, 122 of the differential rotate relative to one another, the support wheel 125 also rotates. The support wheel speed and thus the relative rotation of the input and output shafts 121, 122 can be regulated via a brake or friction clutch .
  • FIG. 10 shows an arrangement for controlling the planet gear speed of a gear planet gear with the aid of the gear according to the invention. This is not possible with conventional transmissions or only with an unacceptable effort.
  • CVT transmission continuous) Variable transmission
  • FIG. 10 shows a concept for an adjusting gear according to the invention with a power split.
  • a four-wheel planetary gear 165 with two sun gear shafts 166, 167, two planet gears 168, 169 and a web 170 is used.
  • a pair of wheels 171 is mounted on the web 170, which is driven by the planet wheels 168, 169 and rotates with the web 170.
  • This pair of wheels 171 in turn can drive a sun gear 172 coaxial with the sun gear shafts 166, 167, ' which contains a slot 174 in its shaft 173, in which an engagement body 175 is axially displaceably mounted.
  • the web shaft 170 is axially elongated and contains an oscillating groove 176, in which the engagement body 175 engages with a mandrel 177. With an annular bead 178, the engaging body 175 also engages in an annular groove 179 of a ring 180 surrounding the three shafts 166, 170 and 173. The ring 180 in turn engages with an arbor 182 in an oscillating groove 183 in the housing 185 the ring 180 also in
  • the transmission ratio i can now be used instead of the construction ratio z, since the planet gears no longer have to reach an equilibrium state, but are controlled in a targeted manner by an additional torque.
  • the power flow through the hydrostatic transmission is low.
  • the power flow through the CVT transmission is low.
  • FIG. 11 shows a controllable differential for the targeted regulation of the speeds of the two output shafts.
  • a differential provides advantages over “controllable limited slip differentials", especially when cornering.
  • cornering an accelerating force vector from the road acts on the wheel on the inside of the curve. This reduces the torque on the two output shafts and the desired power can no longer be brought to the road.
  • a targeted speed control depending on the vehicle speed and the
  • Steering wheel lock can always bring the desired performance to the road even in curves. If the possibility of self-locking is taken into account when determining the differential, a different torque on the vehicle wheels cannot change the set speeds.
  • the propeller shaft 200 of the vehicle rotates the drive shaft 201 of the differential.
  • the slots 202 of this drive shaft 201 there are four engagement bodies, of which only the lower 203 and the upper 204 can be seen in FIG. 11, which engage with thorns in oscillating grooves 222, 223 of the two output shafts 207, 208.
  • the two further (not visible) engagement bodies are in the direction of view in front of or behind the output shafts 207, 208 and engage in further oscillating grooves 224, 22-5 in these.
  • the engagement bodies 203, 204 engage in annular grooves of sleeves 212, 213, while the two further engagement bodies, not visible in FIG. 11, engage in the sleeves 210, 211.
  • the sleeves 210 ... 213 are axially displaceable in axial slots 215 of the housing 216.
  • mandrels 218, 219 they also engage in oscillating grooves 220 of a control shaft 221 coaxially surrounding all shafts.
  • the control shaft 221 can be rotated by an adjustable hydraulic motor.
  • the differential works as follows. If the control shaft 221 is not rotated, the two output shafts 207, 208 of the differential have the same speed (the differential is locked). If the control shaft 221 is rotated in one direction, e.g. the right output shaft 208 faster than the left; if the control shaft 221 is rotated in the other direction, the left output shaft 207 rotates faster than the right. The speed differences of the two output shafts 207, 208 depend on the speed of rotation of the control shaft 221.
  • Figure 12 shows a clutch for torque-free starting of motors on work machines.
  • a high torque is often required to overcome the static friction of stationary machines necessary.
  • electric motors already require considerable energy to start up. This often results in high switching impulses.
  • Centrifugal clutches are known which produce the frictional connection between two shafts only from a certain engine speed. Such centrifugal clutches can only be used at high shaft speeds.
  • the transmission according to the invention according to FIG. 12 enables a starting clutch even for low shaft speeds.
  • the drive shaft 230 has an oscillating groove 231 in its circumference.
  • the output shaft 232 has axial slots 233 in which balls 234 can be moved back and forth as engagement bodies.
  • the third coaxial gear element is a ring 235 with a likewise oscillating groove 236, which lies around the input and output shaft 230, 232.
  • the balls 234 engage in the two grooves 231, 236.
  • the output shaft> 232 and the ring 235 are connected to one another via spring elements 237.
  • the clutch works as follows. In the start-up phase, when a high torque acts on the output shaft 232, the ring 235 rotates around the two shafts since it does not yet provide any support torque. Only when the springs 237 are tensioned to such an extent that the ring 235 and the output shaft 232 are connected with a sufficiently high positive connection is the output shaft 232 moved as well. Such a clutch therefore also enables a very smooth start-up, since the transmitted torque gradually increases (start-up ramp).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Transmission Devices (AREA)

Abstract

Le mécanisme décrit comporte un premier élément (40) possédant une première came (41) fermée oscillant axialement qui se déplace autour de l'axe dudit élément, un deuxième élément (42) coaxial au premier élément (40) et pourvu d'une rainure axiale (43), un trroisième élément (44) coaxial aux premier et deuxième éléments (40, 42) et présentant une deuxième came (45) qui se déplace autour de l'axe, ainsi qu'un élément d'engagement (46) qui est animé d'un mouvement alternatif dans la rainure axiale (43) et qui s'engage dans les deux cames (41, 45). Ces dernières sont conformées de telle manière et l'élément d'engagement (46) animé d'un mouvement alternatif axial est conçu de telle manière que l'on peut faire varier le mouvement alternatif de ce dernier pour réguler le couple transmis par le mécanisme. Dans un autre mode de réalisation , on peut faire varier le rapport des couples ou des régimes, on peut réaliser l'entraînement d'un élément supplémentaire ou bien un arrêt automatique.
PCT/DE1989/000189 1988-03-24 1989-03-23 Commande a cames WO1989009351A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19893924548 DE3924548A1 (de) 1989-03-23 1989-07-25 4-wellen-umlaufgetriebe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3809992.6 1988-03-24
DE19883809992 DE3809992A1 (de) 1988-03-24 1988-03-24 Vorrichtung zur formschluessigen uebertragung oder umwandlung von kraeften und bewegungen

Publications (1)

Publication Number Publication Date
WO1989009351A1 true WO1989009351A1 (fr) 1989-10-05

Family

ID=6350606

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1989/000189 WO1989009351A1 (fr) 1988-03-24 1989-03-23 Commande a cames

Country Status (3)

Country Link
EP (1) EP0366737A1 (fr)
DE (1) DE3809992A1 (fr)
WO (1) WO1989009351A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2920509A1 (fr) * 2007-09-03 2009-03-06 Luc Sauteraud Demultiplicateur a progressions variables

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW341638B (en) * 1995-12-28 1998-10-01 Kenji Mimura Differential gear and method of manufacturing disc-like members for use in same
DE102009005838B4 (de) 2009-01-21 2014-10-16 Gerhard Thien Getriebevorrichtung zum Übertragen eines Drehmoments und Vorrichtung zum Erzeugen oder Wandeln eines Drehmoments
DE102010003098A1 (de) * 2010-03-22 2011-09-22 Anlagenbau Neuried Gmbh & Co. Kg Übersetzungsgetriebe
DE102017106171B4 (de) * 2017-03-22 2019-12-24 Paul Hettich Gmbh & Co. Kg Haushaltsgerät, insbesondere Kühl- oder Gefrierschrank, oder Möbel mit wenigstens einer Ablage
DE102017106170A1 (de) 2017-03-22 2018-09-27 Paul Hettich Gmbh & Co. Kg Vorrichtung zur rotatorischen und translatorischen Bewegung eines Gegenstands
DE102017218030A1 (de) * 2017-10-10 2019-04-11 Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Bamberg Getriebe mit Planetenelement und Führungsbahn
DE102018108977A1 (de) * 2018-04-16 2019-10-17 Paul Hettich Gmbh & Co. Kg Ablageboden für ein Möbel oder Haushaltsgerät, Möbel und Haushaltsgerät

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE801421C (de) * 1949-01-25 1951-01-08 Werner Altmann Ausgleichgetriebe fuer Kraftfahrzeuge
FR1286129A (fr) * 1961-03-20 1962-03-02 Dispositifs de transformation de mouvement et de transmission de force conçus selonun nouveau principe d'entraînement
US4069718A (en) * 1976-09-13 1978-01-24 The United States Of America As Represented By The Secretary Of The Army Speed change device
DE3712458A1 (de) * 1987-04-11 1988-10-27 Franz Koop Kurvengetriebe mit konstanten uebersetzungsverhaeltnissen fuer beengte einsatzbereiche

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE348513C (de) * 1919-10-08 1922-02-10 Wilhelm Vogt UEbersetzungsgetriebe mit gleichachsig liegender treibender und getriebener Welle
US3807243A (en) * 1971-11-17 1974-04-30 Agency Ind Science Techn Mechanical power transmission apparatus using balls
DE3505396A1 (de) * 1985-02-16 1986-08-21 Alfred Prof. Dipl.-Kaufm. 7142 Marbach Evert Stufenloses getriebe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE801421C (de) * 1949-01-25 1951-01-08 Werner Altmann Ausgleichgetriebe fuer Kraftfahrzeuge
FR1286129A (fr) * 1961-03-20 1962-03-02 Dispositifs de transformation de mouvement et de transmission de force conçus selonun nouveau principe d'entraînement
US4069718A (en) * 1976-09-13 1978-01-24 The United States Of America As Represented By The Secretary Of The Army Speed change device
DE3712458A1 (de) * 1987-04-11 1988-10-27 Franz Koop Kurvengetriebe mit konstanten uebersetzungsverhaeltnissen fuer beengte einsatzbereiche

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2920509A1 (fr) * 2007-09-03 2009-03-06 Luc Sauteraud Demultiplicateur a progressions variables

Also Published As

Publication number Publication date
DE3809992A1 (de) 1989-10-12
EP0366737A1 (fr) 1990-05-09

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