DE3924548A1 - Four shaft gear with one stationary housing at shaft - has three rotary shafts with planetary wheels and adjusting gear - Google Patents

Four shaft gear with one stationary housing at shaft - has three rotary shafts with planetary wheels and adjusting gear

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Publication number
DE3924548A1
DE3924548A1 DE19893924548 DE3924548A DE3924548A1 DE 3924548 A1 DE3924548 A1 DE 3924548A1 DE 19893924548 DE19893924548 DE 19893924548 DE 3924548 A DE3924548 A DE 3924548A DE 3924548 A1 DE3924548 A1 DE 3924548A1
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Germany
Prior art keywords
shaft
gear
planetary gear
planetary
shafts
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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.)
Withdrawn
Application number
DE19893924548
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German (de)
Inventor
Peter Graf Von Ingelheim
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Individual
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Individual
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Filing date
Publication date
Priority claimed from PCT/DE1989/000189 external-priority patent/WO1989009351A1/en
Application filed by Individual filed Critical Individual
Priority to DE19893924548 priority Critical patent/DE3924548A1/en
Priority to DE19893927783 priority patent/DE3927783A1/en
Publication of DE3924548A1 publication Critical patent/DE3924548A1/en
Withdrawn legal-status Critical Current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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • 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
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/104—Power split variators with one end of the CVT connected or connectable to two or more differentials
    • 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

Abstract

The 4-shaft gear has a shaft formed by a stationary housing, with three shafts which rotate (1,4,11). Alternatively, the 4-shaft gear consists of five shafts three of which are positioned in a planetary gear. One shaft is connected to the planetary wheels of a further planetary gear; the other shaft is joined to one shaft of a continuously adjustable gear (28), and its third shaft if joined to the drive and driven shaft of the operating line. The gear joins the third planetary set of a planetary gear positioned between a drive and driven shaft engaging with the two other planetary sets, to a shaft of an adjusting gear, and the other shaft of the adjusting gear drives the flange of the planetary gear. USE/ADVANTAGE - The type of gear is especially suitable for incorporating in continuously adjustable gears.

Description

Die Erfindung bezieht sich auf ein 4-Wellen-Umlaufgetriebe. Derartige Getriebe sind in der Regel Zahnradgetriebe bzw. Zahnradumlaufgetriebe. Es gibt aber auch andere Umlaufgetriebe, wie z. B. Kurvengetriebe.The invention relates to a 4-shaft epicyclic gear. Such transmissions are usually gear transmissions or planetary gear. But there are other epicyclic gears, such as B. cam gear.

Nach Müller, H. W.; Umlaufgetriebe; in: Dubbel, Taschenbuch für den Maschinenbau; 16. Aufl.; Springer-Verlag Heidelberg 1987; gilt für alle Umlaufgetriebe die GrundgleichungAccording to Müller, H. W .; Epicyclic gear; in: Dubbel, paperback for mechanical engineering; 16th ed .; Springer-Verlag Heidelberg 1987; the basic equation applies to all epicyclic gears

(1.1) n 1-n 2*i 0-nS* (1-i 0)=0
bzw.
(1.1a) (n 1-nS)/(n 2-nS) = i 0(1.1) n 1- n 2 * i 0- nS * (1- i 0) = 0
respectively.
(1.1a) (n 1- nS) / (n 2- nS) = i 0

mit
n 1=Drehzahl der Welle 1
n 2=Drehzahl der Welle 2
nS=Drehzahl der Welle S bzw. des Steges
i 0=Bauverhältnis des GetriebesWith
n 1 = speed of shaft 1
n 2 = speed of shaft 2
nS = speed of shaft S or of the web
i 0 = construction ratio of the gearbox

Die Erfindung beinhaltet 4-Wellen-Getriebe, bei denen eine Welle vom Gehäuse gebildet wird und bei dem für die drei anderen Wellen eine andere Grundgleichung erreicht wird. In Verbindung mit konventionellen Planetengetrieben und stufenlos verstellbaren Getrieben werden damit stufenlos verstellbare Getriebe mit Leistungsverzweigung möglich, bei denen nur eine geringe Leistung über das Verstellgetriebe geht.The invention includes 4-shaft gear, in which one Shaft is formed by the case and for the other three Waves another basic equation is reached. In Connection with conventional planetary gears and stepless adjustable gears are infinitely adjustable Gearboxes with power split possible where only a small amount of power goes through the adjustment gear.

Anhand von Abb. 1 soll die neue Grundgleichung erläutert werden.
Abb. 1 zeigt ein Getriebe mit rotatorischer und oszillierender Bewegung. Eine Antriebswelle 1 hat zwei oszillierende (schräg liegende), geschlossene Kurvenzüge 2, 3 am Umfang. Diese Kurvenzüge können z. B. schräg liegende Wälz- oder Gleitlager sein.
Die Abtriebswelle 4 liegt rohrförmig um die Antriebswelle 1 und hat axiale Schlitze 5 in denen Eingriffskörper 6 hin- und herschiebbar sind.
Die Eingriffskörper 6 greifen in die Kurven 2, 3 und in einen kreisförmigen Nut 7 oder ein ringförmiges Wälz- oder Gleitlager in einer ringförmigen Hülse 8, die rohrförmig um An- und Abtriebswelle liegt. Die Hülse 8 ist in axialen Schlitzen 9 des Gehäuses 10 hin- und herschiebbar. Die Hin- und Herbewegung der Hülse wird genutzt, eine dritte Welle 11 zu drehen.
Man erkennt zunächst, daß für das in Abb. 1 gezeigte Getriebe die Drehzahlgleichung die Form annimmtThe new basic equation will be explained using Fig. 1.
Fig. 1 shows a gear with rotary and oscillating movement. A drive shaft 1 has two oscillating (inclined), closed curves 2, 3 on the circumference. These curves can e.g. B. be inclined roller or plain bearings.
The output shaft 4 is tubular around the drive shaft 1 and has axial slots 5 in which engagement bodies 6 can be pushed back and forth.
The engaging bodies 6 engage in the curves 2, 3 and in a circular groove 7 or an annular roller or slide bearing in an annular sleeve 8 which is tubular around the input and output shaft. The sleeve 8 can be pushed back and forth in axial slots 9 of the housing 10 . The reciprocating movement of the sleeve is used to rotate a third shaft 11 .
It can first be seen that the speed equation takes the form of the gearbox shown in Fig. 1

(1.2) n 1-n 4=z*n 11; z = beliebige rationale Zahl;(1.2) n 1- n 4 = z * n 11; z = any rational number;

Diese Gleichung ist grundsätzlich von der Gleichung (1.1a) verschieden, wie man sich folgendermaßen klarmacht: This equation is fundamentally different from equation (1.1a) different, how to make yourself clear as follows:  

Wenn man versucht im Nenner von Gleichung (1.1a) nS = 0 zu setzen, um Gleichung (1.2) zu realisieren, dann verschwindet nS auch im Zähler und man hat nurmehr ein 2-Wellen-Getriebe. Daher ist Gleichung (1.2) grundsätzlich von (1.1a) verschieden.
Wenn Mi das Drehmoment der Welle i ist und M 10 das vom Gehäuse aufgenommene Stützmoment, dann gelten die Momentengleichungen:If you try to set nS = 0 in the denominator of equation (1.1a) to implement equation (1.2), then nS also disappears in the numerator and you only have a 2-shaft gearbox. Therefore, equation (1.2) is fundamentally different from (1.1a).
If Mi is the torque of shaft i and M 10 is the support torque absorbed by the housing, then the torque equations apply:

M 1+M 4+M 10+M 11=0;
M 1+M 4=0;
M 10+M 11=0;
M 11=-z*M 1; M 1+ M 4+ M 10+ M 11 = 0;
M 1+ M 4 = 0;
M 10+ M 11 = 0;
M 11 = - z * M 1;

Damit fließt über die einzelnen Wellen die Leistung:The power flows over the individual waves:

P 1/(2*pi) = n 1*M 1
P 4/(2*pi) = n 4*M 4=-n 4*M 1
P 11/(2*pi) = n 11*M 11=-(n 1-n 4)*z*M 1/z = (n 4-n 1)*M 1;
P 10/(2*pi) = 0*M 10=0; P 1 / (2 * pi) = n 1 * M 1
P 4 / (2 * pi) = n 4 * M 4 = - n 4 * M 1
P 11 / (2 * pi) = n 11 * M 11 = - (n 1- n 4) * z * M 1 / z = (n 4- n 1) * M 1;
P 10 / (2 * pi) = 0 * M 10 = 0;

und damit ist auch die Leistungsgleichgewichtsgleichung:and thus the power balance equation is:

P 1+P 4+P 10+P 11=0; P 1+ P 4+ P 10+ P 11 = 0;

erfüllt.Fulfills.

Die Gleichung (1.2) ist aber nicht nur mit Hilfe von neuartigen Getrieben, sondern auch mit Zahnradumlaufgetrieben realisierbar.Equation (1.2) is not only with the help of novel ones Gearboxes, but also with epicyclic gearboxes realizable.

Abb. 2 dient dem Verständnis des stufenlosen Getriebes mit Leistungsverzweigung, welches ausschließlich mit Zahnradgetrieben realisiert wird.
Eine Antriebswelle 20 vom Motor treibt über ein Wendegetriebe 22 ein Zwischenrad 23. Das Zwischenrad 23 dreht mit der Drehzahl der Antriebswelle, aber entgegengesetzt zu dieser. Dieses Zwischenrad bildet die eine Abtriebswelle eines Differentials 24, dessen Käfig 25 über ein Zahnrad 26 mit einem hydrostatischen Verstellpumpe-Motor 28 verbunden ist. Fig. 2 is used to understand the continuously variable transmission with power split, which is only realized with gear drives.
A drive shaft 20 from the motor drives an idler gear 23 via a reversing gear 22 . The intermediate gear 23 rotates at the speed of the drive shaft, but opposite to it. This intermediate wheel forms the one output shaft of a differential 24 , the cage 25 of which is connected to a hydrostatic variable displacement pump motor 28 via a gear wheel 26 .

Die Antriebswelle 20 treibt mit dem Sonnenrad 40 die Planetenräder 30 eines Planetengetriebes 31 und über das Sonnenrad 42 die Abtriebswelle. Der Steg S wird über das Zahnrad 35 von einem zweiten Verstellpumpenmotor 36 getrieben. Dieses Planetengetriebe 31 hat die Grundgleichung:The drive shaft 20 drives the planet gears 30 of a planetary gear 31 with the sun gear 40 and the output shaft via the sun gear 42 . The web S is driven via the gear 35 by a second variable displacement pump motor 36 . This planetary gear 31 has the basic equation:

(n 40-ns)/(n 42-nS) = 4 bzw. n 40-4*n 42-(1-4)*nS 0: (n 40- ns) / (n 42- nS) = 4 or n 40-4 * n 42- (1-4) * nS 0:

mit
n 40=Drehzahl der Antriebswelle
n 42=Drehzahl der Abtriebswelle
nS = Drehzahl des StegesWith
n 40 = speed of the drive shaft
n 42 = speed of the output shaft
nS = speed of the web

Ein dritter Planetensatz 32 treibt den zweiten Abtriebsstrang 33 des Differentials 24.A third planetary gear set 32 drives the second drive train 33 of the differential 24 .

Die beiden hydrostatischen Verstellaggregate 28, 36 fördern zueinander, bilden also ein hydrostatisches Verstellgetriebe.The two hydrostatic adjustment units 28, 36 convey to each other, thus forming a hydrostatic adjustment gear.

Zunächst betrachte man die beiden "Differentiale" 22, 24. Für das erste Differential 22 gilt die GrundgleichungFirst, consider the two "differentials" 22, 24 . The basic equation applies to the first differential 22

(n 20-0)/(n 23-0)=-1; (n 20-0) / (n 23-0) = - 1;

und für das zweite Differential 24 gilt die Grundgleichungand the basic equation applies to the second differential 24

(n 23-n 25)/(n 33-n 25)=-1; (n 23- n 25) / (n 33- n 25) = - 1;

Daraus wirdThis becomes

(n 20+n 25)/(n 33-n 25)=1; (n 20+ n 25) / (n 33- n 25) = 1;

oder (n 33-n 20)/n 25=2;or (n 33- n 20) / n 25 = 2;

Diese letzte Form entspricht aber genau der Gleichung (1.2).This last form corresponds exactly to equation (1.2).

Für n 20=n 33 ist n 25=0. Das heißt, dann fließt keine Leistung über das Hydraulikgetriebe.For n 20 = n 33, n 25 = 0. This means that no power flows through the hydraulic transmission.

Zur Berechnung des Getriebes werden zunächst folgende Größen definiert:The following parameters are used to calculate the gearbox Are defined:

i 0=Bauverhältnis des Planetengetriebes (=4)
i = n 20/n 21=n 40/n 42=M 21/M 20=M 42/M 40= momentane Getriebeübersetzung
M 32=über den Planetenantrieb eingebrachtes Differenzmoment= -M 38-M 30 i 0 = construction ratio of the planetary gear (= 4)
i = n 20 / n 21 = n 40 / n 42 = M 21 / M 20 = M 42 / M 40 = current gear ratio
M 32 = differential torque introduced via the planetary drive = - M 38- M 30

Für dieses Getriebe gilt:The following applies to this gearbox:

nS = (i 0*n 42-n 40)/(i 0-1)=(((i 0/i)-1)/(i 0-1))*n 40;
n 42=(i 0/(i 0-1))*((i-1)/i) *(r 40/r 30)*n 40;
MS = (i-1)*M 40;
M 42=((i/i 0)-1)*(r 30/r 40)*M 40; nS = (i 0 * n 42- n 40) / (i 0-1) = (((i 0 / i) -1) / (i 0-1)) * n 40;
n 42 = (i 0 / (i 0-1)) * ((i -1) / i) * (r 40 / r 30) * n 40;
MS = (i -1) * M 40;
M 42 = ((i / i 0) -1) * (r 30 / r 40) * M 40;

Über den Stegantrieb bzw. das zweite Hydraulikaggregat 36 fließt somit die normierte Leistung:The standardized power therefore flows via the web drive or the second hydraulic unit 36 :

PS/(2*pi) = MS *nS = ((i-1)*((i 0/i)-1)/(i 0-1))*M 40*n 40; PS / (2 * pi) = MS * nS = ((i -1) * ((i 0 / i) -1) / (i 0-1)) * M 40 * n 40;

Über das erste Hydraulikaggregat 28 fließt die normierte Leistung:The standardized power flows via the first hydraulic unit 28 :

P 32/(2*pi) = M 32*n 32=
((i/i 0)-1)*(1-1/i) *(i 0/(i 0-1))*(r 30/r 40)*(r 40/r 30)*n 40*M 40=
-((i-1)*((i 0/i) -1)/(i 0-1)*M 40*n 40; P 32 / (2 * pi) = M 32 * n 32 =
((i / i 0) -1) * (1-1 / i) * ( i 0 / (i 0-1)) * (r 30 / r 40) * (r 40 / r 30) * n 40 * M 40 =
- ((i -1) * ((i 0 / i) -1) / (i 0-1) * M 40 * n 40;

Damit fließt über die beiden Hydraulikaggregate stets die gleiche Leistung.So that always flows through the two hydraulic units same performance.

Man erkennt, daß für i = 1 und i = i 0 der Leistungsfluß ausschließlich über das Zahnradgetriebe geht, da dann eines der beiden Hydraulikaggregate steht.It can be seen that for i = 1 and i = i 0 the power flow is exclusively via the gear transmission, since then one of the two hydraulic units is stopped.

In den Zwischenbereichen ist der Leistungsfluß über die Hydraulik ebenfalls gering.
Er erreicht sein Maximum fürIn the intermediate areas, the power flow via the hydraulics is also low.
It reaches its maximum for

i = (i 0)o,5; i = (i 0) 0.5 ;

und nimmt dort den Wert an:and takes the value there:

P 32/(2*pi) = ((i 0)0,5-1)/((i 0)0,5+1))*M 40*n 40; P 32 / (2 * pi) = ((i 0) 0.5 -1) / ((i 0) 0.5 +1)) * M 40 * n 40;

Ein derartiges Verzweigungsgetriebe ermöglicht einen sehr hohen Getriebewirkungsgrad.Such a branching gear enables a very high gear efficiency.

In Abb. 3 ist ein Diagramm für die Wirkungsgradkurven des Getriebes gezeigt.
Die Wirkungsgradkurven der beiden Hydraulikaggregate über dem Verstellbereich des Getriebes sind gezeigt und daraus ist der Wirkungsgrad H des Hydraulikgetriebes hergeleitet. Zum Vergleich ist darunter der Leistungsfluß über das Hydraulikgetriebe als Funktion des Übersetzungsverhältnisses des Getriebes gezeigt.
Man erkennt, daß der Leistungsfluß über das Hydraulikgetriebe dann groß ist, wenn der Wirkungsgrad H des Hydraulikgetriebes hoch ist.
Der Wirkungsgrad G des Gesamtgetriebes errechnet sich nach der Formel: Fig. 3 shows a diagram for the efficiency curves of the transmission.
The efficiency curves of the two hydraulic units over the adjustment range of the transmission are shown and from this the efficiency H of the hydraulic transmission is derived. For comparison, the power flow via the hydraulic transmission as a function of the transmission ratio of the transmission is shown below.
It can be seen that the power flow through the hydraulic transmission is large when the efficiency H of the hydraulic transmission is high.
The efficiency G of the overall transmission is calculated using the formula:

G = (1-(i-1)*((i 0/i) -1)/(i 0-1))+H *(i -1)*((i 0/i) -1)/(i 0-1); G = (1- (i -1) * ((i 0 / i) -1) / (i 0-1)) + H * (i -1) * ((i 0 / i) -1) / ( i 0-1);

Er ist ebenfalls als Kurve in das Diagramm eingezeichnet.It is also drawn as a curve in the diagram.

Claims (4)

1. 4-Wellengetriebe, bei dem eine Welle 22 von dem stillstehenden Gehäuse gebildet wird und bei dem 3 Wellen 1, 20; 4, 33; 11, 25 drehbar sind,
dadurch gekennzeichnet, daß die drei drehbaren Wellen 1, 20; 4, 33; 11, 25; mit ihren Drehzahlen n 1, n 20; n 4, n 33; n 11, n 25; so angeordnet sind, daß für sie die Drehzahlgleichung gilt: n 1-n 4=z *n 11;
mit z = rationale Zahl bzw.
n 20-n 33=z *n 251. 4-shaft transmission, in which a shaft 22 is formed by the stationary housing and in which 3 shafts 1, 20; 4.33; 11, 25 are rotatable,
characterized in that the three rotatable shafts 1, 20; 4.33; 11, 25; with their speeds n 1, n 20; n 4, n 33; n 11, n 25; are arranged so that the speed equation applies to them: n 1- n 4 = z * n 11;
with z = rational number or
n 20- n 33 = z * n 25 2. 4-Wellengetriebe unter Patentanspruch 1, dadurch gekennzeichnet, daß es aus insgesamt 5 Wellen 20, 22, 23, 25, 33 gebildet wird von denen drei Wellen 20, 22, 23 in einem Umlaufgetriebe mit der Grundgleichung (n 20-n 22)/(n 23-n 22)=-(1/a); a = rationale Zahl;und drei Wellen 23, 25, 33 in einem Umlaufgetriebe mit der Grundgleichung(n 23-n 25)/(n 33-n 25)=-averbunden sind und die eine Welle 22 gehäusefest ist, so daß ihre Drehzahl Null ist n 22=0, und daher für das Gesamtgetriebe die Gleichung gilt:(n 33-n 20)/n 25=(1+a)/a = z;2. 4-shaft transmission under claim 1, characterized in that it is formed from a total of 5 shafts 20, 22, 23, 25, 33 of which three shafts 20, 22, 23 in a planetary gear with the basic equation (n 20- n 22nd ) / (n 23- n 22) = - (1 / a) ; a = rational number; and three shafts 23, 25, 33 are connected in a planetary gear with the basic equation (n 23- n 25) / (n 33- n 25) = - a and one shaft 22 is fixed to the housing, so that their Speed zero is n 22 = 0, and therefore the equation applies to the entire transmission: (n 33- n 20) / n 25 = (1+ a) / a = z ; 3. Getriebe unter Patentanspruch 1, 2, dadurch gekennzeichnet, daß seine eine Welle 33 mit den Planetenrädern 32 eines weiteren Umlaufgetriebes verbunden ist, seine andere Welle 25 mit einer Welle eines stufenlos verstellbaren Getriebes 28 verbunden ist und seine dritte Welle 23 mit der An- oder Abtriebswelle 20 eines sonstigen Antriebsstrangs verbunden ist.3. Transmission under claim 1, 2, characterized in that its one shaft 33 is connected to the planet gears 32 of another epicyclic gear, its other shaft 25 is connected to a shaft of a continuously variable transmission 28 and its third shaft 23 with the or output shaft 20 of another drive train is connected. 4. Getriebe unter Patentanspruch 3, dadurch gekennzeichnet, daß es den dritten Planetensatz 32 eines Planetengetriebes 31, welches zwischen einer Antriebswelle 20 und einer Abtriebswelle 21 angeordnet ist, die mit den beiden anderen Planetensätzen 30, 38 in Eingriff stehen, mit einer Welle 26 eines Verstellgetriebes verbindet und die andere Welle 35 des Verstellgetriebes 28, 36 den Steg S des Planetengetriebes 11 treibt.4. Transmission under claim 3, characterized in that it is the third planetary gear set 32 of a planetary gear 31 , which is arranged between an input shaft 20 and an output shaft 21 , which are in engagement with the other two planetary gear sets 30, 38 , with a shaft 26 one Connecting gear connects and the other shaft 35 of the adjusting gear 28, 36 drives the web S of the planetary gear 11 .
DE19893924548 1989-03-23 1989-07-25 Four shaft gear with one stationary housing at shaft - has three rotary shafts with planetary wheels and adjusting gear Withdrawn DE3924548A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19893924548 DE3924548A1 (en) 1989-03-23 1989-07-25 Four shaft gear with one stationary housing at shaft - has three rotary shafts with planetary wheels and adjusting gear
DE19893927783 DE3927783A1 (en) 1989-07-25 1989-08-23 Planetary gear with two sections and two sections an three shafts - has hydrostatic pump and motor, with transformer with drive and driven shafts

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/DE1989/000189 WO1989009351A1 (en) 1988-03-24 1989-03-23 Cam gearing
DE19893924548 DE3924548A1 (en) 1989-03-23 1989-07-25 Four shaft gear with one stationary housing at shaft - has three rotary shafts with planetary wheels and adjusting gear

Publications (1)

Publication Number Publication Date
DE3924548A1 true DE3924548A1 (en) 1990-09-27

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Application Number Title Priority Date Filing Date
DE19893924548 Withdrawn DE3924548A1 (en) 1989-03-23 1989-07-25 Four shaft gear with one stationary housing at shaft - has three rotary shafts with planetary wheels and adjusting gear

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0628751A1 (en) * 1993-05-28 1994-12-14 Friedrich Prof. Dr.-Ing. Jarchow Powershift transmission with continously variable hydrostatic ratios
WO2012105868A2 (en) * 2011-02-01 2012-08-09 Закрытое Акционерное Общество "Комбарко" Continuously variable transmission (variants)
RU2523508C2 (en) * 2009-07-20 2014-07-20 Закрытое Акционерное Общество "Комбарко" Wide-range continuously variable-ratio drive (supervariator)
RU2523507C2 (en) * 2009-09-22 2014-07-20 Закрытое Акционерное Общество "Комбарко" Wide-range continuously variable-ratio drive (supervariator)
US9261181B2 (en) 2011-06-14 2016-02-16 Valtra Oy Ab Continuously variable power-split vehicle transmission

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0628751A1 (en) * 1993-05-28 1994-12-14 Friedrich Prof. Dr.-Ing. Jarchow Powershift transmission with continously variable hydrostatic ratios
RU2523508C2 (en) * 2009-07-20 2014-07-20 Закрытое Акционерное Общество "Комбарко" Wide-range continuously variable-ratio drive (supervariator)
RU2523507C2 (en) * 2009-09-22 2014-07-20 Закрытое Акционерное Общество "Комбарко" Wide-range continuously variable-ratio drive (supervariator)
WO2012105868A2 (en) * 2011-02-01 2012-08-09 Закрытое Акционерное Общество "Комбарко" Continuously variable transmission (variants)
WO2012105868A3 (en) * 2011-02-01 2012-10-04 Закрытое Акционерное Общество "Комбарко" Continuously variable transmission (variants)
US9261181B2 (en) 2011-06-14 2016-02-16 Valtra Oy Ab Continuously variable power-split vehicle transmission

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