DE4226575A1 - Five ratio gearbox with intermediate shaft arrangement - has fourth gear with 1:1 ratio, adjacent ratios achieved via multiple coupling on intermediate train and all progressively stepped - Google Patents

Five ratio gearbox with intermediate shaft arrangement - has fourth gear with 1:1 ratio, adjacent ratios achieved via multiple coupling on intermediate train and all progressively stepped

Info

Publication number
DE4226575A1
DE4226575A1 DE19924226575 DE4226575A DE4226575A1 DE 4226575 A1 DE4226575 A1 DE 4226575A1 DE 19924226575 DE19924226575 DE 19924226575 DE 4226575 A DE4226575 A DE 4226575A DE 4226575 A1 DE4226575 A1 DE 4226575A1
Authority
DE
Germany
Prior art keywords
gear
transmission
ratio
gears
countershaft
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.)
Withdrawn
Application number
DE19924226575
Other languages
German (de)
Inventor
Helmut Dipl Ing Bender
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daimler Benz AG
Original Assignee
Daimler Benz AG
Mercedes Benz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Benz AG, Mercedes Benz AG filed Critical Daimler Benz AG
Priority to DE19924226575 priority Critical patent/DE4226575A1/en
Publication of DE4226575A1 publication Critical patent/DE4226575A1/en
Withdrawn legal-status Critical Current

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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
    • F16H3/0915—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft with coaxial input and output shafts
    • 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
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/043—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds

Abstract

In order to achieve five increasing ratio, forward gears, the fourth gear has a ratio 1:1, and both adjacent ratios (third and fifth) are achieved by multiple coupling with a gear (H2) on the base geartrain (7) with one of the constant gears (K1,K2). This provides a more rapid gear change. The changing forwards of the gears is progressively stepped as is that of the four lower gears. ADVANTAGE - Reduced number of gears, allows progressive ratio change.

Description

Die Erfindung bezieht sich auf ein Zahnräderwechselgetriebe nach dem Oberbegriff von Patentanspruch 1.The invention relates to a gear change transmission according to the preamble of claim 1.

Bei einem Zahnräderwechselgetriebe der eingangs genannten Art (deutsche Patentanmeldung P 41 29 290) werden die Vorwärtsgänge so gebildet, daß die Zahnradstufen des Grundgetriebes in der Reihenfolge ihrer Übersetzung nacheinander mit beiden Getriebe­ konstanten multiplikativ verknüpft werden, so daß eine pro­ gressive Stufung bei einem Grundgetriebe mit nur zwei Zahnrad­ stufen nicht möglich wäre.In a gear change transmission of the type mentioned (German patent application P 41 29 290) are the forward gears formed so that the gear stages of the basic transmission in the Sequence of their translation one after the other with both gears constant multiplicative, so that one per gressive gradation in a basic gearbox with only two gearwheels levels would not be possible.

Die der Erfindung zugrunde liegende Aufgabe besteht im wesent­ lichen darin, ein fünfgängiges Zahnräderwechselgetriebe mit einer geringen Anzahl von Zahnradstufen und der Möglichkeit der progressiven Stufung der Gangübersetzungen zu schaffen.The object underlying the invention is essentially in a five-speed gear change transmission a small number of gear stages and the possibility of to create progressive grading of gear ratios.

Die erläuterte Aufgabe ist in vorteilhafter Weise mit den kenn­ zeichnenden Merkmalen von Patentanspruch 1 gelöst.The task explained is advantageous with the kenn Drawing features of claim 1 solved.

Bei dem Zahnräderwechselgetriebe nach der Erfindung ist eine progressive Stufung der Vorwärtsgang-Übersetzungen ermöglicht, weil die beiden durch eine Zahnradstufe des Grundgetriebes ge­ bildeten Gänge quasi durch den direkten Gang aufgesplittet sind, wobei man zur Erzielung von insgesamt fünf Vorwärtsgängen mit insgesamt nur vier Zahnradstufen auskommt.In the gear change transmission according to the invention is one allows progressive grading of forward gear ratios, because the two ge by a gear stage of the basic transmission formed aisles almost split by the direct aisle are, to achieve a total of five forward gears with only four gear stages.

Einzelheiten der Erfindung ergeben sich aus der nachstehenden Beschreibung eines in der Zeichnung schematisch dargestellten Ausführungsbeispieles.Details of the invention will become apparent from the following Description of a schematically shown in the drawing Embodiment.

In der Zeichnung bedeuten:In the drawing:

Fig. 1 ein Getriebeschema eines fünfgängigen Zahnräder­ wechselgetriebes der Vorgelegebauart nach der Erfindung, und Fig. 1 is a transmission diagram of a five-speed gear change gearbox of the countershaft type according to the invention, and

Fig. 2 ein Übersichtsschema über den Kraftfluß in den Vorwärtsgängen des Zahnräderwechselgetriebes von Fig. 1. FIG. 2 is an overview diagram of the flow of force in the forward gears of the gear change transmission of FIG. 1.

Unter Bezugnahme auf Fig. 1 ist eine von einem Antriebsmotor eines Kraftfahrzeuges antreibbare Eingangswelle 4 durch zwei Getriebekonstanten K1 und K2 mit einer parallelen Vorgelegewelle 6 verbunden. Die Vorgelegewelle 6 ist durch zwei Zahnradstufen H1 und H2 eines Grundgetriebes 7 mit einer zur Eingangswelle 4 koaxialen Ausgangswelle 5 verbunden. Die Losräder der Getriebekonstanten K1 und K2 sind durch eine Wechselschaltkupplung 19 fakultativ mit der Eingangswelle 4 kuppelbar.With reference to FIG. 1, an input shaft 4 that can be driven by a drive motor of a motor vehicle is connected to a parallel countershaft 6 by two gear constants K1 and K2. The countershaft 6 is connected by two gear stages H1 and H2 of a basic transmission 7 to an output shaft 5 coaxial with the input shaft 4 . The idler gears of the transmission constants K1 and K2 can optionally be coupled to the input shaft 4 by a changeover clutch 19 .

Eingangswelle 4 und Ausgangswelle 5 sind durch eine Schalt­ kupplung 20 direkt miteinander kuppelbar.Input shaft 4 and output shaft 5 can be coupled directly to one another by a switching clutch 20 .

Die Losräder der Zahnradstufen H1 und H2 des Grundgetriebes 7 sind durch eine Wechselschaltkupplung 21 mit der Ausgangswelle 5 fakultativ kuppelbar.The idler gears of the gear stages H1 and H2 of the basic transmission 7 can optionally be coupled to the output shaft 5 by means of a two-way clutch 21 .

Die Getriebekonstante K1 weist aufgrund ihres größeren Losrades die schnellere Übersetzung gegenüber der Getriebekonstanten K2 auf.The gear constant K1 has a larger idler gear the faster gear ratio compared to the transmission constant K2 on.

Die Zahnradstufe H1 des Grundgetriebes 7 weist wegen ihres kleineren Vorgelegewellenzahnrades die langsamere Übersetzung gegenüber der anderen Zahnradstufe H2 des Grundgetriebes 7 auf. The gear stage H1 of the basic transmission 7 has, because of its smaller countershaft gear, the slower translation than the other gear stage H2 of the basic transmission 7 .

Unter Bezugnahme auf Fig. 2 werden bei dem Zahnräderwechselge­ triebe von Fig. 1 fünf Vorwärtsgänge wie folgt gebildet:With reference to FIG. 2, five forward gears are formed in the gearwheel transmissions of FIG. 1 as follows:

Im niedrigsten Vorwärtsgang I sind die langsame Getriebekon­ stante K2 durch die Wechselschaltkupplung 19 und die langsame Zahnradstufe H1 des Grundgetriebes 7 durch die Wechselschalt­ kupplung 21 in den Kraftfluß zwischen Ein- und Ausgangswelle 4 und 5 eingeschaltet, so daß die Leistungsübertragung von der Eingangswelle 4 über die Getriebekonstante K2 zur Vorgelege­ welle 6 und von letzterer über die Zahnradstufe H1 zur Aus­ gangswelle 5 erfolgt.In the lowest forward gear I, the slow gear constant K2 through the changeover clutch 19 and the slow gear stage H1 of the basic transmission 7 through the changeover clutch 21 in the power flow between the input and output shaft 4 and 5 , so that the power transmission from the input shaft 4 through the Gearbox constant K2 to countershaft 6 and from the latter via gear stage H1 to output shaft 5 .

In dem benachbarten höheren Vorwärtsgang II sind die schnellere Getriebekonstante K1 durch die Wechselschaltkupplung 19 und die Zahnradstufe H1 des Grundgetriebes 7 durch die Wechselschalt­ kupplung 21 in den Kraftfluß eingeschaltet, so daß die Lei­ stungsübertragung von der Eingangswelle 4 über die Getriebe­ konstante K1 zur Vorgelegewelle und von letzterer über die Zahnradstufe H1 zur Ausgangswelle 5 erfolgt.In the adjacent higher forward gear II, the faster transmission constant K1 through the changeover clutch 19 and the gear stage H1 of the basic transmission 7 through the changeover clutch 21 in the power flow, so that the power transmission from the input shaft 4 via the transmission constant K1 to the countershaft and from the latter takes place via the gear stage H1 to the output shaft 5 .

In dem sich anschließenden III. Vorwärtsgang sind die langsame Getriebekonstante K2 durch die Wechselschaltkupplung 19 und die schnellere Zahnradstufe H2 des Grundgetriebes 7 durch die Wechselschaltkupplung 21 in den Kraftfluß eingeschaltet, so daß die Leistungsübertragung von der Eingangswelle 4 über die Ge­ triebekonstante K2 zur Vorgelegewelle und von letzterer über die Zahnradstufe H2 zur Ausgangswelle 5 erfolgt.In the subsequent III. Forward gear are the slow transmission constant K2 through the changeover clutch 19 and the faster gear stage H2 of the basic transmission 7 through the changeover clutch 21 in the power flow, so that the power transmission from the input shaft 4 via the gearbox constant K2 to the countershaft and from the latter via the gear stage H2 to Output shaft 5 takes place.

Im IV. Gang (direkter Gang) ist die Schaltkupplung 20 einge­ rückt, so daß die Leistungsübertragung direkt von der Ein­ gangswelle 4 zur Ausgangswelle 5 erfolgt.In IV gear (direct gear), the clutch 20 is moved so that the power transmission takes place directly from the input shaft 4 to the output shaft 5 .

Im benachbarten höchsten Gang V sind die schnellere Getriebe­ konstante K1 durch die Wechselschaltkupplung 19 und die Zahnradstufe H2 des Grundgetriebes 7 durch die Wechselschalt­ kupplung 21 in den Kraftfluß eingeschaltet, so daß die Lei­ stungsübertragung von der Eingangswelle 4 über die Getriebe­ konstante K1 zur Vorgelegewelle 6 und von letzterer über die Zahnradstufe H2 zur Ausgangswelle 5 erfolgt.In the adjacent highest gear V, the faster transmission constant K1 through the change-over clutch 19 and the gear stage H2 of the basic transmission 7 through the change-over clutch 21 in the power flow, so that the power transmission from the input shaft 4 via the transmission constant K1 to the countershaft 6 and from the latter via the gear stage H2 to the output shaft 5 .

Die Stufung s der Gangübersetzungen kann bei einem ersten Aus­ führungsbeispiel wie folgt getroffen sein:The step s of the gear ratios can be at a first off example should be taken as follows:

sI/II=x5
sII/III=x4
sIII/IV=x3
sIV/V=x2.s I / II = x 5
s II / III = x 4
s III / IV = x 3
s IV / V = x 2 .

Die Stufung s der Gangübersetzungen kann bei einer zweiten Aus­ führungsform wie folgt getroffen sein:The step s of the gear ratios can be a second off management can be taken as follows:

sI/II=x4
sII/III=x3
sIII/IV=x2
sIV/V=x2.s I / II = x 4
s II / III = x 3
s III / IV = x 2
s IV / V = x 2 .

Claims (3)

1. Zahnräderwechselgetriebe der Vorgelegebauart, bei dem eine Eingangswelle durch zwei ein- und ausschaltbare Getriebekon­ stanten (Zahnradstufen) mit einer parallelen Vorgelegewelle und eine zur Ausgangswelle koaxiale Ausgangswelle durch zwei ein- und ausschaltbare Zahnradstufen eines Grundgetriebes mit der Vorgelegewelle verbunden und eine Kupplungsanordnung zum Kuppeln der Eingangswelle mit der Ausgangswelle in einem die Übersetzung 1:1 aufweisenden Vorwärtsgang verwendet ist, dadurch gekennzeichnet, daß zur Bildung von insgesamt fünf in bezug auf ihre Überset­ zung in Reihe aufeinander folgenden Vorwärtsgängen (I bis V) der IV. Gang die Übersetzung 1:1 aufweist und die beiden in bezug auf die Übersetzung dem IV. Vorwärtsgang benachbarten beiden Vorwärtsgänge (III und V) durch die die schnellere Über­ setzung aufweisende Zahnradstufe (H2) des Grundgetriebes (7) unter multiplikativer Verknüpfung mit jeweils einer der beiden Getriebekonstanten (K1, K2) gebildet werden.1. Gear change transmission of the countershaft type, in which an input shaft is connected to the countershaft by means of two transmission constants which can be switched on and off (gear stages) with a parallel countershaft and an output shaft which is coaxial with the output shaft is connected to the countershaft by two gear stages of a basic transmission that can be switched on and off and a clutch arrangement for coupling the Input shaft with the output shaft is used in a forward gear having the ratio 1: 1, characterized in that to form a total of five with respect to their translation in succession in forward gears (I to V), the fourth gear ratio 1: 1 has and the two with respect to the translation of the IV forward gear adjacent two forward gears (III and V) by the faster transmission gear stage (H2) of the basic transmission ( 7 ) with multiplicative linkage with one of the two transmission constants (K1, K2 ) are formed. 2. Getriebe nach Anspruch 1, dadurch gekennzeichnet, daß die Übersetzungen der Vorwärtsgänge (I bis V) progressiv gestuft sind. 2. Transmission according to claim 1, characterized, that the translations of the forward gears (I to V) are progressive are graded.   3. Getriebe nach Anspruch 1, dadurch gekennzeichnet, daß die Übersetzungen der vier unteren Vorwärtsgänge (I bis IV) progressiv gestuft sind.3. Transmission according to claim 1, characterized, that the translations of the four lower forward gears (I to IV) are progressively graded.
DE19924226575 1992-08-11 1992-08-11 Five ratio gearbox with intermediate shaft arrangement - has fourth gear with 1:1 ratio, adjacent ratios achieved via multiple coupling on intermediate train and all progressively stepped Withdrawn DE4226575A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19924226575 DE4226575A1 (en) 1992-08-11 1992-08-11 Five ratio gearbox with intermediate shaft arrangement - has fourth gear with 1:1 ratio, adjacent ratios achieved via multiple coupling on intermediate train and all progressively stepped

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19924226575 DE4226575A1 (en) 1992-08-11 1992-08-11 Five ratio gearbox with intermediate shaft arrangement - has fourth gear with 1:1 ratio, adjacent ratios achieved via multiple coupling on intermediate train and all progressively stepped

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DE4226575A1 true DE4226575A1 (en) 1993-09-23

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0624739A1 (en) * 1993-05-14 1994-11-17 Mercedes-Benz Ag Countershaft transmission
DE10025684A1 (en) * 2000-05-24 2001-11-29 Zahnradfabrik Friedrichshafen Group construction discrete gearbox allows highest gear of main group to be selected in only one gear of range group,with ratio change to main group highest gear being much smaller than others
DE10114557A1 (en) * 2001-03-24 2002-09-26 Zahnradfabrik Friedrichshafen Vehicle gearbox with group structure has main gear group with three wheel sets for six forward gears and one for reverse and with seventh gear shifted through shift clutch which connects drive to output shaft in shifted state
DE10239396A1 (en) * 2002-08-28 2004-03-11 Zf Friedrichshafen Ag Car drive gearing with drive and output shafts uncouples gear parts not involved in direct drive during which only shafts and internal parts rotate for friction loss reduction.
FR2852652A1 (en) * 2003-03-21 2004-09-24 Renault Sa Gear box for motor vehicle, has interlocking device linked to two pinions, and parallel transmission unit set driving output shaft by main shaft without torque passage by secondary shaft to obtain intermediary connection passage
WO2006032312A1 (en) * 2004-09-23 2006-03-30 Daimlerchrysler Ag Automated transmission for a motor vehicle and method for operating the same
WO2006117099A1 (en) * 2005-05-03 2006-11-09 Daimlerchrysler Ag Transmission having an idler shaft which can be decoupled in the direct gear
WO2007134943A1 (en) * 2006-05-24 2007-11-29 Zf Friedrichshafen Ag Multi-group transmission and method for changing gear in a multi-group transmission
WO2009135726A1 (en) * 2008-05-09 2009-11-12 Zf Friedrichshafen Ag Multi-group transmission of a motor vehicle
WO2009149993A1 (en) * 2008-06-09 2009-12-17 Zf Friedrichshafen Ag Multigroup transmission of a motor vehicle
GB2514995A (en) * 2013-04-08 2014-12-17 Paratus Developments Ltd A Gear Box
DE102011085900B4 (en) * 2011-11-08 2017-06-29 Bayerische Motoren Werke Aktiengesellschaft Transmission for vehicles

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3614752A1 (en) * 1985-05-17 1986-11-20 Nissan Motor Co., Ltd., Yokohama, Kanagawa WHEEL GEARBOX

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3614752A1 (en) * 1985-05-17 1986-11-20 Nissan Motor Co., Ltd., Yokohama, Kanagawa WHEEL GEARBOX

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5507195A (en) * 1993-05-14 1996-04-16 Mercedes-Benz Ag Change-speed layshaft gearbox configurable as a single range or a multiple range transmission
EP0624739A1 (en) * 1993-05-14 1994-11-17 Mercedes-Benz Ag Countershaft transmission
DE10025684A1 (en) * 2000-05-24 2001-11-29 Zahnradfabrik Friedrichshafen Group construction discrete gearbox allows highest gear of main group to be selected in only one gear of range group,with ratio change to main group highest gear being much smaller than others
DE10114557A1 (en) * 2001-03-24 2002-09-26 Zahnradfabrik Friedrichshafen Vehicle gearbox with group structure has main gear group with three wheel sets for six forward gears and one for reverse and with seventh gear shifted through shift clutch which connects drive to output shaft in shifted state
US7350430B2 (en) 2002-08-28 2008-04-01 Zf Friedrichshafen Ag Transmission having direct gear
DE10239396A1 (en) * 2002-08-28 2004-03-11 Zf Friedrichshafen Ag Car drive gearing with drive and output shafts uncouples gear parts not involved in direct drive during which only shafts and internal parts rotate for friction loss reduction.
WO2004025140A1 (en) * 2002-08-28 2004-03-25 Zf Friedrichshafen Ag Transmission having a direct gear
FR2852652A1 (en) * 2003-03-21 2004-09-24 Renault Sa Gear box for motor vehicle, has interlocking device linked to two pinions, and parallel transmission unit set driving output shaft by main shaft without torque passage by secondary shaft to obtain intermediary connection passage
WO2006032312A1 (en) * 2004-09-23 2006-03-30 Daimlerchrysler Ag Automated transmission for a motor vehicle and method for operating the same
US7731617B2 (en) 2004-09-23 2010-06-08 Daimler A.G. Automated motor vehicle transmission and method of operating the same
WO2006117099A1 (en) * 2005-05-03 2006-11-09 Daimlerchrysler Ag Transmission having an idler shaft which can be decoupled in the direct gear
US7798937B2 (en) 2005-05-03 2010-09-21 Daimler Ag Transmission with a countershaft which can be idled in direct gear
WO2007134943A1 (en) * 2006-05-24 2007-11-29 Zf Friedrichshafen Ag Multi-group transmission and method for changing gear in a multi-group transmission
US8161835B2 (en) 2006-05-24 2012-04-24 Zf Friedrichshafen Ag Multi-group transmission and method for changing gear in a multi-group transmission
WO2009135726A1 (en) * 2008-05-09 2009-11-12 Zf Friedrichshafen Ag Multi-group transmission of a motor vehicle
WO2009149993A1 (en) * 2008-06-09 2009-12-17 Zf Friedrichshafen Ag Multigroup transmission of a motor vehicle
US9068636B2 (en) 2008-06-09 2015-06-30 Zf Friedrichshafen Ag Multigroup transmission of a motor vehicle
DE102011085900B4 (en) * 2011-11-08 2017-06-29 Bayerische Motoren Werke Aktiengesellschaft Transmission for vehicles
GB2514995A (en) * 2013-04-08 2014-12-17 Paratus Developments Ltd A Gear Box

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