WO2002009998A1 - Actuator for an automotive steering system - Google Patents
Actuator for an automotive steering system Download PDFInfo
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- WO2002009998A1 WO2002009998A1 PCT/EP2001/008116 EP0108116W WO0209998A1 WO 2002009998 A1 WO2002009998 A1 WO 2002009998A1 EP 0108116 W EP0108116 W EP 0108116W WO 0209998 A1 WO0209998 A1 WO 0209998A1
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- Prior art keywords
- planet
- stepped
- gears
- shaft
- planetary
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/008—Changing the transfer ratio between the steering wheel and the steering gear by variable supply of energy, e.g. by using a superposition gear
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- 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
- F16H1/2863—Arrangements for adjusting or for taking-up backlash
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- 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
- F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
Definitions
- the invention relates to an actuating device of a vehicle steering device, according to the preamble of patent claim 1.
- An actuating device for vehicle steering devices known from DE 197 23 358 A1 serves for the superimposed rotation angle transmission of two transmission inputs. While one transmission input is actuated by a steering handwheel and the other by a motor, the transmission output is connected to the steering transmission.
- the actuating device is designed as a planetary gear, with its sun gear hub forming the transmission output and its sun gear sleeve coaxial with the sun gear hub forming the first transmission input.
- the second transmission input is formed from a planet gear carrier, which carries planet gears and is concentric with this sun gear hub and the sun gear sleeve. Of the planet gears of the planet gear carrier, two are rotatably connected to one another and can be rotated coaxially about an axis defined in the planet gear carrier and in constant engagement with the sun gear hub and sun gear sleeve.
- the ring gear and pinion are each larger than the width of the planet gear meshing with them.
- This excess width is assigned to the meshing planet gear so that it projects on one side of the planet gear.
- the pinion projects beyond an end face of the planet gear, which is opposite to that on which the excess width of the ring gear projects beyond the planet gear.
- an additional gearwheel which is rotatable in the same axis as the planetary gear and which is each elastically braced relative to the planetary gear is mounted.
- one of the additional gearwheels is in meshing engagement with the pinion alone and the other alone with the ring gear, so that one additional gearwheel is radially internally exciting while the other is radially externally exciting additional gear works.
- the solution specified in claim 1 is based on the problem of designing an actuating device of the type specified at the beginning, which is designed as a play-free planetary gear transmission, in which the freedom from play is realized by means that are reliable and structurally simple.
- the problem is solved by the features listed in the characterizing part of patent claim 1, in that the planetary gear transmission has at least one rigid and at least one torsionally elastic, prestressed step planet.
- the advantages achieved by the invention are, in particular, that with the torsionally flexible step planet, which is self-adjusting when worn, the overall play of a planetary gear is compensated without adjusting the center distance, the solution being simple, inexpensive and small in size. It can be the inventive Solution for helical gearing and degree gearing of the gears of the planetary gear.
- Advantageous developments of the invention are specified in the dependent claims.
- Figure 1 is a backlash-free two-stage planetary gear transmission in longitudinal section.
- FIG. 2 shows a backlash-free planetary gear as an actuating device for a vehicle steering device
- FIG. 3 shows a stiffness characteristic of a planetary gear transmission according to the invention.
- the drawing shows an actuating device designed as a planetary gear 1 with two step planets 2, 7. These step planets 2, 7 are held in a planet gear carrier 6 via roller bearings 21 and each carry two planet gears 4, 5 and 9, 10, which are connected to one another in pairs. While the planet gears 4, 5 of the one stepped planet 2 are rigidly connected by a shaft 3, the second shaft 8 is designed as a torsion bar (spring) and permits elastic rotation of the planet gears 9, 10 carried by it.
- the planet gears 4, 5 and 9, 10 of the stepped planet 2, 7 are in constant toothed engagement with two sun gears 11, 12. One of these sun gears 1 1, 12 is connected to the transmission input 14, while the other is assigned to the transmission output 19.
- the shaft 8, designed as a torsion bar, of the torsionally flexible step planet 7 is prestressed by a predetermined angle of rotation, so that the spring-back moment acts on both planet gears 9, 10. These lie with their tooth flanks on the tooth flanks of the special teeth that are in mesh with them. internal gears 1 1, 12 and exert a force on them. This force generates a torque that rotates the sun gears 1 1, 12 until they in turn rest against the tooth flanks of the planet gears 4, 5 of the rigid step planet 2.
- all tooth flanks in engagement are resiliently in contact with one another, so that the total play of the planetary gear mechanism is compensated for up to a defined torque.
- the force transmission takes place via the rigid or the torsionally flexible step planet 2 or 7.
- a rigidity characteristic of a planetary gear 1 according to the invention is shown in FIG. 3.
- a planetary gear with the functionality described can also be designed such that the planet gears of the stepped planet mesh with two ring gears or a ring gear and a sun gear.
- the principle of operation can also be applied to compound planetary gear units.
- the compensation of the overall play of the planetary gear is achieved by the rigid shaft of the torsionally flexible stepped planet receiving two planet gears, at least one of which is rotatably and without axial play on the shaft.
- a torsion spring for example a helical or leg spring, is arranged on this shaft and connects the two planet gears in such a way that they can be rotated in a resilient manner relative to one another.
- the configuration of the torsionally flexible step planet with a claw coupling acting as a stop which limits the angle of rotation in both directions of rotation, so that the torsionally flexible step planet absorbs a portion of the torque to be transmitted in the event of an excessive load on the planetary gear.
- Fig. 1 shows a longitudinal section through an inventive planetary gear 1, which is designed as a translating two-stage gear.
- step planets 2, 7 enable an input speed to be reduced or increased in both directions of rotation with low-noise operation and without play.
- This version opens the application of the planetary gear 1 in all areas of the machine or. Vehicle construction in which stepped or stepped speeds are required.
- FIG. 2 shows a preferred application of the planetary gear 1 in a vehicle steering device, in particular a longitudinal section of an actuating device of a servo-assisted steering device designed as a superposition gear.
- a second gear input 15, 16, here shown as a worm 15 and worm wheel 16 is integrated.
- the worm wheel 16 is connected to the planet gear carrier 6.
- Steering handwheel 18, the servomotor 17 and the steering gear 20 are only shown symbolically as blocks.
- the angle of rotation introduced by the driver into the steering handwheel 18 is initiated via the first transmission input 14 and the sun gear 11.
- a gearbox output 19 connected in a rotationally fixed manner to the sun gear 12 is connected to the vehicle steering wheels via the steering gear 20.
- a control unit not shown, which detects the adjustment of the steering angle and possibly other characteristic values influencing the steering characteristic via sensors, activates the servomotor 17, which acts on the second transmission input 15, 16 and thus on the planet gear carrier 6.
- the transmission ratio between the transmission input 14 and the transmission output 19 is now determined by the direction of rotation and the speed of rotation of the servomotor 17, by superimposing the angle of rotation introduced via the steering handwheel 18.
- a planetary gear 1 of the type specified is at any time in other steering devices, for. B. a mechanical steering device without steering assistance, can be used.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Power Steering Mechanism (AREA)
- Retarders (AREA)
Abstract
Description
Betätigungseinrichtung einer Fahrzeug - LenkvorrichtungActuating device of a vehicle steering device
Die Erfindung betrifft eine Betätigungseinrichtung einer Fahrzeug - Lenkvorrichtung, nach dem Oberbegriff des Patentanspruches 1.The invention relates to an actuating device of a vehicle steering device, according to the preamble of patent claim 1.
Eine aus der DE 197 23 358 A 1 bekannte Betätigungseinrichtung für Fahrzeug - Lenkvorrichtungen dient der überlagerten Drehwinkel Übertragung von zwei Getriebeeingängen. Während der eine Getriebeeingang von einem Lenkhandrad und der andere von einem Motor beaufschlagt wird, ist der Getriebeausgang mit dem Lenkgetriebe verbundenen. Die Betätigungseinrichtung ist als Planetenradgetriebe ausgebildet, wobei dessen Sonnenradnabe den Getriebeausgang und dessen zur Sonnenradnabe koaxiale Sonnenradhülse den ersten Getriebeeingang bildet. Der zweite Getriebeeingang wird aus einem zu dieser Sonnenradnabe und der Son- nenradhülse konzentrischen Planetenradträger, der Planetenräder trägt, gebildet. Von den Planetenrädern des Planetenradträgers sind jeweils zwei miteinander drehfest verbunden und koaxial um eine im Planetenradträger festgelegte Achse drehbar und im ständigen Eingriff mit Sonnenradnabe und Sonnenradhülse.An actuating device for vehicle steering devices known from DE 197 23 358 A1 serves for the superimposed rotation angle transmission of two transmission inputs. While one transmission input is actuated by a steering handwheel and the other by a motor, the transmission output is connected to the steering transmission. The actuating device is designed as a planetary gear, with its sun gear hub forming the transmission output and its sun gear sleeve coaxial with the sun gear hub forming the first transmission input. The second transmission input is formed from a planet gear carrier, which carries planet gears and is concentric with this sun gear hub and the sun gear sleeve. Of the planet gears of the planet gear carrier, two are rotatably connected to one another and can be rotated coaxially about an axis defined in the planet gear carrier and in constant engagement with the sun gear hub and sun gear sleeve.
Bei Zahnradgetrieben, wie auch bei mit Zahnrädern betriebenen Planeten- radgetrieben, treten herstellungsbedingte Toleranzen, wie Zahndickenabmaß, Flankenformfehler, Rundlauffehler, Teilungsfehler und Achsabstands- abweichungen auf. Um ein Klemmen der Getrieberäder zu vermeiden, muß zwischen den Flanken daher stets ein Spiel vorhanden sein. Dieses Zahnflankenspiel ist bei Anwendungen, wie der Betätigungseinrichtung für Fahrzeug - Lenkvorrichtungen störend, da dort bis zu einem definierten Moment eine Spielfreiheit in beide Drehrichtungen erforderlich ist. Ein Planetenzahnradgetriebe mit Mitteln zur Beseitigung des störenden Zahnflankenspiels ist in der DE 197 57 433 A1 beschrieben. Dieses Planetenzahnradgetriebe weist ein Hohlrad, ein Ritzel und einen Umlaufträger mit gleichzeitig in dem Hohlrad und dem Ritzel kämmenden Planetenrä- dem auf. Von ihrer Breite her sind Hohlrad und Ritzel jeweils größer als die Breite des mit ihnen im Eingriff stehenden Planetenrades. Diese überschüssige Breite ist dem kämmenden Planetenrad jeweils so zugeordnet, daß sie jeweils auf einer Seite des Planetenrades übersteht. Dabei überragt das Ritzel eine Stirnseite des Planetenrades, die derjenigen gegenüberliegt, an der die überschüssige Breite des Hohlrades das Planetenrad überragt. Auf beiden Stirnseiten des Planetenrades ist ein achsgleich mit dem Planetenrad drehbares Zusatzzahnrad, welches jeweils gegenüber dem Planetenrad drehelastisch verspannt ist, gelagert. Durch die vorstehend beschriebene Zahnbreiten-Ausbildung ist es möglich, daß von den Zusatzzahnrädern ei- nes allein mit dem Ritzel und das andere allein mit dem Hohlrad in einem verzahnten Eingriff steht, so daß ein Zusatzzahnrad als radial innen spannendes, während das andere als radial außen spannendes Zusatzzahnrad wirkt.In the case of gearwheels, as well as in the case of planetary gearwheels operated with gearwheels, manufacturing-related tolerances such as tooth thickness dimension, flank shape errors, concentricity errors, pitch errors and center distance deviations occur. In order to avoid jamming of the gear wheels, there must always be play between the flanks. This backlash is disruptive in applications such as the actuating device for vehicle steering devices, since there is a need for play in both directions of rotation up to a defined moment. A planetary gear transmission with means for eliminating the annoying backlash is described in DE 197 57 433 A1. This planetary gear transmission has a ring gear, a pinion and a revolving carrier with planet wheels meshing simultaneously in the ring gear and the pinion. In terms of their width, the ring gear and pinion are each larger than the width of the planet gear meshing with them. This excess width is assigned to the meshing planet gear so that it projects on one side of the planet gear. The pinion projects beyond an end face of the planet gear, which is opposite to that on which the excess width of the ring gear projects beyond the planet gear. On both end faces of the planetary gear, an additional gearwheel which is rotatable in the same axis as the planetary gear and which is each elastically braced relative to the planetary gear is mounted. Due to the tooth width design described above, it is possible that one of the additional gearwheels is in meshing engagement with the pinion alone and the other alone with the ring gear, so that one additional gearwheel is radially internally exciting while the other is radially externally exciting additional gear works.
Diese Lösung erfordert einen verhältnismäßig hohen Bauaufwand, bei den speziellen Zusatzzahnrädern und deren Anordnung zu der Zahnbreiten- Ausbildung von Ritzel und Hohlrad des Planetenradgetriebes.This solution requires a relatively high level of construction, with the special additional gears and their arrangement for the tooth width formation of pinion and ring gear of the planetary gear.
Der im Patentanspruch 1 angegebenen Lösung liegt das Problem zugrun- de, eine als spielfreies Planetenradgetriebe ausgeführte Betätigungseinrichtung der eingangs angegebenen Art zu konzipieren, bei welchem die Spielfreiheit durch betriebssichere und baulich einfache Mittel realisiert wird. Das Problem wird durch die im kennzeichnenden Teil des Patentanspruches 1 aufgeführten Merkmalen gelöst, indem das Planetenradgetriebe minde- stens einen starren und mindestens einen drehelastischen, vorgespannten Stufenplaneten aufweist. Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, daß mit dem drehelastischen Stufenplaneten, der bei Verschleiß selbstnachstellend ist, das Gesamtspiel eines Planetenradgetriebes ohne Verstellung des Achsabstandes kompensiert wird, wobei die Lö- sung einfach, preiswert und kleinbauend ist. Dabei kann die erfinderische Lösung bei Schrägverzahnung und Gradverzahnung der Zahnräder des Planetenradgetriebes zur Anwendung kommen. Vorteilhafte Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen angegeben.The solution specified in claim 1 is based on the problem of designing an actuating device of the type specified at the beginning, which is designed as a play-free planetary gear transmission, in which the freedom from play is realized by means that are reliable and structurally simple. The problem is solved by the features listed in the characterizing part of patent claim 1, in that the planetary gear transmission has at least one rigid and at least one torsionally elastic, prestressed step planet. The advantages achieved by the invention are, in particular, that with the torsionally flexible step planet, which is self-adjusting when worn, the overall play of a planetary gear is compensated without adjusting the center distance, the solution being simple, inexpensive and small in size. It can be the inventive Solution for helical gearing and degree gearing of the gears of the planetary gear. Advantageous developments of the invention are specified in the dependent claims.
Ein Ausführungsbeispiele der Erfindung ist in der Zeichnung dargestellt und im folgenden näher erläutert. Es zeigen:An embodiment of the invention is shown in the drawing and explained in more detail below. Show it:
Fig. 1 ein spielfreies zweistufig übersetzendes Planetenradgetriebe im Längsschnitt;Figure 1 is a backlash-free two-stage planetary gear transmission in longitudinal section.
Fig. 2 ein spielfreies Planetenradgetriebe als Betätigungseinrichtung für eine Fahrzeug - Lenkvorrichtung;2 shows a backlash-free planetary gear as an actuating device for a vehicle steering device;
Fig. 3 eine Steifigkeitskennlinie eines erfindungsgemäßen Planeten- radgetriebes.3 shows a stiffness characteristic of a planetary gear transmission according to the invention.
Im Wesentlichen gleiche Teile in den unterschiedlichen Figuren sind mit gleichen Bezugszeichen versehen.Substantially identical parts in the different figures are provided with the same reference symbols.
In der Zeichnung ist eine als Planetenradgetriebe 1 konzipierte Betätigungseinrichtung mit zwei Stufenplaneten 2, 7 dargestellt. Diese Stufenplaneten 2, 7 sind über Wälzlager 21 in einem Planetenradträger 6 gehalten und tragen jeweils zwei Planetenräder 4, 5 und 9, 10, die paarweise miteinander verbunden sind. Während die Planetenräder 4, 5 des einen Stufenplaneten 2 durch eine Welle 3 starr verbunden sind, ist die zweite Welle 8 als Drehstab(-feder) ausgebildet und läßt eine elastische Verdrehung der durch sie getragenen Planetenräder 9, 10 zu. Die Planetenräder 4, 5 und 9, 10 der Stufenplaneten 2, 7 stehen im ständigen verzahnten Eingriff mit zwei Sonnenrädern 11 , 12 . Eines dieser Sonnenräder 1 1 , 12 ist mit den Getriebeeingang 14 verbunden, während das andere dem Getriebeausgang 19 zugeordnet ist. Montageseitig wird die als Drehstab ausgebildete Welle 8 des drehelastischen Stufenplaneten 7 um einen vorbestimmten Drehwinkel vorgespannt, so daß das Rückfedermoment auf beide Planetenräder 9, 10 wirkt. Diese legen sich mit ihren Zahnflanken an die jeweils mit ihnen im verzahnten Eingriff stehenden Zahnflanken der Son- nenräder 1 1 , 12 an und üben eine Kraft auf diese aus. Diese Kraft erzeugt ein Drehmoment, das die Sonnenräder 1 1 , 12 solange verdreht, bis sie wiederum an den Zahnflanken der Planetenräder 4, 5 des starren Stufenplaneten 2 anliegen. Als Ergebnis dieses Vorspannens des Drehstabes lie- gen alle im Eingriff befindlichen Zahnflanken federnd aneinander an, so daß bis zu einem definierten Drehmoment das Gesamtspiel des Planeten- radgetriebes kompensiert wird. Je nach Drehrichtung erfolgt die Kraftübertragung über den starren oder den drehelastischen Stufenplaneten 2 oder 7. Eine Steifigkeitskennlinie eines erfindungsgemäßen Planetenradgetriebes 1 ist in der Fig. 3 dargestellt.The drawing shows an actuating device designed as a planetary gear 1 with two step planets 2, 7. These step planets 2, 7 are held in a planet gear carrier 6 via roller bearings 21 and each carry two planet gears 4, 5 and 9, 10, which are connected to one another in pairs. While the planet gears 4, 5 of the one stepped planet 2 are rigidly connected by a shaft 3, the second shaft 8 is designed as a torsion bar (spring) and permits elastic rotation of the planet gears 9, 10 carried by it. The planet gears 4, 5 and 9, 10 of the stepped planet 2, 7 are in constant toothed engagement with two sun gears 11, 12. One of these sun gears 1 1, 12 is connected to the transmission input 14, while the other is assigned to the transmission output 19. On the assembly side, the shaft 8, designed as a torsion bar, of the torsionally flexible step planet 7 is prestressed by a predetermined angle of rotation, so that the spring-back moment acts on both planet gears 9, 10. These lie with their tooth flanks on the tooth flanks of the special teeth that are in mesh with them. internal gears 1 1, 12 and exert a force on them. This force generates a torque that rotates the sun gears 1 1, 12 until they in turn rest against the tooth flanks of the planet gears 4, 5 of the rigid step planet 2. As a result of this pretensioning of the torsion bar, all tooth flanks in engagement are resiliently in contact with one another, so that the total play of the planetary gear mechanism is compensated for up to a defined torque. Depending on the direction of rotation, the force transmission takes place via the rigid or the torsionally flexible step planet 2 or 7. A rigidity characteristic of a planetary gear 1 according to the invention is shown in FIG. 3.
Ein Planetenradgetriebe mit der beschriebenen Funktionalität kann auch derart ausgebildet sein, daß die Planetenräder der Stufenplaneten in zwei Hohlräder oder ein Hohlrad und ein Sonnenrad kämmend eingreifen. Ebenso ist das Funktionsprinzip auf zusammengesetzte Planetenradgetriebe anwendbar.A planetary gear with the functionality described can also be designed such that the planet gears of the stepped planet mesh with two ring gears or a ring gear and a sun gear. The principle of operation can also be applied to compound planetary gear units.
In einem nicht dargestellten Anwendungsfall wird die Kompensierung des Gesamtspiels des Planetenradgetriebes erreicht, indem die an sich starre Welle des drehelastischen Stufenplaneten zwei Planetenräder aufnimmt, von denen mindestens eins drehbar und ohne Axialspiel auf der Welle gelagert ist. Auf dieser Welle ist eine Drehfeder, beispielhaft eine Schraubenoder Schenkelfeder, angeordnet, die beide Planetenräder derart verbindet, daß sie federnd relativ zueinander verdrehbar sind.In an application case, not shown, the compensation of the overall play of the planetary gear is achieved by the rigid shaft of the torsionally flexible stepped planet receiving two planet gears, at least one of which is rotatably and without axial play on the shaft. A torsion spring, for example a helical or leg spring, is arranged on this shaft and connects the two planet gears in such a way that they can be rotated in a resilient manner relative to one another.
Ebenfalls nicht dargestellt ist die Ausstattung des drehelastischen Stufenplaneten mit einer als Anschlag wirkenden Klauenkupplung, die den Verdrehwinkel in beide Drehrichtungen begrenzt, so daß der drehelastische Stufenplanet im Falle einer übermäßigen Belastung des Planetenradgetrie- bes einen Anteil des zu übertragenden Drehmomentes aufnimmt.Also not shown is the configuration of the torsionally flexible step planet with a claw coupling acting as a stop, which limits the angle of rotation in both directions of rotation, so that the torsionally flexible step planet absorbs a portion of the torque to be transmitted in the event of an excessive load on the planetary gear.
Um montageseitig das Vorspannen des drehelastischen Stufenplaneten 7 zu erleichtern, sind an der gehäuseaußenseitigen wellenstumpfartigen Verlängerung dieses Stufenplaneten 7 Werkzeugangriffsflächen 13 inte- griert. Fig. 1 zeigt einen Längsschnitt durch ein erfindungsgemäßes Planetenradgetriebe 1 , das als übersetzendes zweistufiges Getriebe ausgebildet ist. Die Stufenplaneten 2, 7 ermöglichen je nach Art der Getriebestufung eine Eingangsdrehzahl bei geräuscharmen Lauf und spielfrei in beide Drehrichtungen zu reduzieren oder zu erhöhen. Diese Ausführung eröffnet die Anwendung des Planetenradgetriebes 1 in allen Bereichen des Maschinenbzw. Fahrzeugbaues, in denen ab- oder hochgestufte Drehzahlen benötigt werden.In order to facilitate the pretensioning of the torsionally elastic stepped planet 7 on the assembly side, tool engagement surfaces 13 are integrated on the shaft-like extension of this stepped planet 7 on the outside of the housing. Fig. 1 shows a longitudinal section through an inventive planetary gear 1, which is designed as a translating two-stage gear. Depending on the type of gear ratio, step planets 2, 7 enable an input speed to be reduced or increased in both directions of rotation with low-noise operation and without play. This version opens the application of the planetary gear 1 in all areas of the machine or. Vehicle construction in which stepped or stepped speeds are required.
In Fig. 2 ist ein bevorzugter Anwendungsfall des Planetenradgetriebes 1 in einer Fahrzeug - Lenkvorrichtung, speziell ein Längsschnitt einer als Überlagerungsgetriebe ausgeführten Betätigungseinrichtung einer servounter- stützten Lenkeinrichtung, zu sehen.FIG. 2 shows a preferred application of the planetary gear 1 in a vehicle steering device, in particular a longitudinal section of an actuating device of a servo-assisted steering device designed as a superposition gear.
Im Unterschied zu dem in Fig. 1 ausgeführten Anwendungsfall ist hier ein zweiter Getriebeeingang 15, 16, hier als Schnecke 15 und Schneckenrad 16 zu erkennen, integriert. Das Schneckenrad 16 ist mit dem Planetenradträger 6 verbunden. Lenkhandrad 18, der Stellmotor 17 sowie das Lenkgetriebe 20 sind nur symbolisch als Blöcke dargestellt. Der vom Fahrer in das Lenkhandrad 18 eingeleitete Drehwinkel wird über den ersten Getriebeeingang 14 und das Sonnenrad 1 1 eingeleitet. Eine mit dem Sonnenrad 12 drehfest verbundener Getriebeausgang 19 ist über das Lenkgetriebe 20 mit den Fahrzeuglenkrädern verbunden. Eine nicht dargestellte Regeleinheit, die über Sensoren die Verstellung des Lenkwinkels und ggf. andere die Lenkcharakteristik beeinflussende Kennwerte erfaßt, aktiviert den Stellmotor 17, der auf den zweiten Getriebeeingang 15, 16 und damit auf den Planetenradträger 6 wirkt. Das Übersetzungsverhältnis zwischen dem Getriebeeingang 14 und dem Getriebeausgang 19 wird nun durch die Drehrichtung und die Drehgeschwindigkeit des Stellmotors 17, durch Überlagerung des über das Lenkhandrad 18 eingeleiteten Drehwinkels, bestimmt. Ein Planetenradgetriebe 1 der angegebenen Art ist jederzeit auch in anderen Lenkeinrichtungen, z. B. einer mechanischen Lenkeinrichtung ohne Lenkunterstützung, einsetzbar. In contrast to the application shown in FIG. 1, a second gear input 15, 16, here shown as a worm 15 and worm wheel 16, is integrated. The worm wheel 16 is connected to the planet gear carrier 6. Steering handwheel 18, the servomotor 17 and the steering gear 20 are only shown symbolically as blocks. The angle of rotation introduced by the driver into the steering handwheel 18 is initiated via the first transmission input 14 and the sun gear 11. A gearbox output 19 connected in a rotationally fixed manner to the sun gear 12 is connected to the vehicle steering wheels via the steering gear 20. A control unit, not shown, which detects the adjustment of the steering angle and possibly other characteristic values influencing the steering characteristic via sensors, activates the servomotor 17, which acts on the second transmission input 15, 16 and thus on the planet gear carrier 6. The transmission ratio between the transmission input 14 and the transmission output 19 is now determined by the direction of rotation and the speed of rotation of the servomotor 17, by superimposing the angle of rotation introduced via the steering handwheel 18. A planetary gear 1 of the type specified is at any time in other steering devices, for. B. a mechanical steering device without steering assistance, can be used.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2000136937 DE10036937A1 (en) | 2000-07-28 | 2000-07-28 | Backlash-free planetary gear, in particular for an actuating device of a vehicle steering device |
| DE10036937.5 | 2000-07-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2002009998A1 true WO2002009998A1 (en) | 2002-02-07 |
Family
ID=7650615
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2001/008116 Ceased WO2002009998A1 (en) | 2000-07-28 | 2001-07-13 | Actuator for an automotive steering system |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE10036937A1 (en) |
| WO (1) | WO2002009998A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1903254A1 (en) * | 2006-09-25 | 2008-03-26 | Jtekt Corporation | Steering device for vehicle |
| WO2009106222A1 (en) * | 2008-02-26 | 2009-09-03 | Maxon Motor Ag | Play-free planetary gear set with split planet gears which are preloaded by means of spring bars arranged parallel to the planet rotational axis |
| EP1686287A3 (en) * | 2005-01-26 | 2010-01-06 | Jtekt Corporation | Differential gear apparatus |
| WO2016131529A1 (en) * | 2015-02-17 | 2016-08-25 | Renk Aktiengesellschaft | Transmission arrangement |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10239968A1 (en) | 2002-08-30 | 2004-03-04 | Zf Lenksysteme Gmbh | Backlash-free planetary gear |
| DE50309712D1 (en) * | 2002-11-29 | 2008-06-05 | Continental Teves Ag & Co Ohg | VIBRATION AND NOISE EXCESSIVE TRANSMISSION GEARBOX FOR A SLOPING STEERING |
| JP4248960B2 (en) | 2003-07-23 | 2009-04-02 | 株式会社デンソー | Variable transmission ratio steering device |
| JP2006150994A (en) * | 2004-11-25 | 2006-06-15 | Fuji Kiko Co Ltd | Variable steering angle mechanism using differential gear unit |
| DE102005036127A1 (en) | 2005-07-26 | 2007-02-01 | Dr. Fritz Faulhaber Gmbh & Co. Kg | Transmission element for a backlash-free transmission, especially for precision engineering |
| KR100842324B1 (en) * | 2006-01-27 | 2008-07-01 | 주식회사 만도 | Gear ratio convertible steering system of car |
| CN104121335A (en) * | 2013-04-23 | 2014-10-29 | 刘绍全 | Planetary speed reducer with two planetary gears |
| KR101749375B1 (en) | 2013-12-06 | 2017-06-20 | 주식회사 만도 | Planetary Gear Apparatus |
| DE102022106149A1 (en) | 2022-03-16 | 2023-09-21 | Schaeffler Technologies AG & Co. KG | Steering angle limiting unit for steering unit and steering unit with steering angle limiting unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2642496A1 (en) * | 1989-01-10 | 1990-08-03 | Renault | Electrically controlled mechanism with variable step-down gearing |
| RU1798566C (en) * | 1991-04-03 | 1993-02-28 | Могилевский Машиностроительный Институт | Planetary gear |
| US5409431A (en) * | 1993-11-02 | 1995-04-25 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Carrier-less, anti-backlash planetary drive system |
| US5704864A (en) * | 1993-12-27 | 1998-01-06 | Yugen Kaisha Sozoan | Drive unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT189469B (en) * | 1955-11-17 | 1957-04-10 | Me Ra Mechanische Regelanlagen | Backlash-free planetary gear transmission |
| GB1108194A (en) * | 1965-10-26 | 1968-04-03 | Cincinnati Milling Machines Lt | Improvements relating to motion transmission mechanism |
| DE2925833A1 (en) * | 1975-08-29 | 1981-01-15 | Ver Flugtechnische Werke | Play-free drive with parallel perpendicular counter-braced drives - uses existing transfer path shafts as torsion rods, and gear wheel at both ends |
| US4811615A (en) * | 1987-12-14 | 1989-03-14 | Borg-Warner Automotive, Inc. | Mechanism for eliminating gear rattle in a shiftable transmission |
| US5671636A (en) * | 1996-01-24 | 1997-09-30 | Heidelberg Harris Inc. | Method and apparatus for preventing circumferential separation between two gears of a gear train |
| DE19723358B4 (en) * | 1997-06-04 | 2010-07-29 | Robert Bosch Gmbh | Motorized power steering system |
| DE19757433A1 (en) * | 1997-12-23 | 1999-06-24 | Alpha Getriebebau Gmbh | Planet wheel gear with hollow wheel and pinion |
-
2000
- 2000-07-28 DE DE2000136937 patent/DE10036937A1/en not_active Withdrawn
-
2001
- 2001-07-13 WO PCT/EP2001/008116 patent/WO2002009998A1/en not_active Ceased
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2642496A1 (en) * | 1989-01-10 | 1990-08-03 | Renault | Electrically controlled mechanism with variable step-down gearing |
| RU1798566C (en) * | 1991-04-03 | 1993-02-28 | Могилевский Машиностроительный Институт | Planetary gear |
| US5409431A (en) * | 1993-11-02 | 1995-04-25 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Carrier-less, anti-backlash planetary drive system |
| US5704864A (en) * | 1993-12-27 | 1998-01-06 | Yugen Kaisha Sozoan | Drive unit |
Non-Patent Citations (1)
| Title |
|---|
| DATABASE WPI Section PQ Week 199419, Derwent World Patents Index; Class Q64, AN 1994-157771, XP002185174 * |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1686287A3 (en) * | 2005-01-26 | 2010-01-06 | Jtekt Corporation | Differential gear apparatus |
| EP1903254A1 (en) * | 2006-09-25 | 2008-03-26 | Jtekt Corporation | Steering device for vehicle |
| US7699136B2 (en) | 2006-09-25 | 2010-04-20 | Jtekt Corporation | Steering device for vehicle |
| WO2009106222A1 (en) * | 2008-02-26 | 2009-09-03 | Maxon Motor Ag | Play-free planetary gear set with split planet gears which are preloaded by means of spring bars arranged parallel to the planet rotational axis |
| KR101197598B1 (en) | 2008-02-26 | 2012-11-09 | 맥슨 모터 아게 | Play-free planetary gear set with split planet gears which are preloaded by means of spring bars arranged parallel to the planet rotational axis |
| US8313411B2 (en) | 2008-02-26 | 2012-11-20 | Maxon Motor Ag | Backlash-free planetary gear unit with split planet gears, which are preloaded by spring bars arranged parallel to the planetary axis of rotation |
| WO2016131529A1 (en) * | 2015-02-17 | 2016-08-25 | Renk Aktiengesellschaft | Transmission arrangement |
| US10400860B2 (en) | 2015-02-17 | 2019-09-03 | Renk Aktiengesellschaft | Transmission arrangement |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10036937A1 (en) | 2002-02-07 |
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