EP0379527A1 - Boite de vitesses commutable avec marche avant et marche arriere pour vehicules motorises ou similaire - Google Patents

Boite de vitesses commutable avec marche avant et marche arriere pour vehicules motorises ou similaire

Info

Publication number
EP0379527A1
EP0379527A1 EP19890902039 EP89902039A EP0379527A1 EP 0379527 A1 EP0379527 A1 EP 0379527A1 EP 19890902039 EP19890902039 EP 19890902039 EP 89902039 A EP89902039 A EP 89902039A EP 0379527 A1 EP0379527 A1 EP 0379527A1
Authority
EP
European Patent Office
Prior art keywords
shaft
drive
gear
output shaft
driven
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Withdrawn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
EP19890902039
Other languages
German (de)
English (en)
Inventor
Josef Pelzer
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
Application filed by Individual filed Critical Individual
Publication of EP0379527A1 publication Critical patent/EP0379527A1/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Withdrawn legal-status Critical Current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
    • F16H3/14—Gearings for reversal only
    • F16H3/145—Gearings for reversal only with a pair of coaxial bevel gears, rotatable in opposite directions
    • 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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/60—Gearings for reversal only

Definitions

  • the invention relates to a switchable transmission according to the preamble of claim 1, which is particularly suitable for motor-driven vehicle models, such as RC cars, car and truck models, functional models, ship models or the like.
  • Such a known switchable transmission (DE-OS 36 03 676), which is intended for the above-mentioned purposes, is designed as a spherical disk transmission for forward and reverse gear and has a disk-shaped ball cage for the transmission of the drive from a disk-shaped drive member to a disk-shaped output member on, which is freely rotatable and axially displaceable between a drive pressure plate fixed on the drive shaft and an output pressure plate fixed on the output shaft in such a way that it is under the pressure of a helical spring with driver pins arranged on its opposite flat side in a direct manner positive engagement with corresponding coupling bores on the output pressure plate can occur; also one is via a hand lever Actuatable braking device is provided, which engages the ball cage and axially displaces it against the force of the compression spring mentioned in the direction of the drive pressure plate.
  • the drive pins of the ball cage come out of engagement with the coupling bores on the output pressure plate, and in the case of a further axial displacement counter to the pressure of the helical spring in the direction of the drive pressure plate, drive pins reach the opposite flat or end face of the ball cage in contact with a stop on the base plate of the transmission, so that the ball cage is stopped and the drive transmission from the drive disk via the balls to the driven disk now takes place by frictional contact.
  • the well-known spherical disc transmission also has a compact design thanks to the design with the ball cage Construction still requires a relatively large amount of space, but is often not available in the vehicle models for which it is intended.
  • the invention has for its object to provide a particularly compact switchable transmission according to the preamble of claim 1 with dimensions so small that it fits practically in all model vehicles on the market with internal combustion engines, and which is also designed so that it enables a loss-free positive drive transmission even in reverse gear.
  • the bevel gear transmission according to the invention has the advantage of high power transmission with a very compact design. In the forward gear position, practically lossless power transmission is ensured, and even in the reverse gear position there are only such small losses due to the positive drive transmission that they are practically irrelevant. It is also of particular advantage that the idle position can be achieved practically without any additional design effort and thus enables the internal combustion engine, for example of RC cars, to be revved up in a simple manner before the start.
  • the invention therefore also enables a completely new starting line-up and a new starting process for races with RC cars. All three gearshift positions can be effected by using an electronic pulse circuit when using electromechanical control devices that are common in model making, the pulse taking place via the second channel that is already present in the customary 2-channel radio remote control systems.
  • the transmission according to the invention enables a completely encapsulated construction and is therefore extremely robust and requires little maintenance.
  • FIG. 1 shows a longitudinal section through a first embodiment of a switchable transmission in a clutch position, in which the output or output shaft of the transmission is directly coupled to its drive or input shaft and thus rotates in the same direction,
  • Fig. 4 is a side view of the transmission 'with a
  • Shift paddle for switching from forward gear to neutral gear in reverse gear 5 is a plan view of the transmission with rocker switch in the direction of the 'arrow V of Fig. 4,
  • FIG. 10 shows yet another modified embodiment of a transmission with a rotatably mounted transmission housing and braking device in the direct drive position for forward gear
  • Fig. 13 is an associated braking device in the release or release position
  • Fig. 14 the braking device in the braking position.
  • the switchable transmission 1 for forward and reverse gear is provided with a drive member 2 and an output member 3 between a drive shaft 4 and a coaxial orderly output shaft 5, wherein means 6 for transmitting torques are arranged between the drive member 2 and the output member 3.
  • the Ab ⁇ drive member 3 is also selectively engaged by an axially displaceable coupling member 7 or movable with the opposite direction of rotation.
  • the switchable transmission 1 is a bevel gear transmission with a drive wheel 2a, with two intermediate gears 6a, 6b opposite each other in mirror image and with an output gear 3a in a closed transmission housing or cage 8 trained.
  • the gear housing or the cage 8 is fixedly mounted on a carrier 9, and the drive wheel 2a and the driven gear 3a are mounted on the gear housing or cage 8 in roller bearings 10.
  • a third roller bearing 10a coaxial therewith is provided on the gear housing or cage 8.
  • the driven gear 3a is rotatably arranged on the driven shaft 5 and can be coupled to this shaft as required.
  • a coupling pin 11 is provided as a coupling member 7 between the driven gear 3a, which is rotatably arranged on the output shaft 5 and can be coupled as required, and the drive gear 2a which is coaxially arranged on the drive shaft 4 and which is longitudinally displaceable relative to the two shafts 4, 5
  • the drive wheel 2a fixed on the drive shaft 4 couples directly to the output shaft 4 in a form-fitting manner
  • the output gear 3a rotatable on the output shaft 5 with the output shaft 5 connects conclusively, wherein in the case of kinematic reversal of the transmission input and the transmission output instead of the driven gear 3a, the drive gear 2a and instead of the drive gear 2a, the driven gear 3a is designed or arranged accordingly.
  • the coupling pin 11 is longitudinally displaceable with a cylindrical shaft end 12a in a cylindrical bore 4a on the drive shaft 4 and with a profiled driver shaft end 12b in a profiled coaxial driver recess 5a on the output shaft 5 guided.
  • the coupling pin 11 has between the two shaft ends 12a, 12b a profiled central section 13 of larger cross section, with which it can be coupled with the drive wheel 2a fixed on the drive shaft 4 or with the driven wheel 3a rotatable on the output shaft 5 such that it in a first coupling position (FIG. 1) a direct positive connection between the drive shaft 4 and the output shaft 5 and in a second coupling position (FIG. 2) a positive connection between the output gear 3a and the output shaft 5 while he in an intermediate position (FIG. 3) is disengaged both from the drive wheel 2a and from the driven wheel 3a.
  • a first coupling position FIG. 1
  • a direct positive connection between the drive shaft 4 and the output shaft 5 and in a second coupling position
  • FIG. 2 a positive connection between the output gear 3a and the output shaft 5 while he in an intermediate position (FIG. 3) is disengaged both from the drive wheel 2a and from the driven wheel 3a.
  • the coupling pin 11 advantageously has a hexagonal profile both on its profiled driver shaft end 12b and on its profiled middle section 13 for engagement in correspondingly profiled driver recesses 5a, 14, 15 on the output shaft 5 as well as on the drive and output bevel gear 2a, 3a.
  • the gear housing or the cage 8 is fixedly mounted on the carrier 9, and a clutch fork 16 (FIGS. 4 to 6) is used to actuate the coupling pin 11.
  • the clutch fork 16 can in turn be actuated by means of a bow-shaped switching rocker 19 pivotally mounted on the gearbox housing or cage 8, which can be pivoted by an electromagnetic, pneumatic or similar drive.
  • the gear housing or the cage 8 is mounted rotatably about the longitudinal axis of the gear in two roller bearings 20 relative to the fixed support 9, and one against the Gearbox housing or the cage 8 in the braking position movable brake member 21 is arranged.
  • the brake member 21 can be a brake bolt which can be displaced against the transmission housing 8 and which can be actuated via a Bowden cable or a linkage 22 and an adjusting lever 23 which in turn is connected to the clutch bolt 11 and counteracted by means of a double thrust bearing 24 shown enlarged in FIG.
  • the effect of a pressure spring 25 acting on the other end of the coupling bolt 11 is adjustable such that the brake bolt or the brake member 21 in a first coupling position of FIG. 1, in which the coupling bolt 11 drives the drive wheel 2a as in FIG the output shaft 5 connects directly, releases the gear housing or the cage 8, and in a second coupling position from FIG. 8, in which the coupling pin 11, as in FIG. 2, the output gear 3a with the output shaft 5 in a form-fitting manner connects, the transmission housing 8 defines, so that the output shaft 5 rotates in the opposite direction to the drive shaft 4, while the brake bolt, as in Fig. 9 geze Is in an idle position of the transmission 1 in a position only slightly released from the transmission housing or cage 8 with unchanged clutch engagement.
  • the gear housing or the cage 8 in the forward gear position of FIG. 7 can rotate in the same direction with the input and output shafts 4, 5 so that the intermediate gears 6a , 6b there is no or only a very small flow of force to the freely rotatable driven bevel gear 3a.
  • the intermediate gears 6a, 6b are therefore protected in the mainly used forward gear position and can be of simpler design than would be necessary for a constant flow of force. Only in the much rarer reverse gear position of FIG.
  • the driven bevel gear 3a can be coupled to the driven shaft 5 without a power flow from the drive shaft 4 to the driven shaft 5, since the gear housing or the cage 8 rotates freely with the drive shaft 4 and thus through the idle gears 6a, 6b no drive torque is transmitted to the driven bevel gear 3a.
  • the coupling bolt 11 also has a profiled central section 13 of larger cross section, which is, however, continuously smooth and none Incision.
  • the coupling pin 11 is provided with coaxial cylindrical bearings at both ends. journals 12a, 12c in cylindrical bores 4a, 5c on the drive shaft 4 and on the output shaft 5 so as to be longitudinally displaceable, specifically against the pressure of a helical compression spring 25 which is in the bore 4a on the drive shaft 4 on an adjusting screw 26 rests for adjusting the spring pressure.
  • An actuating pin 27 engages on the other journal 12c of the coupling pin 11, which can be displaced in the longitudinal bore 5c on the output shaft 5 by means of a conventional adjusting device against the compression spring 25 in such a way that the coupling pin 11 in a first position from FIG its profiled central section 13 with the two profiled driver recesses 14, 15 is in positive engagement both on the drive shaft 4 and on the driven shaft 5, while in its other position from FIG. 11 it disengages from the profiled driver recess 15 on the output drive ⁇ shaft 5 and thus releases the drive transmission from the drive shaft 4 via the bevel gear to the output shaft 5 in the opposite direction.
  • both the drive wheel 2a and the driven wheel 3a are integral with the drive shaft 4 and with the driven shaft 5 in one piece, and the gear housing or the cage 8 is directly next to the Drive wheel 2a and next to the driven wheel 3a are rotatably supported by means of ball bearings 10, and for the drive shaft 4 and the driven shaft 5 there are ball bearings on the two bearing blocks 9a which protrude from the carrier 9, as in the exemplary embodiment of FIGS. 7 to 9 20 provided.
  • the brake member 21 is a brake shoe 21a which engages the outer circumference of the transmission housing and is part of a brake lever 21b which, as shown in FIGS. 13 and 14, is attached to one of the bearing blocks 9a for the transmission housing or the cage 8 is pivotally mounted and, in addition to the brake shoe 21a, has a hook-shaped latching projection 21c, which in the braking position of FIG.
  • the brake lever 21b In the shift position of FIG. 10 of the transmission, the brake lever 21b is in the release or release position of FIG. 13, so that the transmission housing or the cage 8 in the forward gear position rotate with the drive shaft 4 and the output shaft 5 in the same direction of rotation can.
  • the gear housing or the cage 8 is also fixed by the brake lever 21b, but here the coupling pin 11 is out of engagement with the driver recess 15 on the output shaft 5 or on the output gear 3a, so that the drive wheel 2a can rotate freely together with the two intermediate wheels 6a, 6b relative to the driven wheel 3a without a torque being transmitted from the drive shaft 4 to the driven shaft 5.

Landscapes

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

Abstract

Une boîte de vitesses commutable compacte permettant une position de ralenti en plus d'une position de marche avant et de marche arrière est essentielle dans des véhicules motorisés tels que des voitures de course, voitures de tourisme, poids lourds, utilitaires ainsi que bateaux. Pour garantir un fonctionnement fiable, la boîte de vitesse doit être aisément commutable et robuste. On y parvient grâce à une boîte de vitesses (1) se présentant sous la forme d'un réducteur à pignons coniques avec un pignon d'entraînement (2a), au moins un pignon intermédiaire (6a, 6b) et un pignon de sortie (3a) dans un carter de boîte de vitesses fermé ou une cage (8). Un axe d'embrayage profilé (11) agencé entre le pignon d'entraînement (2a) et le pignon de sortie (3a) coulisse longitudinalement par rapport à l'arbre d'entrée (4) et à l'arbre de sortie (5). Dans une première position, l'arbre d'entrée (4) ou le pignon d'entrée (2a) fixé sur celui-ci engrène directement avec l'arbre de sortie (5), et dans une seconde position libère la liaison d'entraînement direct entre l'arbre d'entrée (4) et l'arbre de sortie (5). La transmission s'effectue ainsi via le réducteur à pignons coniques sur l'arbre de sortie (5) dans le sens de rotation inverse.
EP19890902039 1988-02-08 1989-02-04 Boite de vitesses commutable avec marche avant et marche arriere pour vehicules motorises ou similaire Withdrawn EP0379527A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3803726 1988-02-08
DE19883803726 DE3803726A1 (de) 1988-02-08 1988-02-08 Schaltbares getriebe, insbesondere fuer motorgetriebene fahrzeugmodelle

Publications (1)

Publication Number Publication Date
EP0379527A1 true EP0379527A1 (fr) 1990-08-01

Family

ID=6346878

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19890902039 Withdrawn EP0379527A1 (fr) 1988-02-08 1989-02-04 Boite de vitesses commutable avec marche avant et marche arriere pour vehicules motorises ou similaire

Country Status (3)

Country Link
EP (1) EP0379527A1 (fr)
DE (1) DE3803726A1 (fr)
WO (1) WO1989007210A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19730199B4 (de) * 1997-07-15 2005-06-09 Robert Bosch Gmbh Mehrganggetriebe für eine elektrische Werkzeug- oder Küchenmaschine
JP3615502B2 (ja) * 2001-08-09 2005-02-02 株式会社タミヤ エンジンを備えた玩具車両の動力伝達機構
US7390280B2 (en) * 2005-05-25 2008-06-24 Hobbico, Inc. Model vehicle transmission system
DE102013010504A1 (de) * 2013-06-25 2015-01-08 Rheinmetall Waffe Munition Gmbh Getriebe zur Drehrichtungsumschaltung
DE102019219679A1 (de) * 2019-12-16 2021-06-17 Zf Friedrichshafen Ag Schaltvorrichtung für eine Getriebevorrichtung eines Kraftfahrzeugs

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191413111A (en) * 1914-05-28 1914-12-03 John Pomeroy An Improved Reversing Gearing.
US1983835A (en) * 1931-04-25 1934-12-11 Lgs Devices Corp Marine reverse gear
US2538933A (en) * 1949-07-28 1951-01-23 Knoedler Manufacturers Inc Reversing and direct drive mechanism for a pair of shafts
US2749766A (en) * 1951-07-25 1956-06-12 Rockwell Spring & Axle Co Reverse gearing

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8907210A1 *

Also Published As

Publication number Publication date
DE3803726A1 (de) 1989-08-17
WO1989007210A1 (fr) 1989-08-10

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