WO2000050291A1 - Systeme de commande pour vehicule a chenilles - Google Patents

Systeme de commande pour vehicule a chenilles Download PDF

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Publication number
WO2000050291A1
WO2000050291A1 PCT/CH2000/000094 CH0000094W WO0050291A1 WO 2000050291 A1 WO2000050291 A1 WO 2000050291A1 CH 0000094 W CH0000094 W CH 0000094W WO 0050291 A1 WO0050291 A1 WO 0050291A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
gear mechanism
steering system
planetary
output shaft
Prior art date
Application number
PCT/CH2000/000094
Other languages
English (en)
Inventor
Jürg FRUTIGER
Urs Frutiger
Morio Nakamura
Hiroo Nakajima
Original Assignee
Frutiger Baumaschinen + Co.
C.C.D. Limited
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 Frutiger Baumaschinen + Co., C.C.D. Limited filed Critical Frutiger Baumaschinen + Co.
Priority to DE10083898T priority Critical patent/DE10083898T1/de
Priority to CH01574/01A priority patent/CH694583A5/de
Priority to AU25313/00A priority patent/AU2531300A/en
Publication of WO2000050291A1 publication Critical patent/WO2000050291A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
    • B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
    • B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source
    • B62D11/10—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears
    • B62D11/14—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source
    • B62D11/18—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears differential power outputs being effected by additional power supply to one side, e.g. power originating from secondary power source the additional power supply being supplied hydraulically

Definitions

  • This invention relates to a steering system for a track-laying ⁇ .
  • vehicle such as a scrape dozer on which an engine for running is mounted sideways to drive the right and left caterpillar bands by mechanical transmission.
  • Track-laying vehicles such as a bulldozer and a scrape dozer which run to work move by transmitting engine power mechanically.
  • a scrape dozer with both functions of a scraper and a bulldozer can be operated forward for excavating, loading, conveying, removing earth, and preparing land and successively driven backward to the excavation position, like a shuttle. This characteristic leads to the use of scrape dozers for constructing roads, developing building lots and the golf links and carrying out agrarian reform.
  • a scrape dozer has a bowl 51 between right and left caterpillar bands 50 for excavating and loading earth and sand, a blade 52 for preparing land on the front thereof and a cab seat 53 on the top of the body.
  • the steering system 4 changes a direction of the vehicle, so that the power transmitted from an output shaft 3a of the transmission through a shaft coupling 8 is transmitted to right and left pinions 10a and 10b via clutches 7a and 7b.
  • Some types of bulldozer have a steering system with a differential mechanism combining bevel gears, so that the speed is kept when a vehicle turns.
  • This steering system is like one shown in Fig. 5.
  • An output shaft of transmission 3 is provided with a bevel gear 61 which is connected to an input shaft 62 of a working gear 60.
  • Output shafts 63 and 64 on the right and left sides of the working gear are connected to right and left driving wheels which are not shown in the figure.
  • the output shafts 63 and 64 are provided with brakes 66a and 66b respectively.
  • Numeral 65 indicates a clutch for difflock.
  • the output shaft may be provided with a type of hydraulic pump motor which is changeable in capacity (for example, unexamined Japanese Patent Publication No.6- 183366).
  • An engine of a bulldozer is placed lengthwise (the output shaft is placed in the moving direction ).
  • the output shaft of a transmission is provided almost at the center and right-angled between right and left driving wheels. Therefore, the length of a steering system can be extended to a maximum space between caterpillar bands.
  • An object of the present invention is to provide a compact steering system having differential mechanism suitable for track-laying vehicles on which an engine is mounted sideways.
  • a steering system comprises an input shaft connected to an output shaft of a transmission, output shafts for transmitting power respectively to driving wheels of right and left caterpillar bands.
  • the input shaft is inserted through a hollow shaft on which each sun gear of first, second and third planetary gear mechanisms is fixedly installed.
  • the end of the input shaft is connected to a planetary carrier of the first planetary gear mechanism.
  • a ring gear of the second planetary gear mechanism is connected to the hydraulic motor.
  • a planetary carrier of the second planetary gear mechanism is connected to a ring gear of the first planetary gear mechanism and one output shaft.
  • a ring gear of the third planetary gear mechanism is fixed on a case.
  • a planetary carrier of the third planetary gear mechanism is connected to the other output shaft.
  • the steering system according to the present invention is applied to track-laying vehicles wherein engine power is transmitted via a transmission mechanically to the driving wheels of caterpillar bands such as bulldozers, scrape dozers, combines and the like, but not intended for track-laying vehicles which move by using a hydraulic pump and a hydraulic motor such as mobile cranes and pile drivers.
  • the steering system according to the present invention works well especially for track-laying vehicles wherein an engine is mounted sideways. Even if an engine is mounted lengthwise, however, when the engine cannot be mounted at the center of the body, the steering system can be applied.
  • both output shafts actuating pinions are outwardly engaged with a hollow shaft between second planetary gear mechanism and third planetary gear mechanism.
  • the third planetary gear mechanism may be arranged on the side to be limited in order to set the steering system in a manner that the center between the both pinions is the center position of the body.
  • an engine is mounted sideways with the transmission and the steering system placed between the caterpillar bands on the right and left sides, such as a scrape dozer (Refer to Claim 3).
  • Fig. 1 is a diagrammatic view showing the composition of the steering system of track-laying vehicle as one embodiment of the present invention.
  • Fig. 2 is a partial sectional view of the steering system of track-laying vehicle as one embodiment of the present invention.
  • Fig. 3 is an explanatory view showing the power system of a conventional scrape dozer.
  • Fig. 4 is a side view of a scrape dozer.
  • Fig. 5 is an explanatory view of a conventional steering system.
  • Fig. 6 is a perspective view of the steering system shown in Fig. 2.
  • an input shaft 11 is provided via the output shaft 3a of the transmission 3 and the shaft coupling 8 and inserted through a hollow shaft 25 on which a first sun gear 13, a second sun gear 18 and a third sun gear 26 are fixedly installed.
  • the end of the input shaft 11 is connected with a first planetary carrier 12.
  • the hollow shaft 25 is the common shaft of three planetary gear mechanisms 37, 38 and 39.
  • the first planetary carrier 12 is provided with a planetary gear
  • the second planetary gear mechanism 38 is comprised of the second sun gear 18 fixedly installed on the hollow shaft 25, a second planetary gear 17 which is provided with a second planetary carrier 16a connected with the first ring gear 15, and a second ring gear 19 which is connected with a gear 22 engaged with a gear 21 connected with an output shaft of a hydraulic motor 40.
  • the second planetary gear 14 is connected with a right output shaft 20b by a second planetary carrier 16b.
  • the circuit of the hydraulic motor 40 is constituted so that the hydraulic motor 40 can rotate normally and inversely and revolution numbers can be changed.
  • the third planetary gear mechanism 39 is comprised of the third sun gear 26 fixedly installed on the hollow shaft 25, a third planetary gear 27 and a third ring gear 30 fixedly installed on a case 35.
  • a third planetary carrier 28 is connected with a left output shaft 20a.
  • the numbers of teeth on corresponding gears are same between the second planetary gear mechanism 38 and the third planetary gear mechanism 39. Therefore, the numbers of teeth are same between the second sun gear 18 and the third sun gear 26, the second planetary gear 17 and the third planetary gear 27, the second ring gear 19 and the third ring gear 30.
  • the left output shaft 20a and the right output shaft 20b are provided, facing each other, between the second planetary gear mechanism 38 and the third planetary gear mechanism 39.
  • the pinion 10a and the pinion 10b are installed adjacently and fixedly to the output shafts 20a, 20b.
  • Numerals 33 and 34 show brake mechanisms fixedly installed within the case 35.
  • the brake mechanism 33 is engaged with the first ring gear 15 and the brake mechanism 34 is engaged with the third planetary carrier 28.
  • the operation of the steering system is now explained. [0019]
  • the hydraulic motor 40 In straight-ahead motion, the hydraulic motor 40 is in the stopped state.
  • the power of an engine 1 is transmitted, via the shaft coupling 8 connected with the output shaft 3a of the transmission 3, to the input shaft 11 and rotates the first planetary carrier 12 of the first planetary gear mechanism 37.
  • This turns the first ring gear 15 and the first sun gear 13.
  • the second ring gear 19 is in the fixed state and the rotation of the first ring gear 15 rotates the second planetary carrier 16a and then the right output shaft 20b via the second planetary carrier 16b.
  • a direction for turning depends on the turning direction of the hydraulic motor 40.
  • a radius for turning depends on the revolution numbers of the hydraulic motor 40.
  • the rotation of the hydraulic motor 40 turns the gear 22 via the gear 21. This rotates the second ring gear 19 and changes the revolution numbers of the right output shaft 20b. If the right output shaft 20b is increased more than is in straight-ahead motion, the rotation of the second sun gear 18 is decreased more than is in straight-ahead motion. [0022]
  • the left output shaft 20a is decreased as the right output shaft 20b is increased.
  • the right output shaft 20b is decreased (the hydraulic motor 40 is reversed )
  • the right output shaft 20b is decreased and the rotation of the second sun gear 18 is increased more than is in straight-ahead motion. Therefore, the left output shaft 20a is increased as the right output shaft 20b is decreased.
  • the turning is performed by increasing and decreasing the revolution numbers of the right output shaft 20a by the hydraulic motor 40. The speed in turning motion is same as the speed in straight-ahead motion, however.
  • the brake mechanisms 33, 34 are not related to the planetary gear mechanism.
  • the brake mechanisms 33, 34 are simultaneously operated, and decrease speed of the vehicle, and work to stop and park the vehicle.
  • the present invention realizes smooth turning of the vehicle without decreasing the speed thereof, since the input shaft is inserted through the hollow shaft on which each sun gear of the first, second and third planetary gear mechanisms is fixedly installed, and the end of the input shaft is connected to the planetary carrier of the first planetary gear mechanism, and the ring gear of the second planetary gear mechanism is connected to the hydraulic motor and one output shaft. Furthermore, since the engine can be placed sideways so that the transmission and the steering system can be arranged between the caterpillars bands, the present invention can be effectively applied to not only track-laying vehicles which an engine cannot be placed lengthwise but also vehicles which an engine cannot be arranged at the center of the body.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)

Abstract

L'invention concerne un système de commande compact doté d'un mécanisme différentiel approprié pour un véhicule à chenilles à moteur latéral, présentant un arbre d'entrée (11) connecté à un arbre de sortie (3a) d'une transmission et des arbres de sortie (20a, 20b) pour la transmission de puissance, respectivement aux roues motrices (6a, 6b) des bandes de chenilles droite et gauche, afin d'assurer la rotation du véhicule par changement de vitesse de l'un des arbres de sortie (20a, 20b) par un moteur hydraulique (40), caractérisé en ce que l'arbre d'entrée (11) est inséré dans un arbre creux (25) sur lequel chaque roue solaire (13, 18, 26) du premier, deuxième et troisième mécanismes à trains planétaires (37, 38, 39) est montée fixe, une extrémité de l'arbre d'entrée (11) est connectée à un support planétaire (12) du premier mécanisme à trains planétaires (37), une couronne (19) du deuxième mécanisme à trains planétaires (38) est connectée au moteur hydraulique (40), un support planétaire (16a) du deuxième mécanisme (38) est connecté à une couronne (15) du premier mécanisme (37) et d'un arbre de sortie (20b), une couronne (30) du troisième mécanisme (39) est fixée sur un boîtier (35), et un support planétaire (28) du troisième mécanisme (39) est connecté à l'autre arbre de sortie (20a).
PCT/CH2000/000094 1999-02-24 2000-02-22 Systeme de commande pour vehicule a chenilles WO2000050291A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE10083898T DE10083898T1 (de) 1999-02-24 2000-02-22 Steueranlage für Gleiskettenfahrzeuge
CH01574/01A CH694583A5 (de) 1999-02-24 2000-02-22 Steueranlage für ein Gleiskettenfahrzeug.
AU25313/00A AU2531300A (en) 1999-02-24 2000-02-22 Steering system for a truck-laying vehicle

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP04651499A JP4132356B2 (ja) 1999-02-24 1999-02-24 装軌車両の操向装置
JP11/46514 1999-02-24

Publications (1)

Publication Number Publication Date
WO2000050291A1 true WO2000050291A1 (fr) 2000-08-31

Family

ID=12749388

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CH2000/000094 WO2000050291A1 (fr) 1999-02-24 2000-02-22 Systeme de commande pour vehicule a chenilles

Country Status (5)

Country Link
JP (1) JP4132356B2 (fr)
AU (1) AU2531300A (fr)
CH (1) CH694583A5 (fr)
DE (1) DE10083898T1 (fr)
WO (1) WO2000050291A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107839751A (zh) * 2017-12-01 2018-03-27 北京履坦科技有限公司 一种履带车辆双功率流动力差速转向机构
CN108340776A (zh) * 2018-03-02 2018-07-31 第拖拉机股份有限公司 一种用于水田型履带拖拉机的传动系后箱

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7041089B2 (ja) 2019-03-19 2022-03-23 山▲さき▼建設株式会社 削土運搬用装軌車両

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982000867A1 (fr) * 1980-09-02 1982-03-18 Riediger C Differentiel de direction planetaire

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982000867A1 (fr) * 1980-09-02 1982-03-18 Riediger C Differentiel de direction planetaire

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107839751A (zh) * 2017-12-01 2018-03-27 北京履坦科技有限公司 一种履带车辆双功率流动力差速转向机构
CN107839751B (zh) * 2017-12-01 2023-12-08 北京履坦科技有限公司 一种履带车辆双功率流动力差速转向机构
CN108340776A (zh) * 2018-03-02 2018-07-31 第拖拉机股份有限公司 一种用于水田型履带拖拉机的传动系后箱
CN108340776B (zh) * 2018-03-02 2023-09-19 第一拖拉机股份有限公司 一种用于水田型履带拖拉机的传动系后箱

Also Published As

Publication number Publication date
DE10083898T1 (de) 2002-05-02
JP4132356B2 (ja) 2008-08-13
AU2531300A (en) 2000-09-14
JP2000247254A (ja) 2000-09-12
CH694583A5 (de) 2005-04-15

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