EP1180078A1 - Transmission a branchement de puissance - Google Patents

Transmission a branchement de puissance

Info

Publication number
EP1180078A1
EP1180078A1 EP00927222A EP00927222A EP1180078A1 EP 1180078 A1 EP1180078 A1 EP 1180078A1 EP 00927222 A EP00927222 A EP 00927222A EP 00927222 A EP00927222 A EP 00927222A EP 1180078 A1 EP1180078 A1 EP 1180078A1
Authority
EP
European Patent Office
Prior art keywords
clutches
level
power split
split transmission
transmission according
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Withdrawn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
EP00927222A
Other languages
German (de)
English (en)
Inventor
Markus Liebherr
Josef HÄGLSPERGER
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
Priority claimed from DE19954894A external-priority patent/DE19954894A1/de
Application filed by Individual filed Critical Individual
Publication of EP1180078A1 publication Critical patent/EP1180078A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
    • B60K17/105—Units comprising at least a part of the gearing and a torque-transmitting axle, e.g. transaxles
    • 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
    • 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
    • F16H2047/045—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 the fluid gearing comprising a plurality of pumps or motors

Definitions

  • the invention relates to a power split transmission, in particular for tractors, wheel and chain driven work machines and commercial vehicles.
  • This includes vehicles and machines of all types, in particular wheeled vehicles and tracked vehicles of all types, self-propelled work machines and construction machinery as well as trucks, mobile cranes and the like.
  • the object of the invention is to provide an advantageous power split transmission.
  • the power split transmission has a mechanical branch (mechanical drive, mechanical branch transmission), a hydrostatic branch (hydrostatic drive, hydrostatic branch transmission) and one or more planetary gears.
  • the transmission input shaft of the power split transmission divides the power, for example the engine power of the tractor, the working machine, the other vehicle or the other machine, into a mechanical branch and into a hydrostatic branch.
  • the mechanical power share and the hydrostatic power component is then brought together again by the planetary gear and delivered.
  • a planetary gearbox another gearbox can be used, which makes it possible to combine the mechanical power share and the hydrostatic power share.
  • the mechanical branch preferably comprises several couplings. It is advantageous if multi-plate clutches are used.
  • the clutches or multi-plate clutches are preferably hydraulically lockable. They should preferably be opened with spring force.
  • the mechanical branch preferably comprises several shafts. It is advantageous if the mechanical branch comprises three shafts, which are preferably arranged in a triangle.
  • Another advantageous development is characterized in that several or all shafts of the mechanical branch are each provided with two couplings. It is advantageous if the respective first clutches and the respective second clutches lie in one plane.
  • the mechanical branch comprises three shafts, preferably arranged in a triangle, which are each provided with two clutches, preferably multi-plate clutches, it is advantageous if three clutches lie in one plane.
  • the first three clutches are therefore in one plane and the three second clutches are also in one plane.
  • the arrangement in which the respective first and second clutches lie in one plane is also advantageous with more or less than three shafts.
  • the mechanical branch comprises three shafts, preferably arranged in a triangle, two shafts each having two clutches, preferably multi-plate clutches.
  • two clutches preferably multi-plate clutches.
  • the first two clutches are therefore in one plane and the two second clutches are also in one plane.
  • a clutch can preferably be switched in one plane.
  • the fact that one clutch is switched in one plane means that a large number of gear ratios can be realized in an advantageous manner.
  • a further advantageous development is characterized in that the translations of the mechanical part are designed such that with a maximum 40% hydraulic power share of a stage, the next higher stage begins with 100% mechanical power. As a result, the hydraulic power can be kept low and in good efficiency. In certain applications, it may be sufficient that at least one or more translations of the mechanical part are designed in the manner described.
  • the hydrostatic part preferably has a pump and a motor (hydraulic motor). This is preferably a variable displacement pump and / or an adjusting motor. Pump and motor are arranged in a closed hydraulic circuit.
  • a motor (hydraulic motor), preferably an adjusting motor, is assigned to each planetary gear.
  • a planetary gear can be provided on each power-emitting side of the tracked vehicle or on each power-emitting wheel of the wheel-driven working machine for the purpose of combining power.
  • the sun gear of each planetary gear is driven separately by a motor or hydraulic motor or adjusting motor. In this way, the vehicle can be steered by the hydrostatic power share: GE wheel, which receives a larger hydrostatic power share, rotates faster, so that the vehicle makes a corresponding cornering.
  • a single pump which is preferably a variable displacement pump, supplies several or all of the motors.
  • the hydrostatic part preferably has a number of pumps, preferably a number of variable displacement pumps. It is advantageous if a pump is assigned to each motor and thus also to each planetary gear. In this case, each individual motor can be supplied with its own pump. This has the advantage that losses from pressure differences can be avoided.
  • a further advantageous development is characterized in that the direction of rotation of the sun gear of the planetary gear remains the same after the starting stage up to the highest gear, preferably up to the 6th gear.
  • the starting level can be 2nd gear, but also 3rd or 4th gear. This is particularly advantageous if the level change is or is automated.
  • the invention further relates to a tractor or a wheel-driven or chain-driven work machine or a commercial vehicle (a commercial vehicle), which is characterized by a power split transmission according to the invention.
  • Fig. 1 shows a power split transmission in a schematic view
  • the power split transmission shown in Fig. 1 consists of a mechanical branch 1, a hydrostatic branch 2 and a planetary gear 3 Input 4 of the power split transmission is connected via a universal joint 5 to the transmission input shaft 6, which divides the input power into a mechanical branch and a hydrostatic branch.
  • the mechanical power component and the hydrostatic power component are then combined again by the planetary gear 3 (a differential gear could also be used instead of the planetary gear).
  • the planetary gear 3 has a sun gear 7, a planet carrier 8 with planet gears and a ring gear 9.
  • the sum of the powers of the mechanical branch and the hydrostatic branch is delivered to the axle transfer case via the planetary web 8. This takes place via a gearwheel 11 which is connected to the planetary web 8 and which cooperates with a gearwheel 12 seated on the transmission output shaft 10.
  • the transmission output shaft 10 is connected to the axles via universal joints 13, 14, 15, 16.
  • the mechanical branch 1 or the mechanical drive consists of three shafts 17, 18 arranged in a triangle; 19, 20 and 21, 22 with two clutches 2, C; R, B and 1, A. There are three couplings on one level.
  • the three first clutches 2, R and 1, which are connected to the input shafts 17, 19 and 21, lie in one plane, namely in plane 1.
  • the three clutches C, B and A, which are connected to the output shafts 18, 20 and 22 are connected in one level, namely in level 2.
  • the input and output shafts of two clutches are aligned with one another, namely the input and output shafts 17 and 18 of clutches 2 and C, which Input and output shafts 19 and 20 of the clutches R and B and the input and output shafts 21 and 22 of the clutches 1 and A.
  • All clutches are multi-plate clutches. Furthermore, all clutches can be switched under load.
  • the transmission input shaft 6 is connected to gears 23, 24, 25.
  • the gear 23 cooperates with the gear 26, which is seated on the input shaft 21.
  • the gear 24 cooperates with the gear 27, which is on the input shaft 19 sits.
  • the gear 25 cooperates with the gear 28 which sits on the input shaft 17.
  • the gearwheel 29 is seated on the output shaft 18.
  • the gearwheels 30 and 31 and the ring gear 9 of the planetary gear are seated on the output shaft 20.
  • Gear 32 is seated on output shaft 22.
  • the clutches 2 and C include a clutch housing with a clutch gear 33.
  • the clutches R and B include a clutch housing with a clutch gear 34.
  • the clutches 1 and A include a clutch housing with a clutch gear 35.
  • the clutch gears 33, 34 and 35 engage into each other.
  • the three shafts 17, 18 and 19, 20 and 21, 22 are arranged in a triangle.
  • a clutch is always switched from each level in order to obtain a continuous flow of power up to the ring gear 9 of the planetary gear.
  • One of the clutches 2, R or 1 of level 1 is always switched and one of the clutches C, B or A of level 2.
  • the clutches designed as multi-plate clutches are hydraulically closed and opened with spring force.
  • the planetary gear is seated on the shaft with which a change in direction of rotation can be achieved at three speeds, namely on shaft 20.
  • the three speeds with the opposite direction of rotation can be used for reversing.
  • the hydrostatic branch 2 or the hydrostatic drive consists of a variable displacement pump 36, which can be driven by the transmission input shaft 6, and an adjusting motor (hydraulic motor) 37, which interact in a closed hydraulic circuit 38.
  • the shaft 39 of the sun gear 7 of the planetary gear can be driven by the adjusting motor.
  • the ring gear 9 of the planetary gear can be driven mechanically in six speeds in one direction of rotation and in three speeds in the other direction of rotation; the sun gear 7 of the planetary gear can be driven hydrostatically continuously in both directions of rotation.
  • a particular advantage of the power split transmission is that the power can be transmitted fully hydrostatically or fully mechanically or in a mixed manner.
  • the mechanical ratios in mechanical branch 1 are laid out in such a way that with a maximum 40% hydraulic power share of a stage, the next higher stage begins with 100% mechanical power. As a result, the hydraulic power can be kept low and in good efficiency.
  • FIG. 2 shows a modified embodiment of a power split transmission, in which those components which correspond to the embodiment according to FIG. 1 are provided with the same reference symbols, so that they do not have to be described again.
  • the power split transmission consists of a mechanical branch 1, a hydrostatic branch 2 and two planetary gears 41, 42, each of which is assigned an adjusting motor (hydraulic motor) 43 and 44.
  • the mechanical branch 1 consists of three shafts 17, 18 arranged in a triangle; 19, 29 and 21, 22, but two clutches 2, B and 1, A are provided only on the shafts 17, 18 and 21, 22.
  • clutches 2 and 1 which are connected to the input shafts 17 and 21 (level 1)
  • the clutches B and A which are connected to the output shafts 18 and 22 ( Level 2).
  • the input and output shafts of two clutches are aligned with one another, namely the input and output shafts 17 and 18 of clutches 2 and B and the input and output shafts 21 and 22 of clutches 1 and A.
  • the transmission input shaft 6 is connected to gears 23 and 25.
  • the gear 23 cooperates with the gear 26, which is seated on the input shaft 21.
  • the gear 25 cooperates with the gear 28 which sits on the input shaft 17.
  • the gearwheel 29 is seated on the output shaft 18.
  • the gearwheels 30 and 31 as well as the gearwheel (bevel gear) 45 of an axle transfer gear 46 are seated on the output shaft 20, which meshes with a further gearwheel (bevel gear) 47 of the axle transfer gearbox 46, which sits on a shaft 48 .
  • the axes of rotation of the gear wheels (bevel gears) 45 and 47 run at right angles to one another.
  • Gear 32 is seated on output shaft 22.
  • the clutches 2 and B include a clutch housing with a clutch gear 33.
  • the clutches 1 and A include a clutch housing with a clutch gear 35.
  • the clutch gear 33 engages with a gear 34 which in turn engages with the gear 35.
  • the shafts 17, 18 and 19, 20 and 21, 22 are arranged in a triangle.
  • a clutch is always switched on each level, i.e. one of the clutches 2 and 1 of level 1 and one of the clutches B and A of level 2.
  • the hydrostatic branch 2 consists of two adjusting pumps 49, 50, which can be driven by the transmission input shaft 6, and the two adjusting motors (hydraulic motors) 43 and 44, the first variable pump 49 interacting with the first variable motor 43 in a closed hydraulic circuit 51 and the second variable pump 50 interacting with the second adjusting motor 44 in a second closed hydraulic circuit 52.
  • the shaft 53 of the sun gear of the first planetary gear 41 can be driven by the first adjustment motor 43.
  • the shaft 54 of the sun gear of the second planetary gear 42 can be driven by the second adjustment motor 44.
  • gear wheels 55, 56 are provided, each of which engages in toothings which are provided on the ring gears of the planetary gears 41 and 42.
  • the planetary web 57 of the first planetary gear 41 is connected to a first wheel 58 of a wheel-driven working machine.
  • the planetary web 59 of the second planetary gear 42 is connected to a second wheel 60 of the wheel-driven working machine.
  • the wheel-driven working machine can be steered by adjusting the adjustment motors 43 and 44 differently.
  • the power is combined at the output of the mechanical branch and in front of the axle transfer gear.
  • the embodiment shown in FIG. 2 is suitable, in which the mechanical branch is guided up to the wheels 58, 60 or chains and in which the power is combined at the end the drive train is made.
  • the sun wheel of each of these planetary gears is driven separately by a hydraulic motor 43, 44. This allows the vehicle to be steered by the hydrostatic power component.
  • a single pump can supply all hydraulic motors or, in order to avoid losses from pressure differences, every single individual motor 43, 44 are supplied with their own pump 49, 50, as shown in Figure 2.
  • the number of mechanical stages can be reduced and placed in the main working direction in order to obtain a high mechanical power share and a low hydrostatic power share. Reversing can be done fully hydrostatically by blocking the ring gear. You can also drive fully hydrostatically in both directions.
  • FIG. 1 is primarily suitable for tractors
  • FIG. 2 is primarily suitable for wheel and chain-driven machines.

Abstract

Une transmission à branchement de puissance est utilisée principalement pour des tracteurs, des machines de chantier à entraînement par roues et par chaînes, ainsi que pour des véhicules utilitaires. En vue d'obtenir une transmission de puissance avantageuse, celle-ci comprend une dérivation mécanique (1), une dérivation hydrostatique (2) et un ou plusieurs trains planétaires (3) au moyen desquels la fraction de puissance mécanique et la fraction de puissance hydrostatique sont recombinées.
EP00927222A 1999-05-25 2000-05-19 Transmission a branchement de puissance Withdrawn EP1180078A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19923974 1999-05-25
DE19923974 1999-05-25
DE19954894 1999-11-15
DE19954894A DE19954894A1 (de) 1999-05-25 1999-11-15 Leistungsverzweigungsgetriebe
PCT/EP2000/004538 WO2000071377A1 (fr) 1999-05-25 2000-05-19 Transmission a branchement de puissance

Publications (1)

Publication Number Publication Date
EP1180078A1 true EP1180078A1 (fr) 2002-02-20

Family

ID=26053511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00927222A Withdrawn EP1180078A1 (fr) 1999-05-25 2000-05-19 Transmission a branchement de puissance

Country Status (3)

Country Link
EP (1) EP1180078A1 (fr)
CA (1) CA2383121A1 (fr)
WO (1) WO2000071377A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109723789A (zh) * 2019-01-16 2019-05-07 江苏大学 一种混合动力多模式切换的无级变速传动系统

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002243018A (ja) * 2001-02-14 2002-08-28 Sauer-Danfoss-Daikin Ltd 液圧機械式変速装置及びその変速装置を搭載した車両
JP2004217111A (ja) 2003-01-16 2004-08-05 Komatsu Ltd ホイール式作業車両のトランスミッション
EP2193293B1 (fr) 2007-10-02 2011-11-23 ZF Friedrichshafen AG Transmission de répartition de puissance hydrostatique-mécanique
AT11366U1 (de) 2009-06-04 2010-09-15 Dieter Ing Stoeckl Überlagerungsgetriebe
EP2955418B1 (fr) 2014-06-13 2019-02-20 Perkins Engines Company Limited Transmission assistée par variateur

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4115624C2 (de) * 1991-05-14 1995-06-22 Deere & Co Hydrostatisch-mechanisches Leistungsverzweigungsgetriebe
US5249475A (en) * 1992-08-31 1993-10-05 Deere & Company Eight- to sixteen-speed powershift transmission
DE4443267A1 (de) * 1994-12-05 1996-06-13 Claas Ohg Lastschaltgetriebe mit 5-welligem Umlaufgetriebe
JP3465470B2 (ja) * 1996-03-12 2003-11-10 ダイキン工業株式会社 無段変速機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0071377A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109723789A (zh) * 2019-01-16 2019-05-07 江苏大学 一种混合动力多模式切换的无级变速传动系统
CN109723789B (zh) * 2019-01-16 2021-07-20 江苏大学 一种混合动力多模式切换的无级变速传动系统

Also Published As

Publication number Publication date
CA2383121A1 (fr) 2000-11-30
WO2000071377A1 (fr) 2000-11-30

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