WO2019174852A1 - Boîte de vitesses compacte à commande sous charge - Google Patents

Boîte de vitesses compacte à commande sous charge Download PDF

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Publication number
WO2019174852A1
WO2019174852A1 PCT/EP2019/053770 EP2019053770W WO2019174852A1 WO 2019174852 A1 WO2019174852 A1 WO 2019174852A1 EP 2019053770 W EP2019053770 W EP 2019053770W WO 2019174852 A1 WO2019174852 A1 WO 2019174852A1
Authority
WO
WIPO (PCT)
Prior art keywords
switching element
switching
shaft
gear
rotation
Prior art date
Application number
PCT/EP2019/053770
Other languages
German (de)
English (en)
Inventor
Martin Reck
Wolfgang Rebholz
Original Assignee
Zf Friedrichshafen 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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2019174852A1 publication Critical patent/WO2019174852A1/fr

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
    • 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
    • F16H3/093—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 with two or more countershafts
    • F16H2003/0935—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 with two or more countershafts with multiple countershafts comprising only one idle gear and one gear fixed to the countershaft
    • 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
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means

Definitions

  • the present invention relates to a compact power transmission for a work machine such as a construction machine, an agricultural machine, a forklift or the like.
  • the invention relates to a compact construction of such a transmission, which can be carried out in particular with a small axial dimension.
  • Power transmissions for work machines are known and offer the advantage that the switching between switching stages with different gear ratios is also possible during a load transfer between input shaft and output shaft.
  • switching elements in the form of clutches are selectively switched to switch from one switching stage to another switching stage, so that a power break during the switching process can be avoided as well as possible.
  • a power shift transmission according to the prior art is disclosed in DE 10 2008 002 069 A1.
  • this transmission several gear stages are provided to allow multiple switching stages.
  • a power shift transmission according to the invention can be used for a work machine.
  • the power shift transmission may have a drive shaft and an output shaft.
  • a rotation of the drive shaft selectively transferable to achieve multiple switching stages via spur gears
  • the spur gear sets may include: a coupled to the drive shaft first fixed wheel, which is selectively coupled via a first switching element with a first intermediate gear; a meshing with the first fixed gear second intermediate wheel, the over a second switching element is selectively coupled to a second fixed gear, and coupled to an intermediate shaft third fixed gear, which is selectively coupled via a third switching element with a third Eisenradrad which meshes with the second fixed gear, coupled.
  • the driving force is transferable to the output shaft through a single load-carrying engagement of a pair of gears from the drive shaft.
  • a single load-carrying engagement namely between the first fixed gear and the second intermediate gear
  • the first switching element may be provided on the drive shaft, the second switching element may be provided on the output shaft and the third switching element may be provided on the intermediate shaft.
  • the switching elements are each provided on one of the shafts and there are no further waves for receiving the switching elements necessary.
  • the meshing engagement between the gears designated as fixed gears and intermediate gears means that the teeth of the corresponding gear pairing mesh with each other and thereby a force is transferable from one gear to the other gear of the gear pair.
  • the gears used may be straight-toothed or helical gears.
  • the first fixed gear can be directly connected to the drive shaft.
  • the first switching element may be fixedly connected to the first fixed gear and produce a selective connection between the first fixed gear and the first intermediate gear.
  • the second switching element may be fixedly connected to the second fixed gear and produce a selective connection between the second fixed gear and the second intermediate gear.
  • the second fixed wheel can be connected directly to the output shaft.
  • the third switching element may be firmly connected to the third fixed gear and produce a selective connection between the third fixed gear and the third intermediate gear.
  • a first shift stage having a first gear ratio with respect to rotation on the input shaft and rotation on the output shaft can be effected.
  • a second switching stage with a second gear ratio with respect to the rotation of the input shaft and the rotation of the output shaft can be brought about.
  • the first gear ratio may differ from the second gear ratio.
  • the first gear ratio may be smaller than the second gear ratio, so that when starting or when the need for a larger driving force on drive wheels, the first gear ratio can be used, while the second gear ratio can be used at higher speeds.
  • the ratios of the first and second switching stage can be set according to the application by different diameter ratios of the gears.
  • a third shift stage having a third gear ratio with respect to the rotation of the input shaft and the rotation of the output shaft is brought about, wherein the rotational direction of the output shaft in the third switching stage corresponds to the direction of rotation of the input shaft.
  • the third switching stage can be used as a reverse switching stage, while the first and second switching stage can serve as a forward switching stage.
  • the transmission with a forward shift stage and two reverse shift stages by setting up the linkage of the transmission to the work machine accordingly.
  • the direction of rotation of the output shaft is in the first and second switching stage opposite to the direction of rotation of the input shaft.
  • the arrangement of gear sets, which have pairs of gears in the first and second shift stage, the direction of rotation is reversed with respect to the input speed.
  • the first, second and third shift element may be formed as a multi-plate clutch.
  • a multi-disc clutch can be engaged and disengaged by hydraulic or mechanical actuation. In this case, a certain slip is also allowed at the transition between engaged and disengaged state and thus shocks when switching the switching stages can be reduced.
  • the switching element may also have another configuration, as long as the function for selectively connecting and disconnecting between the elements is provided, between which the switching element is provided.
  • the switching of the shift stages is enabled by operating the shift members under load. This is accomplished by the particular construction in which a gear set is incorporated by engaging a switching element in the power flow, while at the same time excluding another gear set from force flow by disengaging a switching element.
  • the output shaft and the intermediate shaft may be arranged parallel to the drive shaft.
  • a compact structure is achieved, in which in particular the axial dimension of the transmission can be made short.
  • the centers of the intermediate shaft, the drive shaft and the output shaft can form a triangle, so that the size of the transmission can be reduced overall.
  • the first, second and third switching element can be arranged aligned in an axial region of the transmission, in particular between two planes, in order to further optimize the use of the installation space.
  • the drive shaft may be connected to a torque converter which transmits driving force introduced thereto from a drive source to the drive shaft.
  • the torque converter may be a hydrodynamic converter which, depending on the input speed, the connection establishes or interrupts between the drive source and drive shaft.
  • the drive source may be an internal combustion engine, such as a diesel engine or the like, and may also include a hybrid drive or a hydraulic drive.
  • Fig. 1 is a schematic and simplified representation of a power shift transmission according to an embodiment of the invention.
  • Figs. 2 a-c show the transmission in a schematic representation with power flows indicated therein for the various switching stages.
  • the power shift transmission according to the illustrated embodiment has a transmission housing 14, in which the elements of the power shift transmission are housed.
  • a drive shaft 1 extends through the transmission housing 14 and is connected outside of the transmission housing 14 with a hydrodynamic torque converter 13.
  • the torque converter 13 is connected on the input side to an output shaft of an internal combustion engine, not shown.
  • the introduced into the torque converter 13 driving force is transmitted in a known manner to the drive shaft 1.
  • an oil pump 15 Connected to the input member of the torque converter 13 is an oil pump 15 which generates a required oil pressure.
  • a first fixed wheel 4 is fixedly mounted so that it rotates with the drive shaft 1.
  • a first switching element 5 is provided in the form of a multi-plate clutch.
  • the first switching element 5 is fixedly connected to the first fixed gear 4 and is provided to connect a first intermediate gear 6 to the first fixed gear 4 when it is engaged.
  • the first fixed gear 4 and the first intermediate gear 6 are rotatable relative to each other.
  • an output shaft 2 is provided, with which a second fixed wheel 9 is fixedly connected and which is guided through the gear housing 14 to the outside.
  • a second switching element 8 is provided in the form of a multi-plate clutch.
  • the second switching element 8 is fixedly connected to the second fixed gear 9 and is provided to connect a second intermediate gear 7 with the second fixed gear 9 when it is engaged. In the disengaged state of the second switching element 8, the second fixed gear 9 and the second intermediate gear 7 are rotatable relative to each other.
  • an intermediate shaft 3 is provided, with a third fixed gear 10 is fixedly connected.
  • a third switching element 11 is provided in the form of a multi-plate clutch.
  • the third switching element 11 is fixedly connected to the third fixed gear 10 and is provided to connect a third idler gear 12 to the third fixed gear 10 when it is engaged. In the disengaged state of the third switching element 11, the third fixed gear 10 and the third intermediate gear 12 are rotatable relative to each other.
  • the first fixed gear 4 meshes with the second intermediate 7.
  • the second fixed gear 9 meshes with the third intermediate 12 a.
  • the first fixed wheel 4 also engages with the third fixed wheel 10.
  • the arrangement of the waves in relation to each other is designed so that the above-mentioned interventions can be realized.
  • the diameter of the above-mentioned spur gears and intermediate wheels is designed so that a meshing engagement with the possibility of power transmission can be maintained continuously.
  • the switching elements allow different power flows between the input shaft 1 and the output shaft 2.
  • two switching stages in the forward direction and a switching stage in the reverse direction are possible.
  • the first forward speed is achieved by engaging the first shift element 5 and thus coupling the first fixed wheel 4 to the first idler 6. Upon rotation of the input shaft 1, this is thus on the first Fixed gear 4 and the engaged first switching element 5 transmitted to the first intermediate 6.
  • the first intermediate 6 transmits its rotation to the second fixed gear 9, which emits the rotation to the output shaft 2.
  • the second switching element 8 and the third switching element 11 are disengaged.
  • the power flow in the first switching stage is indicated in Fig. 2a with an arrow.
  • the second switching stage in the forward direction is achieved by the second switching element 8 is engaged and thus the second fixed gear 9 is coupled to the second intermediate gear 7.
  • this is thus transmitted to the second fixed gear 9 via the first fixed gear 4 and the second intermediate gear 7 and the engaged switching element 8.
  • the second fixed wheel 9 is the rotation of the output shaft 2 from.
  • the first switching element 5 and the third switching element 11 are disengaged.
  • the power flow in the second switching stage is indicated in Fig. 2b with an arrow.
  • the ratio between the diameter of the first fixed wheel 4 and the diameter of the second intermediate gear 7 is greater than the ratio between the diameter of the first intermediate gear 6 and the diameter of the second fixed gear 9.
  • the reverse shift stage is achieved by the third switching element 11 is engaged and thus the third fixed gear 10 is coupled to the third intermediate gear 12. Upon rotation of the input shaft 1, this rotation is thus transmitted via the first fixed gear 4 to the third fixed gear 10 and via the engaged third switching element 11 to the third intermediate gear 12. From the third intermediate 12, the rotation is transmitted to the second fixed gear 9 and this practice on the output shaft 2. In this case, the first switching element 5 and the second switching element 8 are disengaged.
  • the power flow in the reverse stage is indicated in Fig. 2c with an arrow. Due to the arrangement of gears in the power flow in the reverse shift stage, the direction of rotation of the output shaft 2 is the same as the direction of rotation of the input shaft. 1 Thus, in the reverse shift stage, a direction of rotation opposite to the forward shift stages can be achieved on the output shaft 2 while the input shaft rotation direction remains the same.
  • the switching operations of the powershift transmission are coordinated in time, so that a torque drop during a switching operation can be reduced.
  • the slip of the switching elements designed as multi-plate clutches is used to reduce shocks during switching operations.
  • the control of the switching elements is performed by a control device of the working machine and an associated hydraulic system.
  • the switching elements are each provided on a shaft to which the associated gear pairs are attached. Due to the paraxial configuration of drive shaft 1, output shaft 2 and intermediate shaft 3, the associated with a small axial space in the transmission housing 14 can be accommodated.
  • the driving force is transmitted via only one pair of gears. Even in the reverse stage, there are only two gear pairs in the load-transmitting engagement. This reduces the need for maintenance and extends the service life.
  • the power shift transmission has been described in the above-described embodiment with a first and second forward stage and a reverse stage. However, with appropriate integration into the work machine architecture, the transmission can also be used with one forward stage and two reverse stages. Reference to drive shaft

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

Abstract

L'invention concerne une boîte de vitesses à commande sous charge comportant un arbre d'entraînement (1) et un arbre de sortie (2). Une rotation de l'arbre d'entraînement (1) est transmise de manière sélective par l'intermédiaire de jeux de roues frontales pour obtenir plusieurs rapports. Des jeux de roues frontales situés dans la boîte de transmission à commande sous charge comprennent les éléments qui suivent : une première roue fixe (4) couplée à l'arbre d'entraînement (1), qui peut être couplée par l'intermédiaire d'un premier élément de commande (5) de manière sélective à une première roue intermédiaire (6) ; une deuxième roue intermédiaire (7) qui vient en prise par engagement avec la première roue fixe (4) et qui peut être couplée par l'intermédiaire d'un deuxième élément de commande (8) de manière sélective à une deuxième roue fixe (9) ; et une troisième roue fixe (10) qui est couplée à un arbre intermédiaire (3) et qui peut être couplée par l'intermédiaire d'un troisième élément de commande (11) de manière sélective à une troisième roue intermédiaire (12) qui vient en prise par engagement avec la deuxième roue fixe (9). Dans la boîte de vitesses à commande sous charge, la force d'entraînement peut être transmise par une unique prise de guidage de charge d'une paire de roues dentées de l'arbre d'entraînement (1) à l'arbre de sortie (2).
PCT/EP2019/053770 2018-03-13 2019-02-15 Boîte de vitesses compacte à commande sous charge WO2019174852A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018203770.1 2018-03-13
DE102018203770.1A DE102018203770B4 (de) 2018-03-13 2018-03-13 Kompaktes Lastschaltgetriebe

Publications (1)

Publication Number Publication Date
WO2019174852A1 true WO2019174852A1 (fr) 2019-09-19

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ID=65520249

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Application Number Title Priority Date Filing Date
PCT/EP2019/053770 WO2019174852A1 (fr) 2018-03-13 2019-02-15 Boîte de vitesses compacte à commande sous charge

Country Status (2)

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DE (1) DE102018203770B4 (fr)
WO (1) WO2019174852A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1232471A (fr) * 1959-04-22 1960-10-10 Perfectionnements aux boîtes de transmission
EP1721520A1 (fr) * 2005-05-11 2006-11-15 Trioliet Mullos B.V. Mélangeur de fourrage
DE102008002069A1 (de) 2008-05-29 2009-12-03 Zf Friedrichshafen Ag Mehrgängiges Lastschaltgetriebe
CN101240832B (zh) * 2008-02-22 2010-06-02 四川成都成工工程机械股份有限公司 适用于工程机械的动力换档变速箱
DE202013004051U1 (de) * 2013-04-29 2014-07-30 Gkn Walterscheid Gmbh Getriebe für Zerkleinerungsmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016203502A1 (de) * 2016-03-03 2017-09-07 Zf Friedrichshafen Ag Lastschaltgetriebe für Arbeitsmaschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1232471A (fr) * 1959-04-22 1960-10-10 Perfectionnements aux boîtes de transmission
EP1721520A1 (fr) * 2005-05-11 2006-11-15 Trioliet Mullos B.V. Mélangeur de fourrage
CN101240832B (zh) * 2008-02-22 2010-06-02 四川成都成工工程机械股份有限公司 适用于工程机械的动力换档变速箱
DE102008002069A1 (de) 2008-05-29 2009-12-03 Zf Friedrichshafen Ag Mehrgängiges Lastschaltgetriebe
DE202013004051U1 (de) * 2013-04-29 2014-07-30 Gkn Walterscheid Gmbh Getriebe für Zerkleinerungsmaschine

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DE102018203770B4 (de) 2020-03-19
DE102018203770A1 (de) 2019-09-19

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