DE1171692B - Friction gear with several flat friction discs - Google Patents
Friction gear with several flat friction discsInfo
- Publication number
- DE1171692B DE1171692B DES61185A DES0061185A DE1171692B DE 1171692 B DE1171692 B DE 1171692B DE S61185 A DES61185 A DE S61185A DE S0061185 A DES0061185 A DE S0061185A DE 1171692 B DE1171692 B DE 1171692B
- Authority
- DE
- Germany
- Prior art keywords
- friction
- spring
- output shaft
- cam
- pressure
- 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.)
- Pending
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
- F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
- F16H13/10—Means for influencing the pressure between the members
- F16H13/14—Means for influencing the pressure between the members for automatically varying the pressure mechanically
Description
Reibungsgetriebe mit mehreren flachen Reibscheiben Die Erfindung bezieht sich auf ein Reibungsgetriebe mit mehreren flachen Reibscheiben. Eine bekannte Ausbildung eines derartigen Getriebes ist in A b b. 1 dargestellt.Friction Transmission With Multiple Flat Friction Discs The invention relates relies on a friction gear with several flat friction discs. A well-known training such a transmission is in A b b. 1 shown.
Das Antriebsmoment wirkt auf die Antriebswelle 1, und ein System von Zahnrädern 2 und 3, 31 treibt eine oder zwei Antriebsreibscheiben 4,41 an. Eine oder zwei Rollen 5, 51 werden gegen die Antriebs.reibscheiben 4, 41 sowie gegen eine Abtriebsscheibe 6 gedrückt. Eine Abtriebswelle 7 wird durch die Abtriebsscheibe 6 über eine Druckvorrichtung angetrieben, welche den Gegenstand der Erfindung bildet. Die Kraftübertragung von der Antriebswelle 1 bis zu der Abtriebswelle 7 ist gestrichelt eingezeichnet. Je nach der übertragenen Leistung kann das Getriebe mit einer einzigen oder mit zwei Reibscheiben und Reibrollen ausgebildet sein, wie es ebenfalls gestrichelt dargestellt ist.The drive torque acts on the drive shaft 1, and a system of Gears 2 and 3, 31 drive one or two drive friction disks 4.41. One or two rollers 5, 51 are against the drive pulleys 4, 41 as well as against a driven pulley 6 pressed. An output shaft 7 is through the output pulley 6 driven by a printing device which forms the subject of the invention. The power transmission from the drive shaft 1 to the output shaft 7 is shown in dashed lines drawn. Depending on the transmitted power, the transmission can be with a single or be designed with two friction disks and friction rollers, as is also shown in dashed lines is shown.
Bei einem derartigen Reibungsgetriebe ist es wesentlich, daß ein genügender Antriebsdruck zwischen den Reibrollen und den Reibscheiben erzeugt wird, da das geringste Gleiten unter Belastung die Scheiben zerstört. Bisweilen müssen auch Änderungen des widerstehenden Moments im Verhältnis zu dem Antriebsmoment, große Geschwindigkeitsschwankungen usw. berücksichtigt werden.In such a friction transmission, it is essential that a sufficient Driving pressure is generated between the friction rollers and the friction disks, as the The slightest sliding under load destroys the panes. Sometimes changes also need to be made of the resisting torque in relation to the drive torque, large speed fluctuations etc. are taken into account.
Es ist bekannt, hierfür zwischen der Abtriebsscheibe 6 und der der Abtriebswelle 7 eine doppeltwirkende Druckvorrichtung anzuordnen. Diese Vorichtung enthält ein oder mehrere elastische Glieder, welche z. B. durch Tellerfedern oder auch eine Schraubenfeder großen Querschnitts 8 gebildet werden, welche einen starken Druck ausüben können. Der von der Feder in Richtung auf die Scheiben und Rollen ausgeübte Druck ist dauernd vorhanden und erzeugt den zur Erzeugung der Reibung erforderlichen Druck, wenn das widerstehende Moment nicht vorhanden ist oder nur einen geringen Wert hat.It is known to do this between the output pulley 6 and the Output shaft 7 to arrange a double-acting pressure device. This device contains one or more elastic members which, for. B. by disc springs or also a coil spring of large cross-section 8 can be formed, which has a strong Be able to apply pressure. The one from the spring towards the washers and rollers The pressure exerted is always present and generates the force required to generate the friction required pressure when the resisting moment is absent or only has little value.
Ferner enthält die Druckvorrichtung Einrichtungen, welche bei einer Verschiedenheit des Antriebsmoments und des widerstehenden Moments eine gegenseitige Verdrehung ausführen und mit Kurvenbahnen oder anderen Einrichtungen zur gegenseitigen Berührung versehen sind, welche so ausgebildet sind, daß sie diese gegenseitige Verdrehung in einen Axialschub umwandeln, welcher selbsttätig zu dem widerstehenden Moment proportional ist und in Richtung auf die Scheiben und Rollen wirkt, um zwischen diesen für beliebige Werte des widerstehenden Moments einen Reibungsschluß ohne jedes Gleiten herzustellen. Diese Einrichtungen werden durch die Teile 9 und 10 gebildet, welche unmittelbar oder mittelbar mit der Abtriebsscheibe 6 drehfest, aber gleitend verschieblich mit der Abtriebswelle 7 verbunden sind, wie dies schematisch in A b b. 1 und 2 dargestellt ist.Furthermore, the printing device contains devices which are at a The driving torque and the resisting torque are mutually different Carry out rotation and with curved tracks or other devices for mutual Contact are provided, which are designed so that they are mutual Convert rotation into axial thrust, which automatically becomes the resisting Moment is proportional and acts towards between the discs and rollers this for any values of the resisting torque a frictional engagement without to make every slide. These facilities are represented by parts 9 and 10 formed, which directly or indirectly rotatably with the output pulley 6, but are slidably connected to the output shaft 7, as shown schematically in A b b. 1 and 2 is shown.
Zur Umwandlung der gegenseitigen Verdrehung der Teile 9 und 10 in einen Axialschub weisen diese je zwei Paare von entgegengesetzten Kurvenbahnen 91-92 bzw. 101-102 auf, wobei jede Kurvenbahn ein Viertel des Ganges einer Flanke eines Gewindes mit quadratischem Querschnitt ist. Je nach der Richtung der gegenseitigen Verdrehung der Teile 9 und 10 halten stets zwei Kurvenbahnen eines jeden Teils die Berührung auf einem wesentlichen Abschnitt ihrer Oberfläche aufrecht. Bei den bekannten Vorrichtungen dieser Art haben die Kurvenbahnen gewöhnlich eine geringe Steigung oder eine geringe Ganghöhe, um die Drehmomentschwankungen mit einer hinreichenden Empfindlichkeit in einen Axialschub umzuwandeln. Andererseits muß die Ausbildung so getroffen sein, daß eine Umkehrbarkeit der gegenseitigen Verdrehung der Teile 9 und 10 zulässig ist. Wenn die Steigung der Kurvenbahnen zu groß ist, ist die selbsttätige Änderung des Axialschubes insbesondere bei großen Geschwindigkeiten schlecht und folgt nicht allen Änderungen des widerstehenden Moments.To convert the mutual rotation of parts 9 and 10 into an axial thrust, they each have two pairs of opposing cam tracks 91-92 and 101-102, each cam track being a quarter of the turn of a flank of a thread with a square cross-section. Depending on the direction of mutual rotation of the parts 9 and 10 , two cam tracks of each part always maintain contact on a substantial portion of its surface. In the known devices of this type, the cam tracks usually have a low pitch or a low pitch in order to convert the torque fluctuations into an axial thrust with sufficient sensitivity. On the other hand, the design must be such that reversibility of the mutual rotation of parts 9 and 10 is permissible. If the slope of the cam tracks is too great, the automatic change in the axial thrust is poor, especially at high speeds, and does not follow all changes in the resisting torque.
Anders ausgedrückt: Bei Kurvenbahnen 91-92 und 101-102 geringer Steigung, wie sie im allgemeinen zur Berücksichtigung der ihre Umkehrbarkeit zulassenden Grenze ausgeführt werden, erhält man gute Axialdrücke bei großen Geschwindigkeiten, während bei kleinen Geschwindigkeiten ein übermäßiger Schub und in beiden Fällen eine schlechte Umkehrbarkeit vorhanden ist.In other words: with curved paths 91-92 and 101-102 with a low gradient, like them in general to take into account their reversibility permissible limit, good axial pressures are obtained at high speeds, while at low speeds an excessive thrust and in both cases there is poor reversibility.
Bei der dargestellten bekannten Ausführung sind die durch die Schraubenfeder 8 bzw. durch die Kurvenbahnen der Teile 9 und 10 erzeugten Axialschübe in Reihe geschaltet, was durch eine Rückwirkung des durch die Teile 9 und 10 erzeugten Schubes in entgegengesetzter Richtung den erheblichen Schub der Schraubenfeder 8 neutralisiert. Diese Feder ist nämlich zwischen dem Boden der Bohrung der Welle 7 und dem Teil 10 angeordnet. Aus A b b. 2 geht hervor, daß bei einer großen Änderung des widerstehenden Moments der durch die Kurvenbahnen 91-92 und 101-102 erzeugte Axialschub nicht nur in Richtung der Scheiben und Rollen wirkt, sondern auch eine Rückwirkung in entgegengesetzter Richtung gemäß dem Pfeil R erzeugt, welche den starken Schub F der Feder 8 verringert und häufig aufhebt.In the known embodiment shown, the axial thrusts generated by the helical spring 8 or the cam tracks of the parts 9 and 10 are connected in series, which neutralizes the considerable thrust of the helical spring 8 by a reaction of the thrust generated by the parts 9 and 10 in the opposite direction . This spring is namely arranged between the bottom of the bore of the shaft 7 and the part 10 . From A b b. 2 shows that with a large change in the resisting moment, the axial thrust generated by the cam tracks 91-92 and 101-102 not only acts in the direction of the disks and rollers, but also generates a reaction in the opposite direction according to the arrow R, which causes the strong thrust F of the spring 8 is reduced and often cancels.
Es ist noch eine Aasführung bekannt, bei welcher die Feder und die eine Verdrehung in einen Axialschub umwandelnde Kurvenbahnanordnung nicht in Reihe, sondern parallel geschaltet sind. Bei dieser bekannten Vorrichtung sucht jedoch die Feder die beiden Teile der Kurvenbahnanordnung voneinander zu trennen, wodurch deren Wirkungsweise beeinträchtigt wird, da nun nicht mehr die ganze gegenseitige Verdrehung zur Erzeugung eines Axialschubes ausgenutzt wird, sondern teilweise zur Aufholung des Spiels dient.Another carrion is known in which the spring and the a cam track arrangement that converts a rotation into an axial thrust is not in series, but are connected in parallel. In this known device, however, seeks the spring to separate the two parts of the cam assembly from each other, whereby whose mode of action is impaired, as now no longer the whole of the mutual Rotation is used to generate an axial thrust, but partly to The purpose of catching up is the game.
Die obigen Nachteile werden bei einem Reibungsgetriebe mit mehreren flachen Reibscheiben, die über radial verschiebbare Druckrollen miteinander im Eingriff stehen, und mit einem in einer Bohrung der Abtriebswelle angeordneten Drucksystem mit einer Feder und einer eine gegenseitige Verdrehung in einen Axialschub umwandelnden Kurvenbahnanordnung, von der das eine DruckgUed mit der Abtriebswelle und das andere- mit der Abtriebsscheibe drehfest verbunden ist,' vermieden, welches erfindungsgemäß dadurch gekennzeichnet ist, daß sich die Feder einerseits an einer mit der Abtriebswelle starr verbundenen Auflagefläche und andererseits über ein Axiallager an einer Auflagefläche des von den Windungen der Feder umgebenen, mit der Abtriebsscheibe verbundenen Druckgliedes abstützt.The above disadvantages are in a friction transmission with multiple flat friction disks which engage with one another via radially displaceable pressure rollers stand, and with a pressure system arranged in a bore in the output shaft with one spring and one that converts a mutual twist into an axial thrust Cam track arrangement, one of which is printed with the output shaft and the other is non-rotatably connected to the output disk, 'avoided which according to the invention is characterized in that the spring is on the one hand on one with the output shaft rigidly connected support surface and on the other hand via an axial bearing on a support surface of the pressure member, which is surrounded by the windings of the spring and connected to the driven pulley supports.
Durch diese Ausbildung wird zunächst der Vorteil erzielt, daß entgegen den bekannten Ausführungen der gesamte sowohl von der Feder als auch von der Kurvenbahnanordnung erzeugte Axialschub voll zur Wirkung kommt. Ferner wird durch die Anordnung der Feder und eines Axiallagers in dem Ringraum zwischen dem mit der Abtriebsscheibe verbundenen Druckglied der Kurvenbahnanordnung und der Bohrung der Abtriebswelle eine besonders geschlossene zweckmäßige raumsparende Ausbildung erzielt, welche unter anderem ermöglicht, den Kurvenbahnen einen verhältnismäßig kleinen Durchmesser zu geben, wodurch das Arbeiten der Kurvenbahnanordnung infolge der Verkleinerung der auftretenden Hebelarme verbessert wird.By this training the advantage is first achieved that contrary the known designs of the entire both of the spring and of the cam arrangement generated axial thrust comes fully into effect. Furthermore, the arrangement of the Spring and a thrust bearing in the annular space between the one with the output pulley connected pressure member of the cam arrangement and the bore of the output shaft a particularly closed expedient space-saving training achieved which among other things, enables the cam tracks to have a relatively small diameter to give, whereby the working of the cam arrangement as a result of the downsizing the occurring lever arms is improved.
Gemäß einer weiteren Ausbildung der Erfindung liegt die Steigung der Kurvenbahnen der Kurvenbahnanordnung zwischen 25 und 35°, wodurch gleichzeitig die gewünschte Ansprechempfindlichkeit als auch die Umkehrbarkeit der Arbeitsweise der Kurvenbahnanordnung gewährleistet werden.According to a further embodiment of the invention, the slope of the Curved paths of the curved path arrangement between 25 and 35 °, whereby at the same time the desired responsiveness as well as the reversibility of the operation of the Cam track arrangement can be guaranteed.
Die Erfindung ist unter Bezugnahme auf die Zeichnung beispielshalber erläutert: A b b. 1 und 2 zeigen schematisch eine bekannte Ausbildung eines Reibungsgetriebes mit einer oder zwei Antriebsscheiben und einer Druckvorrichtung, deren beide in Reihe geschaltete Glieder durch eine Schraubenfeder großen Querschnitts und eine Kurvenbahnanordnung gebildet werden, wobei die beiden Abbildungen zwei verschiedene Betriebszustände darstellen; A b b. 3 und 4 zeigen schematisch eine erfindungsgemäße Druckvorrichtung in zwei verschiedenen, ververschiedenen Werten des widerstehenden Moments entsprechenden Betriebszuständen; A b b. 5 und 6 sind schaubildliche Ansichten der Enden der Kurvenbahnen der Druckglieder des erfindungsgemäßen Getriebes; A b b. 7 und 8 zeigen beispielshalber zwei praktische Ausführungsformen der erfindungsgemäßen Ausbildung für verschiedene Arten von Reibungsgetrieben mit zwei bzw. einer Antriebsscheibe.The invention is given by way of example with reference to the drawing explained: A b b. 1 and 2 show schematically a known design of a friction gear with one or two drive pulleys and a pressure device, both of which are in Series connected links by a coil spring of large cross-section and a Cam track arrangement are formed, the two figures being two different Represent operating states; A b b. 3 and 4 schematically show an inventive Pressure device in two different, different values of the resisting Operating conditions corresponding to the moment; A b b. 5 and 6 are perspective views the ends of the cam tracks of the pressure members of the transmission according to the invention; Away b. 7 and 8 show, by way of example, two practical embodiments of the invention Training for different types of friction gears with two or one drive pulley.
Auf A b b. 3 und 4 wird das elastische Glied zur Erzeugung eines ständigen Drucks durch eine Schraubenfeder 11 starken Querschnitts gebildet, welche n-it einer gewissen Vorspannung zwischen einer Auflagefläche 71 in der Bohrung der Antriebswelle 7 und einer Auflagefläche 123 des unmittelbar oder mittelbar mit der Abtriebsscheibe 6 verbundenen Druckgliedes 12 angeordnet ist. Abweichend von der dargestellten Ausführung kann die Feder 11 auch unmittelbar auf die Scheibe 6 drücken. Zwischen der Feder 11 und der Auflagefläche 123 ist ein Axiallager 13 angeordnet, welches geringe gegenseitige Verdrehungen zwischen diesen beiden Teilen ermöglicht.On A b b. 3 and 4, the elastic member for generating constant pressure is formed by a helical spring 11 with a strong cross-section, which n-it a certain bias between a bearing surface 71 in the bore of the drive shaft 7 and a bearing surface 123 of the directly or indirectly connected to the driven pulley 6 Pressure member 12 is arranged. In a departure from the embodiment shown, the spring 11 can also press directly on the disk 6. An axial bearing 13 is arranged between the spring 11 and the bearing surface 123 , which allows small mutual rotations between these two parts.
Infolge dieser Anordnung der Feder ist das Druckglied 12 verlängert und weist Kurvenbahnen 121-122 vor der Auflagefläche 71 auf. Diese Kurvenbahnen wirken mit Kurvenbahnen 141-142 des zweiten Druckgliedes 14 zusammen, welches an dem Boden der Bohrung der Abtriebswelle 7 angeordnet ist. Das Glied 14 ist mit der Welle 7 drehfest, aber gleitend verschieblich z. B. durch Keile 143 verbunden, wobei die Bewegung des Gliedes 14 in Richtung auf den Boden der Bohrung in an sich bekannter Weise durch einen Anschlag 15 einer Vorrichtung zur selbsttätigen Aufholung des Spiels begrenzt wird.As a result of this arrangement of the spring, the pressure member 12 is lengthened and has cam tracks 121-122 in front of the support surface 71. These cam tracks interact with cam tracks 141-142 of the second pressure member 14 , which is arranged on the bottom of the bore of the output shaft 7. The member 14 is rotationally fixed to the shaft 7 , but slidably displaceable z. B. connected by wedges 143, the movement of the member 14 in the direction of the bottom of the bore is limited in a known manner by a stop 15 of a device for automatically catching up the game.
Die Kurvenbahnen 121-122 und 141-142 haben eine verhältnismäßig große, zwischen 25 und 35° liegende Steigung. Hierdurch wird der Vorteil einer sehr guten Umkehrbarkeit der gegenseitigen Verdrehungen der Teile 12 und 14 und einer großen Empfindlichkeit für Schwankungen des widerstehenden Moments bei mittleren und kleinen Geschwindigkeiten erzielt. Der bei den bekannten Vorrichtungen austretende Nachteil einer ungenügenden Empfindlichkeit derartiger Kurvenbahnen großer Steigung bei großen Geschwindigkeiten wird durch den erfindungsgemäßen Einbau der Feder 11 beseitigt, deren Schub voll in Richtung auf die Reibscheiben und Reibrollen wirksam wird. Dieser zusätzliche Schub, welcher zu dem von den Rückwirkungen der Kurvenbahnen 121-122 und 141-142 erzeugten Schub hinzutritt, ist, selbst wenn dieser letztere Schub gering ist, stets ausreichend, um reichlich den erforderlichen Druck zwischen den Reibscheiben und Reibrollen zu erzeugen, wie dies in A b b. 3 schematisch dargestellt ist.The cam tracks 121-122 and 141-142 have a relatively large, incline between 25 and 35 °. This has the advantage of being a very good one Reversibility of the mutual rotations of parts 12 and 14 and a large one Sensitivity to fluctuations in the resisting moment in medium and small Speeds achieved. The disadvantage emerging from the known devices insufficient sensitivity of such curved paths with a large gradient and a large one Velocities are eliminated by the installation of the spring 11 according to the invention, whose thrust is fully effective in the direction of the friction disks and friction rollers. This additional thrust, which is added to that of the repercussions of the cam tracks 121-122 and 141-142 generated thrust is added, even if this latter thrust is small is, always sufficient, to amply the required pressure between the Friction disks and to generate friction rollers, as shown in A b b. 3 is shown schematically.
Bei mittleren und kleinen Geschwindigkeiten tritt der Hub der Feder 11 zu dem durch die Kurvenbahnen 121-12 und 141-14z erzeugten bedeutenden Schub hinzu, wie dies in A b b. 4 dargestellt ist, wodurch ein noch größerer Druck zwischen den Reibrollen und Reibscheiben entsteht.The stroke of the spring occurs at medium and low speeds 11 to the significant thrust generated by the cam tracks 121-12 and 141-14z added, as in A b b. 4 is shown, creating an even greater pressure between the friction rollers and friction disks.
Aus dem Vergleich der A b b. 3 und 4 mit A b b. 1 und 2 geht die durch die erfindungsgemäße Ausbildung erzielte Verkleinerung des Durchmessers der Kurvenbahnen deutlich hervor.From the comparison of A b b. 3 and 4 with A b b. 1 and 2 goes through the inventive training achieved reduction of the diameter of the cam tracks clearly.
Ferner ist zu bemerken, daß bei der erfindungsgemäßen Ausbildung entgegen der eingangs angeführten bekannten Vorrichtung die Feder nicht die Kurvenbahnen voneinander zu trennen sucht, welche stets miteinander in Berührung bleiben und so auf einem großen Teil ihrer Oberflächen arbeiten, was bei den von ihnen ausgeübten starken Drücken wesentlich ist.It should also be noted that contrary to the training according to the invention of the known device mentioned above, the spring not the cam tracks seeks to separate from each other which always stay in contact and so work on a large part of their surfaces what happens with those exercised by them heavy pressing is essential.
Eine erste praktische Anwendung der erfindungsgemäßen Druckvorrichtung ist auf A b b. 7 für ein Getriebe mit doppelter Antriebsscheibe und Antriebsrollen dargestellt. In dieser Abbildung finden sich die oben beschriebeenen Teile wieder. Ein Nadellager 16 ist in die in der Bohrung der Abtriebswelle 7 angebrachte Auflagefläche 71 eingesetzt, welche nur die Verdrehung des Druckgliedes 12 erleichtern soll. Das Axiallager 13 erfüllt die unter Bezugnahme auf A b b. 3 und 4 erläuterte Aufgabe.A first practical application of the printing device according to the invention is on A b b. 7 for a gear with double drive pulley and drive rollers shown. The parts described above can be found in this figure. A needle bearing 16 is in the bearing surface provided in the bore of the output shaft 7 71 is used, which is only intended to facilitate the rotation of the pressure member 12. That Axial bearing 13 fulfills the requirements with reference to A b b. 3 and 4 explained task.
Eine zweite Ausführungsform und praktische Anwendung der erfindungsgemäßen Druckvorrichtung ist in Abb. 8 für ein Getriebe mit einer Antriebsscheibe und Antriebsrolle dargestellt. Auch auf dieser Abbildung finden sich die Teile der erfindungsgemäßen Anordnung wieder.A second embodiment and practical application of the invention Printing device is shown in Fig. 8 for a transmission with a drive pulley and drive roller shown. The parts of the invention can also be found on this figure Arrangement again.
Schließlich ist noch zu bemerken, daß gegebenenfalls bei einer erfindungsgemäßen Anordnung die Kurvenbahnen in Form von Gewindeflanken durch mit Ausnehmungen zusammenwirkende Kugeln ersetzt werden können.Finally, it should be noted that, if necessary, in an inventive Arrangement of the cam tracks in the form of thread flanks by interacting with recesses Balls can be replaced.
Claims (3)
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FR1171692X | 1958-01-09 |
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US11174922B2 (en) | 2019-02-26 | 2021-11-16 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
US11215268B2 (en) | 2018-11-06 | 2022-01-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
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