EP2591250A2 - Transmission à dérivation de puissance hydrostatique-mécanique à variation continue, procédé de fonctionnement d'une telle transmission à dérivation de puissance, ainsi que chargeuse sur roues équipée de cette transmission à dérivation de puissance - Google Patents

Transmission à dérivation de puissance hydrostatique-mécanique à variation continue, procédé de fonctionnement d'une telle transmission à dérivation de puissance, ainsi que chargeuse sur roues équipée de cette transmission à dérivation de puissance

Info

Publication number
EP2591250A2
EP2591250A2 EP11733609.9A EP11733609A EP2591250A2 EP 2591250 A2 EP2591250 A2 EP 2591250A2 EP 11733609 A EP11733609 A EP 11733609A EP 2591250 A2 EP2591250 A2 EP 2591250A2
Authority
EP
European Patent Office
Prior art keywords
hydrostatic
power split
split transmission
power
displacement
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Withdrawn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
EP11733609.9A
Other languages
German (de)
English (en)
Inventor
Markus Liebherr
Peter Dziuba
Josef HÄGLSPERGER
Erich Eckhardt
Patrick Wohlhauser
Franz-Josef Schwede
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.)
Mali Holding AG
Original Assignee
Mali Holding 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
Priority claimed from CH01119/10A external-priority patent/CH703429A1/de
Priority claimed from CH01296/10A external-priority patent/CH703566A1/de
Application filed by Mali Holding AG filed Critical Mali Holding AG
Publication of EP2591250A2 publication Critical patent/EP2591250A2/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Withdrawn legal-status Critical Current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
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/40—Special vehicles
    • B60Y2200/41—Construction vehicles, e.g. graders, excavators
    • B60Y2200/415—Wheel loaders
    • 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
    • F16H2037/044—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion comprising a separate gearing unit for shifting between forward or reverse
    • 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
    • F16H2037/049—Forward-reverse units with forward and reverse gears for achieving multiple forward and reverse gears, e.g. for working machines
    • 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
    • F16H2037/0866—Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • 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
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital 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
    • 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
    • F16H3/14—Gearings for reversal only

Definitions

  • Stepless hydrostatic-mechanical power split transmission method for operating such a power split transmission, and wheel loader with such a power split transmission
  • the present invention relates to the field of vehicle drives. It relates to a continuously variable hydrostatic-mechanical power split transmission according to the preamble of claim 1, which is preferably intended for use in wheel loaders.
  • FIG. 1 An exemplary wheel loader of a higher performance class, as it is known from US D540352, is shown in Fig. 1 in the side view.
  • the wheel loader 1 0 of FIG. 1 comprises a front part 1 1 and a H interteil 1 2, which are pivotable for steering the vehicle against each other about a vertical pivot axis.
  • a front axle 1 3 is arranged with corresponding wheels, in H interteil 1 2
  • a hydraulically movable arm 1 8 is arranged at the front end of a hydraulically movable blade 1 6 is attached.
  • a part of the hydraulic system can be seen and designated by the reference numeral 1 7.
  • the wheel loader 10 is driven by an internal combustion engine 20, which is arranged behind the rear axle 1 4 for reasons of weight compensation.
  • a propeller shaft 1 5 runs to the front axle 1 3, which is also driven.
  • the front part 1 1 is hydraulically pivoted relative to the H interteil 1 2.
  • Such a wheel loader 1 0 has just in Erdschuls than partially greater distances in both forward drive and in reverse drive. Furthermore, if For example, the scoop 1 6 is pushed to receive soil in the ground, a high initial torque needed to overcome the resistance during insertion of the blade 1 6. Overall, therefore, there is a desire to have a high torque at the wheels available at the beginning of the driving range and to be able to cover a large speed range as possible without traction interruption both in forward drive and in reverse.
  • a power split transmission with a hydrostatic power branch and a mechanical power branch which should be suitable for wheel loaders via a first drive range clutch a first drive range and a second drive range clutch a second drive range and a clutch for reversing a reverse range to Provides.
  • the hydrostatic power branch is formed by two hydrostats operating as pump and motor, which are only synchronously adjustable with each other via a common component.
  • the subdivision of the forward driving range by mechanical transmission means in a first and second driving range is mechanically complex. The positively coupled adjustment of the two hydrostats leads to severe limitations of the working area.
  • the publication DE 2335629 discloses a drive device, in particular for agricultural and construction-use vehicles, which operates with a hydrostatic-mechanical power split and has a hydrostatic primary machine and two hydrostatic secondary machines in the hydrostatic power branch, which are fixedly coupled to one another via a common shaft ,
  • This known drive device completely dispenses with mechanical switching means. The transition between reverse and forward is thereby by changing the direction of rotation of the secondary machinery causes.
  • the disadvantage here is that the speed range for reversing only about half as large as in the forward drive.
  • the power delivered by an internal combustion engine to a drive shaft is distributed via a planetary drive to a mechanical branch and a hydrostatic branch and summed on the output side with the aid of summation means, the hydrostatic branch having at least one first pump operating volume in the displacement volume or conveying volume adjustable hydrostats and at least one second, acting as a motor, adjustable in displacement volume Hydrostat, which are hydraulically connected to each other, wherein a forward drive range and a reverse range are provided.
  • both the forward drive range and the reverse drive range are steplessly passable exclusively by adjusting the displacement volumes of the hydrostatic drives, that two second hydrostatic drives are provided which operate as motors and that a reversing drive is provided for changing between the forward drive range and the reverse drive range is.
  • An embodiment of the power split transmission according to the invention is characterized in that the reversing gear at the output of the power split transmission bes is arranged, and that the reversing comprises a reversing clutch with which the summed power can be given either via a first drive unit for forward drive or a second drive unit for the reverse drive to an output shaft. H hereby a particularly compact construction of the transmission is made possible.
  • the reversing gear is arranged at the input of the power branching transmission, and that the reversing gear comprises a reversing clutch with which the input power either via a first drive unit for forward drive or a second Cetriebeein unit for reversing on the Power branching gear can be given.
  • Another embodiment of the power split transmission according to the invention is characterized in that the two second hydrostats have the same design, that the two second hydrostats each have a maximum displacement that corresponds to the maximum displacement of the first hydrostat, and that the two second hydrostats are synchronously adjustable. As a result, a high torque at the beginning of the driving range is available.
  • Another embodiment of the power split transmission according to the invention is characterized in that the two second hydrostats are connected to each other in a rotationally fixed manner via a common shaft and that the common shaft acts as a summation shaft for the summation of the powers of the two power branches. This measure also reduced space requirements.
  • Another embodiment of the power split transmission according to the invention is characterized in that the hydrostats are designed as swivellable oblique-axis hydrostats in wide-angle technology and in particular in each case pivoting having from 0 ° to at least 45 °. In this way, a high efficiency can be achieved over a wide speed range.
  • Another embodiment of the inventive power split transmission is characterized in that the drive shaft is guided as a central shaft through the transmission and drives at the output of the transmission arranged pump units.
  • the inventive method for operating a power split transmission according to the invention is characterized in that to achieve a continuous forward range before starting first the displacement or delivery volume of the first Hydrostaten to zero and the displacement of the second Hydrostaten is set to maximum, that in a first phase the sip volume of the second hydrostats is kept at maximum and the sip volume of the first hydrostate in the forward direction is increased until it reaches its maximum in the forward direction, and in a second phase the sip volume of the first hydrostate is maintained at its maximum and the sump volume of the second hydrostats is maintained Maximum is reduced to zero.
  • An embodiment of the method according to the invention is characterized in that to achieve a continuous reverse range of the direction of rotation at the input or output of the power split transmission is reversed by a reversing, and that is reversed in the direction of rotation of the stepless forward range.
  • the wheel loader according to the invention is equipped with a front axle and a H interachse, as well as arranged between two axles cabin and an arranged behind the rear axle combustion engine. It is characterized in that in front of the internal combustion engine in the region of the H interachse a power-split transmission connected to the internal combustion engine is provided according to the invention.
  • An embodiment of the wheel loader according to the invention is characterized in that the H interachse of the wheel loader is driven via the power split transmission.
  • An embodiment of the wheel loader according to the invention is characterized in that the front axle of the wheel loader is also driven via a cardan shaft.
  • FIG. 1 in side view of an exemplary wheel loader, as from the prior
  • FIG. 2 shows the transmission diagram of a power split transmission according to an embodiment of the present invention
  • Fig. 3 based on three sub-figures 3a), 3b) and 3c) the adjustment of the hydrostats of the power split transmission of Figure 2 for sweeping the forward drive range, wherein for the sake of simplicity, only one of the two second hydrostat is shown.
  • Fig. 2 the transmission diagram of a power split transmission according to an embodiment of the present invention is shown.
  • the power split transmission 40 is connected via a drive shaft 21 with an internal combustion engine 20, which is symbolized by an indicated crankshaft.
  • the drive shaft 21 is rotatably connected to the planet carrier 23 of a planetary drive 22, which has a sun gear 25, 26, a Planetary gear 24 and a ring gear 27 includes.
  • a first Hydrostat H l which operates as a pump P, with the planetary gear 22 in operative connection.
  • the part 26 of the sun gear 25, 26 meshes with a gear 29 which is non-rotatably mounted on a summation shaft 41.
  • the summation wave 41 is at the same time the common connecting shaft of two second hydrostatic units H2, which operate as motors M and are supplied with hydraulic pressure fluid from the first hydrostatic unit H1 via lines which are not shown.
  • a second gear 31 is further arranged rotatably, which meshes with a gear 30 which is connected via a hollow shaft with a reversing coupling 32.
  • the first and second hydrostats H 1, H 2 are preferably of the oblique-axis type and implemented in a wide-angle technique and can be carried out as described and shown in the publication WO 2006 / 042434A1.
  • the Reversierkupplung 32 switches the power taken from the summation of wave 41 selectively via a first Cetriebeech 33 or a second Cetriebeech 34 on a propeller shaft 35, which connects the provided with a bevel gear 36 H interaxis HA with the front axle VA.
  • the first Cetriebeech 33 is designed for the forward drive V, the second Cetriebeech 34 by reversing the direction of rotation for the reverse drive R.
  • the power split transmission 40 is preferably disposed immediate area of the rear axle HA and can be combined with the bevel gear 36 to a structural unit.
  • the input of the reversing clutch 32 is connected to the drive shaft 21 and switches the power either over the first Ce gear unit 33 or the second gear unit 34 on the planet carrier 23 of the power branching gear 40th
  • the sun gear 25, 26 of the planetary drive 22 is connected via a hollow axle.
  • a hollow axle Through this hollow axle, as well as through the other hollow shaft which connects the gear 30 with the reversing coupling 32 extends in extension of the drive shaft 21, a central shaft 37 through the transmission and drives two pump units 38 and 39, which the hydraulics of the wheel loader with hydraulic Supply pressure fluid.
  • FIG. 3 forward travel range
  • the first hydrostat H l is not pivoted and thus has a vanishing displacement volume or delivery volume
  • the second hydrostat H2 is fully (approximately 45 °) pivoted and the maximum absorption volume Has.
  • the first hydrostat is swung out to the responsible for the forward movement upper side, whereby the vehicle is picking up speed.
  • the maximum deflection of the second hydrostatic units H2 ensures a high torque (high tensile force) at a low rotational speed. If the first hydrostat H l is fully deflected (FIG. 3 b), it is held there and the second hydrostatic units H 2 are swung back inwards to the zero position (vanishing displacement volume) (FIG. 3 c). The decreasing absorption volume in the second hydrostat H2 ensures ever higher rotational speed with decreasing torque.
  • a power of 90 kW can be transmitted.
  • the wheel loader 1 0 reaches a speed of 50 km / h at a speed of the internal combustion engine 20 of 2200 U / min.
  • the pumping first hydrostat H 1 has, for example, a maximum displacement volume or delivery volume of 1 60 cm 3
  • the hydrostatic units H 2 working as motors each have a maximum absorption volume of likewise approximately 1 60 cm 3 .
  • the hydrostat is designed accordingly (eg with several 1 00 cm 3 displacement), also significantly higher power can be transmitted. It is therefore quite conceivable that such a transmission is also used in ship propulsion or track vehicles.
  • the absorption volume of the first hydrostat H l and the displacement of the second hydrostatic units H2 are adjustable independently of one another, it is possible and advantageous that the adjustment of the displacement volumes takes place in accordance with the high pressure prevailing in the hydraulic circuit of the hydrostats. It is particularly advantageous if, in a starting region, the second hydrostatic units H2 are operated in the region of their maximum absorption volume, and if the intake volume of the first hydrostatic unit H1 is controlled to control the traction force.
  • this can be done by adjusting the displacement of the first hydrostatic valve H l via a spring-centered actuating system subjected to a speed-proportional control pressure, and to control the first hydrostatic valve H 1 in such a way that the high-pressure-proportional actuating forces are combined with the spring-centered actuating system and the speed-proportional control pressure, the desired tensile force or torque characteristic result.
  • H 1 .H 2 hydrostat e.g., sloped axis type

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une transmission à dérivation de puissance (40) hydrostatique-mécanique à variation continue pour un véhicule utilitaire tel qu'une chargeuse sur roues. Dans cette transmission à dérivation de puissance (40), la puissance transmise par un moteur de combustion à un arbre moteur (21) est répartie par l'intermédiaire d'un train planétaire (22) entre une branche mécanique (26, 29) et une branche hydrostatique (H1, H2), et additionnée à l'aide de moyens totalisateurs (41) du côté sortie, la branche hydrostatique (H1, H2) comportant au moins un premier ensemble hydrostatique (H1) à cylindrée réglable, travaillant en pompe (P), et au moins un second ensemble hydrostatique (H2) à cylindrée réglable, travaillant en moteur (M), reliés par une liaison hydraulique, une plage de marche avant (V) et une plage de marche arrière (R) étant prévues. Pour obtenir une telle transmission à dérivation de puissance présentant une structure compacte, ainsi qu'un couple initial élevé et une grande gamme de vitesses lors de la marche avant et de la marche arrière, il est prévu que le parcours de la plage de marche avant (V) et de la plage de marche arrière (R) se fasse en continu uniquement par modification des cylindrées des ensembles hydrostatiques (H1, H2), et que la transmission comporte des seconds ensembles hydrostatiques (H2) travaillant en moteur (M), ainsi qu'un inverseur (32, 33, 34) pour le passage entre la plage de marche avant (V) et la plage de marche arrière (R).
EP11733609.9A 2010-07-09 2011-06-29 Transmission à dérivation de puissance hydrostatique-mécanique à variation continue, procédé de fonctionnement d'une telle transmission à dérivation de puissance, ainsi que chargeuse sur roues équipée de cette transmission à dérivation de puissance Withdrawn EP2591250A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH01119/10A CH703429A1 (de) 2010-07-09 2010-07-09 Stufenloses hydrostatisch-mechanisches Leistungsverzweigungsgetriebe, Verfahren zum Betrieb eines solchen Leistungsverzweigungsgetriebes, sowie Radlader mit einem solchen Leistungsverzweigungsgetriebe.
CH01296/10A CH703566A1 (de) 2010-08-11 2010-08-11 Verfahren zum Betrieb eines stufenlosen Getriebes mit hydrostatisch-mechanischer Leistungsverzweigung sowie Getriebe zur Durchführung des Verfahrens.
PCT/EP2011/060944 WO2012004173A2 (fr) 2010-07-09 2011-06-29 Transmission à dérivation de puissance hydrostatique-mécanique à variation continue, procédé de fonctionnement d'une telle transmission à dérivation de puissance, ainsi que chargeuse sur roues équipée de cette transmission à dérivation de puissance

Publications (1)

Publication Number Publication Date
EP2591250A2 true EP2591250A2 (fr) 2013-05-15

Family

ID=45441584

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11733609.9A Withdrawn EP2591250A2 (fr) 2010-07-09 2011-06-29 Transmission à dérivation de puissance hydrostatique-mécanique à variation continue, procédé de fonctionnement d'une telle transmission à dérivation de puissance, ainsi que chargeuse sur roues équipée de cette transmission à dérivation de puissance

Country Status (3)

Country Link
EP (1) EP2591250A2 (fr)
RU (1) RU2013105451A (fr)
WO (1) WO2012004173A2 (fr)

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CN104728385A (zh) * 2015-03-23 2015-06-24 合肥工业大学 并联式双流变速传动装置

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EP3037692B1 (fr) * 2014-12-23 2018-02-07 NAF Neunkirchener Achsenfabrik AG Boîte de vitesses à division de puissance pour un véhicule automobile
DE102016200755A1 (de) 2016-01-20 2017-07-20 Avl Commercial Driveline & Tractor Engineering Gmbh Stufenloses, hydrostatisch-mechanisches Leistungsverzweigungsgetriebe sowie Nutzfahrzeug mit einem solchen Leistungsverzweigungsgetriebe
DE102016200752A1 (de) 2016-01-20 2017-07-20 Avl Commercial Driveline & Tractor Engineering Gmbh Stufenloses, hydrostatisch-mechanisches Leistungsverzweigungsgetriebe, Nutzfahrzeug mit einem solchen Leistungsverzweigungsgetriebe sowie Verfahren zum Betrieb eines derartigen Leistungsverzweigungsgetriebes
CN105966381B (zh) * 2016-06-15 2019-05-14 中国煤炭科工集团太原研究院有限公司 煤矿四驱车辆用智能电子式轴间扭矩分配控制***及方法
DE102018004409A1 (de) 2018-06-05 2019-12-05 RODIING GmbH Antriebssystem sowie Mehrachsenfahrzeug mit zumindest einem solchen
JP6924292B2 (ja) 2020-01-22 2021-08-25 日本化薬株式会社 エポキシ樹脂混合物、エポキシ樹脂組成物およびその硬化物

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CN104728385B (zh) * 2015-03-23 2017-02-22 合肥工业大学 并联式双流变速传动装置

Also Published As

Publication number Publication date
RU2013105451A (ru) 2014-08-20
WO2012004173A3 (fr) 2012-12-27
WO2012004173A2 (fr) 2012-01-12

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