EP1266150A1 - Mecanisme de renversement a plusieurs rapports, commutable sous charge - Google Patents

Mecanisme de renversement a plusieurs rapports, commutable sous charge

Info

Publication number
EP1266150A1
EP1266150A1 EP01915370A EP01915370A EP1266150A1 EP 1266150 A1 EP1266150 A1 EP 1266150A1 EP 01915370 A EP01915370 A EP 01915370A EP 01915370 A EP01915370 A EP 01915370A EP 1266150 A1 EP1266150 A1 EP 1266150A1
Authority
EP
European Patent Office
Prior art keywords
gear
fixed
gears
input shaft
countershafts
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Withdrawn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
EP01915370A
Other languages
German (de)
English (en)
Inventor
Fritz Leber
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.)
ZF Friedrichshafen AG
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 EP1266150A1 publication Critical patent/EP1266150A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H3/097—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 the input and output shafts being aligned on the same axis
    • 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
    • B60K17/28—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of power take-off
    • 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

Definitions

  • the invention relates to a switchable under load, multi-speed reversing gear according to the kind defined in the preamble of claim 1.
  • Reversible gearboxes that can be switched under load are preferably used in construction machines in which a drive motor preferably uses a hydrodynamic converter
  • Reverse gear drives and the output shaft of the reverse gear is connected to the wheels or caterpillars of the construction machine.
  • Reversible gearboxes that can be shifted under load often require a power take-off, which is dependent on the drive speed of the reversing gearbox.
  • the reversing gear For the use of the reversing gear as a crawler gear for driving a crawler vehicle, for. B. a bulldozer, the reversing gear is compact due to the small space.
  • a particular advantage with regard to the installation space is if the output of the reversing gear is arranged coaxially with the drive of the reversing gear.
  • the power take-off of the reversing gear which is to be carried out depending on the drive speed of the reversing gear and in the construction machine e.g. B. drives a winch, is to be arranged at a defined distance from the output of the reversing gear.
  • EP 0 759 129 B1 discloses a multi-speed reversing gear which can be shifted under load, in which the output of the reversing gear is arranged axially offset from the drive and the power take-off is arranged coaxially to the drive. Due to the coaxial arrangement of the power take-off and the axially offset Downforce this reversing gearbox requires too much installation space for use in a caterpillar vehicle.
  • the present invention has for its object to provide a switchable under load, multi-speed reversing gear, in which the output is arranged coaxially to the drive and the reversing gear is compact in the axial and radial directions and the power take-off is arranged at a defined distance from the drive shaft.
  • two fixed gears are arranged on a countershaft in the output gear set, of which one fixed gear with two idler gears and one fixed gear with a further fixed gear, which is arranged in a rotationally fixed manner on the output shaft, are in constant engagement.
  • the drive wheel set consists of an input shaft on which a
  • Fixed gear is arranged, which is in constant engagement with two idler gears.
  • a further fixed gear is arranged on the input shaft, which is in constant engagement with a fixed gear which is non-rotatably connected to the power take-off shaft.
  • the power take-off shaft is also a countershaft on which an idler gear is arranged, which is in constant mesh with fixed gears in the distributor gear set.
  • the distributor wheel set consists of two idler gears, which are arranged on countershafts and are in constant mesh with fixed gears. All countershafts are arranged in a circle around the drive shaft, which means that the radial extension of the gear unit can be made even and compact.
  • the output shaft coaxially to the input shaft and the power take-off shaft at a defined distance from the input shaft. Only if a countershaft of the distributor wheel set forms a power take-off shaft on the one hand and carries an idler gear of the distribution wheel set on the other hand, is it possible to arrange the power take-off at a defined distance from the drive shaft and to make the transmission radially compact, since all countershafts are arranged in a circle around the drive shaft.
  • the input shaft can be non-rotatably connected to both fixed gears, so that both the drive gear set and the fixed gear, which is in constant engagement with the fixed gear of the power take-off shaft, have the speed of the input shaft.
  • the fixed gear which is in constant engagement with the idler gears of the drive gear set, can be connected in a rotationally fixed manner to the input shaft
  • the fixed gear which is in constant engagement with the fixed gear of the power take-off shaft
  • the input shaft can thus be driven by the turbine wheel of a hydrodynamic converter and the power take-off can be carried out as a function of the pump speed of the hydrodynamic converter.
  • the idler wheels of the drive wheel set can be alternately connected to the fixed wheels of the distributor wheel set via couplings, whereby the direction of travel of the vehicle can be changed.
  • the wheels of the driven gear set can be connected to the wheels of the distributor gear set via couplings, as a result of which different gears of the reversing gear can be shifted.
  • Fig. 1 is a transmission diagram of a reverse gear with three forward and three reverse gears and
  • Fig. 2 is a schematic front view of the reversing gear according to Fig. 1 to illustrate the spatial position of the countershaft and the fixed and idler gears.
  • the drive gear set 1 consists of a first gear 2, which is connected in a rotationally fixed manner to the input shaft 3, and with an idler gear 4, which is arranged on a countershaft 5, and with an idler gear 6, which is arranged on the countershaft 7, in constant intervention.
  • a gear 8 is in constant engagement with a fixed gear 9, which is arranged on a power take-off shaft 10.
  • the power take-off shaft 10 simultaneously fulfills the function of a countershaft.
  • the gear wheel 8 can be connected in a rotationally fixed manner to the input shaft 3, as a result of which the power take-off shaft 10 is dependent on the rotational speed of the input shaft 3, or can be connected to a shaft (not shown) which is arranged within the input shaft 3, this shaft being connected to a Not shown pump wheel of a hydrodynamic converter and the input shaft 3 is rotatably connected to a turbine wheel of a hydrodynamic converter, not shown.
  • the idler gear 4 can be connected for forward travel via a clutch 11 to a fixed gear 12 which is non-rotatably connected to the countershaft 5.
  • the idler gear 6 is connected via a clutch 13 with a fixed gear 14, which is arranged on the countershaft 7 in a rotationally fixed manner. connectable upward.
  • the fixed gear 14 is in constant engagement with the fixed gear 12 and an idler gear 15 which is arranged on the power take-off shaft 10.
  • the idler gear 15 is in constant engagement with a fixed gear 16.
  • the fixed gear 12 is in constant engagement with a fixed gear 17.
  • the fixed gear 17 is in constant engagement with an idler gear 18.
  • the fixed gears 12, 14, 16 and 17 and the idler gears 15 and 18 form a distributor wheel set 19, which establishes the connection between the drive wheel set 1 and an output gear set 20.
  • the driven gear set consists of the fixed gears 21, 22 and 23 and two idler gears 24 and 25.
  • the fixed gears 21 and 22 are non-rotatably connected to the countershaft 26 on which the idler gear 18 is arranged.
  • the idler gear 24 is arranged on the countershaft 27, which is rotatably connected to the fixed gear 17.
  • the output shaft 28 is rotatably connected to the fixed gear 23 and is arranged coaxially with the input shaft 3.
  • the idler gear 25 is arranged on the countershaft 29, which is rotatably connected to the fixed gear 16.
  • the secondary output shaft 10 is arranged at a distance from the input shaft 3 and output shaft 28. If the first gear is to be shifted in the forward driving direction, the clutch 11 is closed, whereby the idler gear 4 of the drive gear set is non-rotatably connected to the fixed gear 12 of the distributor gear set. The remaining clutches remain open.
  • the clutch 30 is closed, whereby the idler gear 25 of the driven gear set is rotatably connected to the fixed gear 16 of the transfer gear set. If the second gear is to be shifted in the forward driving direction, the clutch 11 remains closed and the clutch 31 is also closed and connects the idler gear 24 of the driven gear set to the fixed gear 17 of the distributor gear set. The clutch 30, the clutches 32 and 13 are open. If the third gear is to be shifted in the forward direction of travel, the clutch 11 remains closed and the clutch 32 is closed and connects the idler gear 18 of the distributor gear set to the fixed gear 22 of the driven gear set. The clutches 30, 31 and 13 are open.
  • the clutch 13 is closed, whereby the idler gear 6 of the drive gear set is rotatably connected to the fixed gear 14 of the distributor gear set.
  • the clutch 30 is closed and the clutches 31, 32 and 11 opened. If the second gear is to be shifted in the reverse direction, the clutches 13 and 31 are closed and the clutches 11, 30 and 32 are open. If the third gear is to be shifted in the reverse direction, the clutches 13 and 32 are closed and the clutches 11, 31 and 30 are open.
  • the driven gear set 20 from a fixed gear 23, which is arranged coaxially to the input shaft 3 and forms the output, and two fixed gears 22 and 21, which are arranged on a countershaft 26, and two idler gears 24 and 25, which are arranged on countershafts 27 and 29, and the distributor wheel set 19 comprising two idler wheels 15 and 18, which are arranged on countershafts 10 and 26, and four fixed gears 12 , 17, 14 and 16,
  • the output can be arranged coaxially to the input shaft 3 and the countershafts 5, 7, 10, 26, 27 and 29 in a circle around the input shaft 3 or output shaft 28.
  • a fixed gear 8 is rotatably connected to the input shaft 3, which is in constant engagement with a fixed gear 9 of the power take-off shaft 10, the power take-off can be arranged at a distance from the input shaft 3 and output shaft 28.
  • the countershafts 5, 27, 26, 29, 10 and 7 are arranged in a circle around the input shaft 3 and the output shaft 28. This creates a very compact gearbox which has a uniform extension in the radial direction.
  • the output shaft 28 is arranged coaxially with the input shaft 3.
  • the secondary output shaft 10 is arranged at a distance from the output shaft 28 and input shaft 3.
  • a spaced-apart power take-off shaft 10 is only possible in that an intermediate shaft of the powershift transmission serves on the one hand as a power take-off shaft 10 and on the other hand as a countershaft for the idler gear 15.
  • the power take-off shaft 10 is thus directly connected to the input shaft 3 and at the same time carries the idler gear 15 of the distributor wheel set 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

La présente invention concerne un mécanisme de renversement à plusieurs rapports, commutable sous charge, entraîné par l'intermédiaire d'un arbre d'entrée (3), et entraînant un arbre de sortie (28) disposé de façon coaxiale par rapport à l'arbre d'entrée (3). Le mécanisme de renversement à plusieurs rapports, commutable sous charge présente une prise de force (10) qui se trouve à distance de l'arbre d'entrée (3). L'arbre (10) de la prise de force est relié d'un côté à l'arbre d'entrée par l'intermédiaire de roues fixes (9, 8) et porte d'un autre côté une roue folle (15) faisant partie d'un engrenage de répartition (19). Les arbres de transmission (5, 7, 10, 26, 27, 29) encerclent l'arbre d'entrée (3). Cela permet de former un mécanisme de renversement à plusieurs rapports, commutable sous charge qui est très compact, présente une extension radiale uniforme, et possède un entraînement d'entrée et sortie (3, 28) coaxial ainsi qu'une prise de force (10) située à distance de celui-ci.
EP01915370A 2000-03-22 2001-03-17 Mecanisme de renversement a plusieurs rapports, commutable sous charge Withdrawn EP1266150A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE2000114132 DE10014132A1 (de) 2000-03-22 2000-03-22 Unter Last schaltbares, mehrgängiges Wendegetriebe
DE10014132 2000-03-22
PCT/EP2001/003078 WO2001071214A1 (fr) 2000-03-22 2001-03-17 Mecanisme de renversement a plusieurs rapports, commutable sous charge

Publications (1)

Publication Number Publication Date
EP1266150A1 true EP1266150A1 (fr) 2002-12-18

Family

ID=7635851

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01915370A Withdrawn EP1266150A1 (fr) 2000-03-22 2001-03-17 Mecanisme de renversement a plusieurs rapports, commutable sous charge

Country Status (3)

Country Link
EP (1) EP1266150A1 (fr)
DE (1) DE10014132A1 (fr)
WO (1) WO2001071214A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10232835B4 (de) * 2002-07-19 2010-02-11 Zf Friedrichshafen Ag Doppelkupplungsgetriebe
DE10248826A1 (de) * 2002-10-19 2004-04-29 Zf Friedrichshafen Ag Unter Last schaltbares mehrgängiges Wendegetriebe
DE10259424A1 (de) * 2002-12-19 2004-07-01 Zf Friedrichshafen Ag Lastschaltbares mehrgängiges Wendegetriebe
DE10320777A1 (de) * 2003-05-09 2004-11-18 Zf Friedrichshafen Ag Unter Last schaltbares mehrgängiges Wendegetriebe
DE102009021141A1 (de) * 2009-05-13 2010-11-18 Voith Patent Gmbh Antriebsstrang für ein Fahrzeug mit zwei gleichwertigen Fahrtrichtungen
EP3998143B1 (fr) 2016-07-28 2024-04-17 BIC Violex Single Member S.A. Tête de rasoir comprenant un film de protection

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR747170A (fr) * 1932-11-30 1933-06-12 Mécanisme de changement de vitesse notamment pour véhicules automobiles
GB1426718A (en) * 1972-03-17 1976-03-03 Turner Mfg C Oltd Gear boxes
AT327015B (de) * 1972-10-30 1976-01-12 Kloeckner Humboldt Deutz Ag Zahnraderwechselgetriebe in gruppenbauweise, insbesondere fur land- und/oder bauwirtschaftlich nutzbare motorfahrzeuge
CA1033969A (fr) * 1975-06-30 1978-07-04 Edward J. Ziegler Boite de vitesses multiplages a passage direct
US4549443A (en) * 1983-12-07 1985-10-29 Twin Disc, Incorporated Multi-speed reversible transmission of countershaft construction
DE3715880A1 (de) * 1987-05-13 1988-05-19 Bayerische Motoren Werke Ag Stirnraederwechselgetriebe fuer kraftfahrzeuge, insbesondere personenkraftwagen
US4785682A (en) * 1987-05-20 1988-11-22 Honda Giken Kogyo Kabushiki Kaisha Power transmission device
JPH0251642A (ja) * 1988-08-11 1990-02-21 Fuji Heavy Ind Ltd 自動変速装置
US5249475A (en) * 1992-08-31 1993-10-05 Deere & Company Eight- to sixteen-speed powershift transmission
DE4416930A1 (de) * 1994-05-13 1995-11-16 Zahnradfabrik Friedrichshafen Unter Last schaltbares, mehrgängiges Wendegetriebe
DE4444843A1 (de) * 1994-12-16 1996-06-20 Zahnradfabrik Friedrichshafen Unter Last schaltbares, mehrgängiges Wendegetriebe
IT1287635B1 (it) * 1996-03-21 1998-08-06 Landini Spa Cambio di velocita' sotto carico a doppia frizione per trattori agricoli con o senza frizione motore

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0171214A1 *

Also Published As

Publication number Publication date
DE10014132A1 (de) 2001-09-27
WO2001071214A1 (fr) 2001-09-27

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