DE4312869A1 - Gearing with positive prevention of torque reversal from both directions of rotation in combination with minimum gearing inertia - Google Patents

Gearing with positive prevention of torque reversal from both directions of rotation in combination with minimum gearing inertia

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Publication number
DE4312869A1
DE4312869A1 DE19934312869 DE4312869A DE4312869A1 DE 4312869 A1 DE4312869 A1 DE 4312869A1 DE 19934312869 DE19934312869 DE 19934312869 DE 4312869 A DE4312869 A DE 4312869A DE 4312869 A1 DE4312869 A1 DE 4312869A1
Authority
DE
Germany
Prior art keywords
gearing
output
gearbox
rotation
transmission part
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.)
Granted
Application number
DE19934312869
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German (de)
Other versions
DE4312869C2 (en
Inventor
Lothar Strach
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to DE19934312869 priority Critical patent/DE4312869C2/en
Priority to DE19944429315 priority patent/DE4429315A1/en
Publication of DE4312869A1 publication Critical patent/DE4312869A1/en
Application granted granted Critical
Publication of DE4312869C2 publication Critical patent/DE4312869C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Abstract

Gearing is used to alter the speed and torque ratio of an input and an output. The gearing components are here in rotation about their geometrical axis or about the axis of the gearing. In pauses between operation and with the energy supply to the driving motor switched off, the reactive effect of raised loads or other dynamic reaction forces is prevented by inserting into the gearing a worm gear with a shallow worm pitch or, alternatively, inserting cone or disc brakes. The worm gear results in poor driving efficiency, while cone or disc brakes are frictional elements and are subject to wear, with dangerous consequences in the event of inadequate maintenance - due to external influences, the friction coefficient can change very rapidly for the worse. In the present invention, a gearing has been inserted into a transmission member which executes torsional vibrations without, however, rotating about its own axis. This torsional vibration is used to move a positively engaging part out of a stand-by position into the space in which this torsional vibration takes place, the intention being by this means to prevent reaction forces in pauses between operation from turning the gearing backwards.

Description

Eine beliebig geformte Ebene wird in eine kreisschiebende Bewegung gebracht mittels mindestens drei Parallel-Kurbeln mit gleichem Radius und infolge eines Drehantriebes einer dieser Parallel-Kurbeln. Jeder
Punkt dieser Ebene vollzieht somit einen Kreis-Schub. Die günstigste Lage der mindestens drei Parallel-Kurbeln befindet sich auf den Eck­ punkten eines spitzwinkligen Dreiecks, dessen Seitenlängen ungleich sein können. Wird an beliebiger Stelle einer so bewegten Ebene eine geschlossene Innenverzahnung eingebracht, so vermag diese zusammen mit einem außenverzahnten Rad mit geringerer Zähnezahl ein Unterset­ zungsgetriebe zu bilden. Das kreisschiebende Zahnrad (Innen- und Außen- Verzahnung sind kinematisch austauschbar) bildet eine gekrümmte Zahn­ stange, welche in jedem Bewegungspunkt gleiche Verschiebegeschwindigkeit hat. Die kreisschiebende Ebene bietet die Möglichkeit einer formschlüssigen Sperrung in beiden Drehrichtungen.An arbitrarily shaped plane is brought into a circular pushing movement by means of at least three parallel cranks with the same radius and as a result of a rotary drive of one of these parallel cranks. Everyone
Point of this level thus creates a circle push. The most favorable position of the at least three parallel cranks is on the corner points of an acute-angled triangle, the side lengths of which may be different. If a closed internal toothing is introduced at any point on a plane that is moved in this way, it can form a reduction gear together with an externally toothed wheel with fewer teeth. The circular pushing gear (inner and outer teeth are kinematically interchangeable) forms a curved toothed rack, which has the same displacement speed in every point of movement. The circular pushing level offers the possibility of a positive locking in both directions of rotation.

Bild 1 zeigt eine technische Möglichkeit eines solchen Getriebes, einmal mit koaxialem Abtrieb, einmal mit einem parallelem Abtrieb. Der Antrieb erfolgt dabei zentral, es werden 3 Blindkurbeln benötigt. Figure 1 shows a technical possibility of such a gearbox, one with a coaxial output, one with a parallel output. The drive is central, 3 blind cranks are required.

Bild 2 zeigt ein solches Getriebe bestehend aus einer Antriebskurbel und 2 Blindkurbeln und der untersetzenden Zahnradpaarung mittels Kreisschub, ferner die formschlüssig wirkende Drehsperrung mit einem sehr geringen Wirkhub. Figure 2 shows such a gearbox consisting of a drive crank and 2 blind cranks and the step-down gear pairing by means of a circular thrust, as well as the positive-locking rotary lock with a very small effective stroke.

Bild 3 zeigt in vergrößertem Maß die Bewegung der gekrümmten Zahnstange auf dem Bogen des kleinen Kurbelkreises, infinitesimal eine Geradführung darstellend nach dem Proportional-Axiom von Euklid. Bei einem e von ∞ nach Bild 4 in eine klassische, gerade Zahnstange übergehend. Figure 3 shows the movement of the curved rack on the arc of the small crank circle to an enlarged extent, infinitesimally representing a straight line according to the proportional axiom of Euclid. With an e of ∞ according to Fig. 4, transitioning into a classic, straight rack.

Bild 5 zeigt die Ausbildung als Hohlwellengetriebe mit einem bisher in der Technik nicht möglichen hohen Quotient aus innendurchmesser/Außendurch­ messer, bereits beginnend mit einem i von 2. Figure 5 shows the design as a hollow shaft gear with a high quotient of inner diameter / outer diameter that has not been possible in technology, starting with an i of 2.

Bild 6 zeigt die gleiche Getriebetechnik einer Kreisschubbewegung sogar für ein i von 1, womit erstmals in der Technik eine hermetische Dichtung von Drehantrieben möglich wird mit der Besonderheit, daß die Drehmoment­ übertragung zwischen An- und Abtrieb auf dem größtmöglichen System­ durchmesser erfolgt. Figure 6 shows the same gear technology of a circular thrust movement even for an i of 1, which makes it possible for the first time in hermetic sealing of rotary drives with the special feature that the torque transmission between input and output takes place on the largest possible system diameter.

Claims (9)

1. Getriebe mit formschlüssiger Verhinderung eines Momenten- Rückflusses aus beiden Drehrichtungen dadurch gekennzeichnet, daß ein Getriebe gebildet ist aus mehreren gestellfest und drehfähig gelagerten Parallelkurbeln bzw. Exzentern und daß eine dieser Kurbeln angetrieben wird und eine Kreisschiebung ausübt auf ein Übertragungsteil und dieses Übertragungsteil Träger ist eines Hohlrades, welches ein außenverzahntes Stirnrad um­ schließt mit geringerer Zähnezahl und diese Kreisschiebung umsetzt in eine Rotationsabtriebsbewegung mit einer Stufenuntersetzung gemäß der gewählten Zähnezahldifferenz.1. Gearbox with positive prevention of a backflow of torque from both directions of rotation, characterized in that a gear is formed from several frame-fixed and rotatably mounted parallel cranks or eccentrics and that one of these cranks is driven and exerts a circular movement on a transmission part and this transmission part is carrier a ring gear which closes an externally toothed spur gear with a smaller number of teeth and converts this circular shift into a rotational output movement with a step-down ratio according to the selected number of teeth difference. 2. Getriebe mit formschlüssiger Verhinderung eines Momenten-Rück­ flusses aus beiden Drehrichtungen nach Anspruch 1 dadurch gekennzeichnet, daß ein Übertragungsteil mit prismatischer oder sonstwie geformter Kontur in dem Freiheitsgrad der Kreisschiebung dadurch behindert wird, daß ein formschlüssig wirkender Körper in den Raum der Schwingungsbewegung des Übertragungsteiles eingeführt wird und die weitere Schwingungsfähigkeit behindert.2. Gearbox with positive prevention of a torque back flow from both directions of rotation according to claim 1 characterized in that a transmission part with prismatic or otherwise shaped contour in the degree of freedom of the circular displacement is hindered in that a form-fitting body in the space of Vibration movement of the transmission part is introduced and the further vibration ability hindered. 3. Getriebe mit formschlüssiger Verhinderung eines Momenten- Rückflusses aus einer Drehrichtung dadurch gekennzeichnet, daß in den Schwingungsraum des Übertragungsteiles formschlüssig ein Körper eingeführt wird, dessen Sperrkraft infolge der Kreisschiebung in rückwärtiger Wirkung verstärkt wird, die Sperrung aber gelöst wird mit dem Antriebsbeginn.3. Gearbox with positive prevention of a torque Return flow from one direction characterized in that in the vibration space of the transmission part form-fitting a body is introduced, the locking force as a result the circular shift is increased in the backward effect, the blocking but is solved with the start of the drive. 4. Getriebe mit formschlüssiger Verhinderung eines Momenten- Rückflusses aus beiden Drehrichtungen für jede mögliche Winkelstellung des Abtriebes dadurch gekennzeichnet, daß die Kreisschiebung des Übertragungsteiles aufgelöst wird in eine geradlinige Bewegung jeweils in x- und y-Bewe­ gungsrichtung mittels jeweils angelenkter Kreuzschieber, womit jeder Winkel der Antriebsparallelkurbel formschlüssig sperrbar wird.4. Gearbox with positive locking of a torque Return flow from both directions of rotation for every possible angular position of the output characterized in that the circular displacement of the transmission part is resolved in a straight line movement in x and y movement direction by means of articulated cross slide, with which everyone Angle of the parallel drive crank is positively lockable. 5. Getriebe nach Anspruch 1, 2, 3 und 4 dadurch gekennzeichnet, daß im Abtrieb eine kinematische Umkehr von Hohlrad und außenverzahntem Stirnrad ausgeführt wird. 5. Transmission according to claim 1, 2, 3 and 4 characterized in that in the output a kinematic reversal of Ring gear and externally toothed spur gear is executed.   6. Getriebe nach Anspruch 1 und 5 dadurch gekennzeichnet, daß bei schneller Drehzahländerung erforderliche Beschleunigungs- oder Verzögerungskräfte dadurch verringert werden, indem das massengrößte und mit größter Geschwindigkeit sich bewegende Übertragungsglied sich nicht um seine geometrische oder Schwerpunkt­ achse dreht, sondern daß diese Masse vereint im Schwerpunkt sich nur mit dem Radius der halben Differenz von Hohlrad minus außenverzahntem Stirnrad um die Getriebeabtriebsachse in einer Kreisschiebung dreht.6. Transmission according to claim 1 and 5 characterized in that required for rapid speed change Acceleration or deceleration forces are reduced by being the largest in mass and moving at the highest speed Transmission link is not about its geometric or center of gravity axis rotates, but that this mass only unites in the center of gravity with the radius of half the difference between the ring gear minus the external gear Spur gear rotates in a circular shift around the gearbox output axis. 7. Getriebe nach Anspruch 1 und 5 dadurch gekennzeichnet, daß An- und Abtriebsachse koaxial angeordnet sind.7. Transmission according to claim 1 and 5 characterized in that the input and output axes are arranged coaxially are. 8. Getriebe nach Anspruch 1 und 5 dadurch gekennzeichnet, daß An- und Abtriebsachse parallel mit belie­ bigem Abstand zueinander angeordnet sind und wirken.8. Transmission according to claim 1 and 5 characterized in that the input and output axes are parallel with are spaced from each other and work. 9. Getriebe nach Anspruch 2 und 3 dadurch gekennzeichnet, daß die gegen einen Rücklauf aufeinander wirkenden Teile in der Ausbildungsform einer niederen Elementen­ paarung verwendet werden.9. Transmission according to claim 2 and 3 characterized in that against each other a return acting parts in the form of training of lower elements pairing can be used.
DE19934312869 1993-04-20 1993-04-20 Circular thrust gear Expired - Fee Related DE4312869C2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19934312869 DE4312869C2 (en) 1993-04-20 1993-04-20 Circular thrust gear
DE19944429315 DE4429315A1 (en) 1993-04-20 1994-08-18 Mechanism with positive prevention of torque reversal in both directions of rotation in combination with very low mechanism inertia

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19934312869 DE4312869C2 (en) 1993-04-20 1993-04-20 Circular thrust gear

Publications (2)

Publication Number Publication Date
DE4312869A1 true DE4312869A1 (en) 1994-12-08
DE4312869C2 DE4312869C2 (en) 1999-09-16

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DE19934312869 Expired - Fee Related DE4312869C2 (en) 1993-04-20 1993-04-20 Circular thrust gear

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4429315A1 (en) * 1993-04-20 1995-02-23 Lothar Strach Mechanism with positive prevention of torque reversal in both directions of rotation in combination with very low mechanism inertia
DE19515146A1 (en) * 1995-04-25 1996-04-18 Lothar Strach Gear=drive with internally and externally-toothed gears
DE19709020A1 (en) * 1996-12-23 1997-11-06 Lothar Strach Gear transmission with minimal overall reversing play
DE10059069A1 (en) * 2000-11-28 2002-06-20 Gpm Ges Fuer Antriebstechnik G Mechanical loader
EP1403155A2 (en) * 2002-09-30 2004-03-31 Robert Bosch Gmbh Symmetric motor for wiper elements
EP1626202A1 (en) * 2004-08-11 2006-02-15 Cornelius Peter Reduction gearing and drive mechanism comprising the reduction gearing
DE102006052253B3 (en) * 2006-11-03 2008-07-10 Zf Friedrichshafen Ag Adjustment drive for local adjustment of a chassis component
DE102017003305A1 (en) * 2017-04-05 2018-10-11 Forschungszentrum Jülich GmbH Rotary feedthrough with gearbox

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7217212B2 (en) 2004-10-27 2007-05-15 Orbiter Gears Marketing & Finance Ag Differential gear system having a stably-oriented orbiting gear
CN111958334B (en) * 2020-08-18 2021-03-12 广州市万力工艺制品有限公司 Finish machining device and process for connection structure of assembled furniture

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH564709A5 (en) * 1973-01-23 1975-07-31 Aginfor Ag
GB2101263A (en) * 1981-06-24 1983-01-12 Peter James Griffin Motion conversion device
EP0169646A1 (en) * 1984-06-21 1986-01-29 Jaguar Cars Limited A mechanism for transmitting rotational motion from one shaft to another
EP0589760A1 (en) * 1992-09-25 1994-03-30 An Bang Yu Single-ring-gear planetary transmission unit with small difference between teeth of meshing gears

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2218181A (en) * 1988-05-04 1989-11-08 Reliance Gear Co Gearing device
DE4127051A1 (en) * 1991-08-16 1993-02-18 Standard Elektrik Lorenz Ag Precision gearbox with differential gears - has externally cogged gearwheel disc engaging with internally cogged spur wheel bell

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH564709A5 (en) * 1973-01-23 1975-07-31 Aginfor Ag
GB2101263A (en) * 1981-06-24 1983-01-12 Peter James Griffin Motion conversion device
EP0169646A1 (en) * 1984-06-21 1986-01-29 Jaguar Cars Limited A mechanism for transmitting rotational motion from one shaft to another
EP0589760A1 (en) * 1992-09-25 1994-03-30 An Bang Yu Single-ring-gear planetary transmission unit with small difference between teeth of meshing gears

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4429315A1 (en) * 1993-04-20 1995-02-23 Lothar Strach Mechanism with positive prevention of torque reversal in both directions of rotation in combination with very low mechanism inertia
DE19515146A1 (en) * 1995-04-25 1996-04-18 Lothar Strach Gear=drive with internally and externally-toothed gears
DE19515146C2 (en) * 1995-04-25 1998-09-17 Lothar Strach Circular thrust gear
DE19709020A1 (en) * 1996-12-23 1997-11-06 Lothar Strach Gear transmission with minimal overall reversing play
DE19709020C2 (en) * 1996-12-23 1999-11-25 Lothar Strach Circular thrust gear
DE10059069A1 (en) * 2000-11-28 2002-06-20 Gpm Ges Fuer Antriebstechnik G Mechanical loader
EP1403155A2 (en) * 2002-09-30 2004-03-31 Robert Bosch Gmbh Symmetric motor for wiper elements
EP1403155A3 (en) * 2002-09-30 2005-04-20 Robert Bosch Gmbh Symmetric motor for wiper elements
EP1626202A1 (en) * 2004-08-11 2006-02-15 Cornelius Peter Reduction gearing and drive mechanism comprising the reduction gearing
DE102006052253B3 (en) * 2006-11-03 2008-07-10 Zf Friedrichshafen Ag Adjustment drive for local adjustment of a chassis component
DE102017003305A1 (en) * 2017-04-05 2018-10-11 Forschungszentrum Jülich GmbH Rotary feedthrough with gearbox

Also Published As

Publication number Publication date
DE4312869C2 (en) 1999-09-16

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