DE3838768A1 - Hydrostatic/mechanical power-shift transmission with a continuously variable effect and with toothed selector clutches for shifts proprietary to gear changes and multi-plate clutches for the gear changes - Google Patents

Hydrostatic/mechanical power-shift transmission with a continuously variable effect and with toothed selector clutches for shifts proprietary to gear changes and multi-plate clutches for the gear changes

Info

Publication number
DE3838768A1
DE3838768A1 DE19883838768 DE3838768A DE3838768A1 DE 3838768 A1 DE3838768 A1 DE 3838768A1 DE 19883838768 DE19883838768 DE 19883838768 DE 3838768 A DE3838768 A DE 3838768A DE 3838768 A1 DE3838768 A1 DE 3838768A1
Authority
DE
Germany
Prior art keywords
gear
shaft
clutches
stages
transmission
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
DE19883838768
Other languages
German (de)
Other versions
DE3838768C2 (en
Inventor
Friedrich Prof Dr Ing Jarchow
Peter Dr Ing Tenberge
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to DE19883838768 priority Critical patent/DE3838768A1/en
Publication of DE3838768A1 publication Critical patent/DE3838768A1/en
Application granted granted Critical
Publication of DE3838768C2 publication Critical patent/DE3838768C2/de
Granted 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
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/202—Mechanical transmission, e.g. clutches, gears
    • 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
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The transmission consists of a four-shaft planetary gear mechanism, a continuously variable hydrostatic transmission, rear-mounted gear stages and selector clutches. The hydrostatic transmission includes two positive displacement machines. In the planetary mechanism, one shaft forms the input shaft, to which one positive displacement machine is connected. A second shaft of the planetary mechanism is connected to the other positive displacement machine. The third and fourth shafts of the planetary mechanism are coupler shafts, the speeds of which are infinitely variable and which, when rear-mounted stages are connected to the output shaft, form gears, a gear change being associated with a change of the coupler shafts. In the extreme positions of the hydrostatic transmission, selector clutches effect the gear changes at synchronous speeds of rotation, in a manner free from load and without interruption of the tractive effort, and do this without a jerk, i.e. provide a very smooth gear change. In addition, such transmissions have good efficiencies and a wide transmission-ratio adjustment range. They are therefore advantageously suitable for motor vehicles.

Description

Stufenlos wirkende hydrostatisch-mechanische Lastschaltge­ triebe der im Oberbegriff der Patentansprüche angegebenen Art eignen sich vorteilhaft für Kraftfahrzeuge, da sie sich in weiten Bereichen stufenlos verstellen lassen und außerdem gu­ te Wirkungsgrade haben. Der relativ große Stellbereich er­ laubt den Betrieb der Brennkraftmaschine auf Vorzugskennli­ nien. Solche Kennlinien können z. B. die Kurve für minimalen Kraftstoffverbrauch oder eine Linie für ein gutes Beschleu­ nigungsverhalten sein.Stepless hydrostatic-mechanical powershift drives the type specified in the preamble of the claims are advantageous for motor vehicles because they are in wide areas continuously adjustable and also gu have efficiencies. The relatively large adjustment range allows the operation of the internal combustion engine on preferential characteristics no. Such characteristics can e.g. B. the curve for minimum Fuel consumption or a line for good acceleration cleaning behavior.

Die DE 31 47 447 C2 beschreibt ein Getriebe nach dem Oberbe­ griff der Patentansprüche. Die Nachschaltstufen werden mit Schalt-Zahnkupplungen angeschlossen. Die Steuerung des Ge­ triebes sorgt dafür, daß der Gangwechsel im theoretischen Synchronpunkt erfolgt. Sie löst zunächst das Einschalten des neuen Ganges und anschließend das Herausnehmen des alten Gan­ ges aus. Die Erfahrung an einem ausgeführten Getriebe lehrt, daß der Gangwechsel mit Schaltrucken verbunden sein kann. Beim Ausrücken des alten Ganges muß eine ausreichend große Schaltkraft zur Verfügung stehen, um den Schaltweg genügend schnell zurückzulegen. Die Schaltkraft trennt so die noch be­ lastete Kupplung, was zu einem Drehmomentstoß in der Kupplung des neuen Ganges führt.DE 31 47 447 C2 describes a transmission according to the Oberbe attacked the claims. The switching stages are with Gear clutches connected. The control of the Ge drives ensures that the gear change in the theoretical Synchronization point takes place. It first triggers the switching on of the new gear and then removing the old gan total. Experience with a gearbox that has been carried out teaches that the gear change can be associated with shift jerks. When disengaging the old aisle, a sufficiently large one Shifting force is available to make the shift path sufficient to cover quickly. The switching force is still separating them loaded clutch, resulting in a torque surge in the clutch of the new corridor.

Schalt-Reibungskupplungen, d. h. Schalt-Lamellenkupplungen, die z. B. in den Figuren der Patentschriften US 38 88 139, US 37 09 060, US 37 09 061 sowie in der Offenlegungsschrift DE 36 22 045 A1 vorgesehen sind, können für eine hohe Schalt­ qualität überlappend geschaltet werden, so daß ausreichend Zeit für eine Drehmomentumverlagerung bleibt und keine Schaltstöße entstehen. Allerdings bauen Schalt-Lamellenkupp­ lungen im Vergleich zu Schalt-Zahnkupplungen erheblich größer und erzeugen im geöffneten Zustand bei Differenzdrehzahlen Leerlaufverlustleistungen, die den Wirkungsgrad des Getriebes verschlechtern.Switching friction clutches, d. H. Shift multi-plate clutches, the z. B. in the figures of US 38 88 139, US 37 09 060, US 37 09 061 and in the published patent application DE 36 22 045 A1 are provided for high switching quality can be switched overlapping, so that sufficient  There is time for a torque shift and none Switching shocks occur. However, build multi-plate clutch lungs compared to gear-tooth clutches considerably larger and generate in the open state at differential speeds Idling power loss, which affects the efficiency of the transmission worsen.

Die Erfindung stellt sich daher die Aufgabe, eine stoßfreie, d. h. eine stetige Drehmomentverlagerung von dem alten auf den neuen Gang bei kleiner Baugröße und guten Getriebewir­ kungsgraden zu erreichen.The object of the invention is therefore to provide a shock-free, d. H. a steady torque shift from the old to the new gear with a small size and good gearbox to achieve degrees of efficiency.

Der kennzeichnende Teil des Anspruches 1 beschreibt die Lö­ sung der Aufgabenstellung.The characterizing part of claim 1 describes the Lö solution of the task.

Zur Verringerung des Bauaufwandes wird in weiterer Ausgestal­ tung der Erfindung einer der in Anspruch 1 vorgesehenen Schalt-Reibungskupplungen in bekannter Weise, vergl. z. B. DE 36 22 045 A1, als Anfahrkupplung vorgesehen.In order to reduce the construction work, the project will be expanded tion of the invention provided for in one of the claims Switching friction clutches in a known manner, cf. B. DE 36 22 045 A1, intended as a starting clutch.

Fig. 1 stellt ein Ausführungsbeispiel dar. Das vierwellige Planetengetriebe besteht aus der Planetenstufe I mit dem Son­ nenrad 1′, Hohlrad 2′ und Planetenradträger s′ mit den Plane­ tenrädern p′ und der Planetenstufe II mit dem Sonnenrad 1′′, Hohlrad 2′′ und Planetenradträger s′′ mit den Planetenrädern p′′. Es bilden die Glieder s′′ und 2′ die Antriebswelle 1, die Glieder 1′ und 1′′ die Welle B für den Anschluß der volumen­ konstanten Verdrängermaschine b, Glied s′ die langsamlaufende Koppelwelle E und Glied 2′′ die schnellaufende Koppelwelle A. Die Zahnräder 3; 4 verbinden die volumenverstellbare Verdrän­ germaschine a mit der Antriebswelle 1. Es stehen die Schalt- Lamellenkupplung L 1 für den Anschluß des 1. Ganges mit den Rädern 5; 6, des 3. Ganges mit den Rädern 7; 8 und des Rück­ wärtsganges mit den Rädern 9; 10; 11 an die Koppelwelle E und die Schalt-Lamellenkupplung L 2 für den Anschluß des 2. Ganges mit den Rädern 5′; 6′ und des 4. Ganges mit den Rädern 7′; 8′ an die Koppelwelle A zur Verfügung. Die Schalt-Doppelzahn­ kupplungen Z 1 und Z 2 verfügen über Synchronisie­ rungseinrichtungen. Z 1 und Z 2 führen vorbereitende Schaltun­ gen aus und haben lediglich leerlaufende Getriebeteile anzu­ synchronisieren. Es gehören Z 1 zum 1. und 3. Gang sowie Z 2 zum 2. und 4. Gang. Um keine nennenswerte Differenzdrehzahl in der jeweils geöffneten Schalt-Lamellenkupplung zu er­ zwingen, erfolgt bei einem neu einzulegenden Gang die vorbe­ reitende Schaltung erst dann, wenn die Lamellenkupplung da­ durch schon fast synchrone Drehzahlen bekommt. Wenn die La­ mellenkupplung schließt, öffnet die andere überlappend, so daß das Drehmoment stetig umverlagert wird. Unmittelbar nach Öffnen der Lamellenkupplung wird die Zahnkupplung der Stufe des alten Ganges gelöst. Die Aktivierung des Rückwärtsganges übernimmt das Schiebe-Zwischenrad 10. Fig. 1 shows an embodiment. The four-shaft planetary gear consists of the planetary stage I with the Son nenrad 1 ', ring gear 2 ' and planet carrier s ' with the tarpaulin tarpaulin p 'and the planetary stage II with the sun gear 1 '', ring gear 2 ''And planet carrier s '' with the planet gears p ''. It form the links s ''and 2 ' the drive shaft 1 , the links 1 'and 1 ''the shaft B for the connection of the volume constant displacement machine b , link s ' the slow-running coupling shaft E and link 2 ''the high-speed coupling shaft A. . The gears 3 ; 4 connect the volume-adjustable displacement machine a to the drive shaft 1 . There are the multi-plate clutch L 1 for connecting the 1st gear with the wheels 5 ; 6 , the 3rd gear with the wheels 7 ; 8 and the reverse gear with the wheels 9 ; 10 ; 11 to the coupling shaft E and the multi-plate clutch L 2 for connecting the 2nd gear with the wheels 5 '; 6 'and the 4th gear with the wheels 7 '; 8 'to the coupling shaft A available. The shift double tooth clutches Z 1 and Z 2 have synchronization devices. Z 1 and Z 2 carry out preparatory circuits and only have to synchronize idle gear parts. Z 1 belong to 1st and 3rd gear and Z 2 belong to 2nd and 4th gear. In order not to force a noteworthy differential speed in the respective open multi-plate clutch, the gear shifting takes place in a new gear only when the multi-plate clutch is getting through almost synchronous speeds. When the clutch closes, the other opens overlapping, so that the torque is continuously shifted. Immediately after opening the multi-plate clutch, the tooth clutch of the stage of the old gear is released. Activation of the reverse gear is carried out by the intermediate sliding gear 10 .

Nachfolgende Tafel demonstriert die Schaltlogik. Es bedeuten die ZeichenThe following table demonstrates the switching logic. Mean it the characters

Claims (2)

1. Stufenlos wirkendes hydrostatisch-mechanisches Lastschalt­ getriebe
bestehend aus einem vierwelligen Zahnräder-Planetengetriebe, einem stufenlos einstellbaren hydrostatischen Getriebe mit einer Verdrängermaschine a und einer Verdrängermaschine b sowie Zahnräder-Nachschaltstufen,
wobei bei dem Planetengetriebe eine Welle die Antriebswelle 1 bildet, an die die Verdrängermaschine a angeschlossen ist, eine zweite Welle die Welle B darstellt, mit der die Verdrän­ germaschine b in Verbindung steht, und zwei weitere Wellen als Koppelwellen A und E fungieren,
wobei die Koppelwellen sich stufenlos verstellen lassen und durch den Anschluß von Nachschaltstufen an die Abtriebs­ welle (2) Gänge realisieren,
wobei ein Gangwechsel mit einem Wechsel der Koppelwellen ver­ bunden
und wobei schließlich alle Nachschaltstufen bei synchronen Drehzahlen, lastfrei und ohne Zugkraftunterbrechung geschal­ tet werden,
dadurch gekennzeichnet,
daß jeweils zum Anschluß der Koppelwellen A und E des vier­ welligen Planetengetriebes vor den Nachschaltstufen eine Schalt-Reibungskupplung vorgesehen ist,
daß Schalt-Zahnkupplungen die Verbindung der Nachschaltstufen mit der Abtriebswelle 2 besorgen und
daß die Schalt-Zahnkupplungen Synchronisierungseinrichtungen aufweisen.1. Infinitely variable hydrostatic-mechanical powershift transmission
Consisting of a four-shaft planetary gear transmission, a continuously adjustable hydrostatic transmission with a positive displacement machine a and a positive displacement machine b as well as gear shift stages,
wherein in the planetary gear a shaft forms the drive shaft 1, to which the displacement machine A is connected, a second shaft is the shaft B with which the Verdrän germaschine b is in communication, and act two waves as coupling shafts A and E,
the coupling shafts are infinitely adjustable and realize gears by connecting additional stages to the output shaft ( 2 ),
wherein a gear change with a change of the coupling shafts a related party
and finally all switching stages are switched at synchronous speeds, load-free and without interruption in tractive power,
characterized,
that a shift-friction clutch is provided in each case for connecting the coupling shafts A and E of the four-shaft planetary gear before the additional shift stages,
that gear-tooth clutches provide the connection of the secondary stages with the output shaft 2 and
that the gear clutches have synchronization devices. 2. Getriebe nach Anspruch 1 dadurch gekennzeichnet, daß in an sich bekannter Weise das Anfahren mit einer der beiden für die Koppelwellen A und E vorgesehenen Schalt- Reibungskupplungen geschieht.2. Transmission according to claim 1, characterized in that the starting takes place in a manner known per se with one of the two provided for the coupling shafts A and E switching friction clutches.
DE19883838768 1987-05-12 1988-05-09 Hydrostatic/mechanical power-shift transmission with a continuously variable effect and with toothed selector clutches for shifts proprietary to gear changes and multi-plate clutches for the gear changes Granted DE3838768A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19883838768 DE3838768A1 (en) 1987-05-12 1988-05-09 Hydrostatic/mechanical power-shift transmission with a continuously variable effect and with toothed selector clutches for shifts proprietary to gear changes and multi-plate clutches for the gear changes

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3715730 1987-05-12
DE19883838768 DE3838768A1 (en) 1987-05-12 1988-05-09 Hydrostatic/mechanical power-shift transmission with a continuously variable effect and with toothed selector clutches for shifts proprietary to gear changes and multi-plate clutches for the gear changes

Publications (2)

Publication Number Publication Date
DE3838768A1 true DE3838768A1 (en) 1989-06-08
DE3838768C2 DE3838768C2 (en) 1990-04-19

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DE19883838768 Granted DE3838768A1 (en) 1987-05-12 1988-05-09 Hydrostatic/mechanical power-shift transmission with a continuously variable effect and with toothed selector clutches for shifts proprietary to gear changes and multi-plate clutches for the gear changes

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DE (1) DE3838768A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5403241A (en) * 1987-05-12 1995-04-04 Friedrich Jarchow Infinitely variable hydrostatic mechanical power shift gearbox
WO2006132986A2 (en) * 2005-06-03 2006-12-14 Caterpillar Inc. Hydromechanical transmission

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4236671C1 (en) * 1992-10-30 1993-11-18 Jarchow Friedrich Staglessly working hydrostatic-mechanical load switch gear - comprises four-shaft gearwheel circulating gear, stagelessly adjustable hydrostatic gear comprising gearwheel switch stages, and switch couplings
DE19621201A1 (en) * 1996-05-25 1997-11-27 Zahnradfabrik Friedrichshafen Infinitely variable automotive gear box

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3709061A (en) * 1971-02-16 1973-01-09 Urs Syst Corp Non-regenerative hydromechanical transmission
US3709060A (en) * 1971-02-16 1973-01-09 Urs Syst Corp Narrow range hydromechanical transmission
DE2423626A1 (en) * 1973-05-17 1974-12-05 Orshansky Transmission Corp TRANSMISSION WITH POWER BRANCHING
US3888139A (en) * 1971-06-21 1975-06-10 Orshansky Transmission Corp Hydromechanical transmission
DE3147447C2 (en) * 1981-12-01 1984-06-14 Jarchow, Friedrich, Prof. Dr.-Ing., 4300 Essen Hydrostatic-mechanical actuating coupling gear with input-side power split
DE3512523C1 (en) * 1985-03-21 1986-09-11 Friedrich Prof. Dr.-Ing. 4300 Essen Jarchow Infinitely variable split-torque compound power-shift transmission with range changes
DE3622045A1 (en) * 1985-09-18 1987-03-26 Michael Meyerle CONTINUOUSLY HYDROMECHANICAL BRANCHING GEARBOX, ESPECIALLY FOR MOTOR VEHICLES

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3709061A (en) * 1971-02-16 1973-01-09 Urs Syst Corp Non-regenerative hydromechanical transmission
US3709060A (en) * 1971-02-16 1973-01-09 Urs Syst Corp Narrow range hydromechanical transmission
US3888139A (en) * 1971-06-21 1975-06-10 Orshansky Transmission Corp Hydromechanical transmission
DE2423626A1 (en) * 1973-05-17 1974-12-05 Orshansky Transmission Corp TRANSMISSION WITH POWER BRANCHING
DE3147447C2 (en) * 1981-12-01 1984-06-14 Jarchow, Friedrich, Prof. Dr.-Ing., 4300 Essen Hydrostatic-mechanical actuating coupling gear with input-side power split
DE3512523C1 (en) * 1985-03-21 1986-09-11 Friedrich Prof. Dr.-Ing. 4300 Essen Jarchow Infinitely variable split-torque compound power-shift transmission with range changes
DE3622045A1 (en) * 1985-09-18 1987-03-26 Michael Meyerle CONTINUOUSLY HYDROMECHANICAL BRANCHING GEARBOX, ESPECIALLY FOR MOTOR VEHICLES

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5403241A (en) * 1987-05-12 1995-04-04 Friedrich Jarchow Infinitely variable hydrostatic mechanical power shift gearbox
WO2006132986A2 (en) * 2005-06-03 2006-12-14 Caterpillar Inc. Hydromechanical transmission
WO2006132986A3 (en) * 2005-06-03 2007-01-18 Caterpillar Inc Hydromechanical transmission
US7530914B2 (en) 2005-06-03 2009-05-12 Caterpillar Inc. Hydromechanical transmission

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Publication number Publication date
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